CN117685067A

CN117685067A - High-flexibility thermal stress operation monitoring method and device for in-service steam turbine

Info

Publication number: CN117685067A
Application number: CN202311387832.9A
Authority: CN
Inventors: 史进渊; 谢岳生; 江路毅; 范雪飞; 李汪繁; 徐望人; 徐佳敏; 张琳; 王宇轩; 王得谖
Original assignee: Shanghai Power Equipment Research Institute Co Ltd
Current assignee: Shanghai Power Equipment Research Institute Co Ltd
Priority date: 2023-10-24
Filing date: 2023-10-24
Publication date: 2024-03-12

Abstract

The disclosure provides a high-flexibility thermal stress operation monitoring method and device for an in-service steam turbine. Wherein the method comprises the following steps: acquiring thermal stress basic data of key parts of the in-service steam turbine; acquiring measuring point metal temperature basic data of a key component; judging whether the thermal stress of the in-service steam turbine under the operating condition meets the operating monitoring qualification condition or not based on the thermal stress basic data and the measuring point metal temperature basic data; and in response to the operation monitoring qualification condition not being met, optimizing the operation strategy of the in-service steam turbine. Therefore, the scheme ensures the long service life and high flexibility of the turbine design by performing operation monitoring and optimization on the thermal stress of the key parts.

Description

High-flexibility thermal stress operation monitoring method and device for in-service steam turbine

Technical Field

The disclosure relates to the technical field of steam turbines, in particular to a high-flexibility thermal stress operation monitoring method and device for an in-service steam turbine.

Background

Because renewable energy sources such as wind energy, solar energy and the like generate electricity with the problems of intermittence, randomness, volatility and the like, a power grid can only usually accommodate 15% of unstable power sources, and the phenomena of wind discarding and light discarding are serious. In the prior art, the peak shaving minimum load is usually 35% of rated power. Through the operation control high flexibility steam turbine, the degree of depth peak shaver reaches 20% rated power and has the quick start climbing function, and the electric wire netting just can increase the unsteady power of holding corresponding steam turbine rated power 15%, helps solving and abandons wind abandons the light problem.

Disclosure of Invention

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

Therefore, a first object of the present disclosure is to provide a thermal stress operation monitoring method with high flexibility for an in-service steam turbine, which ensures long service life and high flexibility for operation of the steam turbine.

A second object of the present disclosure is to provide a thermal stress operation monitoring device with high flexibility for an in-service steam turbine.

A third object of the present disclosure is to propose an electronic device.

A fourth object of the present disclosure is to propose a computer readable storage medium.

A fifth object of the present disclosure is to propose a computer programme product.

To achieve the above object, an embodiment of a first aspect of the present disclosure provides a method for monitoring thermal stress operation of an in-service steam turbine with high flexibility, including: acquiring thermal stress basic data of key parts of the in-service steam turbine; acquiring measuring point metal temperature basic data of the key component; judging whether the thermal stress of the in-service steam turbine under the operating condition meets the operating monitoring qualification condition or not based on the thermal stress basic data and the measuring point metal temperature basic data; and in response to the operation monitoring qualification condition not being met, optimizing the operation strategy of the in-service steam turbine.

To achieve the above object, according to a second aspect of the present disclosure, there is provided a thermal stress operation monitoring device with high flexibility for an in-service steam turbine, including: the first acquisition module is used for acquiring thermal stress basic data of key components of the in-service steam turbine; the second acquisition module is used for acquiring the metal temperature basic data of the measuring point of the key component; the judging module is used for judging whether the thermal stress of the in-service steam turbine under the operating condition meets the operating monitoring qualification condition or not based on the thermal stress basic data and the measuring point metal temperature basic data; and the optimizing module is used for optimizing the operation strategy of the in-service steam turbine in response to the condition that the operation monitoring qualification condition is not met.

To achieve the above object, an embodiment of a third aspect of the present disclosure provides an electronic device, including: a processor; and a memory communicatively coupled to the processor; the memory stores computer-executable instructions; the processor executes the computer-executable instructions stored in the memory, so that the processor can execute the high-flexibility thermal stress operation monitoring method of the in-service steam turbine according to the embodiment of the first aspect.

To achieve the above object, an embodiment of a fourth aspect of the present disclosure provides a computer-readable storage medium having stored thereon a computer program, where the computer instructions are configured to cause the computer to execute the method for monitoring the thermal stress operation of the in-service steam turbine with high flexibility according to the embodiment of the above aspect.

To achieve the above object, a fifth aspect of the present disclosure provides a computer program product, which includes a computer program, where the computer program is executed by a processor to implement the high-flexibility thermal stress operation monitoring method for an in-service steam turbine according to the above aspect.

According to the high-flexibility thermal stress operation monitoring method and device for the in-service steam turbine, the thermal stress basic data and the measuring point metal temperature basic data of the key parts of the in-service steam turbine are obtained through operation monitoring of the in-service steam turbine, and then the thermal stress judgment value of the key parts under the operation working condition is determined. And further judging whether the thermal stress judgment value meets the operation monitoring qualification condition, and under the condition that the operation monitoring qualification condition is not met, performing operation optimization control on the steam turbine, and repeating the operation until the thermal stress judgment value meets the operation monitoring qualification condition, thereby ensuring long service life and high flexibility of the design of the steam turbine.

Additional aspects and advantages of the disclosure will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the disclosure.

Drawings

The foregoing and/or additional aspects and advantages of the present disclosure will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a schematic flow chart of a method for monitoring the operation of thermal stress with high flexibility of an in-service steam turbine according to an embodiment of the disclosure;

FIG. 2 is a schematic diagram of an apparatus for monitoring a steam turbine according to an embodiment of the present disclosure;

FIG. 3 is a flow chart of another method for monitoring high flexibility thermal stress operation of an in-service steam turbine according to an embodiment of the present disclosure;

FIG. 4 is a flow chart of another method for monitoring high flexibility thermal stress operation of an in-service steam turbine according to an embodiment of the present disclosure;

FIG. 5 is a schematic diagram of a high flexibility thermal stress operation monitoring device for an in-service steam turbine according to an embodiment of the present disclosure.

Detailed Description

Embodiments of the present disclosure are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and intended for the purpose of explaining the present disclosure and are not to be construed as limiting the present disclosure.

The following describes a high-flexibility thermal stress operation monitoring method and device for an in-service steam turbine according to an embodiment of the present disclosure with reference to the accompanying drawings.

FIG. 1 is a schematic flow chart of a method for monitoring the operation of thermal stress with high flexibility of an in-service steam turbine according to an embodiment of the disclosure, as shown in FIG. 1, the method includes the following steps:

s101, acquiring thermal stress basic data of key parts of the in-service steam turbine.

It should be noted that, in the embodiment of the present disclosure, the execution body of the thermal stress operation monitoring method with high flexibility of the in-service steam turbine is a hardware device with data processing capability and/or software necessary for driving the hardware device to work. Alternatively, the execution body may include a server, a computer, a user terminal, and other intelligent devices. Optionally, the user terminal includes, but is not limited to, a mobile phone, a computer, an intelligent voice interaction device, etc. Alternatively, the server includes, but is not limited to, a web server, an application server, a server of a distributed system, a server incorporating a blockchain, etc.

