A method and system for correcting main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit

Abstract

The present disclosure provides a method and system for correcting the main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit, comprising: determining the power, main steam flow and main steam pressure values ​​at each preselected non-rated operating point based on the relationship between the main steam pressure and the main steam flow and the main steam flow and the power; adjusting the corresponding main steam pressure value for each preselected non-rated operating point according to a preset arithmetic progression, and obtaining a series of new unit heat rates according to a steam turbine variable operating condition calculation method; fitting the relationship between the unit heat rate and the main steam pressure based on the arithmetic progression of the main steam pressure values ​​corresponding to each preselected non-rated operating point and the corresponding unit heat rate; obtaining the high-pressure valve rear pressure corresponding to each non-rated operating point under actual measurement conditions, and obtaining the corrected main steam pressure in combination with the inlet steam pressure loss of the high-pressure steam inlet valve group under rated conditions, and at the same time, obtaining the unit heat rate corresponding to the corrected main steam pressure based on the relationship between the unit heat rate and the main steam pressure.

Description

Technical Field

[0001] The present disclosure belongs to the technical field of steam turbine thermal calculation, and in particular relates to a method and system for correcting main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit. Background Art

[0002] The statements in this section merely provide background information related to the present disclosure and do not necessarily constitute prior art.

[0003] The full-circle steam inlet unit is designed with only two high-pressure control valves, which are designed to remain fully open at any load. This results in low control valve pressure loss, high high-pressure cylinder efficiency, and low energy consumption. However, the inventors discovered that in actual applications, in order to meet the primary frequency regulation requirements of the power grid, the control valves of the full-circle steam inlet unit must maintain a certain opening at any load. This results in a large actual pressure loss for the full-circle steam inlet unit. Moreover, as the unit load decreases, the high-pressure control valve opening also decreases, resulting in greater control valve pressure loss. This control valve pressure loss leads to low high-pressure cylinder efficiency and high energy consumption. Current steam turbine parameter correction methods, including GB / T 8117 and ASME PTC6, are based on the original throttling regulation steam inlet group, that is, control valve adjustment. In these methods, the main steam pressure is not corrected under non-rated operating conditions. However, the design concept of full-circle steam inlet units is different from that of traditional throttling regulation steam inlet units. These methods are obviously no longer applicable to current full-circle steam inlet units. Summary of the Invention

[0004] In order to solve the above-mentioned problems, the present disclosure provides a method and system for correcting the main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit. In the performance test of the full-cycle steam inlet unit under non-rated operating conditions, the scheme can still obtain the main steam pressure corrected to the condition where the high-speed control valve is fully opened, and then, based on the equation of main steam pressure and heat consumption, the heat consumption of the unit under non-rated operating conditions can be obtained after the main steam pressure is corrected.

[0005] According to a first aspect of an embodiment of the present disclosure, a method for correcting main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit is provided, comprising:

[0006] Based on the relationship between main steam pressure and main steam flow and between main steam flow and power, determine the power, main steam flow and main steam pressure values ​​at each preselected non-rated operating point;

[0007] For each preselected non-rated operating point, the corresponding main steam pressure value is adjusted according to the preset arithmetic progression, and a series of new unit heat rates are obtained based on the calculation method of the turbine variable operating condition;

[0008] Based on the arithmetic progression of main steam pressure values ​​corresponding to each preselected non-rated operating point and the corresponding unit heat rate, the relationship between unit heat rate and main steam pressure is obtained by fitting;

[0009] The pressure behind the high-pressure regulating valve corresponding to each non-rated operating point under the actual measured conditions is obtained, and combined with the steam inlet pressure loss of the high-pressure steam inlet valve group under the rated operating conditions, the corrected main steam pressure is obtained. At the same time, based on the relationship between the unit heat rate and the main steam pressure, the unit heat rate corresponding to the corrected main steam pressure is obtained.

[0010] Furthermore, the obtained high-pressure regulating valve rear pressure corresponding to each non-rated operating point under the measured conditions is combined with the high-pressure steam inlet valve group inlet steam pressure loss under the rated operating conditions to obtain the corrected main steam pressure, specifically using the following formula:

[0011]

[0012] in, is the pressure behind the high-pressure door measured under various non-rated working conditions, Design pressure loss for the high-pressure steam inlet valve group, To correct the main steam pressure to the fully open throttle valve.

