A control method and device for a super-supercritical unit heat supply system

Abstract

The present application relates to the technical field of heat supply control, and particularly relates to a control method and device of a super-supercritical unit heat supply system. The method comprises: obtaining a current heat supply demand load of a heat supply pipe network and a current heat supply load of a super-supercritical unit; determining a unit operation mode based on the current heat supply demand load and the current heat supply load; wherein the unit operation mode comprises a priority power generation mode, a priority heat supply mode and a heat and power balance mode; controlling the super-supercritical turbine high-pressure cylinder, the steam extraction valve group and the heat supply pipe network based on the unit operation mode; and after a preset time length, re-executing the step of obtaining the current heat supply load demand load and the current unit power generation load. In this way, the present application can improve the energy utilization rate of the super-supercritical unit heat supply system.

Description

Technical Field

[0001] This invention relates to the field of heating control technology, and in particular to a control method and device for an ultra-supercritical unit heating system. Background Technology

[0002] Ultra-supercritical units have advantages such as high thermal efficiency, low energy consumption, and good environmental performance, and have been widely used in power generation. With the adjustment of energy structure and the increase in demand for centralized heating, ultra-supercritical units are gradually developing towards combined heat and power (CHP), which can meet both power supply needs and provide centralized heating services.

[0003] However, existing ultra-supercritical heating systems generally face difficulties in coordinating heat and power loads during operation. When heating demand conflicts with power generation demand, traditional control systems often adopt fixed operating strategies and cannot dynamically adjust according to actual conditions, resulting in low energy utilization efficiency. Either heating demand is met at the expense of power generation efficiency, or power generation efficiency is guaranteed but heating requirements cannot be met.

[0004] Based on this, the present invention proposes a control method and device for an ultra-supercritical unit heating system to solve the above-mentioned technical problems. Summary of the Invention

[0005] This invention describes a control method and apparatus for an ultra-supercritical unit heating system, which can improve the energy utilization rate of the ultra-supercritical unit heating system.

[0006] According to a first aspect, the present invention provides a control method for a heating system of an ultra-supercritical unit. The method is applied to a controller of the ultra-supercritical unit heating system. The system includes the controller and, in sequence, an ultra-supercritical boiler, an ultra-supercritical steam turbine high-pressure cylinder, an extraction valve group, a surface heat exchanger, and a heating network. The controller is connected to the ultra-supercritical boiler, the steam turbine high-pressure cylinder, the extraction valve group, the surface heat exchanger, and the heating network, respectively. The method includes: Obtain the current heating demand load of the heating network and the current heating load of the ultra-supercritical unit; Based on the current heating demand load and the current heating load, determine the unit operation mode; The unit operation modes include priority power generation mode, priority heating mode, and heat and power balance mode; The high-pressure cylinder of the ultra-supercritical steam turbine, the extraction valve group, and the heating network are controlled based on the unit operation mode. After a preset time, the process of "obtaining the current heating load demand and current generator load of the heating network" will be repeated.

[0007] According to a second aspect, the present invention provides a control device for a heating system of an ultra-supercritical unit. The device is applied to a controller of the ultra-supercritical unit heating system. The system includes the controller and, in sequence, an ultra-supercritical boiler, an ultra-supercritical steam turbine high-pressure cylinder, an extraction valve group, a surface heat exchanger, and a heating network. The controller is connected to the ultra-supercritical boiler, the steam turbine high-pressure cylinder, the extraction valve group, the surface heat exchanger, and the heating network, respectively. The device includes: The acquisition unit is configured to acquire the current heating demand load of the heating network and the current heating load of the ultra-supercritical unit; The first data processing unit is configured to determine the unit operation mode based on the current heating demand load and the current heating load; The unit operation modes include priority power generation mode, priority heating mode, and heat and power balance mode; The second data processing unit is configured to control the high-pressure cylinder of the ultra-supercritical steam turbine, the extraction valve group, and the heating network based on the unit's operating mode. The third data processing unit is configured to re-execute "obtain the current heating load demand and current generator load of the heating network" after a preset time.

