CN114962222B - Advanced adiabatic compressed air energy storage energy hub equipment and modeling method thereof - Google Patents

Advanced adiabatic compressed air energy storage energy hub equipment and modeling method thereof Download PDF

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CN114962222B
CN114962222B CN202110203988.1A CN202110203988A CN114962222B CN 114962222 B CN114962222 B CN 114962222B CN 202110203988 A CN202110203988 A CN 202110203988A CN 114962222 B CN114962222 B CN 114962222B
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storage tank
temperature
transfer fluid
heat
heat storage
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CN114962222A (en
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梅生伟
陈来军
吴丹曼
魏韡
薛小代
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Tsinghua University
State Grid Hubei Electric Power Co Ltd
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State Grid Hubei Electric Power Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
    • 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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/14—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having both steam accumulator and heater, e.g. superheating accumulator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • 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
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/08—Thermal analysis or thermal optimisation
    • 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
    • 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

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  • Mechanical Engineering (AREA)
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  • General Physics & Mathematics (AREA)
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Abstract

The invention provides an advanced adiabatic compressed air energy storage energy junction device and a modeling method thereof, wherein the energy junction device comprises: the system comprises a compressor, a turbine, a heat exchanger, a gas storage tank, a heat load, an electric heating device, a heat pump and a heat storage system; the heat storage system comprises a high-temperature heat storage tank, a low-temperature heat storage tank and a normal-temperature heat storage tank; the compression side heat exchanger is connected with the inlet end of the air storage tank, and the outlet end of the air storage tank is connected with the turbine side heat exchanger; the inlet end of the high-temperature heat storage tank is respectively connected with the outlet end of the compression side heat exchanger and the electric heating device, and the outlet end of the high-temperature heat storage tank is respectively connected with the heat load and the inlet end of the turbine side heat exchanger; the inlet end of the low-temperature heat storage tank is connected with the heat pump, and the outlet end of the low-temperature heat storage tank is connected with the heat load; the inlet end of the normal temperature heat storage tank is respectively connected with the heat load and the inlet end of the turbine side heat exchanger, and the outlet end of the normal temperature heat storage tank is respectively connected with the heat pump, the electric heating device and the inlet end of the compression side heat exchanger.

Description

Advanced adiabatic compressed air energy storage energy hub equipment and modeling method thereof
Technical Field
The invention relates to the technical field of energy, in particular to advanced heat-insulating compressed air energy storage energy hub equipment and a modeling method thereof.
Background
At present, the increasingly consumed fossil energy, the increasingly increased environmental problems and the increasingly outstanding contradiction between energy supply and demand all promote the comprehensive energy system with the functions of multi-energy combined storage and multi-energy combined supply to become the necessary trend of the development of energy structures. Electric energy and heat energy have been widely studied as two main forms of daily production and living energy consumption. In order to realize coordination coupling between electricity and heat, the respective advantages of the electric heat energy source are fully exerted, the energy utilization efficiency is improved, and the comprehensive energy system of the heat and electricity also draws great attention.
The thermoelectric comprehensive energy system couples two main energy consumption modes of electric energy and heat energy based on infrastructure such as a cogeneration unit, a battery energy storage tank and a heat storage tank, can effectively realize flexible conversion between electric heat, is beneficial to improving the overall utilization efficiency of energy and reduces the energy supply cost. The energy hub serves as a core of the thermoelectric integrated energy system and plays an important role of cogeneration and combined storage. Meanwhile, the continuous development of renewable energy power generation and the increasing peak-to-valley difference of loads make the power system need more flexible adjustment resources to relieve uncertainty and provide peak shaving assistance. Advanced adiabatic compressed air energy storage (Advanced Adiabatic Compressed Air Energy Storage, abbreviated as AA-CAES) is a large-scale clean physical energy storage technology, has the combined heat and power storage characteristic naturally, and can be used as an energy hub to be connected into a thermoelectric comprehensive energy system.
Advanced adiabatic compressed air energy storage energy junction (AA-CAES energy junction for short) in the prior art generally adopts a double heat storage tank system (high temperature and normal temperature), the high temperature heat energy grade is single, and the problems of multi-grade heat energy combined storage and heat energy cascade utilization are rarely considered.
In addition, when modeling advanced adiabatic compressed air energy storage energy hubs, the AA-CAES energy hub models created in the prior art typically contain complex nonlinear differential algebraic equations, which are not useful for further studying AA-CAES optimization scheduling problems.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides advanced heat-insulating compressed air energy storage energy junction equipment and a modeling method thereof.
The invention provides an advanced adiabatic compressed air energy storage energy hub device, comprising: the system comprises a compressor, a turbine, a heat exchanger, a gas storage tank, a heat load, an electric heating device, a heat pump and a heat storage system; the heat storage system comprises a high-temperature heat storage tank, a low-temperature heat storage tank and a normal-temperature heat storage tank;
the compression side heat exchanger is connected with the inlet end of the air storage tank, and the outlet end of the air storage tank is connected with the turbine side heat exchanger; the compression side heat exchanger is a heat exchanger connected with the compressor, and the turbine side heat exchanger is a heat exchanger connected with the turbine;
The inlet end of the high-temperature heat storage tank is respectively connected with the outlet end of the compression side heat exchanger and the electric heating device, and the outlet end of the high-temperature heat storage tank is respectively connected with the heat load and the inlet end of the turbine side heat exchanger;
the inlet end of the low-temperature heat storage tank is connected with the heat pump, and the outlet end of the low-temperature heat storage tank is connected with the heat load;
the inlet end of the normal temperature heat storage tank is connected with the heat load and the outlet end of the turbine side heat exchanger respectively, and the outlet end of the normal temperature heat storage tank is connected with the inlet ends of the heat pump, the electric heating device and the compression side heat exchanger respectively.
The invention also provides a modeling method of the advanced adiabatic compressed air energy storage energy junction device, which is used for modeling the advanced adiabatic compressed air energy storage energy junction device, and comprises the following steps:
determining a device contained in the model of the advanced adiabatic compressed air energy storage energy hub device according to the structure of the advanced adiabatic compressed air energy storage energy hub device;
constructing a heat energy conversion relation in the air compression process according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger and the temperature change condition in the compression side heat exchanger;
According to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger and the temperature change condition of the air in the turbine side heat exchanger, constructing a heat energy conversion relation in the air expansion process;
according to the flow condition of the heat transfer fluid, constructing a dynamic change relation of the mass of the heat transfer fluid of each heat storage tank contained in the heat storage system;
according to the flow condition of the heat transfer fluid, constructing a quality balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment;
setting constraint conditions for a cross-grade heat supply process;
and constructing a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing the power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
According to the modeling method provided by the invention, the heat energy conversion relation of the air compression process is constructed according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger and the temperature change condition in the compression side heat exchanger, and the modeling method comprises the following steps:
For the i-th stage air compression, the thermal energy conversion relationship is:
wherein i is more than or equal to 1 and n is more than or equal to n c -1，n c Represents the last stage of air compression; c oil Representing the heat transfer fluid heat capacity, which is a constant;representing the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the ith stage of compression at the time t; />Representing the heat transfer fluid output temperature of the heat exchanger at the ith stage of compression at time t; />Representing heat transfer fluid input temperature of the heat exchanger at the ith stage of compression at time t; />Represents the heat capacity of air, which is a constant; />Air mass flow representing the compression process;representing the temperature of the air at the outlet end of the ith stage of compressor at time t; />Representing the temperature of the air at the inlet end of the i+1st stage compressor at time t;
for the final stage of air compression, the thermal energy conversion relationship is:
wherein ,n represents the air compression side c Air temperature at the outlet end of the stage heat exchanger.
According to the modeling method provided by the invention, the heat energy conversion relation of the air expansion process is constructed according to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger and the temperature change condition of the air in the turbine side heat exchanger, and the modeling method comprises the following steps:
for stage 1 air expansion, the thermal energy conversion relationship is:
wherein ,representing the high temperature tank heat transfer fluid output flow rate at time t, stage 1 expansion stage; />Representing heat transfer fluid input temperature to the heat exchanger at time t, stage 1 expansion stage; />Representing the heat transfer fluid output temperature of the heat exchanger at time t, stage 1 expansion stage; />Air mass flow representing the expansion process; />Representing the air temperature at the inlet end of the stage 1 turbine; τ st Indicating the temperature of the air storage tank;
for the j-th stage of the air expansion except the initial stage, the heat energy conversion relationship is as follows:
wherein j is more than or equal to 2 and n is more than or equal to n e ，n e Representing the final stage of air expansion;representing the high temperature tank heat transfer fluid output flow rate at time t, stage j expansion stage; />Representing heat transfer fluid input temperature of the heat exchanger at time t and in the j-th expansion stage; />Representing the heat transfer fluid output temperature of the heat exchanger at the j-th expansion stage at time t; />Representing the air temperature at the inlet end of the j-th stage turbine; />Representing the air temperature at the outlet end of the j-1 stage turbine.
