CN114412587B

CN114412587B - Multi-dimensional reliability monitoring method for nuclear turbine

Info

Publication number: CN114412587B
Application number: CN202111452774.4A
Authority: CN
Inventors: 史进渊; 蒋俊; 谢岳生; 杨志鹏; 华浩磊; 闫立鹏
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: 2022-11-08
Anticipated expiration: 2041-12-01
Also published as: CN114412587A

Abstract

The invention provides a multi-dimensional reliability monitoring method and device of a nuclear turbine, electronic equipment and a storage medium, and relates to the technical field of nuclear turbines. The scheme is as follows: acquiring monitoring data of dynamic strength and vibration reliability of a moving blade of a nuclear turbine under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force; acquiring torsional vibration reliability monitoring data of a multi-rotor system of a nuclear turbine subjected to power grid electrical disturbance fault; acquiring first shaft system vibration reliability monitoring data and second shaft system vibration reliability monitoring data of a rotor and bearing system of a nuclear turbine under the action of forced vibration and self-excited vibration; generating an optimization improvement strategy of the nuclear power turbine according to at least one abnormal reliability monitoring data in the reliability monitoring data; and performing optimization control on the nuclear turbine according to an optimization improvement strategy. The method disclosed by the invention can realize high-reliability operation of the nuclear turbine.

Description

Multi-dimensional reliability monitoring method for nuclear turbine

Technical Field

The disclosure relates to the technical field of nuclear turbines, in particular to a multidimensional reliability monitoring method and device of a nuclear turbine, electronic equipment and a storage medium.

Background

The nuclear turbine can bear the action of various damage mechanisms in operation, and the high-reliability operation of the nuclear turbine is influenced. At present, a method for monitoring the reliability of a nuclear turbine under the action of various damage mechanisms is not available.

Disclosure of Invention

The disclosure provides a multi-dimensional reliability monitoring method and device for a nuclear turbine, electronic equipment and a storage medium.

According to one aspect of the present disclosure, a method for monitoring the multidimensional reliability of a nuclear turbine is provided, which includes:

acquiring dynamic strength and vibration reliability monitoring data of a moving blade of a nuclear turbine under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force;

acquiring torsional vibration reliability monitoring data of a multi-rotor system of a nuclear turbine subjected to power grid electrical disturbance fault;

acquiring first shaft system vibration reliability monitoring data and second shaft system vibration reliability monitoring data of a rotor and bearing system of a nuclear turbine under the action of forced vibration and self-excited vibration;

generating an optimization improvement strategy of the nuclear power turbine according to at least one abnormal reliability monitoring data of the dynamic intensity and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data;

and performing optimization control on the nuclear turbine according to an optimization improvement strategy.

In the method, the high reliability of the nuclear turbine is realized by performing design monitoring on the dynamic strength and vibration of a moving blade bearing the centrifugal force, the low-frequency excitation force and the high-frequency excitation force in a design stage, performing design monitoring on torsional vibration of a multi-rotor system bearing the electric disturbance fault of a power grid, performing design monitoring on shafting vibration of a rotor and bearing system bearing the forced vibration and the self-excited vibration, and performing monitoring on shafting vibration operation of the rotor and bearing system bearing the forced vibration and the self-excited vibration in an operation stage, so that the aims of long service life, high safety guarantee and high reliability operation of the nuclear turbine are fulfilled.

According to another aspect of the present disclosure, there is provided a multi-dimensional reliability monitoring device for a nuclear turbine, comprising:

the first acquisition module is used for acquiring the monitoring data of the dynamic strength and the vibration reliability of the moving blade of the nuclear turbine under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force;

the second acquisition module is used for acquiring torsional vibration reliability monitoring data of a multi-rotor system of the nuclear turbine, which bears the electrical disturbance fault of a power grid;

the third acquisition module is used for acquiring the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data of the rotor and bearing system of the nuclear turbine under the action of forced vibration and self-excited vibration;

the generating module is used for generating an optimization improvement strategy of the nuclear power turbine according to at least one abnormal reliability monitoring data in the dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data;

and the optimization module is used for carrying out optimization control on the nuclear turbine according to an optimization improvement strategy.

According to another aspect of the present disclosure, there is provided an electronic device comprising a memory, a processor;

the processor is used for implementing the multidimensional reliability monitoring method for the nuclear power turbine according to the embodiment of the first aspect of the disclosure by reading the executable program codes stored in the memory to run programs corresponding to the executable program codes.