In the embodiment of the disclosure, the steam turbine is a non-positive-displacement machine which is flexibly operated, and in order to realize long service life and high flexibility of the steam turbine, design monitoring and operation monitoring can be performed under multiple dimensions and multiple targets.

In the disclosed embodiments, the goal of flexible turbine life is to run calendar life to 40 years with a life loss of only 0.75 (75%) of the total life. The high flexibility of the flexible operation turbine aims at 10000 times of starting, 16000 times of load variation, 250 times of starting every year and 400 times of load variation, the lowest safe and stable operation load is 20% rated power, and the load change rate of rapid starting climbing above 20% rated power exceeds 5% rated power.

In one possible implementation, the critical 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. Optionally, the thermal stress base data includes, but is not limited to: material elastic modulus, material linear expansion coefficient, poisson ratio, thermal stress monitoring parameter criterion value and simulation calculation value of rotor volume average temperature.

In one possible implementation, thermal stress base data for a critical component of an in-service turbine may be determined by obtaining a material modulus of elasticity, a coefficient of linear expansion, and poisson's ratio for the critical component, obtaining a thermal stress monitoring parameter criterion value for the critical component corresponding to a calendar total life design criterion value for the in-service turbine, and obtaining a simulated calculation of a first volume average temperature of a high pressure rotor and a simulated calculation of a second volume average temperature of a medium pressure rotor in the in-service turbine.

Alternatively, thermal stress base data for critical components of an in-service steam turbine may be obtained via a Digital Electro-hydraulic control system (Digital Electro-Hydraulic Control System, DEH), a steam turbine control system (Turbine Control System, TCS), a steam turbine monitoring instrumentation system (Turbine Supervisory Instruments, TSI), or the like.

S102, acquiring measuring point metal temperature basic data of the key component.

In the embodiment of the disclosure, metal temperature collection can be performed at different measuring points of the key component to obtain measuring point metal temperature basic data, and then the measuring point metal temperature of the key component in two types of wall thickness depth ranges is determined based on the measuring point metal temperature basic data.

In one possible implementation, the metal temperature may be sampled over a first wall thickness depth range specified for the critical component to obtain a first site metal temperature for the critical component. And sampling the metal temperature in a second wall thickness depth range appointed by the key part, and obtaining the metal temperature of a second measuring point of the key part. The first wall thickness depth range is 82% -98% of the wall thickness depth, and the second wall thickness depth range is 40% -60% of the wall thickness depth.

S103, judging whether the thermal stress of the in-service steam turbine under the operating condition meets the operating monitoring qualification condition or not based on the thermal stress basic data and the measuring point metal temperature basic data.

Alternatively, operating conditions may include, but are not limited to: and the whole operation processes of starting, grid connection, load lifting, stable load carrying, full load, load reducing, disconnection, shutdown and the like of the in-service steam turbine comprise rapid starting and/or rapid load variation climbing transient working conditions.

In the embodiment of the disclosure, whether the thermal stress of the in-service steam turbine meets the operation monitoring qualification condition can be judged according to the thermal stress judgment value of the key component. Alternatively, the thermal stress determination value of the critical component may be determined based on the volume average temperature difference of the critical component and the thermal stress base data.

In one possible implementation, the volume average temperature difference of the critical component may be obtained based on the first site metal temperature and the second site metal temperature. And further, according to the volume average temperature difference of the key component and the thermal stress basic data, obtaining the temperature difference ratio of the key component as a thermal stress judgment value.

Further, according to the thermal stress judgment value of the key component, whether the thermal stress of the in-service steam turbine meets the operation monitoring qualification condition is judged. Alternatively, it may be determined whether the thermal stress of the in-service steam turbine satisfies the operation monitoring qualification condition based on the set value of the thermal stress determination value.

In one possible implementation, in response to the thermal stress determination value for each critical component being less than the set point, it is determined that the thermal stress of the in-service turbine meets the operational monitoring qualifying condition. If the thermal stress judgment value of at least one key component is larger than or equal to the set value, determining that the thermal stress of the in-service steam turbine does not meet the operation monitoring qualification condition.

And S104, optimizing the operation strategy of the in-service steam turbine in response to the condition that the operation monitoring qualification is not met.

In the embodiment of the disclosure, in response to the in-service steam turbine not meeting the operation monitoring qualification condition, the operation parameters in the operation strategy of the in-service steam turbine can be adjusted to optimize the operation strategy of the in-service steam turbine.

In one possible implementation, the temperature change rate and/or the load change rate may be adjusted, and the operation strategy of the in-service steam turbine may be optimized by obtaining the current inlet steam temperature change rate and/or the load change rate of the in-service steam turbine and reducing the inlet steam temperature change rate and/or the load change rate.

In one possible implementation, the steam turbine operates according to the optimized operation strategy, and re-acquires the thermal stress determination value of the key component and performs the subsequent steps until the thermal stress of the key component meets the operation monitoring qualification condition, and the operation optimization is finished.

In the high-flexibility thermal stress operation monitoring method for the in-service steam turbine, the thermal stress basic data and the measuring point metal temperature basic data of the key component of the in-service steam turbine are obtained through operation monitoring of the in-service steam turbine, and then the thermal stress judgment value of the key component under the operation working condition is determined. And further judging whether the thermal stress judgment value meets the operation monitoring qualification condition, and under the condition that the operation monitoring qualification condition is not met, performing operation optimization control on the steam turbine, and repeating the operation until the thermal stress judgment value meets the operation monitoring qualification condition, thereby ensuring long service life and high flexibility of the design of the steam turbine.

Fig. 2 shows a schematic view of an apparatus for monitoring a steam turbine, and the apparatus 200 includes a life monitoring module 21, a thermal stress monitoring module 22, a dynamic and static friction monitoring module 23, an optimal design module 24, an optimal operation module 25, and a data processing server 26. Wherein, life monitoring module 21, thermal stress monitoring module 22, sound bump friction monitoring module 23, optimal design module 24 and optimal operation module 25 are connected with data processing server 26. Alternatively, the apparatus 200 may be connected to a turbine digital electrohydraulic control system DEH or a turbine control system TCS, turbine monitoring instrumentation system TSI.

