CN114396320A

CN114396320A - Safety monitoring method for dynamic strength and vibration of moving blade of nuclear turbine

Info

Publication number: CN114396320A
Application number: CN202111456668.3A
Authority: CN
Inventors: 史进渊; 朱志劼; 蒋俊; 万震天; 郭嘉靖; 祝自芳
Original assignee: Shanghai Power Equipment Research Institute Co Ltd
Current assignee: Shanghai Power Equipment Research Institute Co Ltd
Priority date: 2021-12-01
Filing date: 2021-12-01
Publication date: 2022-04-26
Anticipated expiration: 2041-12-01
Also published as: CN114396320B

Abstract

The application provides a safety monitoring method for dynamic strength and vibration of a moving blade of a nuclear turbine, which relates to the technical field of nuclear turbines and comprises the following steps: obtaining vibration stress, vibration resistance strength and allowable dynamic strength safety factors of a moving blade of a nuclear turbine, and a first-order vibration frequency of the moving blade, a first vibration frequency at the highest limit of the working rotating speed, a second vibration frequency at the lowest working rotating speed, an m-order diameter vibration frequency of a long blade connected in a whole circle, and the working rotating speed of the nuclear turbine as operation state data of the moving blade; determining dynamic strength and vibration reliability monitoring data according to the running state data of the moving blades; and performing optimized control on the nuclear turbine according to the dynamic strength and vibration reliability monitoring data. In the application, the dynamic strength and the vibration safety of the moving blade of the nuclear turbine can be accurately monitored, and the nuclear turbine is optimally controlled, so that the service life of the nuclear turbine is prolonged, and the long-period safe operation of the nuclear turbine is ensured.

Description

Safety monitoring method for dynamic strength and vibration of moving blade of nuclear turbine

Technical Field

The application relates to the technical field of nuclear turbines, in particular to a safety monitoring method for dynamic strength and vibration of a moving blade of a nuclear turbine.

Background

When the safety margin of the dynamic strength of the moving blade of the nuclear turbine is small and the vibration is large, parts are easily damaged, so that the safety and the service life of the nuclear turbine are affected, and in order to improve the service life and the operation safety of the nuclear turbine and ensure the long-period safe operation of the nuclear turbine, the dynamic strength and the vibration of the moving blade of the nuclear turbine need to be monitored.

Disclosure of Invention

The present application is directed to solving, at least to some extent, one of the technical problems in the related art. Therefore, an object of the present application is to provide a method for safely monitoring the dynamic strength and vibration of a moving blade of a nuclear turbine.

The second purpose of the present application is to provide a safety monitoring device for the dynamic strength and vibration of a moving blade of a nuclear turbine.

A third object of the present application is to provide an electronic device.

A fourth object of the present application is to propose a non-transitory computer readable storage medium.

A fifth object of the present application is to propose a computer program product.

In order to achieve the above object, an embodiment of the first aspect of the present application provides a method for safely monitoring dynamic strength and vibration of a moving blade of a nuclear turbine, including:

obtaining vibration stress, vibration resistance strength and allowable dynamic strength safety factors of a moving blade of a nuclear turbine, and a first-order vibration frequency of the moving blade, a first vibration frequency at the highest limit of the working rotating speed, a second vibration frequency at the lowest working rotating speed, an m-order diameter vibration frequency of a full-circle connected long blade and the working rotating speed of the nuclear turbine as operation state data of the moving blade;

determining dynamic strength and vibration reliability monitoring data according to the running state data of the moving blades;

and performing optimized control on the nuclear turbine according to the dynamic strength and vibration reliability monitoring data.

In one possible implementation, determining dynamic strength and vibration reliability monitoring data according to the operation state data of the moving blade includes:

determining the safety ratio of the dynamic strength of the moving blade according to the vibration resistance strength, the vibration stress and the allowable safety factor of the dynamic strength of the moving blade;

determining a first frequency resonance ratio of the moving blade avoiding the low-frequency exciting force according to a first vibration frequency of the moving blade at the highest limit of the working rotating speed, a second vibration frequency of the moving blade at the lowest limit of the working rotating speed, the rotating speed multiplying power of the exciting force and the working rotating speed of the nuclear power turbine, wherein the first frequency resonance ratio comprises a lower limit ratio and an upper limit ratio of a first-order vibration frequency avoiding the low-frequency exciting force;

determining a second frequency resonance ratio of the moving blade to avoid high-frequency exciting force according to the first-order vibration frequency of the moving blade, the number of the static blades and the working rotating speed of the nuclear turbine;

determining a third frequency resonance ratio of the m-order diameter vibration frequency of the full-circle connected long blade to avoid the high-frequency exciting force according to the m-order diameter vibration frequency of the full-circle connected long blade, the number of the static blades and the working rotating speed of the nuclear power turbine;

and determining the dynamic intensity safety ratio, the first frequency resonance ratio, the second frequency resonance ratio and the third frequency resonance ratio as dynamic intensity and vibration reliability monitoring data.

In one possible implementation, the method for performing optimization control on a nuclear turbine according to the dynamic intensity and vibration reliability monitoring data includes:

according to the safety ratio of the dynamic strength, the safety of the dynamic strength of the moving blade is optimally controlled;

according to the first frequency resonance ratio, optimally controlling the moving blade to avoid the low-frequency excitation force frequency resonance;

according to the second frequency resonance ratio, optimally controlling the moving blade to avoid the high-frequency excitation force frequency resonance;

and optimally controlling the whole circle of the connecting long blade to avoid the high-frequency excitation force frequency resonance according to the third frequency resonance ratio.