According to another aspect of the present disclosure, there is provided a computer readable storage medium having stored thereon a computer program which, when executed by a processor, implements a method for multidimensional reliability monitoring of a nuclear power turbine in accordance with an embodiment of the first aspect of the present disclosure.

According to another aspect of the present disclosure, a computer program product is provided, comprising a computer program which, when executed by a processor, implements the method for multidimensional reliability monitoring of a nuclear power turbine according to an embodiment of the first aspect of the present disclosure.

It should be understood that the statements in this section do not necessarily identify key or critical features of the embodiments of the present disclosure, nor do they necessarily limit the scope of the present disclosure. Other features of the present disclosure will become apparent from the following description.

Drawings

FIG. 1 is a schematic illustration of a combined monitoring platform for a nuclear turbine;

FIG. 2 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 3 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 4 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 5 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 6 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 7 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 8 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 9 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 10 is a flow chart of a multi-dimensional reliability monitoring method of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 11 is a flow chart of a method for multidimensional reliability monitoring of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 12 is a block diagram of a multi-dimensional reliability monitoring apparatus of a nuclear power turbine according to one embodiment of the present disclosure;

FIG. 13 is a block diagram of an electronic device for implementing a multi-dimensional reliability monitoring method of a nuclear power turbine according to an embodiment of the present disclosure.

Detailed Description

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

Fig. 1 is a combined monitoring platform of a nuclear turbine according to an embodiment of the present application, as shown in fig. 1, the combined monitoring platform includes:

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

The component model library server stores component design parameters and three-dimensional mechanical models of the nuclear turbine, and the load database server stores pressure load, centrifugal force load, thermal load, rigidity coefficient and damping coefficient of a bearing oil film and shaft vibration relative displacement peak value D of the nuclear turbine rotor shaft neck on-line monitoring _p-pr (mum) and bearing on-line monitoring tile vibration displacement peak value D _p-pb The method comprises the steps that (mum) and a start-stop curve of the nuclear turbine are obtained, a material database server stores physical properties, mechanical properties of materials, high-temperature long-time mechanical properties and fatigue fracture mechanical properties of the nuclear turbine, a calculation server comprises a memory, a processor and a computer program which is stored in the memory and can be used for monitoring the long service life, high safety and high reliability of the nuclear turbine and run on the processor, and when the processor executes the computer program, the multidimensional reliability monitoring method of the nuclear turbine provided by the invention is realized.

The component model data 1, the load database 2 and the material database 3 are in communication connection with the calculation server and used for sending mechanical models and data required by the nuclear turbine for monitoring under different targets and different dimensions to the calculation server 4;

the calculation 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 disclosed method, apparatus, electronic device and storage medium for monitoring the reliability of multiple dimensions of a nuclear turbine are described below with reference to the accompanying drawings.

Fig. 2 is a schematic flow chart of a multidimensional reliability monitoring method for a nuclear turbine provided in the embodiment of the present application.

As shown in fig. 2, the multidimensional reliability monitoring method for a nuclear turbine includes the following steps:

s201, obtaining the dynamic intensity and vibration reliability monitoring data of the action of centrifugal force, low-frequency exciting force and high-frequency exciting force borne by a moving blade of the nuclear turbine.

The dynamic strength and vibration reliability monitoring data of the moving blade of the nuclear turbine are used for determining whether the dynamic strength and vibration reliability of the moving blade of the nuclear turbine subjected to the centrifugal force, the low-frequency exciting force and the high-frequency exciting force are qualified or not.

Optionally, the data for monitoring the dynamic strength and the vibration reliability of the moving blade of the nuclear turbine includes at least one of:

the safety ratio of the dynamic strength of the moving blade; the moving blade avoids the low-frequency excitation force frequency resonance ratio; the moving blade avoids the frequency resonance ratio of the high-frequency excitation force; the m-order diameter vibration frequency of the whole circle of the connected long blade avoids the resonance ratio of the high-frequency exciting force frequency.

