CN117189287A - Compressed air energy storage and thermal power heat supply coupling system and planning operation method - Google Patents
Compressed air energy storage and thermal power heat supply coupling system and planning operation method Download PDFInfo
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Abstract
The invention relates to a compressed air energy storage and thermal power heat supply coupling system and a planning operation method thereof: the back pressure machine comprises a boiler for generating steam, a back pressure machine for supplying heat to external exhaust gas and outputting power, a generator for generating power through the back pressure machine, and a water circulation device for circulating the exhaust steam of the back pressure machine to the boiler; compressed air energy storage system: the system comprises a compressor system for compressing air, a gas storage system for storing compressed air, a turbine system for generating power for a generator by releasing the compressed air of the gas storage system, and a heat exchange system for respectively transmitting energy to the compressor system and the turbine system; the heat exchange system is finally communicated to the water circulation device, the scheme has no cold source loss of the condenser, and the heat generated in the compressed air energy storage operation process is completely remained in the thermodynamic system, so that higher energy utilization efficiency can be obtained; the scheme can match the heat supply and the power supply of the system according to the demand of the heat load and the electric load, and has stronger operation flexibility.
Description
Technical Field
The invention relates to the field of compressed air energy storage, in particular to a compressed air energy storage and thermal power heating coupling system and a planning operation method.
Background
The compressed air energy storage is used as one of energy storage modes, has the characteristics of cleanness, high efficiency, large scale and the like, and is one of the most promising energy storage technologies. The thermodynamic system of the compressed air system comprises a compressor system, a heat exchange system, a heat storage system, a turbine system, a gas storage chamber and other system components. When the load of the power grid is low, the compressed air energy storage system absorbs redundant electric quantity of the power grid, drives the compressor to do work, compresses air into high-pressure air and stores the high-pressure air in the air storage cavity. Heat is generated in the compression process, is exchanged out through a heat exchange system and is stored in a heat storage system. And when the power grid is in a load peak, the compressed air energy storage system releases high-pressure air from the air storage cavity, and the high-pressure air enters the turbine to expand and do work to generate power which is transmitted to the power grid, and the heat stored by the heat storage system is absorbed through the heat exchange system in the working process. In general, a large-scale heat storage device is needed for storing heat generated in the operation process by compressed air energy storage, the investment of a heat storage system is large, the heat generated by heat storage is larger than the heat required by heat release, and energy waste is inevitably generated.
The patent application number 2022108527224 discloses a cogeneration compressed air energy storage combined cycle power generation system and a method, which have the advantages that the steam consumption of a heat user is complementary with that of a small steam turbine, and the output of the back pressure type turbine generator is ensured not to be influenced by the change of a thermal load when the stability of the steam discharge of the back pressure type turbine generator is maintained; the small turbine directly drives the air compressor, so that the energy conversion process is reduced, and the efficiency of the small turbine for driving the air compressor is improved.
However, the scheme drives the small turbine to operate by taking exhaust steam of the back pressure type turbine generator as driving steam, and further drives the air compressor to operate by the small turbine. And exhaust steam after driving the small steam turbine to do work is discharged into the condenser and then enters the deaerator through the condensate pump. The cold source loss exists, and the improvement of the system operation efficiency is not utilized; and the condensate pump is energy-consuming equipment, so that the power consumption in the running process can be increased, namely, the back pressure unit runs in a heat fixed electricity mode, the load change adjusting capability is poor, and the generated energy is subjected to the change of the heat load.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides a compressed air energy storage and thermal power heating coupling system, which controls the operation parameters of devices in each system through reasonable planning, reasonably converts the energy of the whole system, greatly reduces the energy loss in the operation process of the system and solves the problems in the prior art.