In a possible implementation manner, the optimization control of the moving blade dynamic strength safety according to the dynamic strength safety ratio comprises the following steps:

responding to the fact that the dynamic strength safety ratio is larger than a preset dynamic strength safety ratio threshold value, and determining that the dynamic strength safety design monitoring of the moving blade is qualified;

responding to the fact that the dynamic strength safety ratio is smaller than or equal to a preset dynamic strength safety ratio threshold, determining that the dynamic strength safety design monitoring of the moving blade is not qualified, and generating a dynamic strength optimization improvement strategy of the nuclear turbine;

and performing optimization control on the nuclear turbine according to a dynamic intensity optimization improvement strategy until the dynamic intensity safety ratio is greater than a preset dynamic intensity safety ratio threshold value, and finishing the optimization.

In a possible implementation manner, the optimally controlling the moving blade to avoid the low-frequency excitation force frequency resonance according to the first frequency resonance ratio includes:

in response to the fact that the lower limit ratio is larger than the first percentage threshold value and the upper limit ratio is larger than the second percentage threshold value, determining that the design and monitoring of the movable blade avoiding the low-frequency excitation force frequency resonance are qualified;

in response to the fact that the lower limit ratio is smaller than or equal to the first percentage threshold and/or the upper limit ratio is smaller than or equal to the second percentage threshold, determining that the design and monitoring of the moving blade avoiding the low-frequency excitation force frequency resonance is not qualified, and generating an optimization improvement strategy for the moving blade avoiding the low-frequency excitation force frequency resonance;

according to an optimization improvement strategy that the moving blades avoid low-frequency excitation force frequency resonance, optimization control is carried out on the nuclear power turbine until the lower limit ratio is larger than a first percentage threshold value and the upper limit ratio is larger than a second percentage threshold value, and optimization is finished; wherein the second percentage threshold is less than the first percentage threshold.

In a possible implementation manner, the optimally controlling the moving blade to avoid the high-frequency excitation force frequency resonance according to the second frequency resonance ratio includes:

responding to the fact that the second frequency resonance ratio is larger than or equal to the first percentage threshold value, and determining that the moving blade is qualified for avoiding the high-frequency excitation force frequency resonance design monitoring;

in response to the fact that the second frequency resonance ratio is smaller than the first percentage threshold value, determining that the design and monitoring of the moving blade avoiding the high-frequency excitation force frequency resonance is not qualified, and generating an optimization improvement strategy for the moving blade avoiding the high-frequency excitation force frequency resonance;

and performing optimization control on the nuclear power turbine according to an optimization improvement strategy of avoiding the high-frequency excitation force frequency resonance of the moving blade until the second frequency resonance ratio is greater than or equal to the first percentage threshold value, and finishing the optimization.

In a possible implementation manner, according to a third frequency resonance ratio, the optimal control of avoiding the high-frequency excitation force frequency resonance of the whole circle of the connecting long blade is performed, and the method comprises the following steps:

responding to the third frequency resonance ratio value being larger than or equal to the first percentage threshold value, and determining that the whole circle of connected long blades are qualified for avoiding the high-frequency exciting force frequency resonance design monitoring;

in response to the third frequency resonance ratio being smaller than the first percentage threshold, determining that the design and monitoring of the whole circle of the long blades for avoiding the high-frequency excitation force frequency resonance is not qualified, and generating an optimization and improvement strategy of the whole circle of the long blades for avoiding the high-frequency excitation force frequency resonance;

and performing optimization control on the nuclear turbine according to an optimization improvement strategy of avoiding high-frequency excitation force frequency resonance by connecting the long blades in a whole circle until the third frequency resonance ratio is greater than or equal to the first percentage threshold value, and finishing optimization.

The embodiment of the application can accurately monitor the dynamic strength and the vibration safety of the moving blade of the nuclear turbine and optimally control the nuclear turbine, thereby prolonging the service life of the nuclear turbine and ensuring the long-period safe operation of the nuclear turbine.

In order to achieve the above object, a second aspect of the present invention provides a safety monitoring device for monitoring dynamic strength and vibration of a moving blade of a nuclear turbine, including:

the acquisition module is used for acquiring allowable safety factors of the vibration stress, the vibration resistance strength and the dynamic strength of a moving blade of the nuclear power turbine, and the first-order vibration frequency of the moving blade, the first vibration frequency at the highest limit of the working rotating speed, the second vibration frequency at the lowest working rotating speed, the m-order diameter vibration frequency of a long blade connected in a whole circle and the working rotating speed of the nuclear power turbine as the running state data of the moving blade;

the determining module is used for determining the monitoring data of the dynamic strength and the vibration reliability according to the running state data of the moving blades;

and the optimization module is used for carrying out optimization control on the nuclear turbine according to the dynamic strength and vibration reliability monitoring data.

In one possible implementation, the determining module is further configured to:

In one possible implementation, the optimization module is further configured to:

To achieve the above object, a third aspect of the present application provides an electronic device, including:

at least one processor; and

a memory communicatively coupled to the at least one processor; wherein,

the memory stores instructions executable by the at least one processor, the instructions being executable by the at least one processor to enable the at least one processor to perform the method for safety monitoring of dynamic strength and vibration of a moving blade of a nuclear power turbine provided in the embodiments of the first aspect of the present application.

To achieve the above object, a fourth aspect of the present application provides a computer-readable storage medium having stored thereon computer instructions, where the computer instructions are used to make a computer execute a method for safety monitoring of dynamic strength and vibration of a moving blade of a nuclear power turbine provided in the first aspect of the present application.

To achieve the above object, a fifth aspect of the present application provides a computer program product, which includes a computer program, and the computer program, when being executed by a processor, implements the method for safely monitoring the dynamic strength and vibration of the moving blade of the nuclear power turbine provided in the first aspect of the present application.