Correspondingly, the dynamic strength and the vibration reliability of the moving blade of the nuclear turbine bearing the centrifugal force, the low-frequency exciting force and the high-frequency exciting force are designed and monitored, and the method comprises the following steps:

monitoring the dynamic strength of a moving blade of a nuclear turbine based on the safe ratio of the dynamic strength of the moving blade;

the method comprises the following steps that on the basis of the frequency resonance ratio of low-frequency excitation force avoided by a moving blade of the nuclear turbine, the design of the moving blade avoiding the low-frequency excitation force frequency resonance is monitored;

the method comprises the following steps that on the basis of the frequency resonance ratio of high-frequency excitation force avoided by a moving blade of the nuclear turbine, the design that the moving blade avoids the high-frequency excitation force frequency resonance is monitored;

the method is based on the m-step diameter vibration frequency avoiding high-frequency exciting force frequency resonance ratio of the whole-circle connecting long blade of the nuclear turbine, and the design of the whole-circle connecting long blade avoiding high-frequency exciting force frequency resonance is monitored.

S202, torsional vibration reliability monitoring data of a multi-rotor system of the nuclear turbine subjected to the electrical disturbance fault of the power grid are obtained.

The torsional vibration reliability monitoring data of the multi-rotor system subjected to the electric disturbance fault of the power grid are used for determining whether the torsional vibration reliability design of the multi-rotor system subjected to the electric disturbance fault of the power grid is qualified or not.

Optionally, the torsional vibration reliability monitoring data of the multi-rotor system subjected to the grid electrical disturbance fault includes at least one of the following items:

the torsional vibration frequency of the multi-rotor system avoids the ratio of the working frequency of the power grid; the torsional vibration frequency of the multi-rotor system avoids the ratio of twice the working frequency of the power grid; the torsional vibration stress ratio of the multi-rotor system of the nuclear turbine when the two-phase short circuit occurs in the power system.

Correspondingly, the torsional vibration design monitoring that the many rotor systems of nuclear power steam turbine bore electric disturbance trouble of electric wire netting includes:

and optimally designing and controlling the torsional vibration frequency of the multi-rotor system of the nuclear turbine to avoid the working frequency of the power grid based on the ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid.

Based on the ratio of the torsional vibration frequency of the multi-rotor system to the doubled working frequency of the power grid, the torsional vibration frequency of the multi-rotor system of the nuclear turbine to the doubled working frequency of the power grid is optimally designed and controlled.

Based on the torsional vibration stress ratio of the multi-rotor system of the nuclear turbine when the two-phase short circuit occurs in the power system, the torsional vibration stress of the multi-rotor system of the nuclear turbine when the two-phase short circuit occurs is optimally designed and controlled.

S203, obtaining the vibration reliability monitoring data of the first shaft system and the vibration reliability monitoring data of the second shaft system of the rotor and the bearing system of the nuclear turbine which bear the action of forced vibration and self-excited vibration.

And the first shafting vibration reliability monitoring data of the rotor and bearing system under the action of forced vibration and self-excited vibration is used for determining whether the shafting vibration reliability design of the rotor and bearing system under the action of forced vibration and self-excited vibration is qualified.

Optionally, the first shaft system vibration reliability monitoring data of the rotor and bearing system subjected to the forced vibration and the self-excited vibration comprises at least one of the following:

the ratio of the critical rotational speed of the rotor to the critical rotational speed of the bearing system; the ratio of the unstable rotating speed of the rotor to the unstable rotating speed of the bearing system; a logarithmic decrement ratio of the rotor to the bearing system; the imbalance response ratio of the rotor and the bearing system at the working rotating speed; the rotor to bearing system imbalance response ratio at critical rotational speeds.

Correspondingly, the design and monitoring of the shafting vibration reliability of the rotor and bearing system under the action of forced vibration and self-excited vibration comprise the following steps:

based on the ratio of the critical rotating speeds of the rotor and the bearing system, optimally designing and controlling the critical rotating speeds of the rotor and the bearing system to avoid the working rotating speed;

and optimally designing and controlling the stability of the rotor and the bearing system based on the instability rotating speed ratio of the rotor and the bearing system.

And optimally designing and controlling the logarithmic decrement of the rotor and bearing system based on the logarithmic decrement ratio of the rotor and bearing system.

And carrying out optimal design control on the unbalanced response of the rotor and the bearing system at the working rotating speed based on the unbalanced response ratio of the rotor and the bearing system at the working rotating speed.

And performing optimal design control on the unbalanced response of the rotor and the bearing system at the critical rotating speed based on the unbalanced response ratio of the rotor and the bearing system at the critical rotating speed.

