A compressed air energy storage and coal-fired heating supply coupling system and a planning operation method

Abstract

The application relates to a compressed air energy storage and heat supply system coupled with a thermal power supply and a planning operation method, which comprises a boiler for generating steam, a back pressure machine for exhausting steam for heat supply and output power, a generator for generating power through the back pressure machine, and a water circulation device for circulating the back pressure machine exhaust steam to the boiler; a compressed air energy storage system, which comprises a compressor system for compressing air, a gas storage system for storing the compressed air, a turbine system for generating power through the compressed air released from the gas storage system, and a heat exchange system for transferring energy to the compressor system and the turbine system respectively; and the heat exchange system is finally connected to the water circulation device, so that the cold source loss of the condenser is avoided, the heat generated in the compressed air energy storage operation process is completely left in the thermal system, and relatively high energy utilization efficiency can be obtained; the scheme can match the heat supply and power supply of the system according to the demand of heat and power loads, and has relatively strong operation flexibility.

Description

Technical Field

[0001] This invention relates to the field of compressed air energy storage, and specifically to a compressed air energy storage coupled with thermal power heating system and its planning and operation method. Background Technology

[0002] Compressed air energy storage, as a type of energy storage, is characterized by its cleanliness, high efficiency, and scalability, making it one of the most promising energy storage technologies. The thermal system of a compressed air system includes components such as a compressor system, heat exchange system, thermal storage system, turbine system, and air storage chamber. During periods of low grid load, the compressed air energy storage system absorbs excess electricity from the grid, driving the compressor to compress air into high-pressure air, which is then stored in the air storage chamber. Heat is generated during compression, which is exchanged through the heat exchange system and stored in the thermal storage system. During periods of high grid load, the compressed air energy storage system releases high-pressure air from the air storage chamber, which enters the turbine to expand and generate electricity, which is then fed back to the grid. During this process, the heat stored in the thermal storage system is absorbed through the heat exchange system. Typically, compressed air energy storage requires large-scale thermal storage devices to store the heat generated during operation. These systems involve significant investment, and the amount of heat generated often exceeds the amount of heat released, inevitably leading to energy waste.

[0003] Patent application number 2022108527224 discloses a combined cycle power generation system and method for cogeneration and compressed air energy storage. The advantages are that the steam consumption of heat users and the steam consumption of small steam turbines are complementary, ensuring that the output of the back-pressure steam turbine generator is no longer affected by changes in heat load while maintaining the stability of the exhaust steam volume. The small steam turbine directly drives the air compressor, reducing the energy conversion process and improving the efficiency of the small steam turbine driving the air compressor.

[0004] However, this scheme uses exhaust steam from a back-pressure turbine generator to drive a small turbine, which in turn drives an air compressor. The exhaust steam from the small turbine is then discharged into the condenser and pumped into the deaerator. This results in cooling losses and does not improve system efficiency. Furthermore, the condensate pump is an energy-consuming device, increasing power consumption during operation. In other words, the back-pressure unit operates in a heat-driven power generation mode, exhibiting poor load regulation capabilities, and its power generation is constrained by changes in heat load. Summary of the Invention

[0005] To address the shortcomings of existing technologies, this invention provides a compressed air energy storage and thermal power heating coupling system. Through rational planning and control of the operating parameters of devices in each system, the energy of the entire system is rationally converted, greatly reducing energy loss during system operation and solving the problems mentioned in the background technology.

[0006] To achieve the above objectives, the present invention is implemented as follows:

[0007] A planning and operation method for a compressed air energy storage system and a thermal power heating system includes the following steps:

[0008] S1: Obtain the deviation range of the average power output of the back pressure unit from the electrical load;

[0009] S2: When the system heat load increases and the electrical load decreases, the compressor runs while the turbine does not run. The power consumption of the running compressor is determined by the deviation fluctuation range curve.

[0010] S3: Use the power consumption of the compressor to determine the air flow and air pressure parameters when the compressor is running;

[0011] S4: Calculate the temperature of the demineralized water makeup water for the back pressure unit; the makeup water is delivered to the water-side inlet of the compression-side heat exchanger; the water in the compression-side heat exchanger receives heat from the compressed air, is raised to the calculated temperature, and enters the deaerator to recover the heat into the thermal system; the compressed air formed during the compression process enters the air storage chamber to store the compression energy.

