Method and device for obtaining equivalent stress of deep peak-shaving steam turbine

Abstract

The present application proposes a method and device for obtaining equivalent stress of a deep peak-shaving steam turbine, the method comprising: obtaining thermal stress of high-temperature key components of the deep peak-shaving steam turbine in all directions, obtaining mechanical stress of high-temperature key components in all directions, determining the composite stress of high-temperature key components in all directions according to the thermal stress in all directions and the mechanical stress in all directions, and determining the first equivalent stress of high-temperature key components according to the composite stress of high-temperature key components in all directions, wherein the first equivalent stress has positive and negative properties. In the present application, the first equivalent stress with positive and negative signs of high-temperature key components can be determined according to thermal stress and mechanical stress, so as to provide a calculation basis for stress-related data and life-related data for subsequent closed-loop control of steam turbine speed and load, so that closed-loop control based on stress and life can be performed to achieve long life and flexible operation of the steam turbine.

Description

Technical Field

[0001] The present application relates to the technical field of steam turbines, and in particular to a method and device for obtaining the equivalent stress of a deep peak-shaving steam turbine. Background Art

[0002] In the context of building a new power system with new energy as the main body, renewable energy such as wind power and solar energy has developed rapidly. In view of the intermittent, random and volatile problems in renewable energy power generation, it is required that the power station steam turbine be deeply peak-shifted and flexibly operated and transformed into emergency guarantee and flexible adjustment power supply to provide a bottom-line guarantee for power supply. The deep peak-shifting, rapid start-up and rapid load change of the steam turbine lead to increased thermal stress and shortened life of the high-temperature components of the steam turbine, affecting the service life and safety of the steam turbine. Summary of the invention

[0003] The embodiments of the present application provide a method and device for obtaining the equivalent stress of a deep peak-shaving steam turbine.

[0004] The first embodiment of the present application proposes a method for obtaining the equivalent stress of a deep peak-shaving steam turbine, comprising:

[0005] Obtain the thermal stress of high-temperature key components of deep peak-shaving steam turbines in all directions;

[0006] Obtaining the mechanical stress of the high-temperature key component in each direction;

[0007] Determine the composite stress of the high-temperature key component in each direction according to the thermal stress in each direction and the mechanical stress in each direction;

[0008] According to the synthetic stress of the high-temperature key component in each direction, the first equivalent stress of the high-temperature key component is determined, and the first equivalent stress has positive and negative properties.

[0009] The second embodiment of the present application proposes a device for obtaining equivalent stress of a deep peak-shaving steam turbine, comprising:

[0010] The first acquisition module is used to obtain the thermal stress of the high-temperature key components of the deep peak-shaving steam turbine in various directions;

[0011] A second acquisition module is used to acquire the mechanical stress of the high-temperature key component in various directions;

[0012] A first determination module is used to determine the composite stress of the high-temperature key component in each direction according to the thermal stress in each direction and the mechanical stress in each direction;

[0013] The second determination module is used to determine the first equivalent stress of the high-temperature key component according to the synthetic stress of the high-temperature key component in each direction, and the first equivalent stress has positive and negative properties.

[0014] The third aspect of the present application provides an electronic device, including:

[0015] one or more processors;

[0016] a memory for storing instructions executable by the processor;

[0017] Among them, the processor is configured to execute the instructions to implement the method proposed in the embodiment of the first aspect of the present application.

[0018] The fourth aspect embodiment of the present application proposes a non-temporary computer-readable storage medium. When the instructions in the storage medium are executed by the processor of an electronic device, the electronic device can execute the method proposed in the first aspect embodiment of the present application.

[0019] The fifth aspect embodiment of the present application proposes a computer program product, including a computer program, which implements the method proposed in the first aspect embodiment of the present application when executed by a processor in a communication device.

[0020] The technical solution provided by the embodiments of the present application brings at least the following beneficial effects:

[0021] The thermal stress of high-temperature key components can be determined based on the temperature difference and material physical properties of high-temperature key components, and the mechanical stress of high-temperature key components can be determined based on relevant basic data. Further, based on the thermal stress and mechanical stress, the first equivalent stress with positive and negative signs of the high-temperature key components can be determined to provide a calculation basis for stress-related data and life-related data for subsequent turbine control, thereby enabling closed-loop control based on stress and life to achieve long life and flexible operation of the turbine.

[0022] It should be understood that the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the following description of the embodiments in conjunction with the accompanying drawings, in which:

[0024] Figure 1 A schematic flow chart of a method for obtaining equivalent stress of a deep peak-shaving steam turbine provided in an embodiment of the present application;

[0025] Figure 2A schematic flow chart of another method for obtaining equivalent stress of a deep peak-shaving steam turbine provided in an embodiment of the present application;

[0026] Figure 3 A schematic flow chart of another method for obtaining equivalent stress of a deep peak-shaving steam turbine provided in an embodiment of the present application;

[0027] Figure 3a A schematic diagram of a process for determining the average volume temperature of a high-temperature rotor provided in an embodiment of the present application;

[0028] Figure 3b A process for determining the center temperature of a high-temperature rotor provided in an embodiment of the present application is intended;

[0029] Figure 4 A schematic diagram of the structure of a device for obtaining equivalent stress of a deep peak-shaving steam turbine provided in an embodiment of the present application;

[0030] Figure 5 A schematic diagram of the structure of an electronic device provided in an embodiment of the present application;

[0031] Figure 6 A schematic diagram of the structure of another electronic device provided in an embodiment of the present application. DETAILED DESCRIPTION

[0032] Exemplary embodiments will be described in detail herein, examples of which are shown in the accompanying drawings. When the following description refers to the drawings, unless otherwise indicated, the same numbers in different drawings represent the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the embodiments of the present application. Instead, they are merely examples of devices and methods consistent with some aspects of the embodiments of the present application as detailed in the appended claims.

[0033] The terms used in the embodiments of the present application are only for the purpose of describing specific embodiments, and are not intended to limit the embodiments of the present application. The singular forms of "a" and "the" used in the embodiments of the present application and the appended claims are also intended to include plural forms, unless the context clearly indicates other meanings. It should also be understood that the term "and / or" used herein refers to and includes any or all possible combinations of one or more associated listed items.

[0034] It should be understood that, although the terms first, second, third, etc. may be used to describe various information in the embodiments of the present application, these information should not be limited to these terms. These terms are only used to distinguish the same type of information from each other. For example, without departing from the scope of the embodiments of the present application, the first information may also be referred to as the second information, and similarly, the second information may also be referred to as the first information. Depending on the context, the words "if" and "if" as used herein may be interpreted as "at..." or "when..." or "in response to determination".

[0035] The embodiments of the present application are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present application, and should not be construed as limiting the present application.

[0036] It should be noted that the equivalent stress acquisition method of the deep peak-shaving steam turbine provided in any embodiment of the present application can be executed alone, or can be executed in combination with possible implementation methods in other embodiments, or can be executed in combination with any technical solution in the related technology.

[0037] The following describes the method, device, electronic device and storage medium for obtaining the equivalent stress of the deep peak-shaving steam turbine disclosed in the present invention with reference to the accompanying drawings.