According to the modeling method provided by the invention, the dynamic change relation of the heat transfer fluid quality of each heat storage tank contained in the heat storage system is constructed according to the flow condition of the heat transfer fluid, and the modeling method comprises the following steps:
the dynamic change relation of the heat transfer fluid mass in the high-temperature heat storage tank is as follows:
wherein ,representing the total mass of heat transfer fluid of the high-temperature heat storage tank at the time t+1; />Representing the total mass of heat transfer fluid of the high-temperature heat storage tank at the moment t; />The mass flow of the heat transfer fluid at the air compression side flowing into the high-temperature heat storage tank at the time t+1 is represented;the mass flow of the heat transfer fluid flowing from the normal-temperature heat storage tank to the high-temperature heat storage tank at the time t+1 and heated by the electric heating device is shown; />Indicating the high temperature heat storage at the time t+1The tank outputting a mass flow rate for the heat transfer fluid on the expansion side; />The mass flow of the high-temperature heat storage tank for supplying high-temperature heat load output at the time t+1 is shown; />The mass flow of the high-temperature heat storage tank for supplying low-temperature heat load output at the time t+1 is shown;
compression side high temperature heat transfer fluid mass flow flowing into high temperature heat storage tank at time t+1The sum of the input mass flow rates of the heat transfer fluid of the high-temperature heat storage tank in each air compression stage at the moment t+1; namely:
wherein ,representing the input mass flow rate of the heat transfer fluid of the high-temperature heat storage tank in the ith stage of compression at the time t+1;
the high-temperature heat storage tank outputs mass flow to heat transfer fluid at expansion side at time t+1The sum of the output mass flow rates of the heat transfer fluid of the high-temperature heat storage tank in each air expansion stage at the moment t+1; namely:
wherein ,representing the output mass flow rate of heat transfer fluid of high-temperature heat storage tank in ith stage expansion stage at t+1 moment ；
The dynamic change relation of the heat transfer fluid mass in the low-temperature heat storage tank is as follows:
wherein ,representing the total mass of the heat transfer fluid of the low-temperature heat storage tank at the time t+1; />Representing the total mass of the heat transfer fluid of the low-temperature heat storage tank at the moment t; />The mass flow of the normal-temperature heat transfer fluid which flows from the normal-temperature heat storage tank to the low-temperature heat storage tank at the time t+1 and is heated by the heat pump is shown; />The mass flow of the low-temperature heat storage tank output to the low-temperature heat load at the time t+1 is shown;
the dynamic change relation of the heat transfer fluid mass in the normal temperature heat storage tank is as follows:
wherein ,the total mass of the heat transfer fluid of the normal-temperature heat storage tank at the time t+1 is shown; />The total mass of heat transfer fluid of the normal-temperature heat storage tank at the moment t is represented; />Indicating the expansion from air at time t+1The heat exchanger on the expansion side flows into the mass flow of the heat transfer fluid of the normal temperature heat storage tank, wherein the heat transfer fluid releases heat; />The mass flow of the heat transfer fluid at the outlet side of the high-temperature heat storage supply high-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the heat transfer fluid at the outlet side of the high-temperature heat storage supply low-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the heat transfer fluid at the outlet side of the low-temperature heat storage supply low-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the normal-temperature heat transfer fluid which is output from the normal-temperature heat storage tank at the time t+1 and is used for heat collection in the air compression process is shown; / >The mass flow of the heat transfer fluid flowing from the normal-temperature heat storage tank to the high-temperature heat storage tank at the time t+1 and heated by the electric heating device is shown; />The mass flow of the normal-temperature heat transfer fluid which flows from the normal-temperature heat storage tank to the low-temperature heat storage tank at the time t+1 and is heated by the heat pump is shown;
normal temperature heat transfer fluid mass flow for air compression process heat collection at time t+1Is equal to the sum of the mass flow of the normal-temperature heat transfer fluid consumed by each compression stage; namely:
wherein ,the output mass flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the ith stage of compression at the time t+1 is shown;
mass flow of heat transfer fluid released heat flowing from heat exchanger on air expansion side into normal temperature heat storage tank at time t+1Equal to the sum of the mass flow rates of the heat transfer fluid consumed by the respective turboexpansion stages; namely:
wherein ,and the input mass flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the j-th expansion stage at the time t+1 is shown.
According to the modeling method provided by the invention, the mass balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment is constructed according to the flow condition of the heat transfer fluid, and the modeling method comprises the following steps:
in the air compression process, the total input mass flow of the heat transfer fluid of the high-temperature heat storage tank is equal to the total output mass flow of the heat transfer fluid of the normal-temperature heat storage tank, and the input mass flow of the heat transfer fluid of the high-temperature heat storage tank in each compression stage is equal to the corresponding output mass flow of the normal-temperature heat storage tank in each compression stage;
In the air expansion process, the total output mass flow of the heat transfer fluid of the high-temperature heat storage tank is equal to the total input mass flow of the heat transfer fluid of the normal-temperature heat storage tank, and the output mass flow of the heat transfer fluid of the high-temperature heat storage tank in each expansion stage is equal to the corresponding input mass flow of the normal-temperature heat storage tank in each expansion stage;
for heat exchangers on the heat load supply side, the mass flow rate of the heat transfer fluid input of each grade is equal to the corresponding output mass flow rate.
According to the modeling method provided by the invention, constraint conditions are set for a cross-grade heat supply process, and the modeling method comprises the following steps:
for a normal temperature heat storage tank, the set constraint conditions include:
the normal temperature heat transfer fluid available in the normal temperature heat storage tank is firstly used for heat collection in the air compression process, and then provides heat energy supplement for other heat storage tanks;
for a low temperature heat storage tank, the constraints set include:
the output of the heat transfer fluid used for supplying low-temperature heat load in the low-temperature heat storage tank does not exceed the remaining usable range of the low-temperature heat storage tank;
for a high temperature heat storage tank, the constraints set include:
the available high temperature heat transfer fluid in the high temperature heat storage tank preferentially meets the air expansion heating demand and is then used for heat load supply.
According to the modeling method provided by the invention, the power consumption model is built for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and the power consumption model is built for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and the modeling method comprises the following steps:
according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, a power consumption model constructed for the electric heating device is as follows:
wherein ,indicating the power consumption of the electric heating device at time t, eta H Indicating the efficiency of the electric heating device, Δτ H Represents the difference between the rated high-temperature heat storage tank temperature and the normal-temperature heat storage tank temperature, τ H Indicating rated high-temperature heat storage tank temperature, tau O Representing the temperature of the normal-temperature heat storage tank; c oil Representing heat transfer fluid heat capacity; />The mass flow of the heat transfer fluid flowing from the normal-temperature heat storage tank to the high-temperature heat storage tank and heated by the electric heating device at the moment t is shown;
according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, a power consumption model constructed for the heat pump is as follows:
wherein ,representing the power consumption of the heat pump at time t, eta L Indicating the efficiency of the heat pump, deltaτ L Represents the difference between the rated low-temperature heat storage tank temperature and the normal-temperature heat storage tank temperature, τ L Representing the rated low-temperature heat storage tank temperature; />The mass flow of the normal temperature heat transfer fluid heated by the heat pump flowing from the normal temperature heat storage tank to the low temperature heat storage tank at time t is shown.
According to the modeling method provided by the invention, the method further comprises the following steps:
simulating the power consumption condition of the compressor, and setting air mass flow constraint conditions of the compressor in each compression stage; the method specifically comprises the following steps:
at time t, the power consumption required by the ith stage of compressor satisfies the following equation:
wherein ,representing the electric power consumed by the i-th stage air compression at time t; />Representing the mass air flow during compression at time t; />Representing the heat capacity of air; />Representing the i-th stage compressor inlet air temperature at time t; />Representing the efficiency of the i-th stage compressor; />Represents the compression ratio of the i-th stage compressor, < ->Indicates the outflow pressure of the i-th stage compressor at time t,/>The inflow air pressure of the ith stage compressor at the time t; kappa represents the air insulation index;
the total power consumption of all compressors meets the following conditions:
wherein Indicating the total charging power at time t; n is n c Representing the total number of compression stages;
the mass air flow of each compression stage satisfies:
wherein A binary variable indicating a state of charge at time t; / >Representing the mass air flow during compression at time t; />Lower bound representing the mass air flow in the compression phase, < ->Representing the upper bound of the mass air flow in the compression stage.
According to the modeling method provided by the invention, the method further comprises the following steps:
simulating the working power condition of the turbine, and setting air mass flow constraint conditions of the turbine in each expansion stage; the method specifically comprises the following steps:
at the time t, the j-th stage turbine working power meets the following conditions:
wherein ,the j-th stage air expansion power generation at the time t is shown; />Representing the mass air flow during expansion at time t; />Representing the inlet air temperature of the jth stage turbine at time t; />Representing the expansion ratio of the jth stage expander; />Representing the efficiency of the j-th stage expander;
the total acting power of all turbines meets the following conditions:
wherein Indicating the total discharge power at time t; n is n e Representing the total expansion progression;
the mass air flow of each expansion stage satisfies:
wherein A binary variable indicating a discharge state at time t; />Representing the mass air flow during expansion at time t; />Lower bound representing the mass air flow during the expansion phase, < ->Representing the upper bound of mass airflow during the expansion phase.
According to the modeling method provided by the invention, the method further comprises the following steps:
simulating the air pressure change condition for the air storage tank; the method specifically comprises the following steps:
the air pressure change condition of the air storage tank in two continuous time periods is expressed by the following formula:
wherein ,the air pressure of the air storage tank at the time t is shown; />The air pressure of the air storage tank at the time t+1 is shown; v represents the volume of the air storage tank; r is R g Represents the air gas constant; τ st Indicating the temperature of the air storage tank; />A binary variable indicating a state of charge at time t; />A binary variable indicating a discharge state at time t; />Representing the mass air flow during compression at time t; />The mass airflow during expansion at time t is indicated.
According to the modeling method provided by the invention, the method further comprises the following steps:
simulating a thermal load supply condition and an electrical load supply condition in the advanced adiabatic compressed air energy storage energy hub device; the method specifically comprises the following steps:
the supply model of the high-temperature heat load is as follows:
wherein ,representing the thermal energy supplying the high temperature thermal load; Δτ Hd Representing the temperature difference between the front and back of the high temperature heat transfer fluid supply high temperature heat load; c oil Representing heat transfer fluid heat capacity; />The mass flow of the high-temperature heat storage tank for supplying high-temperature heat load output at the moment t is shown;
The low temperature thermal load supply model is as follows:
wherein ,representing the thermal energy supplied to the low temperature thermal load; Δτ Ld Representing the temperature difference between the front and back of the low temperature heat transfer fluid supply low temperature heat load; Δτ HLd Representing the temperature difference between the front and back of the high temperature heat transfer fluid supply low temperature heat load; />The mass flow of the high-temperature heat storage tank output to the low-temperature heat load at the moment t is represented; />The mass flow of the low-temperature heat storage tank output to the low-temperature heat load at the moment t is represented;
the electrical load supply model is:
wherein ,representing the supply electric power of the AA-CAES energy hub device electric load at the time t; />The method comprises the steps that the electricity purchasing power of AA-CAES energy hub equipment from a power grid at the time t is represented; />Indicating the power consumption of the electric heating device at time t; />Representing the power consumption of the heat pump at time t; />Indicating the total charging power at time t; />Indicating the total discharge power at time t.