[0012] S5: When the system heat load decreases and the electrical load increases, the compressor does not run, but the turbine runs. The power generation of the turbine is determined by the fluctuation curve, and the air flow parameters of the turbine are calculated and determined. The air storage chamber delivers the air to the turbine according to the calculated air flow parameters. The compressed air in the air storage chamber enters the turbine and expands to do work.

[0013] S6: Calculate the heating steam flow rate in the turbine-side heat exchanger. The turbine-side heat exchanger delivers the heating steam flow rate according to the calculated data. Before the compressed air enters each stage of the turbine cylinder, the air is heated by the heating steam flow rate of the back compressor exhaust through the turbine-side heat exchanger before entering the turbine cylinder.

[0014] As a further aspect of the present invention,

[0015] The average power output P of the back pressure unit in S1 b Heating flow rate Q b The deviation range of the average power generation output of the back-pressure turbine from the electrical load

[0016] The power consumption of the compressor in S2 is calculated as follows:

[0017]

[0018] The compressor airflow rate in S3 is determined by the formula:

[0019]

[0020]

[0021] In the formula W c_ ε represents the power consumption of the i-th stage compression cylinder; c_ The pressure ratio of the i-th stage compression cylinder; m i R represents the polytropic index of the i-th stage compressor cylinder; R represents the gas constant of air; T c__ η is the inlet temperature of the i-th stage compression cylinder; d_ For the polytropic efficiency of the i-th stage compression cylinder, η c_d Q represents the motor efficiency of the compressor. c The compressor airflow rate needs to be determined;

[0022] The outlet pressure of each stage of the compression cylinder can be determined by the following formula:

[0023] p c__ =ε c_ p c__i

[0024] In the formula p c__ Let be the inlet pressure of the i-th stage compression cylinder;

[0025] The back pressure turbine demineralized water makeup water temperature in S4 is calculated using the following formula:

[0026]

[0027] In the formula h hx___ h represents the enthalpy value of the air inlet of the i-th stage heat exchanger. hx__ut_ Q represents the enthalpy of the air outlet of the i-th stage heat exchanger. c η is the air flow rate of the compressor. hx h represents the heat exchange efficiency of the heat exchanger. hx__ c represents the enthalpy value at the inlet of the water medium in the heat exchanger. p This indicates the specific heat capacity of water;

[0028] The turbine power generation capacity in S5 is calculated as follows:

[0029]

[0030] The airflow rate of a turbine is determined by the formula:

[0031] W t_i =(h t_out_i -h t_in_i )Q t η t_d

[0032]

[0033] In the formula W t_i h represents the output power of the i-th stage turbine cylinder. t_oui_ih represents the enthalpy of the outlet air of the i-th stage turbine cylinder. t_in_i Q represents the enthalpy of the inlet air of the i-th stage turbine cylinder. t η represents the airflow rate of the turbine that needs to be determined. t_d This indicates the motor efficiency of the turbine;

[0034] The heating steam flow rate in the turbine-side heat exchanger in S6 can be calculated as follows:

[0035]

[0036] In the formula h hx_a_in_i h represents the enthalpy value of the air inlet of the i-th stage heat exchanger. Hx_a_out_i Q represents the enthalpy of the air outlet of the i-th stage heat exchanger. t η is the airflow rate of the turbine. hx h represents the heat exchange efficiency of the heat exchanger. hx_w_out h represents the enthalpy value at the outlet of the water medium in the heat exchanger. hx_w_in This indicates the enthalpy value of the steam heated by the heat exchanger.

[0037] A compressed air energy storage and thermal power heating coupling system using the above-mentioned planning and operation method includes,

[0038] Thermal power heating system: includes a boiler that generates steam, a back pressure turbine for exhausting heat and outputting power, a generator that generates electricity through the back pressure turbine, and a water circulation device for circulating the exhaust steam from the back pressure turbine back to the boiler.