Thermal stress monitoring module 22 stores turbine rotor, valve housing and turbine shaftModulus of elasticity E of the cylinder material _jk Coefficient of linear expansion alpha _jk And poisson ratio mu _jk Design criterion value tau of total calendar life of steam turbine ₀ Corresponding thermal stress monitoring parameter criterion value S of turbine rotor, valve shell and cylinder _thjk Basic data of thermal stress monitoring parameter criterion values, simulation calculated values t of turbine starting, stopping, load variation and rotor volume average temperature of loaded operation _mjR The surface temperature t of the high-pressure rotor and the medium-pressure rotor, which are characterized by adopting the metal temperature of the measuring point at the depth of 82% -98% of the wall thickness of the high-pressure inner cylinder and the medium-pressure inner cylinder _jR0 Metal temperature t of measuring point at 82% -98% depth of wall thickness of high-pressure valve casing and medium-pressure valve casing _jV90 Metal temperature t of measuring point at depth of 40% -60% of wall thickness of high-pressure valve casing and medium-pressure valve casing _jV50 The metal temperature t of the measuring point at the depth of 82% -98% of the wall thickness of the high-pressure cylinder and the medium-pressure cylinder _jC90 Basic data t of metal temperature of measuring points at depth of 40% -60% of wall thickness of high-pressure cylinder and medium-pressure cylinder _jC50 The metal temperature of the measuring point is taken from a digital electrohydraulic control system DEH or a TCS of the steam turbine. Wherein, subscript j represents a key component working environment, H represents a high pressure, I represents a medium pressure, L represents a low pressure, subscript k represents a turbine component name, V represents a valve housing, R represents a rotor, and C represents a cylinder. The functions of the thermal stress monitoring module 12 include: and acquiring a thermal stress judgment value of a key component of the steam turbine under the operating condition.

And the optimizing operation module 25 is used for optimizing and improving the operation of the steam turbine according to the monitoring abnormal data of the thermal stress judgment value of the key component of the steam turbine under the operation working condition so as to ensure the long service life and high flexibility of the operation of the steam turbine.

The data processing server 26 is used for performing thermal stress operation monitoring under the operation condition of the steam turbine, and the obtained optimized operation measures are fed back to the digital electrohydraulic control system DEH or the turbine control system TCS of the steam turbine to guide the optimized operation of the steam turbine with long service life and high flexibility.

FIG. 3 is a schematic flow chart of a method for monitoring the operation of thermal stress with high flexibility of an in-service steam turbine according to an embodiment of the disclosure, as shown in FIG. 3, the method includes the following steps:

s301, performing operation monitoring on the thermal stress of the key parts of the in-service steam turbine under the operation working condition, and obtaining a thermal stress operation judgment value of the key parts of the in-service steam turbine under the operation working condition.

In the embodiment of the disclosure, the thermal stress judgment value of the key component under the operating condition can be determined based on the thermal stress basic data of the key component and the measuring point metal temperature basic data, and the thermal stress of the key component of the in-service steam turbine under the operating condition is monitored.

In the embodiment of the disclosure, 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.

Alternatively, the material elastic modulus, the material linear expansion coefficient, the poisson ratio, the thermal stress monitoring parameter criterion value and the simulation calculation value of the rotor volume average temperature of the key component can be obtained to serve as the thermal stress basic data of the key component.

Alternatively, the site metal temperature base data for the critical component refers to the site metal temperature for the critical component over two types of wall thickness depth ranges. Comprising the following steps: the surface temperature of the high-pressure rotor and the medium-pressure rotor, which are characterized by the metal temperature of the measuring point at the depth of 82% -98% of the wall thickness of the high-pressure inner cylinder and the medium-pressure inner cylinder, the metal temperature of the measuring point at the depth of 82% -98% of the wall thickness of the high-pressure valve casing and the medium-pressure valve casing, the metal temperature of the measuring point at the depth of 40% -60% of the wall thickness of the high-pressure valve casing and the medium-pressure valve casing, the surface temperature of the high-pressure rotor and the medium-pressure rotor, which are characterized by the metal temperature of the measuring point at the depth of 82% -98% of the wall thickness of the high-pressure inner cylinder and the medium-pressure inner cylinder, and the base data of the metal temperature of the measuring point at the depth of 40% -60% of the wall thickness of the high-pressure cylinder and the medium-pressure starting.

Alternatively, the measured point metal temperature base data may be obtained based on the turbine digital electrohydraulic control system DEH or the turbine control system TCS.

Further, the thermal stress judgment value of the in-service steam turbine under the operating condition can be determined by acquiring the thermal stress basic data of the key parts of the in-service steam turbine and the measuring point metal temperature basic data, so that whether the thermal stress judgment value of the in-service steam turbine under the operating condition is qualified or not is judged, namely whether the thermal stress judgment value of the in-service steam turbine meets the operating monitoring qualification condition or not is judged.

FIG. 4 is a schematic diagram of a method for monitoring the operation of thermal stress with high flexibility of an in-service steam turbine according to an embodiment of the disclosure, as shown in FIG. 4, the method includes the following steps:

S401, acquiring thermal stress basic data of key parts of the in-service steam turbine.

In embodiments of the present disclosure, key components of a 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 elastic modulus E, the linear expansion coefficient alpha, the Poisson ratio mu and the thermal stress monitoring parameter criterion value S of the material can be obtained _th Simulation calculation value t of rotor volume average temperature _m Thermal stress basis data for critical components of the steam turbine is determined.

Alternatively, the modulus of elasticity E of the materials of the turbine rotor, valve housing and cylinder can be obtained _jk Coefficient of linear expansion alpha _jk And poisson ratio mu _jk Design criterion value tau of total calendar life of steam turbine ₀ Corresponding thermal stress monitoring parameter criterion value S of turbine component _thjk Thermal stress basis data of (a) turbine start-up, shut-down, load variation and rotor volume average temperature for loaded operation _mjR 。

Where subscript j denotes the critical component operating environment and subscript k denotes the turbine component name.

Wherein E is _HV Modulus of elasticity, E, of the material of the high-pressure valve housing _HR Modulus of elasticity, E, of the material for the high-pressure rotor _HC Modulus of elasticity, E, of the material for high-pressure cylinders _IV Elastic modulus of material for medium pressure valve housing, E _IR Modulus of elasticity, E, of the material for the medium-pressure rotor _IC The elastic modulus of the material is the elastic modulus of the medium-pressure cylinder. Wherein, H represents high pressure, I represents medium pressure, V represents a valve casing, C represents a cylinder, and R represents a rotor.

Wherein alpha is _HV Linear expansion coefficient of material for high-pressure valve casing, alpha _HR Linear expansion coefficient of material for high-pressure rotor, alpha _HC Linear expansion coefficient of material for high-pressure cylinder, alpha _IV Linear expansion coefficient of material for medium pressure valve housing, alpha _IR Linear expansion coefficient of material for medium-pressure rotor, alpha _IC Is the linear expansion coefficient of the material of the medium pressure cylinder. Wherein, H represents high pressure, I represents medium pressure, V represents a valve casing, C represents a cylinder, and R represents a rotor.

Wherein mu _HV Poisson ratio, mu, of material for high-pressure valve casings _HR Poisson ratio, mu, of the material of the high-pressure rotor _HC Poisson ratio, mu, of the material of the high-pressure cylinder _IV Poisson ratio, mu, of the material of the medium-pressure valve housing _IR Poisson ratio, mu, of the material of the medium-pressure rotor _IC Poisson's ratio for the material of the medium pressure cylinder. Wherein, H represents high pressure, I represents medium pressure, V represents a valve casing, C represents a cylinder, and R represents a rotor.