And the second shaft system vibration reliability monitoring data of the rotor and bearing system under the action of the forced vibration and the self-excited vibration is used for determining whether the shaft system vibration reliability operation of the rotor and bearing system under the action of the forced vibration and the self-excited vibration is qualified.

Optionally, the second shaft system vibration reliability monitoring data that the rotor and the bearing system are subjected to the forced vibration and the self-excited vibration comprises:

the method comprises the steps of monitoring the ratio of shaft vibration relative displacement of a nuclear power turbine rotor shaft neck on line and monitoring the ratio of bearing vibration displacement on line.

Correspondingly, the shafting vibration reliability operation monitoring method for the rotor and bearing system under the action of forced vibration and self-excited vibration comprises the following steps:

and on the basis of the ratio of the shaft vibration relative displacement of the rotor journal of the nuclear power steam turbine, the shaft vibration relative displacement of the rotor journal is monitored on line, and the operation is controlled.

And based on the bearing on-line monitoring tile vibration displacement ratio, carrying out operation control on the bearing on-line monitoring tile vibration displacement.

And S204, generating an optimization improvement strategy of the nuclear turbine according to at least one abnormal reliability monitoring data in the dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data.

Judging whether at least one abnormal reliability monitoring data in the obtained dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data meets a monitoring qualified condition, and if the abnormal reliability monitoring data which does not meet the monitoring qualified condition exists, generating an optimization improvement strategy of the nuclear power turbine based on the abnormal reliability monitoring data.

For example, if the abnormal reliability monitoring data can be dynamic strength and vibration reliability monitoring data, an optimization and improvement strategy for designing the dynamic strength and vibration reliability of the moving blade under the action of centrifugal force, low-frequency excitation force and high-frequency excitation force is generated; and if the abnormal reliability monitoring data are second shaft system vibration reliability monitoring data, generating an optimization and improvement strategy for reliable operation of shaft system vibration, wherein the rotor and bearing system bears the action of forced vibration and self-excited vibration.

The abnormal reliability monitoring data may be one or more.

And S205, performing optimization control on the nuclear turbine according to an optimization improvement strategy.

Optionally, the optimization and improvement strategy comprises an adjusting component and an adjusting parameter of the nuclear turbine, and the nuclear turbine can be optimally controlled according to the adjusting component and the adjusting parameter. Wherein the optimization control may comprise design optimization control and/or operation optimization control.

In the embodiment of the disclosure, dynamic strength and vibration reliability monitoring data of a moving blade of a nuclear turbine bearing centrifugal force, low-frequency exciting force and high-frequency exciting force are obtained, torsional vibration reliability monitoring data of a multi-rotor system bearing power grid electrical disturbance fault is obtained, first shaft system vibration reliability monitoring data and second shaft system vibration reliability monitoring data of a rotor and bearing system bearing forced vibration and self-excited vibration are obtained, an optimization improvement strategy of the nuclear turbine is generated according to at least one abnormal reliability monitoring data of the dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data, and optimization control is performed on the nuclear turbine according to the optimization improvement strategy. According to the method, the high reliability of the nuclear turbine is realized by performing design monitoring on the dynamic strength and vibration of the moving blade under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force, the torsional vibration of a multi-rotor system under the action of electric disturbance fault, the shafting vibration of a rotor and bearing system under the action of forced vibration and self-excited vibration, and the shafting vibration reliability of the rotor and bearing system under the action of forced vibration and self-excited vibration in the operation stage, so that the purposes of long service life, high safety guarantee and high reliability operation of the nuclear turbine are realized.

Fig. 3 is a flowchart of a multidimensional reliability monitoring method for a nuclear power turbine according to an embodiment of the present disclosure, and further with reference to fig. 3, on the basis of the above embodiment, a process of generating an optimization improvement strategy for a nuclear power turbine and performing optimization control on the nuclear power turbine according to the optimization improvement strategy is explained, including the following steps:

s301, judging whether the nuclear turbine meets monitoring qualified conditions or not according to the dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data.

Optionally, each type of reliability monitoring data may be compared with respective monitoring qualified conditions to determine abnormal reliability monitoring data, and when the abnormal reliability monitoring data is determined, it may be determined that the nuclear turbine does not meet the monitoring qualified conditions and needs to be optimally controlled. If the abnormal reliability monitoring data are not determined, the nuclear power turbine can be determined to meet the monitoring qualified conditions, and optimization control is not needed.