[0039] Compressed air energy storage system: includes a compressor system that compresses air, an air storage system that stores the compressed air, a turbine system that generates electricity by releasing the compressed air from the air storage system, and a heat exchange system that transfers energy to the compressor system and the turbine system respectively; the heat exchange system is finally connected to a water circulation device.

[0040] The heat exchange system includes several compression-side heat exchangers and several turbine-side heat exchangers; the compressor system is connected to the air-side inlet and outlet of each compression-side heat exchanger, and the turbine system is connected to the air-side inlet and outlet of each turbine-side heat exchanger.

[0041] The water circulation system includes a deaerator and a feedwater pump connected to the deaerator and supplying water to the boiler.

[0042] As a further aspect of the present invention, the gas storage system includes a gas storage chamber and valves and pipes for connection.

[0043] As a further embodiment of the present invention, the water inlet of the compression-side heat exchanger is connected to the makeup water pipeline via branch pipes to form a main pipe, and each branch pipe is equipped with a regulating valve; the water outlet of the compression-side heat exchanger is connected to the water circulation device via branch pipes to form a main pipe; the steam inlet of the turbine-side heat exchanger is connected to the external heating pipeline of the back pressure unit via branch pipes to form a main pipe, and a first valve is installed on the main pipe, and each branch pipe is equipped with a regulating valve; the water outlet of the turbine-side heat exchanger is connected to the pipeline connecting the compression-side heat exchanger and the water circulation device via branch pipes to form a main pipe, and a second valve is installed on the main pipe.

[0044] As a further aspect of the present invention, the compressor system includes a compressor, which includes a plurality of compression cylinders and valves and pipes for connection. The air inlet of the first-stage compression cylinder is connected to the atmosphere through an air pipe. Each compression cylinder is connected in series with the air side of the corresponding compression-side heat exchanger through an air pipe. The air outlet of the last-stage compression cylinder is connected in series with the air side of the compression-side heat exchanger and the air storage system in sequence. The compression cylinders between the first-stage and last-stage compression cylinders are respectively connected in series with the adjacent compression cylinders through their connected compression-side heat exchangers.

[0045] As a further embodiment of the present invention, the compression cylinder is driven by a connected electric motor, and the generator is connected to the electric motor of the compression cylinder via a power cable to provide driving power.

[0046] As a further aspect of the present invention, the turbine system includes a turbine, which includes a plurality of turbine cylinders and valves and pipes for connection. The air inlet of the first-stage turbine cylinder is connected in series with the air side of the turbine-side heat exchanger and the gas storage system. The turbine cylinder is connected in series with the air side of the turbine-side heat exchanger through an air pipe. The air outlet of the last-stage turbine cylinder is connected to the atmosphere through an air pipe. The turbine cylinders between the first-stage and last-stage turbine cylinders are connected in series with the adjacent turbine cylinders through the turbine-side heat exchangers they are connected to.

[0047] As a further embodiment of the present invention, the turbine cylinders are connected in series via shafts and ultimately connected to a generator to generate electricity.

[0048] Compared with the prior art, the beneficial effects of this invention are:

[0049] 1. This scheme eliminates the cold source loss of the condenser and retains all the heat generated during the operation of compressed air energy storage in the thermal system, thus achieving relatively high energy utilization efficiency.

[0050] 2. This solution can match the system's heat supply and power supply according to the demand for heat and electricity loads, and has strong operational flexibility;

[0051] 3. Compared with traditional compressed air energy storage systems, it saves investment and space for heat storage devices; it saves radiators, reduces radiator investment, eliminates heat loss, and reduces pressure loss of compressed air in radiators. Attached Figure Description

[0052] Figure 1 This is a connection diagram of a compressed air energy storage and thermal power heating coupling system according to the present invention;

[0053] Figure 2 This is the material balance diagram of the present invention;

[0054] Figure 3 This is a flowchart illustrating the planning and operation method of a compressed air energy storage system and a thermal power heating system according to the present invention.

