CN220185192U - Novel thermoelectric coupling compressed air energy storage system - Google Patents
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- 238000004146 energy storage Methods 0.000 title claims abstract description 64
- 230000008878 coupling Effects 0.000 title claims abstract description 16
- 238000010168 coupling process Methods 0.000 title claims abstract description 16
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 16
- 239000007788 liquid Substances 0.000 claims abstract description 31
- 238000007906 compression Methods 0.000 claims description 25
- 230000006835 compression Effects 0.000 claims description 17
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 17
- 230000008676 import Effects 0.000 claims 3
- 230000001502 supplementing effect Effects 0.000 abstract description 8
- 238000010276 construction Methods 0.000 abstract description 3
- 230000007547 defect Effects 0.000 abstract description 2
- 238000000034 method Methods 0.000 description 17
- 238000005485 electric heating Methods 0.000 description 15
- 238000005338 heat storage Methods 0.000 description 11
- 150000003839 salts Chemical class 0.000 description 11
- 230000005611 electricity Effects 0.000 description 10
- 238000006243 chemical reaction Methods 0.000 description 9
- 238000003303 reheating Methods 0.000 description 9
- 238000002485 combustion reaction Methods 0.000 description 5
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- 238000009825 accumulation Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 239000010687 lubricating oil Substances 0.000 description 2
- 239000010734 process oil Substances 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
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Abstract
The utility model provides a novel thermoelectric coupling compressed air energy storage system, which is additionally provided with a heat supplementing loop, wherein the heat supplementing loop comprises a second reheater arranged at the inlet of an expansion machine of each stage, a heat exchange medium inlet pipeline of the second reheater is connected with a second high-temperature liquid storage tank, a heat exchange medium outlet pipeline of the second reheater is connected with a second low-temperature liquid storage tank, the second low-temperature liquid storage tank is connected with the second high-temperature liquid storage tank through an electric heater, and the electric heater heats a low-temperature heat exchange medium in the second low-temperature liquid storage tank and then sends the heated low-temperature heat exchange medium into the second high-temperature liquid storage tank. The energy storage system can overcome the defects that the unit construction cost of a non-afterburning type compressed air energy storage system in the prior art is high, and the turbine output power of the energy storage system is smaller compared with that of an equivalent-magnitude afterburning type compressed air energy storage system.
Description
Technical Field
The utility model relates to the technical field of compressed air energy storage, in particular to a novel thermoelectric coupling compressed air energy storage system.
Background
The compressed air energy storage technology refers to an energy storage mode that electric energy is used for compressed air in the low-load period of a power grid, the air is sealed in a scrapped salt cavern, a mine, a settled submarine gas storage tank, a mountain cave, an expired oil-gas well or a newly built gas storage well at high pressure, and the compressed air is released in the peak period of the power grid to push an expander to generate electricity.
There are many types of compressed air energy storage systems, and there may be different classifications depending on different criteria. The combustion chamber preheated air can be classified into an afterburned system and a non-afterburned system according to whether it is required.
The post-combustion type compressed air energy storage system is based on the working principle of a gas turbine, a post-combustion chamber is arranged at the inlet of an expander, and the work load of the turbine is increased by using fuel to heat high-pressure air released in a gas storage device. The non-afterburning type compressed air energy storage system is characterized in that when the compressed air energy storage system works, an external heat source is not needed, and the system relies on heat energy stored in a compression stage and then is used for heating high-pressure air entering each stage of the expander in an expansion stage to improve the electric-electric conversion efficiency of the system.
The afterburning type compressed air energy storage system is reliable and high in stability, but the fuel combustion can discharge pollutants to cause environmental pollution, so that the development trend of 'double carbon' and green environmental protection is not met, the overall efficiency of the system is lower, and the turbine output power is higher compared with that of a non-afterburning type compressed air energy storage system with the same magnitude.
The non-afterburning type compressed air energy storage system does not need fossil energy combustion, and is provided with a heat storage and exchange device for recovering heat generated in the process of compressed air, and the heat is returned to the air at the inlet of the expander in the energy release stage through the heat exchanger, so that the heat efficiency of the system is improved. Compared with the traditional afterburning type compressed air energy storage system, the efficiency of the non-afterburning type compressed air energy storage system is higher, but because the heat storage and exchange device is added, the unit construction cost is relatively increased, and because of the existence of heat exchange end difference and the like, compared with the same-magnitude afterburning type compressed air energy storage system, the turbine output power is smaller.