For example, the safe ratio R of the dynamic strength of the moving blade can be determined _σv Comparing the value with a preset dynamic strength safety ratio threshold value, and if R is equal to the preset dynamic strength safety ratio threshold value _σv If the value is greater than the preset dynamic strength safety ratio threshold value, determining that the dynamic strength design monitoring of the moving blade is qualified, and if R is greater than the preset dynamic strength safety ratio threshold value _σv And determining that the dynamic strength design monitoring of the moving blade is not qualified when the value is less than or equal to the preset dynamic strength safety ratio threshold. For example, the preset dynamic intensity safety ratio threshold may be 1. If R is _σv The dynamic strength of the moving blade of the nuclear turbine is qualified by design and monitoring; if R is _σv Less than or equal to 1, and the dynamic strength design monitoring of the moving blade of the nuclear turbine is unqualified.

S302, if one reliability monitoring data does not meet the qualified monitoring condition, generating an optimization improvement strategy of the nuclear turbine based on abnormal reliability monitoring data which does not meet the qualified monitoring condition.

If the reliability monitoring data do not meet the monitoring qualified conditions, the reliability monitoring data are abnormal reliability monitoring data, the part to which the abnormal reliability monitoring data belong is obtained, the optimization model of the nuclear turbine is called based on the part to which the abnormal reliability monitoring data belong, and the optimization improvement strategy of the nuclear turbine is generated based on the optimization model.

Safety ratio R of dynamic strength of moving blade _σv This reliability monitoring data is taken as an example, if R _σv Less than or equal to 1, the dynamic strength of the movable blade of the nuclear turbine is not designed and monitored properly, and R is _σv And calling an optimization model corresponding to the moving blade to generate a design optimization improvement strategy of the nuclear turbine.

On-line monitoring of shaft vibration relative displacement ratio R by nuclear power steam turbine rotor shaft neck _p-pr This reliability monitoring data is taken as an example, if R _p-pr Not less than 1, if the operation monitoring of the shaft vibration relative displacement is unqualified when the nuclear power steam turbine rotor shaft neck on-line monitoring is carried outR _p-pr And for the abnormal reliability monitoring data, the part to which the abnormal reliability monitoring data belongs is a rotor journal of the nuclear turbine, and an optimization model corresponding to the rotor journal can be called to generate an operation optimization improvement strategy of the nuclear turbine.

And S303, acquiring an adjusting component of the nuclear turbine according to the optimization and improvement strategy.

Optionally, the optimization and improvement strategy includes adjustment components required by the nuclear turbine and adjustment parameters of each adjustment component, where the adjustment components are components to which the abnormal reliability monitoring data belongs in the above embodiments, and may further include other related components.

Illustratively, the abnormal reliability monitoring data is dynamic strength and vibration reliability monitoring data, and the optimization improvement strategy may include a design optimization improvement strategy of the moving blade, for example, a blade profile width and thickness, a structure fillet, a connection structure, a shroud thickness, a material model, and the like of the moving blade.

Illustratively, the abnormal reliability monitoring data is torsional vibration reliability monitoring data of the multi-rotor system subjected to the grid electrical disturbance fault, and the optimization and improvement strategy may include a design optimization and improvement strategy of the multi-rotor system, for example, optimization and improvement of the structure of the rotor or the coupling, adoption of a material with better yield strength, optimization of the structural geometry of the multi-rotor system, and the like.

For example, the abnormal reliability monitoring data is the first shaft system vibration reliability monitoring data of the rotor and bearing system subjected to the forced vibration and the self-excited vibration, and the optimization and improvement strategy may include the design optimization and improvement strategy of the rotor and bearing system, for example, the optimization and improvement of the bearing form or the rotor structure is performed, a bearing with better stability is used instead, or the geometric dimension of the rotor structure is optimized, and the like.

For example, the abnormal reliability monitoring data is second shaft system vibration reliability monitoring data of the rotor and bearing system under the action of forced vibration and self-excited vibration, and the optimization and improvement strategy may include an operation optimization and improvement strategy of the rotor and bearing system, for example, in a use stage, the rotor and bearing of the steam turbine are required to be overhauled, a cause of excessive rotor and bearing vibration is found and improved, and the like.