[0055] Reference numerals: 1. Boiler; 2. Back pressure machine; 3. Generator; 4. Deaerator; 5. Feed water pump; 6. Second valve; 7. Regulating valve; 8. Electric motor; 9. First valve; 11. Compression cylinder; 21. Compression-side heat exchanger; 22. Turbine-side heat exchanger; 31. Gas storage chamber; 51. Turbine cylinder. Detailed Implementation

[0056] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0057] Connection method:

[0058] The thermal power heating system includes a boiler 1 that generates steam, a back pressure turbine 2 that exhausts steam for external heating and power output, a generator 3 that generates electricity through the back pressure turbine 2, and a water circulation device for circulating the exhaust steam from the back pressure turbine 2 back to the boiler 1. Specifically, the main steam outlet of the boiler 1 is connected to the main steam inlet of the back pressure turbine 2 via a pipeline. The exhaust steam outlet of the back pressure turbine 2 is connected to both an external heating pipeline and the deaerated steam inlet of the deaerator 4. The feedwater outlet of the deaerator 4 is connected to the inlet of the feedwater pump 5 via a water pipeline, and the outlet of the feedwater pump 5 is connected to the feedwater inlet of the boiler 1 via a water pipeline. The output shaft of the back pressure turbine 2 is connected to the generator 3 for power generation.

[0059] Compressed air energy storage system: includes a compressor system for compressing air, an air storage system for storing compressed air, a turbine system for generating electricity by releasing compressed air from the air storage system to the generator 3, and a heat exchange system for transferring energy to the compressor system and the turbine system respectively; the heat exchange system is finally connected to the water circulation device.

[0060] The water circulation device includes a deaerator 4 and a feed water pump 5 connected to the deaerator 4 and outputting water to the boiler 1. The water circulation device in the thermal power heating system may include, but is not limited to, the water circulation device mentioned in this invention, or other devices or systems that can recirculate the exhaust gas in the back pressure machine 2 and the water in the heat exchange system of the compressed air energy storage system back to the boiler 1.

[0061] Furthermore, the heat exchange system of the present invention includes a plurality of compression-side heat exchangers 21 and a plurality of turbine-side heat exchangers 22; the compressor system is connected to the air-side inlet and outlet of each compression-side heat exchanger 21, the turbine system is connected to the air-side inlet and outlet of each turbine-side heat exchanger 22, the water-side inlet of the compression-side heat exchanger 21 is connected to the makeup water pipeline through a main pipe formed by branch pipes, and a regulating valve 7 is installed on each branch pipe; the water-side outlet of the compression-side heat exchanger 21 is connected to the water circulation device through a main pipe formed by branch pipes; the steam inlet of the turbine-side heat exchanger 22 is connected to the external heating pipeline of the back compressor 2 through a main pipe formed by branch pipes, a first valve 9 is installed on the main pipe, and a regulating valve 7 is installed on each branch pipe; the water outlet of the turbine-side heat exchanger 22 is connected to the pipeline connecting the compression-side heat exchanger 21 and the water circulation device through a main pipe formed by branch pipes, and a second valve 6 is installed on the main pipe; the first valve 9 and the second valve 6 are used to control the operation and shutdown of the heat exchange system of the compressed air energy storage system.

[0062] The compressor system of the present invention specifically includes a compressor, which includes a plurality of compression cylinders 11 and valves and pipes for connection. The air inlet of the first-stage compression cylinder 11 is connected to the atmosphere through an air pipe. Each compression cylinder 11 is connected in series with the air side of the corresponding compression-side heat exchanger 21 through an air pipe. The air outlet of the last-stage compression cylinder 11 is connected in series with the air side of the compression-side heat exchanger 21 and the air storage system in sequence. The compression cylinders 11 between the first-stage and last-stage compression cylinders 11 are connected in series with the adjacent compression cylinders 11 through the compression-side heat exchangers 21 they are connected to.

[0063] The compression cylinder 11 is driven by a connected electric motor 8, and the generator 3 is connected to the electric motor 8 of the compression cylinder 11 via a power cable to provide driving power.

[0064] The turbine system of the present invention specifically includes a turbine, which includes a plurality of turbine cylinders 51 and valves and pipes for connection. The air inlet of the first-stage turbine cylinder 51 is connected in series with the air side of the turbine-side heat exchanger 22 and the gas storage system. The turbine cylinder 51 is connected in series with the air side of the turbine-side heat exchanger 22 through an air pipe. The air outlet of the last-stage turbine cylinder 51 is connected to the atmosphere through an air pipe. The turbine cylinders 51 between the first-stage and last-stage turbine cylinders 51 are connected in series with the adjacent turbine cylinders 51 through the turbine-side heat exchanger 22 they are connected to.

