Multi-dimensional monitoring platform for flexible operation of steam turbines

Abstract

The present disclosure proposes a multi-dimensional monitoring platform for a flexibly operated steam turbine, comprising: a processing server, a database and a wireless communication component, wherein the processing server and the steam turbine are transmitted data via the wireless communication component, and the processing server is connected to the database; the database is used to store a first monitoring data set of key components of the steam turbine under target conditions during the design phase and a second monitoring data set of key components under target conditions during the operation phase; the processing server is used to obtain monitoring instructions, determine a steam turbine to be monitored from multiple steam turbines based on the monitoring instructions, identify the target stage currently in which the steam turbine to be monitored is located, and determine a target data set from the first monitoring data set and the second monitoring data set based on the target stage, and based on the target data set, execute a target optimization process matching the target stage for the key components of the steam turbine to be monitored. Thus, the long life and high flexibility of the steam turbine are guaranteed.

Description

Technical Field

[0001] The present disclosure relates to the technical field of steam turbines, and in particular to a multi-dimensional monitoring platform for flexibly operating steam turbines. Background Art

[0002] Due to the intermittent, random and volatile nature of renewable energy generation such as wind and solar power, the power grid can usually only accommodate 15% of unstable power sources, resulting in serious wind and solar power abandonment. With existing steam turbine technology, the minimum load for peak load regulation is usually 35% of rated power. By designing and using highly flexible steam turbines, deep peak load regulation to 20% of rated power and fast starting and ramping functions, the power grid can add new unstable power sources that can accommodate 15% of the rated power of the corresponding steam turbine, which helps solve the problem of wind and solar power abandonment. Summary of the invention

[0003] The present disclosure aims to solve one of the technical problems in the related art at least to some extent.

[0004] To this end, the first purpose of the present invention is to propose a multi-dimensional monitoring platform for flexible operation of steam turbines, so as to ensure that the key components of the steam turbine are in a controlled state under target operating conditions, thereby ensuring the long life and high flexibility of the target steam turbine design.

[0005] To achieve the above-mentioned objectives, the first aspect of the present disclosure proposes a multi-dimensional monitoring platform for flexibly operating steam turbines, comprising: a processing server, a database and a wireless communication component, wherein the wireless communication component is connected to the steam turbine and the multi-dimensional monitoring platform, and the multi-dimensional monitoring platform and the steam turbine are transmitted data through the wireless communication component, and the processing server is connected to the database; the database is used to store a first monitoring data set of key components of the steam turbine design stage under target conditions and a second monitoring data set of key components of the operation stage under target conditions; the processing server is used to obtain monitoring instructions, determine a steam turbine to be monitored from multiple steam turbines based on the monitoring instructions, identify the target stage currently in which the steam turbine to be monitored is in, and determine a target data set from the first monitoring data set and the second monitoring data set based on the target stage, and based on the target data set, execute a target optimization process matching the target stage for the key components of the steam turbine to be monitored.

[0006] The multi-dimensional monitoring platform for flexibly operating steam turbines provided by the present invention can obtain the first monitoring data set and the second monitoring data set of the steam turbine from the database through the processing server of the monitoring platform, determine the steam turbine to be monitored from multiple steam turbines based on the monitoring instructions, and identify the target stage of the steam turbine to be monitored, and then determine the corresponding target data set based on the target stage, so as to execute the target optimization process matching the target stage for the key components of the steam turbine to be monitored, so that the key components of the steam turbine to be monitored are in a controlled state, thereby ensuring the long life and high flexibility of the steam turbine design.

[0007] Additional aspects and advantages of the present disclosure will be given in part in the following description and in part will be obvious from the following description or learned through practice of the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] The above and / or additional aspects and advantages of the present disclosure will become apparent and easily understood from the following description of the embodiments in conjunction with the accompanying drawings, in which:

[0009] Figure 1 A schematic diagram of the structure of a multi-dimensional monitoring platform for flexibly operating steam turbines provided by an embodiment of the present disclosure;

[0010] Figure 2 A schematic diagram of the flow of the multi-dimensional monitoring platform provided in the embodiment of the present disclosure for the structural design and operation monitoring of a flexible operation steam turbine;

[0011] Figure 3 A schematic flow chart of a design and monitoring process of the structural transient strength of key components of a steam turbine under target operating conditions in the structural design and operation monitoring of a flexibly operated steam turbine provided by an embodiment of the present disclosure;

[0012] Figure 4 A flow chart of a process for monitoring the life-related design of a high-pressure cylinder and an intermediate-pressure cylinder of a steam turbine under target working conditions in the structural design and operation monitoring of a flexible operation steam turbine provided by an embodiment of the present disclosure;

[0013] Figure 5 A flow chart of a process for monitoring the life-related design of a low-pressure cylinder of a steam turbine under target working conditions in the structural design and operation monitoring of a flexible operation steam turbine provided by an embodiment of the present disclosure;

[0014] Figure 6 A schematic flow chart of a process for operating monitoring of crack initiation remaining calendar life of key components of a steam turbine under target operating conditions in the structural design and operation monitoring of a flexible operation steam turbine provided by an embodiment of the present disclosure;

[0015] Figure 7A flow chart of the operation monitoring process of the thermal stress determination value of the key components of the steam turbine under the target working condition in the structural design and operation monitoring of the flexible operation steam turbine provided by the embodiment of the present disclosure;

[0016] Figure 8 A flow chart of the process of operational monitoring of the safety judgment value of dynamic and static friction of a steam turbine under target operating conditions in the structural design and operational monitoring of a flexibly operated steam turbine provided in an embodiment of the present disclosure. DETAILED DESCRIPTION

[0017] Embodiments of the present disclosure are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present disclosure, and should not be construed as limiting the present disclosure.

[0018] The following describes a multi-dimensional monitoring platform for a flexibly operated steam turbine according to an embodiment of the present disclosure with reference to the accompanying drawings.

[0019] Figure 1 A flow chart of a multi-dimensional monitoring platform for flexibly operating a steam turbine provided by an embodiment of the present disclosure, such as Figure 1 As shown, the monitoring platform 100 includes the following contents: a processing server 11, a database 12 and a wireless communication component 13.

[0020] The processing server 11 and the steam turbine are connected to each other through a wireless communication group 13 for data transmission, and the processing server 11 is connected to the database.

[0021] In the disclosed embodiment, the function of the processing server 11 is related to the target stage of the steam turbine, and the function of the processing server will change when the steam turbine is in different target stages, wherein the target stage includes the design stage of the steam turbine and the operation stage of the steam turbine.

[0022] In some embodiments, the database 12 is used to store a first monitoring data set of key components under target conditions during the design phase of the steam turbine and a second monitoring data set of key components under target conditions during the operation phase.

[0023] Optionally, the target operating conditions may include, but are not limited to: rapid start-up of the steam turbine and / or rapid load change and ramp-up transient operating conditions.

[0024] In one possible implementation, if the target stage is the design stage of the steam turbine, the processing server 11 obtains the first monitoring data set of the steam turbine to be monitored from the database 12, determines the target data set, and executes a structural optimization process for key components of the steam turbine to be monitored.

[0025] Optionally, the first monitoring data set includes: the yield strength of the material of the key components of the steam turbine at the transient operating temperature, the maximum equivalent stress of the structure of the key components under the target working condition, and the stress ratio of the key components. The design life basic data of the key components, the design operation target basic data of the steam turbine, and the crack initiation calendar life of the key components.

[0026] In a possible implementation, if the target stage is the operation stage, the processing server 11 obtains the second monitoring data set of the steam turbine to be monitored from the database 12, determines the target data set, and executes the operation optimization process for the key components of the steam turbine to be monitored.

[0027] Optionally, the second monitoring data set includes: basic data on the design life of key components of the steam turbine, basic data on the design and operation targets of the steam turbine, and the remaining calendar life of the crack initiation of key components of the steam turbine under target operating conditions. Basic data on thermal stress of key components of the steam turbine, basic data on metal temperature, and thermal stress judgment values ​​under target operating conditions. Operating limit values ​​of the axial displacement and differential expansion of the steam turbine rotor, monitoring data on the axial displacement and differential expansion of the rotor, and safety judgment values ​​of dynamic and static friction under target operating conditions of key components.

[0028] In a possible implementation, the database 12 includes a first storage space and a second storage space, the first storage space is used to store a first monitoring data set, and the second storage space is used to store a second monitoring data set.

[0029] In a possible implementation, the monitoring platform further includes a data collection component 14. Optionally, the data collection component 14 is connected to the processing server 11 via a wireless communication component 13.

[0030] Optionally, the data acquisition component 14 is used to collect design monitoring data of key components of the steam turbine during the design phase, and to collect operation monitoring data of key components of the steam turbine during the operation phase.

[0031] Optionally, the data acquisition component 14 may include but is not limited to: a steam turbine digital electro-hydraulic control system (DEH), a steam turbine control system (TCS), a steam turbine monitoring instrument system (TSI), etc. The monitoring data of the steam turbine can be obtained through the data acquisition component.

[0032] Further, the data collection component 14 sends the collected monitoring data to the processing server 11. The processing server 11 is used to receive the monitoring data, identify the monitoring data as design monitoring data of key components, and store it in the first storage space, and identify the monitoring data as operation monitoring data of key components, and store it in the second storage space.

[0033] In one possible implementation, the processing server 11 is used to obtain monitoring instructions, determine a steam turbine to be monitored from multiple steam turbines based on the monitoring instructions, identify the target stage currently in which the steam turbine to be monitored is located, and determine a target data set from a first monitoring data set and a second monitoring data set based on the target stage, and based on the target data set, execute a target optimization process matching the target stage on key components of the steam turbine to be monitored.

[0034] In a possible implementation, the monitoring platform is a distributed network structure, including a scheduling server 15, and the distributed network structure includes multiple processing servers 11. Among them, the scheduling server 15 is used to receive the monitoring instruction, schedule the monitoring instruction, determine the target processing server corresponding to the monitoring instruction, and send the monitoring instruction to the target processing server.

[0035] In a possible implementation, the scheduling server 15 is further used to obtain a first load status of each processing server, and schedule the monitoring instruction according to the first load status to determine the target processing server.

[0036] In a possible implementation, the monitoring platform further includes a remote client 16, which is connected to the processing server 11. The remote client 16 is used to send monitoring instructions to the processing server and receive optimization results of key components of the steam turbine to be monitored fed back by the processing server.

[0037] In a possible implementation, the remote client 16 is further configured to obtain control information of a user who controls the remote client, and generate a monitoring instruction based on the control information.

[0038] Optionally, the database 12 may also store monitoring qualified conditions corresponding to each type of monitoring data in the first monitoring data set and the second monitoring data set. For example, the first monitoring data set includes: the first design monitoring data of the structural transient strength of the key component under the target working condition, and the second design monitoring data related to the life of the key component under the target working condition. The database 12 may store the first monitoring qualified conditions corresponding to the first design monitoring data and the second monitoring qualified conditions corresponding to the second design monitoring data. The second monitoring data set includes: the remaining calendar life of crack initiation of the key component under the target working condition, the thermal stress judgment value of the key component under the target working condition, and the safety judgment value of dynamic and static friction of the key component under the target working condition. The database 12 may store the third monitoring qualified conditions corresponding to the remaining calendar life of crack initiation, the fourth monitoring qualified conditions corresponding to the thermal stress judgment value, and the fifth monitoring qualified conditions corresponding to the safety judgment value of dynamic and static friction.

[0039] In the multi-dimensional monitoring platform for flexibly operating steam turbines provided by the embodiments of the present disclosure, the processing server of the monitoring platform can obtain the first monitoring data set and the second monitoring data set of the steam turbine from the database, determine the steam turbine to be monitored from multiple steam turbines based on the monitoring instructions, and identify the target stage of the steam turbine to be monitored, and then determine the corresponding target data set based on the target stage, so as to execute the target optimization process matching the target stage for the key components of the steam turbine to be monitored, so that the key components of the steam turbine to be monitored are in a controlled state, thereby ensuring the long life and high flexibility of the steam turbine design.

[0040] In a possible implementation, the database 12 may store the yield strength R of the material of the key components of the steam turbine at the transient operating temperature. t p0.2jk , the maximum equivalent stress S of key components under target conditions eqjk Strength basic data, low cycle fatigue crack initiation life of key components N ijk 、Creep crack initiation life of key components τ cjk The basic data of design life. Among them, the subscript i indicates the start and stop type of the steam turbine, c indicates cold start and stop, w indicates warm start and stop, h indicates hot start and stop, v indicates extremely hot start and stop, 20% indicates 20% to 100% load change, subscript j indicates the working environment of key components, H indicates high pressure, I indicates medium pressure, L indicates low pressure, subscript k indicates the name of the steam turbine component, V indicates valve housing, R indicates rotor, and C indicates cylinder. Number of cold starts of steam turbine n c0 , Number of warm-state starts of steam turbine n w0 , Number of hot starts of steam turbine n h0 、Number of extremely hot start-ups of the steam turbine v0 、The number of times the turbine load changes from 20% to 100% is n 20％0, Annual average operating hours of steam turbine t y , the design operation target basic data of the total calendar life design criterion value τ0 of the turbine, the cumulative number of cold starts of the in-service turbines n c1 , cumulative number of warm starts n w1 , cumulative number of hot starts n h1 , Accumulated number of extremely hot starts n v1 , cumulative 20% to 100% load change climbing times n 20％1 , cumulative running hours t SH , the actual operating basic data of the calendar life τ1 of the turbine since it was put into operation.

[0041] In a possible implementation, the database 12 may also store the elastic modulus E of the material of the turbine rotor, valve housing and cylinder. jk 、Linear expansion coefficient α jk and Poisson's ratio μ jk And the thermal stress monitoring parameter criterion value S of the turbine rotor, valve housing and cylinder corresponding to the total calendar life design criterion value τ0 of the turbine thjk The basic data of the thermal stress monitoring parameter criterion value, the simulation calculation value of the rotor volume average temperature of the turbine startup, shutdown, load change and load operation t mjR The surface temperature t of the high-pressure rotor and the intermediate-pressure rotor is represented by the metal temperature at the measuring point at the depth of 82% to 98% of the wall thickness of the high-pressure inner cylinder and the intermediate-pressure inner cylinder. jR0 , Metal temperature t at the measuring point where the wall thickness of high-pressure valve shell and medium-pressure valve shell is 82% to 98% jV90 , Metal temperature t of the measuring point at the depth of 40% to 60% of the wall thickness of the high-pressure valve shell and the medium-pressure valve shell jV50 , the metal temperature t of the measuring point at the depth of 82% to 98% of the wall thickness of the high-pressure cylinder and the medium-pressure cylinder jC90 , Basic data of metal temperature at the measuring point at 40% to 60% depth of the wall thickness of high-pressure cylinder and medium-pressure cylinder jC50 The metal temperature of the measuring point is taken from the turbine digital electro-hydraulic control system DEH or the turbine control system TCS.

[0042] In a possible implementation, the database 12 may also store the online monitoring data y of the axial displacement of the turbine rotor at the thrust bearing part, the online monitoring data x of the expansion difference between the high-pressure rotor at the exhaust side of the high-pressure cylinder of the turbine and the high-pressure cylinder. H , Online monitoring data of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side far away from the thrust bearing and the intermediate pressure cylinder I , Basic data for online monitoring of the expansion difference between the low-pressure rotor and the low-pressure cylinder of the steam turbine generator side LThe online monitoring data of the rotor axial displacement and expansion difference are taken from the turbine monitoring instrument system TSI; the lower limit value of the axial displacement of the turbine rotor at the thrust bearing is y L , Upper limit of axial displacement of turbine rotor at thrust bearing position y U , The lower limit of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine and the high-pressure cylinder x HL , The upper limit of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine and the high-pressure cylinder x HU , The lower limit of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side of the thrust bearing and the intermediate pressure cylinder x IL , The upper limit value of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side of the thrust bearing and the intermediate pressure cylinder x IU , The lower limit of the expansion difference between the low-pressure rotor on the generator side of the steam turbine low-pressure cylinder and the low-pressure cylinder x LL , The upper limit value of the expansion difference between the low-pressure rotor on the generator side of the steam turbine low-pressure cylinder and the low-pressure cylinder x LU operating limit value.

[0043] Based on the multi-dimensional monitoring platform of the steam turbine provided in the above embodiment, the flexible operation steam turbine can be monitored. In some embodiments, the multi-dimensional monitoring platform can perform structural design and operation monitoring on the flexible operation steam turbine.

[0044] In some embodiments, the multi-dimensional monitoring platform can perform design monitoring on the structural transient strength of key components of the flexibly operated steam turbine under target conditions. In some embodiments, the multi-dimensional monitoring platform can perform design monitoring on the high-pressure cylinder and the medium-pressure cylinder of the flexibly operated steam turbine under target conditions in relation to life. In some embodiments, the multi-dimensional monitoring platform can perform design monitoring on the low-pressure cylinder of the flexibly operated steam turbine under target conditions in relation to life. In some embodiments, the multi-dimensional monitoring platform can perform operational monitoring on the remaining calendar life of crack initiation of key components of the flexibly operated steam turbine under target conditions. In some embodiments, the multi-dimensional monitoring platform can perform operational monitoring on the thermal stress judgment value of key components of the flexibly operated steam turbine under target conditions. In some embodiments, the multi-dimensional monitoring platform can perform operational monitoring on the safety judgment value of dynamic and static friction of the flexibly operated steam turbine under target conditions.