[0008] Thirdly, embodiments of this specification also provide an electronic device, including a memory and a processor, wherein the memory stores a computer program, and when the processor executes the computer program, it implements the method described in any embodiment of this specification.

[0009] Fourthly, embodiments of this specification also provide a control system for an ultra-supercritical unit heating system. The system includes a controller and an ultra-supercritical boiler, an ultra-supercritical turbine high-pressure cylinder, an extraction valve group, a surface heat exchanger, and a heating network connected in sequence. The controller is connected to the ultra-supercritical boiler, the turbine high-pressure cylinder, the extraction valve group, the surface heat exchanger, and the heating network, respectively. The controller is used to execute the methods described in any embodiment of this specification.

[0010] According to the control method and apparatus for an ultra-supercritical unit heating system provided by the present invention, the present invention collects the current heating demand load of the heating network (such as real-time heat consumption at the user end and heat loss of the network) and the current heating load of the ultra-supercritical unit (such as steam extraction heat from the turbine and heat exchanger heat exchange) through sensing devices and real-time monitoring devices of the unit installed at preset nodes of the heating network. Based on the current heating demand load and the current heating load, the unit operating mode is determined, wherein the unit operating mode includes priority power generation mode, priority heating mode, and heat and power balance mode; for different operating modes, different control logics are implemented on the high-pressure cylinder of the ultra-supercritical turbine, the extraction valve group, and the heating network to achieve dynamic balance of heat and power output. This effectively improves the energy utilization efficiency of the ultra-supercritical unit heating system. A preset time period (the preset time period is dynamically adjusted according to the fluctuation of operating conditions, usually 3-10 minutes) is set to re-collect load data in each cycle, reducing losses in the energy conversion process, thereby improving the energy utilization efficiency of the ultra-supercritical unit heating system. Attached Figure Description

[0011] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0012] Figure 1 A schematic flowchart of a control method for an ultra-supercritical unit heating system according to one embodiment is shown. Figure 2 A schematic block diagram of a control device for an ultra-supercritical unit heating system according to one embodiment is shown. Figure 3 A schematic block diagram of the control system of an ultra-supercritical unit heating system according to one embodiment is shown. Detailed Implementation

[0013] The solution provided by the present invention will now be described with reference to the accompanying drawings.

[0014] Figure 1 A flowchart illustrating a control method for an ultra-supercritical unit heating system according to one embodiment is shown. It is understood that this method can be executed by any device, equipment, platform, or cluster of devices with computing and processing capabilities. The control method for an ultra-supercritical unit heating system is applied to a controller of the system. The system includes a controller and, in sequence, an ultra-supercritical boiler, an ultra-supercritical turbine high-pressure cylinder, an extraction valve group, a surface heat exchanger, and a heating network. The controller is connected to the ultra-supercritical boiler, the turbine high-pressure cylinder, the extraction valve group, the surface heat exchanger, and the heating network, respectively. Figure 1 As shown, the method includes: Step 100: Obtain the current heating demand load of the heating network and the current heating load of the ultra-supercritical unit; Step 102: Determine the unit operation mode based on the current heating demand load and the current heating load; wherein, the unit operation mode includes priority power generation mode, priority heating mode and heat and power balance mode; Step 104: Control the high-pressure cylinder, extraction valve group, and heating network of the ultra-supercritical steam turbine based on the unit operation mode; Step 106: After a preset time, re-execute "Get the current heating load demand and current generator load of the heating network".

[0015] In this embodiment, the present invention collects the current heating demand load of the heating network (such as real-time heat consumption at the user end and heat loss in the network) and the current heating load of the ultra-supercritical unit (such as steam extraction heat from the turbine and heat exchanger heat exchange) through sensing devices and real-time monitoring devices installed at preset nodes in the heating network. Based on the current heating demand load and the current heating load, the unit operation mode is determined, which includes priority power generation mode, priority heating mode, and heat and power balance mode. For different operation modes, different control logics are implemented on the high-pressure cylinder of the ultra-supercritical turbine, the extraction valve group, and the heating network to achieve dynamic balance of heat and power output. This effectively improves the energy utilization efficiency of the ultra-supercritical unit heating system. A preset time period (the preset time period is dynamically adjusted according to the fluctuation of operating conditions, usually 3-10 minutes) is set to re-collect load data in each cycle, reducing losses in the energy conversion process, thereby improving the energy utilization efficiency of the ultra-supercritical unit heating system.