To achieve the above object, the present invention is achieved by:
a planning operation method of a compressed air energy storage system and a thermal power heating system comprises the following steps:
s1: obtaining the deviation fluctuation range of the average power generation output force and the electric load of the back pressure machine;
s2: when the heat load of the system rises and the electric load of the system falls, the compressor is operated, the turbine is not operated, and the consumed power for operating the compressor is determined by means of the deviation fluctuation range curve;
s3: determining air flow and air pressure parameters when the compressor is operated by using the consumed power of the compressor;
s4: calculating the temperature of the desalted water replenishing water of the back pressure computer; the make-up water is conveyed to a water side inlet of the compression side heat exchanger; the water in the compression side heat exchanger receives heat transferred by the compressed air, the heat is lifted to the calculated temperature, and the water enters the deaerator to be recovered into the thermodynamic system; compressed air formed in the compression process enters the air storage chamber to store compression energy;
s5: when the thermal load of the system is reduced and the electrical load is increased, the compressor is not operated, the turbine is operated, and the power generation power of the turbine is determined by means of a fluctuation curve, so that the air flow parameter of the turbine is calculated and determined; the gas storage chamber is conveyed to the turbine according to the calculated air flow parameter; compressed air in the gas storage chamber enters a turbine to expand and do work;
s6: calculating heating steam flow in the turbine side heat exchanger, and conveying the heating steam flow by the turbine side heat exchanger according to the calculated data; before compressed air enters each stage of turbine cylinder, the air is heated by the turbine side heat exchanger through the heating steam flow of the back pressure machine exhaust steam and then enters the turbine cylinder.
As a further aspect of the present invention,
the average power generation output P of the back pressure machine in the step S1 b Heat supply flow rate Q b Deviation fluctuation range of average power generation output and electric load of back pressure machine
The compressor consumption power in S2 is calculated as:
the compressor air flow in S3 is determined by the formula:
w in the formula c_ Power consumption for the i-th stage compression cylinder; epsilon c_ The pressure ratio of the compression cylinder of the ith stage; m is m i A polytropic index for the i-th stage compression cylinder; r represents the gas constant of air; t (T) c__ Inlet temperature for the i-th stage compression cylinder; η (eta) d_ For the polytropic efficiency, eta of the ith stage of compression cylinder c_d For motor efficiency of compressor, Q c For a compressor air flow to be determined;
the outlet pressure of each stage of compression cylinder may be determined by the following equation:
p c__ ＝ε c_ p c__i
in p c__ Inlet pressure for the ith stage compression cylinder;
and (4) calculating the temperature of the desalted water replenishing water of the back pressure machine in the step (S4) as follows:
h in hx___ Indicating the enthalpy value of the air inlet of the ith stage heat exchanger, h hx__ut_ Representing the enthalpy value of the air outlet of the ith stage heat exchanger, Q c For compressor air flow, eta hx Indicating the heat exchange efficiency of the heat exchanger, h hx__ Representing the enthalpy value of the water medium inlet of the heat exchanger, c p Represents the specific heat capacity of water;
the turbine power generation in the step S5 is calculated as follows:
the turbine air flow is determined by the formula:
W t_i ＝(h t_out_i -h t_in_i )Q t η t_d
w in the formula t_i Indicating the output power of the turbine cylinder of the ith stage, h t_oui_i Indicating the enthalpy value of outlet air of the ith stage turbine cylinder, h t_in_i Representing the enthalpy value, Q, of the inlet air of the turbine cylinder of the ith stage t Indicating the air flow, eta, of the turbine to be determined t_d Representing the motor efficiency of the turbine;
the heating steam flow in the turbine side heat exchanger in S6 may be calculated as:
h in hx_a_in_i Indicating the enthalpy value of the air inlet of the ith stage heat exchanger, h Hx_a_out_i Representing the enthalpy value of the air outlet of the ith stage heat exchanger, Q t For turbine air flow, eta hx Indicating the heat exchange efficiency of the heat exchanger, h hx_w_out Indicating the enthalpy value of the water medium outlet of the heat exchanger, h hx_w_in Indicating the enthalpy of the heat exchanger heating steam.
A compressed air energy storage and thermal power heating coupling system applying the planning operation method, which comprises,
thermal power heating system: the back pressure machine comprises a boiler for generating steam, a back pressure machine for supplying heat to external exhaust gas and outputting power, a generator for generating power through the back pressure machine, and a water circulation device for circulating the exhaust steam of the back pressure machine to the boiler;
compressed air energy storage system: the system comprises a compressor system for compressing air, a gas storage system for storing compressed air, a turbine system for generating power for a generator by releasing the compressed air of the gas storage system, and a heat exchange system for respectively transmitting energy to the compressor system and the turbine system; the heat exchange system is finally communicated to the water circulation device;
the heat exchange system comprises a plurality of compression side heat exchangers and a plurality of turbine side heat exchangers; the compressor system is connected with the air inlet and outlet of each compression side heat exchanger, and the turbine system is connected with the air inlet and outlet of each turbine side heat exchanger;
the water circulation device comprises a deaerator and a water feed pump which is connected with the deaerator and outputs water to the boiler.