Drawings

FIG. 1 is a schematic illustration of a combined monitoring platform for a nuclear turbine according to an embodiment of the present application;

FIG. 2 is a flow chart of a method for safely monitoring the dynamic strength and vibration of a moving blade of a nuclear turbine according to an embodiment of the present application;

FIG. 3 is a flow chart of optimization control in a safety monitoring method for dynamic strength and vibration of a moving blade of a nuclear turbine according to an embodiment of the present application;

FIG. 4 is a flow chart of a method for monitoring the safety of the dynamic strength and vibration of a moving blade of a nuclear turbine of a specific type according to an embodiment of the present application;

FIG. 5 is a block diagram of a safety monitoring device for monitoring the dynamic strength and vibration of a moving blade of a nuclear turbine according to an embodiment of the present application;

fig. 6 is a schematic structural diagram of an electronic device according to an embodiment of the present application.

Detailed Description

Reference will now be made in detail to embodiments of the present application, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present application and should not be construed as limiting the present application.

FIG. 1 is a schematic view of a combined monitoring platform for a nuclear turbine according to one embodiment of the present application, as shown in FIG. 1, including:

a component model database 1, a load database 2, a materials database 3, a calculation server 4, a web server 5, and a client browser 6.

The component model database 1 stores component design parameters and three-dimensional mechanical models of the nuclear turbine, the load database 2 stores pressure load, centrifugal force load and thermal load of the nuclear turbine, the material database 3 stores material physical performance, material mechanical performance, high-temperature long-time mechanical performance and fatigue fracture mechanical performance of the nuclear turbine, the calculation server 4 comprises a memory, a processor and a safety monitoring computer program for monitoring dynamic strength and vibration of moving blades of the nuclear turbine, the safety monitoring computer program is stored on the memory and can run on the processor, and when the processor executes the computer program, the safety monitoring method for the dynamic strength and the vibration of the moving blades of the nuclear turbine is realized.

The design component model database 1, the load database 2 and the material database 3 are in communication connection with the computer server 4 and are used for sending mechanical models and data required by safety monitoring of dynamic strength and vibration of a moving blade of the nuclear turbine to the computer server 4;

the computer server 4 is in communication connection with the web server 5, the web server 5 is in communication connection with the client browser 6, and monitoring data or optimization information can be fed back to the web server 5 and the client browser 6 to be displayed.

The method, the device, the electronic equipment and the storage medium for monitoring the dynamic strength and the vibration of the moving blade of the nuclear turbine under the action of the rapid start thermal stress are described in the following by combining with the attached drawings.

Fig. 2 is a flowchart of a method for safely monitoring dynamic strength and vibration of a moving blade of a nuclear turbine according to an embodiment of the present application, as shown in fig. 2, the method includes the following steps:

s201, obtaining allowable safety factors of vibration stress, vibration resistance strength and dynamic strength of a moving blade of the nuclear turbine, and a first-order vibration frequency of the moving blade, a first vibration frequency at the highest limit of the working rotating speed, a second vibration frequency at the lowest working rotating speed, an m-order diameter vibration frequency of a full-circle connected long blade and the working rotating speed of the nuclear turbine as the operation state data of the moving blade.

The moving blade has an important influence on the safety and the service life of the nuclear power turbine, and when the moving blade bears centrifugal force and steam flow exciting force, parts are easily damaged, so that the safety and the service life of the nuclear power turbine are influenced.

In some implementations, design parameters, a three-dimensional mechanical model, a centrifugal force load, an excitation force load and material mechanical property data of a moving blade of the nuclear turbine can be input based on a component model database, a load database and a material database of the nuclear turbine, and a method and a subprogram for designing and monitoring the dynamic strength and vibration of the moving blade bearing the action of the centrifugal force, the low-frequency excitation force and the high-frequency excitation force are used to calculate the vibration stress, the vibration resistance strength and the allowable safety factor of the dynamic strength of the moving blade of the nuclear turbine, as well as the first-order vibration frequency of the moving blade, the first vibration frequency at the highest limit of the working rotation speed, the second vibration frequency at the lowest limit of the working rotation speed, the m-order diameter vibration frequency of the long blades connected in a whole circle and the working rotation speed of the nuclear turbine, as the operation state data of the moving blade.

Optionally, in this embodiment of the present application, the first vibration frequency at the highest limit of the operating rotation speed may be (1+0.01) times of the operating rotation speed of the nuclear turbine, and the second vibration frequency at the lowest operating rotation speed may be (1-0.03) times of the operating rotation speed of the nuclear turbine.

S202, determining dynamic strength and vibration reliability monitoring data according to the running state data of the moving blades.

In this embodiment of the application, the dynamic strength and vibration reliability monitoring data may include a dynamic strength safety ratio, a first frequency resonance ratio, a second frequency resonance ratio, and a third frequency resonance ratio.

In some implementations, the safety ratio of the dynamic strength of the moving blade is determined according to the vibration resistance, the vibration stress and the allowable safety factor of the dynamic strength of the moving blade by the following formula:

wherein R is_σvThe safe ratio, sigma, of the dynamic strength of the moving blade of the nuclear turbine bearing the centrifugal force and the steam flow exciting force_aThe vibration resistance of the moving blades, sigma_vIs the vibration stress of the moving blade, [ S ]_f]Safety factors are allowed for the dynamic strength of the moving blades.