The invention also provides a modeling device of the advanced adiabatic compressed air energy storage energy junction device, which is used for modeling the advanced adiabatic compressed air energy storage energy junction device, and comprises:
the device determining module is used for determining the device contained in the advanced adiabatic compressed air energy storage energy junction equipment model according to the structure of the advanced adiabatic compressed air energy storage energy junction equipment;
The heat energy conversion relation construction module is used for constructing the heat energy conversion relation of the air compression process according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger and the temperature change condition of the heat transfer fluid in the compression side heat exchanger;
the heat energy conversion relation construction module is used for constructing the heat energy conversion relation of the air expansion process according to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger and the temperature change condition of the air in the turbine side heat exchanger;
the heat transfer fluid quality dynamic change relation construction module is used for constructing the dynamic change relation of the heat transfer fluid quality of each heat storage tank contained in the heat storage system according to the flow condition of the heat transfer fluid;
the heat transfer fluid quality balance relation construction module is used for constructing a quality balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment according to the flow condition of the heat transfer fluid;
the constraint condition setting module is used for setting constraint conditions for the cross-grade heat supply process;
the power consumption model construction module is used for constructing a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing a power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
The invention also provides an electronic device comprising a memory, a processor and a computer program stored on the memory and executable on the processor, wherein the processor implements the steps of the modeling method of the advanced adiabatic compressed air energy storage energy hub device when the program is executed.
The present invention also provides a non-transitory computer readable storage medium having stored thereon a computer program which, when executed by a processor, implements the steps of the modeling method of the advanced adiabatic compressed air energy storage energy hub device.
According to the advanced heat-insulating compressed air energy storage energy junction device and the modeling method thereof, provided by the invention, through arranging the heat storage tanks with different temperatures in the heat storage system, the combined storage and the gradient utilization of various grade heat energy are realized, and the utilization efficiency of the heat energy can be improved.
Drawings
In order to more clearly illustrate the invention or the technical solutions of the prior art, the following description will briefly explain the drawings used in the embodiments or the description of the prior art, and it is obvious that the drawings in the following description are some embodiments of the invention, and other drawings can be obtained according to the drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic diagram of the structure of an advanced adiabatic compressed air energy storage energy hub device provided by the present invention;
FIG. 2 is a flow chart of a method of modeling an advanced adiabatic compressed air energy storage energy hub device provided by the present invention;
FIG. 3 is a schematic structural diagram of an advanced adiabatic compressed air energy storage energy hub device modeling apparatus provided by the present invention;
fig. 4 is a schematic structural diagram of an electronic device provided by the present invention.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is apparent that the described embodiments are some embodiments of the present invention, not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The advanced adiabatic compressed air energy storage energy hub device and modeling method of the present invention are described below in conjunction with fig. 1-3.
Fig. 1 is a schematic structural diagram of an advanced adiabatic compressed air energy storage energy hub device provided by the present invention, and as shown in fig. 1, the advanced adiabatic compressed air energy storage energy hub device provided by the present invention includes: the system comprises a compressor, a turbine, a heat exchanger, a gas storage tank, a heat load, an electric heating device, a heat pump and a heat storage system; the heat storage system comprises a high-temperature heat storage tank, a low-temperature heat storage tank and a normal-temperature heat storage tank.
The advanced adiabatic compressed air energy storage energy hub device of the present invention has a multi-stage compression and a multi-stage turbine, and in the embodiment shown in fig. 1, the multi-stage compression is a two-stage compression, and the compressor includes a first stage compressor and a second stage compressor. The multi-stage turbine is a two-stage turbine, and the turbine comprises a first-stage turbine and a second-stage turbine.
Referring to fig. 1, the connection relationship between each component in the advanced adiabatic compressed air energy storage energy junction device of the present invention is:
the outlet end of the first-stage compressor is connected with the first inlet end of the first heat exchanger; the first outlet end of the first heat exchanger is connected with the inlet end of the second-stage compressor; the outlet end of the second-stage compressor is connected with the first inlet end of the second heat exchanger; the first outlet end of the second heat exchanger is connected with the inlet end of the air storage tank; the outlet end of the air storage tank is connected with the first inlet end of the third heat exchanger, the first outlet end of the third heat exchanger is connected with the inlet end of the first-stage turbine, the outlet end of the first-stage turbine is connected with the first inlet end of the fourth heat exchanger, and the first outlet end of the fourth heat exchanger is connected with the inlet end of the second-stage turbine.
The second inlet end of the fourth heat exchanger is connected with the outlet end of the high-temperature heat storage tank, and the second outlet end of the fourth heat exchanger is connected with the inlet end of the normal-temperature heat storage tank; the second inlet end of the third heat exchanger is connected with the outlet end of the high-temperature heat storage tank, and the second outlet end of the third heat exchanger is connected with the inlet end of the normal-temperature heat storage tank; the second inlet end of the second heat exchanger is connected with the outlet end of the normal-temperature heat storage tank, and the second outlet end of the second heat exchanger is connected with the inlet end of the high-temperature heat storage tank; the second inlet end of the first heat exchanger is connected with the outlet end of the normal-temperature heat storage tank, and the second outlet end of the first heat exchanger is connected with the inlet end of the high-temperature heat storage tank.
The inlet end of the high-temperature heat storage tank is also connected with the electric heating device, and the outlet end of the high-temperature heat storage tank is also connected with the inlet end of the high-temperature heat load and the inlet end of the low-temperature heat load respectively; the inlet end of the low-temperature heat storage tank is connected with the outlet end of the heat pump, and the outlet end of the low-temperature heat storage tank is connected with the inlet end of the low-temperature heat load; the inlet end of the normal temperature heat storage tank is also connected with the outlet end of the high temperature heat load and the outlet end of the low temperature heat load respectively, and the outlet end of the normal temperature heat storage tank is also connected with the inlet ends of the heat pump and the electric heating device respectively.
In this embodiment, the heat storage temperature of the high-temperature heat storage tank is about 300 ℃, the heat storage temperature of the low-temperature heat storage tank is about 120 ℃, and the heat storage temperature of the normal-temperature heat storage tank is about 25 ℃.
In this embodiment, the thermal load with a temperature demand in the range of 260-300 ℃ is a thermal load; the heat load with the temperature requirement in the range of 80-120 ℃ belongs to the low temperature heat load.
In the embodiment shown in fig. 1, although only one high-temperature heat storage tank, one low-temperature heat storage tank and one normal-temperature heat storage tank are identified, it should be understood by those skilled in the art that the number of the three types of energy storage tanks is not limited to only one each, and the number thereof can be adjusted according to practical situations.
In the embodiment shown in fig. 1, the compressor and turbine are each provided with two stages reflecting the number of stages of gas compression and expansion. In practical applications, the number of stages of the compressor and the turbine can be adjusted according to practical conditions.
In the embodiment shown in fig. 1, the heat exchangers connected to the compressor (i.e., the first heat exchanger and the second heat exchanger) are denoted as compression side heat exchangers, and the heat exchangers connected to the turbine (i.e., the third heat exchanger and the fourth heat exchanger) are denoted as turbine side (or expansion side) heat exchangers.
In this embodiment, the inlet and outlet ends of the air tank are provided with throttle valves for air pressure regulation.
In the energy storage process of the advanced adiabatic compressed air energy storage energy hub device provided by the invention, the first-stage compressor compresses air into high-pressure air by utilizing external residual electric energy, and simultaneously, the compression heat in the air compression process is transferred to the heat transfer fluid through the first heat exchanger, and the heat transfer fluid flows from the normal-temperature heat storage tank to the high-temperature heat storage tank; the second-stage compressor compresses air into high-pressure air by utilizing external residual electric energy, and simultaneously, the compression heat in the air compression process is transferred to the heat transfer fluid through the second heat exchanger, and the heat transfer fluid at the moment also flows from the normal-temperature heat storage tank to the high-temperature heat storage tank. The compressed high-pressure gas is stored in a gas storage tank. The heat transfer fluid output by the normal temperature heat storage tank can be heated by the electric heating device and input into the high temperature heat storage tank, and can be heated by the heat pump and input into the low temperature heat storage tank besides being heated by the first heat exchanger and the second heat exchanger and input into the high temperature heat storage tank.
In the process of releasing energy, the advanced adiabatic compressed air energy storage energy junction device releases high-pressure gas in the gas storage tank, the high-pressure gas absorbs heat released by the heat transfer fluid in the third heat exchanger, the heat transfer fluid flows from the high-temperature heat storage tank to the normal-temperature heat storage tank, and the high-pressure gas absorbs heat and expands in the first-stage turbine; the high-pressure gas also absorbs heat released by the heat transfer fluid in the fourth heat exchanger, the heat transfer fluid flows from the high-temperature heat storage tank to the normal-temperature heat storage tank, and the high-pressure gas absorbs heat and expands in the second-stage turbine; the gas after absorbing heat and expanding drives a generator to generate electricity. The heat transfer fluid output by the high-temperature heat storage tank releases heat through the third heat exchanger and the fourth heat exchanger and is input into the normal-temperature heat storage tank, and releases heat through the high-temperature heat load and the low-temperature heat load and is finally input into the normal-temperature heat storage tank. The heat transfer fluid output by the low-temperature heat storage tank releases heat through low-temperature heat load and is finally input into the normal-temperature heat storage tank.
The above is an explanation of the structure of the advanced adiabatic compressed air energy storage energy junction device provided by the invention, and the energy storage process and the energy release process thereof.
As can be seen from the above description, the energy junction device of the present invention converts the external surplus electric energy into the internal air energy and the heat energy during the energy storage process, and stores the internal air energy and the heat energy through the air tank and the heat storage tank, respectively; in the energy release process, the internal energy and the heat energy in the air are converted into mechanical energy, and then the mechanical energy drives the generator to generate electricity.
According to the advanced heat-insulating compressed air energy storage energy junction device provided by the invention, through arranging the heat storage tanks with different temperatures in the heat storage system, the combined storage and the gradient utilization of various grade heat energy are realized, and the utilization efficiency of the heat energy can be improved.
Based on any embodiment, the invention also provides a modeling method of the advanced heat-insulating compressed air energy storage energy hub device. FIG. 2 is a flowchart of a modeling method of an advanced adiabatic compressed air energy storage energy hub device according to the present invention, as shown in FIG. 2, where the modeling method of the present invention includes:
step 201, determining a device contained in the advanced adiabatic compressed air energy storage energy junction device model according to the structure of the advanced adiabatic compressed air energy storage energy junction device.
In the present invention, the model refers to the structure of an advanced adiabatic compressed air energy storage energy junction device and its mathematical description, which is also a simulation of the transmission, conversion and storage of various forms of energy in the energy junction device.
