A quick cooling device of compressed air energy storage system and a control method thereof

Abstract

This invention discloses a rapid cooling device and its control method for a compressed air energy storage system, belonging to the field of compressed air energy storage technology. The device includes a compressor rapid cooling device and a turbine rapid cooling device respectively located on the compressor side and turbine side. The rapid cooling device uses compressed air as the cooling medium, heats the cooling air through a heating module, and selects a co-current or counter-current channel according to the unit's structural characteristics to introduce the heated air into the compressor or turbine, achieving uniform cooling. The cooling medium can be selected from compressed air stations or compressed air recovered from the system, and the heating method can be compression heating, electric heating, or a combination thereof. This invention can effectively reduce the turning time of the compressor and turbine during scheduling intervals, reduce auxiliary machine energy consumption, improve the system's electro-to-electric conversion efficiency, and shorten maintenance downtime, thereby improving equipment availability.

Description

Technical Field

[0001] This invention belongs to the field of compressed air energy storage technology, specifically relating to a rapid cooling device for a compressed air energy storage system and its control method. Background Technology

[0002] Compressed air energy storage systems, as a large-scale energy storage technology, play a crucial role in power grid peak shaving and frequency regulation. In actual operation, the compressor and turbine units of compressed air energy storage systems need to be frequently started and stopped according to power grid dispatch instructions. After the compression or expansion process is completed, in order to prevent thermal bending deformation of the compressor or turbine rotor due to uneven heating or cooling, and to ensure equipment safety and readiness for immediate start-up, it is usually necessary to perform long-term rotary cranking of the compressor or turbine.

[0003] However, existing technologies have the following shortcomings: First, because compressors or turbines are typically equipped with insulation layers, natural cooling results in a very slow temperature drop due to the large heat capacity and poor heat dissipation of the cylinders, requiring a long period of natural cooling to meet the requirements for shutting down the turning gear. Second, during the charging and discharging scheduling intervals of the compressed air energy storage system, the compressor or turbine unit needs to maintain a turning gear position for an extended period to keep the unit in operation. This necessitates the continuous operation of auxiliary equipment such as the lubrication system, jacking oil system, and turning gear system, significantly increasing plant power consumption and reducing the overall electro-electric conversion efficiency of the compressed air energy storage system. Finally, when the compressor or turbine unit needs to be shut down for maintenance, the lengthy natural cooling process makes the time from shutdown to meeting the conditions for cylinder reopening for maintenance excessively long, severely restricting the unit's availability factor and affecting the power plant's power generation efficiency and economic benefits. Summary of the Invention

[0004] The purpose of this invention is to overcome the above-mentioned defects in the prior art and provide a rapid cooling device and control method for a compressed air energy storage system, which solves the problem that the long natural cooling time of the compressor unit and turbine unit leads to a reduction in the overall electro-electric conversion efficiency of the compressed air energy storage system.

[0005] On one hand, the present invention provides a rapid cooling device for a compressed air energy storage system, comprising: A compressor rapid cooling device is installed on the compression side of a compressed air energy storage system to cool the compressor; A turbine rapid cooling device is installed on the turbine side of the compressed air energy storage system to cool the turbine. The compressor rapid cooling device and the turbine rapid cooling device each independently include: Cooling medium supply module, used to provide cooling air; A heating module, connected to the cooling medium supply module, is used to heat the cooling air; The control module is electrically connected to the cooling medium supply module and the heating module respectively. The control module is used to obtain the real-time metal temperature of the compressor or turbine, and calculate the required cooling air volume and target cooling air temperature based on the real-time metal temperature, thereby controlling the supply volume of the cooling medium supply module and the heating power of the heating module. The medium delivery pipeline has its inlet end connected to the outlet end of the heating module, and its outlet end is used to connect to the fast cooling interface of the compressor or turbine to introduce heated cooling air into the unit for cooling.

[0006] Furthermore, the cooling air source for the cooling medium supply module is compressed air from a compressed air station or compressed air recovered from a compressed air energy storage system. Choosing these two air sources ensures the cleanliness and dryness of the cooling medium, preventing contamination or damage to precision high-speed rotating components.