In some implementations, a first frequency resonance ratio of the moving blade to avoid the low-frequency excitation force is determined according to a first vibration frequency of the moving blade at the highest limit of the working rotation speed, a second vibration frequency of the moving blade at the lowest limit of the working rotation speed, a rotation speed multiplying factor of the excitation force and the working rotation speed of the nuclear turbine, optionally, the first frequency resonance ratio includes a lower limit ratio and an upper limit ratio of a first-order vibration frequency to avoid the low-frequency excitation force, and the first frequency resonance ratio of the moving blade to avoid the low-frequency excitation force is determined by using the following formula:

wherein R is_d1Lower ratio, R, of low frequency excitation force frequency to first order vibration frequency away_u1Upper ratio of frequency of low frequency exciting force to first order vibration frequency avoiding_d1For the moving blade at the maximum working speed limit (1+0.01) n₀Frequency of vibration of time, f_d2For the moving blade at the lowest working rotating speed (1-0.03) n₀The vibration frequency of the time, K is the rotating speed multiplying power of the exciting force, n₀The working rotating speed of the nuclear turbine.

In some implementations, a second frequency resonance ratio of the moving blade to avoid the high-frequency excitation force is determined according to the first-order vibration frequency of the moving blade, the number of the stationary blades and the operating speed of the nuclear turbine by using the following formula:

wherein, Δ f_hSecond frequency resonance ratio, f, for moving blades to avoid high frequency excitation forces₁Is the first order vibration frequency, Z, of the moving blade_nNumber of stationary blades, n₀The working rotating speed of the nuclear turbine.

In some implementations, a third frequency resonance ratio of the m-order diameter vibration frequency of the full-circle connected long blade to avoid the high-frequency exciting force is determined by the following formula according to the m-order diameter vibration frequency of the full-circle connected long blade, the number of the static blades and the working rotating speed of the nuclear turbine:

wherein, Δ f_mThe m-step diameter vibration frequency of the long blade is connected for a whole circle to avoid the third frequency resonance ratio, f, of the high-frequency exciting force_dmThe m-order diameter vibration frequency of the long blades is connected for a whole circle, m is the pitch diameter number of the vibration of the whole circle of blades, Z_nNumber of stationary blades;

and S203, performing optimized control on the nuclear turbine according to the dynamic intensity and vibration reliability monitoring data.

In some implementations, the moving blade dynamic strength safety can be optimally controlled according to the dynamic strength safety ratio. In the embodiment of the application, the larger the safety ratio of the dynamic strength is, the higher the safety of the moving blade is.

In some implementations, the moving blade can be optimally controlled to avoid the low-frequency excitation force frequency resonance according to the first frequency resonance ratio, and the moving blade can be optimally controlled to avoid the high-frequency excitation force frequency resonance according to the second frequency resonance ratio. In the embodiment of the present application, the greater the first frequency resonance ratio or the second frequency resonance ratio is, the higher the safety of the rotor blade is.

In some implementations, the whole circle of connected long blades can be optimally controlled to avoid the high-frequency excitation force frequency resonance according to the third frequency resonance ratio. In the embodiment of the application, the larger the third frequency resonance ratio is, the higher the safety of the moving blade is.

Optionally, the dynamic strength and the vibration safety of the moving blade of the nuclear turbine are judged according to the dynamic strength and vibration reliability monitoring data, and if the safety of the moving blade does not meet preset conditions, the nuclear turbine is subjected to optimized control, so that the service life and the safety of the nuclear turbine are improved.

In the embodiment of the application, the dynamic strength and vibration reliability monitoring data can be determined according to the acquired running state data of the moving blade, and the nuclear power turbine is optimally controlled according to the dynamic strength and vibration reliability monitoring data. The embodiment of the application can accurately monitor the dynamic strength and the vibration safety of the moving blade of the nuclear turbine and optimally control the nuclear turbine, thereby prolonging the service life of the nuclear turbine and ensuring the long-period safe operation of the nuclear turbine.

Fig. 3 is a flowchart of optimization control performed in a safety monitoring method for dynamic strength and vibration of a moving blade of a nuclear turbine according to an embodiment of the present application, as shown in fig. 3, the method includes the following steps:

s301, obtaining allowable safety factors of vibration stress, vibration resistance strength and dynamic strength of a moving blade of the nuclear turbine, and a first-order vibration frequency of the moving blade, a first vibration frequency at the highest limit of the working rotating speed, a second vibration frequency at the lowest working rotating speed, an m-order diameter vibration frequency of a full-circle connected long blade and the working rotating speed of the nuclear turbine as the operation state data of the moving blade.

S302, determining dynamic strength and vibration reliability monitoring data according to the running state data of the moving blades.

For the related description of step S301 and step S302, reference may be made to the contents in the foregoing embodiments, and details are not repeated here.

S303, carrying out optimization control on the dynamic strength safety of the moving blade according to the dynamic strength safety ratio.

And determining that the dynamic strength safety design monitoring of the moving blade is qualified in response to the fact that the dynamic strength safety ratio is larger than a preset dynamic strength safety ratio threshold, determining that the dynamic strength safety design monitoring of the moving blade is unqualified in response to the fact that the dynamic strength safety ratio is smaller than or equal to the preset dynamic strength safety ratio threshold, and generating a dynamic strength optimization improvement strategy of the nuclear turbine.

Optionally, in this embodiment of the present application, the preset dynamic intensity safety ratio threshold may be 1, that is, if R is equal to R_σvIf R is greater than 1, the safety of the dynamic strength of the moving blade of the nuclear turbine is qualified by design and monitoring, which indicates that the safety of the dynamic strength of the moving blade of the nuclear turbine is in a controlled state_σvLess than or equal to 1, the design of the dynamic strength safety of the moving blade of the nuclear turbine is unqualified, and the requirement for optimizing and improving the blade profile width and thickness, the structure fillet, the connecting structure, the shroud thickness, the material grade and the like of the moving blade in the design stage is shown, so that the nuclear turbine is subjected to optimization control, the running state data of the moving blade is re-detected, and the optimization is finished until the dynamic strength safety ratio is greater than the preset dynamic strength safety ratio threshold.