S304, optimizing the adjusting component according to the adjusting parameters of the adjusting component in the optimization and improvement strategy.

And performing design optimization or operation optimization on the adjusting part according to the adjusting parameters of the adjusting part in the optimization and improvement strategy.

In some implementations, a moving blade of a nuclear turbine is designed and optimized according to the tuning parameters.

In other implementations, a multi-rotor system of a nuclear turbine is designed and optimized based on the tuning parameters.

In other implementations, a rotor and bearing system of a nuclear turbine is designed and optimized based on the tuning parameters.

In other implementations, a rotor and bearing system of a nuclear turbine is optimized for operation based on the tuning parameters.

And S305, continuing to monitor the abnormal reliability monitoring data which do not meet the monitoring qualified conditions, if the newly acquired reliability monitoring data do not meet the monitoring qualified conditions, updating the optimization improvement strategy, and continuing to optimize the adjusting part based on the updated optimization improvement strategy.

Continuing to monitor the abnormal reliability monitoring data which do not meet the qualified monitoring conditions, and if the newly acquired reliability monitoring data meet the qualified monitoring conditions, ending the monitoring; and if the newly acquired reliability monitoring data still do not meet the monitoring qualified conditions, increasing the optimization strength of the optimization improvement strategy, updating the optimization improvement strategy, and continuously optimizing the adjusting part based on the updated optimization improvement strategy until the reliability monitoring data meet the monitoring qualified conditions.

In the embodiment of the disclosure, an optimization improvement strategy of the nuclear turbine is generated based on abnormal reliability monitoring data which do not meet monitoring qualified conditions, an adjusting component of the nuclear turbine is obtained according to the optimization improvement strategy, the adjusting component is optimized according to adjusting parameters of the adjusting component in the optimization improvement strategy, monitoring is continuously performed on the abnormal reliability monitoring data which do not meet the monitoring qualified conditions after optimization, if the service life monitoring data obtained again do not meet the monitoring qualified conditions, the optimization improvement strategy is updated, and the adjusting component is continuously optimized based on the updated optimization improvement strategy. In the embodiment of the disclosure, an optimization and improvement strategy is generated based on abnormal reliability monitoring data and the nuclear turbine is optimized, so that main factors influencing the reliability and safe operation of the nuclear turbine are improved in a targeted manner, the nuclear turbine is operated safely and reliably, the service life of the nuclear turbine is prolonged, and the purpose of long-life operation of the nuclear turbine is achieved.

Fig. 4 is a flowchart of a method for monitoring reliability of a nuclear turbine according to an embodiment of the present disclosure, and on the basis of the above embodiment, with reference to fig. 4, a process of designing and monitoring a moving blade is explained, including the following steps:

s401, acquiring operation state data of the moving blade under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force.

Optionally, based on a component model library server, a load database server and a material database server of the nuclear turbine, inputting 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, and calculating operation state data of the moving blade of the nuclear turbine by using a method and a subprogram for monitoring the dynamic strength and the vibration design of the moving blade bearing the action of the centrifugal force, the low-frequency excitation force and the high-frequency excitation force, wherein the operation state data comprises the vibration stress sigma of the moving blade _v Vibration resistance σ _a Allowable safety factor of dynamic strength _f ]First order vibration frequency f ₁ The maximum working rotation speed is (1 + 0.01) n ₀ Frequency of vibration of time f _d1 N is lowest (1-0.03) at working rotating speed ₀ Time-limited vibration frequency f _d2 M-order diameter vibration frequency f of long blades connected in full circle _dm And the working speed n of the nuclear turbine ₀ 。

S402, determining dynamic strength and vibration reliability monitoring data according to the running state data of the moving blades.

Optionally, according to the operation state data of the moving blade, a dynamic strength safety ratio of the moving blade, a first frequency resonance ratio of the moving blade avoiding the low-frequency excitation force, a second frequency resonance ratio of the moving blade avoiding the high-frequency excitation force, and a third frequency resonance ratio of the m-step diameter vibration frequency of the full-circle connected long blade avoiding the high-frequency excitation force are determined as the dynamic strength and vibration reliability monitoring data.