[0016] In one embodiment of the present invention, the unit operating mode is determined based on the heating load demand and the current unit power generation load, including: When the current heating demand load is greater than the current generating load of the unit, the unit is determined to operate in the priority generating mode. When the current heating demand load is less than the current generating load of the unit, the unit is determined to operate in the priority heating mode. When the current heating demand load equals the current generating load of the unit, the unit is determined to be in heat and power balance mode.

[0017] In this embodiment, when the current heating demand load is greater than the current generating load of the unit, it is determined to be in priority generating mode, in which priority is given to ensuring the stability and efficiency of power; when the current heating demand load is less than the current generating load of the unit, it switches to priority heating mode, in which priority is given to ensuring the utilization rate of steam extraction and maximizing heat output to match the heating demand; and when the current heating demand load is equal to the current generating load of the unit, the heat and power balance mode is triggered to achieve a reasonable configuration of energy conversion efficiency.

[0018] In one embodiment of the present invention, the control of the high-pressure cylinder, extraction valve group, and heating network of the ultra-supercritical steam turbine based on the unit operation mode includes: When the unit is operating in priority power generation mode, the main steam pressure fluctuation rate, the actual main steam pressure, and the actual main steam temperature of the unit are obtained. Based on the main steam pressure fluctuation rate and the actual main steam pressure, determine the first target opening degree of the extraction steam valve, and control the extraction steam valve group according to the first target opening degree; Based on the actual temperature and pressure of the main steam, the target steam intake of the first high-pressure cylinder is determined, and the high-pressure cylinder of the ultra-supercritical steam turbine is controlled according to the target steam intake of the first high-pressure cylinder.

[0019] In this embodiment, the main steam pressure fluctuation rate, actual main steam pressure (a fundamental parameter for measuring energy output level), and actual main steam temperature are collected in real time. For the extraction valve group control, the first target opening degree is determined based on the main steam pressure fluctuation rate and actual pressure. Simultaneously, for the control of the ultra-supercritical turbine high-pressure cylinder, the target steam intake for the first high-pressure cylinder is determined by combining the actual main steam temperature and actual main steam pressure, ensuring that the high-pressure cylinder always operates within its optimal efficiency range. This maximizes energy conversion efficiency in the priority power generation mode while ensuring the safety and stability of the unit operation.

[0020] In one embodiment of the present invention, the first target opening degree and the first high-pressure cylinder target steam intake amount are determined by the following formula:

[0021] In the formula, The first target opening degree, This is the rated opening of the extraction valve. This is the dynamic pressure correction factor. The actual pressure of the main steam. Main steam rated pressure, The preset lower limit for main steam. The main steam pressure fluctuation rate This is the fluctuation rate correction factor. This is the power loss compensation coefficient. The power loss is due to steam extraction. For rated power generation load, The target steam intake for the first high-pressure cylinder. For the rated steam intake, This represents the current generating load of the unit. This is a nonlinear compensation term for extraction steam power loss. The rated generating load of the unit, This is the pressure influence coefficient. This is the temperature influence coefficient. The actual temperature of the main steam. The rated temperature of the main steam.