[0045] It can be understood that, in the above-mentioned multiple types of monitoring, the multi-dimensional monitoring platform provided in the embodiment of the present disclosure is the execution subject. The following multi-dimensional monitoring platform explains each type of monitoring performed on the flexible operation steam turbine separately:

[0046] Figure 2 A schematic diagram of the flow chart of the structural design and operation monitoring of a flexible steam turbine by the multi-dimensional monitoring platform provided in the embodiment of the present disclosure, such as Figure 2 As shown, the method comprises the following steps:

[0047] S201, performing design monitoring on the structural transient strength of key components of the steam turbine under target operating conditions, and obtaining first design monitoring data of the structural transient strength of key components of the steam turbine under target operating conditions.

[0048] In the embodiment of the present disclosure, the first design monitoring data includes the yield strength of the material at the transient operating temperature of the key components of the steam turbine and the strength basic data of the maximum equivalent stress of the structure of the key components under the target working condition. Optionally, by obtaining the yield strength R of the material at the transient operating temperature of the key components of the steam turbine t p0.2jk , the maximum equivalent stress S of key components under target conditions eqjk The basic strength data can be used to determine whether it is necessary to perform structural optimization on the key components of the steam turbine, that is, to determine whether the first design monitoring data of the key components meets the first monitoring qualification conditions.

[0049] S202, performing design monitoring on the life of key components of the steam turbine under target operating conditions, and obtaining second design monitoring data related to the life of key components of the steam turbine under target operating conditions.

[0050] In the disclosed embodiment, the high-pressure cylinder, the medium-pressure cylinder and the low-pressure cylinder of the steam turbine can be used as the key components of the steam turbine. By obtaining the basic data of the design life and the basic data of the design operation target of the high-pressure cylinder, the medium-pressure cylinder and the low-pressure cylinder of the steam turbine, and using the basic data of the design life and the basic data of the design operation target as the second design monitoring data, it can be judged whether it is necessary to perform structural optimization on the key components of the steam turbine, that is, to judge whether the second design monitoring data of the key components meets the second monitoring qualification condition.

[0051] Optionally, based on the first design monitoring data of the key component, it is determined whether the structural transient strength design of the key component meets the first monitoring qualification condition, and based on the second design monitoring data of the key component, it is determined whether the life design of the key component meets the second monitoring qualification condition. If one type of design monitoring data does not meet the corresponding monitoring qualification condition, it is determined that the key component of the steam turbine needs to be structurally optimized. Then, the key component of the steam turbine is structurally optimized to obtain a target steam turbine.

[0052] S203, performing operation monitoring of the crack initiation remaining calendar life of key components of the target steam turbine in service under the target operating conditions, and obtaining operation monitoring data of the crack initiation remaining calendar life of key components of the target steam turbine in service under the target operating conditions.

[0053] In the disclosed embodiment, the crack initiation remaining calendar life of the key components of the target steam turbine in service under the target operating conditions can be monitored based on the design life basic data, design operation basic data and actual operation basic data of the key components.

[0054] Optionally, by obtaining the basic data on the design life and the actual operation basic data of key components such as the high-pressure cylinder, medium-pressure cylinder and low-pressure cylinder of the turbine, it is possible to determine whether the crack initiation remaining life operation monitoring of the target turbine in service is qualified, that is, to determine whether the key components of the target turbine in service meet the third monitoring qualification conditions.

[0055] S204, performing operation monitoring on the thermal stress of key components of the target steam turbine in service under the target operating condition, and obtaining the thermal stress operation determination value of the key components of the target steam turbine in service under the target operating condition.

[0056] In the disclosed embodiment, the thermal stress judgment value of the key components under the target operating conditions can be determined based on the basic thermal stress data of the key components and the basic metal temperature data of the measuring points, and the thermal stress of the key components of the target steam turbine in service under the target operating conditions can be monitored.

[0057] Optionally, by obtaining the basic thermal stress data of the key components of the target steam turbine in service and the basic metal temperature data of the measuring points, it is possible to determine whether the thermal stress operation monitoring of the flexible operation steam turbine in service under the target operating conditions is qualified, that is, to determine whether the key components of the target steam turbine in service meet the fourth monitoring qualification condition.

[0058] S205 , operating monitoring is performed on the dynamic and static friction safety of key components of the target steam turbine in service under the target operating conditions, and a safety determination value of the dynamic and static friction of key components of the target steam turbine in service under the target operating conditions is obtained.

[0059] In the disclosed embodiment, the safety judgment value of dynamic and static friction of key components under target operating conditions can be determined based on the monitoring data of rotor axial displacement and the monitoring data of rotor and cylinder expansion difference, and operational monitoring of the dynamic and static friction safety of key components of the target steam turbine in service under target operating conditions can be performed.

[0060] Optionally, by acquiring the axial displacement monitoring data of the in-service steam turbine rotor and the rotor-cylinder expansion difference monitoring data, it is possible to determine whether the operation monitoring of the dynamic-static friction safety of the flexibly operating steam turbine under the target operating conditions is qualified, that is, to determine whether the key components of the in-service target steam turbine meet the fifth monitoring qualification condition.

[0061] In the multi-dimensional monitoring platform for flexibly operating steam turbines provided by the embodiments of the present disclosure, a target steam turbine is obtained by obtaining a first monitoring data set of key components of the steam turbine under target working conditions, and optimizing the structure of the key components of the steam turbine based on the first monitoring data set, so that the structural transient strength and crack initiation calendar life of the key components of the target steam turbine under target working conditions are under control. Then, a second monitoring data set of the target steam turbine is obtained, and based on whether each type of monitoring data in the second monitoring data set is qualified, the operating parameters of the steam turbine are optimized, thereby ensuring the long life and high flexibility of the target steam turbine design.

[0062] Based on the above implementation, the disclosed embodiment can explain the design monitoring process of the structural transient strength of the key components of the steam turbine under the target working conditions, such as Figure 3 As shown in FIG. 1 , the design monitoring process of the structural transient strength of the key components of the steam turbine under the target operating conditions includes the following steps:

[0063] S301, obtain the yield strength R of the material at the transient operating temperature of the key components of the steam turbine t p0.2jk .

[0064] In the embodiment of the present disclosure, the key components of the steam turbine include a high-pressure valve housing, a high-pressure rotor, a high-pressure cylinder, a medium-pressure valve housing, a medium-pressure rotor, a medium-pressure cylinder, a low-pressure rotor and a low-pressure cylinder. The yield strength R of the material at the transient operating temperature of the key components t p0.2jk In, R t p0.2 It represents the yield strength of the material, subscript j represents the working environment of the key components (high pressure, medium pressure, low pressure), and subscript k represents the name of the turbine component (valve housing, rotor, cylinder).

[0065] Optionally, obtain the yield strength R of the material of the high-pressure valve casing of the steam turbine at the transient operating temperature t p0.2HV , the yield strength R of the material at the transient operating temperature of the high-pressure rotor t p0.2HR , the yield strength R of the material at the transient working temperature of the high-pressure cylinder t p0.2HC .

[0066] Optionally, obtain the yield strength R of the material of the medium pressure valve housing at the transient operating temperature t p0.2IV , the yield strength R of the material at the transient operating temperature of the medium pressure rotor t p0.2IR , the yield strength R of the material at the transient operating temperature of the medium pressure cylinder t p0.2IC .

[0067] Optionally, obtain the yield strength R of the material at the transient operating temperature of the low-pressure rotor t p0.2LR , the yield strength R of the material at the transient operating temperature of the low-pressure cylinder t p0.2LC .

[0068] Among them, R t p0.2 Indicates the yield strength of the material, H represents high pressure, I represents medium pressure, L represents low pressure, V represents valve housing, R represents rotor, and C represents cylinder.

[0069] S302, obtain the maximum equivalent stress S of the key components of the steam turbine under the target working condition eqjk .

[0070] In the disclosed embodiment, S eq represents the maximum equivalent stress of the structure, subscript j represents the working environment of the key components, and subscript k represents the name of the turbine component.

[0071] Optionally, the maximum equivalent stress S of the high-pressure valve casing of the steam turbine under the target operating condition can be obtained: eqHV , the maximum equivalent stress S of the high-pressure rotor of the steam turbine under the target operating conditions eqHR , the maximum equivalent stress S of the high-pressure cylinder of the steam turbine under the target operating conditions eqHC .

[0072] Optionally, the maximum equivalent stress S of the steam turbine medium-pressure valve casing under the target operating condition can be obtained: eqIV , the maximum equivalent stress S of the steam turbine intermediate pressure rotor under the target operating conditions eqIR , the maximum equivalent stress S of the turbine intermediate pressure cylinder under the target operating conditions eqIC .

[0073] Optionally, the maximum equivalent stress S of the low-pressure rotor of the steam turbine under the target operating condition can be obtained: eqLR , the maximum equivalent stress S of the low-pressure cylinder of the steam turbine under the target operating conditions eqLC .

[0074] Among them, S eq It represents the maximum equivalent stress of the structure, H represents high pressure, I represents medium pressure, L represents low pressure, V represents valve housing, R represents rotor, and C represents cylinder.

[0075] S303, determine the structural stress ratio R of key components of the steam turbine under target operating conditions sjk .

[0076] In the disclosed embodiment, R sIt represents the structural stress ratio, subscript j represents the working environment of the key components, and subscript k represents the name of the turbine component. The structural stress ratio can be determined by calculating the ratio of the maximum equivalent stress of the structure to the yield strength of the material.

[0077] Optionally, the calculation formula for the structural stress ratio of the high-pressure valve casing of the steam turbine under the target operating condition is: The calculation formula of the structural stress ratio of the high-pressure rotor of the steam turbine under the target operating condition is: The calculation formula of the structural stress ratio of the high-pressure cylinder of the steam turbine under the target working condition is:

[0078] Optionally, the calculation formula for the structural stress ratio of the steam turbine medium-pressure valve casing under the target operating condition is: The calculation formula of the structural stress ratio of the steam turbine intermediate pressure rotor under the target operating condition is: The calculation formula of the structural stress ratio of the intermediate pressure cylinder of the steam turbine under the target working condition is:

[0079] Optionally, the calculation formula for the structural stress ratio of the low-pressure rotor of the steam turbine under the target operating condition is: The calculation formula of the structural stress ratio of the low-pressure cylinder of the steam turbine under the target working condition is:

[0080] Among them, R s Represents the structural stress ratio, R t p0.2 Indicates the yield strength of the material, S eq It represents the maximum equivalent stress of the structure, H represents high pressure, I represents medium pressure, L represents low pressure, V represents valve housing, R represents rotor, and C represents cylinder.

[0081] S304, determining whether the structural transient strength of the key component meets the first monitoring qualification condition.

[0082] In the disclosed embodiment, it is determined whether the structural transient strength of the key component meets the first monitoring qualification condition, that is, it is determined whether the first design monitoring data meets the first monitoring qualification condition. Among them, the key components can be divided into high-pressure cylinders, medium-pressure cylinders and low-pressure cylinders. The high-pressure cylinder includes a high-pressure valve housing, a high-pressure rotor, and a high-pressure cylinder; the medium-pressure cylinder includes a medium-pressure valve housing, a medium-pressure rotor, and a medium-pressure cylinder; and the low-pressure cylinder includes a low-pressure rotor and a low-pressure cylinder. Then the first monitoring qualification condition of the high-pressure cylinder refers to the structural stress ratio of the high-pressure valve housing, the high-pressure rotor, and the high-pressure cylinder being less than 1; the first monitoring qualification condition of the medium-pressure cylinder refers to the structural stress ratio of the medium-pressure valve housing, the medium-pressure rotor, and the medium-pressure cylinder being less than 1; the first monitoring qualification condition of the low-pressure cylinder refers to the structural stress ratio of the low-pressure rotor and the low-pressure cylinder being less than 1.

[0083] That is to say, the transient strength design of the high-pressure cylinder of the steam turbine meets the first monitoring qualification condition (R sHV <1)∩(R sHR <1)∩(R sHC <1). The structural transient strength design of the steam turbine intermediate pressure cylinder meets the first monitoring qualification condition (R sIV <1)∩(R sIR <1)∩(R sIC <1). The transient strength design of the low-pressure cylinder of the steam turbine does not meet the first monitoring qualification condition (R sLR <1)∩(R sLC <1).

[0084] Optionally, the transient strength design of the steam turbine high-pressure cylinder does not meet the first monitoring qualification condition (R sHV ≥1)∪(R sHR ≥1)∪(R sHC ≥1). The transient strength design of the steam turbine intermediate pressure cylinder does not meet the first monitoring qualification condition (R sIV ≥1)∪(R sIR ≥1)∪(R sIC ≥1). The transient strength design of the low-pressure cylinder of the steam turbine does not meet the first monitoring qualification condition (R sLR <1)∪(R sLC <1).

[0085] S305 , in response to the structural transient strength design monitoring of the key components of the steam turbine not satisfying the first monitoring qualified condition, generating a structural optimization strategy set of the key components of the steam turbine.

[0086] Optionally, the optimization and improvement of the key components of the steam turbine may include optimizing and improving the structural dimensions, structural fillets, supporting structures, material design and selection, etc. In other words, the optimization objects of the optimization and improvement strategy set include the materials, structures and processes of the key components of the steam turbine.

[0087] S306, performing structural optimization and improvement on key components of the steam turbine according to the structural optimization strategy set, and continuing to perform structural transient operating strength monitoring on structural transient strength design monitoring data of key components of the steam turbine.

[0088] In the embodiment of the present disclosure, after the key components of the steam turbine are structurally optimized based on the structural optimization strategy set, the yield strength R of the material at the transient operating temperature of the key components of the steam turbine is re-obtained. t p0.2jk , the maximum equivalent stress S of key components eqjk If the strength basic data of the steam turbine still does not meet the first monitoring qualification condition, the structural optimization strategy set is updated, and the structural optimization of the key components of the steam turbine is continued based on the updated structural optimization strategy set.

[0089] In the embodiment of the present disclosure, the key components of the steam turbine are structurally optimized and improved according to the structural optimization strategy set, and the yield strength R of the material of the key components of the steam turbine at the transient operating temperature is re-obtained. t p0.2jk , the maximum equivalent stress S of key components eqjk If the re-acquired data meets the first monitoring qualification condition, the structural transient strength design monitoring of the key components of the steam turbine is terminated; if the re-acquired data still does not meet the first monitoring qualification condition, the optimization intensity of the structural optimization strategy set is increased.

[0090] Furthermore, the key components of the steam turbine are structurally optimized based on the updated structural optimization strategy set, and the yield strength R of the material of the key components of the steam turbine at the transient operating temperature is further obtained. t p0.2jk , the maximum equivalent stress S of key components eqjk The strength basic data of the steam turbine is obtained, and when the first design monitoring data does not meet the first monitoring qualification condition, the structural optimization strategy set is updated again and the structural optimization and improvement of the key components of the steam turbine are performed until the first monitoring qualification condition is met.

[0091] In the multi-dimensional monitoring platform for the flexibly operating steam turbine provided in the embodiment of the present disclosure, by obtaining the structural transient strength monitoring data of the key components of the steam turbine under the target operating conditions, and optimizing and improving the structural design of the key components of the steam turbine when the structural transient strength monitoring data under the target operating conditions does not meet the monitoring qualification conditions, the structural transient strength of the key components of the flexibly operating steam turbine under the target operating conditions is under controlled state, thereby ensuring the long life and high flexibility of the design of the flexible operating steam turbine from the aspect of designing the structural transient strength.

[0092] For example, based on a certain type of ultra-supercritical 1050MW single-reheat steam turbine, the maximum equivalent stress S under the target operating condition is calculated. eqjk , material yield strength R at transient working temperature t p0.2jk and stress ratio R sjk The results are listed in Table 1.

[0093] Table 1 Structural transient strength design monitoring of key components of ultra-supercritical 1050MW steam turbine under target operating conditions

[0094]

[0095] Optionally, based on Table 1 above, the first design monitoring data of the structural transient strength of the high-pressure cylinder of the ultra-supercritical 1050MW steam turbine of this model under the target operating condition can be determined, and the result that meets the first monitoring qualification condition is (R sHV=0.41<1)∩(R sHR =0.50<1)∩(R sHC =0.96<1).

[0096] Optionally, based on the above Table 1, the first design monitoring data of the structural transient strength of the intermediate pressure cylinder of the ultra-supercritical 1050MW steam turbine of this model under the target operating condition can be determined, and the result that meets the first monitoring qualification condition is (R sIV =0.66<1)∩(R sIR =0.50<1)∩(R sIC =0.83<1).

[0097] Optionally, based on the above Table 1, the first design monitoring data of the structural transient strength of the low-pressure cylinder of the ultra-supercritical 1050MW steam turbine of this model under the target operating condition can be determined, and the result that meets the first monitoring qualification condition is (R sLR =0.35<1)∩(R sLC =0.92<1).