As a further aspect of the present invention, the gas storage system includes a gas storage chamber and a valve and a pipe for connection.
As a further scheme of the invention, the water side inlets of the compression side heat exchangers are converged into a main pipe through branch pipes and connected to the water supplementing pipeline, and each branch pipe is provided with a regulating valve; the water side outlets of the compression side heat exchangers are converged into a main pipe through branch pipes and connected to the water circulation device; the steam inlet of the turbine side heat exchanger is converged into a main pipe through branch pipes and is connected to an external heat supply pipeline of the back pressure machine, a first valve is arranged on the main pipe, and regulating valves are arranged on the branch pipes; the water outlet of the turbine side heat exchanger is converged into a main pipe through a branch pipe and is connected to a pipeline of the compression side heat exchanger connected with the water circulation device, and a second valve is arranged on the main pipe.
As a further scheme of the invention, the compressor system comprises a compressor, the compressor comprises a plurality of compression cylinders, valves and pipelines for connection, an air inlet of a first-stage compression cylinder is connected with the atmosphere through an air pipeline, each compression cylinder is connected with an air side of a corresponding compression side heat exchanger in series through an air pipeline, an air outlet of a last-stage compression cylinder is connected with the air side of the compression side heat exchanger and a gas storage system in series in sequence, and the compression cylinders between the first-stage compression cylinder and the last-stage compression cylinder are connected with adjacent compression cylinders in series through the compression side heat exchangers connected with the compression cylinders respectively.
As a further aspect of the invention, the compression cylinder is driven by a motor connected thereto, and the generator is connected to the motor of the compression cylinder by a power cable to supply driving power.
As a further scheme of the invention, the turbine system comprises a turbine, the turbine comprises a plurality of turbine cylinders, valves and pipelines for connection, the air inlet of the first-stage turbine cylinder is sequentially connected with the air side of the turbine-side heat exchanger and the air storage system in series, the turbine cylinders are connected with the air side of the turbine-side heat exchanger in series through the air pipelines, the air outlet of the last-stage turbine cylinder is connected with the atmosphere through the air pipelines, and the turbine cylinders between the first-stage turbine cylinder and the last-stage turbine cylinder are respectively connected with adjacent turbine cylinders in series through the turbine-side heat exchangers connected with the turbine cylinders.
As a further aspect of the invention, the turbine cylinders are connected in series by a shaft and are ultimately connected to a generator for generating electricity.
Compared with the prior art, the invention has the beneficial effects that:
1. the scheme has no cold source loss of the condenser, and the heat generated in the operation process of storing the energy of the compressed air is completely remained in the thermodynamic system, so that higher energy utilization efficiency can be obtained;
2. the scheme can match the heat supply and the power supply of the system according to the demand of the heat load and the electric load, and has stronger operation flexibility;
3. compared with the traditional compressed air energy storage system, the investment and the occupied area of the heat storage device are saved; the radiator is saved, the investment of the radiator is reduced, the heat dissipation loss is avoided, and the pressure loss of the compressed air in the radiator is reduced.
Drawings
FIG. 1 is a diagram showing a connection between a compressed air energy storage and thermal power heating coupling system according to the present invention;
FIG. 2 is a diagram of the material balance of the present invention;
fig. 3 is a step diagram of a method for planning and operating a compressed air energy storage system and a thermal power heating system according to the present invention.
Reference numerals: 1. a boiler; 2. a back press; 3. a generator; 4. a deaerator; 5. a water feed pump; 6. a second valve; 7. a regulating valve; 8. a motor; 9. a first valve; 11. a compression cylinder; 21. a compression side heat exchanger; 22. a turbine side heat exchanger; 31. a gas storage chamber; 51. a turbine cylinder.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all embodiments of the invention; 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 connection mode is as follows:
thermal power heating system: comprises a boiler 1 for generating steam, a back press 2 for supplying heat to the external exhaust gas and outputting power, a generator 3 for generating power through the back press 2, and a water circulation device for circulating the exhaust steam of the back press 2 to the boiler 1; specifically, a main steam outlet of the boiler 1 is connected to a main steam inlet of the back pressure machine 2 through a pipeline, a steam exhaust outlet of the back pressure machine 2 is connected to an external heat supply pipeline, a deoxygenated steam inlet of the deoxygenator 4 is connected to a water supply outlet of the deoxygenator 4 is connected to an inlet of the water supply pump 5 through a water pipeline, and an outlet of the water supply pump 5 is connected to a water supply inlet of the boiler 1 through a water pipeline; the output shaft of the back press 2 is connected to a generator 3 for generating electricity.