Wherein S is _thHV Design criterion value tau for total calendar life of steam turbine ₀ Corresponding thermal stress monitoring parameter criterion value of high-pressure valve casing, S _thHR Is tau ₀ Corresponding thermal stress monitoring parameter criterion value of high-pressure rotor, S _thHC Is tau ₀ Corresponding thermal stress monitoring parameter criterion value of high-pressure cylinder, S _thIV Is tau ₀ Corresponding thermal stress monitoring parameter criterion value of medium-pressure valve casing, S _thIR Is tau ₀ Corresponding medium-pressure rotor thermal stress monitoring parameter criterion value S _thIC Is tau ₀ And the thermal stress of the corresponding medium-pressure cylinder is monitored by a parameter criterion value. Wherein H represents high pressure, IThe medium pressure, V, valve housing, C, cylinder, R, rotor.

Wherein t is _mHR Simulation calculation value t for volume average temperature of high-pressure rotor of steam turbine _mIR A simulated calculation of the volume average temperature of the medium-pressure rotor of the steam turbine is provided. Wherein H represents high pressure, and I represents medium pressure.

S402, measuring point metal temperature basic data of key parts of the in-service steam turbine are obtained.

Optionally, the measured point metal temperature base data of the key component includes: surface temperature t of high-pressure rotor and medium-pressure rotor represented by measuring point metal temperature at depth of 82% -98% of wall thickness of high-pressure inner cylinder and medium-pressure inner cylinder _jR0 Metal temperature t of measuring point at 82% -98% depth of wall thickness of high-pressure valve casing and medium-pressure valve casing _jV90 Metal temperature t of measuring point at depth of 40% -60% of wall thickness of high-pressure valve casing and medium-pressure valve casing _jV50 The surface temperature t of the high-pressure rotor and the medium-pressure rotor, which are characterized by adopting the metal temperature of the measuring point at the depth of 82% -98% of the wall thickness of the high-pressure inner cylinder and the medium-pressure inner cylinder _jR0 Basic data t of metal temperature of measuring point at depth of 40% -60% of wall thickness of high-pressure cylinder and medium-pressure starting _jC50 。

Wherein t is _HR0 The surface temperature t of the high-pressure rotor is characterized by adopting the metal temperature of the measuring point at the depth of 82% -98% of the wall thickness of the high-pressure inner cylinder _IR0 The surface temperature of the medium-pressure rotor is characterized by adopting the metal temperature of the measuring point at the depth of 82% -98% of the wall thickness of the medium-pressure inner cylinder.

Wherein t is _HV90 The metal temperature, t, is measured at the depth of 82-98% of the wall thickness of the high-pressure valve casing _IV90 The metal temperature is measured at the depth of 82% -98% of the wall thickness of the medium-pressure valve shell; t is t _HV50 The metal temperature, t, is measured at the depth of 40-60% of the wall thickness of the high-pressure valve shell _IV50 The metal temperature is measured at the depth of 40% -60% of the wall thickness of the medium-pressure valve shell; t is t _HC90 The metal temperature, t, is measured at the depth of 82-98% of the wall thickness of the high-pressure cylinder _IC90 Is at a depth of 82-98% of the wall thickness of the medium-pressure cylinderMeasuring the metal temperature; t is t _HC50 The metal temperature, t, is measured at the depth of 40-60% of the wall thickness of the high-pressure cylinder _IC50 The metal temperature is measured at the depth of 40% -60% of the wall thickness of the high-pressure cylinder. Wherein, H represents high pressure, I represents medium pressure, V represents a valve casing, and C represents a cylinder.

S403, calculating the volume average temperature difference of the key component under the operation condition on line.

In the embodiment of the disclosure, the volume average temperature difference of the key component under the operating condition can be calculated based on the metal temperature of the measuring point in the depth range of two types of wall thickness of the steam turbine.

Alternatively, the metal temperature t can be measured at a depth of 82-98% based on the wall thickness of the high-pressure valve casing of the steam turbine _HV90 And the metal temperature t of the measuring point at the depth of 40-60% of the wall thickness of the high-pressure valve shell _HV50 On-line calculating the volume average temperature difference delta t of the high-pressure valve casing of the steam turbine _mHV The calculation formula is as follows:

Δt _mHV ＝|t _HV50 -t _HV90 |

alternatively, the calculated value t may be based on a simulation of the mean temperature of the high pressure rotor volume of the turbine _mHR And the high-pressure rotor surface temperature t represented by the metal temperature of the measuring point at the depth of 82% -98% of the high-pressure inner cylinder wall thickness _HR0 On-line calculation of volume average temperature difference delta t of high-pressure rotor of steam turbine _mHR The calculation formula is as follows:

Δt _mHR ＝|t _mHR -t _HR0 |

alternatively, the metal temperature t can be measured at the depth of 82-98% based on the wall thickness of the high-pressure cylinder of the steam turbine _HC90 And the metal temperature t of the measuring point at the depth of 40-60% of the wall thickness of the high-pressure cylinder _HC50 On-line calculating the volume average temperature difference delta t of the high-pressure cylinder of the steam turbine _mHC The calculation formula is as follows:

Δt _mHC ＝|t _HC50 -t _HC90 |

Alternatively, the metal temperature t can be measured at a depth of 82% -98% based on the wall thickness of the intermediate pressure valve casing of the steam turbine _IV90 And the depth of 40% -60% of the wall thickness of the medium pressure valve shellPoint metal temperature t _IV50 On-line calculating the volume average temperature difference delta t of the medium pressure valve shell of the steam turbine _mIV The calculation formula is as follows:

Δt _mIV ＝|t _IV50 -t _IV90 |

alternatively, the calculated value t may be based on a simulation of the average temperature of the volume of the intermediate-pressure rotor of the steam turbine _mIR And the surface temperature t of the medium-pressure rotor is characterized by adopting the metal temperature of the measuring point at the depth of 82% -98% of the wall thickness of the medium-pressure inner cylinder _IR0 On-line calculation of average temperature difference delta t of medium-pressure rotor volume of steam turbine _mIR The calculation formula is as follows:

Δt _mIR ＝|t _mIR -t _IR0 |

alternatively, the metal temperature t can be measured at the depth of 82-98% based on the wall thickness of the intermediate pressure cylinder of the steam turbine _IC90 And the metal temperature t of the measuring point at the depth of 40-60% of the wall thickness of the medium-pressure cylinder _IC50 On-line calculating the average temperature difference delta t of the volume of the medium-pressure cylinder of the steam turbine _mIC The calculation formula is as follows:

Δt _mIC ＝|t _IC50 -t _IC90 |

s404, calculating the temperature difference value of the key parts of the steam turbine on line.

In embodiments of the present disclosure, a turbine critical component temperature difference ratio may be calculated based on a critical component volume average temperature difference and thermal stress base data.

