Molten salt system, deep peak regulation method, storage medium and electronic equipment

Abstract

The invention discloses a molten salt system, a deep peak regulation method, a storage medium and electronic equipment. The fused salt system comprises a high-temperature fused salt tank, a high-temperature fused salt pump, a fused salt heat release system, a fused salt heat release system steam outlet valve, a deep peak regulation steam supply header, a steam inlet valve from the deep peak regulation steam supply header to a water feeding pump turbine and the water feeding pump turbine. An outlet of the high-temperature molten salt tank communicates with an inlet of the high-temperature molten salt pump through a pipeline, and an outlet of the high-temperature molten salt pump communicates with a hot salt side inlet of the molten salt heat release system through a pipeline. A steam side outlet of the fused salt heat release system communicates with an inlet of a steam outlet valve of the fused salt heat release system through a pipeline, and an outlet of the steam outlet valve of the fused salt heat release system communicates with an inlet of the deep peak regulation steam supply header through a pipeline. An outlet of the deep peak regulation steam supply header communicates with an inlet from the deep peak regulation steam supply header to a steam inlet valve of the water feeding pump turbine through a pipeline, and an outlet from the deep peak regulation steam supply header to the steam inlet valve of the water feeding pump turbine communicates with a steam inlet of the water feeding pump turbine through a pipeline.

Description

Technical Field

[0001] This application relates to the field of control technology, and in particular to a molten salt system, a deep peak-shaving method, a storage medium, and an electronic device. Background Technology

[0002] In the context of increasingly stringent requirements for deep peak-shaving capabilities in the current power system, combined heat and power (CHP) units often face insufficient support from critical auxiliary systems due to adjustments in unit operating parameters during deep peak-shaving operations. When the unit's electrical load decreases to the deep peak-shaving range, the parameters of the conventional steam sources (such as specific extraction sections of the turbine) that were previously relied upon will fluctuate, causing the power steam source used to drive the core auxiliary equipment to be unable to maintain a stable supply. This may in turn affect the normal output of the unit's critical auxiliary equipment, thus restricting the unit's continuous and stable operation under deep peak-shaving conditions. Summary of the Invention

[0003] In view of the above problems, this application provides a molten salt system, a deep peak shaving method, a storage medium, and an electronic device.

[0004] To solve the above-mentioned technical problems, this application proposes the following solution:

[0005] In a first aspect, this application provides a molten salt system, comprising: a high-temperature molten salt tank, a high-temperature molten salt pump, a molten salt heat release system, a steam outlet valve for the molten salt heat release system, a deep peak-shaving steam supply header, a steam inlet valve from the deep peak-shaving steam supply header to the feedwater pump turbine, and a feedwater pump turbine; the outlet of the high-temperature molten salt tank is connected to the inlet of the high-temperature molten salt pump via a pipeline, and the outlet of the high-temperature molten salt pump is connected to the hot salt side inlet of the molten salt heat release system via a pipeline; the steam-side outlet of the molten salt heat release system is connected to the inlet of the steam outlet valve of the molten salt heat release system via a pipeline, and the outlet of the steam outlet valve of the molten salt heat release system is connected to the inlet of the deep peak-shaving steam supply header via a pipeline; the outlet of the deep peak-shaving steam supply header is connected to the inlet of the steam inlet valve from the deep peak-shaving steam supply header to the feedwater pump turbine via a pipeline, and the outlet of the steam inlet valve from the deep peak-shaving steam supply header to the feedwater pump turbine is connected to the steam inlet of the feedwater pump turbine via a pipeline.

[0006] Secondly, this application provides a deep peak shaving method, which includes: when receiving an instruction for the unit to enter deep peak shaving operation, starting the high-temperature molten salt pump and opening the drain valves before and after the feedwater pump inlet valve from the deep regulating valve steam supply manifold; adjusting the speed of the high-temperature molten salt pump based on the molten salt flow rate output from the high-temperature molten salt tank and the steam pressure at the outlet of the molten salt exothermic system; collecting the drain temperatures at the outlets of the drain valves before and after the feedwater pump inlet valve from the deep regulating valve steam supply manifold, and adjusting the drain valves before and after the feedwater pump inlet valve according to the real-time change rate and cumulative change of the drain temperature. The opening of the drain valve after the feedwater pump inlet valve from the deep regulating valve steam supply header is adjusted until the drain temperature rises to a preset condition and remains stable for a preset duration. Then, the drain valves before and after the feedwater pump inlet valve from the deep regulating valve steam supply header are closed. Based on the real-time speed of the feedwater pump turbine, the boiler feedwater flow rate, and the boiler feedwater temperature, the target steam pressure and target steam flow rate required by the feedwater pump turbine are determined. Based on the target steam pressure, target steam flow rate, and the actual steam pressure and actual steam flow rate at the outlet of the deep peak-shaving steam supply header, the opening of the steam inlet valve from the deep peak-shaving steam supply header to the feedwater pump turbine is adjusted to match the steam supply with the steam demand of the feedwater pump turbine.

[0007] To achieve the above objectives, according to a third aspect of this application, an electronic device is provided, the device including at least one processor, and at least one memory and bus connected to the processor; wherein the processor and memory communicate with each other through the bus; the processor is used to call program instructions in the memory to execute the deep peaking method of the second aspect described above.

[0008] By employing the above-described technical solution, the technical solution provided in this application has at least the following advantages:

[0009] This application adds a steam outlet valve to the molten salt exothermic system, a deep peak-shaving steam supply header, and a connection between the deep peak-shaving steam supply header and the feedwater pump turbine inlet valve. When the unit enters deep peak-shaving operation and conventional steam source parameters are insufficient, the high-temperature molten salt stored in the high-temperature molten salt tank can serve as an independent heat source, transported to the hot salt side of the molten salt exothermic system via a high-temperature molten salt pump. The molten salt releases heat within the molten salt exothermic system, heating the feedwater on the steam side of the system and generating stable steam. This steam, after parameter adjustment via the molten salt exothermic system outlet valve, enters the deep peak-shaving steam supply header for buffering and parameter stabilization. Subsequently, the stabilized steam passes through the deep peak-shaving steam supply header to the feedwater pump turbine inlet valve, precisely delivering it to the feedwater pump turbine inlet, providing a reliable drive steam source for the feedwater pump turbine, ensuring the feedwater pump turbine maintains its rated output, and thus guaranteeing stable flow and pressure in the boiler feedwater system.

[0010] The above description is only an overview of the technical solution of this application. In order to better understand the technical means of this application and to implement it in accordance with the contents of the specification, and to make the above and other objects, features and advantages of this application more obvious and understandable, the following are specific embodiments of this application. Attached Figure Description

[0011] Various other advantages and benefits will become apparent to those skilled in the art upon reading the following detailed description of preferred embodiments. The accompanying drawings are for illustrative purposes only and are not intended to limit the scope of this application. Furthermore, the same reference numerals denote the same parts throughout the drawings. In the drawings:

[0012] Figure 1 A schematic diagram of a molten salt system provided in an embodiment of this application is shown;

[0013] Figure 2 A schematic diagram of another molten salt system provided in an embodiment of this application is shown;

[0014] Figure 3 A schematic diagram of another molten salt system provided in an embodiment of this application is shown;

[0015] Figure 4 A schematic diagram of another molten salt system provided in an embodiment of this application is shown;

[0016] Figure 5 A schematic diagram of another molten salt system provided in an embodiment of this application is shown;

[0017] Figure 6 A schematic diagram of another molten salt system provided in an embodiment of this application is shown;

[0018] Figure 7 A flowchart illustrating a deep peak-shaving method provided in an embodiment of this application is shown;

[0019] Figure 8 A schematic diagram of the structure of an electronic device provided in an embodiment of this application is shown. Detailed Implementation

[0020] Exemplary embodiments of the present application will now be described in more detail with reference to the accompanying drawings. While exemplary embodiments of the present application are shown in the drawings, it should be understood that the present application may be implemented in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this application will be thorough and complete, and will fully convey the scope of the present application to those skilled in the art.

[0021] In the embodiments of this application, the terms "first," "second," etc., do not have a logical or temporal dependency, nor do they limit the quantity or execution order. It should also be understood that although the following description uses the terms "first," "second," etc., to describe various elements, these elements should not be limited by the terms. These terms are merely used to distinguish one element from another.

[0022] In this application, the term "at least one" means one or more, and the term "multiple" means two or more.

[0023] It should also be understood that the term “if” can be interpreted as “when” or “upon”, or “in response to determination” or “in response to detection”. Similarly, depending on the context, the phrase “if determination…” or “if detection [the stated condition or event]” can be interpreted as “when determination…” or “in response to determination…” or “when detection [the stated condition or event]” or “in response to detection [the stated condition or event]”.

[0024] The molten salt system of this application will be described in detail below with reference to the accompanying drawings and actual operating scenarios.

[0025] The molten salt system described in this application is a core peak-shaving unit formed by coupling the conventional thermodynamic cycle architecture of a thermal power unit with the heat storage and release functions of molten salt. Its core function is to generate stable steam through the heat released by molten salt when the unit enters deep peak-shaving operation and the conventional steam source parameters are insufficient. This provides a reliable driving steam source for the feedwater pump turbine, ensuring the stable operation of the unit's feedwater system and thus supporting the unit's deep peak-shaving capability. The basic components of this system include a high-temperature molten salt tank 1, a high-temperature molten salt pump 2, a molten salt heat release system 3, a steam outlet valve for the molten salt heat release system 4, a deep peak-shaving steam supply header 5, a steam inlet valve from the deep peak-shaving steam supply header to the feedwater pump turbine 6, and the feedwater pump turbine 7. The components form a complete molten salt transport, heat release, steam transport, and power drive link through pipelines. All pipelines are made of high-temperature and corrosion-resistant materials to adapt to the transport requirements of high-temperature molten salt (operating temperature is usually 300-565℃) and steam, avoiding pipeline corrosion or thermal deformation from affecting system reliability.

[0026] like Figure 1 As shown, the high-temperature molten salt tank serves as a storage container for high-temperature molten salt. It is equipped with temperature and level monitoring sensors to monitor the temperature and quantity of the molten salt in real time, ensuring a stable supply during peak shaving. The outlet of the high-temperature molten salt tank is connected to the inlet of the high-temperature molten salt pump via a pipeline.

[0027] The high-temperature molten salt pump, serving as the power source for molten salt transport, employs a variable frequency drive design. By adjusting the speed, it controls the molten salt output flow rate to adapt to the heat demand under different peak load conditions. The outlet of the high-temperature molten salt pump is connected to the hot salt side inlet of the molten salt exothermic system via a pipeline. A check valve is connected in series on this pipeline to prevent backflow of molten salt due to system pressure fluctuations.