[0007] Furthermore, the heating module includes an electric heating assembly, which comprises a header, a first electric heater, a second electric heater, and a valve group. The valve group is used to switch the connection methods between the first and second electric heaters, and between the first and second electric heaters and the header. The connection methods include series and parallel connections. The inlet end of the medium conveying pipeline is connected to the outlet end of the header. By switching between series and parallel connections, the heating power and flow characteristics can be flexibly changed to adapt to the differentiated needs of different cooling stages.

[0008] Furthermore, the inlet of the heating module is connected via a pipeline to a heat exchanger for recovering the heat of compression from the final stage of compression. The cold side of the heat exchanger is connected to the cooling medium supply module, and the hot side is connected to the high-temperature tank of the compressed air energy storage system, so as to preheat the cooling air using the heat of compression. This design achieves cascaded energy utilization, using free heat of compression for preliminary heating when the unit temperature is high, significantly reducing the energy consumption of electric heating.

[0009] Furthermore, the media delivery pipeline includes a compression-side rapid cooling main pipe connected to the compressor side and a turbine-side rapid cooling main pipe connected to the turbine side; the compression-side rapid cooling main pipe is connected to the rapid cooling interfaces of multiple compressors through multiple branch pipes and corresponding control valves; the turbine-side rapid cooling main pipe is connected to the rapid cooling interfaces of multiple turbines through multiple branch pipes and corresponding control valves. This modular piping design allows for independent or synchronous cooling control of compressors and turbines arranged in series or in multiple rows.

[0010] Furthermore, the compressor side is equipped with a venting pipeline linked to the control valve, and the venting pipeline has a venting valve that opens when the rapid cooling device is activated; the turbine side is equipped with an independent cooling air discharge pipeline, which is connected to the turbine's exhaust pipeline through a discharge valve. This provides a smooth flow path for the cooling air, ensuring the cooling effect.

[0011] The present invention also provides a control method for a rapid cooling device in a compressed air energy storage system, comprising the following steps: Step S1: After the unit is shut down and enters the turning gear state, check the status of each system and the monitoring data to determine whether the conditions for the rapid cooling unit to be put into operation are met. Step S2: When the input conditions are met, start the rapid cooling device, and the control module obtains the metal temperature monitored after the unit is shut down; Step S3: The control module calculates the maximum cooling temperature difference based on the metal temperature and the structural characteristics of the unit, and determines the cooling rate based on the target cooling time, and then calculates the required cooling air volume and electric heating temperature; Step S4: The control module controls the opening of the valve of the cooling medium supply module and starts the heating module; Step S5: During the cooling process, the control module monitors the metal temperature in real time and dynamically adjusts the cooling air supply and the output of the heating module to make the actual cooling parameters approach the calculated values. Step S6: When the monitored metal temperature drops to the first preset threshold, the control module closes the inlet valve of the cooling device, exits the rapid cooling device, and performs the unit shutdown operation.

[0012] Furthermore, in step S4, when the unit's metal temperature is higher than the second preset threshold, the control module controls the valve group of the heating module to switch the first electric heater and the second electric heater to a series connection; when the unit's metal temperature is lower than the second preset threshold, the control module controls the valve group to switch the first electric heater and the second electric heater to a parallel connection to increase the cooling air flow. For example, when the unit temperature is higher than 200°C, the heating temperature requirement is high, and a series connection can provide a higher outlet temperature; when the temperature is lower than 200°C, the cooling speed requirement is higher, and a parallel connection can reduce flow resistance, increase flow rate, and achieve rapid cooling.

[0013] Furthermore, the control method also includes a maintenance cooling mode: after step S6, if further cooling to the maintenance temperature is required, the cooling air supply is increased until the unit's metal temperature drops to a third preset threshold, which is lower than the first preset threshold. For example, the shutdown cylinder temperature threshold can be 150°C, while the temperature threshold for opening the cylinder during maintenance is typically 60°C. This method can seamlessly switch to the maintenance cooling mode, greatly shortening maintenance preparation time.