[0013] Furthermore, the relationship between the heat consumption of the unit and the main steam pressure is specifically expressed as follows:

[0014]

[0015] in, is the heat consumption of the new unit; is the new main steam pressure; 、 、 is a constant.

[0016] Furthermore, the relationship between the main steam pressure and the main steam flow, and between the main steam flow and the power is obtained by, specifically: based on the main steam pressure-main steam flow curve and the main steam flow-power curve provided by the full-cycle steam inlet unit design data, by determining the data of several known points on the curve, constructing the relationship equations between the main steam pressure and the main steam flow, and between the main steam flow and the power.

[0017] Furthermore, the method of obtaining the high-pressure regulating valve rear pressure corresponding to each non-rated operating point under actual measured conditions is specifically: conducting a thermal performance test on the unit, and using a pre-selected non-rated operating point as the test operating point to obtain the high-pressure regulating valve rear pressure under actual measured conditions.

[0018] Furthermore, the steam inlet pressure loss of the high-pressure steam inlet valve group under the rated working conditions is specifically expressed as:

[0019]

[0020] in, The main steam valve forward steam pressure, that is, the main steam pressure, For high-profile door pressure, Design the pressure drop for the high-pressure steam inlet valve group.

[0021] Furthermore, the preselected non-rated operating point is obtained as a percentage of the rated operating point THA condition.

[0022] According to a second aspect of an embodiment of the present disclosure, a main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions is provided, comprising:

[0023] a data acquisition unit for determining the power, main steam flow, and main steam pressure values ​​at each preselected non-rated operating point based on the relationship between the main steam pressure and the main steam flow, and between the main steam flow and the power;

[0024] A fitting data set construction unit is used to adjust the corresponding main steam pressure value for each preselected non-rated operating point according to a preset arithmetic progression, and obtain a series of new unit heat rates based on the turbine variable operating condition calculation method;

[0025] A fitting unit is used to fit the relationship between the unit heat consumption and the main steam pressure based on the arithmetic progression of the main steam pressure values ​​corresponding to each preselected non-rated operating point and the corresponding unit heat consumption;

[0026] The correction unit is used to obtain the pressure behind the high-pressure regulating valve corresponding to each non-rated operating point under actual conditions, and obtain the corrected main steam pressure in combination with the steam inlet pressure loss of the high-pressure steam inlet valve group under rated conditions. At the same time, based on the relationship between the unit heat rate and the main steam pressure, the unit heat rate corresponding to the corrected main steam pressure is obtained.

[0027] According to the third aspect of an embodiment of the present disclosure, an electronic device is provided, comprising a memory, a processor, and a computer program stored and running on the memory, wherein when the processor executes the program, a method for correcting the main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit is implemented.

[0028] According to a fourth aspect of an embodiment of the present disclosure, a non-transitory computer-readable storage medium is provided, on which a computer program is stored. When the program is executed by a processor, the method for correcting the main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit is implemented.

[0029] Compared with the prior art, the present invention has the following advantages:

[0030] The present disclosure provides a method and system for correcting the main steam pressure under non-rated conditions of a full-cycle steam intake unit. The scheme overcomes the problem that traditional steam turbine thermal test methods such as GB / T 8117 and ASME PTC6 cannot correct the main steam pressure under non-rated conditions. For the full-cycle steam intake unit, a new main steam pressure correction concept is proposed based on its design characteristics. In the performance test of the full-cycle steam intake unit under non-rated conditions, the scheme described in the present disclosure can still obtain the main steam pressure corrected to the condition where the high-pressure regulating valve is fully opened, even if the high-pressure regulating valve is not fully opened. Then, based on the equation of main steam pressure and heat consumption, the heat consumption of the unit under non-rated conditions after the main steam pressure is corrected is obtained.

[0031] Advantages of additional aspects of the present disclosure will be given in part in the following description and in part will become apparent from the following description or learned through practice of the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] The accompanying drawings, which constitute a part of the present disclosure, are used to provide a further understanding of the present disclosure. The exemplary embodiments of the present disclosure and their descriptions are used to explain the present disclosure and do not constitute an improper limitation to the present disclosure.

[0033] Figure 1 This is a flow chart of a method for correcting the main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit described in an embodiment of the present disclosure. DETAILED DESCRIPTION

[0034] The present disclosure will be further described below with reference to the accompanying drawings and embodiments.