[0038] Figure 1 A schematic flow chart of a method for obtaining equivalent stress of a deep peak-shaving steam turbine provided in an embodiment of the present application. Figure 1 As shown, the method includes but is not limited to the following steps:

[0039] S101, obtaining thermal stresses of high-temperature key components of the deep peak-shaving steam turbine in various directions.

[0040] In an embodiment of the present application, the high-temperature key components of the deep peak-shaving steam turbine include a main steam valve housing, a regulating valve housing, a high-temperature rotor and a high-temperature cylinder. The main steam valve housing of the steam turbine includes an ultra-high-pressure main steam valve housing, a high-pressure main steam valve housing and a medium-pressure main steam valve housing. The regulating valve housing of the steam turbine includes an ultra-high-pressure regulating valve housing, a high-pressure regulating steam valve housing and a medium-pressure regulating valve housing. The high-temperature rotor of the steam turbine includes an ultra-high-pressure rotor, a high-pressure rotor and a medium-pressure rotor. The high-temperature outer cylinder of the steam turbine includes an ultra-high-pressure outer cylinder, a high-pressure outer cylinder and a medium-pressure outer cylinder.

[0041] In some implementations, high temperature critical components of the steam turbine are associated with the reheat type of the steam turbine.

[0042] In the embodiment of the present application, the reheat type of the steam turbine is determined. Optionally, the reheat type of the steam turbine can be determined based on the equipment information or model information of the steam turbine. The reheat type can include double reheat, single reheat and no reheat. Further, according to the reheat type of the steam turbine, the high temperature key components of the steam turbine are determined.

[0043] Optionally, if the steam turbine is a secondary reheat steam turbine, the high-temperature key components of the steam turbine include the main steam valve housings of the ultra-high pressure cylinder, the high pressure cylinder and the medium pressure cylinder, the regulating valve housings, the high-temperature rotor and the high-temperature outer cylinder.

[0044] Optionally, if the steam turbine is a single reheat steam turbine, the high-temperature key components of the steam turbine include the main steam valve housings of the high-pressure cylinder and the medium-pressure cylinder, the regulating valve housings, the high-temperature rotor and the high-temperature outer cylinder.

[0045] Optionally, if the steam turbine is a non-reheat steam turbine, the high-temperature key components of the steam turbine include a main steam valve housing of the high-pressure cylinder, a regulating valve housing, a high-temperature rotor and a high-temperature outer cylinder.

[0046] In some embodiments, the temperature difference of the high temperature key component is determined, and the tangential thermal stress and axial thermal stress of the high temperature key component are determined according to the material physical properties of the high temperature key component and the temperature difference, wherein the radial thermal stress of the high temperature key component is zero.

[0047] In some embodiments, the material physical properties of the high temperature critical component may include, but are not limited to: the material linear expansion coefficient, the material elastic modulus, and the material Poisson's ratio of the high temperature critical component.

[0048] Optionally, if the high temperature key component is a high temperature rotor, the process of determining the temperature difference of the high temperature rotor includes:

[0049] The volume average temperature of the high temperature rotor, the outer surface temperature of the high temperature rotor and the center temperature of the high temperature rotor are obtained, and the temperature difference of the high temperature rotor is determined according to the volume average temperature of the high temperature rotor, the outer surface temperature of the high temperature rotor and the center temperature of the high temperature rotor.

[0050] Optionally, the rotor outer diameter of the high-temperature rotor is obtained, and the volume average temperature of the high-temperature rotor is determined based on the rotor outer diameter and the previous volume average temperature of the high-temperature rotor, as well as the first-class inertia link time constant used to calculate the volume average temperature of the high-temperature rotor, and based on the outer surface temperature of the high-temperature rotor and the first-class inertia link time constant set.

[0051] Optionally, the rotor outer diameter of the high-temperature rotor is obtained, and the high-temperature rotor center temperature is determined based on the rotor outer diameter and the previous rotor center temperature of the high-temperature rotor, as well as the second-type inertia link time constant used to calculate the rotor center temperature of the high-temperature rotor, and based on the outer surface temperature of the high-temperature rotor and the set of second-type inertia link time constants.

[0052] Optionally, the metal temperature of the high temperature inner cylinder at the set wall thickness depth is determined, and the metal temperature of the high temperature inner cylinder at the set wall thickness depth is determined as the outer surface temperature of the high temperature rotor. For example, the outer surface temperature of the high temperature rotor can be the metal temperature of the measuring point at 90% of the wall thickness of the high temperature inner cylinder.

[0053] In some implementations, the surface temperature difference between the volume average temperature of the high temperature rotor and the outer surface temperature of the high temperature rotor is obtained, and the center temperature difference between the volume average temperature of the high temperature rotor and the center temperature is obtained. Further, the temperature difference of the high temperature rotor is determined based on the surface temperature difference and the center temperature difference. Optionally, the maximum value is determined from the surface temperature difference and the center temperature difference as the temperature difference of the high temperature rotor; optionally, the larger value of the surface temperature difference and the center temperature difference is used as the temperature difference of the high temperature rotor.

[0054] Optionally, the high temperature key component is not a high temperature rotor, for example, the high temperature key component is a main steam valve housing, a regulating valve housing and a high temperature outer cylinder, etc. The process of determining the temperature difference of the high temperature key component includes: detecting the metal temperature of the measuring point of the high temperature key component at different wall thickness depths, and determining the temperature difference of the high temperature key component according to the metal temperature of the measuring point at different wall thickness depths.

[0055] S102, obtaining the mechanical stress of high-temperature key components in various directions.

[0056] In some implementations, the high-temperature key component is a high-temperature rotor, and the online monitoring value of the operating speed and the rated operating speed of the steam turbine are obtained, and the finite element calculated values ​​of the centrifugal stress in each direction of the high-temperature rotor monitoring point at the rated operating speed of the steam turbine are obtained. For any direction, the centrifugal stress of the high-temperature rotor in any direction is determined based on the online monitoring value of the operating speed and the rated operating speed, as well as the finite element calculated values ​​of the centrifugal stress in any direction.

[0057] In some implementations, the high temperature key component is a non-high temperature rotor, the pressure on the inner surface of the cylinder wall of the high temperature key component is obtained, the radius on the inner surface of the cylinder wall of the high temperature key component and the radius on the outer surface are obtained, and further, the radial mechanical stress and the tangential mechanical stress of the high temperature key component are determined according to the pressure on the inner surface of the cylinder wall, the radius on the inner surface of the cylinder wall and the radius on the outer surface, wherein the axial mechanical stress is 0.

[0058] S103, determining the composite stress of the high-temperature key component in each direction according to the thermal stress in each direction and the mechanical stress in each direction.

[0059] Optionally, the radial thermal stress and the radial mechanical stress of the high-temperature critical component are added together to obtain the radial composite stress of the high-temperature critical component.

[0060] Optionally, the tangential thermal stress and the tangential mechanical stress of the high-temperature critical component are added together to obtain the tangential composite stress of the high-temperature critical component.

[0061] Optionally, the axial thermal stress and the axial mechanical stress of the high-temperature critical component are added together to obtain the axial composite stress of the high-temperature critical component.

[0062] S104, determining a first equivalent stress of the high-temperature key component according to the synthetic stress of the high-temperature key component in various directions, where the first equivalent stress has positive and negative properties.