[0014] Furthermore, the maximum supply of cooling air is determined based on the metal temperature range of the compressor or turbine unit, using the following formula: The cooling temperature difference and the required cooling air volumetric flow rate are matched, and their relationship satisfies the heat balance equation:

[0015] in, The required cooling air volumetric flow rate, in m³ / s. 3 / min; Mass of all components in contact with the cooling air of a compressor or turbine, expressed in kg; The mass heat capacity of each component in a compressor or turbine that comes into contact with cooling air, expressed in J / (kg). K); Cooling rate of the components in contact with the cooling air of a compressor or turbine, expressed in K / min; The mass heat capacity of cooling air, expressed in J / (kg). K); Temperature rise of cooling air, measured in Kelvin (K). The density of cooling air is expressed in kg / m³. 3 ;

[0016] in, The temperature difference is measured in Kelvin (K). For Bishop's number; This refers to the elastic modulus, expressed in MPa. This is the coefficient of thermal expansion, with units of 1 / K; Poisson's ratio; This represents the maximum stress at the stress concentration point in the critical component, expressed in MPa. For safety margin, a value of 1.5 to 2 is used; is the stress concentration factor.

[0017] Compared with the prior art, the present invention has the following beneficial effects: First, by installing independent rapid cooling devices on both the compression and turbine sides, active and rapid cooling is achieved during unit scheduling downtime, significantly reducing the turning gear time required for the compressor or turbine. This reduction in turning gear time means a substantial decrease in the operating time of related auxiliary equipment such as the lubrication system, jacking oil system, and turning gear system, thereby effectively reducing plant power consumption and ultimately improving the overall electro-electric conversion efficiency of the compressed air energy storage system.

[0018] Second, for maintenance shutdown scenarios, the rapid cooling device of this invention can quickly reduce the unit's metal temperature to the temperature required for maintenance cylinder opening (e.g., 60°C), shortening the natural cooling time that originally required several days or even longer to several hours. This significantly reduces the unit's maintenance waiting time, increases the annual utilization hours and availability factor of the equipment, and brings direct economic benefits to the power plant.

[0019] Third, the control method of this invention is based on real-time monitoring of the metal temperature. Through precise thermal balance calculations, it dynamically adjusts the flow rate and temperature of the cooling air, achieving precise control of the cooling rate. Simultaneously, depending on the structural characteristics of the compressor and turbine, either co-current or counter-current cooling channels can be selected, ensuring uniform cooling of core components such as the rotor and cylinder. This effectively avoids thermal bending deformation caused by concentrated thermal stress or uneven cooling, guaranteeing the safe operation of the equipment.

[0020] Fourth, this invention can use the recycled compressed air or instrument compressed air from the compressed air energy storage system itself as the cooling medium, eliminating the need for an additional air source. In terms of heating, it prioritizes the use of the heat of compression generated in the final stage of compression for preheating, significantly reducing the power consumption of electric heating. Furthermore, by switching between series and parallel electric heaters, it can flexibly adapt to the cooling strategy requirements of "high temperature, low flow rate" or "low temperature, high flow rate" in different temperature ranges, exhibiting strong adaptability and energy efficiency advantages. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the rapid cooling device of the compressed air energy storage system described in Embodiment 1 of the present invention.

[0022] Figure 2 This is a schematic diagram of the rapid cooling device of the compressed air energy storage system described in Embodiment 2 of the present invention.

[0023] Figure 3 This is a schematic diagram of the compressor's rapid cooling device.

[0024] Figure 4 This is a schematic diagram of the rapid cooling device for a turbine.

[0025] The components include: 1. Cooling air tank; 2. Heat exchanger; 3. Compressor rapid cooling device; 4. Turbine rapid cooling device; 5. First electric heater; 6. Second electric heater; 7. Header; 8. Compressor-side rapid cooling header; 9. Turbine-side rapid cooling header; V1-1~V1-4, Compressor rapid cooling control valve; V2-1~V2-4, Compressor vent valve; V4-1~V4-3, Turbine inlet isolation valve; V5-1~V5-3, Turbine rapid cooling control valve; V6-1~V6-3, Turbine cooling discharge valve; V7-1, Compressor rapid cooling main valve; V7-2~V7-5, Compressor-side heating mode switching valve; V8-1, Turbine rapid cooling main valve; V8-2~V8-5, Turbine-side heating mode switching valve. Detailed Implementation

[0026] The specific embodiments of the present invention are described below to enable those skilled in the art to understand the present invention. However, it should be understood that the present invention is not limited to the scope of the specific embodiments. For those skilled in the art, various changes are obvious as long as they are within the spirit and scope of the present invention as defined and determined by the appended claims. All inventions utilizing the concept of the present invention are protected.

[0027] Example 1, as Figure 1 The embodiment shown provides a rapid cooling device for a compressed air energy storage system. This device is mainly used to utilize the compressed air recovered by the system itself as a cooling medium and to prioritize the use of compression heat for preheating.