[0035] It should be noted that the following detailed descriptions are illustrative and intended to provide further explanation of the present disclosure. Unless otherwise specified, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art to which the present disclosure belongs.

[0036] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present disclosure. As used herein, unless the context clearly indicates otherwise, the singular form is intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, they indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0037] In the absence of conflict, the embodiments of the present disclosure and the features thereof may be combined with each other.

[0038] Example 1:

[0039] The purpose of this embodiment is to provide a method for correcting the main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit.

[0040] like Figure 1 As shown, a method for correcting the main steam pressure of a full-cycle steam inlet unit under non-rated operating conditions includes:

[0041] Based on the relationship between main steam pressure and main steam flow and between main steam flow and power, determine the power, main steam flow and main steam pressure values ​​at each preselected non-rated operating point;

[0042] For each preselected non-rated operating point, the corresponding main steam pressure value is adjusted according to the preset arithmetic progression, and a series of new unit heat rates are obtained based on the calculation method of the turbine variable operating condition;

[0043] Based on the arithmetic progression of main steam pressure values ​​corresponding to each preselected non-rated operating point and the corresponding unit heat rate, the relationship between unit heat rate and main steam pressure is obtained by fitting;

[0044] The pressure behind the high-pressure regulating valve corresponding to each non-rated operating point under the actual measured conditions is obtained, and combined with the steam inlet pressure loss of the high-pressure steam inlet valve group under the rated operating conditions, the corrected main steam pressure is obtained. At the same time, based on the relationship between the unit heat rate and the main steam pressure, the unit heat rate corresponding to the corrected main steam pressure is obtained.

[0045] Furthermore, the obtained high-pressure regulating valve rear pressure corresponding to each non-rated operating point under the measured conditions is combined with the high-pressure steam inlet valve group inlet steam pressure loss under the rated operating conditions to obtain the corrected main steam pressure, specifically using the following formula:

[0046]

[0047] in, is the pressure behind the high-pressure door measured under various non-rated working conditions, Design pressure loss for the high-pressure steam inlet valve group, To correct the main steam pressure to the fully open throttle valve.

[0048] Furthermore, the relationship between the heat consumption of the unit and the main steam pressure is specifically expressed as follows:

[0049]

[0050] in, is the heat consumption of the new unit; is the new main steam pressure; 、 、 is a constant.

[0051] Furthermore, the relationship between the main steam pressure and the main steam flow, and between the main steam flow and the power is obtained by, specifically: based on the main steam pressure-main steam flow curve and the main steam flow-power curve provided by the full-cycle steam inlet unit design data, by determining the data of several known points on the curve, constructing the relationship equations between the main steam pressure and the main steam flow, and between the main steam flow and the power.

[0052] Furthermore, the method of obtaining the high-pressure regulating valve rear pressure corresponding to each non-rated operating point under actual measured conditions is specifically: conducting a thermal performance test on the unit, and using a pre-selected non-rated operating point as the test operating point to obtain the high-pressure regulating valve rear pressure under actual measured conditions.

[0053] Furthermore, the steam inlet pressure loss of the high-pressure steam inlet valve group under the rated working conditions is specifically expressed as:

[0054]

[0055] in, The main steam valve forward steam pressure, that is, the main steam pressure, For high-profile door pressure, Design the pressure drop for the high-pressure steam inlet valve group.

[0056] Furthermore, the preselected non-rated operating point is obtained as a percentage of the rated operating point THA condition.

[0057] Specifically, for ease of understanding, the solution described in this embodiment is described in detail below with reference to the accompanying drawings:

[0058] In order to solve the problems existing in the prior art, this embodiment provides a method for correcting the main steam pressure of a full-cycle steam inlet unit under non-rated operating conditions, which specifically includes the following steps:

[0059] Step 1: Based on the main steam pressure-main steam flow curve and main steam flow-power curve provided in the full-cycle steam inlet unit design data, these two curves are different from the throttling steam inlet unit in that they are both linear. Determine the data of several known points on the curves and first calculate the equations of main steam pressure and main steam flow, and main steam flow and power as follows:

[0060]

[0061] in, is the main steam flow, is the main steam pressure, is power, 、 、 、 is a constant.