Disclosure of Invention
Therefore, the utility model provides a novel thermoelectric coupling compressed air energy storage system, which can overcome the defects of high unit construction cost of a non-afterburning compressed air energy storage system and smaller turbine output power compared with an equivalent-magnitude afterburning compressed air energy storage system in the prior art.
In order to solve the problems, the utility model provides a novel thermoelectric coupling compressed air energy storage system, which comprises a compressor unit, a gas storage device and an expansion unit which are sequentially connected, wherein the compressor unit comprises a plurality of compressors, each stage of expansion unit comprises a plurality of expansion machines, the outlet of each compressor is connected with a heat exchanger, the heat exchanger takes away compression heat and then enters the next stage of compression, a heat exchange medium high-temperature outlet pipeline of the heat exchanger is connected with a first high-temperature liquid storage tank, a low-temperature inlet pipeline of the heat exchanger is connected with a first low-temperature liquid storage tank, the inlet of each expansion machine of each stage is connected with a first reheater, a heat exchange medium inlet pipeline of the first reheater is connected with the first high-temperature liquid storage tank, a heat exchange medium outlet pipeline of the first reheater is connected with the first low-temperature liquid storage tank, the heat exchange medium outlet pipeline of the heat exchanger is connected with a second low-temperature liquid storage tank, and the second reheater is connected with the second high-temperature liquid storage tank, and then the heat exchange medium is sent into the second high-temperature liquid storage tank through the second electric heater.
In some embodiments, the heat exchangers are arranged in series for two sets of heat exchangers.
In some embodiments, the heat exchange medium is water.
Compared with the traditional non-afterburning compressed air energy storage system, the novel thermoelectric coupling compressed air energy storage system provided by the utility model has the advantages that an electric heating and supplementing loop is added in the compressed air energy storage system to reheat air entering an inlet of an expander, so that the air is reheated twice before entering the expander, the air is reheated by heat storage in a compression process for the first time, and the air is reheated by the electric heating loop for the second time, so that the temperature of the air entering a turbine is higher, and the output power of the turbine is higher.
Drawings
Fig. 1 is a schematic structural diagram of a novel thermoelectric coupling compressed air energy storage system according to an embodiment of the present utility model.
The reference numerals are expressed as:
1. air; 2. a compressor; 3. a heat exchanger; 4. a gas storage device; 5. a first low temperature storage tank; 6. a first high temperature liquid storage tank; 7. an expander; 8. a first reheater; 9. a second low temperature liquid storage tank; 10. a second high temperature liquid storage tank; 11. an electric heater; 12. and a second reheater.
Detailed Description
According to the embodiment of the utility model, referring to fig. 1, a novel thermoelectric coupling compressed air energy storage system is provided, which comprises a compressor unit, a gas storage device 4 and an expansion unit which are sequentially connected, wherein the compressor unit comprises a plurality of compressors 2, each expansion unit comprises a plurality of expansion machines 7, the outlet of each compressor 2 is connected with a heat exchanger 3, the heat exchangers 3 take away compression heat and then enter the next stage of compression, a heat exchange medium high-temperature outlet pipeline of each heat exchanger 3 is connected with a first high-temperature liquid storage tank 6, a low-temperature inlet pipeline of the heat exchange medium high-temperature outlet pipeline is connected with a first low-temperature liquid storage tank 5, each stage of the heat exchange medium high-temperature outlet pipeline is connected with a first reheater 8, the first reheater 8 provides heat for air to be expanded, a heat exchange medium inlet pipeline of the first reheater 8 is connected with the first high-temperature liquid storage tank 6, a heat exchange medium outlet pipeline of the first low-temperature liquid storage tank 5 is connected with a heat supplementing loop, the heat supplementing loop comprises a second reheater 12 arranged at the inlet of each stage of the expansion machines 7, the second high-temperature liquid storage tank 12 is connected with a second electric heater 10, and the second high-temperature liquid storage tank 10 is connected with the second electric heater 10.