S304, optimally controlling the moving blade to avoid the low-frequency excitation force frequency resonance according to the first frequency resonance ratio.

And determining that the design and monitoring of the moving blade avoiding the low-frequency excitation force frequency resonance are qualified in response to the lower limit ratio being greater than the first percentage limit value and the upper limit ratio being greater than the second percentage limit value, determining that the design and monitoring of the moving blade avoiding the low-frequency excitation force frequency resonance are unqualified in response to the lower limit ratio being less than or equal to the first percentage limit value and/or the upper limit ratio being less than or equal to the second percentage limit value, and generating an optimization improvement strategy for the moving blade avoiding the low-frequency excitation force frequency resonance. Wherein the second percentage threshold is less than the first percentage threshold.

Optionally, in this embodiment of the present application, the first percentage threshold may be 5%, and the second percentage threshold may be 3%, that is, if R is greater than the first percentage threshold, then R is greater than the second percentage threshold_d1> 5% and R_u1The design and monitoring of the nuclear turbine moving blade avoiding low-frequency excitation force frequency resonance is qualified, which indicates that the nuclear turbine moving blade is in a controlled state avoiding low-frequency excitation force frequency resonance, and if R is higher than 3 percent_d1Less than or equal to 5% or R_u1And the design monitoring is unqualified when the nuclear turbine moving blade avoids the low-frequency excitation force frequency resonance, which indicates that the blade profile width and thickness, the structure fillet, the connecting structure, the shroud thickness, the material grade and the like of the moving blade need to be optimized and improved in the design stage, so that the nuclear turbine is optimized and controlled, the running state data of the moving blade is detected again, and the optimization is finished until the lower limit ratio is greater than the first percentage threshold value and the upper limit ratio is greater than the second percentage threshold value.

And S305, optimally controlling the moving blade to avoid the high-frequency excitation force frequency resonance according to the second frequency resonance ratio.

And determining that the design and monitoring of the moving blade avoiding the high-frequency excitation force frequency resonance is qualified in response to the second frequency resonance ratio being greater than or equal to the first percentage threshold value, determining that the design and monitoring of the moving blade avoiding the high-frequency excitation force frequency resonance is unqualified in response to the second frequency resonance ratio being less than the first percentage threshold value, and generating an optimization and improvement strategy for the moving blade avoiding the high-frequency excitation force frequency resonance.

That is, if Δ f_hNot less than 5 percent, the design and the monitoring of the moving blade of the nuclear turbine avoiding the high-frequency excitation force frequency resonance are qualified, which indicates that the moving blade is in a controlled state avoiding the high-frequency excitation force frequency resonance, if delta f_hLess than 5 percent, the nuclear turbine moving blade avoids the high-frequency excitation force frequency resonance design and is unqualified to monitor, which shows that the blade profile width and thickness, the structure fillet, the connecting structure, the shroud thickness and the material grade of the moving blade need to be optimized and improved in the design stage, thereby optimally controlling the nuclear turbine and further optimizing and improving the nuclear turbineAnd detecting the operating state data of the moving blade again until the second frequency resonance ratio value is larger than or equal to the first percentage limit value, and finishing the optimization.

And S306, optimally controlling the whole circle of the long blades to avoid the high-frequency excitation force frequency resonance according to the third frequency resonance ratio.

And in response to the third frequency resonance ratio being greater than or equal to the first percentage threshold, determining that the design and monitoring of the whole-circle connected long blade for avoiding the high-frequency excitation force frequency resonance is qualified, in response to the third frequency resonance ratio being less than the first percentage threshold, determining that the design and monitoring of the whole-circle connected long blade for avoiding the high-frequency excitation force frequency resonance is unqualified, and generating an optimization improvement strategy of the whole-circle connected long blade for avoiding the high-frequency excitation force frequency resonance.

That is, if Δ f_mNot less than 5 percent, the design and the monitoring of the whole-circle connected long blade avoiding the high-frequency exciting force frequency resonance of the nuclear turbine are qualified, which indicates that the whole-circle connected long blade avoiding the high-frequency exciting force frequency resonance is in a controlled state, if delta f_mAnd the frequency resonance design monitoring of the whole circle of the long blade of the hollow nuclear power turbine is unqualified when the whole circle of the long blade avoids the high-frequency excitation force frequency resonance, which indicates that the blade profile width and thickness, the structure fillet, the connecting structure, the shroud thickness, the material mark and the like of the last-stage moving blade need to be optimized and improved in the design stage, so that the nuclear power turbine is optimized and controlled, the operation state data of the moving blade is detected again, and the optimization is finished until the third frequency resonance ratio is greater than or equal to the first percentage threshold value.

In the embodiment of the application, the dynamic strength safety of the moving blade is optimally controlled according to the dynamic strength safety ratio, the moving blade is optimally controlled by avoiding the low-frequency excitation force frequency resonance according to the first frequency resonance ratio, the moving blade is optimally controlled by avoiding the high-frequency excitation force frequency resonance according to the second frequency resonance ratio, and the whole circle of long blades is optimally controlled by avoiding the high-frequency excitation force frequency resonance according to the third frequency resonance ratio. The embodiment of the application can accurately monitor the dynamic strength and the vibration safety of the moving blade of the nuclear turbine and optimally control the nuclear turbine, thereby prolonging the service life of the nuclear turbine and ensuring the long-period safe operation of the nuclear turbine.

FIG. 4 is a flow chart of a method for monitoring the safety of the dynamic strength and vibration of a moving blade of a nuclear turbine of a specific type according to an embodiment of the present application, as shown in FIG. 4, the method includes the following steps:

s401, calculating the operation state data of the moving blade of the nuclear turbine.