[0098] When the first design monitoring data of the structural transient strength of key components such as the high-pressure cylinder, intermediate-pressure cylinder and low-pressure cylinder of this type of ultra-supercritical 1050MW steam turbine is qualified under the target operating conditions, indicating that the structural transient strength of this type of ultra-supercritical 1050MW steam turbine under the target operating conditions is under control, the subsequent monitoring process will be entered.

[0099] Based on the above implementation, the disclosed embodiment can explain the process of monitoring the life-related design of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine under the target working conditions, such as Figure 4 As shown, the process of monitoring the life-related design of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine under the target operating conditions includes the following steps:

[0100] S401, obtaining basic data of design life of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine under target operating conditions.

[0101] In the disclosed embodiment, the key components include a high-pressure valve housing, a high-pressure rotor, a high-pressure cylinder, a medium-pressure valve housing, a medium-pressure rotor, and a medium-pressure cylinder. The basic design life data of the high-pressure cylinder and the medium-pressure cylinder of the steam turbine under the target working condition can be determined by obtaining the low-cycle fatigue crack initiation life of the cold start-stop, the low-cycle fatigue crack initiation life of the warm start-stop, the low-cycle fatigue crack initiation life of the hot start-stop, the low-cycle fatigue crack initiation life of the extremely hot start-stop, the low-cycle fatigue crack initiation life of the 20% to 100% load change climbing, and the creep crack initiation life of the key components.

[0102] Optionally, the low-cycle fatigue crack initiation life N of the high-pressure valve shell during cold start-stop can be obtained. cHV , Low cycle fatigue crack initiation life of high pressure valve shell during warm start-stop NwHV , High-pressure valve shell hot start-stop low-cycle fatigue crack initiation life N hHV , High-pressure valve shell extremely hot start-stop low-cycle fatigue crack initiation life N vHV , High-pressure valve shell 20% ~ 100% load change climbing low cycle fatigue crack initiation life N 20％HV , creep crack initiation life of high pressure valve shell τ cHV .

[0103] Optionally, the low-cycle fatigue crack initiation life N of the high-pressure rotor during cold start-stop can be obtained. cHR , High-pressure rotor warm start-stop low-cycle fatigue crack initiation life N wHR , High-pressure rotor hot start-stop low-cycle fatigue crack initiation life N hHR , High-pressure rotor extremely hot start-stop low-cycle fatigue crack initiation life N vHR 、High-pressure rotor 20%~100% load change climbing low cycle fatigue crack initiation life N 20％HR , high pressure rotor creep crack initiation life τ cHR .

[0104] Optionally, the low-cycle fatigue crack initiation life N of the high-pressure cylinder during cold start-stop can be obtained. cHC , Low cycle fatigue crack initiation life of high pressure cylinder at warm start and stop N wHC , High-pressure cylinder hot start-stop low-cycle fatigue crack initiation life N hHC , High-pressure cylinder extremely hot start-stop low-cycle fatigue crack initiation life N vHC 、High-pressure cylinder 20%~100% load change climbing low cycle fatigue crack initiation life N 20％HC , creep crack initiation life of high pressure cylinder τ cHC .

[0105] Optionally, the low-cycle fatigue crack initiation life N of the medium-pressure valve shell during cold start-stop can be obtained. cIV , Medium pressure valve shell warm start-stop low cycle fatigue crack initiation life N wIV , Medium pressure valve shell hot start-stop low cycle fatigue crack initiation life N hIV , Medium pressure valve shell extremely hot start and stop low cycle fatigue crack initiation life N vIV , Medium pressure valve shell 20% ~ 100% load change climbing low cycle fatigue crack initiation life N 20％IV , creep crack initiation life of medium pressure valve shell τ cIV .

[0106] Optionally, the low-cycle fatigue crack initiation life N of the medium-pressure rotor during cold start-stop can be obtained. cIR , Low cycle fatigue crack initiation life of medium pressure rotor during warm start-stop N wIR , Low cycle fatigue crack initiation life of medium pressure rotor during hot start and stop N hIR, Low cycle fatigue crack initiation life of medium pressure rotor during extremely hot start and stop N vIR 、Intermediate pressure rotor 20% ~ 100% load change climbing low cycle fatigue crack initiation life N 20％IR , creep crack initiation life of medium pressure rotor τ cIR .

[0107] Optionally, the low-cycle fatigue crack initiation life N of the medium-pressure cylinder during cold start-stop can be obtained. cIC , Medium pressure cylinder warm start-stop low cycle fatigue crack initiation life N wIC , Medium pressure cylinder hot start-stop low cycle fatigue crack initiation life N hIC , Medium pressure cylinder extremely hot start-stop low cycle fatigue crack initiation life N vIC 、 Medium pressure cylinder 20% ~ 100% load change climbing low cycle fatigue crack initiation life N 20％IC , creep crack initiation life of medium pressure cylinder τ cIC .

[0108] Where N is the low cycle fatigue crack initiation life, τ c Indicates creep crack initiation life, H indicates high pressure, I indicates medium pressure, V indicates valve housing, R indicates rotor, and C indicates cylinder. c indicates cold start and stop, w indicates warm start and stop, h indicates hot start and stop, v indicates extremely hot start and stop, and 20% indicates 20% to 100% load change.

[0109] S402, obtaining basic data of design operation targets of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine under target operating conditions.

[0110] Optionally, the number of cold starts of the steam turbine n can be obtained c0 , Number of warm-state starts of steam turbine n w0 , Number of hot starts of steam turbine n h0 、Number of extremely hot start-ups of the steam turbine v0 、The number of times the turbine load changes from 20% to 100% is n 20％0 , Annual average operating hours of steam turbine t y , the design criterion value τ0 of the total calendar life of the turbine, which serves as the basic data for the design and operation of the high-pressure cylinder and the intermediate-pressure cylinder of the turbine under the target operating conditions.

[0111] Where n represents the number of starts, t y It represents the annual average operating hours, c represents cold start and stop, w represents warm start and stop, h represents hot start and stop, v represents extremely hot start and stop, and 20% represents 20% to 100% load change.

[0112] S403, determine the crack initiation calendar life τ of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine jk .

[0113] In the embodiment of the present disclosure, τ represents the crack initiation calendar life, subscript j represents the working environment of the key component, and subscript k represents the name of the steam turbine component. The crack initiation calendar life τ of the steam turbine high-pressure cylinder and the medium-pressure cylinder can be determined based on the design life basic data and the design operation target basic data of the steam turbine high-pressure cylinder and the medium-pressure cylinder under the target working condition. jk .

[0114] Alternatively, the crack initiation calendar life τ of the high pressure valve casing of the steam turbine HV The calculation formula is

[0115] Alternatively, the crack initiation calendar life τ of the high pressure rotor of the steam turbine HR The calculation formula is

[0116] Alternatively, the crack initiation calendar life τ of the high pressure cylinder of the steam turbine HC The calculation formula is

[0117] Optionally, the crack initiation calendar life τ of the medium pressure valve casing of the steam turbine IV The calculation formula is

[0118] Optionally, the crack initiation calendar life τ of the intermediate pressure rotor of the steam turbine IR The calculation formula is

[0119] Optionally, the crack initiation calendar life τ of the medium pressure cylinder of the steam turbine IC The calculation formula is

[0120] Where, τ represents the crack initiation calendar life, n represents the number of starts, τ0 represents the design criterion value of the total calendar life of the turbine, N represents the low-cycle fatigue crack initiation life, t y represents the annual average operating hours, τ c represents creep crack initiation life, H represents high pressure, I represents medium pressure, V represents valve housing, R represents rotor, and C represents cylinder. Subscript 0 represents basic data of turbine design operation target, c represents cold start and stop, w represents warm start and stop, h represents hot start and stop, v represents extremely hot start and stop, and 20% represents 20% to 100% load change.

[0121] S404, determining whether the life designs of the high-pressure cylinder and the medium-pressure cylinder meet the second monitoring qualification condition.

[0122] In the disclosed embodiment, the second monitoring qualified condition of the high-pressure cylinder refers to that the crack initiation calendar life of the high-pressure valve casing, the high-pressure rotor, and the high-pressure cylinder are all greater than the design criterion value of the total calendar life of the turbine; the second monitoring qualified condition of the medium-pressure cylinder refers to that the crack initiation calendar life of the medium-pressure valve casing, the medium-pressure rotor, and the medium-pressure cylinder are all greater than the design criterion value of the total calendar life of the turbine.

[0123] That is to say, the crack initiation calendar life design of the high-pressure cylinder of the steam turbine meets the second monitoring qualification condition (τ HV ≥τ0)∩(τ HR ≥τ0)∩(τ HC ≥τ0); The crack initiation calendar life design of the intermediate pressure cylinder of the steam turbine meets the second monitoring qualification condition (τ IV ≥τ0)∩(τ IR ≥τ0)∩(τ IC ≥τ0).

[0124] Optionally, the life design of the crack initiation calendar of the steam turbine high-pressure cylinder does not meet the second monitoring qualification condition (τ HV <τ0)∪(τ HR <τ0)∪(τ HC <τ0); The calendar life design of the crack initiation of the intermediate pressure cylinder of the steam turbine does not meet the second monitoring qualification condition (τ IV <τ0)∪(τ IR <τ0)∩(τ IC <τ0).

[0125] S405: In response to the life design of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine not satisfying the second monitoring qualification condition, a set of structural optimization improvement strategies for the high-pressure cylinder and the intermediate-pressure cylinder is generated.

[0126] Optionally, a set of strategies for optimizing and improving the structure of the high-pressure cylinder and the intermediate-pressure cylinder of the turbine include: selecting materials with good high-temperature and long-term mechanical properties; selecting materials with good low-cycle fatigue performance; adopting a whole rotor structure; using a cylindrical cylinder for coal-fired steam turbines; using thin-walled cylinders and high and narrow flanges for combined cycle steam turbines and solar thermal steam turbines; installing electric heating tape, insulation clothing and insulation structure on the outer surface of the outer cylinder; avoiding the use of structures that cause stress concentration in high stress areas; using structural fillet transitions at structural discontinuities; increasing the radius of structural fillets to reduce the stress concentration coefficient; designing the weld location away from stress concentration points; using heat treatment processes to improve material toughness; improving processing accuracy and eliminating machining stress concentration; using heat treatment processes to reduce welding residual tensile stress; surface shot peening to improve low-cycle fatigue performance, etc.

[0127] S406: Structural optimization and improvement of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine are performed according to the structural optimization strategy set.

[0128] In the disclosed embodiment, after structural optimization is performed on key components of the steam turbine based on the structural optimization strategy set, the life-related design monitoring data of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine are reacquired. If the second monitoring qualification condition is still not met, the structural optimization strategy set is updated, and based on the updated structural optimization strategy set, the structural optimization of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine is continued.

[0129] Optionally, after optimizing the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine according to the structural optimization strategy set, the life-related design monitoring data of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine are re-acquired. If the second design monitoring qualified condition is met, the design monitoring of the crack initiation calendar life of the high-pressure cylinder and the intermediate-pressure cylinder is terminated; if the second design monitoring qualified condition is not met, the optimization intensity of the structural optimization strategy set is increased.

[0130] Furthermore, the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine are structurally optimized based on the updated structural optimization strategy set, and the design monitoring data related to the life of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine are continuously obtained for monitoring, and when the design monitoring data related to the life of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine does not meet the second monitoring qualified condition, the structural optimization strategy set is updated again and the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine are structurally optimized until the crack initiation calendar life of the high-pressure cylinder and the intermediate-pressure cylinder meets the second design monitoring qualified condition.

[0131] In the multi-dimensional monitoring platform for flexibly operating steam turbines provided by the embodiments of the present disclosure, by obtaining the life-related design monitoring data of the high-pressure cylinder and the intermediate-pressure cylinder, and when the life-related design monitoring data of the high-pressure cylinder and the intermediate-pressure cylinder do not meet the second monitoring qualification condition, the structural design optimization and improvement of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine are performed, so that the design life of the high-pressure cylinder and the intermediate-pressure cylinder of the steam turbine is under control, thereby ensuring the long life and high flexibility of the steam turbine design in terms of the design life of the high-pressure cylinder and the intermediate-pressure cylinder.

[0132] As an example, based on a certain type of ultra-supercritical 1050MW single-reheat steam turbine, the basic data of the design and operation targets of the key components of this type of steam turbine are listed in Table 2.

[0133] Table 2 Basic data of steam turbine design and operation targets

[0134] project Numeric <![CDATA[Number of cold starts of steam turbine n c0 (times)]]> 300 <![CDATA[Number of warm starts of steam turbine n w0 (times)]]> 1500 <![CDATA[Number of warm starts of steam turbine n h0 (times)]]> 7900 <![CDATA[Number of extremely hot start-ups of steam turbine n v0 (times)]]> 300 <![CDATA[Number of ramps n for steam turbine load changes from 20% to 100% 20％0 (times)]]> 16000 <![CDATA[Annual average operating hours t of steam turbine y (h)]]> 7000 <![CDATA[Calendar total life design criterion value τ0 (year) of steam turbine]]> 40

[0135] The basic data of design life of high-pressure valve casing of this type of ultra-supercritical 1050MW single-reheat steam turbine are calculated and listed in Table 3, the basic data of design life of high-pressure rotor are listed in Table 4, and the basic data of design life of high-pressure cylinder are listed in Table 5.

[0136] Table 3 Basic data of design life of high pressure valve casing of ultra-supercritical 1050MW single reheat steam turbine

[0137] project Numeric <![CDATA[Low cycle fatigue crack initiation life N of high-pressure valve housing during cold start and stop cHV (times)]]> 35499 <![CDATA[Low cycle fatigue crack initiation life N of high-pressure valve housing during warm start and stop wHV (times)]]> 7210 <![CDATA[Low cycle fatigue crack initiation life N of high-pressure valve housing during hot start and stop hHV (times)]]> 159230 <![CDATA[Low cycle fatigue crack initiation life N of the high-pressure valve housing during extremely hot start and stop]] vHV (times)]]> 1000000 <![CDATA[Low cycle fatigue crack initiation life N (times) of high-pressure valve housing under 20% - 100% load change ramp-up 20％HV (times)]]> 190114 <![CDATA[Creep crack initiation life τ of high-pressure valve housing cHV (h)]]> <![CDATA[4.51×10 7 ]]>

[0138] Table 4 Basic data of design life of high pressure rotor of ultra-supercritical 1050MW single reheat steam turbine

[0139] project Numeric <![CDATA[Low cycle fatigue crack initiation life N of high-pressure rotor during cold start and stop cHR (times)]]> 40168 <![CDATA[Low cycle fatigue crack initiation life N of the high-pressure rotor during warm start and stop wHR (times)]]> 38256 <![CDATA[Low cycle fatigue crack initiation life N of the high-pressure rotor during hot start and stop hHR (times)]]> 38580 <![CDATA[Low cycle fatigue crack initiation life N of the high-pressure rotor pole during hot start and stop vHR (times)]]> 108814 <![CDATA[Low cycle fatigue crack initiation life N of high-pressure rotor during 20% - 100% load change ramp-up 20％HR (times)]]> 112486 <![CDATA[High-pressure rotor creep crack initiation life τ cHR (h)]]> 7010340

[0140] Table 5 Basic data of design life of high pressure cylinder of ultra-supercritical 1050MW single reheat steam turbine

[0141]

[0142]

[0143] The basic data of the design life of the medium-pressure valve casing of this type of ultra-supercritical 1050MW single-reheat steam turbine are calculated and listed in Table 6, the basic data of the design life of the medium-pressure rotor are listed in Table 7, and the basic data of the design life of the medium-pressure cylinder are listed in Table 8.