In a specific embodiment, the heat exchangers 3 are arranged in series for two groups of heat exchangers.
In a specific embodiment, the heat exchange medium is water.
Aiming at the novel thermoelectric coupling compressed air energy storage system provided by the utility model, the energy efficiency calculation is expanded, and the calculation result is compared and analyzed with the energy efficiency of the traditional non-afterburning compressed air energy storage system, so that the efficiency of the novel thermoelectric coupling compressed air energy storage system provided by the utility model is better. The specific method comprises the following steps:
first, it is necessary to obtain key technical parameters of the compressed air energy storage system. Mainly comprises the following steps:
(1) The expander generator outputs rated power;
(2) A compressor compression heat recovery scheme;
(3) The exhaust temperature of each section of the compressor;
(4) The water storage temperature of the hot water tank;
(5) The water storage temperature of the cold water tank;
(6) The temperature of air inlet of each section of the expander;
(7) Compressor unit end cylinder charge pressure and expander unit inlet pressure. The pressure values refer to the positions of the compressor and the exhaust inlet flange of the expander, and the working pressure range of the compressor unit is determined by the geological conditions and the volume of salt caves.
(8) Heat exchange and reheater resistance loss;
(9) The high-temperature compression heat of the front three cylinders of the compressor is recovered, and the compression heat of the fourth cylinder is not accumulated and recovered.
(10) The temperature of the compressed air entering/exiting the salt cavern;
(11) The compressor unit working time and the expander unit working time (the compressor unit is operated at valley power and the expander unit is operated at peak power) in the energy storage process.
Second, the calculation is expanded. In general, the compressed air energy storage system calculation optimization process is:
(1) The air flow and the exhaust temperature of each section required by the expansion turbine work are calculated by planning the set generator scale and the charging and discharging time and combining the reheat temperature determined by different heat storage schemes (such as high-pressure water heat storage and heat conduction oil heat storage) and the turbine air inlet pressure determined by different air storage devices (such as salt caves).
(2) And calculating the reheating heat required by the expansion turbine power generation according to the exhaust temperature and the reheating inlet temperature of each section of the expansion turbine.
(3) The working flow of the compressor can be obtained according to the flow of the power generation requirement of the expander and the compression and expansion time ratio, and the shaft power consumed by the compressor can be calculated according to the section exhaust temperature (or the total number of sections divided) of the compressor and the gas storage pressure determined by different gas storage devices (such as salt caves) according to the heat storage scheme.
(4) According to the exhaust temperature and the inlet temperature of the compressor section, the total heat generated in the compression process can be calculated, and the heat required by expansion reheating is combined to complete the determination of the heat recovery scheme. The heat recovery amount of compression and the heat required by reheating in the expansion process are required to be balanced for a plurality of times so as to improve the system efficiency.
Calculation of system working air flow
1) The calculation formula of the intake air flow of the expander is as follows:
2) The calculation formula of the outlet temperature of the expander comprises the following steps:
3) The calculation formula of the expansion ratio of the inlet and the outlet of the expander comprises the following steps:
wherein:
subscripts e, ei, eo denote expander, expander inlet, expander outlet, respectively;
ge is the air inlet mass flow of the expander, and the unit is kg/s;
W e,j the power in the expansion machine of the j-th section is in a unit kW;
p ei,j 、p eo,j inlet and outlet pressures of the j-th section of expander are respectively in MPa;
β j the expansion ratio of the expansion machine of the j th section;
T ei,j 、T eo,j the inlet and outlet temperatures of the j-th section of expansion machine are respectively given by a unit K;
η e,j isentropic efficiency for the j-th stage expander;
k is an adiabatic index, 1.4;
r is the air gas constant, 0.287 is taken as the unit kJ/(kg.K).
Calculation of reheat demand heat of expander
The calculation formula is as follows:
ΔT＝T 2 -T 1
wherein:
Q the unit kW is the heat exchange process power;
to the average specific heat capacity of the intake and exhaust, unit kJ/(kg.K), C p,1 To give specific heat capacity of intake air, C p,2 Specific heat capacity of exhaust gas at different temperatures and pressures can be obtained by table lookup;
delta T is the temperature difference between the air inlet and the air outlet, and is in units of K and T 1 Is the temperature of the inlet air, T 2 Is the exhaust temperature;
q is mass flow, unit kg/h.