[0028] The molten salt exothermic system is the core equipment for releasing heat from molten salt. It contains a heat exchange tube bundle. As the molten salt flows within the tube bundle, it releases heat, heating the feedwater outside the tube bundle and generating saturated or superheated steam. The steam-side outlet of the molten salt exothermic system is connected to the inlet of the steam outlet valve of the molten salt exothermic system via a pipeline.

[0029] The steam outlet valve of the molten salt exothermic system is an electrically controlled regulating valve with dual flow and pressure regulation functions. It can control the steam output according to the pressure requirements of the subsequent deep peak shaving steam supply header, avoiding the impact of steam parameter fluctuations on downstream equipment. The outlet of the steam outlet valve of the molten salt exothermic system is connected to the inlet of the deep peak shaving steam supply header through a pipeline.

[0030] The deep peak-shaving steam supply header serves as a steam buffer and distribution unit. It is equipped with pressure and temperature sensors to monitor the steam pressure and temperature within the header in real time. The header's volume is designed to buffer steam flow fluctuations during peak shaving, typically determined based on the steam consumption at the unit's maximum peak load, ensuring stable steam parameters within the header. The outlet of the deep peak-shaving steam supply header is connected via a pipeline to the inlet of the feedwater pump turbine inlet valve. This pipeline is equipped with a steam filter to remove impurities and trace amounts of condensate from the steam, preventing impurities from entering the feedwater pump turbine and causing wear on internal components.

[0031] The steam inlet valve from the deep peak-shaving steam supply header to the feedwater pump turbine adopts a quick-closing electric valve with an emergency shut-off function. When the feedwater pump turbine experiences abnormal operating conditions (such as speed overrun or excessive vibration), the steam supply can be quickly cut off to ensure equipment safety. The outlet of this valve is connected to the steam inlet of the feedwater pump turbine through a pipeline. After the steam enters the feedwater pump turbine, it expands and does work, driving the feedwater pump turbine to operate, which in turn drives the feedwater pump to work, delivering feedwater of qualified pressure and temperature to the boiler, forming a complete peak-shaving support link of molten salt exothermic reaction, steam generation, power drive, and feedwater supply.

[0032] During actual operation, when the unit receives a deep peak shaving command or when the pressure or flow of conventional steam source (such as turbine extraction steam) is insufficient, the peak shaving system starts the high-temperature molten salt pump. High-temperature molten salt flows out from the high-temperature molten salt tank, is pressurized by the high-temperature molten salt pump, and is sent to the hot salt side of the molten salt heat release system to exchange heat with the feedwater in the molten salt heat release system. After absorbing the heat of the molten salt, the feedwater vaporizes to produce steam. The steam enters the deep peak shaving steam supply header after its parameters are adjusted by the steam outlet valve of the molten salt heat release system. After the parameters are stabilized in the deep peak shaving steam supply header, the steam is supplied to the feedwater pump turbine through the deep peak shaving steam supply header to the feedwater pump turbine inlet valve, driving the feedwater pump turbine to maintain its rated speed. This ensures that the output flow and pressure of the feedwater pump meet the boiler's requirements, avoids a decrease in feedwater pump output due to insufficient conventional steam source, and thus ensures the stable operation of the unit under deep peak shaving conditions. Through the coordinated operation of its various components, the entire system achieves deep coupling between molten salt thermal storage and the unit's thermodynamic cycle, effectively solving the core problem of insufficient steam source for the feedwater pump turbine under deep peak shaving, and providing reliable hardware support for improving the unit's deep peak shaving capability.

[0033] like Figure 2 As shown, this application constructs a dual steam source supply architecture of molten salt supplementary steam and conventional steam extraction by adding a fourth-stage extraction steam valve 8 from the turbine to the feedwater pump turbine inlet valve, further enhancing the system's ability to guarantee the steam source for the feedwater pump turbine and its flexibility in adapting to operating conditions. This fourth-stage extraction steam valve to the feedwater pump turbine inlet valve is a fast-closing electric regulating valve of the same model as the one from the deep peak-shaving steam supply header to the feedwater pump turbine inlet valve, possessing the same pressure and flow regulation accuracy and emergency shut-off performance, ensuring a smooth parameter transition during dual steam source switching and avoiding significant fluctuations in the feedwater pump turbine speed. One end of the valve is connected to the extraction port of the fourth stage (intermediate-pressure cylinder 9) of the turbine via a high-temperature, high-pressure pipeline. This pipeline is equipped with an extraction steam parameter monitoring module (including pressure sensors, temperature sensors, and flow sensors) to collect real-time pressure, temperature, and flow data of the fourth-stage extraction steam from the turbine, providing a basis for steam source switching control. The other end is connected to the steam inlet of the feedwater pump turbine via a pipeline. This connecting pipeline and the pipeline from the deep peak-shaving steam supply header to the feedwater pump turbine inlet valve are combined before the steam inlet. A steam mixing buffer section is set at the merging point to ensure that the two steam sources are fully mixed before entering the feedwater pump turbine, avoiding internal airflow impact caused by differences in steam source parameters and ensuring the stability of equipment operation.

[0034] In actual operation, when the unit is in non-deep peak shaving conditions or when conventional steam sources are sufficient at the initial stage of deep peak shaving, the system prioritizes using the fourth stage extraction steam from the turbine as the driving steam source for the feedwater pump turbine. At this time, the opening of the fourth stage extraction steam to the feedwater pump turbine inlet valve is adjusted according to the steam demand of the feedwater pump turbine. The deep peak shaving steam supply header to the feedwater pump turbine inlet valve is closed, and the high-temperature molten salt system remains in standby mode. By utilizing conventional extraction steam resources, the operating losses of the molten salt system are reduced, improving the unit's economic efficiency under normal operating conditions. When the unit enters deep peak shaving conditions, and the pressure or flow rate of the fourth stage extraction steam cannot meet the minimum operating requirements of the feedwater pump turbine due to reduced unit load, the system automatically initiates the deep peak shaving supplementary steam process based on real-time data from the extraction steam parameter monitoring module. The process involves starting the high-temperature molten salt pump and opening relevant drain valves. Once the steam parameters generated by the molten salt exothermic system stabilize, the deep peak-shaving steam supply header to the feedwater pump turbine inlet valve is gradually opened. Simultaneously, based on the real-time speed and steam demand changes of the feedwater pump turbine, the opening ratio between the fourth-stage extraction steam from the turbine and the deep peak-shaving steam supply header to the feedwater pump turbine inlet valve is dynamically adjusted to achieve a smooth connection and coordinated supply of conventional extraction steam and molten salt supplementary steam. If the extraction steam parameters of the fourth stage of the turbine continue to drop to the point where they cannot meet the demand, the system automatically closes the fourth-stage extraction steam to the feedwater pump turbine inlet valve, and the molten salt supplementary steam system provides a stable driving steam source solely for the feedwater pump turbine. This ensures that the feedwater pump turbine maintains its rated output, guarantees the stable operation of the boiler feedwater system, and ultimately achieves deep peak-shaving capability for the unit across a wider load range. In addition, the dual steam source architecture also has a redundancy backup function. When any steam source pipeline or valve fails, the system can quickly switch to the other steam source supply mode, which effectively improves the reliability of the feedwater pump turbine driven steam source and the overall fault tolerance of the system during deep peak shaving.

[0035] like Figure 3As shown, the peak-shaving system of this application also includes: a deep peak-shaving steam supply header to deaerator inlet valve 10, which constructs a dual-purpose steam distribution system for feedwater pump turbine drive and deaerator heating. This allows the steam generated by the molten salt exothermic system to not only provide a driving steam source for the feedwater pump turbine, but also flexibly supplement the deaerator with heating steam, further expanding the functional coverage of the molten salt system and improving the overall stability and energy utilization efficiency of the unit's thermal system under deep peak-shaving conditions. The deep peak-shaving steam supply header to deaerator inlet valve adopts a high-temperature and high-pressure resistant electric regulating valve. Its design parameters (such as rated pressure, rated temperature, and flow capacity) are matched with the outlet steam parameters of the deep peak-shaving steam supply header and the inlet steam demand of the deaerator. The valve has a built-in pressure feedback regulation function, which can dynamically adjust the opening degree according to the real-time pressure demand of the deaerator. It also has a manual emergency regulation mode to ensure that basic steam supply function can still be maintained in the event of automatic control failure. From the perspective of the connecting pipeline, the valve's inlet is directly connected to the outlet of the deep peak-shaving steam supply header via a high-temperature resistant pipeline. A steam flow meter and temperature monitoring point are installed on this connecting pipeline to collect real-time steam flow and temperature data leading to the deaerator, providing data support for steam distribution control and system operation status assessment. The valve's outlet is connected to the steam inlet of deaerator 11 via an insulated pipeline. A check valve is also connected in series on the pipeline to prevent saturated water or wet steam in the deaerator from flowing back into the deep peak-shaving steam supply header, avoiding contamination of the steam quality in the header or causing pressure fluctuations in the pipeline. Simultaneously, the outer layer of the pipeline uses high-efficiency insulation material to reduce heat loss during steam transportation, ensuring that the steam entering the deaerator maintains parameters that meet heating requirements.

[0036] When the unit enters deep peak shaving operation, if the feedwater pump turbine can obtain a stable driving steam source through the aforementioned molten salt steam supplementation and conventional steam extraction, but the deaerator experiences insufficient pressure or flow of conventional heating steam source (such as low-pressure steam extraction from the turbine) due to reduced unit load, resulting in a drop in deaerator water tank temperature and weakened deaeration effect, the system can open the deep peak shaving steam supply header to the deaerator inlet valve based on the deaerator's real-time operating parameters (such as water tank temperature, dissolved oxygen content, and internal pressure). At this time, the excess steam generated by the molten salt exothermic system in the deep peak shaving steam supply header is regulated by this valve and delivered to the deaerator to supplement the heating steam required for deaeration, ensuring that the water in the deaerator is always maintained at the rated saturation temperature, ensuring that the dissolved oxygen content is controlled within the qualified range, avoiding corrosion of the boiler feedwater system due to poor deaeration effect, and ensuring the long-term safe operation of the unit's thermal equipment. If the steam demand of the feedwater pump turbine increases, such as a further decrease in unit load leading to a significant reduction in conventional steam extraction and requiring more molten salt makeup steam to support the feedwater pump turbine output, the system can automatically reduce the opening of the deep peak-shaving steam header to the deaerator inlet valve by comparing the steam demand priorities of the feedwater pump turbine and the deaerator. This will allocate more steam to the feedwater pump turbine side, prioritizing its stable operation. Conversely, if the steam demand of the feedwater pump turbine decreases, there is surplus molten salt makeup steam, and the deaerator requires heating, the valve opening can be increased to fully utilize the surplus steam for deaerator heating, reducing steam waste and improving energy efficiency. Furthermore, during the transition of the unit from deep peak shaving operation to normal operation, when the conventional extraction steam gradually recovers to sufficient levels and the molten salt steam replenishment system is gradually phased out, if the conventional heating steam source for the deaerator has not yet fully recovered and stabilized, the steam inlet valve from the deep peak shaving steam supply header to the deaerator can continue to maintain a certain opening until the conventional heating steam source for the deaerator meets the demand, and then gradually close it, so as to achieve seamless connection of deaerator heating during the operation transition period and further ensure the overall stability of the unit operation.