[0144] Table 6 Basic data of design life of medium pressure valve casing of ultra-supercritical 1050MW single reheat steam turbine

[0145] project Numeric <![CDATA[Cold start and stop low-cycle fatigue crack initiation life N of medium-pressure valve housing cIV (times)]]> 18182 <![CDATA[Low cycle fatigue crack initiation life N of medium pressure valve housing during warm start and stop wIV (times)]]> 19411 <![CDATA[Low cycle fatigue crack initiation life N of the medium-pressure valve housing during hot start and stop hIV (times)]]> 36363 <![CDATA[Low cycle fatigue crack initiation life N of medium pressure valve housing during extremely hot start and stop vIV (times)]]> 100000 <![CDATA[Low cycle fatigue crack initiation life N of the medium-pressure valve housing under 20% - 100% load change ramp-up 20％IV (times)]]> 250000 <![CDATA[Creep crack initiation life τ of medium-pressure valve housing cIV (h)]]> <![CDATA[1.27×10 8 ]]>

[0146] Table 7 Basic data of design life of intermediate pressure rotor of ultra-supercritical 1050MW single reheat steam turbine

[0147] project Numeric <![CDATA[Low cycle fatigue crack initiation life N of medium pressure rotor during cold start and stop cIR (times)]]> 28824 <![CDATA[Medium-pressure rotor warm-state start-stop low-cycle fatigue crack initiation life N wIR (times)]]> 22500 <![CDATA[Low cycle fatigue crack initiation life N of medium pressure rotor during hot start and stop hIR (times)]]> 26667 <![CDATA[Medium-pressure rotor pole hot state start-stop low cycle fatigue crack initiation life N vIR (times)]]> 41428 <![CDATA[Low-cycle fatigue crack initiation life N of the medium-pressure rotor during the 20% - 100% load change ramp-up 20％IR (cycles)]]> 210000 <![CDATA[Creep crack initiation life τ of the intermediate pressure rotor cIR (h)]]> <![CDATA[7.00×10 8 ]]>

[0148] Table 8 Basic data of design life of medium pressure cylinder of ultra-supercritical 1050MW single reheat steam turbine

[0149] project Numeric <![CDATA[Low cycle fatigue crack initiation life N of medium pressure cylinder in cold start and stop cIC (times)]]> 36923 <![CDATA[Low cycle fatigue crack initiation life N of warm start and stop of medium pressure cylinder wIC (times)]]> 21110 <![CDATA[Low cycle fatigue crack initiation life N of medium pressure cylinder during hot start-up and shutdown hIC (times)]]> 41667 <![CDATA[Low cycle fatigue crack initiation life N of the intermediate pressure cylinder during extremely hot start-up and shutdown vIC (times)]]> 120000 <![CDATA[Low-cycle fatigue crack initiation life N of medium-pressure cylinder under 20% - 100% load change ramp-up 20％IC (times)]]> 450000 <![CDATA[Creep crack initiation life τ of the medium-pressure cylinder cIC (h)]]> <![CDATA[8.00×10 8 ]]>

[0150] Optionally, based on the above Table 3, the calendar life τ of the crack initiation of the high-pressure valve casing of the ultra-supercritical 1050MW single-reheat steam turbine of this model can be determined: HV The calculation result is:

[0151]

[0152] Optionally, based on the above Table 4, the crack initiation calendar life τ of the high-pressure rotor of the ultra-supercritical 1050MW single-reheat steam turbine of this model can be determined: HR The calculation result is:

[0153]

[0154] Optionally, based on the above Table 5, the crack initiation calendar life τ of the high-pressure cylinder of the ultra-supercritical 1050MW single-reheat steam turbine of this model can be determined: HC The calculation result is:

[0155]

[0156] Optionally, based on the above Table 6, the crack initiation calendar life τ of the medium-pressure valve casing of the ultra-supercritical 1050MW single-reheat steam turbine of this model can be determined: IV The calculation result is:

[0157]

[0158] Optionally, based on the above Table 7, the crack initiation calendar life τ of the intermediate pressure rotor of the ultra-supercritical 1050MW single-reheat steam turbine of this model can be determined: IR The calculation result is:

[0159]

[0160] Optionally, based on the above Table 8, the crack initiation calendar life τ of the medium-pressure cylinder of the ultra-supercritical 1050MW single-reheat steam turbine of this model can be determined: IC The calculation result is:

[0161]

[0162] Optionally, based on the above calculation results, it can be determined that the life design of the high-pressure cylinder of the ultra-supercritical 1050MW steam turbine of this model meets the second monitoring qualification condition as follows:

[0163] (τ HV =84.09≥τ0=40)∩(τ HR =68.75≥τ0=40)∩(τ HC =85.15≥τ0=40)

[0164] Optionally, based on the above calculation results, it can be determined that the life design of the intermediate pressure cylinder of the ultra-supercritical 1050MW steam turbine of this model meets the second monitoring qualification condition as follows:

[0165] (τ IV =78.90≥τ0=40)∩(τ IR =65.62≥τ0=40)∩(τ IC =97.66≥τ0=40)

[0166] In summary, the life design monitoring of the high-pressure cylinder and the intermediate-pressure cylinder of this model of ultra-supercritical 1050MW steam turbine is qualified under the target operating conditions, indicating that the life of the high-pressure cylinder and the intermediate-pressure cylinder of this model of ultra-supercritical 1050MW steam turbine is under control under the target operating conditions, and the subsequent monitoring process is entered.

[0167] Based on the above implementation, the disclosed embodiment can explain the process of monitoring the life-related design of the low-pressure cylinder of the steam turbine under the target working condition, such as Figure 5 As shown, the process of monitoring the life-related design of the low-pressure cylinder of the steam turbine under the target operating conditions includes the following steps:

[0168] S501, obtaining basic data of the design life of the low-pressure cylinder of the steam turbine under target operating conditions.

[0169] In the disclosed embodiment, the key components include a low-pressure rotor and a low-pressure cylinder. The basic design life data of the low-pressure cylinder of the steam turbine under the target working condition can be determined by obtaining the low-cycle fatigue crack initiation life of the key components during cold start-stop, warm start-stop, hot start-stop, extremely hot start-stop, and 20% to 100% load change climbing.

[0170] Optionally, the low-pressure rotor cold start-stop low-cycle fatigue crack initiation life N can be obtained cLR , Low-pressure rotor warm start-stop low-cycle fatigue crack initiation life N wLR , Low-pressure rotor hot start-stop low-cycle fatigue crack initiation life N hLR , Low-pressure rotor extremely hot start-stop low cycle fatigue crack initiation life N vLR 、Low cycle fatigue crack initiation life of low pressure rotor with 20% to 100% load change climbing N 20％LR .

[0171] Optionally, the low-pressure cylinder cold start-stop low-cycle fatigue crack initiation life N can be obtained cLC , Low-pressure cylinder warm start-stop low cycle fatigue crack initiation life N wLC , Low-pressure cylinder hot start-stop low-cycle fatigue crack initiation life N hLC , Low-pressure cylinder extremely hot start-stop low cycle fatigue crack initiation life N vLC 、Low-pressure cylinder 20%~100% load change climbing low cycle fatigue crack initiation life N 20％LC .

[0172] Among them, N represents the low-cycle fatigue crack initiation life, L represents low pressure, R represents rotor, and C represents cylinder. c represents cold start and stop, w represents warm start and stop, h represents hot start and stop, v represents extremely hot start and stop, and 20% represents 20% to 100% load change.

[0173] S502, obtaining the basic data of the design operation target of the low-pressure cylinder of the steam turbine under the target working condition.

[0174] Optionally, the number of cold starts of the steam turbine n can be obtained c0 , Number of warm-state starts of steam turbine n w0, Number of hot starts of steam turbine n h0 、Number of extremely hot start-ups of the steam turbine v0 、The number of times the turbine load changes from 20% to 100% is n 20％0 , the design criterion value τ0 of the total calendar life of the turbine, which serves as the basic data for the design and operation of the high-pressure cylinder and the intermediate-pressure cylinder of the turbine under the target operating conditions.

[0175] Where n represents the number of starts, t y It represents the annual average operating hours, c represents cold start and stop, w represents warm start and stop, h represents hot start and stop, v represents extremely hot start and stop, and 20% represents 20% to 100% load change.

[0176] S503, determine the crack initiation calendar life τ of the low-pressure cylinder of the steam turbine under the target working condition jk .

[0177] In the embodiment of the present disclosure, τ represents the crack initiation calendar life, subscript j represents the working environment of the key component, and subscript k represents the name of the steam turbine component. The crack initiation calendar life τ of the steam turbine low-pressure cylinder can be determined based on the design life basic data and the design operation target basic data of the steam turbine low-pressure cylinder under the target working condition. jk .

[0178] Alternatively, the crack initiation calendar life τ of the low-pressure rotor of the steam turbine LR The calculation formula is

[0179] Optionally, the crack initiation calendar life τ of the low-pressure cylinder of the steam turbine under the target operating condition LC The calculation formula is

[0180] Among them, τ represents the crack initiation calendar life, n represents the number of starts, τ0 represents the total calendar life design criterion value of the turbine, N represents the low-cycle fatigue crack initiation life, L represents low pressure, R represents rotor, and C represents cylinder. Subscript 0 represents the basic data of the turbine design operation target, c represents cold start and stop, w represents warm start and stop, h represents hot start and stop, v represents extremely hot start and stop, and 20% represents 20% to 100% load change.

[0181] S504, determining whether the life design of the low-pressure cylinder meets the second monitoring qualification condition.

[0182] In the disclosed embodiment, the second monitoring qualified condition of the low-pressure cylinder refers to that the crack initiation calendar life of the low-pressure rotor and the low-pressure cylinder is greater than the design criterion value of the total calendar life of the turbine.

[0183] That is to say, the life design of the low-pressure cylinder of the steam turbine meets the second monitoring qualification condition (τ LR ≥τ0)∩(τLC ≥τ0).

[0184] Optionally, the life design of the low-pressure cylinder of the steam turbine does not meet the second monitoring qualification condition (τ LR <τ0)∪(τ LC <τ0).

[0185] S505: In response to the life design of the low-pressure cylinder of the steam turbine not satisfying the second monitoring qualification condition, a structural optimization strategy set of the low-pressure cylinder is generated.

[0186] Optionally, a set of optimization strategies for the steam turbine low-pressure cylinder structure includes: selecting materials with good stress corrosion resistance; selecting materials with good low-cycle fatigue performance; adopting a welded rotor structure; adopting a whole-section rotor structure; avoiding structures that cause stress concentration in high-stress areas; adopting structural fillet transitions at structural discontinuities; increasing the radius of structural fillets to reduce stress concentration factors; designing weld locations away from high-stress areas; improving processing accuracy to eliminate machining stress concentration; adopting heat treatment processes to reduce welding residual tensile stress; and surface shot peening to improve low-cycle fatigue performance.

[0187] S506: Perform structural optimization and improvement on the low-pressure cylinder of the steam turbine according to the structural optimization strategy set.

[0188] In the disclosed embodiment, after the low-pressure cylinder of the steam turbine is structurally optimized based on the structural optimization strategy set, the design monitoring data related to the low-pressure cylinder and life of the steam turbine is re-acquired. If the second monitoring qualification condition of the low-pressure cylinder is still not met, the structural optimization strategy set is updated, and based on the updated structural optimization strategy set, the structural optimization of the low-pressure cylinder of the steam turbine is continued.

[0189] Optionally, the low-pressure cylinder of the steam turbine is optimized according to the structural optimization strategy set, and the design monitoring data related to the low-pressure cylinder of the steam turbine and the life are reacquired. If the second monitoring qualification condition is met, the life design monitoring of the low-pressure cylinder is terminated; if the second monitoring qualification condition is still not met, the optimization strength of the structural optimization strategy set is increased.

[0190] Furthermore, based on the updated structural optimization strategy set, the steam turbine low-pressure cylinder is structurally optimized and improved, and the life-related design monitoring data of the steam turbine low-pressure cylinder is continued to be obtained. When the life-related design monitoring data of the steam turbine low-pressure cylinder does not meet the second monitoring qualified condition, the structural optimization strategy set is updated again and the steam turbine low-pressure cylinder is structurally optimized and improved until the low-pressure cylinder crack initiation calendar life design monitoring qualified condition is met.

[0191] In the multi-dimensional monitoring platform for flexibly operating steam turbines provided by the embodiments of the present disclosure, by acquiring the design monitoring data related to the life of the low-pressure cylinder, and when the design monitoring data related to the life of the low-pressure cylinder does not meet the second monitoring qualification condition, the structural design of the low-pressure cylinder of the steam turbine is optimized, so that the design life of the low-pressure cylinder of the steam turbine under the target operating conditions is under control, thereby ensuring the long life and high flexibility of the steam turbine design from the aspect of the design life of the low-pressure cylinder.

[0192] As an example, based on a certain type of ultra-supercritical 1050MW single-reheat steam turbine, the basic data of the design and operation targets of the key components of this type of steam turbine are listed in Table 2, and the basic data of the design life of the low-pressure rotor of this type of ultra-supercritical 1050MW single-reheat steam turbine are calculated and listed in Table 9, and the basic data of the design life of the low-pressure cylinder are listed in Table 10.

[0193] Table 9 Basic data of design life of low-pressure rotor of ultra-supercritical 1050MW single-reheat steam turbine

[0194] project Numeric <![CDATA[Low-cycle fatigue crack initiation life N of the low-pressure rotor during cold start and stop cLR (times)]]> 3600 <![CDATA[Low cycle fatigue crack initiation life N of the low-pressure rotor during warm start and stop wLR (times)]]> 20000 <![CDATA[Low cycle fatigue crack initiation life N of the low pressure rotor during hot start and stop hLR (times)]]> 38000 <![CDATA[Low cycle fatigue crack initiation life N of the low-pressure rotor pole during hot start and stop vLR (times)]]> 50000 <![CDATA[Low cycle fatigue crack initiation life N of the low-pressure rotor under 20% - 100% load change ramp-up 20％LR (times)]]> 140000

[0195] Table 10 Basic data of design life of low pressure cylinder of ultra-supercritical 1050MW single reheat steam turbine

[0196] project Numeric <![CDATA[Low-cycle fatigue crack initiation life N of the low-pressure cylinder during cold start and stop cIC (times)]]> 15741 <![CDATA[Low-cycle fatigue crack initiation life N of warm start-up and shutdown of low-pressure cylinder wLC (times)]]> 50000 <![CDATA[Low cycle fatigue crack initiation life N of the low-pressure cylinder during hot start and stop hLC (times)]]> 50000 <![CDATA[Low cycle fatigue crack initiation life N of the low-pressure cylinder in extremely hot start-up and shutdown vLC (times)]]> 60000 <![CDATA[Low cycle fatigue crack initiation life N of low pressure cylinder under 20% - 100% load change ramp-up 20％LC (times)]]> 60000

[0197] Optionally, based on the above Table 9, the crack initiation calendar life τ of the low-pressure rotor of the ultra-supercritical 1050MW single-reheat steam turbine of this model can be determined: LR The calculation result is:

[0198]

[0199] Optionally, based on the above Table 10, the crack initiation calendar life τ of the low-pressure cylinder of the ultra-supercritical 1050MW single-reheat steam turbine of this model can be determined: LC The calculation result is:

[0200]

[0201] Optionally, the result of the life design of the low-pressure cylinder of the ultra-supercritical 1050MW steam turbine of this model meeting the second monitoring qualification condition is:

[0202] (τ LR =61.66≥τ0=40)∩(τ LC =62.67≥τ0=40)

[0203] In summary, when the low-pressure cylinder life design monitoring of this type of ultra-supercritical 1050MW steam turbine is qualified under the target operating conditions, it indicates that the low-pressure cylinder life of this type of ultra-supercritical 1050MW steam turbine is under control under the target operating conditions, and then enters the subsequent monitoring process.

[0204] Based on the above implementation, the disclosed embodiment can explain the process of operating monitoring of the crack initiation remaining calendar life of key components of the steam turbine under target operating conditions, such as Figure 6 As shown, the process of operating monitoring the crack initiation remaining calendar life of key components of a steam turbine under target operating conditions includes the following steps:

[0205] S601, obtain basic data on design life of key components of steam turbine.

[0206] In the disclosed embodiment, the key components of the steam turbine include but are not limited to: high-pressure valve housing, high-pressure rotor, high-pressure cylinder, medium-pressure valve housing, medium-pressure rotor, medium-pressure cylinder, low-pressure rotor, low-pressure cylinder, etc. The basic design life data of the key components of the steam turbine can be determined by obtaining the low-cycle fatigue crack initiation life of cold start-stop, low-cycle fatigue crack initiation life of warm start-stop, low-cycle fatigue crack initiation life of hot start-stop, low-cycle fatigue crack initiation life of extremely hot start-stop, low-cycle fatigue crack initiation life of 20% to 100% load change climbing, and creep crack initiation life of the key components.

[0207] Optionally, obtain the low-cycle fatigue crack initiation life N of the high-pressure valve shell during cold start-stop cHV , Low cycle fatigue crack initiation life of high pressure valve shell during warm start-stop N wHV , High-pressure valve shell hot start-stop low-cycle fatigue crack initiation life N hHV , High-pressure valve shell extremely hot start-stop low-cycle fatigue crack initiation life N vHV , High-pressure valve shell 20% ~ 100% load change climbing low cycle fatigue crack initiation life N 20％HV , creep crack initiation life of high pressure valve shell τ cHV .

[0208] Optionally, obtain the low-cycle fatigue crack initiation life N of the high-pressure rotor during cold start-stop cHR , High-pressure rotor warm start-stop low-cycle fatigue crack initiation life N wHR , High-pressure rotor hot start-stop low-cycle fatigue crack initiation life N hHR , High-pressure rotor extremely hot start-stop low-cycle fatigue crack initiation life N vHR 、High-pressure rotor 20%~100% load change climbing low cycle fatigue crack initiation life N 20％HR , high pressure rotor creep crack initiation life τ cHR .

[0209] Optionally, obtain the low-cycle fatigue crack initiation life N of the high-pressure cylinder during cold start-stop cHC , Low cycle fatigue crack initiation life of high pressure cylinder at warm start and stop N wHC , High-pressure cylinder hot start-stop low-cycle fatigue crack initiation life N hHC , High-pressure cylinder extremely hot start-stop low-cycle fatigue crack initiation life N vHC 、High-pressure cylinder 20%~100% load change climbing low cycle fatigue crack initiation life N 20％HC , creep crack initiation life of high pressure cylinder τ cHC .