[0063] In some implementations, the maximum combined stress and the minimum combined stress are determined from the combined stresses in various directions, and the second equivalent stress of the high-temperature critical component is determined based on the combined stress of the high-temperature critical component in various directions. Further, the first equivalent stress with positive and negative signs of the high-temperature critical component is determined based on the second equivalent stress, the maximum combined stress, and the minimum combined stress.

[0064] In the embodiment of the present application, the thermal stress of the high-temperature key components can be determined based on the temperature difference and material physical properties of the high-temperature key components, and the mechanical stress of the high-temperature key components can be determined based on relevant basic data. Further, based on the thermal stress and mechanical stress, the first equivalent stress with positive and negative signs of the high-temperature key components can be determined to provide a calculation basis for stress-related data and life-related data for the subsequent closed-loop control of the speed and load of the turbine, so that closed-loop control based on stress and life can be performed to achieve long life and flexible operation of the turbine.

[0065] Figure 2 A flow chart of another method for obtaining equivalent stress of a deep peak-shaving steam turbine provided in an embodiment of the present application. Figure 2 As shown, the method includes but is not limited to the following steps:

[0066] S201, obtain the thermal stress and mechanical stress of the high-temperature key components of the deep peak-shaving steam turbine in all directions.

[0067] Optionally, the radial thermal stress σ of the inner surface of the main steam valve housing, the regulating valve housing and the high-temperature outer cylinder of the steam turbine and the outer surface of the high-temperature rotor rth (τ), tangential thermal stress σ θth (τ) and axial thermal stress σ zth The calculation formulas for (τ) are

[0068] σ rth (τ)=0 (2)

[0069]

[0070] Among them, α jk (τ) is the material linear expansion coefficient of high temperature key components, Ejk (τ) is the material elastic modulus of high temperature key components, Δt jk (τ) Temperature difference of key high-temperature components of steam turbine, μ jk (τ) is the material Poisson’s ratio of high-temperature critical components.

[0071] Optionally, the mechanical stress of the high-temperature turbine rotor is the rotor centrifugal stress, and the radial centrifugal stress σ at the monitoring point of the turbine rotor is rm (τ), tangential centrifugal stress σ θm (τ) and axial centrifugal stress σ zm The online calculation formulas for (τ) are

[0072]

[0073]

[0074]

[0075] Among them, σ rm0 is the finite element calculated value of the radial centrifugal stress of the high temperature rotor monitoring point at the rated operating speed of the steam turbine, n is the online monitoring value of the steam turbine operating speed, n0 is the rated operating speed of the steam turbine, σ θm0 is the finite element calculated value of the tangential centrifugal stress at the high temperature rotor monitoring point of the steam turbine at rated operating speed, σ zm0 It is the finite element calculated value of the axial centrifugal stress at the high temperature rotor monitoring point of the steam turbine at rated operating speed.

[0076] Optionally, the radial mechanical stress σ of the main steam valve housing, regulating valve housing and inner surface of the high-temperature outer cylinder of the steam turbine is rm (τ), tangential mechanical stress σ θm (τ) and axial mechanical stress σ zm The calculation formulas for (τ) are:

[0077] σ rm (τ)=-p1 (7)

[0078]

[0079] σ zm (τ)=0 (9)

[0080] Among them, p1 is the pressure on the inner surface of the cylinder wall, r1 is the radius of the inner surface of the cylinder wall, and r n is the radius of the outer surface of the cylinder wall.

[0081] S202, determining the composite stress of the high-temperature key components in each direction based on the thermal stress in each direction and the mechanical stress in each direction.

[0082] Optionally, the radial composite stress σ of the high-temperature key components of the steam turbine r (τ), tangential composite stress σ θ (τ) and the axial composite stress σ z The calculation formulas for (τ) are:

[0083] σ r (τ)=σ rth (τ)+σ rm (τ) (10)

[0084] σ θ (τ)=σ θth (τ)+σ θm (τ) (11)

[0085] σ z (τ)=σ zth (τ)+σ zm (τ) (12)

[0086] Among them, σ rth (τ) is the radial thermal stress of high temperature key components, σ rm (τ) is the radial mechanical stress of high temperature key components, σ θth (τ) is the tangential thermal stress of high-temperature key components, σ θm (τ) is the tangential mechanical stress of high temperature key components, σ zth (τ) is the axial thermal stress of high-temperature key components, σ zm Axial mechanical stress.

[0087] S203, determining a second equivalent stress of the high-temperature key component according to the composite stress of the high-temperature key component in each direction.

[0088] The difference of the composite stress in each two directions is obtained, and the second equivalent stress of the high-temperature key component is determined according to the difference of the composite stress.

[0089] Optionally, the second equivalent stress σ of the high temperature critical component eqjk The calculation formula of (τ) is:

[0090]

[0091] Among them, σ r (τ) is the radial composite stress of high temperature key components, σ θ (τ) is the tangential composite stress of high-temperature key components, σ z (τ) is the axial composite stress of high-temperature key components.

[0092] S204, determining a maximum composite stress and a minimum composite stress from the composite stresses in each direction.

[0093] Optionally, the maximum composite stress σ of the high-temperature key components of the steam turbine max The calculation formula of (τ) is:

[0094] σ max (τ)=max{σ r (τ),σ θ (τ),σ z (τ)} (14)

[0095] Among them, σ r (τ) is the radial composite stress of high temperature key components, σ θ (τ) is the tangential composite stress of high-temperature key components, σ z (τ) is the axial composite stress of high-temperature key components.

[0096] Optionally, the minimum composite stress σ of the high-temperature key components of the steam turbine min The calculation formula of (τ) is:

[0097] σ min (τ)=min{σ r (τ),σ θ (τ),σ z (τ)} (15)

[0098] S205, determining the first equivalent stress of the high temperature key component according to the second equivalent stress, the maximum combined stress and the minimum combined stress of the high temperature key component.

[0099] Optionally, the first equivalent stress σ with positive and negative signs of the high temperature key components of the steam turbine ejk The calculation formula of (τ) is:

[0100] σ ejk (τ)=σ eqjk (τ)×sign[σ max (τ)+σ min (τ)] (16)

[0101] Among them, σ eqjk (τ) is the equivalent stress of high temperature key components, σ max (τ) is the maximum composite stress of high temperature key components, σ min (τ) is the minimum composite stress of high-temperature critical components, sign(x) is the sign function, if x>0, then sign(x)=1, if x<0, then sign(x)=﹣1.

[0102] In the embodiment of the present application, the thermal stress of the high-temperature key components can be determined based on the temperature difference and material physical properties of the high-temperature key components, and the mechanical stress of the high-temperature key components can be determined based on relevant basic data. Further, based on the thermal stress and mechanical stress, the first equivalent stress with positive and negative signs of the high-temperature key components can be determined to provide a calculation basis for stress-related data and life-related data for the subsequent closed-loop control of the speed and load of the turbine, so that closed-loop control based on stress and life can be performed to achieve long life and flexible operation of the turbine.

[0103] Figure 3 A flow chart of another method for obtaining the equivalent stress of a deep peak-shaving steam turbine provided in an embodiment of the present application. Figure 3 As shown, the method includes but is not limited to the following steps:

[0104] S301, obtaining basic data related to stress of high-temperature key components.