Compressed air energy storage system: the system comprises a compressor system for compressing air, a gas storage system for storing compressed air, a turbine system for generating power for the generator 3 by releasing the compressed air of the gas storage system, and a heat exchange system for respectively transmitting energy to the compressor system and the turbine system; the heat exchange system is finally communicated to the water circulation device.
The water circulation device comprises a deaerator 4 and a water supply pump 5 connected with the deaerator 4 and outputting water to the boiler 1, and the water circulation device in the thermal power heating system can comprise, but is not limited to, the water circulation device, and can also be other devices or systems capable of recirculating the exhaust gas in the back pressure machine 2 and the water of the heat exchange system in the compressed air energy storage system to the boiler 1.
Further, for the heat exchange system of the present invention, a plurality of compression side heat exchangers 21, and a plurality of turbine side heat exchangers 22 are included; the compressor system is connected with the air inlet and outlet of each compression side heat exchanger 21, the turbine system is connected with the air inlet and outlet of each turbine side heat exchanger 22, the water side inlets of the compression side heat exchangers 21 are converged into a main pipe through branch pipes to be connected to a water supplementing pipeline, and each branch pipe is provided with an adjusting valve 7; the water side outlets of the compression side heat exchangers 21 are collected into a main pipe through branch pipes and connected to a water circulation device; the steam inlet of the turbine side heat exchanger 22 is converged into a main pipe through branch pipes and is connected to an external heat supply pipeline of the back pressure machine 2, a first valve 9 is arranged on the main pipe, and a regulating valve 7 is arranged on each branch pipe; the water outlet of the turbine side heat exchanger 22 is converged into a main pipe through a branch pipe, and the main pipe is connected to a pipeline of the compression side heat exchanger 21 connected with a water circulation device, and a second valve 6 is arranged on the main pipe; the first valve 9 and the second valve 6 are used to control the operation and closing of the heat exchange system of the compressed air energy storage system.
The compressor system of the invention specifically comprises a compressor, wherein the compressor comprises a plurality of compression cylinders 11, valves and pipelines for connection, an air inlet of a first-stage compression cylinder 11 is connected with the atmosphere through an air pipeline, an air side of each compression cylinder 11 is connected with an air side of a corresponding compression side heat exchanger 21 through an air pipeline in series, an air outlet of a last-stage compression cylinder 11 is sequentially connected with the air side of the compression side heat exchanger 21 and a gas storage system in series, and the compression cylinders 11 between the first-stage compression cylinder 11 and the last-stage compression cylinder 11 are respectively connected with the adjacent compression cylinders 11 in series through the compression side heat exchangers 21 connected with the compression cylinders.
The compression cylinder 11 is driven by the connection motor 8, and the generator 3 is supplied with driving power by the motor 8 connected to the compression cylinder 11 through a power cable.
The turbine system of the invention comprises a turbine, and the turbine comprises a plurality of turbine cylinders 51, valves and pipelines for connection, wherein an air inlet of a first stage turbine cylinder 51 is sequentially connected with an air side of a turbine side heat exchanger 22 and a gas storage system in series, the turbine cylinders 51 are connected with the air side of the turbine side heat exchanger 22 in series through the air pipelines, an air outlet of a last stage turbine cylinder 51 is connected with the atmosphere through the air pipelines, and the turbine cylinders 51 between the first stage turbine cylinder 51 and the last stage turbine cylinder 51 are respectively connected with adjacent turbine cylinders 51 in series through the turbine side heat exchanger 22 connected with the air cylinders.
The turbine cylinders 51 are connected in series by a shaft and are finally connected to the generator 3 to generate electricity.