[0022] In one embodiment of the present invention, the dynamic pressure correction coefficient is determined by the following formula:

[0023] In this embodiment, the calculation formula for the first target opening degree adopts a "dynamic pressure correction coefficient" to solve the problem of poor adaptability of traditional fixed coefficients. Traditional formulas often use a single pressure correction coefficient, which cannot cope with the nonlinear characteristics of the main steam pressure in different ranges (low, stable, high). For example, when the pressure is close to the lower limit (e.g., 25 MPa), the fixed coefficient is prone to insufficient opening degree adjustment, which will still cause the main steam pressure to drop further; when the pressure is too high, it will excessively restrict the opening degree, resulting in energy waste. This formula uses a segmented design of dynamic pressure correction coefficient. When the pressure is below 26 MPa, a high coefficient of 0.6 is used to limit the opening degree to avoid the pressure from continuing to drop; in the stable range of 26-29 MPa, a conventional coefficient of 0.4 is used to balance control accuracy and flexibility; and when the pressure is above 29 MPa, a low coefficient of 0.2 is used to relax the restriction, making full use of redundant pressure, so that the correction degree is dynamically matched with the pressure condition, thus improving the adjustment adaptability of different pressure ranges.

[0024] In one embodiment of the present invention, the control of the high-pressure cylinder, extraction valve group, and heating network of the ultra-supercritical steam turbine based on the unit operation mode includes: When the unit is operating in priority heating mode, the return water temperature, main steam pressure, current power generation load, actual extraction steam pressure, high-pressure cylinder exhaust steam pressure, and current power generation load are obtained. Based on the return water temperature and the actual extraction steam pressure, determine the second target opening degree of the extraction steam valve, and control the extraction steam valve group according to the second target opening degree. Based on the actual exhaust pressure of the high-pressure cylinder and the current power generation load, the target steam intake of the second high-pressure cylinder is determined, and the high-pressure cylinder of the ultra-supercritical steam turbine is controlled according to the target steam intake of the second high-pressure cylinder.

[0025] In this embodiment, when the unit operates in the priority heating mode, the return water temperature, main steam pressure, current power generation load, actual extraction steam pressure, high-pressure cylinder exhaust pressure, and current power generation load are acquired. Regarding the extraction steam valve group control, a second target opening degree is determined based on the return water temperature and actual extraction steam pressure. The extraction steam valve group is then controlled according to this second target opening degree to ensure that the extraction steam flow matches the heating load, while avoiding hydraulic imbalance in the pipeline network caused by fluctuations in extraction steam pressure. Regarding the control of the ultra-supercritical turbine high-pressure cylinder, a second target steam inlet flow rate is determined based on the actual high-pressure cylinder exhaust pressure and current power generation load. The ultra-supercritical turbine high-pressure cylinder is then controlled according to this second target steam inlet flow rate.

[0026] In this embodiment, the calculation formula for the target steam intake of the first high-pressure cylinder solves the problem of inaccurate traditional fixed-coefficient compensation. Traditional formulas often use fixed coefficients (such as 0.05) to calculate the power loss of power generation due to steam extraction, without considering the impact of steam extraction pressure fluctuations. When the steam extraction pressure is lower than the rated value (e.g., dropping from 4.0 MPa to 3.0 MPa), the fixed coefficient leads to an artificially high compensation amount, resulting in an excessively large steam intake. This new formula avoids fluctuations in the main steam parameters (temperature and pressure) caused by an artificially high steam intake.

[0027] In one embodiment of the present invention, the second target opening degree and the second high-pressure cylinder target steam intake amount are determined by the following formula:

[0028] In the formula, For the second target opening, This is the rated opening of the extraction valve. This represents the actual heating load. Set the return water temperature for the pipe network. This is the actual return water temperature. For the rated heating load, This is the compensation coefficient for the rate of change of heat load. For dynamic return water temperature coefficient, The rate of change of heating load. This is the actual extraction steam pressure. This is the optimal value for extraction steam pressure. As a fuzzy factor, The target steam intake for the second high-pressure cylinder. For the rated steam intake, For the current power generation load, The power loss is due to steam extraction. For rated power generation load, For heating load, This is the actual exhaust pressure of the high-pressure cylinder. This is the optimal exhaust pressure for the high-pressure cylinder.

[0029] In this embodiment, the calculation formula for the second target opening degree combines the current heating demand load and the dynamic coefficient of return water temperature deviation with the heating load change rate. The lower the return water temperature and the faster the load increases, the stronger the adjustment force, which can adapt to the actual heating demand of the pipe network in real time and avoid the inaccuracy of heating caused by a single parameter.