Compression process power consumption calculation
And obtaining a specific working flow value of the compressor according to the operation mode of the duration of charging and power generation of the compressed air energy storage system.
Because the front 3 cylinders of the compressor are in a fixed working condition running mode, the 4 th cylinder is in a variable working condition (back pressure) running mode, the energy storage initial and end power consumption of the 4 th cylinder are respectively calculated and averaged through variable rotation speed adjustment.
Wherein:
subscripts c, ci, co represent compressor, compressor inlet, compressor outlet, respectively;
p ci,i 、p co,i 、ε i inlet and outlet pressures and compression ratios for the i-th cylinder compressor;
T ci,i 、T co,i the inlet and outlet temperatures of the ith cylinder compressor are given by a unit K;
W c,i is the power in the ith cylinder compressor;
G c air mass flow is the energy storage process, and the unit is kg/s;
m i and eta ci The polytropic index and polytropic efficiency of the ith cylinder compressor, respectively;
σ i is a multiple variable number of the ith cylinder compressor;
compression process heat exchange heat calculation
The main purpose of the compression process is to reduce the air inlet temperature of the compressor/salt cavern and thus reduce the power consumption of the compressor/meet the requirement of the salt cavern on the air inlet temperature by only heat storage of the No. 1-3 heat exchangers (the positions of which are shown in the figure 1 in detail) and the No. 4-7 heat exchangers (the positions of which are shown in the figure 1 in detail).
The heat stored by the No. 1-3 heat exchangers is calculated as follows:
ΔT＝T 1 -T 2
wherein:
q is the heat load (heat exchangers 1, 2 and 3) of a heat storage heat exchanger in the compression energy storage process, and the unit kW;
to average specific heat capacity of intake and exhaust, unit kJ.kg-1K-1, C p,1 To give specific heat capacity of intake air, C p,2 Specific heat capacity for exhaust (can be obtained by table lookup);
delta T is the temperature difference between the air inlet and the air outlet, and is in units of K and T 1 Is the temperature of the inlet air, T 2 Is the exhaust temperature;
q is mass flow, unit kg/h.
Third, calculate the case.
With the method proposed above, specific calculations were performed on a 100 MW-scale compressed air energy storage system. ( The case A calculated below is the case where no electric heating secondary heat compensating circuit is added; the case B is a case where an electric heating secondary heat compensating circuit is added. )
A. Key technical parameters of the non-afterburning compressed air energy storage system include:
(1) The rated output power of the turbine generator is 100MW;
(2) The compression heat recovery scheme of the compressor adopts high-pressure water for heat storage;
(3) Setting the exhaust temperature of each section of the compressor to 216 ℃;
(4) The water storage temperature of the hot water tank is 205 ℃;
(5) The water storage temperature of the cold water tank is about 50 ℃;
(6) The temperature of the inlet air of each section of the expander is 190 ℃;
(7) According to engineering practice, the end difference of the shell-and-tube heat exchanger is more than or equal to 10 ℃.
(8) The inflation pressure of the end cylinder of the compressor unit is 14.4 MPa-15.9 MPa, and the inlet pressure of the turbine unit is 14.156MPa. The pressure values refer to the positions of the compressor and the exhaust inlet flange of the expander, and the working pressure range of the compressor unit is determined by the geological conditions and the volume of salt caves.
(9) The heat exchange and reheater resistance losses are considered according to 20 kpa;
(10) The high-temperature compression heat of the front three cylinders of the compressor is recovered, and the compression heat of the fourth cylinder is not accumulated and recovered.
(11) The temperature of the compressed air entering/exiting the salt cavern is set to be 40 ℃;
(12) And in the energy storage process, the compressor unit works for 8h to store electric energy, the expansion unit works for 5h to release electric energy, the compressor unit operates in the valley electricity, and the expansion unit operates in the peak electricity.