The planning operation method comprises the following steps:
referring to fig. 3, the invention provides a planning operation method of a compressed air energy storage system and a thermal power heating system, comprising the following steps:
1. when the heat load of the system rises and the electric load falls, the compressor is operated, and the turbine is not operated;
s1: obtaining the deviation fluctuation range of the average power generation output force and the electric load of the back pressure machine;
average power generation output P of back press b Heat supply flow rate Q b Deviation (fluctuation) range of average power generation output and electric load of back pressure machine
S2: determining compressor power consumption; the compressor is according to the calculated P c Doing work, sucking air in the atmosphere, and transferring heat generated by air compression to a water side conveyed by a water feeding pump through a compression side heat exchanger after a compression cylinder of each stage;
the compressor power consumption can be calculated as:
s3: calculating parameters of a compressor, and determining parameters such as air flow, air pressure and the like of the compressor; the compressor operates according to the calculated air flow and air pressure;
the compressor air flow may be determined by the formula:
w in the formula c_i Power consumption for the i-th stage compression cylinder; epsilon c_i The pressure ratio of the compression cylinder of the ith stage; m is m i A polytropic index for the i-th stage compression cylinder; r represents the gas constant of air; t (T) c_in_i Inlet temperature for the i-th stage compression cylinder; η (eta) d_i For the polytropic efficiency, eta of the ith stage of compression cylinder c_d For motor efficiency of compressor, Q c For the compressor air flow to be determined.
The outlet pressure of each stage of compression cylinder may be determined by the following equation:
p c_out_i ＝ε c_i p c_in_i
in p c_in_i Inlet pressure for the ith stage compression cylinder;
s4: calculating the temperature of the desalted water replenishing water of the back pressure computer; the make-up water is conveyed to a water side inlet of the compression side heat exchanger; the water in the compression side heat exchanger receives heat transferred by the compressed air, the heat is lifted to the calculated temperature, and the water enters the deaerator to be recovered into the thermodynamic system;
the temperature of the desalted water replenishing water of the back pressure machine is calculated as follows:
h in hx_a_in_i Indicating the enthalpy value of the air inlet of the ith stage heat exchanger, h hx_a_out_i Representing the enthalpy value of the air outlet of the ith stage heat exchanger, Q c For compressor air flow, eta hx Indicating the heat exchange efficiency of the heat exchanger, h hx_w_in Representing the enthalpy value of the water medium inlet of the heat exchanger (the enthalpy value of the desalted water supplement water), c p Represents the specific heat capacity of water;
compressed air formed in the compression process enters the air storage chamber to store compression energy.
2. When the thermal load of the system is reduced and the electric load is increased, the air storage chamber starts to release energy as the supplement of the electric load, the compressor does not operate, and the turbine operates;
s5, obtaining a deviation fluctuation range of average power generation output and electric load of the back pressure machine;
average power generation output P of back press b Heat supply flow rate Q b Deviation (fluctuation) range of average power generation output and electric load of back pressure machine
S6: determining the power generated by the turbine; the turbine being in accordance with calculated P t Performing work, wherein compressed air in the gas storage chamber enters a turbine to perform expansion work;
the turbine generated power can be calculated as:
s7: calculating turbine parameters, and determining parameters such as turbine air flow and the like; the gas storage chamber is conveyed to the turbine according to the calculated air flow; before compressed air enters each stage of turbine cylinder, the air is heated by the turbine side heat exchanger through the heating steam flow of the back pressure machine exhaust steam and then enters the turbine cylinder.
The turbine air flow may be determined by the formula:
W t_i ＝(h t_out_i -h t_in_i )Q t η t_d
w in the formula t_i Indicating the output power of the turbine cylinder of the ith stage, h t_out_i Indicating the enthalpy value of outlet air of the ith stage turbine cylinder, h t_in_i Representing the enthalpy value, Q, of the inlet air of the turbine cylinder of the ith stage t Indicating the air flow, eta, of the turbine to be determined t_d Representing the motor efficiency of the turbine.
S8: calculating the heating steam flow in the turbine side heat exchanger; the turbine side heat exchanger delivers a heating steam flow according to the calculated data.
The heating steam flow in the turbine side heat exchanger can be calculated as:
h in hx_a_in_i Indicating the enthalpy value of the air inlet of the ith stage heat exchanger, h hx_a_out_i Representing the enthalpy value of the air outlet of the ith stage heat exchanger, Q t For turbine air flow, eta hx Indicating the heat exchange efficiency of the heat exchanger, h hx__ Indicating the enthalpy value of the water medium outlet of the heat exchanger, h hx__ Indicating the enthalpy of the heat exchanger heating steam.