[0030] In this embodiment, the calculation formula for the target steam intake of the second high-pressure cylinder innovatively introduces "heating load trend prediction". Traditional control requires waiting for the actual increase in heating load before passively adjusting the steam intake, which is prone to insufficient steam extraction or a sudden drop in power generation load due to response delay. This formula determines the load growth trend in advance by integrating the rate of change of heating load in the first 3 minutes. For example, when the load continues to rise at 1.5 MW / min, the integral term will calculate the power that needs to be supplemented in advance and increase the steam intake synchronously, preparing before the load fully climbs and avoiding heating gaps or fluctuations in power generation parameters.

[0031] In one embodiment of the present invention, the control of the high-pressure cylinder, extraction valve group, and heating network of the ultra-supercritical steam turbine based on the unit operation mode includes: When the unit is operating in heat and power balance mode, the actual circulating water flow of the heating network is obtained. Determine the corrected speed of the circulating pump in the heating network based on the actual circulating water flow rate; The circulating pumps in the heating network are controlled based on the speed correction of the circulating pump.

[0032] In this embodiment, when the unit is in heat and electricity balance mode, the actual circulating water flow rate of the heating network is first collected in real time by a flow meter installed on the main pipeline. The actual circulating water flow rate is used to characterize the matching status between the network's heat delivery capacity and the user's heat demand. Based on the actual circulating water flow rate, the corrected speed of the heating network circulating pump is determined. Finally, based on the calculated corrected speed of the circulating pump, a control command is sent to the circulating pump frequency converter to dynamically adjust the pump's operating speed. This minimizes energy loss in the energy delivery process while maintaining a balance between heat and electricity output.

[0033] In one embodiment of the present invention, the corrected rotational speed of the circulating pump is determined by the following formula:

[0034] In the formula, Correcting the speed of the circulating pump This is the rated speed of the circulating pump. This represents the actual circulating water flow rate. For the rated circulating flow rate, This represents the actual supply and return water temperature difference. To design the temperature difference.

[0035] The foregoing has described specific embodiments of the invention. Other embodiments are within the scope of the appended claims. In some cases, the actions or steps described in the claims may be performed in a different order than that shown in the embodiments and may still achieve the desired results. Furthermore, the processes depicted in the drawings do not necessarily require the specific or sequential order shown to achieve the desired results. In some embodiments, multitasking and parallel processing are also possible or may be advantageous.

[0036] According to another embodiment, the present invention provides a control device for an ultra-supercritical unit heating system. Figure 2 A schematic block diagram of a control device for an ultra-supercritical unit heating system according to one embodiment is shown. It is understood that this device can be implemented by any device, equipment, platform, or cluster of devices with computing and processing capabilities. The device is applied to a controller for an ultra-supercritical unit heating system, the system including the controller and, in sequence, an ultra-supercritical boiler, an ultra-supercritical turbine high-pressure cylinder, an extraction valve assembly, a surface heat exchanger, and a heating network. The controller is connected to the ultra-supercritical boiler, the turbine high-pressure cylinder, the extraction valve assembly, the surface heat exchanger, and the heating network, respectively. Figure 2 As shown, the device includes: an acquisition unit 200, a first data processing unit 202, a second data processing unit 204, and a third data processing unit 206. The main functions of each component are as follows: The acquisition unit 200 is configured to acquire the current heating demand load of the heating network and the current heating load of the ultra-supercritical unit; The first data processing unit 202 is configured to determine the unit operation mode based on the current heating demand load and the current heating load; The unit operation modes include priority power generation mode, priority heating mode, and heat and power balance mode; The second data processing unit 204 is configured to control the high-pressure cylinder of the ultra-supercritical steam turbine, the extraction valve group, and the heating network based on the unit's operating mode. The third data processing unit 206 is configured to re-execute "obtain the current heating load demand and current generator load of the heating network" after a preset time.