[0037] like Figure 4 As shown, the peak-shaving system of this application also includes four types of condensate drain valves: a condensate drain valve 12 from the deep regulating valve steam supply manifold to the feedwater pump inlet valve, a condensate drain valve 13 from the deep regulating valve steam supply manifold to the feedwater pump inlet valve, a condensate drain valve 14 from the deep regulating valve steam supply manifold to the deaerator inlet valve, and a condensate drain valve 15 from the deep regulating valve steam supply manifold to the deaerator inlet valve. This forms a condensate discharge mechanism covering the entire steam transmission chain, solving the problem of condensate accumulation in the pipeline during the initial start-up of deep peak-shaving operation, operation switching, and low-load operation stages from the source. This prevents condensate from entering core equipment with steam and causing malfunctions, while ensuring stable steam parameters and further enhancing the safety and reliability of system operation.

[0038] From the perspective of steam trap selection and installation layout, all four types of steam traps adopt mechanical structures (such as float type or thermostatic type), which have the function of automatically identifying condensate and quickly discharging it. Their rated working pressure, temperature and the medium parameters of the corresponding installation pipeline are fully compatible, and they can operate stably for a long time in high temperature and high pressure steam environment, avoiding valve damage or incomplete condensation due to parameter mismatch. Among them, the steam trap before the deep peak shaving steam supply header to the feedwater pump inlet valve is installed on the pipeline between the outlet of the deep peak shaving steam supply header and the inlet of the feedwater pump turbine inlet valve. This position is a critical link before steam reaches the feedwater pump turbine, and it can directly discharge the condensate generated by pipeline heat dissipation or pressure fluctuations before the steam is delivered to the inlet valve, preventing condensate from entering the inlet valve and causing valve jamming, reduced regulation accuracy, or entering the feedwater pump turbine along with the steam. The drain valve after the deep peak-shaving steam supply header to the feedwater pump inlet steam valve is installed on the pipeline between the deep peak-shaving steam supply header and the feedwater pump turbine inlet steam valve outlet and the feedwater pump turbine inlet steam port. This position is close to the core components of the feedwater pump turbine and can discharge condensate generated during the steam inlet valve regulation process or the final stage of steam delivery, avoiding water erosion caused by condensate impacting the feedwater pump turbine blades, or causing fluctuations in internal steam parameters and unstable speed of the turbine.

[0039] For the steam delivery link on the deaerator side, the condensate trap before the deaerator inlet valve is installed on the pipeline between the outlet of the deep peak shaving steam supply header and the inlet of the deaerator inlet valve. This allows for the timely discharge of condensate generated during the steam delivery process from the steam supply header to the deaerator inlet valve, preventing condensate from entering the deaerator inlet valve and causing valve malfunction or affecting the stability of subsequent deaerator make-up steam parameters. The condensate trap after the deep peak shaving steam supply header is installed on the pipeline between the outlet of the deaerator inlet valve and the deaerator inlet. This allows for the final condensate discharge before the steam enters the deaerator, preventing condensate from mixing with the feedwater in the deaerator, which could lead to a drop in deaerator water tank temperature, reduced deaeration efficiency, or pressure fluctuations within the deaerator, affecting the overall thermal system balance.

[0040] When the unit receives a deep peak shaving command and starts the high-temperature molten salt pump to prepare for dual steam source switching, the system will first simultaneously open these four types of condensate drain valves: the condensate drain valves before and after the deep peak shaving steam supply header to the feedwater pump inlet valve quickly discharge the initial condensate in the feedwater pump turbine inlet pipeline, laying the dry saturation or superheated parameter foundation for the steam entering the turbine later. The condensate drain valves before and after the deep peak shaving steam supply header to the deaerator inlet valve discharge the condensate in the deaerator supply pipeline, preparing for possible deaerator make-up steam later. As the molten salt exothermic system gradually generates stable steam, and the steam parameters in the deep peak shaving steam supply header reach the preset values, the system will monitor the changes in the condensate temperature and flow rate at the outlet of each condensate drain valve to determine the condensate discharge status in the pipeline. When the condensate temperature rises continuously to near the corresponding steam temperature in the pipeline, and the condensate flow rate drops significantly below the preset threshold, and this state remains stable for a preset duration, it indicates that the condensate in the pipeline has been largely discharged. At this point, the system will first gradually close the condensate valves before and after the steam inlet valve of the feedwater pump from the deep regulating valve steam header. Then, it will determine the closing timing of the other two types of condensate valves based on whether the deaerator needs supplemental steam. If the deaerator does not need supplemental steam, it will close them simultaneously. If supplemental steam is required, it will maintain a certain opening until the supplemental steam is completed before closing them. In addition, during deep peak shaving operation, if the system detects an abnormal drop in temperature in a certain section of the pipeline (which may be accompanied by the regeneration of condensate), it will automatically reopen the condensate valve of the corresponding pipeline until the condensate is discharged and the pipeline temperature returns to normal before closing it. This ensures that the entire steam transmission link is always in a safe operating state without condensate accumulation, providing reliable condensate discharge guarantee for the previously constructed system architecture, and further improving the operational stability and equipment safety of the molten salt system.

[0041] like Figure 5 As shown, the peak-shaving system of this application also includes: a reheat extraction steam molten salt heat exchanger 16, a reheat extraction steam molten salt heat exchanger inlet valve 17, a reheat extraction steam pressure reducing valve 18, a main steam extraction steam molten salt heat exchanger 19, a main steam extraction steam molten salt heat exchanger inlet valve 20, and a main steam extraction steam pressure reducing valve 21, forming a closed-loop energy storage and utilization system of dual-path extraction steam heat exchange + molten salt heat storage, realizing the efficient recovery and storage of surplus heat from boiler main steam and reheat extraction steam, providing a stable high-temperature molten salt source for the molten salt heat release system under deep peak-shaving conditions, and further improving the energy utilization efficiency and operational independence of the entire molten salt system.

[0042] From the perspective of equipment selection and connection logic, both the reheat extraction steam molten salt heat exchanger and the main steam extraction steam molten salt heat exchanger adopt a shell-and-tube heat exchange structure. Molten salt flows on the shell side and high-temperature extraction steam flows on the tube side. The heat exchange tube bundle is made of high-temperature and corrosion-resistant alloy material to ensure that it can adapt to the extreme operating conditions of main steam (typically 500-565℃, pressure 16-25MPa) and reheat extraction steam (typically 500-540℃, pressure 3-5MPa), while having high heat exchange efficiency to meet the requirements of rapid heating of molten salt. In terms of pipeline connections, the outlet of the cold salt pump 25 is connected to the molten salt side inlet of the reheat extraction steam molten salt heat exchanger and the molten salt side inlet of the main steam extraction steam molten salt heat exchanger respectively through branch pipelines. The inlet valves of the reheat extraction steam molten salt heat exchanger and the main steam extraction steam molten salt heat exchanger are connected in series on the two branch pipelines respectively. Both types of inlet valves are electric shut-off valves with fast switching and flow regulation functions. They can independently control the on / off of the two molten salt heat exchange links and the molten salt flow rate according to the extraction steam parameters and molten salt heat storage requirements.

[0043] The molten salt side outlet of the reheat extraction steam molten salt heat exchanger and the molten salt side outlet of the main steam extraction steam molten salt heat exchanger are connected to the inlet of the high-temperature molten salt tank through a confluence pipeline, so that the high-temperature molten salt (usually 480-550℃) heated by the two heat exchangers can be centrally transported to the high-temperature molten salt tank for storage, forming a closed-loop circulation of molten salt.

[0044] In the high-temperature extraction steam connection stage, the inlet of the reheat extraction steam pressure reducing valve is connected via a pipeline to the main steam pipeline supplying the boiler to the intermediate-pressure cylinder 3. This connection point is selected on the main steam pipeline before the inlet of the intermediate-pressure cylinder to ensure stable reheat extraction steam parameters. The reheat extraction steam pressure reducing valve adopts a pilot-operated structure and has high-precision pressure regulation capability. It can reduce the pressure of high-pressure reheat extraction steam to a range matching the design pressure of the reheat extraction steam molten salt heat exchanger tube side (usually 3-4 MPa), preventing high-pressure extraction steam from directly entering the heat exchanger and causing equipment damage. Its outlet is connected via a pipeline to the heat medium inlet of the reheat extraction steam molten salt heat exchanger. The low-temperature extraction steam after heat exchange is connected via a pipeline to the conventional steam supply header, realizing the cascade utilization of extraction steam and avoiding heat waste.

[0045] The inlet of the main steam extraction pressure reducing valve is connected to the pipeline that supplies main steam from boiler 22 to high-pressure cylinder 23 via a pipeline. The connection point is selected on the main steam pipeline before the inlet of the high-pressure cylinder to ensure the acquisition of high-parameter main steam. This pressure reducing valve also has a high-precision pressure regulation function, which can reduce the main steam pressure to a range that matches the design pressure of the tube side of the main steam extraction molten salt heat exchanger (usually 8-12 MPa). Its outlet is connected to the heat medium inlet of the main steam extraction molten salt heat exchanger via a pipeline. The main steam after heat exchange is then reconnected to the boiler and high-pressure cylinder via a pipeline, forming a main steam recycling system and reducing main steam loss.