[0062] Step 2: Determine the non-rated operating points. Except for full load, all other operating points are non-rated operating conditions. The rated operating point is generally the THA (turbine heat acceptance) condition. First, select several non-rated operating points, such as 75%THA, 50%THA, 40%THA, and 30%THA. Other non-rated operating points can also be selected based on actual needs. Based on formulas (1) and (2), determine the values ​​of power, main steam flow, and main steam pressure at each non-rated operating point.

[0063] Step 3: For the non-rated operating point determined in step 2, slightly change the main steam pressure value according to an arithmetic progression, while keeping other parameters unchanged. Calculate a series of new unit heat rates according to the turbine variable operating condition calculation method. Then, use the main steam pressure arithmetic progression as the X value and the unit heat rate as the Y value to fit the equation between the unit heat rate and the main steam pressure. This equation is a linear or quadratic function, and an equation between the unit heat rate and the main steam pressure is fitted for each non-rated operating point:

[0064]

[0065] in, is the heat consumption of the new unit; is the new main steam pressure; 、 、 is a constant.

[0066] Step 4: Based on the design data under rated operating conditions provided by the manufacturer, find out the steam pressure before the main steam valve and the pressure after the high-pressure regulating valve, and calculate the design pressure loss of the high-pressure steam inlet valve group of the unit. The pressure loss of the high-pressure steam inlet valve group includes the pressure loss of the main steam valve and the pressure loss of the high-pressure regulating valve. Even if the main regulating valve is fully open under rated operating conditions, there is still pressure loss. The steam inlet pressure loss of the high-pressure steam inlet valve group is:

[0067]

[0068] in, The main steam valve forward steam pressure, that is, the main steam pressure, For high-profile door pressure, Design the pressure drop for the high-pressure steam inlet valve group.

[0069] Step 5: Conduct thermal performance test on the unit. The test operating point is based on the load point, and the non-rated operating point selected in step 2 is used as the test operating point. The test is mainly to measure the main steam pressure, high-pressure valve back pressure and other parameters of each non-rated operating point, and calculate the test heat consumption of the unit.

[0070] Step 6: Based on the measured high-pressure throttle valve pressure at the non-rated operating point obtained in step 5 and the high-pressure steam inlet valve group inlet pressure loss obtained in step 4, calculate the corrected main steam pressure. This main steam pressure is the main steam pressure when the throttle valve is fully open:

[0071]

[0072] in, is the pressure behind the high-pressure door measured under various non-rated working conditions, Design pressure loss for the high-pressure steam inlet valve group, To correct the main steam pressure to the fully open throttle valve.

[0073] Step 7: Correct the main steam pressure under non-rated conditions obtained in step 6 , and substituting it into formula (3) yields the heat rate after main steam pressure correction. This heat rate is the actual heat rate of the unit, obtained by correcting the measured main steam pressure to the main steam pressure with the throttle fully open under any non-rated operating condition. The design pressure loss of the unit's high-pressure inlet valve group is also taken into account. Therefore, the heat rate obtained is the actual heat rate of the unit.

[0074] Example 2:

[0075] The purpose of this embodiment is to provide a main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions.

[0076] A main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions, comprising:

[0077] a data acquisition unit for determining the power, main steam flow, and main steam pressure values ​​at each preselected non-rated operating point based on the relationship between the main steam pressure and the main steam flow, and between the main steam flow and the power;

[0078] A fitting data set construction unit is used to adjust the corresponding main steam pressure value for each preselected non-rated operating point according to a preset arithmetic progression, and obtain a series of new unit heat rates based on the turbine variable operating condition calculation method;

[0079] A fitting unit is used to fit the relationship between the unit heat consumption and the main steam pressure based on the arithmetic progression of the main steam pressure values ​​corresponding to each preselected non-rated operating point and the corresponding unit heat consumption;

[0080] The correction unit is used to obtain the pressure behind the high-pressure regulating valve corresponding to each non-rated operating point under actual conditions, and obtain the corrected main steam pressure in combination with the steam inlet pressure loss of the high-pressure steam inlet valve group under rated conditions. At the same time, based on the relationship between the unit heat rate and the main steam pressure, the unit heat rate corresponding to the corrected main steam pressure is obtained.

[0081] Furthermore, the system described in this embodiment corresponds to the method described in Example 1, and its technical details have been described in detail in Example 1, so they will not be repeated here.