[0028] The rapid cooling device comprises two main subsystems: a compressor rapid cooling unit 3 located on the compression side and a turbine rapid cooling unit 4 located on the turbine side. The two subsystems are similar in structure and control logic, but differ in interface and parameters depending on the characteristics of their respective cooling objects.

[0029] like Figure 3 As shown, the compressor-side rapid cooling device mainly includes a cooling air tank 1, a heat exchanger 2, a compressor rapid cooling device 3, and related piping and valve assemblies.

[0030] Cooling air tank 1 is used to store the exhaust gas recovered during compressor start-up and shutdown, and its pressure can be controlled between 1 and 2 MPa. The size of the tank is determined based on the capacity calculation of the entire compressed air energy storage system. The outlet of cooling air tank 1 is connected to the cold side inlet of heat exchanger 2 via a pipeline. The hot side inlet of heat exchanger 2 is connected to the high-temperature tank of the compressed air energy storage system, and the hot side outlet returns to the high-temperature tank circuit. Using the high-temperature medium (such as heat transfer oil or high-temperature air) in the high-temperature tank, heat exchanger 2 preheats the cooling air from cooling air tank 1, realizing the cascade utilization of energy.

[0031] The cold-side outlet of heat exchanger 2 is connected to the inlet of compressor rapid cooling device 3 via a pipe and valve V7-1. Compressor rapid cooling device 3 is the core component of this invention, integrating a heating module and a header 7. Specifically, the heating module includes a first electric heater 5 and a second electric heater 6. A valve group (V7-2, V7-3, V7-4, V7-5) is arranged around these two electric heaters to switch their operating modes.

[0032] Series mode: When valves V7-2 and V7-5 are closed and valve V7-3 is open, the cooling air flows sequentially through the first electric heater 5 and the second electric heater 6 to achieve two-stage heating, which can provide a higher outlet air temperature.

[0033] Parallel mode: When valve V7-3 is closed and valves V7-2 and V7-5 are open, the cooling air is split and flows through the first electric heater 5 and the second electric heater 6 at the same time. In this mode, the flow resistance is smaller and a larger cooling air flow can be provided.

[0034] Straight-through mode: When heating is not required, valve V7-4 can be opened to allow cooling air to bypass directly to header 7.

[0035] The outlet of the header 7 of the compressor rapid cooling unit 3 is connected to the main pipe 8 of the compression-side rapid cooling system. This main pipe 8 connects to the rapid cooling interfaces of the first to fourth stage compressors via four branch pipes and corresponding control valves V1-1, V1-2, V1-3, and V1-4. Each compressor's discharge pipe has a vent pipe linked to the rapid cooling system, equipped with vent valves V2-1 to V2-4. Check valves are also installed on the compressor outlet pipes. When the rapid cooling unit is engaged, these check valves are closed to prevent cooling air from flowing back into the downstream system. Simultaneously, the compressor's inlet adjustable guide vanes or stationary vanes must be closed to prevent cooling air leakage from the inlet.

[0036] like Figure 4 As shown, the structure of the turbine-side rapid cooling device is similar to that of the compressor rapid cooling device. The cooling air from the cooling air tank 1 (which can be shared with the compressor side or set up independently) is also preheated by the heat exchanger 2 first, and then enters the turbine rapid cooling device 4 through valve V8-1.

[0037] The turbine rapid cooling device 4 also has a first electric heater 5, a second electric heater 6 and a header 7, as well as valve groups V8-2 (straight-through), V8-3 and V8-5 (parallel), and V8-4 (series) for mode switching.

[0038] The outlet of the header 7 of the turbine rapid cooling device 4 is connected to the turbine-side rapid cooling system header 9. The turbine side is typically divided into multiple sections (such as high-pressure section, medium-pressure section, and low-pressure section). The turbine-side rapid cooling header 9 is connected to the rapid cooling interfaces of the first, second, and third sections of the turbine via valves V5-1, V5-2, and V5-3, respectively. Each cooling section has a dedicated cooling air exhaust pipe, which is connected to the turbine's exhaust pipe via exhaust valves V6-1, V6-2, and V6-3. At the turbine's air inlet, there are air inlet isolation valves V4-1 to V4-3, which must be kept closed during cooling to prevent cooling air from entering the upstream system.