[0046] When the unit is under high load (such as during peak daytime electricity consumption), and there is excess heat in the boiler main steam and reheat extraction steam, and the temperature or storage capacity of the molten salt in the high-temperature molten salt tank has not reached the preset value, the system starts the cold salt pump and selects a single-path or dual-path heat exchange mode according to the extraction steam parameters. If the reheat extraction steam parameters are better (such as stable pressure and temperature and large excess capacity), the inlet valve of the reheat extraction steam molten salt heat exchanger is opened, and the opening of the reheat extraction steam pressure reducing valve is adjusted to reduce the pressure of the reheat extraction steam to the target pressure before it is introduced into the tube side of the reheat extraction steam molten salt heat exchanger. The low-temperature molten salt delivered by the cold salt pump absorbs the heat of the extraction steam and heats up when flowing on the shell side, becoming high-temperature molten salt, which is then sent to the high-temperature molten salt tank for storage. If there is excess heat in the main steam, or if a rapid increase in the molten salt temperature is required, the inlet valve of the main steam extraction molten salt heat exchanger and the main steam extraction pressure reducing valve are opened simultaneously. After pressure reduction, the main steam is introduced into the tube side of the main steam extraction molten salt heat exchanger to exchange heat with the molten salt. The two high-temperature molten salt streams merge and are then sent to the high-temperature molten salt tank. During this process, the system monitors the liquid level and temperature of the high-temperature molten salt tank and the inlet and outlet parameters of the two heat exchangers (such as molten salt temperature and extraction steam temperature), and dynamically adjusts the cold salt pump speed and inlet valve opening to ensure a stable molten salt heating rate and the highest extraction steam utilization efficiency. When the unit enters deep peak-shaving conditions (such as off-peak electricity consumption at night) and the conventional steam source is insufficient, the high-temperature molten salt stored in the high-temperature molten salt tank is transported to the molten salt heat release system according to the previous process, releasing heat to generate steam, providing support for the feedwater pump turbine and deaerator, thus realizing a closed loop of excess heat storage and utilization. In addition, the system also has an emergency adjustment function. When the extraction steam parameters of a certain path fluctuate or the heat exchanger malfunctions, the corresponding inlet valve can be closed to quickly cut off the heat exchange of that path and switch to single-path operation mode to ensure that the molten salt heat storage process is not interrupted and to provide continuous energy guarantee for the stable operation of the molten salt system.

[0047] The existing equipment in the molten salt system of this application is described below with reference to the accompanying drawings.

[0048] like Figure 6As shown, the molten salt system is equipped with a No. 1 high-pressure heater 27, a No. 2 high-pressure heater 28, a No. 3 high-pressure heater 29, a No. 5 low-pressure heater 30, a No. 6 low-pressure heater 31, and a No. 7 low-pressure heater 32. Each heater is equipped with a corresponding emergency drain valve (emergency drain valves 33-35 for No. 1 to No. 3 high-pressure heaters, and emergency drain valves 36-37 for No. 5 to No. 7 low-pressure heaters). One end of each high-pressure heater's emergency drain valve is connected to the drain outlet of the corresponding high-pressure heater via a pipeline, and the other end is connected to a drain expansion container. One end of each low-pressure heater's emergency drain valve is connected to the drain outlet of the corresponding low-pressure heater, and the other end is also connected to the drain expansion container, forming a complete emergency drain path for the heaters. When the differential pressure of the corresponding extraction section (such as the differential pressure between extraction steam No. 1 and extraction steam No. 2, or the differential pressure between extraction steam No. 5 and extraction steam No. 6) is less than the preset first differential pressure value (such as 0.2MPa), the system will automatically open the corresponding emergency drain valve to quickly discharge the condensate accumulated in the heater, avoid abnormal pressure or reduced heat exchange efficiency caused by water accumulation, and thus ensure the synergy between the molten salt system's stable heat supply to the unit and the feedwater heating process.

[0049] Meanwhile, the molten salt system is also equipped with a low-pressure cylinder water spray valve 39 and a medium-pressure cylinder steam inlet regulating valve 40. These valves are crucial supporting components for ensuring stable operation of the molten salt system under deep peak-shaving conditions. The inlet of the low-pressure cylinder water spray valve is connected to the cooling water source via a pipeline, and its outlet is directly connected to the low-pressure cylinder exhaust port. When the system detects that the exhaust temperature of the low-pressure cylinder 41 is higher than the preset first exhaust temperature value (e.g., 80℃), it immediately opens the water spray valve to spray cooling water onto the exhaust port, rapidly reducing the exhaust temperature, preventing cylinder overheating and deformation, and avoiding any impact on the heating stability of the molten salt system due to cylinder malfunction. The medium-pressure cylinder steam inlet regulating valve is connected in series on the main steam pipeline from the boiler to the medium-pressure cylinder and is a core component for controlling the hot reheat steam pressure on which the molten salt system relies. When the reheat steam pressure is lower than the preset first pressure value (e.g., 3MPa), the system will automatically switch to the automatic pressure control mode of the intermediate pressure cylinder steam inlet regulating valve. By dynamically adjusting the valve opening, the reheat steam pressure is kept stable, ensuring that the reheat extraction steam molten salt heat exchanger is always in the optimal heat exchange efficiency range, thus ensuring the continuity and stability of the molten salt heating process.

[0050] In addition, the molten salt system is equipped with a fourth extraction to deaerator inlet valve 42 and a fourth extraction to steam supply header pressure reducing valve 43. Together, they form an inherent switching link between conventional steam source and molten salt supplementary steam, adapting to steam supply needs under different operating conditions. Specifically, the fourth extraction to deaerator inlet valve is connected at one end to the fourth stage extraction port of the turbine and at the other end to the deaerator inlet. Similarly, the fourth extraction to steam supply header pressure reducing valve is connected at one end to the fourth stage extraction port of the turbine and at the other end to the conventional steam supply header. Both types of valves are core components of the molten salt system adapted to the unit's conventional operating conditions, responsible for deaerator heating and steam supply to the conventional steam supply header under conventional operating conditions. When the unit enters deep peak shaving operation, and the steam extraction parameters (pressure and flow rate) of the fourth stage of the turbine cannot meet the needs of the deaerator and the steam supply header, the system will gradually close the steam inlet valve from the fourth extraction stage to the deaerator and the pressure reducing valve from the fourth extraction stage to the steam supply header through the inherent valve switching logic, and smoothly transition to the deep peak shaving steam supply header supplementary steam mode of the molten salt system. The steam generated by the exothermic reaction of the molten salt will replace the conventional extraction steam, and achieve seamless connection between the conventional steam source and the molten salt steam source.

[0051] The deep peak-shaving method will be explained in detail below with reference to the accompanying drawings. Figure 7 A flowchart illustrating a deep peak-shaving method provided in this application is shown. Specifically, it includes the following steps:

[0052] Step 710: When the instruction for the unit to enter deep peak shaving mode is received, start the high-temperature molten salt pump and open the drain valve before the feedwater pump inlet valve from the deep regulating valve steam supply manifold and the drain valve after the feedwater pump inlet valve from the deep regulating valve steam supply manifold.

[0053] Upon receiving a command to enter deep peak-shaving mode (this command is typically issued by the grid dispatch center based on load demand, or automatically generated by the generating unit based on real-time load falling below a preset peak-shaving threshold), the initial operation procedure is initiated: the high-temperature molten salt pump is immediately started in soft-start mode to prevent the pump from operating at full load instantaneously, which could cause a sudden increase in molten salt pipeline pressure or fluctuations in molten salt delivery flow. Simultaneously, the initial molten salt flow rate is collected in real-time by an electromagnetic flowmeter installed on the outlet pipeline of the high-temperature molten salt tank to ensure that the pump output flow rate is within a safe starting range, preventing excessive flow from causing heat exchange shock to the molten salt exothermic system.

[0054] Simultaneously, the drain valves before and after the feedwater pump inlet valve from the depth regulating valve steam supply header are opened, with the initial opening set at 80%-100%, to quickly drain the condensate accumulated in the feedwater pump turbine inlet pipeline (including the pipelines before and after the depth regulating valve steam supply header to the feedwater pump turbine inlet valve). If this condensate is not drained in time, it can easily enter the feedwater pump turbine with the steam during subsequent steam transport, causing equipment failures such as blade erosion and increased rotor vibration. It can also lead to fluctuations in steam parameters, affecting the output stability of the feedwater pump turbine.

[0055] Step 720: Adjust the speed of the high-temperature molten salt pump based on the molten salt flow rate output from the high-temperature molten salt tank and the steam pressure at the outlet of the molten salt exothermic system.

[0056] After the high-temperature molten salt pump is started and running stably, the speed of the high-temperature molten salt pump is finely adjusted based on the molten salt flow rate output from the high-temperature molten salt tank and the steam pressure at the outlet of the molten salt exothermic system, so as to ensure that the molten salt exothermic system can continuously generate steam with stable parameters.

[0057] Specifically, real-time molten salt flow rate data is collected at a frequency of 1 second per second using a high-precision electromagnetic flowmeter installed on the outlet pipeline of the high-temperature molten salt tank. Simultaneously, real-time steam pressure data is collected by a pressure sensor on the steam side outlet pipeline of the molten salt exothermic system. Both types of data undergo filtering preprocessing (using a first-order low-pass filter algorithm) to eliminate outliers caused by transient electromagnetic interference or pressure pulses. Subsequently, the continuously collected flow and pressure data over 10 minutes are arranged in a time series to form a 1200×2 flow and pressure time-series feature matrix (600 seconds in 10 minutes, with one data point taken every 0.5 seconds, including both flow and pressure dimensions). This matrix comprehensively records the dynamic changes in molten salt flow rate and steam pressure during peak shaving, providing a data foundation for subsequent feature extraction. After the matrix is ​​constructed, it is processed using an adaptive filtering algorithm (using the minimum mean square error filtering algorithm). This algorithm effectively separates the steady-state component and dynamic fluctuation component in the data by adjusting the filtering coefficients in real time. The steady-state component reflects the average stable state of molten salt flow rate and steam pressure under the current operating conditions. For example, the molten salt flow rate is stable at 48 m³ / s for a certain period of time. 3 The steam pressure remains stable at around 3.3 MPa per hour; this component is the core basis for determining the basic speed of the high-temperature molten salt pump. The dynamic fluctuation component reflects the instantaneous fluctuations in parameters caused by external disturbances (such as minor changes in the molten salt tank level or fluctuations in pipeline resistance). For example, at a flow rate of 48 m³ / h... 3 / h±1.2m 3 Fluctuations within the range of / h and pressure fluctuations within the range of 3.3MPa±0.05MPa need to be compensated and adjusted to offset their impact on system stability.