[0065] Turbine cylinder 51 is connected in series via a shaft and is ultimately connected to generator 3 to generate electricity.

[0066] Planning and operation methods:

[0067] See Figure 3 This invention provides a planning and operation method for a compressed air energy storage system and a thermal power heating system, comprising the following steps:

[0068] 1. When the system's thermal load increases and electrical load decreases, the compressor runs, but the turbine does not.

[0069] S1: Obtain the deviation range of the average power output of the back pressure unit from the electrical load;

[0070] Average power output P of back pressure unit b Heating flow rate Q b The deviation (fluctuation) range between the average power output of the back-pressure turbine and the electrical load.

[0071] S2: Determine the compressor's power consumption; the compressor operates according to the calculated P... c To perform work, air is drawn in from the atmosphere. After each stage of the compression cylinder, the heat generated by the air compression is transferred to the water side delivered by the feed water pump through the compression-side heat exchanger.

[0072] The power consumption of the compressor can be calculated as follows:

[0073]

[0074] S3: Calculate compressor parameters, determine compressor airflow, air pressure and other parameters; the compressor operates according to the calculated airflow and air pressure;

[0075] The compressor airflow rate can be determined by the formula:

[0076]

[0077]

[0078] In the formula W c_i ε represents the power consumption of the i-th stage compression cylinder; c_i Let m be the pressure ratio of the i-th stage compression cylinder; i R represents the polytropic index of the i-th stage compressor cylinder; R represents the gas constant of air; T c_in_i η is the inlet temperature of the i-th stage compression cylinder; d_i For the polytropic efficiency of the i-th stage compression cylinder, η c_d Q represents the motor efficiency of the compressor. c The compressor airflow needs to be determined.

[0079] The outlet pressure of each stage of the compression cylinder can be determined by the following formula:

[0080] p c_out_i =ε c_i p c_in_i

[0081] In the formula p c_in_i Let be the inlet pressure of the i-th stage compression cylinder;

[0082] S4: Calculate the temperature of the demineralized water makeup water for the back pressure unit; the makeup water is delivered to the water-side inlet of the compression-side heat exchanger; the water in the compression-side heat exchanger receives heat from the compressed air, is raised to the calculated temperature, and enters the deaerator to recover the heat into the thermal system.

[0083] The demineralized water make-up water temperature of the back pressure unit is calculated using the following formula:

[0084]

[0085] In the formula h hx_a_in_i h represents the enthalpy value of the air inlet of the i-th stage heat exchanger. hx_a_out_i Q represents the enthalpy of the air outlet of the i-th stage heat exchanger. c η is the air flow rate of the compressor. hx h represents the heat exchange efficiency of the heat exchanger. hx_w_in c represents the enthalpy of the water medium at the inlet of the heat exchanger (i.e., the enthalpy of the demineralized water makeup water). p This indicates the specific heat capacity of water;

[0086] The compressed air generated during the compression process enters the air storage chamber to store the compressed energy.

[0087] 2. When the system's thermal load decreases and electrical load increases, the gas storage chamber begins to release energy to supplement the electrical load. The compressor does not run, but the turbine does.

[0088] S5: Obtain the deviation range of the average power output of the back pressure unit from the electrical load.

[0089] Average power output P of back pressure unit b Heating flow rate Q b The deviation (fluctuation) range between the average power output of the back-pressure turbine and the electrical load.

[0090] S6: Determine the turbine's power generation capacity; the turbine operates according to the calculated P... t To perform work, the compressed air in the storage chamber enters the turbine and expands to do work;

[0091] The power generation capacity of a turbine can be calculated as follows:

[0092]

[0093] S7: Calculate turbine parameters and determine turbine air flow rate and other parameters; the air storage chamber delivers air to the turbine according to the calculated air flow rate; before the compressed air enters each stage turbine cylinder, the air is heated by the heating steam flow rate of the back pressure turbine exhaust through the turbine-side heat exchanger before entering the turbine cylinder.