Inputting design parameters, a three-dimensional mechanical model, a centrifugal force load, an exciting force load and material mechanical property data of a moving blade of the 1200MW nuclear power turbine based on a component model database 1, a load database 2 and a material database 3 of the nuclear power turbine, using a method and a subprogram for designing and monitoring the dynamic strength and vibration of the moving blade bearing the centrifugal force, the low-frequency exciting force and the high-frequency exciting force, and calculating the running state data of a moving blade at a certain stage of the 1200MW nuclear power turbine_v18.83MPa, vibration resistance intensity sigma_a253.99MPa, allowable safety factor of dynamic strength [ S [ ]_f]2.45, first order vibration frequency f₁123Hz, at the highest limit of the operating speed (1+0.01) n₀Frequency f of vibration of_d1128Hz, lowest (1-0.03) n at operating speed₀Time-limited vibration frequency f_d2107Hz, and m of the whole connected long blade is 6-step diameter vibration frequency f_dm1186Hz and operating speed n of a nuclear turbine₀＝1500r/min＝25Hz。

S402, calculating the dynamic strength safety ratio of the moving blade.

The moving blade of the 1200MW nuclear turbine bears the safe ratio R of the dynamic strength of the centrifugal force and the steam flow exciting force_σvCalculated according to the following formula:

in the above formula, σ_aThe vibration resistance strength of the moving blade is 253.99MPa, sigma_vAs vibrational stress of moving blades18.83MPa， [S_f]The safety factor of 2.45 is allowed for the dynamic strength of the moving blade.

S403, calculating a first frequency resonance ratio of the moving blade avoiding the low-frequency excitation force.

Optionally, the first frequency resonance ratio comprises a lower limit ratio and an upper limit ratio of first-order vibration frequency avoiding low-frequency excitation force frequency, and the first-order vibration frequency avoiding low-frequency excitation force frequency lower limit ratio R of the 1200MW nuclear turbine moving blade_d1And an upper ratio R_u1Respectively according to the following formula:

in the above formula, f_d1For the moving blade at the maximum working speed limit (1+0.01) n₀Vibration frequency of time 128Hz, f_d2For the moving blade at the lowest working rotating speed (1-0.03) n₀The vibration frequency is 107Hz, K is 5, the rotating speed multiplying power of the exciting force, and n₀The working speed 1500r/min of the 1200MW nuclear power turbine is 25 Hz.

S404, calculating a second frequency resonance ratio of the moving blade avoiding the high-frequency excitation force.

The first-order vibration frequency of the moving blade of the 1200MW nuclear power turbine avoids the second frequency resonance ratio delta f of the high-frequency exciting force_hCalculated according to the following formula:

in the above formula, f₁Is the first order vibration frequency of the moving blade of 123Hz, Z_nNumber of stationary blades 60, n₀The working speed of the nuclear power turbine is 1500r/min which is 25 Hz.

S405, calculating a third frequency resonance ratio of m-step diameter vibration frequency of the whole circle of connected long blades to avoid the high-frequency exciting force.

The m-order diameter vibration frequency of the whole circle connected long blade avoids the third frequency resonance ratio delta f of the high-frequency exciting force_mCalculated according to the following formula:

in the above formula, f_dmThe m-6 step diameter vibration frequency 1186Hz of the whole circle connected long blade, the m-6 step diameter number of the whole circle blade vibration, and Z_nThe number of stationary blades is 60.

And S406, optimizing and controlling the safety of the dynamic strength of the moving blade.

The dynamic strength safety of the moving blade of the 1200MW nuclear turbine is optimally designed and controlled through a dynamic strength optimization improvement strategy:

(1) if R is_σvWhen the dynamic strength safety of the moving blade of the 1200MW nuclear power turbine is qualified in design and monitoring, which means that the dynamic strength safety of the moving blade of the 1200MW nuclear power turbine is in a controlled state, the design and monitoring of the vibration strength safety of the moving blade are finished, and the step S407 is entered.

S407, the moving blade avoids the optimization control of the low-frequency excitation force frequency resonance.

The moving blade of the 1200MW nuclear power turbine avoids the low-frequency excitation force frequency resonance to carry out optimization design control through an optimization improvement strategy that the moving blade avoids the low-frequency excitation force frequency resonance:

(1) if R is_d13.60% > 5% and R_u11.90% > 3%, the design monitoring of the moving blade of the 1200MW nuclear power turbine is qualified by avoiding the low-frequency excitation force frequency resonance, which indicates that the moving blade of the 1200MW nuclear power turbine is in a controlled state by avoiding the low-frequency excitation force frequency resonance, the design monitoring of the moving blade avoiding the low-frequency excitation force frequency resonance is finished, and the step S408 is entered.

And S408, optimally controlling the moving blade to avoid the frequency resonance of the high-frequency exciting force.

The moving blade of the 1200MW nuclear power turbine avoids the high-frequency excitation force frequency resonance to carry out optimization design control through an optimization improvement strategy that the moving blade avoids the high-frequency excitation force frequency resonance:

(1) if Δ f_h91.80% or more than 5%, the design and monitoring of the moving blade of the 1200MW nuclear power turbine to avoid the high-frequency excitation force frequency resonance is qualified, the moving blade is in a controlled state to avoid the high-frequency excitation force frequency resonance, the design and monitoring of the moving blade to avoid the high-frequency excitation force frequency resonance are finished, and the step S409 is entered.

And S409, connecting the long blades in a whole circle to avoid the optimal control of the frequency resonance of the high-frequency exciting force.