[0058] After obtaining the steady-state component and the dynamic fluctuation component, the base speed regulation and the compensation speed regulation are calculated respectively. For determining the base speed regulation, the system pre-established a correlation model between molten salt flow rate, steam pressure, and pump speed based on historical commissioning data and simulation experiments. This model is stored in the control unit as a three-dimensional mapping table, which clearly defines the optimal pump speed corresponding to different combinations of steady-state flow rate and steady-state pressure (e.g., when the steady-state flow rate is 48 m³ / s). 3When the steady-state pressure is 3.3 MPa, the corresponding pump speed is 1450 r / min. Substituting the separated steady-state values ​​of molten salt flow rate and steam pressure into this correlation model, the theoretical speed under the current operating conditions is calculated through interpolation. This is then compared with the actual current speed of the high-temperature molten salt pump; the difference is the base speed adjustment. If the theoretical speed is 1450 r / min and the actual speed is 1400 r / min, the base speed adjustment is +50 r / min, indicating that the pump speed needs to be increased to match the current steady-state parameter requirements. To determine the compensation speed adjustment amount, the dynamic fluctuation component is first decomposed using multi-scale wavelet decomposition (using the db4 wavelet basis function, with a decomposition level of 3 layers). This decomposes the fluctuation component into three frequency bands: low-frequency fluctuations (corresponding to slow fluctuations with a period greater than 10 seconds, such as changes in molten salt viscosity caused by ambient temperature changes), mid-frequency fluctuations (corresponding to equipment operation fluctuations with a period of 1-10 seconds, such as slight vibrations of pump bearings), and high-frequency fluctuations (corresponding to instantaneous fluctuations with a period less than 1 second, such as turbulent impacts of molten salt in pipelines). Subsequently, the fluctuation characteristics of each frequency band are judged based on a preset fuzzy control rule base, which is constructed using expert experience and experimental data. For example, "when the high-frequency fluctuation amplitude exceeds 0.8m..." 3 When the flow rate is 0.03 MPa or the pressure is 0.03 MPa, the compensation speed adjustment is +10 r / min; when the medium frequency fluctuation amplitude is 0.3-0.8 m 3 When the flow rate is within the range of 0.01-0.03 MPa (pressure), the compensation speed adjustment is +5 r / min. Based on the actual values ​​of the fluctuation characteristics of each frequency band, the corresponding fuzzy rules are matched to calculate the compensation adjustment for each frequency band. Then, the final compensation speed adjustment is obtained by weighted summation (high-frequency fluctuation weight 0.5, mid-frequency fluctuation weight 0.3, low-frequency fluctuation weight 0.2) to offset the impact of dynamic fluctuations on parameter stability.

[0059] Finally, the final speed regulation of the high-temperature molten salt pump was determined by constructing a dual-closed-loop feedback regulation mechanism. In this dual-closed-loop structure, the outer loop uses the target deviation of molten salt flow rate and the target deviation of steam pressure as input parameters. The target deviation of molten salt flow rate is a preset target value of molten salt flow rate (determined based on the heat exchange efficiency of the molten salt exothermic system design, such as 50m³ / h). 3The difference between the base speed adjustment and the real-time steady-state flow rate is used to determine the steam pressure target deviation. The target steam pressure deviation is the difference between the preset steam pressure target value (determined based on the steam demand of the feedwater pump turbine, e.g., 3.5 MPa) and the real-time steady-state pressure value. The outer loop uses a proportional-integral (PI) control algorithm to initially correct the base speed adjustment, ensuring the adjustment direction aligns with the target parameter requirements. The inner loop uses the superimposed value of the base speed adjustment and the compensated speed adjustment as input parameters. Combined with the speed feedback signal from the high-temperature molten salt pump (acquired by a speed sensor on the pump shaft), model predictive control logic (prediction step size 5 seconds, control step size 1 second) is used to dynamically optimize the superimposed value. This logic establishes a predictive model of pump speed, molten salt flow rate, and steam pressure to anticipate potential parameter changes caused by the superimposed adjustment. If it predicts that the flow rate or pressure will exceed the target range after adjustment, the superimposed value is corrected (e.g., a superimposed value of +60 r / min predicts that the flow rate will exceed the target value by 2 m³ / min). 3 If the speed is / h, it is corrected to +55r / min). Ultimately, the optimized adjustment output of the dual-closed-loop control mechanism is the final speed adjustment of the high-temperature molten salt pump. This adjustment is converted into a control signal and sent to the variable frequency drive of the high-temperature molten salt pump to achieve precise adjustment of the pump speed. Throughout the entire adjustment process, the system repeats the parameter acquisition, feature extraction, adjustment calculation, and feedback control process every 0.5 seconds to ensure that the molten salt flow rate and steam pressure remain stable within the target range, providing a reliable guarantee for the steam supply to the subsequent feedwater pump turbine and deaerator.

[0060] Step 730: Collect the outlet condensate temperature of the condensate drain valve from the steam supply manifold to the feedwater pump inlet valve and the outlet condensate drain valve from the steam supply manifold to the feedwater pump inlet valve. Adjust the opening of the condensate drain valve from the steam supply manifold to the feedwater pump inlet valve and the outlet condensate drain valve from the steam supply manifold to the feedwater pump inlet valve according to the real-time change rate and cumulative change of the condensate temperature. Continue until the condensate temperature rises to the preset condition and remains stable for the preset duration. Then close the condensate drain valve from the steam supply manifold to the feedwater pump inlet valve and the outlet condensate drain valve from the steam supply manifold to the feedwater pump inlet valve.

[0061] While adjusting the speed of the high-temperature molten salt pump, the outlet temperatures of the drain valves from the steam supply manifold to the feedwater pump inlet valve and from the steam supply manifold to the feedwater pump inlet valve are continuously collected. The opening of the two drain valves is dynamically adjusted according to the real-time rate of change and the cumulative change of the drain temperature until the condensate in the pipeline is completely discharged.

[0062] After the steam traps are opened, platinum resistance temperature sensors installed on the outlet pipes of the two steam traps synchronously collect two channels of steam trap temperature data at a frequency of 2 seconds per acquisition, covering the entire process from the opening to the closing of the steam traps. A dynamic sliding window algorithm (window duration set to 1 minute, window data updated every 10 seconds) is used to extract features from the steam trap temperature data, calculating the real-time rate of change of steam trap temperature (reflecting the speed of temperature rise), the acceleration of temperature change (reflecting the trend of the rate of change), the cumulative change (the temperature difference from the start of acquisition to the current value), and the temperature fluctuation variance (reflecting temperature stability). These four feature parameters are integrated to form a multi-dimensional feature vector. For example, at a certain moment, the feature vector might be [0.08℃ / s, 0.002℃ / s]. 2 [25℃, 0.3℃2], this vector comprehensively describes the dynamic state of the current hydrophobic temperature.

[0063] Based on the extracted multi-dimensional feature vectors, a Gaussian membership function is used to fuzzily divide them into multiple fuzzy subsets, thus transforming quantitative parameters into qualitative features. For each feature parameter, a corresponding fuzzy subset and membership function are pre-defined. For example, the real-time temperature change rate is divided into three subsets: "slow" (0-0.05℃ / s), "stable" (0.05-0.1℃ / s), and "fast" (0.1-0.15℃ / s); the cumulative temperature change is divided into three subsets: "small" (0-15℃), "medium" (15-30℃), and "large" (30-45℃). Each subset corresponds to a Gaussian membership function (the function parameters are determined by fitting historical hydrophobic data to ensure the accuracy of the membership calculation). The real-time values ​​of each parameter in the feature vector are substituted into the corresponding membership function to calculate the membership degree of each feature to different fuzzy subsets. For example, if the temperature change rate at a certain moment is 0.08℃ / s, the membership degree to the "stable" subset is 0.9, and the membership degrees to the "slow" and "fast" subsets are 0.1 and 0.05, respectively. This result intuitively reflects the degree of belonging of the current parameter in the fuzzy space.

[0064] By combining a pre-defined fuzzy inference rule base with the membership degrees of each feature, the trigger strength of each rule is calculated and the output results are fused to obtain a preliminary opening adjustment amount. The fuzzy inference rule base is constructed based on the experience of thermal system experts and a large amount of hydrophobic experimental data, covering opening adjustment strategies corresponding to different feature combinations. For example, rule 1: "If the temperature change rate is 'stable,' the cumulative change is 'medium,' and the fluctuation variance is 'small,' then the opening adjustment amount is -10%" (meaning a 10% reduction in opening). Rule 2: "If the temperature change rate is 'slow,' the cumulative change is 'small,' and the fluctuation variance is 'medium,' then the opening adjustment amount is 0%" (meaning maintaining the current opening). For each rule, the minimum membership degree of each feature in the antecedent of the rule is taken as the trigger strength of that rule (i.e., the "smallest" principle). For example, the minimum membership degree of each feature in rule 1 is 0.8, so the trigger strength is 0.8; the minimum membership degree in rule 2 is 0.5, so the trigger strength is 0.5. Subsequently, a weighted average method is used to fuse the output results of all triggering rules. The initial opening adjustment amount is obtained by multiplying the trigger strength of each rule by the corresponding rule's opening adjustment amount, summing all weighted results, and dividing by the sum of the trigger strengths. For example, a result of -8% after fusion indicates that the steam trap opening needs to be reduced by 8%.

[0065] To further improve the regulation accuracy, a PID controller is introduced to calculate the deviation compensation, which is then superimposed with the initial opening adjustment to obtain the final opening adjustment. The input parameters of the PID controller are set as the deviation (denoted as ΔT) between the target condensate temperature (determined based on the steam inlet parameters of the feedwater pump turbine, typically the saturation temperature at the corresponding steam pressure, such as 240℃ for 3.3MPa steam) and the current actual condensate temperature, and the rate of change of the deviation (denoted as ΔT / Δt, reflecting the trend of deviation change). The proportional coefficient Kp, integral coefficient Ki, and derivative coefficient Kd of the controller are determined through trial and error and on-site debugging (e.g., Kp = 2.0, Ki = 0.1, Kd = 0.05) to ensure fast controller response and no overshoot. The system calculates the deviation compensation based on ΔT and ΔT / Δt using the PID control algorithm. For example, when the actual temperature is 5℃ lower than the target value and the rate of change of the deviation is -0.02℃ / s, the compensation is +5% (meaning an additional 5% increase in opening to accelerate temperature rise). The compensation amount is added to the initial opening adjustment amount obtained earlier to obtain the final opening adjustment amount. For example, -8% + 5% = -3%, which means that the opening needs to be reduced by 3% in the end.

[0066] Finally, the opening of the condensate traps before and after the feedwater pump inlet valve is controlled according to the final opening adjustment amount. The final opening adjustment amount is converted into a control signal for the electric valve and sent to the corresponding valve actuator. The actuator adjusts the valve opening according to the signal. For example, if the current opening is 80% and the adjustment amount is -3%, it will be adjusted to 77%. During the adjustment process, condensate temperature data is collected every 30 seconds. The above feature extraction, rule reasoning, and PID compensation process is repeated to dynamically update the opening adjustment amount until the condensate temperature rises to within ±2℃ of the target value and remains stable for a preset time (usually 8-10 minutes). At this point, it is determined that the condensate in the pipeline has been completely discharged, and the system issues a shutdown command to completely close the two condensate traps to prevent steam leakage through the condensate traps and energy loss. At the same time, it ensures that the steam entering the feedwater pump turbine is dry saturated steam or superheated steam, ensuring the safe and stable operation of the equipment.

[0067] Step 740: Determine the target steam pressure and target steam flow rate required by the feedwater pump turbine based on the real-time speed of the feedwater pump turbine, the boiler feedwater flow rate, and the boiler feedwater temperature.