Alternatively, the high pressure valve housing volume average temperature differential Δt may be based on _mHV Elastic modulus E of material of high-pressure valve housing _HV Linear expansion coefficient alpha of material of high-pressure valve casing _HV Poisson ratio mu of material of high-pressure valve casing _HV τ ₀ Thermal stress monitoring parameter criterion value S of corresponding high-pressure valve casing _thHV On-line calculating the temperature difference ratio R of high-pressure valve casing of steam turbine _ΔtHV The calculation formula is as follows:

alternatively, the high pressure rotor volume average temperature difference Δt may be based on _mHR Modulus of elasticity E of material of high-pressure rotor _HR Linear expansion coefficient alpha of material of high-pressure rotor _HR Poisson ratio mu of material of high-pressure rotor _HR τ ₀ Corresponding thermal stress monitoring parameter criterion value S of high-pressure rotor _thHR On-line calculating the temperature difference ratio R of the high-pressure rotor of the steam turbine _ΔtHR The calculation formula is as follows:

alternatively, the high pressure cylinder volume average temperature difference Δt may be based on _mHC Modulus of elasticity E of material for high-pressure cylinder _HC Linear expansion coefficient alpha of material of high-pressure cylinder _HC Poisson ratio mu of material of high-pressure cylinder _HC τ ₀ Thermal stress monitoring parameter criterion value S of corresponding high-pressure cylinder _thHC On-line calculating the temperature difference ratio R of high-pressure cylinder of steam turbine _ΔtHC The calculation formula is as follows:

alternatively, the volume average temperature difference Δt may be based on the medium pressure valve housing _mIV Elastic modulus E of material of medium pressure valve housing _IV Linear expansion coefficient alpha of material of medium pressure valve casing _IV Poisson ratio mu of material of medium-pressure valve casing _IV τ ₀ Thermal stress monitoring parameter criterion value S of corresponding medium-pressure valve casing _thIV On-line calculating temperature difference ratio R of medium-pressure valve casing of steam turbine _ΔtIV The calculation formula is as follows:

alternatively, the medium pressure rotor volume average temperature difference Δt may be based on _mIR Elastic modulus E of material of medium-pressure rotor _IR Linear expansion of material of medium-pressure rotorCoefficient alpha _IR Poisson ratio mu of medium-pressure rotor material _IR τ ₀ Corresponding medium-pressure rotor thermal stress monitoring parameter criterion value S _thIR On-line calculating temperature difference ratio R of medium-pressure rotor of steam turbine _ΔtIR The calculation formula is as follows:

alternatively, the medium pressure cylinder volume average temperature difference Δt may be based on _mIC Modulus of elasticity E of the material of the medium-pressure cylinder _IC Linear expansion coefficient alpha of material of medium-pressure cylinder _IC Poisson ratio mu of material of medium-pressure cylinder _IC τ ₀ Thermal stress monitoring parameter criterion value S of corresponding medium-pressure cylinder _thIC On-line calculating temperature difference ratio R of medium-pressure cylinder of steam turbine _ΔtIC The calculation formula is as follows:

s405, judging whether the thermal stress judgment value of the key part of the steam turbine meets the operation monitoring qualification condition.

In the embodiment of the disclosure, the thermal stress determination value of the turbine key component is namely the temperature difference value of the turbine key component. The operation monitoring qualification 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.

Optionally, the thermal stress judgment value of the key component of the in-service steam turbine meets the operation monitoring qualification condition that:

(R _ΔtHV <1)∩(R _ΔtHR <1)∩(R _ΔtHC <1)∩(R _ΔtIV <1)∩(R _ΔtIR <1)∩(R _ΔtIC <1)

optionally, the thermal stress determination value of the critical component of the in-service steam turbine does not meet the operation monitoring qualification condition is:

(R _ΔtHV ≥1)∪(R _ΔtHR ≥1)∪(R _ΔtHC ≥1)∪(R _ΔtIV ≥1)∪(R _ΔtIR ≥1)∪(R _ΔtIC ≥1)

s406, generating an in-service steam turbine optimized operation strategy in response to the thermal stress judgment value of the in-service steam turbine not meeting the operation monitoring qualification condition.

In the embodiment of the disclosure, the thermal stress judgment value of the in-service turbine does not meet the operation monitoring qualification condition, which indicates that the turbine inlet steam temperature change rate or the load change rate in the operation stage is overlarge and needs to be reduced.

Optionally, the starting process or the loading climbing process of the steam turbine needs to be optimized in the operation stage, monitoring information is fed back to the digital electrohydraulic control system DEH or the control system TCS of the steam turbine, the change rate of the inlet steam temperature of the steam turbine is reduced to be 0.8-0.9 times of the current change rate of the load of the steam turbine or to be 0.8-0.9 times of the current change rate of the load of the steam turbine, electric tracing bands are used for heating in the starting and on-load climbing processes of the steam turbine to reduce the thermal stress of key parts, the thermal stress judgment value of the steam turbine under the operation working condition is continuously calculated on line, the operation monitoring is optimized until the thermal stress judgment value meets the operation monitoring qualification condition, and the operation optimization is ended.

In the high-flexibility thermal stress operation monitoring method for the in-service steam turbine, whether the thermal stress of the in-service steam turbine is monitored is qualified or not is determined by performing operation monitoring on the thermal stress of the in-service steam turbine under the operation working condition, and the steam turbine which is not qualified in monitoring is subjected to operation optimization control, so that the long service life and the high flexibility of the in-service steam turbine are guaranteed.

The following on-line monitoring data is obtained from monitoring information at a certain moment of starting up a loaded climbing and fed back to a digital electrohydraulic control system DEH or a turbine control system TCS of the turbine for the model of the turbine, namely, the high-pressure valve housing, the high-pressure rotor, the high-pressure cylinder, the medium-pressure valve housing, the medium-pressure rotor and the medium-pressure cylinder, based on the model of the ultra-supercritical 1050MW once-reheat turbine.

High pressure valve casing wall thickness 82% -98% depthMetal temperature t at point of measurement _HV90 ＝582.97℃；

Metal temperature t of measuring point at depth of 40% -60% of wall thickness of high-pressure valve casing _HV50 ＝541.16℃；

High-pressure rotor surface temperature t represented by measuring point metal temperature at depth of 82% -98% of high-pressure inner cylinder wall thickness _HR0 ＝578.26℃；

Metal temperature t of measuring point at depth of 82% -98% of wall thickness of high-pressure cylinder _HC90 ＝376.81℃；

Metal temperature t of measuring point at depth of 40% -60% of wall thickness of high-pressure cylinder _HC50 ＝326.68℃；

Metal temperature t of measuring point at depth of 82% -98% of wall thickness of medium pressure valve casing _IV90 ＝580.97℃；

Metal temperature t of measuring point at depth of 40% -60% of wall thickness of medium pressure valve casing _IV50 ＝538.67℃；

The surface temperature t of the medium-pressure rotor is characterized by adopting the metal temperature of a measuring point at the depth of 82% -98% of the wall thickness of the medium-pressure inner cylinder _IR0 ＝573.09℃；

Metal temperature t of measuring point at depth of 82% -98% of wall thickness of medium pressure cylinder _IC90 ＝285.02℃；

Metal temperature t of measuring point at depth of 40% -60% of wall thickness of medium pressure cylinder _IC50 ＝234.13℃。

Volume average temperature difference delta t of high-pressure valve casing of steam turbine of this model _mHV The online calculation result of (a) is as follows:

Δt _mHV ＝|t _HV50 -t _HV90 |＝|541.16-582.97|＝41.81℃

using the data processing server 26, the simulation calculation value of the volume average temperature of the high-pressure rotor of the steam turbine of the model is t _mHR On-line calculation of high-pressure rotor volume average temperature difference Δt= 510.31 ℃ _mHR The result of (2) is:

Δt _mHR ＝|t _mHR -t _HR0 |＝|510.31-578.26|＝67.95℃

alternatively, the high pressure cylinder volume average temperature difference delta t of the model turbine _mHC The online calculation result of (a) is as follows:

Δt _mHC ＝|t _HC50 -t _HC90 |＝|326.68-376.81|＝50.13℃

alternatively, the high pressure valve housing volume average temperature difference Deltat of the steam turbine model _mIV The online calculation result of (a) is as follows:

Δt _mIV ＝|t _IV50 -t _IV90 |＝|538.67-580.97|＝42.30℃

using the data processing server 26, the simulation calculation value of the volume average temperature of the medium pressure rotor of the steam turbine of the model is t _mIR = 496.42 ℃, online calculation of medium-pressure rotor volume average temperature difference Δt _mIR The result of (2) is:

Δt _mIR ＝|t _mIR -t _IR0 |＝|496.42-573.09|＝76.67℃

alternatively, the medium pressure cylinder volume average temperature difference delta t of the steam turbine _mIC The online calculation result of (a) is as follows:

Δt _mIC ＝|t _IC50 -t _IC90 |＝|234.13-285.02|＝50.89℃。

the data processing server 26 is used, the high-pressure valve casing material is ZG1Cr10MoWVNbN, and the metal temperature t is measured according to the depth of 40-60% of the wall thickness of the high-pressure valve casing _HV50 On-line calculation of the modulus of elasticity E of the material of the high-pressure valve housing at = 541.16 ℃ _HV ＝1.736×10 ⁵ Linear expansion coefficient alpha of material of MPa, high-pressure valve casing _HV ＝12.08×10 ^-6 (1/DEGC), poisson's ratio mu for high pressure valve housing material _HV =0.302 and τ ₀ Thermal stress monitoring parameter criterion value S of corresponding high-pressure valve casing _thHV =521 MPa, the high-pressure valve casing temperature difference ratio R of the steam turbine _ΔtHV The online calculation result is as follows:

the high-pressure rotor material is X12 CrMoWVBN 10-1-1, and the simulation calculated value according to the volume average temperature of the high-pressure rotor is t _mHR On-line calculation of high pressure rotor Material elastic modulus E at = 510.31 ℃ _HR ＝1.810×10 ⁵ MPa, high pressureCoefficient of linear expansion alpha of material of rotor _HR ＝12.03×10 ^-6 (1/DEGC), poisson's ratio μ of the material of the high-pressure rotor _HR =0.310, and τ ₀ Corresponding thermal stress monitoring parameter criterion value S of high-pressure rotor _thHR =672 MPa, the high-pressure rotor temperature difference ratio R of the steam turbine _ΔtHR The online calculation result of (a) is as follows:

the high-pressure cylinder material is ZG15CrMoV, and the metal temperature t is measured according to the depth of 40% -60% of the wall thickness of the high-pressure cylinder _HC50 On-line calculation of the modulus of elasticity E of the material for high pressure cylinders = 326.68 ℃ _HC ＝1.979×10 ⁵ Linear expansion coefficient alpha of material of MPa and high-pressure cylinder _HC ＝13.32×10 ^-6 (1/DEGC), poisson's ratio μ of the material of the high-pressure cylinder _HC =0.280 and τ ₀ Thermal stress monitoring parameter criterion value S of corresponding high-pressure cylinder _thHC =452 MPa, the high pressure cylinder temperature difference ratio R of the steam turbine of this type _ΔtHC The online calculation result of (a) is as follows:

the medium-pressure valve casing material is ZG1Cr10MoWVNbN, and the metal temperature t is measured at the depth of 40-60% according to the wall thickness of the medium-pressure valve casing _IV50 On-line calculation of the modulus of elasticity E of the material of the medium pressure valve housing = 538.67 ℃ _IV 1.739×10 ⁵ Linear expansion coefficient alpha of material of MPa, medium pressure valve casing _IV ＝12.08×10 ^-6 (1/DEGC), poisson's ratio μ of the material of the medium pressure valve housing _IV =0.302 and τ ₀ Thermal stress monitoring parameter criterion value S of corresponding medium-pressure valve casing _thIV =534 MPa, the temperature difference ratio R of the medium-pressure valve casing of the steam turbine of this type _ΔtIV The online calculation result of (a) is as follows:

the medium-pressure rotor material is X12 CrMoWVBN 10-1-1, and the simulation calculated value according to the volume average temperature of the medium-pressure rotor is t _mIR On-line calculation of material modulus E for Medium pressure rotors at 496.42 =5248℃ _IR ＝1.823×10 ⁵ Linear expansion coefficient alpha of material of MPa and medium-pressure rotor _IR ＝11.98×10 ⁵ Poisson ratio mu of material of MPa medium-pressure rotor _IR =0.310 and τ ₀ Corresponding medium-pressure rotor thermal stress monitoring parameter criterion value S _thIR =684mpa, the medium-pressure rotor temperature difference ratio R of this type of steam turbine _ΔtIR The online calculation result of (a) is as follows:

the medium-pressure cylinder is made of ZG15CrMoV, and the metal temperature t is measured according to the depth of 40% -60% of the wall thickness of the medium-pressure cylinder _IC50 On-line calculation of modulus of elasticity E of material for medium pressure cylinder = 234.13 ℃ _IC Linear expansion coefficient alpha of material of medium-pressure cylinder _IC Poisson ratio mu of material of medium-pressure cylinder _IC τ ₀ Thermal stress monitoring parameter criterion value S of corresponding medium-pressure cylinder _thIC Temperature difference ratio R of medium-pressure cylinder of steam turbine of this model _ΔtIC The online calculation result of (a) is as follows:

in summary, the result that the thermal stress judgment value of the model ultra-supercritical 1050MW single-reheat steam turbine meets the operation monitoring qualification condition is as follows:

(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)

when the model ultra-supercritical 1050MW steam turbine is in an operation working condition, the thermal stress judging value meets the operation monitoring qualification condition, the thermal stress of the model ultra-supercritical 1050MW steam turbine is in a controlled state under the operation working condition at the moment, monitoring information is fed back to a digital electrohydraulic control system DEH or a turbine control system TCS of the steam turbine, the steam turbine is continuously started and climbs according to the existing steam turbine inlet temperature change rate or the steam turbine load change rate, the steam turbine thermal stress operation is continuously monitored, and the follow-up monitoring flow is entered.

In order to achieve the above embodiments, the present disclosure further provides a thermal stress operation monitoring device with high flexibility for an in-service steam turbine.

Fig. 5 is a schematic structural diagram of a thermal stress operation monitoring device with high flexibility for an in-service steam turbine according to an embodiment of the disclosure.