[0105] Optionally, basic data for calculating the high-temperature rotor volume average temperature and center temperature include:

[0106] The radius r of the rotor outer surface of the high temperature rotor calculation section n , calculate the coefficients A1, A2 and A3 of the time constant T1 of the first inertia link, calculate the proportional coefficient E2 of the time constant of the second inertia link, calculate the proportional coefficient E3 of the time constant of the third inertia link, calculate the proportional coefficient E4 of the time constant of the fourth inertia link, calculate the proportional coefficient E5 of the time constant of the fifth inertia link, calculate the proportional coefficient E6 of the time constant of the sixth inertia link, the weight coefficient K1 of the first inertia link, the weight coefficient K2 of the second inertia link, the weight coefficient K3 of the third inertia link, the weight coefficient K4 of the fourth inertia link, the weight coefficient K5 of the fifth inertia link, and the weight coefficient K6 of the sixth inertia link.

[0107] It should be noted that the first type of inertia link time constant of the high-temperature rotor includes T1, T2 and T3, which are used to determine the volume average temperature of the high-temperature rotor; the second type of inertia link time constant of the high-temperature rotor includes T1, T2, T3, T4, T5 and T6, which are used to determine the center temperature of the high-temperature rotor.

[0108] The metal temperatures of the high-temperature critical components at the depths of 50% and 90% of the wall thickness at time τ are t jk50％ (τ) and t jk90％ (τ), the metal temperature of the measuring point is taken from the steam turbine digital electro-hydraulic control system DEH or the steam turbine control system TCS.

[0109] Material linear expansion coefficient α of high temperature key components jk (τ), material elastic modulus Ejk (τ), material Poisson's ratio μ jk (τ), subscript j indicates the working environment of key components, V indicates ultra-high pressure, H indicates high pressure, and I indicates medium pressure. Subscript k indicates the name of steam turbine components, S indicates the main steam valve housing, A indicates the regulating valve housing, R indicates the rotor, C indicates the outer cylinder, and O indicates the inner cylinder.

[0110] The outer surface radius r of the main steam valve housing, regulating valve housing and high-temperature outer cylinder n , inner surface radius r1, inner surface steam pressure p1, turbine operating speed n, turbine rated operating speed n0, finite element calculation value of radial centrifugal stress at the rotor monitoring point of the turbine at rated operating speed σ rm0 , the finite element calculated value of the tangential centrifugal stress at the rotor monitoring point of the steam turbine at the rated operating speedσ θm0 , the finite element calculated value of the axial centrifugal stress at the rotor monitoring point of the steam turbine at the rated operating speedσ zm0 .

[0111] S302, obtaining the high-temperature rotor outer surface temperature.

[0112] Optionally, the metal temperature t at the depth of 90% of the inner cylinder wall thickness of the corresponding part is used. jO90％ (τ) instead of the high temperature rotor outer surface temperature t n .

[0113] S303, determining three inertia link time constants required for the high-temperature rotor volume average temperature.

[0114] Optionally, the first type of inertia link time constant set required for calculating the volume average temperature of the high-temperature rotor includes: a first inertia link time constant T1, a second inertia link time constant T2 and a third inertia link time constant T3, and the calculation formulas of T1 to T3 are respectively:

[0115]

[0116]

[0117]

[0118] Among them, r n is the radius of the rotor outer surface of the high temperature rotor calculation section, A1, A2 and A3 are the coefficients for calculating the time constant T1 of the first inertia link, t vm(m-1) is the output value of the previous calculation of the high-temperature rotor volume average temperature, E2 is the proportional coefficient for calculating the time constant of the second inertia link, and E3 is the proportional coefficient for calculating the time constant of the third inertia link.

[0119] S304, determining the volume average temperature of the high temperature rotor

[0120] Figure 3a A schematic diagram of a process for determining the average volume temperature of a high-temperature rotor provided in an embodiment of the present application, according to Figure 3a The method shown in the figure shows that the volume average temperature of the high-temperature rotor of the turbine is t jvm The calculation formula of (τ) is

[0121]

[0122] Among them, t jO90％ (τ) is the metal temperature at a depth of 90% of the inner cylinder wall thickness.

[0123] S305, determining six inertia link time constants required for the high-temperature rotor center temperature.

[0124] Optionally, the second type of inertia link time constant set required for calculating the center temperature of the high-temperature rotor includes: a first inertia link time constant T1, a second inertia link time constant T2, a third inertia link time constant T3, a fourth inertia link time constant T4, a fifth inertia link time constant T5 and a sixth inertia link time constant T6, and the calculation formulas of T1 to T6 are respectively:

[0125]

[0126]

[0127]

[0128]

[0129]

[0130]

[0131] Among them, r n is the radius of the rotor outer surface of the high temperature rotor calculation section, A1, A2 and A3 are the coefficients for calculating the time constant T1 of the first inertia link, t vm(m-1) is the output value of the previous calculation of the high-temperature rotor volume average temperature, E2 is the proportional coefficient for calculating the time constant of the second inertia link, E3 is the proportional coefficient for calculating the time constant of the third inertia link, E4 is the proportional coefficient for calculating the time constant of the fourth inertia link, E5 is the proportional coefficient for calculating the time constant of the fifth inertia link, and E6 is the proportional coefficient for calculating the time constant of the sixth inertia link.

[0132] S306, determining the center temperature of the high temperature rotor

[0133] Figure 3bA schematic diagram of a process for determining the center temperature of a high-temperature rotor provided in an embodiment of the present application, according to Figure 3b The method shown, the turbine high temperature rotor center temperature t j1 The calculation formula of (τ) is

[0134]

[0135] Among them, t jO90％ (τ) is the metal temperature at a depth of 90% of the inner cylinder wall thickness.

[0136] S307, determining the temperature difference of the outer surface of the high-temperature rotor.

[0137] Optionally, the temperature difference Δt of the outer surface of the high-temperature rotor of the steam turbine jR The calculation formula of (τ) is:

[0138] Δt jR (τ) = t jvm (τ)-t jO90％ (τ)(28)

[0139] Among them, t jvm (τ) is the average temperature of the high temperature rotor volume, t jO90％ (τ) is the metal temperature at a depth of 90% of the inner cylinder wall thickness.

[0140] S309, determining the center temperature difference of the high-temperature rotor.

[0141] Optionally, the turbine high temperature rotor center temperature difference Δt j1 The calculation formula of (τ) is

[0142] Δt j1 (τ) = t jvm (τ)-t j1 (τ) (29)

[0143] Among them, t jvm (τ) is the volume average temperature of the high temperature rotor, t j1 (τ) is the center temperature of the high temperature rotor.

[0144] S310, determining the temperature difference of the high-temperature rotor.

[0145] Optionally, the temperature difference Δt of the high temperature rotor of the steam turbine jk The calculation formula of (τ) is

[0146] Δt jk (τ)=max{Δt jR (τ),Δt j1 (τ)} (30)

[0147] Among them, Δt jR(τ) is the high temperature rotor surface temperature difference, Δt j1 (τ) is the high temperature rotor center temperature difference.

[0148] S311, determining the temperature difference between the main steam valve housing, the regulating valve housing and the high-temperature outer cylinder.