The optimization and improvement strategy of avoiding high-frequency excitation force frequency resonance by connecting the long blades in a whole circle is to carry out optimization design control on avoiding the high-frequency excitation force frequency resonance by connecting the long blades in a whole circle of the 1200MW nuclear turbine:

(1) if Δ f_mThe design monitoring that the whole circle of the long blade avoids the high-frequency excitation force frequency resonance is qualified, the whole circle of the long blade is in a controlled state, and the design monitoring that the whole circle of the long blade avoids the high-frequency excitation force frequency resonance is finished.

On the basis of the above embodiment, a monitoring report of the nuclear turbine may also be printed or output, where the monitoring report may include monitoring data of multiple dimensions under each target of the nuclear turbine and a corresponding optimization and improvement strategy. Optionally, information such as an optimization result of the nuclear turbine can be included.

As shown in fig. 5, based on the same application concept, an embodiment of the present application further provides a safety monitoring device 500 for monitoring dynamic strength and vibration of a moving blade of a nuclear turbine, including:

an obtaining module 510, configured to obtain allowable safety factors of the vibration stress, the vibration resistance strength, and the dynamic strength of a moving blade of the nuclear turbine, and a first-order vibration frequency of the moving blade, a first vibration frequency at a maximum working rotation speed, a second vibration frequency at a minimum working rotation speed, an m-order diameter vibration frequency of a long blade connected in a full circle, and a working rotation speed of the nuclear turbine as operation state data of the moving blade;

a determining module 520, configured to determine dynamic strength and vibration reliability monitoring data according to the operating state data of the moving blade;

and the optimizing module 530 is used for optimizing and controlling the nuclear turbine according to the dynamic strength and vibration reliability monitoring data.

In one possible implementation, the determining module 520 is further configured to:

In one possible implementation, the optimizing module 530 is further configured to:

Based on the same application concept, the embodiment of the application also provides the electronic equipment.

Fig. 6 is a schematic structural diagram of an electronic device according to an embodiment of the present application. As shown in fig. 6, the electronic device 600 includes a memory 610, a processor 620, and a computer program product stored in the memory 610 and executable on the processor 620, and when the processor executes the computer program, the method for safely monitoring the dynamic strength and vibration of the moving blade of the nuclear turbine is implemented.

As will be appreciated by one skilled in the art, embodiments of the present application may be provided as a method, system, or computer program product. Accordingly, the present application may take the form of an entirely hardware embodiment, an entirely software embodiment or an embodiment combining software and hardware aspects. Furthermore, the present application may take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, and the like) having computer-usable program code embodied therein.

The present application is described with reference to flowchart illustrations and/or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the application. It will be understood that each process and/or block of the flowchart illustrations and/or block diagrams, and combinations of processes and/or blocks in the flowchart illustrations and/or block diagrams, can be implemented by computer program instructions. These computer program instructions may be provided to a processor of a general purpose computer, special purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.

These computer program instructions may also be stored in a computer-readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instruction means which implement the function specified in the flowchart flow or flows and/or block diagram block or blocks.

These computer program instructions may also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.

Based on the same application concept, the embodiment of the present application further provides a computer-readable storage medium, on which computer instructions are stored, wherein the computer instructions are used for causing a computer to execute the safety monitoring method for the dynamic strength and the vibration of the moving blade of the nuclear power turbine in the above embodiment.

Based on the same application concept, the embodiment of the present application further provides a computer program product, which includes a computer program, and the computer program, when being executed by a processor, provides the method for safely monitoring the dynamic strength and the vibration of the moving blade of the nuclear turbine in the above embodiments.

It should be noted that in the claims, any reference signs placed between parentheses shall not be construed as limiting the claim. The word "comprising" does not exclude the presence of elements or steps not listed in a claim. The word "a" or "an" preceding an element does not exclude the presence of a plurality of such elements. The application can be implemented by means of hardware comprising several distinct elements, and by means of a suitably programmed computer. In the unit claims enumerating several means, several of these means may be embodied by one and the same item of hardware. The usage of the words first, second and third, etcetera do not indicate any ordering. These words may be interpreted as names.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present application, "a plurality" means two or more unless specifically limited otherwise.

While the preferred embodiments of the present application have been described, additional variations and modifications in those embodiments may occur to those skilled in the art once they learn of the basic inventive concepts. Therefore, it is intended that the appended claims be interpreted as including preferred embodiments and all alterations and modifications as fall within the scope of the application.

It will be apparent to those skilled in the art that various changes and modifications may be made in the present invention without departing from the spirit and scope of the invention. Thus, if such modifications and variations of the present application fall within the scope of the claims of the present application and their equivalents, the present application is intended to include such modifications and variations as well.

Claims

1. A safety monitoring method for dynamic strength and vibration of a moving blade of a nuclear turbine is characterized by comprising the following steps:

determining the dynamic strength and vibration reliability monitoring data according to the running state data of the moving blade;

and performing optimized control on the nuclear turbine according to the dynamic intensity and vibration reliability monitoring data.

2. The method of claim 1, wherein said determining said dynamic-strength and vibration-reliability monitoring data from operational-condition data of said moving blades comprises:

determining a first frequency resonance ratio of the moving blade avoiding the low-frequency exciting force according to a first vibration frequency of the moving blade at the highest limit of the working rotating speed, a second vibration frequency of the moving blade at the lowest limit of the working rotating speed, the rotating speed multiplying power of the exciting force and the working rotating speed of the nuclear power turbine, wherein the first frequency resonance ratio comprises a lower limit ratio and an upper limit ratio of the first-order vibration frequency avoiding the low-frequency exciting force;

determining a second frequency resonance ratio of the moving blade avoiding high-frequency exciting force according to the first-order vibration frequency of the moving blade, the number of the static blades and the working rotating speed of the nuclear turbine;

determining a third frequency resonance ratio of the m-order diameter vibration frequency of the whole circle of long blades to avoid high-frequency exciting force according to the m-order diameter vibration frequency of the whole circle of long blades, the number of the static blades and the working rotating speed of the nuclear power turbine;

and determining the dynamic intensity safety ratio, the first frequency resonance ratio, the second frequency resonance ratio and the third frequency resonance ratio as the dynamic intensity and vibration reliability monitoring data.