[0210] Optionally, obtain the low-cycle fatigue crack initiation life N of the medium-pressure valve shell during cold start-stop cIV , Medium pressure valve shell warm start-stop low cycle fatigue crack initiation life N wIV , Medium pressure valve shell hot start-stop low cycle fatigue crack initiation life N hIV , Medium pressure valve shell extremely hot start and stop low cycle fatigue crack initiation life N vIV , Medium pressure valve shell 20% ~ 100% load change climbing low cycle fatigue crack initiation life N 20％IV , creep crack initiation life of medium pressure valve shell τ cIV .

[0211] Optionally, obtain the low-cycle fatigue crack initiation life N of the medium-pressure rotor during cold start-stop cIR , Low cycle fatigue crack initiation life of medium pressure rotor during warm start-stop N wIR , Low cycle fatigue crack initiation life of medium pressure rotor during hot start and stop N hIR , Low cycle fatigue crack initiation life of medium pressure rotor during extremely hot start and stop N vIR 、Intermediate pressure rotor 20% ~ 100% load change climbing low cycle fatigue crack initiation life N 20％IR , creep crack initiation life of medium pressure rotor τ cIR .

[0212] Optionally, obtain the low-cycle fatigue crack initiation life N of the medium-pressure cylinder during cold start-stop cIC , Medium pressure cylinder warm start-stop low cycle fatigue crack initiation life N wIC , Medium pressure cylinder hot start-stop low cycle fatigue crack initiation life N hIC , Medium pressure cylinder extremely hot start-stop low cycle fatigue crack initiation life N vIC 、 Medium pressure cylinder 20% ~ 100% load change climbing low cycle fatigue crack initiation life N 20％IC , creep crack initiation life of medium pressure cylinder τ cIC .

[0213] Optionally, obtain the low-pressure rotor cold start-stop low-cycle fatigue crack initiation life N cLR , Low-pressure rotor warm start-stop low-cycle fatigue crack initiation life NwLR , Low-pressure rotor hot start-stop low-cycle fatigue crack initiation life N hLR , Low-pressure rotor extremely hot start-stop low cycle fatigue crack initiation life N vLR 、Low cycle fatigue crack initiation life of low pressure rotor with 20% to 100% load change climbing N 20％LR .

[0214] Optionally, obtain the low-pressure cylinder cold start-stop low-cycle fatigue crack initiation life N cLC , Low-pressure cylinder warm start-stop low cycle fatigue crack initiation life N wLC , Low-pressure cylinder hot start-stop low-cycle fatigue crack initiation life N hLC , Low-pressure cylinder extremely hot start-stop low cycle fatigue crack initiation life N vLC 、Low-pressure cylinder 20%~100% load change climbing low cycle fatigue crack initiation life N 20％LC .

[0215] Where N is the low cycle fatigue crack initiation life, τ c Indicates creep crack initiation life, H indicates high pressure, I indicates medium pressure, L indicates low pressure, V indicates valve housing, R indicates rotor, and C indicates cylinder. c indicates cold start and stop, w indicates warm start and stop, h indicates hot start and stop, v indicates extremely hot start and stop, and 20% indicates 20% to 100% load change.

[0216] S602, obtaining basic data of steam turbine design and operation targets.

[0217] Optionally, the basic data of the steam turbine design operation target include: the number of cold start-ups of the steam turbine n c0 , Number of warm-state starts of steam turbine n w0 , Number of hot starts of steam turbine n h0 、Number of extremely hot start-ups of the steam turbine v0 、The number of times the turbine load changes from 20% to 100% is n 20％0 , annual average operating hours t y , design criterion value τ0 of total calendar life of turbine.

[0218] Among them, n represents the number of starts, c represents cold start and stop, w represents warm start and stop, h represents hot start and stop, v represents extremely hot start and stop, and 20% represents 20% to 100% load change.

[0219] S603, obtaining basic data of actual operation of the steam turbine.

[0220] Optionally, the actual operation basic data of the steam turbine include: the cumulative number of cold starts of the in-service steam turbine n c1 , cumulative number of warm starts n w1 , cumulative number of hot starts n h1, Accumulated number of extremely hot starts n v1 , cumulative 20% to 100% load change climbing times n 20％1 , cumulative running hours t SH , calendar life of the turbine in years from commissioning to date τ1.

[0221] Among them, n represents the number of starts, c represents cold start and stop, w represents warm start and stop, h represents hot start and stop, v represents extremely hot start and stop, and 20% represents 20% to 100% load change.

[0222] S604, determine the cumulative loss of crack initiation life L of key components of steam turbine ejk .

[0223] In the embodiment of the present disclosure, the cumulative loss L of the crack initiation life of the key components of the steam turbine can be determined based on the basic data of the design life of the key components of the steam turbine under the target working conditions and the basic data of the actual operation. ejk Among them, L e It represents the cumulative loss of crack initiation life, subscript j represents the working environment of key components, and subscript k represents the name of turbine components.

[0224] Optionally, the cumulative loss of crack initiation life of the high-pressure valve casing of the steam turbine is L eHV The calculation formula is:

[0225]

[0226] Optionally, the cumulative loss of crack initiation life of the high-pressure rotor of the steam turbine is L eHR The calculation formula is:

[0227]

[0228] Optionally, the cumulative loss of crack initiation life of the high-pressure cylinder of the steam turbine is L eHC The calculation formula is:

[0229]

[0230] Optionally, the cumulative loss of crack initiation life of the steam turbine medium-pressure valve casing L eIV The calculation formula is:

[0231]

[0232] Optionally, the cumulative loss of crack initiation life of the steam turbine intermediate pressure rotor L eIR The calculation formula is:

[0233]

[0234] Optionally, the cumulative loss of crack initiation life of the medium-pressure cylinder of the steam turbine is LeIC The calculation formula is:

[0235]

[0236] Optionally, the cumulative loss of the low-pressure rotor of the steam turbine during initiation life L eLR The calculation formula is:

[0237]

[0238] Optionally, the cumulative loss of the low-pressure cylinder of the steam turbine during initiation life L eLC The calculation formula is:

[0239]

[0240] Among them, L e represents the cumulative loss of crack initiation life, N represents the low cycle fatigue crack initiation life, τ c is the creep crack initiation life, t SH Indicates the cumulative number of operating hours, n indicates the number of starts, subscript 1 indicates the actual basic operating data of the turbine, H indicates high pressure, I indicates medium pressure, L indicates low pressure, V indicates valve housing, R indicates rotor, and C indicates cylinder. c indicates cold start and stop, w indicates warm start and stop, h indicates hot start and stop, v indicates extremely hot start and stop, and 20% indicates 20% to 100% load change.

[0241] S605, determine the average annual crack initiation life loss of key components of steam turbines jk .

[0242] In the embodiment of the present disclosure, the annual average crack initiation life loss e of the key components of the steam turbine can be determined based on the design life basic data and the design operation target basic data of the key components of the steam turbine under the target working conditions. jk Among them, e represents the annual average crack initiation life loss, subscript j represents the working environment of key components, and subscript k represents the name of the turbine component.

[0243] Optionally, the average annual crack initiation life loss of the high-pressure valve casing of the steam turbine is e HV The calculation formula is:

[0244]

[0245] Optionally, the average annual crack initiation life loss of the high-pressure rotor of the steam turbine is e HR The calculation formula is:

[0246]

[0247] Alternatively, the average annual crack initiation life loss of the high-pressure cylinder of the steam turbine is e HC The calculation formula is:

[0248]

[0249] Optionally, the average annual crack initiation life loss of the medium-pressure valve casing of the steam turbine is e IV The calculation formula is:

[0250]

[0251] Optionally, the average annual crack initiation life loss of the steam turbine intermediate pressure rotor is IR The calculation formula is:

[0252]

[0253] Optionally, the average annual crack initiation life loss of the medium-pressure cylinder of the steam turbine is e IC The calculation formula is:

[0254]

[0255] Alternatively, the average annual crack initiation life loss of the low-pressure rotor of the steam turbine is e LR The calculation formula is:

[0256]

[0257] Alternatively, the average annual crack initiation life loss of the low-pressure cylinder of the steam turbine is e LC The calculation formula is:

[0258]

[0259] Among them, e represents the annual average crack initiation life loss, N represents the low-cycle fatigue crack initiation life, subscript 0 represents the basic data of the turbine design operation target, n represents the number of starts, H represents high pressure, I represents medium pressure, L represents low pressure, V represents valve housing, R represents rotor, and C represents cylinder. c represents cold start and stop, w represents warm start and stop, h represents hot start and stop, v represents extremely hot start and stop, 20% represents 20% to 100% load change, and τ0 represents the design criterion value of the total calendar life of the turbine.

[0260] S606, determine the remaining calendar life of key components of the steam turbine before crack initiation.

[0261] In the embodiment of the present disclosure, the remaining calendar life τ of the key components of the steam turbine due to crack initiation can be determined based on the cumulative loss of the key components of the steam turbine due to crack initiation life and the annual average loss of the key components of the steam turbine due to crack initiation life. RLjk Among them, τ RL represents the remaining calendar life for crack initiation, subscript j represents the working environment of key components, and subscript k represents the name of turbine components.

[0262] Optionally, the remaining calendar life of the high-pressure valve casing of the turbine before crack initiation τ RLHV The calculation formula is Remaining calendar life of high pressure rotor of steam turbine before crack initiationτ RLHR The calculation formula is Remaining calendar life of crack initiation in high-pressure cylinder of steam turbine τ RLHC The calculation formula is

[0263] Optionally, the remaining calendar life of the steam turbine medium-pressure valve casing crack initiation τ RLIV The calculation formula is Remaining calendar life of steam turbine intermediate pressure rotor before crack initiationτ RLIR The calculation formula is Remaining calendar life of crack initiation in medium-pressure cylinder of steam turbine τ RLIC The calculation formula is

[0264] Optionally, the remaining calendar life of the low-pressure rotor of the steam turbine before crack initiation τ RLLR The calculation formula is Remaining calendar life of crack initiation in low-pressure cylinder of steam turbine τ RLLC The calculation formula is

[0265] Among them, τ RL represents the remaining calendar life of the key components of the steam turbine due to crack initiation, e represents the annual average crack initiation life loss of the key components of the steam turbine, L e It represents the cumulative loss of crack initiation life, H represents high pressure, I represents medium pressure, L represents low pressure, V represents valve housing, R represents rotor, and C represents cylinder.

[0266] S607, judging whether the crack initiation remaining calendar life of the key components of the target steam turbine in service meets the third monitoring qualification condition.

[0267] In the embodiment of the present disclosure, the remaining calendar life τ of the key components can be calculated based on the crack initiation residual calendar life τ of the key components. RL , the calendar life number of the turbine since it was put into operation τ1, the design criterion value of the total calendar life of the turbine τ0, and determine the third monitoring qualification condition.

[0268] Optionally, the remaining calendar life of the high-pressure cylinder of the steam turbine for crack initiation meets the third monitoring qualification condition:

[0269] Optionally, the remaining calendar life of the intermediate pressure cylinder of the steam turbine for crack initiation satisfies the third monitoring qualification condition:

[0270] Optionally, the remaining calendar life of the low-pressure cylinder of the steam turbine for crack initiation meets the third monitoring qualification condition:

[0271] Optionally, the remaining calendar life of the high-pressure cylinder of the steam turbine for crack initiation does not meet the third monitoring qualification condition:

[0272] Optionally, the remaining calendar life of the intermediate pressure cylinder of the steam turbine for crack initiation does not meet the third monitoring qualification condition:

[0273] Optionally, the remaining calendar life of the low-pressure cylinder crack initiation of the steam turbine does not meet the third monitoring qualification condition:

[0274] Among them, τ RL It represents the remaining calendar life of key components of steam turbine before crack initiation, τ1 represents the calendar life in years since the steam turbine was put into operation, τ0 represents the design criterion value of the total calendar life of the steam turbine, H represents high pressure, I represents medium pressure, L represents low pressure, V represents valve casing, R represents rotor, and C represents cylinder.

[0275] S608: In response to the crack initiation remaining calendar life operation monitoring of the key components of the target steam turbine in service not satisfying the third monitoring qualified condition, an optimized operation strategy for the target steam turbine in service is generated.

[0276] In the disclosed embodiment, if the remaining calendar life for crack initiation of key components of the target steam turbine in service does not meet the third monitoring qualification condition, it indicates that the number of starts in the operation stage is too large and the number of hot starts needs to be reduced.

[0277] Optionally, the design annual average number of hot states y h =n h0 / τ0 is reduced to y h1 =0.5~0.8×(n h0 / τ0), where n h0 is the number of hot starts of the steam turbine, τ0 is the design criterion value of the total calendar life of the steam turbine, and the operation monitoring of the target steam turbine in service is re-performed until the remaining calendar life operation monitoring of the key components of the target steam turbine in service meets the third monitoring qualification condition, and the operation optimization is ended.

[0278] In the multi-dimensional monitoring platform for flexible operation of steam turbines provided by the embodiment of the present disclosure, the target steam turbine in service is calculated by comparing the calendar life years τ1 from commissioning to date with the remaining calendar life τ1 of the key components after crack initiation. RLThe sum is compared with the design criterion value τ0 of the total calendar life of the steam turbine to determine whether the remaining calendar life of the key components of the in-service steam turbine is qualified for crack initiation. The operation of the unqualified steam turbines is optimized and controlled, thereby increasing the service life of the in-service steam turbines and ensuring their long life and high flexibility.

[0279] As an example, based on a certain type of in-service ultra-supercritical 1050MW single-reheat steam turbine, the basic data of the design and operation targets of the key components of this type of steam turbine are listed in Table 2. It is calculated that the basic data of the design life of the high-pressure valve case of this type of ultra-supercritical 1050MW single-reheat steam turbine are listed in Table 3, the basic data of the design life of the high-pressure rotor are listed in Table 4, the basic data of the design life of the high-pressure cylinder are listed in Table 5, the basic data of the design life of the medium-pressure valve case are listed in Table 6, the basic data of the design life of the medium-pressure rotor are listed in Table 7, the basic data of the design life of the medium-pressure cylinder are listed in Table 8, the basic data of the design life of the low-pressure rotor are listed in Table 9, and the basic data of the design life of the low-pressure cylinder are listed in Table 10.

[0280] Table 11 shows the actual operating basic data of an in-service ultra-supercritical 1050MW single-reheat steam turbine of this model.

[0281] Table 11 Basic data of actual operation of steam turbine

[0282] project Numeric <![CDATA[Accumulative number of cold starts of steam turbine n c1 (times)]]> 80 <![CDATA[Accumulative warm start times n of steam turbine w1 (times)]]> 400 <![CDATA[Accumulative number of warm / hot starts of steam turbine n h1 (times)]]> 2500 <![CDATA[Accumulative number of hot - state starts of steam turbine n h1 (times)]]> 120 <![CDATA[The cumulative number of load change ramp-ups n of the steam turbine from 20% to 100% load 20％0 (times)]]> 5000 <![CDATA[The cumulative operating hours t of the steam turbine SH (h)]]> 71000 <![CDATA[Number of calendar years τ1 (years) since the steam turbine was put into operation]]> 10

[0283] Optionally, the cumulative loss of crack initiation life of the high-pressure valve casing of the in-service ultra-supercritical 1050MW single-reheat steam turbine L eHV The calculation result is:

[0284]

[0285] Optionally, the cumulative loss of crack initiation life of the high-pressure rotor of the in-service ultra-supercritical 1050MW once-reheat steam turbine is L eHR The calculation result is:

[0286]

[0287] Alternatively, the cumulative loss of crack initiation life L of the high-pressure cylinder of the in-service ultra-supercritical 1050MW single-reheat steam turbine is eHC The calculation result is:

[0288]

[0289] Optionally, the cumulative loss of crack initiation life of the medium-pressure valve casing of the in-service ultra-supercritical 1050MW single-reheat steam turbine L eIV The calculation result is:

[0290]

[0291] Optionally, the cumulative loss of crack initiation life L of the intermediate pressure rotor of the in-service ultra-supercritical 1050MW single-reheat steam turbine is eIR The calculation result is:

[0292]

[0293] Optionally, the cumulative loss of crack initiation life L of the medium pressure cylinder of the in-service ultra-supercritical 1050MW single-reheat steam turbine is eIC The calculation result is:

[0294]

[0295] Optionally, the cumulative loss of crack initiation life of the low-pressure rotor of the in-service ultra-supercritical 1050MW single-reheat steam turbine is L eLR The calculation result is:

[0296]

[0297] Alternatively, the cumulative loss of crack initiation life of the low-pressure cylinder of the in-service ultra-supercritical 1050MW single-reheat steam turbine is L eLC The calculation result is:

[0298]

[0299] Optionally, the average annual crack initiation life loss of the high pressure valve casing of the in-service ultra-supercritical 1050MW single reheat steam turbine is e HV The calculation result is:

[0300]