The operation mode is as follows:
working condition 1:
the heat load and the electric load of the system rise at the same time, the first valve 9 and the second valve 6 are closed, the generated energy and the heat supply are regulated through the back press 2, and the compressed air energy storage system does not operate.
Working condition 2:
the heat load and the electric load of the system are reduced simultaneously, the first valve 9 and the second valve 6 are closed, the generated energy and the heat supply are regulated through the back press 2, and the compressed air energy storage system does not operate.
Working condition 3:
when the system heat load rises and the electric load falls, the first valve 9 and the second valve 6 are closed, and the power generated by the generator 3 of the back pressure machine 2 drives the compression cylinder 11 to operate through a cable. The compressed air energy storage system receives electric energy from the generator 3, drives the compressor to do work, sucks air in the atmosphere, compresses the air through the compression cylinders 11, and transfers heat generated by the compression of the air to the water side through the compression side heat exchanger 21 between the compression cylinders 11 of each stage. The water in the compression side heat exchanger 21 receives heat transferred from the air, raises the temperature, and enters the deaerator 4 to recover the heat into the thermodynamic system. Compressed air formed during the compression process enters the air storage chamber 31 to store the compression energy.
Working condition 4:
when the system heat load is reduced and the electric load is increased, the first valve 9 and the second valve 6 are opened, and part of exhaust steam of the back pressure machine 2 enters the turbine side heat exchanger 22 through a steam pipeline to exchange heat. The compressed air in the air storage chamber 31 is released to enter the turbine for doing work, electric energy is generated and is transmitted to the electric power system to supplement electric load, and the air after doing work is discharged into the atmosphere. The heat transferred from the exhaust steam of the back press 2 is absorbed by the turbine side heat exchanger 22 before the air enters the turbine cylinder 51 of each stage. Part of exhaust steam of the back press 2 exchanges heat with compressed air and then enters the deaerator 4.
Operating parameters:
referring to fig. 2, the material numbering parameters of the following table are the parameters at each numbered position in fig. 2, and the parameters are the medium, flow, pressure, and temperature in the current pipeline when the system of the present invention is operated according to the planning method.
Working condition 3: typical material balance table of compressed air energy storage system operation under energy storage operating mode:
| material numbering | Temperature (DEG C) | Pressure MPa | Flow t/h | Medium (D) |
| 1 | 25 | 0.1 | 80 | Air-conditioner |
| 2 | 190 | 0.40 | 80 | Air-conditioner |
| 3 | 40 | 0.38 | 80 | Air-conditioner |
| 4 | 190 | 1.37 | 80 | Air-conditioner |
| 5 | 40 | 1.35 | 80 | Air-conditioner |
| 6 | 190 | 5.28 | 80 | Air-conditioner |
| 7 | 40 | 5.26 | 80 | Air-conditioner |
| 8 | 60 | 0.8 | 82 | Water and its preparation method |
| 9 | 25 | 0.8 | 82 | Water and its preparation method |
| 10 | 60 | 0.8 | 83 | Water and its preparation method |
| 11 | 25 | 0.8 | 83 | Water and its preparation method |
| 12 | 60 | 0.8 | 85 | Water and its preparation method |
| 13 | 25 | 0.8 | 85 | Water and its preparation method |
| 14 | 25 | 0.8 | 250 | Water and its preparation method |
| 15 | 60 | 0.8 | 250 | Water and its preparation method |
| 31 | 250 | ～20 | 355 | Water and its preparation method |
| 32 | 540 | 13.7 | 355 | Water vapor |
| 33 | 200 | 0.8 | 40 | Water vapor |
| 34 | 200 | 0.8 | 250 | Water vapor |
At the moment, the power generation capacity of the back pressure machine is about 50MW, the power consumption of the compressor is about 11MW, the power transmitted to the power system is about 39MW, and the external heat supply capacity is 250t/h.
Working condition 4: typical material balance table of compressed air energy storage system operation under the energy release operating mode:
at the moment, the power generation output of the back pressure machine is about 55MW, the turbine output is about 10MW, the power transmitted to the power system is about 65MW, and the external heat supply is 235t/h.
The foregoing is only illustrative of the present invention and is not to be construed as limiting the scope of the invention, and all equivalent structures or equivalent flow modifications which may be made by the teachings of the present invention and the accompanying drawings or which may be directly or indirectly employed in other related art are within the scope of the invention.