[0039] Combination Figure 1 The system structure shown in this embodiment, and the control method of the rapid cooling device are as follows: Step S1: Preparation and Judgment. After the compressor unit or turbine unit is shut down and in the turning gear state, the control system first checks the operating status of all relevant systems (such as the lubrication system and monitoring system) and confirms that the monitoring data such as metal temperature and pressure required by the rapid cooling unit are normal. When all conditions are met, the operator or automatic control system issues a command to allow the rapid cooling unit to be put into operation.

[0040] Step S2: Parameter Acquisition and Calculation. After the rapid cooling unit is activated, the control module immediately acquires key monitoring parameters after the unit stops. For the compressor, this mainly refers to the final stage metal temperature; for the turbine, it mainly refers to the first stage metal temperature. Based on these temperature values ​​and pre-stored unit structural characteristic parameters (such as rotor mass, cylinder heat capacity, etc.), the control module calculates the safe and efficient maximum cooling temperature difference. Then, based on the system-set target cooling time (or default cooling rate), it calculates the required cooling air volumetric flow rate and cooling temperature difference.

[0041] The formula for calculating the volumetric flow rate of cooling air is:

[0042] in, The required cooling air volumetric flow rate, in m³ / s. 3 / min; Mass of all components in contact with the cooling air of a compressor or turbine, expressed in kg; The mass heat capacity of each component in a compressor or turbine that comes into contact with cooling air, expressed in J / (kg). K); Cooling rate of the components in contact with the cooling air of a compressor or turbine, expressed in K / min; The mass heat capacity of cooling air, expressed in J / (kg). K); Temperature rise of cooling air, measured in Kelvin (K). The density of cooling air is expressed in kg / m³. 3 ; The formula for calculating the cooling temperature difference is:

[0043] in, The temperature difference is measured in Kelvin (K). For Bishop's number; This refers to the elastic modulus, expressed in MPa. This is the coefficient of thermal expansion, with units of 1 / K; Poisson's ratio; This represents the maximum stress at the stress concentration point in the critical component, expressed in MPa. For safety margin, a value of 1.5 to 2 is used; is the stress concentration factor.

[0044] Step S3: Perform heating mode switching. The control module opens the inlet main valve (V7-1 or V8-1) of the rapid cooling unit. At the same time, it compares the calculated target temperature with the current metal temperature of the unit and selects the appropriate heating mode.

[0045] High-temperature stage (e.g., unit metal temperature > 200°C): At this stage, hot air with a relatively high temperature but not excessive flow rate is needed to "preheat" the cooling channels and remove initial heat. The control module will issue a command to switch the valve group to series mode (close V7-2 / V7-5, open V7-3; or close V8-3 / V8-5, open V8-4). The cooling air is first preheated by the heat exchanger 2 using compression heat, and then further heated to the target temperature by two electric heaters connected in series before entering the unit.

[0046] In low-temperature stages (e.g., unit metal temperature <200°C): A large amount of heat needs to be removed quickly, thus requiring a higher cooling airflow rate. The control module will instruct the valve group to switch to parallel mode (close V7-3, open V7-2 and V7-5; or close V8-4, open V8-3 and V8-5). In this mode, airflow resistance is reduced, and the flow rate can be significantly increased. The two electric heaters operate in parallel, jointly providing the required heat.

[0047] Step S4: Dynamic Adjustment and Precise Cooling. During the cooling process, the control module monitors the feedback from the metal temperature sensor in real time. Utilizing a PID (Proportional-Integral-Derivative) control algorithm, it continuously adjusts the opening of the main valve (V7-1 or V8-1) and each branch valve (V1-1 to V1-4, V5-1 to V5-3) to precisely control the amount of cooling air entering each unit or section. Simultaneously, it adjusts the power of the electric heater to ensure that the outlet air temperature always follows the calculated optimal value. For example, for four compressors connected in series on the compression side, if rapid cooling of the high-temperature compressor in the later stage is required, the control module can increase the opening of valve V1-4 leading to that stage while decreasing the opening of the preceding stages to achieve targeted cooling.