In the previous embodiments, the structure of the advanced adiabatic compressed air energy storage energy hub device has been described. Thus, in this step, the means comprised in the model of the advanced adiabatic compressed air energy storage energy junction device may be determined based on the structure of the advanced adiabatic compressed air energy storage energy junction device. For example, advanced adiabatic compressed air energy storage energy hub plant models should include compressors, turbines, air storage tanks, high temperature heat storage tanks, low temperature heat storage tanks, and normal temperature heat storage tanks, among others.
The modeled model is based on the following assumptions:
1) The air parameters meet the ideal gas equation;
2) The heat capacity of air and heat transfer fluid is constant;
3) The air storage tank is maintained at the ambient temperature, and the three types of heat storage tanks also maintain respective constant temperatures;
4) The heat transfer fluid booster pump power consumption and the loss of thermal energy and air pressure are ignored.
And 202, constructing a heat energy conversion relation in the air compression process according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the air compression side heat exchanger and the temperature change condition of air in the air compression side heat exchanger.
The advanced adiabatic compressed air energy storage energy hub device comprises a multi-stage compressor, and can realize multi-stage air compression.
The final stage of air compression and the other stages of air compression are described separately with respect to certain differences in the description of the heat energy conversion relationship.
According to the law of conservation of energy, for the ith (1.ltoreq.i.ltoreq.n) c -1，n c The last stage representing air compression) stage air compression, the thermal energy conversion relationship is:
wherein ,coil Representing the heat transfer fluid heat capacity, which is a constant;representing the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the ith stage of compression at the time t; />Representing the heat transfer fluid output temperature of the heat exchanger at the ith stage of compression at time t; />Representing heat transfer fluid input temperature of the heat exchanger at the ith stage of compression at time t; />Represents the heat capacity of air, which is a constant; />Air mass flow representing the compression process; />Representing the temperature of the air at the outlet end of the ith stage of compressor at time t; />The temperature of the air at the inlet end of the i+1st stage compressor at time t is indicated.
For the last phase of air compression (i=n c ) The heat energy conversion relationship is as follows:
wherein ,n represents the air compression side c The air temperature at the outlet end of the stage heat exchanger and the meaning of other parameters in the formula can be determined according to the meaning of the parameters in the previous formula.
And 203, constructing a heat energy conversion relation in the air expansion process according to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the air expansion side heat exchanger and the temperature change condition of the air in the air expansion side heat exchanger.
The advanced adiabatic compressed air energy storage energy hub device comprises a multi-stage turbine, and can realize multi-stage air expansion.
The initial stage of air expansion (stage 1) and the other stages of air expansion are described separately with a certain difference in the description of the heat energy conversion relationship.
According to the law of conservation of energy, for stage 1 air expansion, the thermal energy conversion relationship is:
wherein ,representing the high temperature tank heat transfer fluid output flow rate at time t, stage 1 expansion stage; />Representing heat transfer fluid input temperature to the heat exchanger at time t, stage 1 expansion stage; />Representing the heat transfer fluid output temperature of the heat exchanger at time t, stage 1 expansion stage; />Air mass flow representing the expansion process; />Representing the air temperature at the inlet end of the stage 1 turbine; τ st Indicating the temperature of the air reservoir.
For other stages (j-th stage, 2. Ltoreq.j.ltoreq.n) than the initial stage in the air expansion e ，n e Representing the final stage of air expansion), the thermal energy conversion relationship is:
wherein ,representing the high temperature tank heat transfer fluid output flow rate at time t, stage j expansion stage; />Representing heat transfer fluid input temperature of the heat exchanger at time t and in the j-th expansion stage; />Representing the heat transfer fluid output temperature of the heat exchanger at the j-th expansion stage at time t; />Representing the air temperature at the inlet end of the j-th stage turbine; />Representing the air temperature at the outlet end of the j-1 stage turbine.
And 204, constructing a dynamic change relation of the heat transfer fluid quality of each heat storage tank according to the flow condition of the heat transfer fluid.
In the foregoing description, it has been mentioned that the advanced adiabatic compressed air energy storage energy junction device of the present invention includes a high temperature heat storage tank, a low temperature heat storage tank, and a normal temperature heat storage tank. The flow of the heat transfer fluid in the different types of heat storage tanks is different and in this embodiment is described separately.
For the high-temperature heat storage tank, the input heat transfer fluid includes the heat transfer fluid input from the heat exchanger on the air compression side, and the heat transfer fluid input from the normal-temperature heat storage tank via the electric heating device; the heat transfer fluid to be outputted includes a heat transfer fluid to be outputted to an air expansion side heat exchanger, a heat transfer fluid to be outputted to a high temperature heat load, and a heat transfer fluid to be outputted to a low temperature heat load.
According to the law of conservation of mass, the dynamic change relation of the mass of the heat transfer fluid in the high-temperature heat storage tank is as follows:
wherein ,representing the total mass of heat transfer fluid of the high-temperature heat storage tank at the time t+1; />Representing the total mass of heat transfer fluid of the high-temperature heat storage tank at the moment t; />The mass flow of the heat transfer fluid at the air compression side flowing into the high-temperature heat storage tank at the time t+1 is represented;the mass flow of the heat transfer fluid flowing from the normal-temperature heat storage tank to the high-temperature heat storage tank at the time t+1 and heated by the electric heating device is shown; />The output mass flow of the high-temperature heat storage tank to the heat transfer fluid at the expansion side at the time t+1 is shown; />The mass flow of the high-temperature heat storage tank for supplying high-temperature heat load output at the time t+1 is shown; />And the mass flow of the high-temperature heat storage tank at the time t+1 for supplying low-temperature heat load output is shown. />
In the formula, the mass flow of the compression-side high-temperature heat transfer fluid flowing into the high-temperature heat storage tank at time t+1And the sum of the input mass flow rates of the heat transfer fluid of the high-temperature heat storage tank in each air compression stage at the time t+1 is equal. Namely:
wherein ,and the input mass flow rate of the heat transfer fluid of the high-temperature heat storage tank in the ith stage of compression stage at the time t+1 is shown.
Similarly, the high temperature heat storage tank at time t+1 outputs a mass flow rate to the heat transfer fluid on the expansion sideAnd the sum of the output mass flow rate of the heat transfer fluid of the high-temperature heat storage tank in each air expansion stage at the time t+1 is equal. Namely:
wherein ,and the output mass flow rate of the heat transfer fluid of the high-temperature heat storage tank in the ith stage expansion stage at the time t+1 is shown.
For a low temperature heat storage tank, the input heat transfer fluid comprises the heat transfer fluid input from the normal temperature heat storage tank via the heat pump, and the output heat transfer fluid comprises the heat transfer fluid output to the low temperature heat load.
According to the law of conservation of mass, the dynamic change relation of the mass of the heat transfer fluid in the low-temperature heat storage tank is as follows:
wherein ,representing the total mass of the heat transfer fluid of the low-temperature heat storage tank at the time t+1; />Representing the total mass of the heat transfer fluid of the low-temperature heat storage tank at the moment t; />The mass flow of the normal-temperature heat transfer fluid which flows from the normal-temperature heat storage tank to the low-temperature heat storage tank at the time t+1 and is heated by the heat pump is shown; />And the mass flow of the low-temperature heat storage tank output to the low-temperature heat load at the time t+1 is shown.
For the normal temperature heat storage tank, the input heat transfer fluid includes the heat transfer fluid input from the heat exchanger on the air expansion side, the heat transfer fluid input from the high temperature heat load and the low temperature heat load; the heat transfer fluid to be output includes the heat transfer fluid to be output to the heat exchanger on the air compression side, the heat transfer fluid to be output to the high-temperature heat storage tank (via the electric heating device), and the heat transfer fluid to be output to the low-temperature heat storage tank (via the heat pump).
According to the law of conservation of mass, the dynamic change relation of the mass of the heat transfer fluid in the normal-temperature heat storage tank is as follows:
wherein ,the total mass of the heat transfer fluid of the normal-temperature heat storage tank at the time t+1 is shown; />The total mass of heat transfer fluid of the normal-temperature heat storage tank at the moment t is represented; />The mass flow of the heat transfer fluid which flows into the normal-temperature heat storage tank from the heat exchanger at the air expansion side at the time t+1 and releases heat is shown; />The mass flow of the heat transfer fluid at the outlet side of the high-temperature heat storage supply high-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the heat transfer fluid at the outlet side of the high-temperature heat storage supply low-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the heat transfer fluid at the outlet side of the low-temperature heat storage supply low-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the normal-temperature heat transfer fluid which is output from the normal-temperature heat storage tank at the time t+1 and is used for heat collection in the air compression process is shown; />The mass flow of the heat transfer fluid flowing from the normal-temperature heat storage tank to the high-temperature heat storage tank at the time t+1 and heated by the electric heating device is shown; />Indicating the heated air flowing from the normal temperature heat storage tank to the low temperature heat storage tank at time t+1Pump heated ambient temperature heat transfer fluid mass flow.
In the formula, the mass flow of the normal-temperature heat transfer fluid for heat collection in the air compression process at the time t+1 Is equal to the sum of the mass flow rates of the normal temperature heat transfer fluid consumed by each compression stage. Namely:
wherein ,and the output mass flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the ith stage of compression stage at the time t+1 is shown.
Mass flow of heat transfer fluid released heat flowing from heat exchanger on air expansion side into normal temperature heat storage tank at time t+1Equal to the sum of the mass flows of heat transfer fluid consumed by the respective turboexpansion stages. Namely:
wherein ,and the input mass flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the j-th expansion stage at the time t+1 is shown.
It should be noted that the mass of the heat transfer fluid in each heat storage tank does not exceed the capacity range of the respective heat storage tank, namely:
wherein ,mH,l Indicating a high temperature heat storage tankA lower mass bound of the heat transfer fluid; m is m H,u Representing the upper mass bound of the high temperature heat storage tank heat transfer fluid; m is m L,l Representing the lower mass bound of the low temperature heat storage tank heat transfer fluid; m is m L,u Representing the upper mass bound of the low temperature heat storage tank heat transfer fluid; m is m O,l Representing the mass lower boundary of the heat transfer fluid of the normal temperature heat storage tank; m is m O,u The upper mass limit of the heat transfer fluid of the normal temperature heat storage tank is shown.