Claims (10)
1. A planning operation method of a compressed air energy storage system and a thermal power heating coupling system is characterized by comprising the following steps:
s1: obtaining the deviation fluctuation range of the average power generation output force and the electric load of the back pressure machine;
s2: when the heat load of the system rises and the electric load of the system falls, the compressor is operated, the turbine is not operated, and the consumed power for operating the compressor is determined by means of the deviation fluctuation range curve;
s3: determining air flow and air pressure parameters when the compressor is operated by using the consumed power of the compressor;
s4: calculating the temperature of the desalted water replenishing water of the back pressure computer; the make-up water is conveyed to a water side inlet of the compression side heat exchanger; the water in the compression side heat exchanger receives heat transferred by the compressed air, the heat is lifted to the calculated temperature, and the water enters the deaerator to be recovered into the thermodynamic system; compressed air formed in the compression process enters the air storage chamber to store compression energy;
s5: when the thermal load of the system is reduced and the electrical load is increased, the compressor is not operated, the turbine is operated, and the power generation power of the turbine is determined by means of a fluctuation curve, so that the air flow parameter of the turbine is calculated and determined; the gas storage chamber is conveyed to the turbine according to the calculated air flow parameter; compressed air in the gas storage chamber enters a turbine to expand and do work;
s6: calculating heating steam flow in the turbine side heat exchanger, and conveying the heating steam flow by the turbine side heat exchanger according to the calculated data; before compressed air enters each stage of turbine cylinder, the air is heated by the turbine side heat exchanger through the heating steam flow of the back pressure machine exhaust steam and then enters the turbine cylinder.
2. The method for planning and operating a compressed air energy storage system and a thermal power and heating coupling system according to claim 1,
the average power generation output P of the back pressure machine in the step S1 b Heat supply flow rate Q b Deviation fluctuation range of average power generation output and electric load of back pressure machine
The compressor consumption power in S2 is calculated as:
the compressor air flow in S3 is determined by the formula:
w in the formula c_i Power consumption for the i-th stage compression cylinder; epsilon c_i The pressure ratio of the compression cylinder of the ith stage; m is m i A polytropic index for the i-th stage compression cylinder; r represents the gas constant of air; t (T) c_in_i Inlet temperature for the i-th stage compression cylinder; η (eta) d_i For the polytropic efficiency, eta of the ith stage of compression cylinder c_d For motor efficiency of compressor, Q c For a compressor air flow to be determined;
the outlet pressure of each stage of compression cylinder may be determined by the following equation:
p c_out_i ＝ε c_i p c_in_i
in p c_in_i Inlet pressure for the ith stage compression cylinder;
and (4) calculating the temperature of the desalted water replenishing water of the back pressure machine in the step (S4) as follows:
h in hx_a_in_i Indicating the enthalpy value of the air inlet of the ith stage heat exchanger, h hx_a_out_i Representing the enthalpy value of the air outlet of the ith stage heat exchanger, Q c For compressor air flow, eta hx Indicating the heat exchange efficiency of the heat exchanger, h hx_w_in Representing the enthalpy value of the water medium inlet of the heat exchanger, c p Represents the specific heat capacity of water;
the turbine power generation in the step S5 is calculated as follows:
the turbine air flow is determined by the formula:
W t_i ＝(h t_out_i -h t_in_i )Q t η t_d
w in the formula t_i Indicating the output power of the turbine cylinder of the ith stage, h t_out_i Indicating the enthalpy value of outlet air of the ith stage turbine cylinder, h t_in_i Representing the enthalpy value, Q, of the inlet air of the turbine cylinder of the ith stage t Indicating the air flow, eta, of the turbine to be determined t_d Representing the motor efficiency of the turbine;
the heating steam flow in the turbine side heat exchanger in S6 may be calculated as:
h in hx_a_in_i Indicating the enthalpy value of the air inlet of the ith stage heat exchanger, h hx_a_out_i Representing the enthalpy value of the air outlet of the ith stage heat exchanger, Q t For turbine air flow, eta hx Indicating the heat exchange efficiency of the heat exchanger, h hx_w_out Indicating the enthalpy value of the water medium outlet of the heat exchanger, h hx_w_in Indicating the enthalpy of the heat exchanger heating steam.