[0149] Optionally, the temperature difference Δt between the main steam valve housing, the regulating valve housing and the high-temperature outer cylinder of the steam turbine is jk The online calculation formula for (τ) is:

[0150] Δt jk (τ) = t jk50％ (τ)-t jk90％ (τ) (31)

[0151] Among them, t jk50％ (τ) is the metal temperature at the measuring point at a depth of 50% of the wall thickness, which can be used as the volume average temperature t of the main steam valve housing, regulating valve housing and high-temperature outer cylinder jkvm (τ), t jk90％ (τ) is the metal temperature of the measuring point at 90% of the cylinder wall thickness of the main steam valve housing, regulating valve housing and high-temperature outer cylinder.

[0152] S309, determine the thermal stress of high temperature key components.

[0153] For a detailed description of step S309, please refer to the relevant contents of step S201, which will not be repeated here.

[0154] S310, determining the mechanical stress of the high temperature rotor.

[0155] For a detailed description of step S310, please refer to the relevant contents of step S201, which will not be repeated here.

[0156] S311, determine the mechanical stress of the main steam valve housing, the regulating valve housing and the high-temperature outer cylinder.

[0157] For a detailed description of step S311, please refer to the relevant contents of step S201, which will not be repeated here.

[0158] S312, determine the composite stress of high temperature critical components.

[0159] For a detailed description of step S312, please refer to the relevant contents of step S202, which will not be repeated here.

[0160] S313, determine the maximum composite stress of high temperature critical components.

[0161] For a detailed description of step S313, please refer to the relevant contents of step S204, which will not be repeated here.

[0162] S314, determine the minimum composite stress of high temperature critical components.

[0163] For a detailed description of step S314, please refer to the relevant contents of step S204, which will not be repeated here.

[0164] S315, determine the second equivalent stress of high temperature key components.

[0165] For a detailed description of step S315, please refer to the relevant contents in step S203, which will not be repeated here.

[0166] S316, determine the first equivalent stress with positive and negative signs of high-temperature key components.

[0167] For a detailed description of step S316, please refer to the relevant contents of step S205, which will not be repeated here.

[0168] For example, for a supercritical 1050MW single reheat steam turbine with a main steam temperature of 600°C, the basic data for calculating the average volume temperature of the high-pressure rotor of this turbine are listed in Table 1, and the basic data for calculating the center temperature of the high-pressure rotor are listed in Table 2.

[0169] The time τ of the steam turbine during warm start-up is 10000s, and the metal temperature t at the 90% depth of the high-pressure inner cylinder wall thickness corresponding to the high-pressure rotor thermal stress and life monitoring point is HO90％ (τ)=573.6℃.

[0170] Table 1 Basic data for calculating the average volume temperature of the high-pressure rotor

[0171]

[0172]

[0173] Table 2 Basic data for calculating the center temperature of the high pressure rotor

[0174] Serial number project High pressure rotor 1 <![CDATA[Outer diameter r of high-pressure rotor n (mm)]]> 445 2 <![CDATA[Coefficient A1 of the time constant of the first inertial link]]> 26080.2 3 <![CDATA[Coefficient A2 of the time constant of the first inertial link]]> -15.9735 4 <![CDATA[Coefficient A3 of the time constant of the first inertial link]]> <![CDATA[-1.47646×10 -4 ]]> 5 <![CDATA[Proportionality coefficient E2 of the time constant of the second inertia link]]> 5.27 6 <![CDATA[Proportionality coefficient E3 of the time constant of the third inertia link]]> 12.95 7 <![CDATA[Proportionality coefficient E4 of the time constant of the fourth inertia link]]> 24.04 8 <![CDATA[Proportional coefficient E5 of the time constant of the fifth inertial link]]> 38.56 9 <![CDATA[Proportionality coefficient E6 of the time constant of the sixth inertia link]]> 53.00 10 <![CDATA[Weight coefficient K1 of the first inertia link]]> 1.5992 11 <![CDATA[Weight coefficient K2 of the second inertia link]]> -1.0647 12 <![CDATA[Weight coefficient K3 of the third inertia link]]> 0.8529 13 <![CDATA[Weight coefficient K4 of the fourth inertia link]]> -0.7301 14 <![CDATA[Weight coefficient K5 of the fifth inertia link]]> 0.6471 15 <![CDATA[Weight coefficient K6 of the sixth inertia link]]> -0.3044

[0175] The sampling calculation time of the high-pressure inner cylinder temperature of this steam turbine is taken as τ s =4s, at the moment of warm start process τ = 10000s, at (τ-τ s )=9996s, the average volume temperature of the high-pressure rotor of the steam turbine is t vm(m-1) =483.8℃, metal temperature at 90% depth of high pressure inner cylinder wall thickness t HO90％ (τ) = 573.6°C. The calculation results of the first inertia link time constant T1, the second inertia link time constant T2 and the third inertia link time constant T3 required for the calculation of the average volume temperature of the high-pressure rotor of the steam turbine are:

[0176]

[0177]

[0178]

[0179] The average volume temperature of the high-pressure rotor of the steam turbine is t Hvm The calculation results are:

[0180]

[0181] The calculation results of the first inertia link time constant T1, the second inertia link time constant T2, the third inertia link time constant T3, the fourth inertia link time constant T4, the fifth inertia link time constant T5, and the sixth inertia link time constant T6 required for the calculation of the high-pressure rotor center temperature of the steam turbine are as follows:

[0182]

[0183]

[0184]

[0185]

[0186]

[0187]

[0188] The central temperature of the high pressure rotor of the steam turbine is t H1 The calculation result of (τ) is:

[0189]

[0190] The single-reheat steam turbine was started in warm state for 10000s. The online calculation data of stress of high-temperature components of high-pressure cylinder are listed in Table 3. The online calculation data of stress include thermal stress, mechanical stress, synthetic stress, second equivalent stress and first equivalent stress with positive and negative signs at the monitoring points of the inner surface of high-pressure main steam valve housing, the inner surface of high-pressure regulating valve housing, the outer surface of high-pressure rotor and the inner surface of high-pressure outer cylinder.

[0191] Table 3 Calculation data of stress of high-temperature components of high-pressure cylinder

[0192] Serial number project High pressure main steam valve housing High pressure regulating valve housing High pressure rotor High pressure outer cylinder 1 <![CDATA[Volume-average temperature t jkvm (τ) (°C)]]> 541.2 541.2 483.8 326.7 2 <![CDATA[Surface temperature t jk90％ (τ) (°C)]]> 583.0 582.9 573.6 376.8 3 <![CDATA[Temperature difference Δt jk (τ) (°C)]]> -41.8 -41.7 -89.8 -50.1 4 <![CDATA[Radial thermal stress σ rth (τ) (MPa)]]> 0 0 0 0 5 <![CDATA[Tangential thermal stress σ θth (τ) (MPa)]]> -125.585 -125.284 -383.846 -183.424 6 <![CDATA[Axial thermal stress σ zth (τ) (MPa)]]> -125.585 -125.284 -383.846 -183.424 7 <![CDATA[Radial mechanical stress σ rm (τ) (MPa)]]> -25.738 -25.738 0 -5.950 8 <![CDATA[Tangential mechanical stress σ θm (τ) (MPa)]]> 52.373 39.218 20.807 39.298 9 <![CDATA[Axial mechanical stress σ zm (τ) (MPa)]]> 0 0 6.450 0 10 <![CDATA[Radial composite stress σ r (τ) (MPa)]]> -25.738 -25.738 0 -5.950 11 <![CDATA[Tangential combined stress σ θ (τ) (MPa)]]> -73.212 -86.066 383.846 -144.126 12 <![CDATA[Axial combined stress σ z (τ) (MPa)]]> -125.585 -125.284 -377.396 -183.424 13 <![CDATA[Maximum combined stress σ max (τ) (MPa)]]> -25.738 -25.738 0 -5.950 14 <![CDATA[Minimum combined stress σ min (τ) (MPa)]]> -125.585 -125.284 -383.846 -183.424 15 <![CDATA[The second equivalent stress σ eqjk (τ) (MPa)]]> 86.505 86.853 380.662 161.453 16 <![CDATA[The first equivalent stress σ ejk (τ) (MPa)]]> -86.505 -86.853 -380.662 -161.453