[0037] In one embodiment of the present invention, the first data processing unit 202 is configured to perform the following operations: When the current heating demand load is greater than the current unit power generation load, the unit operation mode is determined to be the priority power generation mode; When the current heating demand load is less than the current generating load of the unit, the unit operation mode is determined to be the priority heating mode; When the current heating demand load is equal to the current generating unit load, the unit operation mode is determined to be the heat and power balance mode.

[0038] In one embodiment of the present invention, the second data processing unit 204 is configured to perform the following operations: When the unit is operating in the priority power generation mode, the main steam pressure fluctuation rate, the actual main steam pressure, and the actual main steam temperature of the unit are obtained. Based on the main steam pressure fluctuation rate and the actual main steam pressure, the first target opening degree of the extraction valve is determined, and the extraction valve group is controlled according to the first target opening degree. Based on the actual temperature and pressure of the main steam, the target steam intake of the first high-pressure cylinder is determined, and the high-pressure cylinder of the ultra-supercritical steam turbine is controlled according to the target steam intake of the first high-pressure cylinder.

[0039] In one embodiment of the present invention, the first target opening degree and the first high-pressure cylinder target steam intake amount are determined by the following formula:

[0040] In the formula, Let the first target opening be... This is the rated opening of the extraction valve. This is the dynamic pressure correction factor. The actual pressure of the main steam. The rated pressure of the main steam. The preset lower limit for main steam. The main steam pressure fluctuation rate is... This is the fluctuation rate correction factor. This is the power loss compensation coefficient. The power loss is due to steam extraction. For rated power generation load, The target steam intake volume for the first high-pressure cylinder. For the rated steam intake, This represents the current generating load of the unit. This is a nonlinear compensation term for extraction steam power loss. The rated generating load of the unit, This is the pressure influence coefficient. This is the temperature influence coefficient. The actual temperature of the main steam. The rated temperature of the main steam.

[0041] In one embodiment of the present invention, the second data processing unit 204 is configured to perform the following operations: When the unit is operating in the priority heating mode, the return water temperature, main steam pressure, current power generation load, actual extraction steam pressure, high-pressure cylinder exhaust steam pressure, and current power generation load of the unit are obtained. Based on the return water temperature and the actual extraction steam pressure, determine the second target opening degree of the extraction steam valve, and control the extraction steam valve group according to the second target opening degree; Based on the actual exhaust pressure of the high-pressure cylinder and the current power generation load, the target steam intake of the second high-pressure cylinder is determined, and the high-pressure cylinder of the ultra-supercritical steam turbine is controlled according to the target steam intake of the second high-pressure cylinder.

[0042] In one embodiment of the present invention, the second target opening degree and the second high-pressure cylinder target steam intake amount are determined by the following formula:

[0043] In the formula, For the second target opening, This is the rated opening of the extraction valve. This represents the actual heating load. Set the return water temperature for the pipe network. This is the actual return water temperature. For the rated heating load, This is the compensation coefficient for the rate of change of heat load. For dynamic return water temperature coefficient, The rate of change of heating load. The actual extraction steam pressure is [value missing]. This is the optimal value for extraction steam pressure. As a fuzzy factor, This represents the target steam intake volume for the second high-pressure cylinder. For the rated steam intake, For the current power generation load, The power loss is due to steam extraction. For rated power generation load, For heating load, This refers to the actual exhaust pressure of the high-pressure cylinder. This is the optimal exhaust pressure for the high-pressure cylinder.

[0044] In one embodiment of the present invention, the second data processing unit 204 is configured to perform the following operations: When the unit is operating in the heat and power balance mode, the actual circulating water flow rate of the heating network is obtained. Based on the actual circulating water flow rate, the corrected rotation speed of the heating network circulating pump is determined; The circulating pumps of the heating network are controlled based on the corrected rotation speed of the circulating pump.