[0068] First, the core input parameters and auxiliary correction parameters are clearly defined, and the correlation mapping relationship between the parameters is established. The core input parameters are the real-time speed of the feedwater pump turbine, the boiler feedwater flow rate, and the boiler feedwater temperature. These three parameters directly determine the output demand of the feedwater pump turbine. The real-time speed reflects the current driving state of the turbine (collected by a photoelectric speed sensor installed on the turbine shaft end). Higher speeds usually require higher steam parameters. The boiler feedwater flow rate reflects the boiler water load (collected by a vortex flow meter in the boiler feedwater pipeline). When the flow rate increases, the turbine needs to increase its output to drive the feedwater pump. The boiler feedwater temperature affects the power consumption of the feedwater pump (collected by a platinum resistance temperature sensor in the feedwater pipeline). Lower temperatures require the feedwater pump to consume more energy, indirectly requiring the turbine to provide higher steam energy. Auxiliary correction parameters include the feedwater pump turbine inlet pressure, outlet feedwater pressure, and ambient temperature. The inlet / outlet feedwater pressure reflects the working resistance of the feedwater pump (collected by a pressure sensor). A larger pressure difference requires the turbine to output greater torque. Ambient temperature affects the heat dissipation of the equipment and the heat exchange efficiency of molten salt (collected by the unit's ambient temperature sensor). In low-temperature environments, steam parameters need to be adjusted appropriately to compensate for heat loss. Based on historical operating data of the unit (covering more than 300 sets of operating condition data under different loads and ambient temperatures), an algorithm combining multiple linear regression and neural networks is used to construct the correlation mapping relationship between core parameters, auxiliary parameters, and steam pressure and steam flow rate. This relationship is expressed in the form of a mathematical model: P=a1×N+a2×Q+a3×T+b1×P1+b2×P2+b3×T0+c, where P is the steam pressure, N is the real-time speed of the feedwater pump turbine, Q is the boiler feedwater flow rate, T is the boiler feedwater temperature, P1 is the feedwater inlet pressure of the feedwater pump turbine, P2 is the feedwater outlet pressure of the feedwater pump turbine, and T0 is the ambient temperature; a1, a2, and a3 are the coefficients corresponding to the core input parameters (speed, feedwater flow rate, and feedwater temperature), b1, b2, and b3 are the coefficients corresponding to the auxiliary correction parameters (inlet feedwater pressure, outlet feedwater pressure, and ambient temperature), and c is the model constant term. F = d1×N + d2×Q + d3×T + e1×P1 + e2×P2 + e3×T0 + f, where d1, d2, and d3 are the coefficients corresponding to the core input parameters, e1, e2, and e3 are the coefficients corresponding to the auxiliary correction parameters, and f is the model constant term.

[0069] Based on the correlation mapping relationship, the main weight and auxiliary correction weights are allocated according to the degree of influence of parameters on steam demand. The influence of each parameter is quantitatively evaluated using the analytic hierarchy process (AHP): Among the core input parameters, the real-time speed of the feedwater pump turbine has the greatest impact on steam pressure and flow rate (main weight 0.4), as it directly determines the turbine's work demand; boiler feedwater flow rate is the second most important (main weight 0.3), directly related to the feedwater pump's output flow demand; boiler feedwater temperature has a relatively small impact (main weight 0.2), mainly affecting power consumption indirectly by changing feedwater viscosity. Among the auxiliary correction parameters, the difference between inlet and outlet feedwater pressure has a significant impact (auxiliary correction weight 0.05), while ambient temperature has the least impact (auxiliary correction weight 0.03), with the remaining 0.02 weight used for dynamic balancing of parameter deviations.

[0070] The real-time values ​​of the core input parameters are correlated with their corresponding sovereign weights, substituted into the correlation mapping relationship, and combined with the design characteristic curve of the feedwater pump turbine to obtain preliminary values ​​of steam pressure and steam flow. Specifically, the real-time speed, feedwater flow rate, and feedwater temperature are first multiplied by their corresponding sovereign weights to obtain weighted core parameter values. These weighted values ​​are then substituted into the core parameter items of the correlation mapping relationship to calculate the basic steam pressure and basic steam flow rate. Subsequently, the basic parameters are corrected using the design characteristic curve of the feedwater pump turbine (which reflects the correspondence between steam pressure, flow rate, and turbine output at different speeds). For example, when the real-time speed exceeds 90% of the design rated speed, the basic steam pressure needs to be increased by 5% according to the characteristic curve to ensure sufficient turbine output, ultimately yielding preliminary values ​​of steam pressure and steam flow.

[0071] Auxiliary correction parameters are introduced to dynamically correct the initial values ​​to eliminate the influence of changes in the external environment and equipment status. The real-time values ​​of inlet feedwater pressure, outlet feedwater pressure, and ambient temperature are multiplied by their corresponding auxiliary correction weights to obtain weighted auxiliary parameter values. These weighted values ​​are then substituted into the auxiliary parameter terms of the correlation mapping relationship to calculate the correction coefficient. For example, when the inlet feedwater pressure is 0.2 MPa higher than the design value, the correction coefficient is 1.03, requiring the initial steam pressure value to be multiplied by 1.03 to compensate for the increased load caused by the increased pressure difference. When the ambient temperature is 10°C lower than the design value, the correction coefficient is 1.02, requiring the initial steam flow rate value to be multiplied by 1.02 to compensate for heat loss. Multiplying the initial values ​​by the corresponding correction coefficients yields the corrected steam pressure and steam flow rates.

[0072] The corrected parameters are compared with the optimal steam parameters under the same historical operating conditions of the feedwater pump turbine, and parameter optimization is achieved through weight adjustment. Using the K-means clustering algorithm, the most similar historical operating conditions are matched from the historical database, and the optimal steam parameters (i.e., the steam pressure and flow rate when the turbine efficiency is highest and energy consumption is lowest) under those conditions are extracted. The deviation between the corrected parameters and the optimal parameters is calculated. If the deviation is within the preset allowable range (pressure deviation ±0.05MPa, flow rate deviation ±1t / h), the corrected parameters are determined as the target steam pressure and target steam flow rate. If the deviation exceeds the allowable range, the allocation ratio of the main weight and auxiliary correction weights is readjusted (for example, if the steam pressure deviation is too large, the main weight of the real-time speed can be increased by 0.02, while the main weight of the feedwater temperature can be decreased by 0.02). The parameter association, preliminary calculation, and dynamic correction process is repeated until the deviation between the corrected parameters and the historical optimal parameters meets the requirements, and the target steam pressure and target steam flow rate are finally determined.

[0073] Step 750: Based on the target steam pressure, target steam flow rate, and the actual steam pressure and actual steam flow rate at the outlet of the deep peak shaving steam supply header, adjust the opening of the steam inlet valve from the deep peak shaving steam supply header to the feedwater pump turbine to match the steam supply with the steam demand of the feedwater pump turbine.

[0074] The actual steam pressure and actual steam flow rate at the outlet of the deep peak-shaving steam header are compared with the target steam pressure and target steam flow rate determined in step 740. The deviation calculation adopts the absolute difference method to obtain the pressure deviation ΔP (ΔP = actual steam pressure - target steam pressure) and flow deviation ΔF (ΔF = actual steam flow rate - target steam flow rate), respectively. The allowable deviation range is preset (pressure deviation ±0.03MPa, flow deviation ±1t / h). This range is determined based on the design and operation requirements of the feedwater pump turbine and the unit commissioning experience to ensure that the turbine can output power stably within this range.

[0075] Based on the comparison between the deviation value and the allowable range, three core adjustment scenarios are identified: First, if the actual parameters are all lower than the target values ​​(ΔP < -0.03MPa and ΔF < -1t / h), it indicates insufficient steam supply, and the valve opening needs to be increased; second, if the actual pressure is higher than the target value but the flow rate meets the requirements (ΔP > 0.03MPa and |ΔF| ≤ 1t / h), the opening needs to be finely adjusted to reduce the pressure and avoid turbine overpressure; third, if the actual flow rate is higher than the target value but the pressure meets the requirements (ΔF > 1t / h and |ΔP| ≤ 0.03MPa), the opening needs to be appropriately reduced to control the flow rate and prevent turbine speed overrun.

[0076] Based on different adjustment scenarios, the system adopts a segmented opening adjustment strategy, combined with closed-loop feedback to achieve precise control. For insufficient supply scenarios, the steam inlet valve opening is gradually increased by 5% per adjustment, with actual parameters collected every 30 seconds after each adjustment to observe the trend of deviation changes. If the deviation decreases rapidly, the adjustment range is maintained. If the deviation decreases slowly, the range can be increased to 8% per adjustment, but the maximum adjustment range per adjustment should not exceed 10% to avoid drastic fluctuations in steam parameters due to sudden changes in opening. For high pressure scenarios, the opening is decreased in small increments of 2% per adjustment, with pressure data collected every 20 seconds after each adjustment until the pressure deviation falls within the allowable range. This small-amplitude adjustment mode avoids affecting the turbine output stability due to sudden pressure drops. For high flow scenarios, the opening is decreased by 3% per adjustment, while simultaneously monitoring the real-time speed of the feedwater pump turbine (collected via a shaft-end photoelectric speed sensor, accuracy ±1 r / min). If the speed shows a downward trend, adjustment is immediately paused and the current opening is maintained. Fine-tuning continues only after the speed stabilizes to ensure that flow control does not affect the normal operation of the turbine.

[0077] During the adjustment process, a dynamic feedback correction mechanism is introduced to optimize the adjustment amplitude and rhythm in real time. By continuously collecting the actual parameters after adjustment, the feedwater pump turbine speed, and the boiler feedwater flow rate (synchronously reflecting changes in boiler demand), a three-dimensional feedback matrix is ​​constructed to determine the impact of the current opening adjustment on steam parameters and equipment operating status. For example, if the pressure rises after increasing the opening but the flow rate does not increase synchronously, it may be due to changes in pipeline resistance. It is necessary to combine the steam pressure data of the molten salt exothermic system outlet and appropriately adjust the high-temperature molten salt pump speed to improve steam supply capacity before continuing to adjust the steam inlet valve opening. If the flow rate drops to the target value after decreasing the opening, but the turbine speed is lower than the rated speed (e.g., rated speed 3000 r / min, actual speed reduced to 2920 r / min), the opening adjustment needs to be paused, and the target steam parameters determined in step 740 need to be re-verified to ensure they are suitable for the current operating conditions. If necessary, the target value should be recalculated before re-implementing the adjustment.