In some implementations, a safety ratio R of the dynamic strength of the moving blade is determined according to the vibration resistance strength, the vibration stress and the allowable safety factor of the dynamic strength of the moving blade _σv 。

Safe ratio R of dynamic strength of moving blade of nuclear turbine subjected to centrifugal force and steam flow exciting force _σv Calculated according to the following formula:

wherein σ _a The vibration resistance of the rotor blade, σ _v Is the vibration stress of the rotor blade, [ S ] _f ]And a safety factor is allowed for the dynamic strength of the moving blade.

In other implementations, a first frequency resonance ratio of the moving blade avoiding the low-frequency exciting force is determined 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 turbine, wherein the first frequency resonance ratio comprises a lower limit ratio R of the first-order vibration frequency avoiding the low-frequency exciting force frequency _d1 And an upper ratio R _u1 。

First-order vibration frequency of moving blade of nuclear turbine avoids lower limit ratio R of low-frequency excitation force frequency _d1 And an upper ratio R _u1 Respectively according to the following formula:

wherein f is _d1 The maximum working rotation speed of the rotor blade is (1 + 0.01) n ₀ Frequency of vibration of time, f _d2 For the moving blade at the lowest working rotating speed (1-0.03) n ₀ The vibration frequency of the time, K is the rotating speed multiplying power of the exciting force, n ₀ The working rotating speed of the nuclear turbine.

In other implementations, a second frequency resonance ratio Δ f of the moving blade avoiding the high frequency exciting force is determined according to a first order vibration frequency of the moving blade, the number of the stationary blades, and an operating speed of the nuclear turbine _h 。

First-order vibration frequency of moving blade of nuclear turbine avoids high-frequency excitation force frequency Z _n n ₀ Ratio of resonance Δ f _h Calculated according to the following formula:

wherein f is ₁ Of the first order of the rotor blade, Z _n Number of stationary blades, n ₀ The working rotating speed of the nuclear turbine.

In other implementations, a third frequency resonance ratio value delta f of the m-order diameter vibration frequency of the full-circle connected long blades avoiding the high-frequency exciting force is determined according to the m-order diameter vibration frequency of the full-circle connected long blades, the number of the static blades and the working rotating speed of the nuclear power turbine _m 。

M-order diameter vibration frequency of full circle connected long blade avoids high frequency exciting force frequency Z _n n ₀ Ratio of resonance Δ f _m Calculated according to the following formula:

wherein, f _dm The m-order diameter vibration frequency of the long blades is connected for a whole circle, m is the pitch diameter number of the whole circle of blade vibration, Z _n Is a static leafThe number of slices;

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.

And S403, optimally controlling the dynamic strength of the moving blade according to the dynamic strength safety ratio.

Responsive to a safe ratio R of dynamic strength _σv If the value is greater than the preset dynamic strength safety ratio threshold value, the dynamic strength of the moving blade is determined to be qualified in design monitoring, and the dynamic strength safety ratio R is responded _σv And the dynamic strength is less than or equal to a preset dynamic strength safety ratio threshold value, the dynamic strength design monitoring of the moving blade is determined to be unqualified, a dynamic strength optimization improvement strategy of the nuclear turbine is generated, and the design optimization control is carried out on the dynamic strength of the moving blade based on the dynamic strength optimization improvement strategy.

Optionally, in this embodiment of the present application, the preset safe ratio threshold of the dynamic intensity may be 1, that is, if R is, R is greater than or equal to the preset safe ratio threshold of the dynamic intensity _σv If R is greater than 1, the dynamic strength of the moving blade of the nuclear turbine is qualified by design and monitoring, which indicates that the dynamic strength of the moving blade of the nuclear turbine is in a controlled state _σv Less than or equal to 1, the dynamic strength design monitoring of the moving blade of the nuclear turbine is unqualified, and the blade profile width, the 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 redetected until R _σv If the reliability monitoring process is more than 1, the optimization is finished, or the next reliability monitoring process is executed.

S404, optimally controlling the moving blade to avoid the low-frequency excitation force frequency resonance according to the first frequency resonance ratio.