[0193] In an embodiment of the present application, the thermal stress of the high-temperature key components can be determined based on the temperature difference and material physical properties of the high-temperature key components, and the mechanical stress of the high-temperature key components can be determined based on relevant basic data. Further, based on the thermal stress and mechanical stress, the first equivalent stress with positive and negative signs of the high-temperature key components can be determined, so as to provide a calculation basis for stress-related data and life-related data for subsequent turbine control, thereby enabling closed-loop control based on stress and life to achieve long life and flexible operation of the turbine.

[0194] On the basis of the above embodiment, after obtaining the first equivalent stress with positive and negative signs of the high-temperature key component, stress-related data such as the stress safety multiple and relative stress margin of the high-temperature key component can be determined based on the first equivalent stress. Optionally, life-related data such as transient low-cycle fatigue crack initiation life loss and low-cycle fatigue crack initiation life cumulative loss of the high-temperature key component can be determined based on the first equivalent stress. According to the above stress-related data and life-related data, the speed and load of the steam turbine can be closed-loop controlled.

[0195] Figure 4 This is a schematic diagram of a structure of a device for acquiring equivalent stress of a deep peak-shaving steam turbine provided in an embodiment of the present application. Figure 4 As shown, the device includes: a first acquisition module 401, a second acquisition module 402, a first determination module 403 and a second determination module 404.

[0196] The first acquisition module 401 is used to obtain the thermal stress of the high-temperature key components of the deep peak-shaving steam turbine in various directions;

[0197] The second acquisition module 402 is used to acquire the mechanical stress of the high-temperature key component in various directions;

[0198] A first determination module 403 is used to determine the composite stress of the high-temperature key component in each direction according to the thermal stress in each direction and the mechanical stress in each direction;

[0199] The second determination module 404 is used to determine the first equivalent stress of the high-temperature key component according to the synthetic stress of the high-temperature key component in each direction, where the first equivalent stress has positive and negative properties.

[0200] In some implementations, the second determining module 404 is further configured to:

[0201] Determine the maximum and minimum combined stresses from the combined stresses in each direction;

[0202] Determining a second equivalent stress of the high-temperature key component according to the composite stress of the high-temperature key component in each direction;

[0203] A first equivalent stress with a positive and negative sign of the high-temperature key component is determined according to the second equivalent stress, the maximum combined stress and the minimum combined stress.

[0204] In some implementations, the first acquisition module 401 is further configured to:

[0205] determining a temperature difference of the high temperature critical component;

[0206] The radial thermal stress, tangential thermal stress and axial thermal stress of the high-temperature key component are determined according to the material physical properties of the high-temperature key component and the temperature difference.

[0207] In some implementations, the high-temperature key component is a high-temperature rotor, and the first acquisition module 401 is further used to:

[0208] Obtaining a volume average temperature of the high-temperature rotor;

[0209] Acquiring the outer surface temperature of the high-temperature rotor;

[0210] A temperature difference of the high temperature rotor is determined based on a volume average temperature of the high temperature rotor and an outer surface temperature of the high temperature rotor.

[0211] In some implementations, the first acquisition module 401 is further configured to:

[0212] The metal temperature of the measuring point at the set depth of the inner cylinder wall thickness is determined, and the metal temperature of the measuring point at the set depth of the inner cylinder wall thickness is determined as the outer surface temperature of the high-temperature rotor.

[0213] In some implementations, the first acquisition module 401 is further configured to:

[0214] Obtaining the rotor outer diameter of the high-temperature rotor;

[0215] Determining a first-order inertia link time constant for calculating the volume average temperature of the high-temperature rotor according to the outer diameter of the rotor and the previous volume average temperature of the high-temperature rotor;

[0216] The high-temperature rotor volume average temperature is determined based on the outer surface temperature of the high-temperature rotor and the first type inertia link time constant set.

[0217] In some implementations, the first acquisition module 401 is further configured to:

[0218] Obtaining the rotor outer diameter of the high-temperature rotor;

[0219] Determining a second type inertia link time constant for calculating the center temperature of the high temperature rotor according to the outer diameter of the rotor and the previous volume average temperature of the high temperature rotor;

[0220] The central temperature of the high-temperature rotor is determined based on the outer surface temperature of the high-temperature rotor and the set of time constants of the second-type inertia links.

[0221] In some implementations, the first acquisition module 401 is further configured to:

[0222] Obtaining a surface temperature difference between a volume average temperature of the high temperature rotor and an outer surface temperature of the high temperature rotor;

[0223] Obtaining a center temperature difference between a volume average temperature of the high temperature rotor and a center temperature of the high temperature rotor;

[0224] The temperature difference of the high-temperature rotor is determined according to the surface temperature difference and the center temperature difference.

[0225] In some implementations, the high temperature key component is not the high temperature rotor, and the first acquisition module 401 is further used to:

[0226] Detecting the metal temperature of the high-temperature key component at different wall thickness depths;

[0227] The temperature difference of the high-temperature key component is determined according to the metal temperature of the measuring points at the different wall thickness depths.

[0228] In some implementations, the high-temperature key component is a high-temperature rotor, and the second acquisition module 402 is further configured to:

[0229] Obtaining an online monitoring value of the operating speed and a rated operating speed of the steam turbine;

[0230] Obtaining finite element calculation values ​​of centrifugal stresses in various directions on the outer surface of the high-temperature rotor of the steam turbine at a rated operating speed;

[0231] For any direction, the centrifugal stress of the high-temperature rotor in any direction is determined based on the online monitoring value and the rated operating speed, as well as the finite element calculated value of the centrifugal stress in any direction.

[0232] In some implementations, the high temperature key component is not a high temperature rotor, and the second acquisition module 402 is further used to:

[0233] Obtaining the inner surface pressure of the cylinder wall of the high-temperature key component;

[0234] Obtaining the inner surface radius and outer surface radius of the cylindrical wall of the high-temperature key component;

[0235] The radial mechanical stress and the tangential mechanical stress of the high-temperature key component are determined according to the inner surface pressure of the cylinder wall, the inner surface radius of the cylinder wall and the outer surface radius.