[0094] The air flow rate of a turbine can be determined by the formula:

[0095] W t_i =(h t_out_i -h t_in_i )Q t η t_d

[0096]

[0097] In the formula W t_i h represents the output power of the i-th stage turbine cylinder. t_out_i h represents the enthalpy of the outlet air of the i-th stage turbine cylinder. t_in_i Q represents the enthalpy of the inlet air of the i-th stage turbine cylinder. t η represents the turbine airflow rate that needs to be determined. t_d This indicates the motor efficiency of the turbine.

[0098] S8: Calculate the heating steam flow rate in the turbine-side heat exchanger; the turbine-side heat exchanger delivers the heating steam flow rate according to the calculated data.

[0099] The heating steam flow rate in the turbine-side heat exchanger can be calculated as follows:

[0100]

[0101] In the formula h hx_a_in_i h represents the enthalpy value of the air inlet of the i-th stage heat exchanger. hx_a_out_i Q represents the enthalpy of the air outlet of the i-th stage heat exchanger. t η is the airflow rate of the turbine. hx h represents the heat exchange efficiency of the heat exchanger. hx__ h represents the enthalpy value at the outlet of the water medium in the heat exchanger. hx__ This indicates the enthalpy value of the steam heated by the heat exchanger.

[0102] Operating method:

[0103] Operating Condition 1:

[0104] When the system's thermal load and electrical load increase simultaneously, the first valve 9 and the second valve 6 are closed. The power generation and heat supply are regulated by the back pressure unit 2, and the compressed air energy storage system does not operate.

[0105] Operating Condition 2:

[0106] The system's thermal load and electrical load decrease simultaneously, the first valve 9 and the second valve 6 are closed, and the power generation and heat supply are regulated by the back pressure machine 2. The compressed air energy storage system does not operate.

[0107] Operating Condition 3:

[0108] When the system's thermal load increases and electrical load decreases, the first valve 9 and the second valve 6 close. The electricity generated by the generator 3 of the back compressor 2 drives the compression cylinder 11 through the cable. The compressed air energy storage system receives electrical energy from the generator 3, drives the compressor to do work, draws in air from the atmosphere, and compresses the air through the compression cylinder 11. Between each stage of the compression cylinder 11, the heat generated by the air compression is transferred to the water side through the compression-side heat exchanger 21. The water in the compression-side heat exchanger 21 receives the heat transferred from the air, increases its temperature, and enters the deaerator 4 to recover the heat into the thermal system. The compressed air formed during the compression process enters the air storage chamber 31 to store the compression energy.

[0109] Operating Condition 4:

[0110] When the system's thermal load decreases and electrical load increases, valves 9 and 6 open, allowing part of the exhaust steam from the back compressor 2 to enter the turbine-side heat exchanger 22 via the steam pipe for heat exchange. Compressed air from the storage chamber 31 is released into the turbine to perform work, generating electricity which is then transmitted to the power system as a supplement to the electrical load. The air after performing work is discharged into the atmosphere. Before entering each stage turbine cylinder 51, the air first absorbs the heat transferred from the exhaust steam from the back compressor 2 through the turbine-side heat exchanger 22. After heat exchange with the compressed air, part of the exhaust steam from the back compressor 2 enters the deaerator 4.

[0111] Operating parameters:

[0112] See Figure 2 The material number parameters in the following table are: Figure 2 The parameters at each numerical position are the medium, flow rate, pressure, and temperature in the pipeline when the system of this invention is running according to the planning method.

[0113] Operating Condition 3: Typical material balance sheet for compressed air energy storage system operating under energy storage conditions:

[0114] 1 25 0.1 80 Air 2 190 0.40 80 Air 3 40 0.38 80 Air 4 190 1.37 80 Air 5 40 1.35 80 Air 6 190 5.28 80 Air 7 40 5.26 80 Air 8 60 0.8 82 water 9 25 0.8 82 water 10 60 0.8 83 water 11 25 0.8 83 water 12 60 0.8 85 water 13 25 0.8 85 water 14 25 0.8 250 water 15 60 0.8 250 water 31 250 ～20 355 water 32 540 13.7 355 water vapor 33 200 0.8 40 water vapor 34 200 0.8 250 water vapor

[0115] At this time, the back pressure generator output is about 50MW, the compressor power consumption is about 11MW, the power transmitted to the power system is about 39MW, and the external heat supply is 250t / h.