Calculation of the system working air flow:
calculating known conditions: the isentropic efficiency of each section of the expander is 0.9, the energy storage generator set outputs 100MW outwards, the generator efficiency is considered to be 96%, the expander support bearing and thrust bearing loss, shaft end leakage loss and the like are considered, then the total output internal power of the expander is=100 MW/0.96+1MW=105.2 MW (average of each section is 35.1 MW), the inlet pressure of the first section of the expander is 14.156MPa, the reheating times are 3 times, the reheating temperature is 190 ℃, the section loss is 20kPa, and the expansion ratio of each section is the same.
Calculating an output result: the mass flow rate of the inlet air of the expander and the temperature of the exhaust air.
And (3) calculating reheating demand heat of the expansion machine:
the heat load required for reheating the three-stage expander is 112901.6972kw×5h= 564.5MWh.
And (5) calculating the power consumption in the compression process:
according to the 8h charging and 5h discharging operation mode, the working flow of the compressor is as follows: 866.592t/h×5/8= 541.62t/h.
Because the front 3 cylinders of the compressor are in a fixed working condition running mode, the 4 th cylinder is in a variable working condition (back pressure) running mode, the energy storage initial and end power consumption of the 4 th cylinder are respectively calculated and averaged through variable rotation speed adjustment.
And (3) calculating heat exchange heat in the compression process:
the main purpose of the compression process is to reduce the air inlet temperature of the compressor/salt cavern and thus reduce the power consumption of the compressor/meet the requirement of the salt cavern on the air inlet temperature by only heat storage of the No. 1-3 heat exchangers (the positions of which are shown in the figure 1 in detail) and the No. 4-7 heat exchangers (the positions of which are shown in the figure 1 in detail).
The heat stored by the No. 1-3 heat exchangers is calculated in detail as follows:
the heat accumulation amount in the compression energy accumulation process is as follows: 73174.54848kw×8h= 585.4MWh.
Total electrical-to-electrical conversion efficiency calculation:
1) Actual grid-connected generating capacity W of energy storage unit 1 100mw×5h=500 MWh (turbine direct connect generator, no gearbox drive loss);
2) Energy storage process unit consumption power W 2 = 780.2 MWh/0.95 (considering gearbox and motor losses) = 821.3MWh.
3) Public and auxiliary engineering consumed electric quantity W of energy storage process oil station, circulating water pump and the like 3 =1 MWh (estimated from similar unit consumption).
4) Lubricating oil station and reheat circulating water pump engineering consumed electric quantity W in energy release process 4 =0.5 MWh (estimated from similar unit consumption).
Total electro-to-electrical conversion efficiency = W 1 /(W 2 +W 3 +W 4 )＝500/(821.3+1+0.5)＝0.6077。
B. The key technical parameters of the novel thermoelectric coupling compressed air energy storage system are the same as those listed in the non-afterburning compressed air energy storage system. The novel system is added with an electric heating loop based on the original non-afterburning compressed air energy storage system, the temperature of air entering a turbine inlet is increased from 190 ℃ to 210 ℃, the efficiency of an electric heat conversion part is required to be additionally calculated, and then the efficiency of the novel system is compared and analyzed with the efficiency of the non-afterburning compressed air energy storage system without the electric heating loop.
After the electric complementary heat loop is added, the total electric-electric conversion efficiency is as follows:
1) Actual grid-connected generating capacity W of energy storage unit 1 100mw×5h=500 MWh (turbine direct connect generator, no gearbox drive loss);
2) Energy storage process unit consumption power W 2 = 780.2 MWh/0.95 (considering gearbox and motor losses) = 821.3MWh.
3) Public and auxiliary engineering consumed electric quantity W of energy storage process oil station, circulating water pump and the like 3 =1 MWh (estimated from similar unit consumption).
4) Lubricating oil station and reheat circulating water pump engineering consumed electric quantity W in energy release process 4 =0.5 MWh (estimated from similar unit consumption).