[0236] In an embodiment of the present application, the thermal stress of the high-temperature key components can be determined based on the temperature difference and material physical properties of the high-temperature key components, and the mechanical stress of the high-temperature key components can be determined based on relevant basic data. Further, based on the thermal stress and mechanical stress, the first equivalent stress with positive and negative signs of the high-temperature key components can be determined, so as to provide a calculation basis for stress-related data and life-related data for subsequent turbine control, thereby enabling closed-loop control based on stress and life to achieve long life and flexible operation of the turbine.

[0237] Figure 5 The present invention is a block diagram of an electronic device according to an exemplary embodiment. Figure 5 The electronic device shown is merely an example and should not bring any limitation to the functions and scope of use of the embodiments of the present application.

[0238] like Figure 5 As shown, the electronic device 500 includes a processor 501, which can perform various appropriate actions and processes according to a program stored in a read-only memory (ROM) 502 or a program loaded from a memory 506 to a random access memory (RAM) 503. In the RAM 503, various programs and data required for the operation of the electronic device 500 are also stored. The processor 501, the ROM 502, and the RAM 503 are connected to each other via a bus 504. An input / output (I / O) interface 505 is also connected to the bus 504.

[0239] The following components are connected to the I / O interface 505: a memory 506 including a hard disk, etc.; and a communication part 507 including a network interface card such as a LAN (Local Area Network) card, a modem, etc., and the communication part 507 performs communication processing via a network such as the Internet; a drive 508 is also connected to the I / O interface 505 as needed.

[0240] In particular, according to an embodiment of the present application, the process described above with reference to the flowchart can be implemented as a computer software program. For example, an embodiment of the present application includes a computer program carried on a computer-readable medium, and the computer program includes a program code for executing the method shown in the flowchart. In such an embodiment, the computer program can be downloaded and installed from the network through the communication part 507. When the computer program is executed by the processor 501, the above-mentioned functions defined in the method of the present application are executed.

[0241] In an exemplary embodiment, a storage medium including instructions is also provided, such as a memory including instructions, and the instructions can be executed by the processor 501 of the electronic device 500 to complete the above method. Optionally, the storage medium can be a non-transitory computer-readable storage medium, for example, the non-transitory computer-readable storage medium can be a ROM, a random access memory (RAM), a CD-ROM, a magnetic tape, a floppy disk, an optical data storage device, etc.

[0242] In the present application, a computer-readable storage medium may be any tangible medium containing or storing a program that may be used by or in combination with an instruction execution system, apparatus, or device. In the present application, a computer-readable signal medium may include a data signal propagated in a baseband or as part of a carrier wave, which carries a computer-readable program code. Such propagated data signals may take a variety of forms, including but not limited to electromagnetic signals, optical signals, or any suitable combination of the above. A computer-readable signal medium may also be any computer-readable medium other than a computer-readable storage medium, which may send, propagate, or transmit a program for use by or in combination with an instruction execution system, apparatus, or device. The program code contained on the computer-readable medium may be transmitted using any suitable medium, including but not limited to: wireless, wire, optical cable, RF, etc., or any suitable combination of the above.

[0243] Figure 6 The present invention is a structural block diagram of an electronic device according to an exemplary embodiment. Figure 6 The electronic device shown is only an example and should not limit the functions and scope of use of the embodiments of the present application. Figure 6 As shown, the electronic device 600 includes a processor 601 and a memory 602. The memory 602 is used to store program codes, and the processor 601 is connected to the memory 602 and is used to read the program codes from the memory 602 to implement the wind speed representative year correction method in the above embodiment.

[0244] Optionally, the number of processors 601 may be one or more.

[0245] Optionally, the electronic device may further include an interface 603, and the number of the interface 603 may be multiple. The interface 603 may be connected to an application program and may receive data from an external device such as a sensor.

[0246] An embodiment of the present application also proposes a non-temporary computer-readable storage medium. When the instructions in the storage medium are executed by a processor of an electronic device, the electronic device can execute the method for obtaining the equivalent stress of the deep peak-shaving steam turbine in the above embodiment.

[0247] An embodiment of the present application further proposes a computer program product, including a computer program, which, when executed by a processor in a communication device, implements the method for obtaining the equivalent stress of the deep peak-shaving steam turbine in the above embodiment.

[0248] Those skilled in the art will readily appreciate other embodiments of the present invention after considering the specification and practicing the invention disclosed herein. This application is intended to cover any variations, uses or adaptations of the present invention that follow the general principles of the present invention and include common knowledge or customary techniques in the art that are not disclosed in this application. The specification and examples are intended to be exemplary only, and the true scope and spirit of the present application are indicated by the following claims.

[0249] It should be understood that the present application is not limited to the precise structures that have been described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present application is limited only by the appended claims.

Claims

1. A method for obtaining equivalent stress of a deep peak-shaving steam turbine, characterized in that: include: Obtain the thermal stress of high-temperature key components of deep peak-shaving steam turbines in all directions; Obtaining the mechanical stress of the high-temperature key component in each direction; Determine the composite stress of the high-temperature key component in each direction according to the thermal stress in each direction and the mechanical stress in each direction; Determine the first equivalent stress of the high-temperature key component according to the synthetic stress of the high-temperature key component in each direction, wherein the first equivalent stress has positive and negative properties; The step of obtaining the thermal stress of the high-temperature key components of the deep peak-shaving steam turbine in various directions includes: determining a temperature difference of the high temperature critical component; Determining radial thermal stress, tangential thermal stress and axial thermal stress of the high-temperature key component according to the material physical properties of the high-temperature key component and the temperature difference; The high-temperature key component is a high-temperature rotor, and determining the temperature difference of the high-temperature key component includes: Obtaining the volume average temperature of the high temperature rotor and the center temperature of the high temperature rotor; Acquiring the outer surface temperature of the high-temperature rotor; A temperature difference of the high temperature rotor is determined based on a volume average temperature of the high temperature rotor, an outer surface temperature of the high temperature rotor, and a center temperature of the high temperature rotor.

2. The method according to claim 1, characterized in that Determining the first equivalent stress of the high-temperature key component with positive and negative signs according to the synthetic stress of the high-temperature key component in each direction includes: Determine the maximum and minimum combined stresses from the combined stresses in each direction; Determining a second equivalent stress of the high-temperature key component according to the composite stress of the high-temperature key component in each direction; A first equivalent stress with a positive and negative sign of the high-temperature key component is determined according to the second equivalent stress, the maximum combined stress and the minimum combined stress.

3. The method according to claim 1, characterized in that The method further comprises: The metal temperature of the measuring point at the set depth of the inner cylinder wall thickness is determined, and the metal temperature of the measuring point at the set depth of the inner cylinder wall thickness is determined as the outer surface temperature of the high-temperature rotor.

4. The method according to claim 1, characterized in that: The obtaining of the volume average temperature of the high-temperature rotor comprises: Obtaining the rotor outer diameter of the high-temperature rotor; Determine a first-order inertia link time constant for calculating the volume average temperature of the high-temperature rotor according to the outer diameter of the rotor and the previous volume average temperature of the high-temperature rotor; The high-temperature rotor volume average temperature is determined based on the outer surface temperature of the high-temperature rotor and the first type inertia link time constant set.