[0082] In further embodiments, there is also provided:

[0083] An electronic device includes a memory and a processor, and computer instructions stored in the memory and executed by the processor. When the computer instructions are executed by the processor, the method described in Example 1 is performed. For the sake of brevity, no further details are given here.

[0084] It should be understood that in this embodiment, the processor may be a central processing unit (CPU), or may be other general-purpose processors, digital signal processors (DSP), application-specific integrated circuits (ASIC), off-the-shelf field-programmable gate arrays (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. The general-purpose processor may be a microprocessor or any conventional processor, etc.

[0085] The memory may include a read-only memory and a random access memory, and provides instructions and data to the processor. A portion of the memory may also include a non-volatile random access memory. For example, the memory may also store information about the device type.

[0086] A computer-readable storage medium is used to store computer instructions, and when the computer instructions are executed by a processor, the method described in embodiment 1 is performed.

[0087] The method in Example 1 can be directly implemented as being executed by a hardware processor, or by a combination of hardware and software modules within the processor. The software module can be located in a storage medium well-established in the art, such as random access memory, flash memory, read-only memory, programmable read-only memory, electrically erasable programmable memory, or registers. The storage medium is located in the memory, and the processor reads the information in the memory and, in conjunction with its hardware, completes the steps of the above method. To avoid repetition, a detailed description is not given here.

[0088] Those skilled in the art will appreciate that the units, i.e., algorithm steps, of the various examples described in this embodiment can be implemented using electronic hardware or a combination of computer software and electronic hardware. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Professionals and technicians may use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of this disclosure.

[0089] The above embodiment provides a method and system for correcting the main steam pressure under non-rated operating conditions of a full-cycle steam-inlet unit, which can be implemented and has broad application prospects.

[0090] The foregoing description is merely a preferred embodiment of the present disclosure and is not intended to limit the present disclosure. Those skilled in the art will readily appreciate that various modifications and variations are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present disclosure shall be included within the scope of protection of the present disclosure.

Claims

1. A method for correcting the main steam pressure of a full-cycle steam inlet unit under non-rated operating conditions, characterized in that: include: Based on the relationship between main steam pressure and main steam flow and between main steam flow and power, determine the power, main steam flow and main steam pressure values ​​at each preselected non-rated operating point, wherein the preselected non-rated operating point is obtained as a percentage of the rated operating point THA condition; For each preselected non-rated operating point, the corresponding main steam pressure value is adjusted according to the preset arithmetic progression, and a series of new unit heat rates are obtained based on the calculation method of the turbine variable operating condition; Based on the arithmetic progression of main steam pressure values ​​corresponding to each preselected non-rated operating point and the corresponding unit heat rate, the relationship between unit heat rate and main steam pressure is obtained by fitting; The pressure behind the high-pressure regulating valve corresponding to each non-rated operating point under the actual measured conditions is obtained, and combined with the steam inlet pressure loss of the high-pressure steam inlet valve group under the rated operating conditions, the corrected main steam pressure is obtained. At the same time, based on the relationship between the unit heat rate and the main steam pressure, the unit heat rate corresponding to the corrected main steam pressure is obtained.

2. The method for correcting the main steam pressure of a full-cycle steam inlet unit under non-rated operating conditions according to claim 1, characterized in that: The obtained high-pressure regulating valve rear pressure corresponding to each non-rated operating point under the actual measurement conditions is combined with the steam inlet pressure loss of the high-pressure steam inlet valve group under the rated operating conditions to obtain the corrected main steam pressure. Specifically, the following formula is used: in, is the pressure behind the high-pressure door measured under various non-rated working conditions, Design pressure loss for the high-pressure steam inlet valve group, To correct the main steam pressure to the fully open throttle valve.

3. The method for correcting the main steam pressure of a full-cycle steam inlet unit under non-rated operating conditions according to claim 1, characterized in that: The relationship between the heat consumption of the unit and the main steam pressure is specifically expressed as follows: in, is the heat consumption of the new unit; is the new main steam pressure; 、 、 is a constant.

4. The method for correcting the main steam pressure of a full-cycle steam inlet unit under non-rated operating conditions according to claim 1, characterized in that: The relationship between the main steam pressure and the main steam flow, and between the main steam flow and the power is obtained specifically as follows: based on the main steam pressure-main steam flow curve and the main steam flow-power curve provided by the full-cycle steam inlet unit design data, by determining the data of several known points on the curve, the relationship equations between the main steam pressure and the main steam flow, and between the main steam flow and the power are constructed.