3. A compressed air energy storage and thermal power heating coupling system using the method of claim 1, comprising,
thermal power heating system: comprises a boiler (1) for generating steam, a back pressure machine (2) for supplying heat to external exhaust gas and outputting power, a generator (3) for generating power through the back pressure machine (2), and a water circulation device for circulating the exhaust steam of the back pressure machine (2) to the boiler (1);
compressed air energy storage system: the system comprises a compressor system for compressing air, a gas storage system for storing compressed air, a turbine system for generating power for a generator (3) by releasing the compressed air of the gas storage system, and a heat exchange system for respectively transmitting energy to the compressor system and the turbine system; the heat exchange system is finally communicated to the water circulation device;
the heat exchange system comprises a plurality of compression side heat exchangers (21) and a plurality of turbine side heat exchangers (22); the compressor system is connected with the air inlet and outlet of each compression side heat exchanger (21), and the turbine system is connected with the air inlet and outlet of each turbine side heat exchanger (22);
the water circulation device comprises a deaerator (4) and a water feed pump (5) which is connected with the deaerator (4) and outputs water to the boiler (1).
4. A compressed air energy storage and thermal power heating coupling system according to claim 3, characterized in that the gas storage system comprises a gas storage chamber (31) and valves and pipes for connection.
5. A compressed air energy storage and thermal power heating coupling system according to claim 3, characterized in that the water side inlets of the compression side heat exchangers (21) are collected into a main pipe through branch pipes to be connected to the make-up water pipeline, and each branch pipe is provided with an adjusting valve (7); the water side outlets of the compression side heat exchangers (21) are converged into a main pipe through branch pipes and connected to a water circulation device; the steam inlet of the turbine side heat exchanger (22) is converged into a main pipe through branch pipes, the main pipe is connected to an external heat supply pipeline of the back pressure machine (2), a first valve (9) is arranged on the main pipe, and regulating valves (7) are arranged on the branch pipes; the water outlets of the turbine side heat exchangers (22) are converged into a main pipe through branch pipes, the main pipe is connected to a pipeline of the compression side heat exchangers (21) connected with the water circulation device, and a second valve (6) is arranged on the main pipe.
6. The compressed air energy storage and thermal power heating coupling system according to claim 5, wherein the compressor system comprises a compressor, the compressor comprises a plurality of compression cylinders (11) and valves and pipelines for connection, an air inlet of a first stage compression cylinder (11) is connected with the atmosphere through an air pipeline, an air side of each compression cylinder (11) and a corresponding compression side heat exchanger (21) are connected in series through an air pipeline, an air outlet of a last stage compression cylinder (11) and an air side of the compression side heat exchanger (21) and a gas storage system are sequentially connected in series, and the compression cylinders (11) between the first stage compression cylinder (11) and the last stage compression cylinder (11) are respectively connected in series with adjacent compression cylinders (11) through the compression side heat exchangers (21) connected with the compression cylinders.
7. A compressed air energy storage and thermal power heating coupling system according to claim 6, characterized in that the compression cylinder (11) is driven by connecting the electric motor (8), the generator (3) being connected to the electric motor (8) of the compression cylinder (11) by means of a power cable for providing driving electric energy.
8. The coupling system for storing energy in compressed air and supplying heat by thermal power according to claim 5, wherein the turbine system comprises a turbine, the turbine comprises a plurality of turbine cylinders (51) and valves and pipelines for connection, the air inlet of the first stage turbine cylinder (51) is sequentially connected with the air side of the turbine side heat exchanger (22) and the gas storage system in series, the turbine cylinder (51) is connected with the air side of the turbine side heat exchanger (22) in series through the air pipeline, the air outlet of the last stage turbine cylinder (51) is connected with the atmosphere through the air pipeline, and the turbine cylinders (51) between the first stage turbine cylinder and the last stage turbine cylinder (51) are respectively connected with the adjacent turbine cylinders (51) in series through the turbine side heat exchangers (22) connected with the turbine cylinders.
9. The coupling system for storing energy in compressed air and supplying heat from thermal power according to claim 8, wherein the turbine cylinder (51) is connected in series through a shaft and finally connected to the generator (3) for generating electricity.
10. The coupling system for storing energy in compressed air and supplying heat from thermal power according to claim 8, wherein the turbine cylinder (51) is connected in series through a shaft and finally connected to the generator (3) for generating electricity.
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