3. The method of claim 2, wherein said optimizing control of said nuclear turbine based on said dynamic intensity and vibration reliability monitoring data comprises:

according to the dynamic strength safety ratio, optimally controlling the dynamic strength safety of the moving blade;

according to the first frequency resonance ratio, optimally controlling the moving blade to avoid low-frequency exciting force frequency resonance;

according to the second frequency resonance ratio, optimally controlling the moving blade to avoid the high-frequency exciting force frequency resonance;

and optimally controlling the whole circle of the long blades to avoid the high-frequency excitation force frequency resonance according to the third frequency resonance ratio.

4. The method according to claim 3, wherein the optimally controlling the moving blade dynamic strength safety according to the dynamic strength safety ratio comprises:

responding to the fact that the dynamic strength safety ratio is smaller than or equal to the preset dynamic strength safety ratio threshold, determining that the design and monitoring of the dynamic strength safety of the moving blade is not qualified, and generating a dynamic strength optimization improvement strategy of the nuclear power turbine;

and carrying out optimization control on the nuclear turbine according to the dynamic intensity optimization improvement strategy until the dynamic intensity safety ratio is greater than the preset dynamic intensity safety ratio threshold value, and finishing the optimization.

5. The method of claim 3, wherein said optimally controlling said rotor blade to avoid low frequency excitation force frequency resonance based on said first frequency resonance ratio comprises:

in response to the lower limit ratio being greater than a first percentage threshold and the upper limit ratio being greater than a second percentage threshold, determining that the moving blade is qualified for avoiding low-frequency excitation force frequency resonance design monitoring;

in response to the lower limit ratio being less than or equal to the first percentage threshold and/or the upper limit ratio being less than or equal to the second percentage threshold, determining that the moving blade design monitoring for avoiding low-frequency excitation force frequency resonance is not qualified, and generating an optimization improvement strategy for the moving blade for avoiding low-frequency excitation force frequency resonance;

according to an optimization improvement strategy of the moving blade for avoiding low-frequency excitation force frequency resonance, performing optimization control on the nuclear power turbine until the lower limit ratio is greater than a first percentage threshold value and the upper limit ratio is greater than a second percentage threshold value, and finishing optimization; wherein the second percentage threshold is less than the first percentage threshold.

6. The method of claim 3, wherein the optimally controlling the moving blade to avoid high frequency excitation force frequency resonance according to the second frequency resonance ratio comprises:

in response to the second frequency resonance ratio being greater than or equal to a first percentage threshold, determining that the rotor blade is qualified for design monitoring avoiding high frequency excitation force frequency resonance;

in response to the second frequency resonance ratio being smaller than the first percentage threshold, determining that the rotor blade is unqualified in design monitoring for avoiding high-frequency excitation force frequency resonance, and generating an optimization improvement strategy for avoiding the high-frequency excitation force frequency resonance by the rotor blade;

7. The method of claim 3, wherein said optimally controlling said full turn long blade to avoid high frequency excitation force frequency resonance according to said third frequency resonance ratio comprises:

in response to the third frequency resonance ratio being greater than or equal to a first percentage threshold, determining that the full circle of connected long blades are qualified for design monitoring avoiding high frequency excitation force frequency resonance;

in response to the third frequency resonance ratio being smaller than the first percentage threshold, determining that the whole circle of long connected blades is unqualified in design monitoring for avoiding high-frequency excitation force frequency resonance, and generating an optimization improvement strategy for avoiding the high-frequency excitation force frequency resonance by the whole circle of long connected blades;

and performing optimization control on the nuclear turbine according to an optimization improvement strategy of avoiding high-frequency excitation force frequency resonance by the whole circle of long blades until the third frequency resonance ratio is greater than or equal to the first percentage threshold value, and finishing optimization.

8. The utility model provides a safety monitoring device of dynamic strength and vibration of moving blade of nuclear power steam turbine which characterized in that includes:

the system comprises an acquisition module, a storage module and a control module, wherein the acquisition module is used for acquiring the vibration stress, the vibration resistance strength and the allowable safety factor of the dynamic strength of a moving blade of a nuclear turbine, and the first-order vibration frequency of the moving blade, the first vibration frequency at the highest limit of the working rotating speed, the second vibration frequency at the lowest working rotating speed, the m-order diameter vibration frequency of a long blade connected in a whole circle and the working rotating speed of the nuclear turbine as the running state data of the moving blade;

the determining module is used for determining the dynamic strength and vibration reliability monitoring data according to the running state data of the moving blades;

and the optimization module is used for carrying out optimization control on the nuclear power turbine according to the dynamic intensity and vibration reliability monitoring data.

9. The apparatus of claim 8, wherein the determining module is further configured to:

10. The apparatus of claim 9, wherein the optimization module is further configured to:

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

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

13. The apparatus of claim 10, wherein the optimization module is further configured to:

14. The apparatus of claim 10, wherein the optimization module is further configured to:

15. An electronic device, comprising:

at least one processor; and

a memory communicatively coupled to the at least one processor; wherein,

the memory stores instructions executable by the at least one processor to enable the at least one processor to perform the method of any one of claims 1-7.

16. A non-transitory computer readable storage medium having stored thereon computer instructions for causing the computer to perform the method of any one of claims 1-7.

17. A computer program product comprising a computer program which, when executed by a processor, implements the method according to any one of claims 1-7.