Step 205, constructing a quality balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment according to the flow condition of the heat transfer fluid.
In the air compression process, the total input mass flow of the heat transfer fluid of the high-temperature heat storage tank is equal to the total output mass flow of the heat transfer fluid of the normal-temperature heat storage tank, and the input mass flow of the heat transfer fluid of the high-temperature heat storage tank in each compression stage is equal to the corresponding output mass flow of the normal-temperature heat storage tank in each compression stage. Namely:
wherein ,the mass flow of the heat transfer fluid at the air compression side flowing into the high-temperature heat storage tank at the time t+1 is represented;representing the input mass flow rate of the heat transfer fluid of the high-temperature heat storage tank in the ith stage of compression at the time t+1; />The mass flow of the normal-temperature heat transfer fluid which is output from the normal-temperature heat storage tank at the time t+1 and is used for heat collection in the air compression process is shown; />And the output mass flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the ith stage of compression stage at the time t+1 is shown.
In the air expansion process, the total output mass flow of the heat transfer fluid of the high-temperature heat storage tank is equal to the total input mass flow of the heat transfer fluid of the normal-temperature heat storage tank, and the output mass flow of the heat transfer fluid of the high-temperature heat storage tank in each expansion stage is equal to the corresponding input mass flow of the normal-temperature heat storage tank in each expansion stage. Namely:
wherein ,the output mass flow of the high-temperature heat storage tank to the heat transfer fluid at the expansion side at the time t+1 is shown;representing the output mass flow rate of the heat transfer fluid of the high-temperature heat storage tank in the ith stage expansion stage at the time t+1; / >The mass flow of the heat transfer fluid which flows into the normal-temperature heat storage tank from the heat exchanger at the air expansion side at the time t+1 and releases heat is shown; />And the input mass flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the j-th expansion stage at the time t+1 is shown.
For heat exchangers on the heat load supply side, the mass flow rate of the heat transfer fluid input of each grade is equal to the corresponding output mass flow rate. Namely:
wherein ,the mass flow of the heat transfer fluid at the outlet side of the high-temperature heat storage supply high-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the high-temperature heat storage tank for supplying high-temperature heat load output at the time t+1 is shown; />The mass flow of the heat transfer fluid at the outlet side of the high-temperature heat storage supply low-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the high-temperature heat storage tank for supplying low-temperature heat load output at the time t+1 is shown; />The mass flow of the heat transfer fluid at the outlet side of the low-temperature heat storage supply low-temperature heat load heat exchanger at the time t+1 is shown; />And the mass flow of the low-temperature heat storage tank output to the low-temperature heat load at the time t+1 is shown.
Step 206, setting constraint conditions for the cross-grade heat supply process.
In the advanced adiabatic compressed air energy storage energy hub device of the present invention, the use of a high temperature heat transfer fluid is allowed to meet low temperature thermal load requirements when the low temperature heat transfer fluid is insufficient. When the low temperature heat transfer fluid is sufficient, the higher grade heat energy is prohibited from supplying the low temperature demand.
For this reason, constraints need to be set for the cross-grade heating process. The method specifically comprises the following steps:
for normal temperature heat storage tanks:
wherein ,the mass flow of the normal-temperature heat transfer fluid which is output from the normal-temperature heat storage tank at the moment t and is used for heat collection in the air compression process is represented; />The total mass of heat transfer fluid of the normal-temperature heat storage tank at the moment t is represented; m is m O,l Representing the mass lower boundary of the heat transfer fluid of the normal temperature heat storage tank; />The mass flow of the normal-temperature heat transfer fluid which flows from the normal-temperature heat storage tank to the low-temperature heat storage tank and is heated by the heat pump at the moment t is shown; />And the mass flow of the heat transfer fluid flowing from the normal-temperature heat storage tank to the high-temperature heat storage tank and heated by the electric heating device at the time t is shown.
From the above constraints, it can be seen that the normal temperature heat transfer fluid available in the normal temperature heat storage tank is first used for heat collection during air compression and then provides thermal energy replenishment for the other heat storage tanks.
For low temperature heat storage tanks:
wherein ,the mass flow of the low-temperature heat storage tank output to the low-temperature heat load at the moment t is represented; />Low-temperature heat storage tank for indicating t momentThe total mass of the heat transfer fluid; m is m L,l Representing the lower mass bound of the low temperature heat storage tank heat transfer fluid; z 1 As binary variable, M 1 Is a sufficiently large number.
From the above constraints, it can be seen that the heat transfer fluid output for supplying the low temperature heat load should not exceed the remaining usable range of the low temperature heat storage tank.
If the residual heat transfer fluid of the available low-temperature heat storage tank is not less than the low-temperature heat load demand, the variable z is calculated 1 Setting to 0, and heating by a low-temperature heat storage tank; when the heat transfer fluid of the low-temperature heat storage tank is insufficient, the variable z is obtained 1 And the heat supply of the low-temperature heat storage tank is stopped by setting the heat storage tank to be 1, and the heat supply auxiliary of the higher-grade heat storage is activated.
wherein ,the output mass flow of the high-temperature heat storage tank to the heat transfer fluid at the expansion side at the moment t is shown; />Representing the total mass of heat transfer fluid of the high-temperature heat storage tank at the moment t; m is m H,l Representing a lower mass bound of the high temperature heat storage tank heat transfer fluid;the mass flow of the high-temperature heat storage tank for supplying high-temperature heat load output at the moment t is shown; />And the mass flow of the high-temperature heat storage tank for supplying low-temperature heat load output at the time t is shown.
From the above constraints, it can be seen that the available high temperature heat transfer fluid in the high temperature heat storage tank should preferentially meet the air expansion heating demand and then be used for heat load supply. If z 1 And 0, wherein the lower grade heat energy heat storage tank has enough surplus, and the cross grade heat supply output flow of the high temperature heat storage tank is forced to be 0. When the high-temperature heat storage tank receives z 1 The signal of =1, then the cross-grade heating works and the cross-grade heating output should be the remainder for air expansion heating and supply of the thermal load.
And 207, constructing a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing a power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
Since each heat storage tank is maintained at a constant temperature, the electric heating device and the heat pump need to heat the normal temperature heat transfer fluid to the rated temperature of the heat storage tank. The electric power consumption model of the electric heating device and the heat pump is as follows:
wherein ,indicating the power consumption of the electric heating device at time t, < >>Representing the power consumption of the heat pump at time t, eta H Indicating the efficiency, eta of the electric heating device L Indicating the efficiency of the heat pump, deltaτ H Represents the difference between the rated high-temperature heat storage tank temperature and the normal-temperature heat storage tank temperature, delta tau L Represents the difference between the rated low-temperature heat storage tank temperature and the normal-temperature heat storage tank temperature, τ H Indicating rated high-temperature heat storage tank temperature, tau L Indicating rated low-temperature heat storage tank temperature, tau O The temperature of the normal temperature heat storage tank is shown.
The above is a description of the relevant steps of the method of the invention.
As can be seen from the above description, although the compression ratio and expansion ratio of the compression side and expansion side of the advanced adiabatic compressed air storage, the inlet and outlet temperatures of the air and heat transfer fluid of each heat exchanger, and the mass flow rate are all variables, the advanced adiabatic compressed air storage energy hub device is actually operated at normal temperature and normal pressure, and the inlet and outlet temperatures of all heat exchangers are constant, so that equations (1) - (4) are linear equations. Furthermore, the advanced adiabatic compressed air energy storage energy junction device model considering the heat energy cascade storage and utilization is a mixed integer linear model, can be directly embedded in a day-ahead optimal scheduling model of the advanced adiabatic compressed air energy storage energy junction device, and can be solved by a mature commercial solver.
The advanced adiabatic compressed air energy storage energy junction equipment model created by the modeling method of the advanced adiabatic compressed air energy storage energy junction equipment provided by the invention considers the problems of multi-grade heat energy joint storage and heat energy cascade utilization, is beneficial to improving the heat energy utilization efficiency, is a mixed integer linear model, can be directly embedded in a day-ahead optimal scheduling model of the advanced adiabatic compressed air energy storage energy junction equipment, and can be solved by a mature commercial solver, so that the simulation efficiency can be improved.
Based on any of the foregoing embodiments, in this embodiment, the method further includes:
and simulating the power consumption condition for the compressor, and setting the air mass flow constraint conditions of the compressor in each compression stage.
The advanced heat-insulating compressed air energy storage energy hub device comprises a multistage compressor, and can respectively calculate the power consumption of each stage of compressor when calculating the power consumption required by the compressor, so as to obtain the total power consumption of the compressor.
According to the adiabatic compression equation and isentropic efficiency of the compressor, the power consumption required by the ith stage of compressor at the moment t satisfies the following formula:
wherein ,Representing the electric power consumed by the i-th stage air compression at time t; />Representing the mass air flow during compression at time t; />Representing the heat capacity of air; />Representing the i-th stage compressor inlet air temperature at time t; />Representing the efficiency of the i-th stage compressor; />Represents the compression ratio of the i-th stage compressor, < ->Indicates the outflow pressure of the i-th stage compressor at time t,/>Is shown inthe inflow air pressure of the ith stage compressor at the moment t; kappa indicates the air insulation index.
The total power consumption of all compressors meets the following conditions:
wherein Indicating the total charging power at time t; n is n c Representing the total number of compression stages.
The mass air flow of each compression stage satisfies:
wherein A binary variable indicating a state of charge at time t; />Representing the mass air flow during compression at time t; />Lower bound representing the mass air flow in the compression phase, < ->Representing the upper bound of the mass air flow in the compression stage.
Based on any of the foregoing embodiments, in this embodiment, the method further includes:
the working power condition of the turbine is simulated, and air mass flow constraint conditions of the turbine in each expansion stage are set.
The advanced adiabatic compressed air energy storage energy hub device comprises a multi-stage turbine, and when the working power of the turbine is calculated, the working power of each stage of turbine can be calculated respectively, so that the total working power of the turbine is obtained.
The isentropic efficiency and the j-th stage turbine working power at the t moment satisfy the following conditions:
wherein ,the j-th stage air expansion power generation at the time t is shown; />Representing the mass air flow during expansion at time t; />Representing the inlet air temperature of the jth stage turbine at time t; />Representing the expansion ratio of the jth stage expander; />Indicating the efficiency of the j-th stage expander.