[0045] According to another embodiment, Figure 3 A schematic block diagram of a control system for an ultra-supercritical unit heating system according to one embodiment is shown. The system includes a controller and, in sequence, an ultra-supercritical boiler, an ultra-supercritical turbine high-pressure cylinder, an extraction valve assembly, a surface heat exchanger, and a heating network. The controller is connected to the ultra-supercritical boiler, the turbine high-pressure cylinder, the extraction valve assembly, the surface heat exchanger, and the heating network, respectively. When executing the executable code, the controller causes the computer to execute a combination of... Figure 1 The method described.

[0046] According to another embodiment, an electronic device is also provided, including a memory and a processor, wherein the memory stores executable code, and when the processor executes the executable code, it implements a combination... Figure 1 The method described.

[0047] The various embodiments in this invention are described in a progressive manner. Similar or identical parts between embodiments can be referred to mutually. Each embodiment focuses on describing the differences from other embodiments. In particular, the apparatus embodiments are basically similar to the method embodiments, so the description is relatively simple; relevant parts can be referred to the descriptions of the method embodiments.

[0048] Those skilled in the art will recognize that, in one or more of the examples above, the functions described in this invention can be implemented using hardware, software, firmware, or any combination thereof. When implemented in software, these functions can be stored in a computer-readable medium or transmitted as one or more instructions or code on a computer-readable medium.

[0049] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of the present invention. It should be understood that the above description is only a specific embodiment of the present invention and is not intended to limit the scope of protection of the present invention. Any modifications, equivalent substitutions, improvements, etc., made on the basis of the technical solution of the present invention should be included within the scope of protection of the present invention.

Claims

1. A control method for a heating system of an ultra-supercritical unit, characterized in that, The method is applied to a controller of a heating system for an ultra-supercritical unit. The system includes the controller and, in sequence, an ultra-supercritical boiler, an ultra-supercritical turbine high-pressure cylinder, an extraction valve group, a surface heat exchanger, and a heating network. The controller is connected to the ultra-supercritical boiler, the turbine high-pressure cylinder, the extraction valve group, the surface heat exchanger, and the heating network, respectively. The method includes: Obtain the current heating demand load of the heating network and the current heating load of the ultra-supercritical unit; Based on the current heating demand load and the current heating load, determine the unit operation mode; The unit operation modes include priority power generation mode, priority heating mode, and heat and power balance mode; The high-pressure cylinder of the ultra-supercritical steam turbine, the extraction valve group, and the heating network are controlled based on the unit operation mode. After the preset time, the process of "obtaining the current heating load demand and current generator load of the heating network" will be executed again. The process of determining the unit operating mode based on the heating load demand and the current unit power generation load includes: When the current heating demand load is greater than the current unit power generation load, the unit operation mode is determined to be the priority power generation mode; When the current heating demand load is less than the current generating load of the unit, the unit operation mode is determined to be the priority heating mode; When the current heating demand load is equal to the current unit power generation load, the unit operation mode is determined to be the heat and power balance mode; The control of the ultra-supercritical steam turbine high-pressure cylinder, the extraction valve group, and the heating network based on the unit operation mode includes: When the unit is operating in the priority power generation mode, the main steam pressure fluctuation rate, the actual main steam pressure, and the actual main steam temperature of the unit are obtained. Based on the main steam pressure fluctuation rate and the actual main steam pressure, the first target opening degree of the extraction valve is determined, and the extraction valve group is controlled according to the first target opening degree. Based on the actual temperature and pressure of the main steam, the target steam intake of the first high-pressure cylinder is determined, and the high-pressure cylinder of the ultra-supercritical steam turbine is controlled according to the target steam intake of the first high-pressure cylinder. The first target opening degree and the first target steam intake amount of the high-pressure cylinder are determined by the following formula: In the formula, Let the first target opening be... This is the rated opening of the extraction valve. This is the dynamic pressure correction factor. The actual pressure of the main steam. Main steam rated pressure, The preset lower limit for main steam. The main steam pressure fluctuation rate is... This is the fluctuation rate correction factor. This is the power loss compensation coefficient. The power loss is due to steam extraction. For rated power generation load, The target steam intake volume for the first high-pressure cylinder. For the rated steam intake, This represents the current generating load of the unit. This is a nonlinear compensation term for extraction steam power loss. The rated generating load of the unit, This is the pressure influence coefficient. This is the temperature influence coefficient. The actual temperature of the main steam. The rated temperature of the main steam.