[0048] Step S5: Shutdown and Mode Switching. When the metal temperature at the monitoring point drops to the first preset threshold (e.g., 150°C), it indicates that the unit has cooled to a level where it is safe to stop the turning gear operation. At this time, the control module will first close the main inlet valve of the rapid cooling unit (V7-1 or V8-1), then close each branch valve (V1-1 to V1-4 or V5-1 to V5-3), and finally execute the standard shutdown and turning gear stop operation procedure.

[0049] Step S6 (Optional): Maintenance Cooling Mode. If the shutdown is for maintenance, the system can remain in maintenance cooling mode after reaching the shutdown temperature. In this mode, the control module will further increase the cooling airflow (e.g., switch the electric heater to direct-flow mode V7-4 for high-flow purging with ambient temperature air) and continue running the rapid cooling device until the monitored metal temperature drops to a lower third preset threshold (e.g., 60°C). Once this temperature is reached, the unit meets the conditions for safe cylinder opening for maintenance, significantly reducing the waiting time before maintenance.

[0050] Example 2 like Figure 2 As shown, this embodiment provides another rapid cooling device and its control method for a compressed air energy storage system. The main difference between this embodiment and Embodiment 1 is the source of the cooling air and the corresponding system configuration.

[0051] In Example 2, the cooling medium supply module of the rapid cooling device no longer relies on the gas recovered by the system, but directly uses the air source from the original compressed air station in the compressed air energy storage system. The compressed air provided by the compressed air station has a pressure of approximately 0.8 MPa and has undergone drying and purification treatment, resulting in high-quality gas that fully meets the cleanliness requirements for use as a rapid cooling medium.

[0052] Because the air source pressure is stable and the quality is guaranteed, the system in Example 2 can be simplified in design. First, the cooling air tank 1 for storing the recycled air can be omitted. Second, since the instrument compressed air is already very dry, there is no need to install an additional air-liquid separator in its pipeline.

[0053] The other structures and working principles are basically the same as in Embodiment 1. Compressed air from the compressed air station also enters the compressor rapid cooling device 3 or the turbine rapid cooling device 4. The rapid cooling device also includes a first electric heater 5, a second electric heater 6, a header 7, and a valve group for switching between series and parallel modes. The cooling air delivery pipeline, the interface with the compressor and turbine, and the control logic are all consistent with those in Embodiment 1.

[0054] The advantage of Example 2 is that the system is simpler and the air source quality is guaranteed. However, its disadvantage is that it requires the plant's power supply to produce compressed air. In practical applications, the choice can be made according to the specific configuration and requirements of the power station. To balance energy efficiency and reliability, a combined solution can also be adopted: during stages requiring high-flow cooling (such as rapid cooling during maintenance), both recycled air and instrument air can be used simultaneously, or the two can be used in series and parallel.

[0055] In summary, the rapid cooling device and control method for compressed air energy storage systems provided by this invention solve the problems of long turning time, high plant power consumption, and long maintenance waiting time in the prior art through an active, controllable, and efficient cooling method. It significantly improves the operating efficiency and economic benefits of compressed air energy storage systems and has extremely high practical value and broad application prospects.

Claims

1. A flash cooler for a compressed air energy storage system, characterized in that, This includes a compressor rapid cooling device and a turbine rapid cooling device respectively installed on the compression side and turbine side of the compressed air energy storage system; Both the compressor rapid cooling device and the turbine rapid cooling device include: Cooling medium supply module, used to provide cooling air; A heating module, connected to the cooling medium supply module, is used to heat the cooling air; The control module is electrically connected to the cooling medium supply module and the heating module respectively. The control module is used to obtain the real-time metal temperature of the compressor or turbine, and calculate the required cooling air volume and target cooling air temperature based on the real-time metal temperature, thereby controlling the supply volume of the cooling medium supply module and the heating power of the heating module. The medium delivery pipeline has its inlet end connected to the outlet end of the heating module, and its outlet end is used to connect to the fast cooling interface of the compressor or turbine to introduce heated cooling air into the unit for cooling.

2. The fast cooling device of a compressed air energy storage system according to claim 1, characterized in that, The cooling air source for the cooling medium supply module is compressed air from a compressed air station or compressed air recovered from a compressed air energy storage system.

3. The fast-cooling device of a compressed air energy storage system according to claim 1, characterized in that, The heating module includes an electric heating assembly, which includes a header, a first electric heater, a second electric heater, and a valve group. The valve group is used to switch the connection mode between the first electric heater and the second electric heater, as well as between the first electric heater and the second electric heater and the header. The connection mode includes series connection and parallel connection. The inlet end of the medium conveying pipeline is connected to the outlet end of the header.