The total acting power of all turbines meets the following conditions:
wherein Indicating the total discharge power at time t; n is n e Representing the total expansion progression.
The mass air flow of each expansion stage satisfies:
wherein A binary variable indicating a discharge state at time t; />Representing the mass air flow during expansion at time t; />Lower bound representing the mass air flow during the expansion phase, < ->Representing the upper bound of mass airflow during the expansion phase.
Based on the above description of the method of the invention, it is known that: although the compression ratio and expansion ratio of the advanced adiabatic compressed air energy storage compression side and expansion side, the inlet and outlet temperatures of the air and the heat transfer fluid of each heat exchanger and the mass flow rate are all variables, the advanced adiabatic compressed air energy storage energy hub device usually works in normal pressure and normal temperature state, that is, the power consumption of each stage of compressor in the formula (20) and the power of each stage of turbine in the formula (22) are only linearly related to the mass flow rate of the air, so the formula (20) and the formula (22) are linear; since the inlet and outlet temperatures of all heat exchangers are constant, equations (1) - (4) are also only linearly related to the mass flow rates of air and heat transfer fluid, and equations (1) - (4) are therefore linear. In summary, the advanced adiabatic compressed air energy storage energy hub equipment model considering the heat energy cascade storage and utilization is a mixed integer linear model, can be directly embedded in the advanced adiabatic compressed air energy storage energy hub equipment day-ahead optimal scheduling model, and can be solved by a mature commercial solver, so that the simulation efficiency can be improved.
Based on any of the foregoing embodiments, in this embodiment, the method further includes:
and simulating the air pressure change condition for the air storage tank.
The air storage tank in the advanced adiabatic compressed air energy storage energy junction device generally adopts a pressure vessel. The temperature of the air storage tank can be kept constant through heat preservation measures. Since the temperature and volume of the air tank are constant, the air pressure and the mass of the air meet the ideal gas equation, the air pressure change of the air tank in two continuous time periods depends on the air mass change, and the air pressure change of the air tank in two continuous time periods can be described by the following formula:
/>
wherein ,the air pressure of the air storage tank at the time t is shown; />The air pressure of the air storage tank at the time t+1 is shown; v represents the volume of the air storage tank; r is R g Represents the air gas constant; τ st Indicating the temperature of the air storage tank; />A binary variable indicating a state of charge at time t; />A binary variable indicating a discharge state at time t; />Representing the mass air flow during compression at time t; />The mass airflow during expansion at time t is indicated.
It should be noted that, the air pressure of the air storage tank should be within the safe air pressure range at any time, namely:
wherein ,prst,l Indicating the lower limit of the air pressure of the air storage tank, pr st,u Indicating the upper limit of the air pressure of the air storage tank.
The advanced adiabatic compressed air energy storage energy junction equipment model created by the modeling method of the advanced adiabatic compressed air energy storage energy junction equipment provided by the invention considers the problems of multi-grade heat energy joint storage and heat energy cascade utilization, is beneficial to improving the heat energy utilization efficiency, is a mixed integer linear model, can be directly embedded in a day-ahead optimal scheduling model of the advanced adiabatic compressed air energy storage energy junction equipment, and can be solved by a mature commercial solver, so that the simulation efficiency can be improved.
Based on any of the foregoing embodiments, in this embodiment, the method further includes:
the simulation is carried out for the heat load supply condition and the electric load supply condition in the advanced adiabatic compressed air energy storage energy hub equipment.
For advanced adiabatic compressed air energy storage energy hub equipment, high temperature heat load is supplied by high temperature heat storage; the low-temperature thermal load is first supplied by low-temperature heat storage, and if necessary also by high-temperature heat storage. The supply model of the high-temperature heat load is as follows:
wherein ,representing the thermal energy supplying the high temperature thermal load; Δτ Hd Representing the temperature difference between the front and back of the high temperature heat transfer fluid supply high temperature heat load; c oil Representing heat transfer fluid heat capacity; />And the mass flow of the high-temperature heat storage tank for supplying high-temperature heat load output at the moment t is shown.
The low temperature thermal load supply model is as follows:
wherein ,representing the thermal energy supplied to the low temperature thermal load; Δτ Ld Representing the temperature difference between the front and back of the low temperature heat transfer fluid supply low temperature heat load; Δτ HLd Representing the temperature difference between the front and back of the high temperature heat transfer fluid supply low temperature heat load; />The mass flow of the high-temperature heat storage tank output to the low-temperature heat load at the moment t is represented; />And the mass flow of the low-temperature heat storage tank output to the low-temperature heat load at the time t is shown.
Advanced adiabatic compressed air energy storage energy hub devices include an electrical load in addition to a thermal load.
The electrical load supply model is:
wherein ,representing the supply electric power of the AA-CAES energy hub device electric load at the time t; />The method comprises the steps that the electricity purchasing power of AA-CAES energy hub equipment from a power grid at the time t is represented; />Indicating the power consumption of the electric heating device at time t; />Representing the power consumption of the heat pump at time t; />Indicating the total charging power at time t; />Indicating the total discharge power at time t.
The advanced adiabatic compressed air energy storage energy junction equipment model created by the modeling method of the advanced adiabatic compressed air energy storage energy junction equipment provided by the invention considers the problems of multi-grade heat energy joint storage and heat energy cascade utilization, is beneficial to improving the heat energy utilization efficiency, is a mixed integer linear model, can be directly embedded in a day-ahead optimal scheduling model of the advanced adiabatic compressed air energy storage energy junction equipment, and can be solved by a mature commercial solver, so that the simulation efficiency can be improved.
Based on any of the above embodiments, fig. 3 is a schematic structural diagram of a modeling apparatus of an advanced adiabatic compressed air energy storage energy hub device provided by the present invention, and as shown in fig. 3, the modeling apparatus of an advanced adiabatic compressed air energy storage energy hub device provided by the present invention is used for modeling the advanced adiabatic compressed air energy storage energy hub device, where the apparatus includes:
a device determining module 301 included in the model, configured to determine a device included in the model of the advanced adiabatic compressed air energy storage energy device according to a structure of the advanced adiabatic compressed air energy storage energy junction device;
the heat energy conversion relation construction module 302 of the air compression process is configured to construct a heat energy conversion relation of the air compression process according to an output flow rate of the heat transfer fluid of the normal temperature heat storage tank, a temperature change condition of the heat transfer fluid in the compression side heat exchanger and a temperature change condition of the heat transfer fluid in the compression side heat exchanger;
the heat energy conversion relation construction module 303 of the air expansion process is configured to construct a heat energy conversion relation of the air expansion process according to an output flow rate of the heat transfer fluid of the high-temperature heat storage tank, a temperature change condition of the heat transfer fluid in the turbine side heat exchanger, and a temperature change condition of air in the turbine side heat exchanger;
A heat transfer fluid quality dynamic change relation construction module 304, configured to construct a dynamic change relation of heat transfer fluid quality of each heat storage tank included in the heat storage system according to a flow condition of the heat transfer fluid;
a heat transfer fluid quality balance relationship construction module 305, configured to construct a quality balance relationship of the heat transfer fluid during transmission between different devices in the advanced adiabatic compressed air energy storage energy hub device according to a flow condition of the heat transfer fluid;
a constraint condition setting module 306, configured to set constraint conditions for the cross-grade heating process;
the power consumption model construction module 307 is configured to construct a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and construct a power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
The advanced adiabatic compressed air energy storage energy junction equipment model created by the modeling device of the advanced adiabatic compressed air energy storage energy junction equipment provided by the invention considers the problems of multi-grade heat energy joint storage and heat energy cascade utilization, is beneficial to improving the heat energy utilization efficiency, is a mixed integer linear model, can be directly embedded in a day-ahead optimal scheduling model of the advanced adiabatic compressed air energy storage energy junction equipment, and can be solved by a mature commercial solver, so that the simulation efficiency can be improved.
Fig. 4 is a schematic structural diagram of an electronic device according to the present invention, as shown in fig. 4, the electronic device may include: processor 410, communication interface (Communications Interface) 420, memory 430 and communication bus 440, wherein processor 410, communication interface 420 and memory 430 communicate with each other via communication bus 440. The processor 410 may invoke logic instructions in the memory 430 to perform a method of modeling an advanced adiabatic compressed air energy storage energy hub device, the method comprising:
determining a device contained in the model of the advanced adiabatic compressed air energy storage energy hub device according to the structure of the advanced adiabatic compressed air energy storage energy hub device;
constructing a heat energy conversion relation in the air compression process according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger and the temperature change condition in the compression side heat exchanger;
according to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger and the temperature change condition of the air in the turbine side heat exchanger, constructing a heat energy conversion relation in the air expansion process;
According to the flow condition of the heat transfer fluid, constructing a dynamic change relation of the mass of the heat transfer fluid of each heat storage tank contained in the heat storage system;
according to the flow condition of the heat transfer fluid, constructing a quality balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment;
setting constraint conditions for a cross-grade heat supply process;
and constructing a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing the power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
Further, the logic instructions in the memory 430 described above may be implemented in the form of software functional units and may be stored in a computer-readable storage medium when sold or used as a stand-alone product. Based on this understanding, the technical solution of the present invention may be embodied essentially or in a part contributing to the prior art or in a part of the technical solution, in the form of a software product stored in a storage medium, comprising several instructions for causing a computer device (which may be a personal computer, a server, a network device, etc.) to perform all or part of the steps of the method according to the embodiments of the present invention. And the aforementioned storage medium includes: a U-disk, a removable hard disk, a Read-Only Memory (ROM), a random access Memory (RAM, random Access Memory), a magnetic disk, or an optical disk, or other various media capable of storing program codes.