[0116] Operating Condition 4: Typical material balance sheet for compressed air energy storage system operating under energy release conditions:

[0117]

[0118]

[0119] At this time, the back pressure generator output 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.

[0120] The above are merely embodiments of the present invention and do not limit the patent scope of the present invention. Any equivalent structural or procedural transformations made based on the content of the present invention specification and drawings, or direct or indirect applications in other related technical fields, are similarly included within the patent protection scope of the present invention.

Claims

1. A planning and operation method for a compressed air energy storage system coupled with a thermal power heating system, characterized in that, Includes the following steps: S1: Obtain the deviation range of the average power output of the back pressure unit from the electrical load; S2: When the system heat load increases and the electrical load decreases, the compressor runs while the turbine does not run. The power consumption of the running compressor is determined by the deviation fluctuation range curve. S3: Use the power consumption of the compressor to determine the air flow and air pressure parameters when the compressor is running; S4: Calculate the temperature of the demineralized water makeup water for the back pressure unit; the makeup water is delivered to the water-side inlet of the compression-side heat exchanger; the water in the compression-side heat exchanger receives heat from the compressed air, is raised to the calculated temperature, and enters the deaerator to recover the heat into the thermal system. The compressed air generated during the compression process enters the air storage chamber to store the compressed energy; S5: When the system heat load decreases and the electrical load increases, the compressor does not run, but the turbine runs. The power generation of the turbine is determined by the fluctuation curve, and the air flow parameters of the turbine are calculated and determined. The air storage chamber delivers the air to the turbine according to the calculated air flow parameters. The compressed air in the air storage chamber enters the turbine and expands to do work. S6: Calculate the heating steam flow rate in the turbine-side heat exchanger. The turbine-side heat exchanger delivers the heating steam flow rate according to the calculated data. Before the compressed air enters each stage of the turbine cylinder, the air is heated by the heating steam flow rate of the back compressor exhaust through the turbine-side heat exchanger before entering the turbine cylinder. The average power output of the back pressure unit in S1 Heating flow The deviation range of the average power generation output of the back-pressure turbine from the electrical load ; The power consumption of the compressor in S2 is calculated as follows: The compressor airflow rate in S3 is determined by the formula: In the formula For the first The power consumption of the multistage compression cylinder; For the first The pressure ratio of the compression cylinder; For the first The variability index of a multistage compression cylinder; The gas constant representing air; For the first The inlet temperature of the primary compression cylinder; For the first The variable efficiency of the multistage compression cylinder For the compressor's motor efficiency, The compressor airflow rate needs to be determined; The outlet pressure of each stage of the compression cylinder can be determined by the following formula: In the formula For the first The inlet pressure of the compression cylinder; The back pressure turbine demineralized water makeup water temperature in S4 is calculated using the following formula: In the formula Indicates the first The enthalpy of the air inlet of the stage heat exchanger. Indicates the first The enthalpy of the air outlet of the stage heat exchanger. For compressor airflow, This indicates the heat exchange efficiency of the heat exchanger. This indicates the enthalpy value at the inlet of the water medium in the heat exchanger. This indicates the specific heat capacity of water; The turbine power generation capacity in S5 is calculated as follows: The airflow rate of a turbine is determined by the formula: In the formula Indicates the first The output power of the stage turbine cylinder, Indicates the first The enthalpy of the outlet air of the turbine cylinder. Indicates the first The enthalpy of the inlet air of the turbine cylinder. This indicates the airflow rate of the turbine that needs to be determined. This indicates the motor efficiency of the turbine; The heating steam flow rate in the turbine-side heat exchanger in S6 can be calculated as follows: In the formula Indicates the first The enthalpy of the air inlet of the stage heat exchanger. Indicates the first The enthalpy of the air outlet of the stage heat exchanger. For turbine airflow, This indicates the heat exchange efficiency of the heat exchanger. This indicates the enthalpy value at the outlet of the water medium in the heat exchanger. This indicates the enthalpy value of the steam heated by the heat exchanger.