As shown in fig. 5, the high-flexibility thermal stress operation monitoring device 500 of the in-service steam turbine comprises:

a first acquisition module 501 is configured to acquire thermal stress base data for critical components of an in-service steam turbine.

And a second acquisition module 502, configured to acquire measurement point metal temperature base data of the key component.

And the judging module 503 is configured to judge whether the thermal stress of the in-service steam turbine under the operating condition meets the operation monitoring qualification condition based on the thermal stress basic data and the measuring point metal temperature basic data.

And an optimizing module 504, configured to optimize the operation strategy of the in-service steam turbine in response to the operation monitoring qualification condition not being met.

In a possible implementation manner of the embodiment of the present disclosure, the first obtaining module 501 is further configured to: acquiring the material elastic modulus, the linear expansion coefficient and the poisson ratio of the key component; acquiring a thermal stress monitoring parameter criterion value of the key component corresponding to a calendar total service life design criterion value of the in-service steam turbine; and obtaining a simulation calculation value of the first volume average temperature of the high-pressure rotor and a simulation calculation value of the second volume average temperature of the medium-pressure rotor in the in-service steam turbine.

In a possible implementation manner of the embodiment of the present disclosure, the second obtaining module 502 is further configured to: sampling metal temperature in a first wall thickness depth range appointed by the key component, and obtaining a first measuring point metal temperature of the key component; and sampling the metal temperature in a second wall thickness depth range appointed by the key component, and obtaining the metal temperature of a second measuring point of the key component.

In a possible implementation manner of the embodiment of the present disclosure, the determining module 503 is further configured to: acquiring a volume average temperature difference of the key component based on the first measuring point metal temperature and the second measuring point metal temperature; acquiring a temperature difference ratio of the key component as the thermal stress judgment value according to the volume average temperature difference of the key component and the thermal stress basic data; and judging whether the thermal stress of the in-service steam turbine meets the operation monitoring qualification condition according to the thermal stress judgment value of the key component.

In a possible implementation manner of the embodiment of the present disclosure, the determining module 503 is further configured to: determining that the thermal stress of the in-service steam turbine meets the operation monitoring qualification condition in response to the thermal stress determination value of each key component being smaller than a set value; and if at least one thermal stress judgment value of the key component is larger than or equal to the set value, determining that the thermal stress of the in-service steam turbine does not meet the operation monitoring qualification condition.

In one possible implementation of the embodiment of the disclosure, the first wall thickness depth range is 82% to 98% of the wall thickness depth, and the second wall thickness depth range is 40% to 60% of the wall thickness depth.

In one possible implementation of the embodiment of the disclosure, the optimization module 504 is further configured to: acquiring the current steam inlet temperature change rate and/or load change rate of the in-service steam turbine, and reducing the steam inlet temperature change rate and/or load change rate.

In one possible implementation of the embodiment of the disclosure, the optimization module 504 is further configured to: and operating according to the optimized operation strategy, re-acquiring the thermal stress judgment value of the key component, and executing the subsequent steps until the thermal stress of the key component meets the operation monitoring qualification condition, and ending operation optimization.

In one possible implementation manner of the embodiment of the disclosure, the operation condition is all operation processes of starting, grid connection, load lifting, stable load carrying, full load, load lowering, disconnection, shutdown and the like of the in-service steam turbine, including rapid starting and/or rapid load variation climbing transient conditions.

In the high-flexibility thermal stress operation monitoring device for the in-service steam turbine, the thermal stress basic data and the measuring point metal temperature basic data of the key component of the in-service steam turbine are obtained through operation monitoring of the in-service steam turbine, and then the thermal stress judgment value of the key component under the operation working condition is determined. And further judging whether the thermal stress judgment value meets the operation monitoring qualification condition, and under the condition that the operation monitoring qualification condition is not met, performing operation optimization control on the steam turbine, and repeating the operation until the thermal stress judgment value meets the operation monitoring qualification condition, thereby ensuring long service life and high flexibility of the design of the steam turbine.

It should be noted that the foregoing explanation of the embodiment of the method for monitoring the operation of the thermal stress with high flexibility of the in-service steam turbine is also applicable to the device for monitoring the operation of the thermal stress with high flexibility of the in-service steam turbine of this embodiment, and will not be repeated here.

In order to achieve the above embodiments, the present disclosure further proposes an electronic device including: a processor, and a memory communicatively coupled to the processor; the memory stores computer-executable instructions; the processor executes the computer-executable instructions stored in the memory to implement the methods provided by the previous embodiments.

In order to implement the above-described embodiments, the present disclosure also proposes a computer-readable storage medium having stored therein computer-executable instructions that, when executed by a processor, are adapted to implement the methods provided by the foregoing embodiments.

To achieve the above embodiments, the present disclosure also proposes a computer program product comprising a computer program which, when executed by a processor, implements the method provided by the foregoing embodiments.

The processes of collecting, storing, using, processing, transmitting, providing, disclosing and the like of the personal information of the user involved in the present disclosure all conform to the regulations of the relevant laws and regulations and do not violate the public order colloquial.

It should be noted that personal information from users should be collected for legitimate and reasonable uses and not shared or sold outside of these legitimate uses. In addition, such collection/sharing should be performed after receiving user informed consent, including but not limited to informing the user to read user agreements/user notifications and signing agreements/authorizations including authorization-related user information before the user uses the functionality. In addition, any necessary steps are taken to safeguard and ensure access to such personal information data and to ensure that other persons having access to the personal information data adhere to their privacy policies and procedures.

The present disclosure contemplates embodiments that may provide a user with selective prevention of use or access to personal information data. That is, the present disclosure contemplates that hardware and/or software may be provided to prevent or block access to such personal information data. Once personal information data is no longer needed, risk can be minimized by limiting data collection and deleting data. In addition, personal identification is removed from such personal information, as applicable, to protect the privacy of the user.

In the foregoing descriptions of embodiments, descriptions of the terms "one embodiment," "some embodiments," "examples," "particular examples," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the disclosure. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present disclosure, the meaning of "a plurality" is at least two, such as two, three, etc., unless explicitly specified otherwise.

Any process or method descriptions in flow charts or otherwise described herein may be understood as representing modules, segments, or portions of code which include one or more executable instructions for implementing specific logical functions or steps of the process, and additional implementations are included within the scope of the preferred embodiment of the present disclosure in which functions may be executed out of order from that shown or discussed, including substantially concurrently or in reverse order, depending on the functionality involved, as would be understood by those reasonably skilled in the art of the embodiments of the present disclosure.

Logic and/or steps represented in the flowcharts or otherwise described herein, e.g., a ordered listing of executable instructions for implementing logical functions, can be embodied in any computer-readable medium for use by or in connection with an instruction execution system, apparatus, or device, such as a computer-based system, processor-containing system, or other system that can fetch the instructions from the instruction execution system, apparatus, or device and execute the instructions. For the purposes of this description, a "computer-readable medium" can be any means that can contain, store, communicate, propagate, or transport the program for use by or in connection with the instruction execution system, apparatus, or device. More specific examples (a non-exhaustive list) of the computer-readable medium would include the following: an electrical connection (electronic device) having one or more wires, a portable computer diskette (magnetic device), a Random Access Memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber device, and a portable compact disc read-only memory (CDROM). In addition, the computer readable medium may even be paper or other suitable medium on which the program is printed, as the program may be electronically captured, via, for instance, optical scanning of the paper or other medium, then compiled, interpreted or otherwise processed in a suitable manner, if necessary, and then stored in a computer memory.