5. The method according to claim 1, characterized in that The obtaining the central temperature of the high-temperature rotor comprises: Obtaining the rotor outer diameter of the high-temperature rotor; Determining a second type inertia link time constant for calculating the center temperature of the high temperature rotor according to the outer diameter of the rotor and the previous volume average temperature of the high temperature rotor; The central temperature of the high-temperature rotor is determined based on the outer surface temperature of the high-temperature rotor and the set of time constants of the second-type inertia links.

6. The method according to claim 1, characterized in that Determining the temperature difference of the high temperature rotor according to the volume average temperature of the high temperature rotor, the outer surface temperature of the high temperature rotor and the central temperature of the high temperature rotor comprises: Obtaining a surface temperature difference between a volume average temperature of the high-temperature rotor and an outer surface temperature of the high-temperature rotor; Obtaining a center temperature difference between a volume average temperature of the high-temperature rotor and a center temperature of the high-temperature rotor; The temperature difference of the high-temperature rotor is determined according to the surface temperature difference and the center temperature difference.

7. The method according to claim 1, characterized in that The high temperature key component is not a high temperature rotor, and determining the temperature difference of the high temperature key component includes: Detecting the metal temperature of the high-temperature key component at different wall thickness depths; The temperature difference of the high-temperature key component is determined according to the metal temperature of the measuring points at the different wall thickness depths.

8. The method according to claim 1, characterized in that The high-temperature key component is a high-temperature rotor, and obtaining the mechanical stress of the high-temperature key component in various directions includes: Obtaining an online monitoring value of the operating speed and a rated operating speed of the steam turbine; Obtaining finite element calculated values ​​of centrifugal stress of the high-temperature rotor in each direction at the rated operating speed of the steam turbine; For any direction, the centrifugal stress of the high-temperature rotor in any direction is determined based on the online monitoring value and the rated operating speed, as well as the finite element calculated value of the centrifugal stress in any direction.

9. The method according to claim 1, characterized in that: The high-temperature key component is not a high-temperature rotor, and obtaining the mechanical stress of the high-temperature key component in each direction includes: Obtaining the inner surface pressure of the cylinder wall of the high-temperature key component; Obtaining the inner surface radius and outer surface radius of the cylindrical wall of the high-temperature key component; The radial mechanical stress and the tangential mechanical stress of the high-temperature key component are determined according to the inner surface pressure of the cylinder wall, the inner surface radius of the cylinder wall and the outer surface radius.

10. A device for obtaining equivalent stress of a deep peak-shaving steam turbine, characterized in that: include: The first acquisition module is used to obtain the thermal stress of the high-temperature key components of the deep peak-shaving steam turbine in various directions; A second acquisition module is used to acquire the mechanical stress of the high-temperature key component in various directions; A first determination module is used to determine the composite stress of the high-temperature key component in each direction according to the thermal stress in each direction and the mechanical stress in each direction; A second determination module is used to determine a first equivalent stress of the high-temperature key component according to the synthetic stress of the high-temperature key component in each direction, wherein the first equivalent stress has positive and negative properties; The first acquisition module is further used for: determining a temperature difference of the high temperature critical component; Determining radial thermal stress, tangential thermal stress and axial thermal stress of the high-temperature key component according to the material physical properties of the high-temperature key component and the temperature difference; The high-temperature key component is a high-temperature rotor, and the first acquisition module is further used for: Acquiring a volume average temperature of the high temperature rotor and a center temperature of the high temperature rotor; Acquiring the outer surface temperature of the high-temperature rotor; A temperature difference of the high temperature rotor is determined based on a volume average temperature of the high temperature rotor, an outer surface temperature of the high temperature rotor, and a center temperature of the high temperature rotor.

11. The device according to claim 10, characterized in that The second determining module is further used for: Determine the maximum and minimum combined stresses from the combined stresses in each direction; Determining a second equivalent stress of the high-temperature key component according to the composite stress of the high-temperature key component in each direction; A first equivalent stress with a positive and negative sign of the high-temperature key component is determined according to the second equivalent stress, the maximum combined stress and the minimum combined stress.

12. The device according to claim 10, characterized in that The first acquisition module is further used for: The metal temperature of the measuring point at the set depth of the inner cylinder wall thickness is determined, and the metal temperature of the measuring point at the set depth of the inner cylinder wall thickness is determined as the outer surface temperature of the high-temperature rotor.

13. The device according to claim 10, characterized in that The first acquisition module is further used for: Obtaining the rotor outer diameter of the high-temperature rotor; Determine a first-order inertia link time constant for calculating the volume average temperature of the high-temperature rotor according to the outer diameter of the rotor and the previous volume average temperature of the high-temperature rotor; The high-temperature rotor volume average temperature is determined based on the outer surface temperature of the high-temperature rotor and the first type inertia link time constant set.

14. The device according to claim 10, characterized in that The first acquisition module is further used for: Obtaining the rotor outer diameter of the high-temperature rotor; Determining a second type inertia link time constant for calculating the center temperature of the high temperature rotor according to the outer diameter of the rotor and the previous volume average temperature of the high temperature rotor; The central temperature of the high-temperature rotor is determined based on the outer surface temperature of the high-temperature rotor and the set of time constants of the second-type inertia links.

15. The device according to claim 10, characterized in that The first acquisition module is further used for: Obtaining a surface temperature difference between a volume average temperature of the high-temperature rotor and an outer surface temperature of the high-temperature rotor; Obtaining a center temperature difference between a volume average temperature of the high-temperature rotor and a center temperature of the high-temperature rotor; The temperature difference of the high-temperature rotor is determined according to the surface temperature difference and the center temperature difference.

16. The device according to claim 10, characterized in that The high-temperature key component is not a high-temperature rotor, and the first acquisition module is further used to: Detecting the metal temperature of the high-temperature key component at different wall thickness depths; The temperature difference of the high-temperature key component is determined according to the metal temperature of the measuring points at the different wall thickness depths.

17. The device according to claim 10, characterized in that The high-temperature key component is a high-temperature rotor, and the second acquisition module is further used for: Obtaining an online monitoring value of the operating speed and a rated operating speed of the steam turbine; Obtaining finite element calculation values ​​of centrifugal stresses in various directions on the outer surface of the high-temperature rotor of the steam turbine at a rated operating speed; For any direction, the centrifugal stress of the high-temperature rotor in any direction is determined based on the online monitoring value and the rated operating speed, as well as the finite element calculated value of the centrifugal stress in any direction.

18. The device according to claim 10, characterized in that The high-temperature key component is not a high-temperature rotor, and the second acquisition module is further used to: Obtaining the inner surface pressure of the cylinder wall of the high-temperature key component; Obtaining the inner surface radius and outer surface radius of the cylindrical wall of the high-temperature key component; The radial mechanical stress and the tangential mechanical stress of the high-temperature key component are determined according to the inner surface pressure of the cylinder wall, the inner surface radius of the cylinder wall and the outer surface radius.

19. An electronic device, characterized in that: include: one or more processors; a memory for storing instructions executable by the processor; The processor is configured to execute the instructions to implement the method according to any one of claims 1 to 9.

20. A non-transitory computer-readable storage medium, when instructions in the storage medium are executed by a processor of an electronic device, the electronic device is enabled to perform the method according to any one of claims 1 to 9.

21. A computer program product comprising a computer program, which, when executed by a processor in a communication device, implements the method according to any one of claims 1 to 9.

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