[0301] Alternatively, the average annual crack initiation life loss of the high pressure rotor of the in-service ultra-supercritical 1050MW single-reheat steam turbine is e HR The calculation result is:

[0302]

[0303] Alternatively, the annual average crack initiation life loss of the high-pressure cylinder of the in-service ultra-supercritical 1050MW single-reheat steam turbine is HC The calculation result is:

[0304]

[0305] Alternatively, the average annual crack initiation life loss of the medium pressure valve casing of the in-service ultra-supercritical 1050MW single-reheat steam turbine is e IV The calculation result is:

[0306]

[0307] Alternatively, the average annual crack initiation life loss of the intermediate pressure rotor of the in-service ultra-supercritical 1050MW single-reheat steam turbine is e IR The calculation result is:

[0308]

[0309] Alternatively, the average annual crack initiation life loss of the intermediate pressure cylinder of the in-service ultra-supercritical 1050MW single-reheat steam turbine is e IC The calculation result is:

[0310]

[0311] Alternatively, the annual average crack initiation life loss of the low-pressure rotor of the in-service ultra-supercritical 1050MW single-reheat steam turbine is e LR The calculation result is:

[0312]

[0313] Alternatively, the annual average crack initiation life loss of the low-pressure cylinder of the in-service ultra-supercritical 1050MW single-reheat steam turbine is e LC The calculation result is:

[0314]

[0315] Optionally, the remaining calendar life τ of the high pressure valve casing crack initiation of the in-service ultra-supercritical 1050MW single reheat steam turbine RLHV The calculation result is:

[0316]

[0317] Optionally, the remaining calendar life τ of the high-pressure rotor crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine RLHR The calculation result is:

[0318]

[0319] Optionally, the remaining calendar life τ of the high-pressure cylinder crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine RLHC The calculation result is:

[0320]

[0321] Optionally, the remaining calendar life τ of the medium pressure valve casing crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine RLIV The calculation result is:

[0322]

[0323] Optionally, the remaining calendar life τ of the intermediate pressure rotor crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine RLIR The calculation result is:

[0324]

[0325] Optionally, the remaining calendar life τ of the intermediate pressure cylinder crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine RLIC The calculation result is:

[0326]

[0327] Optionally, the remaining calendar life τ of the low-pressure rotor crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine RLLR The calculation result is:

[0328]

[0329] Optionally, the remaining calendar life τ of the low-pressure cylinder crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine RLLC The calculation result is:

[0330]

[0331] Furthermore, the result that the remaining calendar life of the high-pressure cylinder crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine meets the third monitoring qualification condition is:

[0332]

[0333] Optionally, the result that the crack initiation remaining calendar life of the intermediate pressure cylinder of the in-service ultra-supercritical 1050MW single-reheat steam turbine meets the third monitoring qualification condition is:

[0334]

[0335] Optionally, the result that the remaining calendar life of the low-pressure cylinder crack initiation of the in-service ultra-supercritical 1050MW single-reheat steam turbine meets the third monitoring qualification condition is:

[0336]

[0337] That is to say, the calendar life of this in-service ultra-supercritical 1050MW single-reheat steam turbine since its commissioning is τ1=10 years, and the remaining calendar life of crack initiation of key components of this turbine meets the third monitoring qualification condition, indicating that the remaining calendar life of crack initiation of this type of ultra-supercritical 1050MW steam turbine since its commissioning is under control. Continuing to participate in deep peak regulation and flexible operation according to the existing number of turbine starts can ensure the long life and high flexibility of the turbine and enter the subsequent monitoring process.

[0338] Based on the above implementation, the disclosed embodiment can explain the operation monitoring process of the thermal stress judgment value of the key components of the steam turbine under the target working conditions, such as Figure 7 As shown in FIG. 1 , the operation monitoring process of the thermal stress determination value of the key components of the steam turbine under the target operating conditions includes the following steps:

[0339] S701, obtain the basic thermal stress data of key components of the target steam turbine in service.

[0340] In the embodiment of the present disclosure, the key components of the steam turbine include but are not limited to: high-pressure valve housing, high-pressure rotor, high-pressure cylinder, medium-pressure valve housing, medium-pressure rotor, medium-pressure cylinder, etc. The material elastic modulus E, material linear expansion coefficient α, Poisson's ratio μ, thermal stress monitoring parameter criterion value S can be obtained. th , the simulated calculated value of the rotor volume average temperature t m , determine the basic data of thermal stress of key components of turbine.

[0341] Optionally, the elastic modulus E of the material of the turbine rotor, valve housing and cylinder can be obtained: jk 、Linear expansion coefficient α jk and Poisson's ratio μ jk And the turbine component thermal stress monitoring parameter criterion value S corresponding to the turbine calendar total life design criterion value τ0 thjk The basic data of thermal stress, the simulation calculation value of the average rotor volume temperature of the turbine during startup, shutdown, load change and load operation t mjR .

[0342] Among them, subscript j represents the working environment of key components, and subscript k represents the name of turbine components.

[0343] Among them, E HV is the elastic modulus of the material of the high-pressure valve housing, E HR is the elastic modulus of the high-pressure rotor material, E HC is the elastic modulus of the material of the high-pressure cylinder, E IV is the elastic modulus of the medium pressure valve housing, E IR is the elastic modulus of the medium pressure rotor, E ICis the material elastic modulus of the medium-pressure cylinder. Among them, H represents high pressure, I represents medium pressure, V represents valve housing, C represents cylinder, and R represents rotor.

[0344] Among them, α HV is the linear expansion coefficient of the material of the high-pressure valve housing, α HR is the material linear expansion coefficient of the high pressure rotor, α HC is the material linear expansion coefficient of the high-pressure cylinder, α IV is the linear expansion coefficient of the medium pressure valve housing, α IR is the material linear expansion coefficient of the medium pressure rotor, α IC is the material linear expansion coefficient of the medium-pressure cylinder. Among them, H represents high pressure, I represents medium pressure, V represents valve housing, C represents cylinder, and R represents rotor.

[0345] Among them, μ HV is the Poisson's ratio of the material of the high-pressure valve shell, μ HR is the Poisson's ratio of the high-pressure rotor material, μ HC is the Poisson's ratio of the material of the high-pressure cylinder, μ IV is the Poisson's ratio of the material of the medium pressure valve housing, μ IR is the material Poisson’s ratio of the medium pressure rotor, μ IC is the Poisson's ratio of the material of the medium-pressure cylinder. Among them, H represents high pressure, I represents medium pressure, V represents valve housing, C represents cylinder, and R represents rotor.

[0346] Among them, S thHV is the thermal stress monitoring parameter criterion value of the high-pressure valve casing corresponding to the total calendar life design criterion value τ0 of the turbine, S thHR is the thermal stress monitoring parameter criterion value of the high-pressure rotor corresponding to τ0, S thHC is the thermal stress monitoring parameter criterion value of the high-pressure cylinder corresponding to τ0, S thIV is the thermal stress monitoring parameter criterion value of the medium pressure valve shell corresponding to τ0, S thIR is the thermal stress monitoring parameter criterion value of the medium pressure rotor corresponding to τ0, S thIC is the thermal stress monitoring parameter criterion value of the medium pressure cylinder corresponding to τ0. Wherein, H represents high pressure, I represents medium pressure, V represents valve housing, C represents cylinder, and R represents rotor.

[0347] Among them, t mHR is the simulated calculated value of the average volume temperature of the high-pressure rotor of the steam turbine, t mIR is the simulated calculated value of the average volume temperature of the medium-pressure rotor of the steam turbine, where H represents high pressure, I represents medium pressure, and R represents rotor.

[0348] S702, obtaining basic data of metal temperature at measuring points of key components of the target steam turbine in service.

[0349] Optionally, the basic data of the metal temperature at the measuring points of the key components include: the surface temperature t of the high-pressure rotor and the medium-pressure rotor represented by the metal temperature at the measuring point at the depth of 82% to 98% of the wall thickness of the high-pressure inner cylinder and the medium-pressure inner cylinder; jR0 , Metal temperature t at the measuring point where the wall thickness of high-pressure valve shell and medium-pressure valve shell is 82% to 98% jV90 , Metal temperature t of the measuring point at the depth of 40% to 60% of the wall thickness of the high-pressure valve shell and the medium-pressure valve shell jV50 , the surface temperature t of the high-pressure rotor and the intermediate-pressure rotor represented by the metal temperature at the measuring point at the depth of 82% to 98% of the wall thickness of the high-pressure inner cylinder and the intermediate-pressure inner cylinder jR0 , basic data of metal temperature at the measuring point at 40% to 60% depth of the wall thickness of high-pressure cylinder and medium-pressure starter jC50 . The subscript j represents the working environment of key components.

[0350] Optionally, basic data of metal temperature at the measuring point may be acquired based on the steam turbine digital electro-hydraulic control system DEH or the steam turbine control system TCS.

[0351] Among them, t HR0 The high-pressure rotor surface temperature, t IR0 It is the surface temperature of the medium-pressure rotor represented by the metal temperature of the measuring point at a depth of 82% to 98% of the medium-pressure inner cylinder wall thickness.

[0352] Among them, t HV90 The metal temperature of the measuring point at the depth of 82% to 98% of the high-pressure valve shell wall thickness, t IV90 The metal temperature of the measuring point at the depth of 82% to 98% of the medium pressure valve shell wall thickness; t HV50 The metal temperature at the measuring point where the high-pressure valve shell wall thickness is 40% to 60%, t IV50 The metal temperature of the measuring point at the depth of 40% to 60% of the medium pressure valve shell wall thickness; t HC90 The metal temperature at the measuring point where the wall thickness of the high-pressure cylinder is 82% to 98%, t IC90 The metal temperature of the measuring point at the depth of 82% to 98% of the medium pressure cylinder wall thickness; t HC50 The metal temperature at the measuring point where the wall thickness of the high-pressure cylinder is 40% to 60%, t IC50 It is the metal temperature of the measuring point at the depth of 40% to 60% of the high-pressure cylinder wall thickness. Among them, H represents high pressure, I represents medium pressure, V represents valve housing, and C represents cylinder.

[0353] S703, online calculation of the volume average temperature difference of key components under target working conditions.

[0354] In the disclosed embodiment, the volume average temperature difference of key components under target operating conditions can be calculated based on the metal temperature of the measuring points within two types of wall thickness depth ranges of the turbine.

[0355] Optionally, the metal temperature t of the measuring point at the depth of 82% to 98% of the wall thickness of the high-pressure valve shell of the steam turbine can be HV90 The metal temperature t of the measuring point at the depth of 40% to 60% of the high-pressure valve shell wall thickness HV50 Online monitoring value, online calculation of the average temperature difference Δt of the high-pressure valve casing of the steam turbine mHV , the calculation formula is as follows:

[0356] Δt mHV =|t HV50 -t HV90 |

[0357] Alternatively, the simulated calculated value t of the average volume temperature of the high-pressure rotor of the steam turbine can be mHR The high-pressure rotor surface temperature t is characterized by the metal temperature at the measuring point at a depth of 82% to 98% of the high-pressure inner cylinder wall thickness. HR0 , online calculation of the average volume temperature difference Δt of the high-pressure rotor of the steam turbine mHR , the calculation formula is as follows:

[0358] Δt mHR =|t mHR -t HR0 |

[0359] Optionally, the metal temperature t can be measured at a depth of 82% to 98% of the wall thickness of the high-pressure cylinder of the turbine. HC90 and the metal temperature t at the measuring point where the high-pressure cylinder wall thickness is 40% to 60% HC50 Online monitoring value, online calculation of the average temperature difference Δt of the high-pressure cylinder volume of the turbine mHC , the calculation formula is as follows:

[0360] Δt mHC =|t HC50 -t HC90 |

[0361] Optionally, the metal temperature t of the measuring point at the depth of 82% to 98% of the wall thickness of the medium-pressure valve shell of the steam turbine can be IV90 The metal temperature t of the measuring point at the depth of 40% to 60% of the medium pressure valve shell wall thickness IV50 Online monitoring value, online calculation of the average temperature difference Δt of the turbine medium pressure valve casing volume mIV , the calculation formula is as follows:

[0362] Δt mIV =|t IV50 -t IV90 |

[0363] Optionally, the simulated calculated value t of the average volume temperature of the intermediate pressure rotor of the steam turbine can be mIRand the surface temperature of the intermediate pressure rotor t represented by the metal temperature at the measuring point at the depth of 82% to 98% of the intermediate pressure inner cylinder wall thickness IR0 , online calculation of the average volume temperature difference Δt of the turbine intermediate pressure rotor mIR , the calculation formula is as follows:

[0364] Δt mIR =|t mIR -t IR0 |

[0365] Optionally, the metal temperature t can be measured at a depth of 82% to 98% of the wall thickness of the medium-pressure cylinder of the steam turbine. IC90 The metal temperature t of the measuring point at the depth of 40% to 60% of the medium pressure cylinder wall thickness IC50 Online monitoring value, online calculation of the average temperature difference Δt of the medium-pressure cylinder volume of the steam turbine mIC , the calculation formula is as follows:

[0366] Δt mIC =|t IC50 -t IC90 |

[0367] S704, online calculation of the temperature difference ratio of key components of the steam turbine.

[0368] In the disclosed embodiment, the temperature difference ratio of the key components of the steam turbine can be calculated based on the volume average temperature difference and thermal stress basic data of the key components.

[0369] Alternatively, the average temperature difference Δt of the high pressure valve casing volume can be calculated based on mHV , Elastic modulus E of the material of the high pressure valve housing HV , Linear expansion coefficient of high pressure valve housing material α HV , Poisson's ratio of the material of the high-pressure valve shell μ HV And the thermal stress monitoring parameter criterion value S of the high-pressure valve shell corresponding to τ0 thHV , online calculation of turbine high pressure valve casing temperature difference ratio R ΔtHV The calculation formula is:

[0370]

[0371] Alternatively, the high pressure rotor volume average temperature difference Δt mHR , material elastic modulus E of the high pressure rotor HR , Material linear expansion coefficient of high pressure rotor α HR , Poisson's ratio of the high-pressure rotor material μ HR And the thermal stress monitoring parameter criterion value S of the high-pressure rotor corresponding to τ0 thHR , online calculation of the turbine high pressure rotor temperature difference ratio R ΔtHR The calculation formula is:

[0372]

[0373] Alternatively, the average temperature difference Δt of the high pressure cylinder volume can be calculated based on mHC , Material elastic modulus E of high pressure cylinder HC , Material linear expansion coefficient of high pressure cylinder α HC , Poisson's ratio of high pressure cylinder material μ HC And the thermal stress monitoring parameter criterion value S of the high-pressure cylinder corresponding to τ0 thHC , online calculation of turbine high pressure cylinder temperature difference ratio R ΔtHC The calculation formula is:

[0374]

[0375] Optionally, the average temperature difference Δt of the medium pressure valve housing volume can be calculated based on mIV , Material elastic modulus E of medium pressure valve housing IV , Linear expansion coefficient of medium pressure valve housing material α IV , Poisson's ratio of the material of the medium pressure valve shell μ IV And the thermal stress monitoring parameter criterion value S of the medium pressure valve shell corresponding to τ0 thIV , online calculation of turbine medium pressure valve casing temperature difference ratio R ΔtIV The calculation formula is:

[0376]

[0377] Optionally, the average temperature difference Δt of the medium-pressure rotor volume can be calculated based on mIR , Material elastic modulus E of the medium pressure rotor IR , Material linear expansion coefficient of medium pressure rotor α IR , Poisson's ratio of the medium pressure rotor IR And the thermal stress monitoring parameter criterion value S of the medium pressure rotor corresponding to τ0 thIR , online calculation of turbine intermediate pressure rotor temperature difference ratio R ΔtIR The calculation formula is:

[0378]

[0379] Alternatively, the average temperature difference Δt of the medium pressure cylinder volume can be calculated based on mIC , Material elastic modulus E of medium pressure cylinder IC , Material linear expansion coefficient α of medium pressure cylinder IC , Poisson's ratio of medium pressure cylinder material μ IC And the thermal stress monitoring parameter criterion value S of the medium pressure cylinder corresponding to τ0 thIC , online calculation of turbine medium pressure cylinder temperature difference ratio R ΔtIC The calculation formula is:

[0380]

[0381] S705, judging whether the thermal stress determination value of the key component of the steam turbine meets the fourth monitoring qualification condition.

[0382] In the disclosed embodiment, the thermal stress judgment value of the key components of the steam turbine is the temperature difference ratio of the key components of the steam turbine. The fourth monitoring qualified condition can be determined based on the high-pressure valve housing temperature difference ratio, the high-pressure rotor temperature difference ratio, the high-pressure cylinder temperature difference ratio, the medium-pressure valve housing temperature difference ratio, the medium-pressure rotor temperature difference ratio, and the medium-pressure cylinder temperature difference ratio.