It should be understood that portions of the present disclosure may be implemented in hardware, software, firmware, or a combination thereof. In the above-described embodiments, the various steps or methods may be implemented in software or firmware stored in a memory and executed by a suitable instruction execution system. As with the other embodiments, if implemented in hardware, may be implemented using any one or combination of the following techniques, as is well known in the art: discrete logic circuits having logic gates for implementing logic functions on data signals, application specific integrated circuits having suitable combinational logic gates, programmable Gate Arrays (PGAs), field Programmable Gate Arrays (FPGAs), and the like.

Those of ordinary skill in the art will appreciate that all or a portion of the steps carried out in the method of the above-described embodiments may be implemented by a program to instruct related hardware, where the program may be stored in a computer readable storage medium, and where the program, when executed, includes one or a combination of the steps of the method embodiments.

Furthermore, each functional unit in the embodiments of the present disclosure may be integrated in one processing module, or each unit may exist alone physically, or two or more units may be integrated in one module. The integrated modules may be implemented in hardware or in software functional modules. The integrated modules may also be stored in a computer readable storage medium if implemented in the form of software functional modules and sold or used as a stand-alone product.

The above-mentioned storage medium may be a read-only memory, a magnetic disk or an optical disk, or the like. Although embodiments of the present disclosure have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the present disclosure, and that variations, modifications, alternatives, and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the present disclosure.

Claims

1. The high-flexibility thermal stress operation monitoring method for the in-service steam turbine is characterized by comprising the following steps of:

acquiring thermal stress basic data of key parts of the in-service steam turbine;

acquiring measuring point metal temperature basic data of the key component;

judging whether the thermal stress of the in-service steam turbine under the operating condition meets the operating monitoring qualification condition or not based on the thermal stress basic data and the measuring point metal temperature basic data;

and in response to the operation monitoring qualification condition not being met, optimizing the operation strategy of the in-service steam turbine.

2. The method of claim 1, wherein the obtaining thermal stress base data for critical components of an in-service steam turbine comprises:

acquiring the material elastic modulus, the linear expansion coefficient and the poisson ratio of the key component;

Acquiring a thermal stress monitoring parameter criterion value of the key component corresponding to a calendar total service life design criterion value of the in-service steam turbine;

and obtaining a simulation calculation value of the first volume average temperature of the high-pressure rotor and a simulation calculation value of the second volume average temperature of the medium-pressure rotor in the in-service steam turbine.

3. The method of claim 1, wherein the obtaining site metal temperature base data for the critical component comprises:

sampling metal temperature in a first wall thickness depth range appointed by the key component, and obtaining a first measuring point metal temperature of the key component;

and sampling the metal temperature in a second wall thickness depth range appointed by the key component, and obtaining the metal temperature of a second measuring point of the key component.

4. A method according to claim 3, wherein said determining whether the thermal stress of the in-service turbine under operating conditions meets an operation monitoring qualification condition based on the thermal stress base data and the site metal temperature base data comprises:

acquiring a volume average temperature difference of the key component based on the first measuring point metal temperature and the second measuring point metal temperature;

Acquiring a temperature difference ratio of the key component as the thermal stress judgment value according to the volume average temperature difference of the key component and the thermal stress basic data;

and judging whether the thermal stress of the in-service steam turbine meets the operation monitoring qualification condition according to the thermal stress judgment value of the key component.

5. The method of claim 4, wherein determining whether the thermal stress of the in-service turbine meets an operational monitoring qualification condition based on the thermal stress determination value of the critical component comprises:

determining that the thermal stress of the in-service steam turbine meets the operation monitoring qualification condition in response to the thermal stress determination value of each key component being smaller than a set value;

and if at least one thermal stress judgment value of the key component is larger than or equal to the set value, determining that the thermal stress of the in-service steam turbine does not meet the operation monitoring qualification condition.

6. A method according to claim 3, wherein the first wall thickness depth range is 82% to 98% of the wall thickness depth and the second wall thickness depth range is 40% to 60% of the wall thickness depth.

7. The method of any one of claims 1-6, wherein optimizing the operating strategy of the in-service steam turbine comprises:

Acquiring the current steam inlet temperature change rate and/or load change rate of the in-service steam turbine, and reducing the steam inlet temperature change rate and/or load change rate.

8. The method of claim 7, wherein said optimizing said operating strategy of said in-service steam turbine further comprises:

and operating according to the optimized operation strategy, re-acquiring the thermal stress judgment value of the key component, and executing the subsequent steps until the thermal stress of the key component meets the operation monitoring qualification condition, and ending operation optimization.

9. The method of claim 1, wherein the operating conditions are all operating processes of startup, grid connection, load lifting, stable load, full load, load dropping, disconnection, shutdown and the like of the in-service steam turbine, and the operating conditions comprise fast startup and/or fast load variation climbing transient conditions.

10. High-flexibility thermal stress operation monitoring device of in-service steam turbine, characterized by comprising:

the first acquisition module is used for acquiring thermal stress basic data of key components of the in-service steam turbine;

the second acquisition module is used for acquiring the metal temperature basic data of the measuring point of the key component;

The judging module is used for judging whether the thermal stress of the in-service steam turbine under the operating condition meets the operating monitoring qualification condition or not based on the thermal stress basic data and the measuring point metal temperature basic data;

and the optimizing module is used for optimizing the operation strategy of the in-service steam turbine in response to the condition that the operation monitoring qualification condition is not met.

11. The apparatus of claim 10, wherein the first acquisition module is further configured to:

12. The apparatus of claim 10, wherein the second acquisition module is further configured to:

13. The apparatus of claim 12, wherein the determining module is further configured to:

14. The apparatus of claim 13, wherein the determining module is further configured to:

15. The device of claim 12, wherein the first wall thickness depth range is 82% to 98% of the wall thickness depth and the second wall thickness depth range is 40% to 60% of the wall thickness depth.

16. The apparatus of any one of claims 10-15, wherein the optimization module is further configured to:

17. The apparatus of claim 16, wherein the optimization module is further configured to:

18. The apparatus of claim 10, wherein the operating conditions are all operating processes of startup, grid connection, load lifting, stable load, full load, load dropping, disconnection, shutdown, etc. of the in-service steam turbine, including fast startup and/or fast load variation climbing transient conditions.

19. An electronic device, comprising:

a processor, and a memory communicatively coupled to the processor;

the memory stores computer-executable instructions;

the processor executes computer-executable instructions stored in the memory to implement the method of any one of claims 1-9.

20. A computer readable storage medium having stored therein computer executable instructions which when executed by a processor are adapted to carry out the method of any one of claims 1-9.

21. A computer program product comprising a computer program which, when executed by a processor, implements the method of any of claims 1-9.