2. A compressed air energy storage and thermal power heating coupling system using the method of claim 1, characterized in that, include, Thermal power heating system: including a boiler (1) that generates steam, a back pressure machine (2) for exhausting heat and outputting power, a generator (3) that generates electricity through the back pressure machine (2), and a water circulation device for circulating the exhaust steam from the back pressure machine (2) back to the boiler (1); Compressed air energy storage system: including a compressor system that compresses air, an air storage system that stores the compressed air, a turbine system that generates electricity for the generator (3) by releasing the compressed air from the air storage system, and a heat exchange system that transfers energy to the compressor system and the turbine system respectively; the heat exchange system is finally connected to the water circulation device. The heat exchange system includes several compression-side heat exchangers (21) and several turbine-side heat exchangers (22); the compressor system is connected to the air-side inlet and outlet of each compression-side heat exchanger (21), and the turbine system is connected to the air-side inlet and outlet of each turbine-side heat exchanger (22). The water circulation device includes a deaerator (4) and a feed pump (5) connected to the deaerator (4) and outputting water to the boiler (1).

3. The compressed air energy storage and thermal power heating coupling system according to claim 2, characterized in that, The gas storage system includes a gas storage chamber (31) and valves and pipes for connection.

4. The compressed air energy storage and thermal power heating coupling system according to claim 2, characterized in that, The water inlet of the compressor-side heat exchanger (21) is connected to the water supply pipeline via a branch pipe to form a main pipe, and each branch pipe is equipped with a regulating valve (7); the water outlet of the compressor-side heat exchanger (21) is connected to the water circulation device via a branch pipe to form a main pipe; the steam inlet of the turbine-side heat exchanger (22) is connected to the external heating pipeline of the back pressure machine (2) via a branch pipe to form a main pipe, and a first valve (9) is installed on the main pipe, and each branch pipe is equipped with a regulating valve (7); the water outlet of the turbine-side heat exchanger (22) is connected to the pipeline connecting the compressor-side heat exchanger (21) and the water circulation device via a branch pipe to form a main pipe, and a second valve (6) is installed on the main pipe.

5. The compressed air energy storage and thermal power heating coupling system according to claim 4, characterized in that, The compressor system includes a compressor, which includes several compression cylinders (11) and valves and pipes for connection. The air inlet of the first-stage compression cylinder (11) is connected to the atmosphere through an air pipe. Each compression cylinder (11) is connected in series with the air side of the corresponding compression-side heat exchanger (21) through an air pipe. The air outlet of the last-stage compression cylinder (11) is connected in series with the air side of the compression-side heat exchanger (21) and the air storage system in sequence. The compression cylinders (11) between the first-stage and last-stage compression cylinders (11) are connected in series with the adjacent compression cylinders (11) through their connected compression-side heat exchangers (21).

6. The compressed air energy storage and thermal power heating coupling system according to claim 5, characterized in that, The compression cylinder (11) is driven by a connected electric motor (8), and the generator (3) is connected to the electric motor (8) of the compression cylinder (11) via a power cable to provide driving power.

7. The compressed air energy storage and thermal power heating coupling system according to claim 4, characterized in that, The turbine system includes a turbine, which includes several turbine cylinders (51) and valves and pipes for connection. The air inlet of the first-stage turbine cylinder (51) is connected in series with the air side of the turbine-side heat exchanger (22) and the gas storage system. The turbine cylinder (51) is connected in series with the air side of the turbine-side heat exchanger (22) through an air pipe. The air outlet of the last-stage turbine cylinder (51) is connected to the atmosphere through an air pipe. The turbine cylinders (51) between the first-stage and last-stage turbine cylinders (51) are connected in series with the adjacent turbine cylinders (51) through the turbine-side heat exchanger (22) they are connected to.

8. The compressed air energy storage and thermal power heating coupling system according to claim 7, characterized in that, The turbine cylinder (51) is connected in series via a shaft and is eventually connected to the generator (3) to generate electricity.

Images