4. The fast cooling device of a compressed air energy storage system according to claim 3, characterized in that The rapid cooling device for the compressed air energy storage system according to claim 3 is characterized in that the inlet end of the heating module is also connected to a heat exchanger for recovering the compression heat of the final stage of compression via a pipeline, the cold side of the heat exchanger is connected to the cooling medium supply module, and the hot side is connected to the high-temperature tank of the compressed air energy storage system, so as to preheat the cooling air using the compression heat.

5. The fast-cooling device of a compressed air energy storage system according to claim 1, characterized in that, The medium delivery pipeline includes a compression-side rapid cooling main pipe connected to the compressor side and a turbine-side rapid cooling main pipe connected to the turbine side; the compression-side rapid cooling main pipe is connected to the rapid cooling interfaces of multiple compressors through multiple branch pipes and corresponding control valves; the turbine-side rapid cooling main pipe is connected to the rapid cooling interfaces of multiple turbines through multiple branch pipes and corresponding control valves.

6. The fast cooling device of a compressed air energy storage system according to claim 5, characterized in that The compressor side is provided with a venting pipeline that is linked to the control valve. The venting pipeline is equipped with a venting valve, which opens when the rapid cooling device is put into operation. The turbine side is provided with an independent cooling air discharge pipeline, which is connected to the turbine's exhaust pipeline through a discharge valve.

7. A control method of a fast cooling device based on the compressed air energy storage system according to any one of claims 1 to 6, characterized in that, Includes the following steps: Step S1: After the unit is shut down and enters the turning gear state, check the status of each system and the monitoring data to determine whether the conditions for the rapid cooling unit to be put into operation are met. Step S2: When the input conditions are met, start the rapid cooling device, and the control module obtains the metal temperature monitored after the unit is shut down; Step S3: The control module calculates the maximum cooling temperature difference based on the metal temperature and the structural characteristics of the unit, and determines the cooling rate based on the target cooling time, and then calculates the required cooling air volume and electric heating temperature; Step S4: The control module controls the opening of the valve of the cooling medium supply module and starts the heating module; Step S5: During the cooling process, the control module monitors the metal temperature in real time and dynamically adjusts the cooling air supply and the output of the heating module to make the actual cooling parameters approach the calculated values. Step S6: When the monitored metal temperature drops to the first preset threshold, the control module closes the inlet valve of the cooling device, exits the rapid cooling device, and performs the unit shutdown operation.

8. The control method according to claim 7, characterized by, In step S4, when the unit's metal temperature is higher than the second preset threshold, the control module controls the valve group of the heating module to switch the first electric heater and the second electric heater to be connected in series; when the unit's metal temperature is lower than the second preset threshold, the control module controls the valve group to switch the first electric heater and the second electric heater to be connected in parallel to increase the cooling air flow.

9. The control method according to claim 7, characterized in that, It also includes a maintenance cooling mode: after step S6, if it is necessary to continue cooling to the maintenance temperature, the cooling air supply is increased until the unit metal temperature drops to a third preset threshold, which is lower than the first preset threshold.

10. The control method according to claim 7, characterized in that, The maximum cooling air supply is determined based on the metal temperature range of the compressor or turbine unit using the following formula: Matching the cooling temperature difference and the required cooling air volumetric flow rate, their relationship satisfies the heat balance equation: in, The required cooling air volumetric flow rate, in m³ / s. 3 / min; Mass of all components in contact with the cooling air of a compressor or turbine, expressed in kg; The mass heat capacity of each component in a compressor or turbine that comes into contact with cooling air, expressed in J / (kg). K); Cooling rate of the components in contact with the cooling air of a compressor or turbine, expressed in K / min; The mass heat capacity of cooling air, expressed in J / (kg). K); Temperature rise of cooling air, measured in Kelvin (K). The density of cooling air is expressed in kg / m³. 3 ; in, The temperature difference is measured in Kelvin (K). For Bishop's number; This refers to the elastic modulus, expressed in MPa. This is the coefficient of thermal expansion, with units of 1 / K; Poisson's ratio; This represents the maximum stress at the stress concentration point in the critical component, expressed in MPa. For safety margin, a value of 1.5 to 2 is used; is the stress concentration factor.

Images