5. The method for correcting main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit according to claim 1, characterized in that: The method of obtaining the high-pressure regulating valve rear pressure corresponding to each non-rated operating point under actual measurement conditions is specifically: conducting a thermal performance test on the unit, and using a preselected non-rated operating point as the test operating point to obtain the high-pressure regulating valve rear pressure under actual measurement conditions.

6. The method for correcting main steam pressure under non-rated operating conditions of a full-cycle steam inlet unit according to claim 1, characterized in that: The inlet steam pressure loss of the high-pressure steam inlet valve group under the rated working conditions is specifically expressed as: in, The main steam valve forward steam pressure, that is, the main steam pressure, For high-profile door pressure, Design the pressure drop for the high-pressure steam inlet valve group.

7. A main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions, characterized in that: include: a data acquisition unit, configured to determine the power, main steam flow, and main steam pressure values ​​at each preselected non-rated operating point based on the relationship between the main steam pressure and the main steam flow, and between the main steam flow and the power, wherein the preselected non-rated operating point is acquired as a percentage of the rated operating point (THA); A fitting data set construction unit is used to adjust the corresponding main steam pressure value for each preselected non-rated operating point according to a preset arithmetic progression, and obtain a series of new unit heat rates based on the turbine variable operating condition calculation method; A fitting unit is used to fit the relationship between the unit heat consumption and the main steam pressure based on the arithmetic progression of the main steam pressure values ​​corresponding to each preselected non-rated operating point and the corresponding unit heat consumption; The correction unit is used to obtain the pressure behind the high-pressure regulating valve corresponding to each non-rated operating point under actual conditions, and obtain the corrected main steam pressure in combination with the steam inlet pressure loss of the high-pressure steam inlet valve group under rated conditions. At the same time, based on the relationship between the unit heat rate and the main steam pressure, the unit heat rate corresponding to the corrected main steam pressure is obtained.

8. The main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions as claimed in claim 7, characterized in that: The obtained high-pressure regulating valve rear pressure corresponding to each non-rated operating point under the actual measurement conditions is combined with the steam inlet pressure loss of the high-pressure steam inlet valve group under the rated operating conditions to obtain the corrected main steam pressure. Specifically, the following formula is used: in, is the pressure behind the high-pressure door measured under various non-rated working conditions, Design pressure loss for the high-pressure steam inlet valve group, To correct the main steam pressure to the fully open throttle valve.

9. The main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions according to claim 7, characterized in that: The relationship between the heat consumption of the unit and the main steam pressure is specifically expressed as follows: in, is the heat consumption of the new unit; is the new main steam pressure; 、 、 is a constant.

10. The main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions according to claim 7, characterized in that: The relationship between the main steam pressure and the main steam flow, and between the main steam flow and the power is obtained specifically as follows: based on the main steam pressure-main steam flow curve and the main steam flow-power curve provided by the full-cycle steam inlet unit design data, by determining the data of several known points on the curve, the relationship equations between the main steam pressure and the main steam flow, and between the main steam flow and the power are constructed.

11. The main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions according to claim 7, characterized in that: The method of obtaining the high-pressure regulating valve rear pressure corresponding to each non-rated operating point under actual measurement conditions is specifically: conducting a thermal performance test on the unit, and using a preselected non-rated operating point as the test operating point to obtain the high-pressure regulating valve rear pressure under actual measurement conditions.

12. The main steam pressure correction system for a full-cycle steam inlet unit under non-rated operating conditions according to claim 7, characterized in that: The inlet steam pressure loss of the high-pressure steam inlet valve group under the rated working conditions is specifically expressed as: in, The main steam valve forward steam pressure, that is, the main steam pressure, For high-profile door pressure, Design the pressure drop for the high-pressure steam inlet valve group.

13. An electronic device comprising a memory, a processor, and a computer program stored and running on the memory, characterized in that: When the processor executes the program, a main steam pressure correction method under non-rated operating conditions of a full-cycle steam inlet unit as described in any one of claims 1-6 is implemented.

14. A non-transitory computer-readable storage medium having a computer program stored thereon, characterized in that: When the program is executed by a processor, a main steam pressure correction method under non-rated operating conditions of a full-cycle steam inlet unit as described in any one of claims 1 to 6 is implemented.

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