[0383] Optionally, the thermal stress judgment value of the key component of the target steam turbine in service meets the fourth monitoring qualification condition:

[0384] (R ΔtHV <1)∩(R ΔtHR <1)∩(R ΔtHC <1)∩(R ΔtIV <1)∩(R ΔtIR <1)∩(R ΔtIC <1)

[0385] Optionally, the thermal stress judgment value of the key component of the target steam turbine in service fails to meet the fourth monitoring qualification condition:

[0386] (R ΔtHV ≥1)∪(R ΔtHR ≥1)∪(R ΔtHC ≥1)∪(R ΔtIV ≥1)∪(R ΔtIR ≥1)∪(R ΔtIC ≥1)

[0387] S706: In response to the thermal stress determination value of the target steam turbine in service not satisfying the fourth monitoring qualified condition, generating an optimized operation strategy for the target steam turbine in service.

[0388] In the disclosed embodiment, the thermal stress judgment value of the target steam turbine in service does not meet the fourth monitoring qualification condition, indicating that the turbine inlet steam temperature change rate or load change rate during the operation stage is too large, and the turbine inlet steam temperature change rate or load change needs to be reduced.

[0389] Optionally, during the operation phase, it is necessary to optimize the start-up process or load climbing process of the turbine, and the monitoring information is fed back to the turbine digital electro-hydraulic control system DEH or the turbine control system TCS. The rate of change of the turbine inlet steam temperature is reduced to 0.8-0.9 times the current value or the rate of change of the turbine load is reduced to 0.8-0.9 times the current value. During the turbine start-up and load climbing process, electric heating tape is used for heating to reduce the thermal stress of key components. The thermal stress judgment value of the turbine under the target operating condition is continued to be calculated online and the operation monitoring is optimized until the thermal stress judgment value meets the fourth monitoring qualification condition, and the operation optimization is terminated.

[0390] In the multi-dimensional monitoring platform for flexibly operating steam turbines provided by the embodiments of the present disclosure, operation monitoring is performed on the thermal stress of the target steam turbine in service under the target operating conditions to determine whether the thermal stress monitoring of the target steam turbine in service is qualified, and operation optimization control is performed on the steam turbine that fails the monitoring, thereby ensuring the long life and high flexibility of the target steam turbine in service.

[0391] As an example, based on a certain model of ultra-supercritical 1050MW single-reheat steam turbine, for the high-pressure valve casing, high-pressure rotor, high-pressure cylinder, medium-pressure valve casing, medium-pressure rotor and medium-pressure cylinder of this model of steam turbine, the following online monitoring data is taken from the monitoring information fed back to the steam turbine digital electro-hydraulic control system DEH or the steam turbine control system TCS at a certain moment of starting and load climbing.

[0392] Metal temperature t at the measuring point where the high-pressure valve shell wall thickness is 82% to 98% HV90 =582.97℃;

[0393] Metal temperature t at the measuring point where the wall thickness of the high-pressure valve shell is 40% to 60% HV50 =541.16℃;

[0394] The high-pressure rotor surface temperature t is represented by the metal temperature at the measuring point at the depth of 82% to 98% of the high-pressure inner cylinder wall thickness. HR0 =578.26℃;

[0395] Metal temperature t at the measuring point where the wall thickness of the high-pressure cylinder is 82% to 98% HC90 =376.81℃;

[0396] Metal temperature t at the measuring point where the wall thickness of the high-pressure cylinder is 40% to 60% HC50 =326.68℃;

[0397] Metal temperature t at the measuring point where the medium pressure valve shell wall thickness is 82% to 98% IV90 =580.97℃;

[0398] Metal temperature t at the measuring point where the medium pressure valve shell wall thickness is 40% to 60% IV50=538.67℃;

[0399] The surface temperature of the medium-pressure rotor t is represented by the metal temperature at the measuring point at the depth of 82% to 98% of the medium-pressure inner cylinder wall thickness. IR0 =573.09℃;

[0400] Metal temperature t at the measuring point where the wall thickness of the medium-pressure cylinder is 82% to 98% IC90 =285.02℃;

[0401] Metal temperature t at the measuring point where the wall thickness of the medium-pressure cylinder is 40% to 60% IC50 =234.13℃.

[0402] The average volume temperature difference of the high pressure valve casing of this type of steam turbine is Δt mHV The online calculation result is:

[0403] Δt mHV =|t HV50 -t HV90 |=|541.16-582.97|=41.81℃

[0404] Using the data processing server 26, the simulation calculation value of the average volume temperature of the high-pressure rotor of this model of steam turbine is t mHR =510.31℃, online calculation of the average temperature difference of the high-pressure rotor volume Δt mHR The result is:

[0405] Δt mHR =|t mHR -t HR0 |=|510.31-578.26|=67.95℃

[0406] Optionally, the average volume temperature difference Δt of the high pressure cylinder of this type of steam turbine mHC The online calculation result is:

[0407] Δt mHC =|t HC50 -t HC90 |=|326.68-376.81|=50.13℃

[0408] Optionally, the average volume temperature difference Δt of the high pressure valve casing of this type of steam turbine mIV The online calculation result is:

[0409] Δt mIV =|t IV50 -t IV90 |=|538.67-580.97|=42.30℃

[0410] Using the data processing server 26, the simulated calculated value of the volume average temperature of the intermediate pressure rotor of this type of steam turbine is t mIR =496.42℃, online calculation of the average temperature difference of the medium pressure rotor volume Δt mIR The result is:

[0411] Δt mIR =|t mIR -t IR0 |=|496.42-573.09|=76.67℃

[0412] Optionally, the average volume temperature difference Δt of the medium-pressure cylinder of this type of steam turbine mIC The online calculation result is:

[0413] Δt mIC =|t IC50 -t IC90 |=|234.13-285.02|=50.89℃.

[0414] Using the data processing server 26, the material of the high-pressure valve shell is ZG1Cr10MoWVNbN, and the metal temperature t of the measuring point at the depth of 40% to 60% of the high-pressure valve shell wall thickness is HV50 =541.16℃, online calculation of the elastic modulus E of the high pressure valve shell HV =1.736×10 5 MPa, material linear expansion coefficient of high pressure valve shell α HV =12.08×10 -6 (1 / ℃), Poisson's ratio of high pressure valve shell material μ HV =0.302 and the thermal stress monitoring parameter criterion value S of the high pressure valve shell corresponding to τ0 thHV =521MPa, the high pressure valve shell temperature difference ratio R of this type of steam turbine ΔtHV The online calculation results are:

[0415]

[0416] The material of the high-pressure rotor is X12CrMoWVNBN10-1-1. The simulation calculation value of the average volume temperature of the high-pressure rotor is t mHR =510.31℃, online calculation of the elastic modulus E of the high-pressure rotor material HR =1.810×10 5 MPa, material linear expansion coefficient of high pressure rotor α HR =12.03×10 -6 (1 / ℃), Poisson's ratio of high pressure rotor material μ HR =0.310, and the thermal stress monitoring parameter criterion value S of the high-pressure rotor corresponding to τ0 thHR=672MPa, the temperature difference ratio of the high pressure rotor of this type of steam turbine is R ΔtHR The online calculation result is:

[0417]

[0418] The material of the high-pressure cylinder is ZG15CrMoV. According to the metal temperature t at the depth of 40% to 60% of the high-pressure cylinder wall thickness, HC50 =326.68℃, online calculation of the elastic modulus E of the material of the high-pressure cylinder HC =1.979×10 5 MPa, material linear expansion coefficient of high pressure cylinder α HC =13.32×10 -6 (1 / ℃), Poisson's ratio of high-pressure cylinder material μ HC =0.280 and the thermal stress monitoring parameter criterion value S of the high-pressure cylinder corresponding to τ0 thHC =452MPa, the temperature difference ratio of the high pressure cylinder of this type of steam turbine is R ΔtHC The online calculation result is:

[0419]

[0420] The material of the medium pressure valve shell is ZG1Cr10MoWVNbN. According to the metal temperature t at the depth of 40% to 60% of the medium pressure valve shell wall thickness, IV50 =538.67℃, online calculation of the elastic modulus E of the medium pressure valve housing IV 1.739×10 5 MPa, linear expansion coefficient of medium pressure valve housing α IV =12.08×10 -6 (1 / ℃), Poisson's ratio of the material of the medium pressure valve shell μ IV =0.302 and the thermal stress monitoring parameter criterion value S of the medium pressure valve shell corresponding to τ0 thIV =534MPa, the temperature difference ratio of the medium pressure valve shell of this type of steam turbine R ΔtIV The online calculation result is:

[0421]

[0422] The material of the medium-pressure rotor is X12CrMoWVNBN10-1-1. The simulation calculation value of the average volume temperature of the medium-pressure rotor is t mIR =496.42℃, the elastic modulus E of the medium pressure rotor is obtained by online calculation IR =1.823×10 5 MPa, material linear expansion coefficient of medium-pressure rotor α IR =11.98×10 5MPa Material Poisson's ratio of medium pressure rotor μ IR =0.310 and the thermal stress monitoring parameter criterion value S of the medium pressure rotor corresponding to τ0 thIR =684MPa, the temperature difference ratio R of the medium pressure rotor of this type of steam turbine ΔtIR The online calculation result is:

[0423]

[0424] The material of the medium-pressure cylinder is ZG15CrMoV. According to the metal temperature t at the depth of 40% to 60% of the medium-pressure cylinder wall thickness, IC50 =234.13℃, online calculation of the elastic modulus E of the medium pressure cylinder IC , Material linear expansion coefficient α of medium pressure cylinder IC , Poisson's ratio of medium pressure cylinder material μ IC And the thermal stress monitoring parameter criterion value S of the medium pressure cylinder corresponding to τ0 thIC , the temperature difference ratio R of the medium pressure cylinder of this type of steam turbine ΔtIC The online calculation result is:

[0425]

[0426] In summary, the thermal stress judgment value of this type of ultra-supercritical 1050MW single-reheat steam turbine meets the fourth monitoring qualification condition as follows:

[0427] (R ΔtHV =0.241<1)∩(R ΔtHR =0.319<1)∩(R ΔtHC =0.406<1)∩(R ΔtIV =0.238<1)∩(R ΔtIR =0.355<1)∩(R ΔtIC =0.383<1)

[0428] When the thermal stress judgment value of this type of ultra-supercritical 1050MW steam turbine is under the target operating condition, it satisfies the fourth monitoring qualification condition, indicating that the thermal stress of this type of ultra-supercritical 1050MW steam turbine is under controlled state under the target operating condition at this moment, and the monitoring information is fed back to the steam turbine digital electro-hydraulic control system DEH or the steam turbine control system TCS, and continues to quickly start and quickly load change and climb according to the existing rate of change of the turbine inlet steam temperature or the rate of change of the turbine load, and continuously monitors the thermal stress operation of the turbine, and enters the subsequent monitoring process.

[0429] Based on the above implementation, the disclosed embodiment can explain the process of operating monitoring of the safety judgment value of dynamic and static friction of the steam turbine under the target working condition, such as Figure 8As shown in FIG. 1 , the process of operating monitoring of the safety judgment value of dynamic and static friction of the steam turbine under the target operating condition includes the following steps:

[0430] S801, obtaining online monitoring data of the axial displacement and expansion difference of the target steam turbine rotor in service.

[0431] Optionally, the online monitoring data of the rotor axial displacement and expansion difference include: online monitoring data y of the turbine rotor axial displacement at the thrust bearing, online monitoring data x of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the turbine and the high-pressure cylinder H , Online monitoring data of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side far away from the thrust bearing and the intermediate pressure cylinder I , Basic data for online monitoring of the expansion difference between the low-pressure rotor and the low-pressure cylinder of the steam turbine generator side L Among them, H represents high pressure, I represents medium pressure, and L represents low pressure.

[0432] Optionally, online monitoring data of the rotor axial displacement and differential expansion may be acquired based on a steam turbine monitoring instrumentation system TSI.

[0433] S802, obtaining the operating limit values ​​of the axial displacement and expansion difference of the target steam turbine rotor in service.

[0434] Optionally, the operating limit values ​​of the rotor axial displacement and differential expansion include: the lower limit value y of the axial displacement of the turbine rotor at the thrust bearing part L , Upper limit of axial displacement of turbine rotor at thrust bearing position y U , the lower limit of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine and the high-pressure cylinder x HL , The upper limit of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine and the high-pressure cylinder x HU , The lower limit of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side of the thrust bearing and the intermediate pressure cylinder x IL , The upper limit value of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side of the thrust bearing and the intermediate pressure cylinder x IU , The lower limit of the expansion difference between the low-pressure rotor on the generator side of the steam turbine low-pressure cylinder and the low-pressure cylinder x LL , The upper limit value of the expansion difference between the low-pressure rotor on the generator side of the steam turbine low-pressure cylinder and the low-pressure cylinder x LU operating limit value.

[0435] S803, online calculation of the lower limit ratio and the upper limit ratio of the axial displacement of the steam turbine rotor.

[0436] In the disclosed embodiment, the lower limit ratio and upper limit ratio of the axial displacement of the turbine rotor can be calculated based on the online monitoring data of the axial displacement of the turbine rotor, the lower limit value of the axial displacement of the turbine rotor at the thrust bearing location, the upper limit value of the axial displacement of the turbine rotor at the thrust bearing location, and the sign of the online monitoring data of the axial displacement of the turbine rotor.

[0437] Optionally, by obtaining the online monitoring data y of the axial displacement of the turbine rotor at the thrust bearing part and the lower limit value y of the axial displacement of the turbine rotor at the thrust bearing part L The upper limit of the axial displacement of the turbine rotor at the thrust bearing position y U According to the positive and negative signs of the online monitoring data y of the axial displacement of the steam turbine rotor, the axial displacement ratio R of the running steam turbine rotor is calculated online. y .

[0438] Optionally, when the rotor axial displacement online monitoring data y<0, the rotor axial displacement ratio

[0439] Optionally, when the rotor axial displacement online monitoring data y ≥ 0, the rotor axial displacement ratio

[0440] S804, online calculation of the lower limit ratio and the upper limit ratio of the turbine expansion difference.

[0441] In the disclosed embodiment, the lower limit ratio and upper limit ratio of the turbine expansion differential can be determined based on the ratio of the online monitoring data of the rotor axial displacement and expansion differential to the operating limit values ​​of the rotor axial displacement and expansion differential.

[0442] Optionally, by obtaining the online monitoring data x of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine and the high-pressure cylinder H , the lower limit of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine and the high-pressure cylinder x HL , The upper limit of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine and the high-pressure cylinder x HU , online calculation of the expansion difference ratio R of the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine relative to the high-pressure cylinder xH .

[0443] Optionally, by obtaining the online monitoring data x of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side away from the thrust bearing relative to the intermediate pressure cylinder I , The lower limit of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side of the thrust bearing and the intermediate pressure cylinder x IL , The upper limit value of the expansion difference between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side of the thrust bearing and the intermediate pressure cylinder x IU , Online calculation of the expansion difference ratio R of the intermediate pressure cylinder of the turbine away from the exhaust side of the intermediate pressure rotor of the thrust bearing relative to the intermediate pressure cylinder xI .

[0444] Optionally, by obtaining basic data x for online monitoring of the expansion difference between the low-pressure rotor on the generator side of the steam turbine low-pressure cylinder and the low-pressure cylinder L , the lower limit of the expansion difference between the low-pressure rotor on the generator side of the steam turbine low-pressure cylinder and the low-pressure cylinder x LL , The upper limit value of the expansion difference between the low-pressure rotor on the generator side of the steam turbine low-pressure cylinder and the low-pressure cylinder x LU The operation target basic data is used to calculate the expansion difference ratio R of the low-pressure rotor on the generator side of the steam turbine low-pressure cylinder relative to the low-pressure cylinder online. xL .

[0445] Alternatively, if the expansion difference during the turbine startup or load-adding process is positive, the expansion difference ratio R of the high-pressure rotor on the high-pressure cylinder exhaust side relative to the high-pressure cylinder is xH , the expansion difference ratio R of the intermediate pressure cylinder away from the exhaust side of the intermediate pressure rotor and the intermediate pressure cylinder xI , the expansion ratio R of the low-pressure rotor on the low-pressure cylinder generator side relative to the low-pressure cylinder xL They are

[0446] Optionally, if the expansion difference during the turbine shutdown process or load reduction process is negative, the expansion difference ratio R of the high-pressure rotor on the high-pressure cylinder exhaust side relative to the high-pressure cylinder is xH , the expansion difference ratio R of the intermediate pressure cylinder away from the exhaust side of the intermediate pressure rotor and the intermediate pressure cylinder xI , the expansion ratio R of the low-pressure rotor on the low-pressure cylinder generator side relative to the low-pressure cylinder xL They are

[0447] S805, determining whether the safety judgment value of the turbine dynamic-static friction meets the fifth monitoring qualification condition.

[0448] In the disclosed embodiment, the safety judgment value of the turbine dynamic-static friction refers to the lower limit ratio and the upper limit ratio of the turbine expansion difference, and the lower limit ratio and the upper limit ratio of the turbine rotor axial displacement. The fifth monitoring qualified condition can be determined based on the expansion difference ratio of the high-pressure rotor on the high-pressure cylinder exhaust side relative to the high-pressure cylinder, the expansion difference ratio of the medium-pressure rotor on the medium-pressure cylinder exhaust side away from the thrust bearing relative to the medium-pressure cylinder, the expansion difference ratio of the low-pressure rotor on the low-pressure cylinder generator side relative to the low-pressure cylinder, and the rotor axial displacement ratio.