In another aspect, the present invention also provides a computer program product comprising a computer program stored on a non-transitory computer readable storage medium, the computer program comprising program instructions which, when executed by a computer, are capable of performing a method of modeling an advanced adiabatic compressed air energy storage energy hub device provided by the methods described above, the method comprising:
determining a device contained in the model of the advanced adiabatic compressed air energy storage energy hub device according to the structure of the advanced adiabatic compressed air energy storage energy hub device;
constructing a heat energy conversion relation in the air compression process according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger and the temperature change condition in the compression side heat exchanger;
according to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger and the temperature change condition of the air in the turbine side heat exchanger, constructing a heat energy conversion relation in the air expansion process;
according to the flow condition of the heat transfer fluid, constructing a dynamic change relation of the mass of the heat transfer fluid of each heat storage tank contained in the heat storage system;
According to the flow condition of the heat transfer fluid, constructing a quality balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment;
setting constraint conditions for a cross-grade heat supply process;
and constructing a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing the power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
In yet another aspect, the present invention also provides a non-transitory computer readable storage medium having stored thereon a computer program which, when executed by a processor, is implemented to perform the method of modeling an advanced adiabatic compressed air energy storage energy hub device provided above, the method comprising:
determining a device contained in the model of the advanced adiabatic compressed air energy storage energy hub device according to the structure of the advanced adiabatic compressed air energy storage energy hub device;
constructing a heat energy conversion relation in the air compression process according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger and the temperature change condition in the compression side heat exchanger;
According to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger and the temperature change condition of the air in the turbine side heat exchanger, constructing a heat energy conversion relation in the air expansion process;
according to the flow condition of the heat transfer fluid, constructing a dynamic change relation of the mass of the heat transfer fluid of each heat storage tank contained in the heat storage system;
according to the flow condition of the heat transfer fluid, constructing a quality balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment;
setting constraint conditions for a cross-grade heat supply process;
and constructing a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing the power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
The apparatus embodiments described above are merely illustrative, wherein the elements illustrated as separate elements may or may not be physically separate, and the elements shown as elements may or may not be physical elements, may be located in one place, or may be distributed over a plurality of network elements. Some or all of the modules may be selected according to actual needs to achieve the purpose of the solution of this embodiment. Those of ordinary skill in the art will understand and implement the present invention without undue burden.
From the above description of the embodiments, it will be apparent to those skilled in the art that the embodiments may be implemented by means of software plus necessary general hardware platforms, or of course may be implemented by means of hardware. Based on this understanding, the foregoing technical solution may be embodied essentially or in a part contributing to the prior art in the form of a software product, which may be stored in a computer readable storage medium, such as ROM/RAM, a magnetic disk, an optical disk, etc., including several instructions for causing a computer device (which may be a personal computer, a server, or a network device, etc.) to execute the method described in the respective embodiments or some parts of the embodiments.
Finally, it should be noted that: the above embodiments are only for illustrating the technical solution of the present invention, and are not limiting; although the invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical scheme described in the foregoing embodiments can be modified or some technical features thereof can be replaced by equivalents; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims (15)

1. An advanced adiabatic compressed air energy storage energy hub device, comprising: the system comprises a compressor, a turbine, a heat exchanger, a gas storage tank, a heat load, an electric heating device, a heat pump and a heat storage system; the heat storage system comprises a high-temperature heat storage tank, a low-temperature heat storage tank and a normal-temperature heat storage tank;
the compression side heat exchanger is connected with the inlet end of the air storage tank, and the outlet end of the air storage tank is connected with the turbine side heat exchanger; the compression side heat exchanger is a heat exchanger connected with the compressor, and the turbine side heat exchanger is a heat exchanger connected with the turbine;
the inlet end of the high-temperature heat storage tank is respectively connected with the outlet end of the compression side heat exchanger and the electric heating device, and the outlet end of the high-temperature heat storage tank is respectively connected with the heat load and the inlet end of the turbine side heat exchanger;
the inlet end of the low-temperature heat storage tank is connected with the heat pump, and the outlet end of the low-temperature heat storage tank is connected with the heat load;
the inlet end of the normal temperature heat storage tank is connected with the heat load and the outlet end of the turbine side heat exchanger respectively, and the outlet end of the normal temperature heat storage tank is connected with the inlet ends of the heat pump, the electric heating device and the compression side heat exchanger respectively.
2. A method of modeling an advanced adiabatic compressed air energy storage energy hub device for modeling the advanced adiabatic compressed air energy storage energy hub device of claim 1, the method comprising:
determining a device contained in the model of the advanced adiabatic compressed air energy storage energy hub device according to the structure of the advanced adiabatic compressed air energy storage energy hub device;
constructing a heat energy conversion relation in the air compression process according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger and the temperature change condition in the compression side heat exchanger;
according to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger and the temperature change condition of the air in the turbine side heat exchanger, constructing a heat energy conversion relation in the air expansion process;
according to the flow condition of the heat transfer fluid, constructing a dynamic change relation of the mass of the heat transfer fluid of each heat storage tank contained in the heat storage system;
according to the flow condition of the heat transfer fluid, constructing a quality balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment;
Setting constraint conditions for a cross-grade heat supply process;
and constructing a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing the power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
3. The modeling method according to claim 2, wherein constructing the thermal energy conversion relation of the air compression process based on the output flow rate of the heat transfer fluid of the normal temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger, and the temperature change condition in the compression side heat exchanger, comprises:
for the i-th stage air compression, the thermal energy conversion relationship is:
wherein i is more than or equal to 1 and n is more than or equal to n c -1，n c Represents the last stage of air compression; c oil Representing the heat transfer fluid heat capacity, which is a constant;representing the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the ith stage of compression at the time t; />Representing the heat transfer fluid output temperature of the heat exchanger at the ith stage of compression at time t; />Representing heat transfer fluid input temperature of the heat exchanger at the ith stage of compression at time t; />Represents the heat capacity of air, which is a constant; />Air mass flow representing the compression process; Representing the temperature of the air at the outlet end of the ith stage of compressor at time t; />Representing the temperature of the air at the inlet end of the i+1st stage compressor at time t;
for the final stage of air compression, the thermal energy conversion relationship is:
wherein ,n represents the air compression side c Air temperature at the outlet end of the stage heat exchanger.
4. The modeling method according to claim 2, wherein constructing the thermal energy conversion relation of the air expansion process based on the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger, and the temperature change condition of the air in the turbine side heat exchanger, comprises:
for stage 1 air expansion, the thermal energy conversion relationship is:
wherein ,representing the high temperature tank heat transfer fluid output flow rate at time t, stage 1 expansion stage; />Representing heat transfer fluid input temperature to the heat exchanger at time t, stage 1 expansion stage; />Representing the heat transfer fluid output temperature of the heat exchanger at time t, stage 1 expansion stage; />Air mass flow representing the expansion process; />Representing the air temperature at the inlet end of the stage 1 turbine; τ st Indicating the temperature of the air storage tank;
for the j-th stage of the air expansion except the initial stage, the heat energy conversion relationship is as follows:
Wherein j is more than or equal to 2 and n is more than or equal to n e ，n e Representing the final stage of air expansion;representing the high temperature tank heat transfer fluid output flow rate at time t, stage j expansion stage; />Representing heat transfer fluid input temperature of the heat exchanger at time t and in the j-th expansion stage;representing the heat transfer fluid output temperature of the heat exchanger at the j-th expansion stage at time t; />Representing the air temperature at the inlet end of the j-th stage turbine; />Representing the air temperature at the outlet end of the j-1 stage turbine.
5. The modeling method according to claim 2, wherein the constructing a dynamic change relation of the heat transfer fluid mass of each heat storage tank included in the heat storage system according to the flow condition of the heat transfer fluid includes:
the dynamic change relation of the heat transfer fluid mass in the high-temperature heat storage tank is as follows:
wherein ,representing the total mass of heat transfer fluid of the high-temperature heat storage tank at the time t+1; />Representing the total mass of heat transfer fluid of the high-temperature heat storage tank at the moment t; />The mass flow of the heat transfer fluid at the air compression side flowing into the high-temperature heat storage tank at the time t+1 is represented;the mass flow of the heat transfer fluid flowing from the normal-temperature heat storage tank to the high-temperature heat storage tank at the time t+1 and heated by the electric heating device is shown; />The output mass flow of the high-temperature heat storage tank to the heat transfer fluid at the expansion side at the time t+1 is shown; / >The mass flow of the high-temperature heat storage tank for supplying high-temperature heat load output at the time t+1 is shown; />The mass flow of the high-temperature heat storage tank for supplying low-temperature heat load output at the time t+1 is shown;
compression side high temperature heat transfer fluid mass flow flowing into high temperature heat storage tank at time t+1The sum of the input mass flow rates of the heat transfer fluid of the high-temperature heat storage tank in each air compression stage at the moment t+1; namely:
wherein ,representing the input mass flow rate of the heat transfer fluid of the high-temperature heat storage tank in the ith stage of compression at the time t+1;
the high-temperature heat storage tank outputs mass flow to heat transfer fluid at expansion side at time t+1The sum of the output mass flow rates of the heat transfer fluid of the high-temperature heat storage tank in each air expansion stage at the moment t+1; namely:
wherein ,representing the output mass flow rate of the heat transfer fluid of the high-temperature heat storage tank in the ith stage expansion stage at the time t+1;
the dynamic change relation of the heat transfer fluid mass in the low-temperature heat storage tank is as follows:
wherein ,representing the total mass of the heat transfer fluid of the low-temperature heat storage tank at the time t+1; />Representing the total mass of the heat transfer fluid of the low-temperature heat storage tank at the moment t; />The mass flow of the normal-temperature heat transfer fluid which flows from the normal-temperature heat storage tank to the low-temperature heat storage tank at the time t+1 and is heated by the heat pump is shown; />The mass flow of the low-temperature heat storage tank output to the low-temperature heat load at the time t+1 is shown;
The dynamic change relation of the heat transfer fluid mass in the normal temperature heat storage tank is as follows:
wherein ,the total mass of the heat transfer fluid of the normal-temperature heat storage tank at the time t+1 is shown; />The total mass of heat transfer fluid of the normal-temperature heat storage tank at the moment t is represented; />The mass flow of the heat transfer fluid which flows into the normal-temperature heat storage tank from the heat exchanger at the air expansion side at the time t+1 and releases heat is shown; />The mass flow of the heat transfer fluid at the outlet side of the high-temperature heat storage supply high-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the heat transfer fluid at the outlet side of the high-temperature heat storage supply low-temperature heat load heat exchanger at the time t+1 is shown; />The mass flow of the heat transfer fluid at the outlet side of the low-temperature heat storage supply low-temperature heat load heat exchanger at the time t+1 is shown;the mass flow of the normal-temperature heat transfer fluid which is output from the normal-temperature heat storage tank at the time t+1 and is used for heat collection in the air compression process is shown; />The mass flow of the heat transfer fluid flowing from the normal-temperature heat storage tank to the high-temperature heat storage tank at the time t+1 and heated by the electric heating device is shown; />The mass flow of the normal-temperature heat transfer fluid which flows from the normal-temperature heat storage tank to the low-temperature heat storage tank at the time t+1 and is heated by the heat pump is shown;
normal temperature heat transfer fluid mass flow for air compression process heat collection at time t+1Is equal to the sum of the mass flow of the normal-temperature heat transfer fluid consumed by each compression stage; namely:
wherein ,the output mass flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the ith stage of compression at the time t+1 is shown;
mass flow of heat transfer fluid released heat flowing from heat exchanger on air expansion side into normal temperature heat storage tank at time t+1Equal to the sum of the mass flow rates of the heat transfer fluid consumed by the respective turboexpansion stages; namely:
wherein ,and the input mass flow rate of the heat transfer fluid of the normal-temperature heat storage tank in the j-th expansion stage at the time t+1 is shown.