[0078] When the deviations of the actual steam pressure and actual steam flow rate from the target values ​​all fall within the preset allowable range, and the real-time speed of the feedwater pump turbine is stable within ±50 r / min of the rated speed, while the boiler feedwater flow rate and feedwater pressure remain within the design requirement range, it indicates that the steam supply and the feedwater pump turbine demand are fully matched. At this time, the system stops actively adjusting the opening degree and switches to steady-state monitoring mode, collecting key parameters every 1 minute. If the parameters drift slightly (such as a pressure deviation close to ±0.03 MPa), a micro-adjustment of 1% per adjustment is made to ensure that the molten salt system continues to operate stably, providing reliable steam support for deep peak shaving of the unit.

[0079] In addition, when carrying out deep peak shaving of the molten salt system, it is also necessary to combine it with the inherent equipment of the molten salt system for coordinated control to ensure the overall stability of the peak shaving process.

[0080] Based on the set unit load variation rate as the first preset rate value (e.g., 1.5% THA / min) and the unit target load as the first preset peak value (e.g., 20% THA), the differential pressure of each extraction section and equipment operating parameters are monitored in real time. When the differential pressure between extraction steam No. 1 and extraction steam No. 2 is less than the preset first differential pressure value (e.g., 0.2 MPa), the emergency drain valve of high-pressure heater No. 1 is opened. When the differential pressure between extraction steam No. 2 and extraction steam No. 3 is less than the preset first differential pressure value, the emergency drain valve of high-pressure heater No. 2 is opened. When the differential pressure between extraction steam No. 5 and extraction steam No. 6, and the differential pressure between extraction steam No. 6 and extraction steam No. 7 are less than the preset first differential pressure values, the emergency drain valves of low-pressure heater No. 5 and low-pressure heater No. 6 are opened respectively. By timely draining the condensate accumulated in the heaters, the heat exchange efficiency is prevented from decreasing or the equipment is damaged due to insufficient differential pressure. Simultaneously, the low-pressure cylinder exhaust temperature is continuously monitored. When this temperature exceeds the preset first exhaust temperature value (e.g., 80℃), the low-pressure cylinder water spray valve is immediately opened to deliver cooling water to the low-pressure cylinder exhaust port to reduce the exhaust temperature and prevent overheating of the cylinder body from affecting the coordinated operation of the molten salt system and the unit. If the reheat steam pressure is detected to be lower than the preset first pressure value (e.g., 3MPa), the automatic pressure control mode of the intermediate-pressure cylinder inlet steam regulating valve is activated. The control pressure object of the intermediate-pressure cylinder inlet steam regulating valve is set to the reheat steam pressure, and the target pressure value is the steam pressure of the steam supply header. The reheat steam pressure is maintained stable by dynamically adjusting the valve opening to ensure the heat exchange efficiency of the reheat extraction molten salt heat exchanger.

[0081] In addition, before starting the molten salt exothermic system, it is necessary to confirm that the electric heating temperature of all equipment on the salt side of the molten salt exothermic system is higher than the first preset electric heating temperature value (e.g., 200℃), and that the steam drum water level in the molten salt exothermic system has reached the preset first steam drum water level value (e.g., 50% of the steam drum volume). At the same time, the unit load coordination control mode should be switched to the coordinated boiler-following mode, with the boiler responsible for adjusting the main steam pressure and the turbine responsible for adjusting the unit electrical load, providing the prerequisites for the stable start-up of the molten salt exothermic system. When starting the molten salt exothermic system, in addition to opening the high-temperature molten salt pump and related drain valves, the high-temperature molten salt pump outlet valve should also be opened to the first preset opening degree (e.g., 5%), and the automatic water level control of the molten salt exothermic system inlet valve should be activated, setting the control object to the steam drum water level of the molten salt exothermic system, with the target water level value being the first preset water level value. When the steam pressure in the deep peak-shaving steam supply header exceeds the first preset steam pressure value (e.g., 3.2 MPa), automatic pressure control of the high-temperature molten salt pump outlet valve is activated. The controlled object is the steam pressure in the deep peak-shaving steam supply header, and the target pressure value is the first preset steam pressure value. During the steam source switching process, the steam inlet valve from the deep peak-shaving steam supply header to the feedwater pump turbine is opened at a first preset rate (e.g., 1% / s). After the valve is fully opened, the steam inlet valve from the fourth pump to the feedwater pump turbine is closed at a second preset rate (e.g., 0.5% / s). The drain valves before and after the steam inlet valve from the deep peak-shaving steam supply header to the deaerator are opened. When the drain temperature exceeds the first preset temperature value (e.g., 250℃), these two types of drain valves are closed. Then, the steam inlet valve from the deep peak-shaving steam supply header to the deaerator is opened at a third preset rate (e.g., 0.8% / s), and the emergency drain valve of the No. 3 high-pressure heater is opened at a fourth preset rate (e.g., 0.3% / s). After the deaerator inlet valve is fully opened, close the fourth extraction to deaerator inlet valve at the fifth preset rate (e.g., 0.6% / s). When starting the reheat extraction system, activate the automatic pressure control mode of the reheat extraction pressure reducing valve, setting the control object to the steam supply header pressure, with a target pressure value of the first preset pressure value (e.g., 3MPa). After opening the inlet valve of the reheat extraction molten salt heat exchanger, activate the automatic temperature control of this valve, setting the control object to the outlet salt temperature of the reheat extraction molten salt heat exchanger, with a target temperature value of the second preset temperature value (e.g., 500℃). When starting the main steam extraction pressure reducing valve, activate its automatic flow control mode, setting the control object to the main steam extraction flow rate, with a target flow rate value of the reheat extraction flow rate (e.g., 50t / h). After opening the inlet valve of the main steam extraction molten salt heat exchanger, activate the automatic temperature control of this valve, setting the control object to the outlet salt temperature of the main steam extraction molten salt heat exchanger, with a target temperature value of the second preset temperature value. Finally, the pressure reducing valve of the four-stage steam supply manifold is closed at the first preset rate until it is completely closed, ensuring a smooth transition between the regular steam source and the molten salt replenishment steam.

[0082] Optionally, the deep peak-shaving method can be deployed on an electronic device with data processing capabilities, or a functional module within that electronic device, without limitation.

[0083] For example, the electronic device can be a server, which can be a single server or a server cluster consisting of multiple servers. As another example, the electronic device can be a mobile phone, tablet computer, desktop computer, laptop computer, handheld computer, notebook computer, ultra-mobile personal computer (UMPC), netbook, as well as cellular phones, personal digital assistants (PDAs), augmented reality (AR) devices, virtual reality (VR) devices, and other terminal devices. As yet another example, the electronic device can also be a recording device, video surveillance equipment, etc. This application does not impose any special limitations on the specific form of the electronic device.

[0084] The following example uses electronic devices, such as... Figure 8 As shown, Figure 8 The hardware structure of an electronic device 800 provided in this application.

[0085] like Figure 8 As shown, the electronic device 800 includes a processor 810, a communication line 820, and a communication interface 830.

[0086] Optionally, the electronic device 800 may also include a memory 840. The processor 810, memory 840, and communication interface 830 can be connected via a communication line 820.

[0087] The processor 810 can be a central processing unit (CPU), a general-purpose processor, a network processor (NP), a digital signal processor (DSP), a microprocessor, a microcontroller, a programmable logic device (PLD), or any combination thereof. The processor 810 can also be any other device with processing capabilities, such as a circuit, device, or software module, without limitation.

[0088] In one example, processor 810 may include one or more CPUs, for example Figure 8 CPU0 and CPU1 in the CPU.

[0089] As an optional implementation, the electronic device 800 may include multiple processors; for example, in addition to processor 810, it may also include processor 880. A communication line 820 is used to transmit information between the various components included in the electronic device 800.

[0090] Communication interface 830 is used for communication with other devices or other communication networks. These other communication networks can be Ethernet, Radio Access Network (RAN), Wireless Local Area Networks (WLAN), etc. Communication interface 830 can be a module, circuit, transceiver, or any device capable of enabling communication.

[0091] Memory 840 is used to store instructions. These instructions can be computer programs.

[0092] The memory 840 can be a read-only memory (ROM) or other type of static storage device that can store static information and / or instructions; it can also be a random access memory (RAM) or other type of dynamic storage device that can store information and / or instructions; it can also be an electrically erasable programmable read-only memory (EEPROM), a compact disc read-only memory (CD-ROM) or other optical disc storage, optical disc storage (including compressed optical discs, laser discs, optical discs, digital universal optical discs, Blu-ray discs, etc.), magnetic disk storage media, or other magnetic storage devices, etc., without limitation.

[0093] It should be noted that the memory 840 can exist independently of the processor 810, or it can be integrated with the processor 810. The memory 840 can be used to store instructions, program code, or some data, etc. The memory 840 can be located inside or outside the electronic device 800, without restriction.

[0094] The processor 810 is configured to execute instructions stored in the memory 840 to implement the communication method provided in the following embodiments of this application. For example, when the electronic device 800 is a terminal or a chip in a terminal, the processor 810 can execute instructions stored in the memory 840 to implement the steps performed by the sending end in the following embodiments of this application.

[0095] As an optional implementation, the electronic device 800 also includes an output device 850 and an input device 860. The output device 850 can be a display screen, speaker, or other device capable of outputting data from the electronic device 800 to the user. The input device 860 can be a keyboard, mouse, microphone, joystick, or other device capable of inputting data into the electronic device 800.

[0096] It should be pointed out that, Figure 8 The structure shown does not constitute a limitation on the electronic device, except... Figure 8 In addition to the components shown, the electronic device may include more or fewer components than illustrated, or combine certain components, or have different component arrangements.

[0097] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this application. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart... Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0098] The above are merely embodiments of this application and are not intended to limit the scope of this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of the claims of this application.

Claims

1. A molten salt system, characterized in that, The molten salt system includes: a high-temperature molten salt tank, a high-temperature molten salt pump, a molten salt heat release system, a steam outlet valve for the molten salt heat release system, a deep peak shaving steam supply header, a steam inlet valve from the deep peak shaving steam supply header to the feedwater pump turbine, and the feedwater pump turbine. The outlet of the high-temperature molten salt tank is connected to the inlet of the high-temperature molten salt pump via a pipeline, and the outlet of the high-temperature molten salt pump is connected to the hot salt side inlet of the molten salt heat release system via a pipeline. The steam-side outlet of the molten salt exothermic system is connected to the inlet of the steam outlet valve of the molten salt exothermic system via a pipeline, and the outlet of the steam outlet valve of the molten salt exothermic system is connected to the inlet of the deep peak shaving steam supply header via a pipeline. The outlet of the deep peak shaving steam supply header is connected to the inlet of the steam inlet valve of the feedwater pump turbine via a pipeline, and the outlet of the deep peak shaving steam supply header to the steam inlet valve of the feedwater pump turbine is connected to the steam inlet of the feedwater pump turbine via a pipeline.