[0449] Optionally, the safety judgment value of the turbine dynamic and static friction meets the fifth monitoring qualification condition:

[0450] (R y <1)∩(R xH <1)∩(R xI <1)∩(R xL <1)

[0451] Optionally, the safety judgment value of the turbine dynamic-static friction does not meet the fifth monitoring qualification condition:

[0452] (R y >1)∪(R xH >1)∪(R xI >1)∪(R xL >1)

[0453] S806: In response to the safety determination value of the dynamic-static friction of the target steam turbine in service not satisfying the fifth monitoring qualified condition, an optimized operation strategy for the target steam turbine in service is generated.

[0454] In the disclosed embodiment, the safety judgment value of the dynamic and static friction of the target steam turbine in service does not meet the fifth monitoring qualification condition, indicating that improper operating operation causes excessive expansion difference or excessive axial displacement, or foreign matter in the flow passage of the turbine causes excessive axial displacement of the rotor.

[0455] In order to solve the problem of excessive expansion difference caused by improper operation, it is necessary to optimize the starting process or load climbing process of the turbine during the operation stage, and feed back the monitoring information to the turbine digital electro-hydraulic control system DEH or the turbine control system TCS. The rate of change of the turbine inlet steam temperature is reduced to 0.8-0.9 times of the current value, or the rate of change of the turbine load is reduced to 0.8-0.9 times of the current value. During the starting and loading climbing process of the turbine, electric heating tape is used to heat the cylinder to reduce the absolute value of the expansion difference. The dynamic and static friction safety of the turbine rapid starting and rapid load change climbing transient conditions is continuously monitored online, and the operation monitoring is optimized.

[0456] If the rotor axial displacement is still too large and the turbine vibrates too much after the improved operation, there may be foreign matter in the flow path of the turbine and the unit needs to be shut down immediately for inspection and maintenance to remove the foreign matter from the flow path of the turbine.

[0457] In the multi-dimensional monitoring platform for flexibly operating steam turbines provided by the embodiments of the present disclosure, operation monitoring is performed on the dynamic and static friction safety of the target steam turbine in service under the target operating conditions, it is determined whether the dynamic and static friction safety monitoring of the target steam turbine in service is qualified, and operation optimization control is performed on the steam turbine that fails the monitoring, thereby ensuring the long life and high flexibility of the target steam turbine in service.

[0458] As an example, based on a certain type of ultra-supercritical 1050MW single-reheat steam turbine, the basic operating target data of the axial displacement and expansion difference of this type of steam turbine are listed in Table 12.

[0459] Table 12 Basic operating target data of axial displacement and expansion difference of ultra-supercritical 1050MW single reheat steam turbine

[0460] project Numeric <![CDATA[Lower limit value y of axial displacement of steam turbine rotor at thrust bearing position L / mm]]> -1.08 <![CDATA[Upper limit value y of axial displacement of steam turbine rotor at thrust bearing part U / mm]]> 0.6 <![CDATA[Lower limit value x of differential expansion of high-pressure rotor relative to high-pressure cylinder on the extraction side of high-pressure cylinder HL / mm]]> -7.3 <![CDATA[Upper limit value x of differential expansion of high-pressure rotor relative to high-pressure cylinder on the extraction side of high-pressure cylinder HU / mm]]> 13.5 <![CDATA[Lower limit value x of differential expansion of intermediate pressure rotor relative to intermediate pressure cylinder on the exhaust side of intermediate pressure cylinder far from thrust bearing IL / mm]]> -7.2 <![CDATA[Upper limit value x of differential expansion between the intermediate-pressure rotor and the intermediate-pressure cylinder on the exhaust side of the intermediate-pressure cylinder away from the thrust bearing IU / mm]]> 10.1 <![CDATA[Lower limit value x of differential expansion of the low-pressure rotor on the generator side of the low-pressure cylinder relative to the low-pressure cylinder LL / mm]]> -6.5 <![CDATA[Upper limit value x of differential expansion of low-pressure rotor on the generator side of low-pressure cylinder relative to low-pressure cylinder LU / mm]]> 32.6

[0461] For this type of ultra-supercritical 1050MW single-reheat steam turbine, during the rapid load ramping process of the steam turbine, the online monitoring data at a certain moment are: online monitoring data of the axial displacement of the steam turbine rotor at the thrust bearing y = 0.55mm, online monitoring data of the expansion difference between the high-pressure rotor on the exhaust side of the high-pressure cylinder of the steam turbine and the high-pressure cylinder x H =13.7mm, online monitoring data of the difference in expansion between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side of the thrust bearing and the intermediate pressure cylinder I =9.5mm, basic data for online monitoring of the expansion difference between the low-pressure rotor and the low-pressure cylinder of the low-pressure cylinder of the steam turbine generator side L =31.0mm, and the online calculation results of axial displacement and expansion difference are obtained.

[0462] Since the online monitoring data of the rotor axial displacement y≥0, the online calculation result of the rotor axial displacement ratio is:

[0463] During the turbine startup or load-adding process, the expansion difference is positive, and the expansion difference ratio of the high-pressure rotor on the high-pressure cylinder exhaust side to the high-pressure cylinder is R xH , the expansion difference ratio R of the intermediate pressure cylinder away from the exhaust side of the intermediate pressure rotor and the intermediate pressure cylinder xI , the expansion ratio R of the low-pressure rotor on the low-pressure cylinder generator side relative to the low-pressure cylinder xL They are:

[0464] The result of the safety judgment value of dynamic and static friction under the target operating condition of this type of ultra-supercritical 1050MW single-reheat steam turbine meeting the fifth monitoring qualification condition is:

[0465] (R y =0.92<1)∪(R xH =1.01>1)∪(R xI =0.94<1)∪(R xL =0.95<1)

[0466] If the dynamic and static friction safety of this type of ultra-supercritical 1050MW steam turbine under the target operating conditions does not meet the fifth monitoring qualification condition, it indicates that this type of ultra-supercritical 1050MW steam turbine has a dynamic and static friction safety risk under the target operating conditions at this moment. It is necessary to optimize the operation of the turbine startup process or load climbing process during the operation stage, and feed back the monitoring information to the turbine digital electro-hydraulic control system DEH or the turbine control system TCS, and reduce the rate of change of the turbine inlet steam temperature to 0.8-0.9 times the current rate or reduce the rate of change of the turbine load to 0.8-0.9 times the current rate. During the turbine startup and load climbing process, use electric heating tape to heat the cylinder to reduce the absolute value of the expansion difference, continue to monitor the dynamic and static friction safety of the turbine rapid startup and rapid load change climbing transient conditions online, and optimize the operation to ensure that the dynamic and static friction safety of the turbine is under control.

[0467] For a certain type of ultra-supercritical 1050MW single-reheat steam turbine, the online monitoring of axial displacement and differential expansion is taken from TSI. During the rapid load ramping process of the steam turbine, the online monitoring data at another moment are: the online monitoring data of the axial displacement of the steam turbine rotor at the thrust bearing is y=0.5mm, and the online monitoring data of the differential expansion of the high-pressure rotor relative to the high-pressure cylinder on the exhaust side of the steam turbine high-pressure cylinder is x H =10.0mm, online monitoring data of the difference in expansion between the intermediate pressure cylinder of the steam turbine and the intermediate pressure rotor on the exhaust side of the thrust bearing and the intermediate pressure cylinder I =9.0mm, basic data for online monitoring of the expansion difference between the low-pressure rotor and the low-pressure cylinder of the low-pressure cylinder of the steam turbine generator side L =30.0mm, and the online calculation results of axial displacement and expansion difference are obtained.

[0468] Since the online monitoring data of the rotor axial displacement y≥0, the online calculation result of the rotor axial displacement ratio is:

[0469] During the turbine startup or load-adding process, the expansion difference is positive, and the expansion difference ratio of the high-pressure rotor on the high-pressure cylinder exhaust side to the high-pressure cylinder is R xH , the expansion difference ratio R of the intermediate pressure cylinder away from the exhaust side of the intermediate pressure rotor and the intermediate pressure cylinder xI , the expansion ratio R of the low-pressure rotor on the low-pressure cylinder generator side relative to the low-pressure cylinder xL They are:

[0470] The result of the safety judgment value of dynamic and static friction of this type of ultra-supercritical 1050MW single-reheat steam turbine under the target operating conditions meeting the fifth monitoring qualification condition is:

[0471] (R y =0.83<1)∩(R xH =0.74<1)∩(RxI =0.89<1)∩(R xL =0.92<1)

[0472] If the dynamic and static friction safety of this type of ultra-supercritical 1050MW steam turbine meets the qualified conditions for operation monitoring under the target operating conditions, it indicates that the dynamic and static friction safety of this type of ultra-supercritical 1050MW steam turbine is under control under the target operating conditions at this moment, and the monitoring information is fed back to the steam turbine digital electro-hydraulic control system DEH or the steam turbine control system TCS, and rapid starting and rapid load change climbing continue according to the existing rate of change of the turbine inlet steam temperature or the rate of change of the turbine load, and continuous operation monitoring is performed.

[0473] The collection, storage, use, processing, transmission, provision and disclosure of user personal information involved in this disclosure shall comply with the relevant laws and regulations and shall not violate public order and good morals.

[0474] It should be noted that personal information from users should be collected for legitimate and reasonable purposes and should not be shared or sold outside of these legitimate uses. In addition, such collection / sharing should be carried out after receiving the user's informed consent, including but not limited to notifying the user to read the user agreement / user notice and sign the agreement / authorization including authorization of relevant user information before the user uses the function. In addition, any necessary steps should be taken to protect and safeguard access to such personal information data and ensure that others who have access to personal information data comply with its privacy policy and procedures.

[0475] The present disclosure anticipates providing implementation schemes for users to selectively block the use or access of personal information data. That is, the present disclosure anticipates providing hardware and / or software to prevent or block access to such personal information data. Once the personal information data is no longer needed, risks can be minimized by limiting data collection and deleting the data. In addition, when applicable, such personal information is de-identified to protect the privacy of the user.

[0476] In the description of the aforementioned embodiments, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present disclosure. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples, unless they are contradictory.

[0477] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the features. In the description of the present disclosure, "plurality" means at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0478] Any process or method description in a flowchart or otherwise described herein may be understood to represent a module, segment or portion of code that includes one or more executable instructions for implementing the steps of a custom logical function or process, and the scope of the preferred embodiments of the present disclosure includes additional implementations in which functions may not be performed in the order shown or discussed, including performing functions in a substantially simultaneous manner or in reverse order depending on the functions involved, which should be understood by technicians in the technical field to which the embodiments of the present disclosure belong.

[0479] The logic and / or steps represented in the flowchart or otherwise described herein, for example, can be considered as an ordered list of executable instructions for implementing logical functions, and can be embodied in any computer-readable medium for use by an instruction execution system, device or apparatus (such as a computer-based system, a system including a processor, or other system that can fetch instructions from an instruction execution system, device or apparatus and execute instructions), or in combination with these instruction execution systems, devices or apparatuses. For the purpose of this specification, "computer-readable medium" can be any device that can contain, store, communicate, propagate or transmit a program for use by an instruction execution system, device or apparatus, or in combination with these instruction execution systems, devices or apparatuses. More specific examples of computer-readable media (a non-exhaustive list) include the following: an electrical connection with one or more wires (electronic device), a portable computer disk box (magnetic device), a random access memory (RAM), a read-only memory (ROM), an erasable and programmable read-only memory (EPROM or flash memory), a fiber optic device, and a portable compact disk read-only memory (CDROM). In addition, the computer-readable medium may even be paper or other suitable medium on which the program is printed, since the program may be obtained electronically, for example, by optically scanning the paper or other medium and then editing, interpreting or processing in other suitable ways if necessary, and then stored in a computer memory.

[0480] It should be understood that the various parts of the present disclosure can be implemented in hardware, software, firmware or a combination thereof. In the above-mentioned embodiments, multiple steps or methods can be implemented in software or firmware stored in a memory and executed by a suitable instruction execution system. For example, if implemented in hardware, as in another embodiment, any one of the following technologies known in the art or a combination thereof can be used to implement: a discrete logic circuit having a logic gate circuit for implementing a logic function for a data signal, a dedicated integrated circuit having a suitable combination of logic gate circuits, a programmable gate array (PGA), a field programmable gate array (FPGA), etc.

[0481] A person skilled in the art may understand that all or part of the steps in the method for implementing the above-mentioned embodiment may be completed by instructing related hardware through a program, and the program may be stored in a computer-readable storage medium, which, when executed, includes one or a combination of the steps of the method embodiment.

[0482] In addition, each functional unit in each embodiment of the present disclosure may be integrated into a processing module, or each unit may exist physically separately, or two or more units may be integrated into one module. The above-mentioned integrated module may be implemented in the form of hardware or in the form of a software functional module. If the integrated module is implemented in the form of a software functional module and sold or used as an independent product, it may also be stored in a computer-readable storage medium.

[0483] The storage medium mentioned above may be a read-only memory, a disk or an optical disk, etc. Although the embodiments of the present disclosure have been shown and described above, it can be understood that the above embodiments are exemplary and cannot be understood as limitations of the present disclosure. A person of ordinary skill in the art may change, modify, replace and modify the above embodiments within the scope of the present disclosure.

Claims

1. A multi-dimensional monitoring platform for flexible operation of steam turbines, characterized in that: The steam turbine is used for peak load regulation, and comprises: A wireless communication component is used to process data transmission between a server and a steam turbine; a database is used to store a first monitoring data set in the design phase and a second monitoring data set in the operation phase of key components of the steam turbine under transient conditions of rapid start-up and rapid load change climbing of the steam turbine, wherein the first monitoring data set includes: obtaining basic data of design life and basic data of design operation targets to determine the crack initiation calendar life; obtaining the yield strength of the material and the maximum equivalent stress of the structure at the transient operating temperature to determine the structural stress ratio; the second monitoring data set includes: obtaining online monitoring data and operation limit values ​​of the rotor axial displacement and expansion difference; calculating the lower limit ratio and upper limit ratio of the axial displacement of the steam turbine rotor, and the lower limit ratio and upper limit ratio of the expansion difference of the steam turbine; judging the safety judgment value of the dynamic and static friction of the steam turbine; a processing server determines a steam turbine to be monitored from multiple steam turbines based on the acquired monitoring instructions, identifies the target stage currently in which the steam turbine to be monitored is located, and determines the target data set from the first monitoring data set and the second monitoring data set based on the target stage, so as to execute a target optimization process matching the target stage for the key components of the steam turbine to be monitored.

2. The monitoring platform according to claim 1, characterized in that: The processing server is further used for: If the target stage is the design stage, a first monitoring data set of the steam turbine to be monitored is obtained from the database, the target data set is determined, and a structural optimization process is performed on key components of the steam turbine to be monitored.

3. The monitoring platform according to claim 2, characterized in that: The processing server is further used for: If the target stage is the operation stage, a second monitoring data set of the steam turbine to be monitored is obtained from the database, the target data set is determined, and an operation optimization process is performed on key components of the steam turbine to be monitored.

4. The monitoring platform according to claim 1, characterized in that: Also includes: a remote client, the remote client being connected to the processing server; The remote client is used to send the monitoring instruction to the processing server, and receive the optimization results of the key components of the steam turbine to be monitored fed back by the processing server.

5. The monitoring platform according to claim 4, characterized in that: The remote client is further used to obtain control information of a user who controls the remote client, and generate the monitoring instruction based on the control information.

6. The monitoring platform according to claim 1, characterized in that: The database includes a first storage space and a second storage space, the first storage space is used to store the first monitoring data set, and the second storage space is used to store the second monitoring data set.

7. The monitoring platform according to claim 6, characterized in that: Also includes: A data acquisition component, wherein the data acquisition component is connected to the processing server via the wireless communication component; The data acquisition component is used to collect design monitoring data of key components of the steam turbine during the design phase, and to collect operation monitoring data of key components of the steam turbine during the operation phase; The processing server is used to receive monitoring data, identify the monitoring data as design monitoring data of the key component, and store it in the first storage space, and identify the monitoring data as operation monitoring data of the key component, and store it in the second storage space.

8. The monitoring platform according to claim 1, characterized in that: The second monitoring data set includes: Design life basic data of key components of the steam turbine, design operation target basic data of the steam turbine, and crack initiation remaining calendar life of key components of the steam turbine; The key components of the steam turbine include thermal stress basic data, metal temperature basic data and thermal stress judgment values.

9. The monitoring platform according to claim 6, characterized in that: The monitoring platform is a distributed network structure, including a scheduling server, and the distributed network structure includes a plurality of processing servers; The scheduling server is used to receive the monitoring instruction, schedule the monitoring instruction, determine the target processing server corresponding to the monitoring instruction, and send the monitoring instruction to the target processing server.

10. The monitoring platform according to claim 9, characterized in that: The scheduling server is further used for: The first load status of each of the processing servers is obtained, and the monitoring instruction is scheduled according to the first load status to determine the target processing server.

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