5) The consumed electric quantity W after the electric heating heat supplementing loop is increased in the energy release process 5 ＝(15.21MW×5h)÷0.98＝77.6MW
6) The power generation increment W of the unit after the electric heating heat supplementing loop is added in the energy release process 6 ＝(12.4MW×5h)×0.96＝59.7MW
Then the total electric-electric conversion effect= (W) after the electric heating complementary heat loop is added in the compressed air energy storage system 1 +W 6 )/(W 2 +W 3 +W 4 +W 5 )＝(500+59.7)/(821.3+77.6+1+0.5)＝0.6216。
Through the calculation, after the electric heating complementary heat loop is added to reheat the turbine inlet air, the temperature of the air inlet turbine inlet is increased from 190 ℃ to 210 ℃. The electrical conversion efficiency of the system was 0.6216.
Compared with the method without increasing the electric conversion efficiency 0.6077 of the electric heating complementary heat loop, the efficiency of the compressed air energy storage system is improved by 1.39%. It can be concluded that the electric heating and heat supplementing loop is added at the front part of the air inlet of the expander, so that the system can be improved in functional capacity, and the electric conversion efficiency of the whole compressed air energy storage system can be improved.
Calculating the increased economic benefit according to the peak-to-valley electricity price comparison
The calculation of the application cases shows that the electric heating coupling is utilized to reheat the air entering the inlet of the three-stage expansion machine for the second time, the required energy is 15210.4kW, the energy is stored by adopting short electricity consumption low-valley time, and the price is the valley electricity price (the industrial valley electricity price in Shaanxi province can be checked to be 0.2168 yuan/kW.h). After the secondary reheating, the inlet temperature of the expander is increased, the capacity of the expander is increased by 12447.2kW, the energy is discharged at the peak value of electricity consumption, and the price is the peak electricity price (0.7976 yuan/kW.h for the peak electricity consumption of the large industrial power consumption of Shanxi province).
Therefore, after the electric heating coupling is adopted to reheat the air entering the inlet of the three-stage expander, the added economic benefit is as follows:
[ 12447.2 kW.0.7976 yuan/kW.h) - (15210.4 kW.0.2168 yuan/kW.h) ] 5h
= 33151.4 yuan
The compressed air energy storage system is additionally provided with an electric heating coupling means to reheat the air entering the inlet of the three-stage expansion machine for the second time, and the compressed air energy storage system is calculated to increase the output and input of part, so that the economic benefit can be increased by 33151.4 yuan per energy storage cycle.
The foregoing description of the preferred embodiments of the utility model is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the utility model. The foregoing is merely a preferred embodiment of the present utility model, and it should be noted that it will be apparent to those skilled in the art that modifications and variations can be made without departing from the technical principles of the present utility model, and these modifications and variations should also be regarded as the scope of the utility model.
Claims (3)
1. The utility model provides a novel thermoelectric coupling compressed air energy storage system, includes compressor unit, gas storage device (4) and the expansion unit that connects gradually, the compressor unit includes a plurality of compressors (2), the expansion unit includes a plurality of expanders (7), each grade the heat exchanger (3) are all connected to compressor (2) exit, heat exchanger (3) take away and get into next stage compression after compressing heat, the heat transfer medium high temperature export pipeline of heat exchanger (3) connects first low temperature liquid storage pot (6), its low temperature import pipeline connects first low temperature liquid storage pot (5), each grade expander (7) entrance all connects first reheat ware (8), first reheat ware (8) provide heat for the air that waits to expand, the heat transfer medium import pipeline of first reheat ware (8) is connected first high temperature liquid storage pot (6), its heat transfer medium export pipeline is connected first low temperature liquid storage pot (5), its characterized in that still includes the heat compensation circuit, the heat transfer medium liquid storage pot is including set up in each grade reheat ware (7) entrance second reheat ware (12), second high temperature liquid storage pot (10) are connected with second heat transfer medium (10) through second heat transfer medium (10) import, second high temperature liquid storage pot (10), the electric heater (11) heats the low-temperature heat exchange medium in the second low-temperature liquid storage tank (9) and then sends the low-temperature heat exchange medium into the second high-temperature liquid storage tank (10).
2. The novel thermally coupled compressed air energy storage system of claim 1, wherein the heat exchangers (3) are arranged in series for two groups of heat exchangers.
3. The novel thermally coupled compressed air energy storage system of claim 1, wherein said heat exchange medium is water.
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