2. The molten salt system according to claim 1, characterized in that, The molten salt system also includes an intermediate pressure cylinder and a steam extraction valve from the fourth stage of the steam turbine to the feedwater pump turbine inlet valve. One end of the steam extraction valve from the fourth stage of the steam turbine to the feedwater pump turbine inlet valve is connected to the steam extraction port of the intermediate pressure cylinder through a pipeline, and the other end of the steam extraction valve from the fourth stage of the steam turbine to the feedwater pump turbine inlet valve is connected to the steam inlet of the feedwater pump turbine through a pipeline.

3. The molten salt system according to any one of claims 1-2, characterized in that, The molten salt system also includes a deep peak shaving steam supply header to the deaerator inlet valve. The inlet of the deep peak shaving steam supply header to the deaerator inlet valve is connected to the outlet of the deep peak shaving steam supply header via a pipeline, and the outlet of the deep peak shaving steam supply header to the deaerator inlet valve is connected to the inlet of the deaerator via a pipeline.

4. The molten salt system according to claim 3, characterized in that, The molten salt system also includes a drain valve before the steam inlet valve of the feedwater pump from the depth regulating valve steam supply manifold, a drain valve after the steam inlet valve of the feedwater pump from the depth regulating valve steam supply manifold, a drain valve before the steam inlet valve of the deaerator from the depth regulating valve steam supply manifold, and a drain valve after the steam inlet valve of the deaerator from the depth regulating valve steam supply manifold. The condensate drain valve from the deep peak shaving steam supply header to the feedwater pump inlet valve is installed on the pipeline between the outlet of the deep peak shaving steam supply header and the inlet of the feedwater pump turbine inlet valve, and is used to drain the condensate in the corresponding pipeline. The condensate drain valve from the deep peak shaving steam supply header to the feedwater pump inlet valve is installed on the pipeline between the outlet of the deep peak shaving steam supply header to the feedwater pump turbine inlet valve and the steam inlet of the feedwater pump turbine, and is used to drain the condensate in the corresponding pipeline. The steam trap from the deep peak shaving steam supply header to the deaerator inlet valve is installed on the pipeline between the outlet of the deep peak shaving steam supply header and the inlet of the deep peak shaving steam supply header to the deaerator inlet valve, and is used to drain the condensate in the corresponding pipeline; the steam trap from the deep peak shaving steam supply header to the deaerator inlet valve is installed on the pipeline between the outlet of the deep peak shaving steam supply header to the deaerator inlet valve and the inlet of the deaerator, and is used to drain the condensate in the corresponding pipeline.

5. The molten salt system according to claim 4, characterized in that, The molten salt system also includes a reheat extraction molten salt heat exchanger, a reheat extraction molten salt heat exchanger inlet valve, a reheat extraction pressure reducing valve, a main steam extraction molten salt heat exchanger, a main steam extraction molten salt heat exchanger inlet valve, and a main steam extraction pressure reducing valve. The outlet of the cold salt pump is connected to the molten salt side inlet of the reheat extraction steam molten salt heat exchanger and the molten salt side inlet of the main steam extraction steam molten salt heat exchanger via pipelines. The molten salt side outlet of the reheat extraction steam molten salt heat exchanger and the molten salt side outlet of the main steam extraction steam molten salt heat exchanger are both connected to the inlet of the high-temperature molten salt tank via pipelines. The reheat extraction steam molten salt heat exchanger inlet valve is connected in series in the pipeline between the cold salt pump and the molten salt side inlet of the reheat extraction steam molten salt heat exchanger, and the main steam extraction steam molten salt heat exchanger inlet valve is connected in series in the pipeline between the cold salt pump and the molten salt side inlet of the main steam extraction steam molten salt heat exchanger. The inlet of the reheat extraction steam pressure reducing valve is connected to the pipeline that supplies main steam from the boiler to the intermediate pressure cylinder via a pipeline, and the outlet is connected to the heat medium inlet of the reheat extraction steam molten salt heat exchanger via a pipeline. The heat medium outlet of the reheat extraction steam molten salt heat exchanger is connected to the conventional steam supply header via a pipeline. The inlet of the main steam extraction pressure reducing valve is connected to the pipeline that supplies main steam from the boiler to the high-pressure cylinder via a pipeline, and the outlet is connected to the heat medium inlet of the main steam extraction molten salt heat exchanger via a pipeline. The heat medium outlet of the main steam extraction molten salt heat exchanger is connected to the boiler and the high-pressure cylinder.

6. A deep peak-shaving method, characterized in that, The method is applied to the molten salt system as described in any one of claims 1-5, and the method includes: When the command to enter deep peak shaving mode is received, the high temperature molten salt pump is started, and the drain valves from the deep regulating valve steam supply manifold to the feedwater pump inlet valve and the drain valves from the deep regulating valve steam supply manifold to the feedwater pump inlet valve are opened. The rotational speed of the high-temperature molten salt pump is adjusted based on the molten salt flow rate output from the high-temperature molten salt tank and the steam pressure at the outlet of the molten salt exothermic system. Collect the outlet temperatures of the drain valves at the steam supply manifold from the depth regulating valve to the feedwater pump inlet valve and the outlet temperatures of the drain valves at the steam supply manifold from the depth regulating valve to the feedwater pump inlet valve. Adjust the opening of the drain valves at the steam supply manifold from the depth regulating valve to the feedwater pump inlet valve and the outlet temperatures of the drain valves at the steam supply manifold from the depth regulating valve to the feedwater pump inlet valve according to the real-time rate of change and the cumulative change of the drain temperature. After the drain temperature rises to a preset condition and remains stable for a preset time, close the drain valves at the steam supply manifold from the depth regulating valve to the feedwater pump inlet valve and the drain valves at the steam supply manifold from the depth regulating valve to the feedwater pump inlet valve. Based on the real-time speed of the feedwater pump turbine, the boiler feedwater flow rate, and the boiler feedwater temperature, determine the target steam pressure and target steam flow rate currently required by the feedwater pump turbine. Based on the target steam pressure, the target steam flow rate, and the actual steam pressure and actual steam flow rate at the outlet of the deep peak shaving steam supply header, the opening of the steam inlet valve from the deep peak shaving steam supply header to the feedwater pump turbine is adjusted to match the steam supply with the steam demand of the feedwater pump turbine.

7. The method according to claim 6, characterized in that, Adjusting the speed of the high-temperature molten salt pump based on the molten salt flow rate output from the high-temperature molten salt tank and the steam pressure at the outlet of the molten salt exothermic system includes: The real-time molten salt flow rate output from the high-temperature molten salt tank and the real-time steam pressure at the outlet of the molten salt exothermic system are collected to construct a flow-pressure time series feature matrix. The steady-state component and dynamic fluctuation component in the flow-pressure time series feature matrix are extracted by an adaptive filtering algorithm. The base speed adjustment is determined based on the steady-state components and the preset correlation between flow rate, pressure, and speed. Multi-scale wavelet decomposition is performed on the dynamic fluctuation components to obtain the fluctuation characteristics of different frequency bands. Based on the fluctuation characteristics and the preset fuzzy control rules, the compensation speed adjustment amount is determined. A dual closed-loop feedback regulation mechanism is constructed, with the target deviation of molten salt flow rate and the target deviation of steam pressure as the outer loop input parameters, and the superposition value of the basic speed regulation and the compensated speed regulation as the inner loop input parameter. The final speed regulation is determined by model predictive control logic.

8. The method according to claim 7, characterized in that, Adjusting the opening of the drain valves before and after the feedwater pump inlet valve from the depth regulating valve steam supply manifold to the depth regulating valve steam supply manifold based on the real-time rate of change and cumulative change of the drain temperature includes: Collect time-series data of condensate temperature from the steam supply manifold of the depth regulating valve to the steam inlet valve of the feedwater pump and from the outlet of the condensate valve of the steam supply manifold to the steam inlet valve of the feedwater pump. Extract the real-time change rate, temperature change acceleration, cumulative change and temperature fluctuation variance of condensate temperature through a dynamic sliding window to form a multi-dimensional feature vector. The multi-dimensional feature vector is fuzzily divided into multiple fuzzy subsets using a Gaussian membership function, and the membership degree of each feature to different fuzzy subsets is output. The trigger strength of each rule is calculated based on the preset fuzzy reasoning rule base and the membership degree of each feature to different fuzzy subsets. The output results of all triggering rules are then fused together. The fused output results are used to indicate the opening adjustment amount of the drain valve from the steam supply manifold to the feedwater pump inlet valve and the drain valve from the steam supply manifold to the feedwater pump inlet valve. The deviation between the target value and the actual value of the hydrophobic temperature and the rate of change of the deviation are taken as inputs. The deviation compensation amount is calculated by the PID controller. The deviation compensation amount is superimposed with the opening adjustment amount to obtain the final opening adjustment amount. The opening of the drain valve from the steam supply manifold to the feedwater pump inlet valve and the drain valve from the steam supply manifold to the feedwater pump inlet valve are adjusted according to the final opening adjustment amount.

9. The method according to claim 8, characterized in that, Based on the real-time speed of the feedwater pump turbine, the boiler feedwater flow rate, and the boiler feedwater temperature, determine the current required steam pressure and steam flow rate for the feedwater pump turbine, including: The real-time speed of the feedwater pump turbine, the boiler feedwater flow rate, and the boiler feedwater temperature are used as core input parameters, and the inlet feedwater pressure, outlet feedwater pressure, and ambient temperature of the feedwater pump turbine are used as auxiliary correction parameters to construct the correlation mapping relationship between the parameters. Based on the aforementioned correlation mapping relationship, according to the degree of influence of each parameter on steam demand, a primary weight is assigned to the core input parameter, and an auxiliary correction weight is assigned to the auxiliary correction parameter. The real-time values ​​of the core input parameters are associated with the corresponding sovereign weights, and the associated mapping relationship is substituted into the relationship. Combined with the design characteristic curve of the feedwater pump turbine, the preliminary values ​​of the steam pressure and steam flow rate required by the feedwater pump turbine are obtained. The real-time values ​​of the auxiliary correction parameters are associated with the corresponding auxiliary correction weights, and the associated mapping relationship is used to dynamically correct the initial values ​​of steam pressure and steam flow. The corrected steam pressure and steam flow values ​​are compared with the optimal steam parameters of the feedwater pump turbine under the same historical operating conditions. If the deviation exceeds the preset allowable range, the allocation ratio of the main weight and the auxiliary correction weight is readjusted through the correlation mapping relationship. The parameter correlation, calculation and correction process is repeated until the obtained steam pressure and steam flow rate meet the historical operating condition matching requirements, and are used as the target steam pressure and target steam flow rate.

10. An electronic device, characterized in that, The device includes at least one processor, at least one memory connected to the processor, and a bus; wherein the processor and the memory communicate with each other through the bus; the processor is used to call program instructions in the memory to execute the deep peaking method as described in any one of claims 6-9.

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