2. The method according to claim 1, characterized in that, The control of the ultra-supercritical steam turbine high-pressure cylinder, the extraction valve group, and the heating network based on the unit operation mode includes: When the unit is operating in the priority heating mode, the return water temperature, main steam pressure, current power generation load, actual extraction steam pressure, high-pressure cylinder exhaust steam pressure, and current power generation load of the unit are obtained. Based on the return water temperature and the actual extraction steam pressure, determine the second target opening degree of the extraction steam valve, and control the extraction steam valve group according to the second target opening degree; Based on the actual exhaust pressure of the high-pressure cylinder and the current power generation load, the target steam intake of the second high-pressure cylinder is determined, and the high-pressure cylinder of the ultra-supercritical steam turbine is controlled according to the target steam intake of the second high-pressure cylinder.

3. The method according to claim 2, characterized in that, The second target opening degree and the second target steam intake amount of the high-pressure cylinder are determined by the following formula: In the formula, For the second target opening, This is the rated opening of the extraction valve. This represents the actual heating load. Set the return water temperature for the pipe network. This is the actual return water temperature. For the rated heating load, This is the compensation coefficient for the rate of change of heat load. For dynamic return water temperature coefficient, The rate of change of heating load. The actual extraction steam pressure is [value missing]. This is the optimal value for extraction steam pressure. As a fuzzy factor, This represents the target steam intake volume for the second high-pressure cylinder. For the rated steam intake, For the current power generation load, The power loss is due to steam extraction. For rated power generation load, For heating load, This refers to the actual exhaust pressure of the high-pressure cylinder. This is the optimal exhaust pressure for the high-pressure cylinder.

4. The method according to claim 3, characterized in that, The control of the ultra-supercritical steam turbine high-pressure cylinder, the extraction valve group, and the heating network based on the unit operation mode includes: When the unit is operating in the heat and power balance mode, the actual circulating water flow rate of the heating network is obtained. Based on the actual circulating water flow rate, the corrected rotation speed of the heating network circulating pump is determined; The circulating pumps of the heating network are controlled based on the corrected rotation speed of the circulating pump.

5. A control device for a heating system of an ultra-supercritical unit, characterized in that, For performing the method as described in any one of claims 1-4, the apparatus is applied to a controller of an ultra-supercritical unit heating system, the system comprising the controller and, in sequence, an ultra-supercritical boiler, an ultra-supercritical turbine high-pressure cylinder, an extraction valve group, a surface heat exchanger, and a heating network, the controller being connected to the ultra-supercritical boiler, the turbine high-pressure cylinder, the extraction valve group, the surface heat exchanger, and the heating network, respectively, the apparatus comprising: The acquisition unit is configured to acquire the current heating demand load of the heating network and the current heating load of the ultra-supercritical unit; The first data processing unit is configured to determine the unit operation mode based on the current heating demand load and the current heating load; The unit operation modes include priority power generation mode, priority heating mode, and heat and power balance mode; The second data processing unit is configured to control the high-pressure cylinder of the ultra-supercritical steam turbine, the extraction valve group, and the heating network based on the unit's operating mode. The third data processing unit is configured to re-execute "obtain the current heating load demand and current generator load of the heating network" after a preset time.

6. An electronic device, characterized in that, It includes a memory and a processor, wherein the memory stores a computer program, and the processor executes the computer program to implement the method as described in any one of claims 1-4.

7. A heating system for an ultra-supercritical unit, characterized in that, The system includes a controller and a supercritical boiler, a supercritical steam turbine high-pressure cylinder, an extraction valve group, a surface heat exchanger, and a heating network connected in sequence. The controller is connected to the supercritical boiler, the steam turbine high-pressure cylinder, the extraction valve group, the surface heat exchanger, and the heating network, respectively. The controller is used to perform the method as described in any one of claims 1-4.

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