6. Modeling method in accordance with claim 2, wherein said constructing a mass balance relationship of heat transfer fluid during transfer between different devices in the advanced adiabatic compressed air energy storage energy hub device based on the flow conditions of the heat transfer fluid comprises:
in the air compression process, the total input mass flow of the heat transfer fluid of the high-temperature heat storage tank is equal to the total output mass flow of the heat transfer fluid of the normal-temperature heat storage tank, and the input mass flow of the heat transfer fluid of the high-temperature heat storage tank in each compression stage is equal to the corresponding output mass flow of the normal-temperature heat storage tank in each compression stage;
in the air expansion process, the total output mass flow of the heat transfer fluid of the high-temperature heat storage tank is equal to the total input mass flow of the heat transfer fluid of the normal-temperature heat storage tank, and the output mass flow of the heat transfer fluid of the high-temperature heat storage tank in each expansion stage is equal to the corresponding input mass flow of the normal-temperature heat storage tank in each expansion stage;
For heat exchangers on the heat load supply side, the mass flow rate of the heat transfer fluid input of each grade is equal to the corresponding output mass flow rate.
7. A modeling method in accordance with claim 2, wherein said setting constraints for a cross-grade heating process comprises:
for a normal temperature heat storage tank, the set constraint conditions include:
the normal temperature heat transfer fluid available in the normal temperature heat storage tank is firstly used for heat collection in the air compression process, and then provides heat energy supplement for other heat storage tanks;
for a low temperature heat storage tank, the constraints set include:
the output of the heat transfer fluid used for supplying low-temperature heat load in the low-temperature heat storage tank does not exceed the remaining usable range of the low-temperature heat storage tank;
for a high temperature heat storage tank, the constraints set include:
the available high temperature heat transfer fluid in the high temperature heat storage tank preferentially meets the air expansion heating demand and is then used for heat load supply.
8. The modeling method according to claim 2, wherein the constructing a power consumption model for the electric heating device based on the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing a power consumption model for the heat pump based on the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, comprises:
According to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, a power consumption model constructed for the electric heating device is as follows:
wherein ,indicating the power consumption of the electric heating device at time t, eta H Indicating the efficiency of the electric heating device, Δτ H Represents the difference between the rated high-temperature heat storage tank temperature and the normal-temperature heat storage tank temperature, τ H Indicating rated high-temperature heat storage tank temperature, tau O Representing the temperature of the normal-temperature heat storage tank; c oil Representing heat transfer fluid heat capacity; />Indicating the inflow from the normal temperature heat storage tank at time tThe mass flow of the heat transfer fluid of the high-temperature heat storage tank which is heated by the electric heating device;
according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, a power consumption model constructed for the heat pump is as follows:
wherein ,representing the power consumption of the heat pump at time t, eta L Indicating the efficiency of the heat pump, deltaτ L Represents the difference between the rated low-temperature heat storage tank temperature and the normal-temperature heat storage tank temperature, τ L Representing the rated low-temperature heat storage tank temperature; />The mass flow of the normal temperature heat transfer fluid heated by the heat pump flowing from the normal temperature heat storage tank to the low temperature heat storage tank at time t is shown.
9. Modeling method according to any of the claims 2-8, characterized in that the method further comprises:
simulating the power consumption condition of the compressor, and setting air mass flow constraint conditions of the compressor in each compression stage; the method specifically comprises the following steps:
At time t, the power consumption required by the ith stage of compressor satisfies the following equation:
wherein ,representing the electric power consumed by the i-th stage air compression at time t; />Indicated at tAir mass flow during etching and compression; />Representing the heat capacity of air; />Representing the i-th stage compressor inlet air temperature at time t; />Representing the efficiency of the i-th stage compressor; />Represents the compression ratio of the i-th stage compressor, < ->Indicates the outflow pressure of the i-th stage compressor at time t,/>The inflow air pressure of the ith stage compressor at the time t; kappa represents the air insulation index;
the total power consumption of all compressors meets the following conditions:
wherein Indicating the total charging power at time t; n is n c Representing the total number of compression stages;
the mass air flow of each compression stage satisfies:
wherein A binary variable indicating a state of charge at time t; />Representing the mass air flow during compression at time t; />Lower bound representing the mass air flow in the compression phase, < ->Representing the upper bound of the mass air flow in the compression stage.
10. Modeling method according to any of the claims 2-8, characterized in that the method further comprises:
simulating the working power condition of the turbine, and setting air mass flow constraint conditions of the turbine in each expansion stage; the method specifically comprises the following steps:
At the time t, the j-th stage turbine working power meets the following conditions:
wherein ,the j-th stage air expansion power generation at the time t is shown; />Representing the mass air flow during expansion at time t; />Representing the inlet air temperature of the jth stage turbine at time t; />Representing the expansion ratio of the jth stage expander；/>Representing the efficiency of the j-th stage expander;
the total acting power of all turbines meets the following conditions:
wherein Indicating the total discharge power at time t; n is n e Representing the total expansion progression;
the mass air flow of each expansion stage satisfies:
wherein A binary variable indicating a discharge state at time t; />Representing the mass air flow during expansion at time t; />Lower bound representing the mass air flow during the expansion phase, < ->Representing the upper bound of mass airflow during the expansion phase.
11. Modeling method according to any of the claims 2-8, characterized in that the method further comprises:
simulating the air pressure change condition for the air storage tank; the method specifically comprises the following steps:
the air pressure change condition of the air storage tank in two continuous time periods is expressed by the following formula:
wherein ,the air pressure of the air storage tank at the time t is shown; />The air pressure of the air storage tank at the time t+1 is shown; v represents the volume of the air storage tank; r is R g Represents the air gas constant; τ st Indicating the temperature of the air storage tank; />A binary variable indicating a state of charge at time t; />A binary variable indicating a discharge state at time t; />Representing the mass air flow during compression at time t; />The mass airflow during expansion at time t is indicated.
12. Modeling method according to any of the claims 2-8, characterized in that the method further comprises:
simulating a thermal load supply condition and an electrical load supply condition in the advanced adiabatic compressed air energy storage energy hub device; the method specifically comprises the following steps:
the supply model of the high-temperature heat load is as follows:
wherein ,representing the thermal energy supplying the high temperature thermal load; Δτ Hd Representing the temperature difference between the front and back of the high temperature heat transfer fluid supply high temperature heat load; c oil Representing heat transfer fluid heat capacity; />The mass flow of the high-temperature heat storage tank for supplying high-temperature heat load output at the moment t is shown;
the low temperature thermal load supply model is as follows:
wherein ,representing the thermal energy supplied to the low temperature thermal load; Δτ Ld Representing the temperature difference between the front and back of the low temperature heat transfer fluid supply low temperature heat load; Δτ HLd Representing the temperature difference between the front and back of the high temperature heat transfer fluid supply low temperature heat load; />The mass flow of the high-temperature heat storage tank output to the low-temperature heat load at the moment t is represented; / >The mass flow of the low-temperature heat storage tank output to the low-temperature heat load at the moment t is represented;
the electrical load supply model is:
wherein ,representing the supply electric power of the AA-CAES energy hub device electric load at the time t; />The method comprises the steps that the electricity purchasing power of AA-CAES energy hub equipment from a power grid at the time t is represented; />Indicating the power consumption of the electric heating device at time t; />Representing the power consumption of the heat pump at time t; />Indicating the total charging power at time t; />Indicating the total discharge power at time t.
13. A modeling apparatus for an advanced adiabatic compressed air energy storage energy hub device for modeling the advanced adiabatic compressed air energy storage energy hub device of claim 1, the apparatus comprising:
the device determining module is used for determining the device contained in the advanced adiabatic compressed air energy storage energy junction equipment model according to the structure of the advanced adiabatic compressed air energy storage energy junction equipment;
the heat energy conversion relation construction module is used for constructing the heat energy conversion relation of the air compression process according to the output flow rate of the heat transfer fluid of the normal-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the compression side heat exchanger and the temperature change condition of the heat transfer fluid in the compression side heat exchanger;
The heat energy conversion relation construction module is used for constructing the heat energy conversion relation of the air expansion process according to the output flow rate of the heat transfer fluid of the high-temperature heat storage tank, the temperature change condition of the heat transfer fluid in the turbine side heat exchanger and the temperature change condition of the air in the turbine side heat exchanger;
the heat transfer fluid quality dynamic change relation construction module is used for constructing the dynamic change relation of the heat transfer fluid quality of each heat storage tank contained in the heat storage system according to the flow condition of the heat transfer fluid;
the heat transfer fluid quality balance relation construction module is used for constructing a quality balance relation of the heat transfer fluid during transmission among different devices in the advanced adiabatic compressed air energy storage energy hub equipment according to the flow condition of the heat transfer fluid;
the constraint condition setting module is used for setting constraint conditions for the cross-grade heat supply process;
the power consumption model construction module is used for constructing a power consumption model for the electric heating device according to the temperature information of the high-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank, and constructing a power consumption model for the heat pump according to the temperature information of the low-temperature heat storage tank and the temperature information of the normal-temperature heat storage tank.
14. An electronic device comprising a memory, a processor and a computer program stored on the memory and executable on the processor, characterized in that the processor implements the steps of the modeling method of an advanced adiabatic compressed air energy storage energy hub device according to any of claims 2 to 12 when the program is executed by the processor.
15. A non-transitory computer readable storage medium having stored thereon a computer program, which when executed by a processor, implements the steps of the modeling method of an advanced adiabatic compressed air energy storage energy hub device according to any of claims 2 to 12.
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