In response to the lower ratio R _d1 Greater than a first percentage threshold and an upper ratio R _u1 If the ratio is larger than the second percentage threshold value, the design and monitoring of the moving blade avoiding the low-frequency excitation force frequency resonance is determined to be qualified, and the lower limit ratio R is responded _d1 Less than or equal to the first percentile limit and/or the upper percentile value R _u1 The frequency of the moving blade avoiding the low-frequency excitation force is determined when the frequency is less than or equal to a second percentage threshold valueAnd (5) the monitoring of the resonance design is not qualified, and an optimized improvement strategy for avoiding the low-frequency excitation force frequency resonance of the moving blade is generated. Wherein the second percentage threshold is less than the first percentage threshold. Further, based on an optimization and improvement strategy, design optimization control is carried out on the moving blade to avoid low-frequency excitation force frequency resonance

Optionally, in this embodiment of the present application, the first percentage limit may be 5%, and the second percentage limit may be 3%, that is, if R is greater than or equal to the first percentage limit _d1 > 5% and R _u1 The 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 _d1 Less than or equal to 5 percent or R _u1 Less than or equal to 3 percent, the nuclear turbine moving blade avoids the low-frequency excitation force frequency resonance design and monitors unqualified, which indicates that the blade profile width, the thickness, the structure fillet, the connecting structure, the shroud thickness, the material mark and the like of the moving blade need to be optimized and improved in the design stage, thereby optimizing and controlling the nuclear turbine, and detecting the running state data of the moving blade again until R _d1 Greater than 5% and R _u1 If the reliability is higher than 3%, the optimization is finished, or the next reliability monitoring process is executed.

And S405, optimally controlling the moving blade to avoid the high-frequency excitation force frequency resonance according to the second frequency resonance ratio.

Resonance ratio value deltaf in response to second frequency _h Greater than or equal to the first percentage threshold value, determining that the moving blade is qualified for design and monitoring by avoiding the high-frequency excitation force frequency resonance, and responding to the second frequency resonance ratio delta f _h And if the frequency deviation is smaller than the first percentage limit value, determining that the design monitoring of the moving blade avoiding the high-frequency excitation force frequency resonance is not qualified, generating an optimization improvement strategy of the moving blade avoiding the high-frequency excitation force frequency resonance, and carrying out design optimization control on the moving blade avoiding the high-frequency excitation force frequency resonance based on the optimization improvement strategy.

That is, if Δ f _h Not 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 the moving blade is in the controlled state, the moving blade is in the controlled stateΔf _h Less than 5 percent, the nuclear turbine moving blade avoids the high-frequency excitation force frequency resonance design and is unqualified in monitoring, which shows that the blade profile width and thickness, the structure fillet, the connecting structure, the shroud thickness and the material mark of the moving blade need to be optimized and improved in the design stage, so that the nuclear turbine is optimized and controlled, and the operation state data of the moving blade is re-detected until delta f _h And ending the optimization for more than or equal to 5 percent, or executing the next reliability monitoring flow.

And S406, 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.

Responsive to a third frequency resonance ratio Δ f _m The frequency resonance design of the whole circle of connected long blades avoiding the high-frequency exciting force is determined to be qualified when the frequency resonance is larger than or equal to a first percentage threshold value, and the frequency resonance is responded to a third frequency resonance ratio delta f _m And if the frequency deviation is less than the first percentage limit value, determining that the design and monitoring of avoiding the high-frequency excitation force frequency resonance by the whole circle of the long blades are not qualified, and generating an optimization and improvement strategy of avoiding the high-frequency excitation force frequency resonance by the whole circle of the long blades.

That is, if Δ f _m Not 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 _m Less than 5 percent, the whole circle of the long blade connected with the hollow nuclear power turbine avoids the high-frequency excitation force frequency resonance design and monitoring to be unqualified, which shows 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, and the operation state data of the moving blade is detected again until delta f _m And finishing the optimization for more than or equal to 5 percent or executing the next reliability monitoring flow.

In the embodiment of the application, the dynamic strength 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 dynamic intensity and the reliability of vibration 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 reliable operation of the nuclear turbine is ensured.

FIG. 5 is a flow chart of a method for monitoring reliability of 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. 5, the method includes the following steps:

and S501, calculating the running state data of the moving blade of the nuclear turbine.

Based on a component model library server 1, a load database server 2 and a material database server 3 of a nuclear turbine, design parameters, a three-dimensional mechanical model, centrifugal force loads, exciting force loads and material mechanical property data of a moving blade of a 1200MW nuclear turbine are input, a method and a subprogram for designing and monitoring the dynamic strength and vibration of the moving blade under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force are calculated, and the running state data of the moving blade at one stage of the 1200MW nuclear turbine is obtained _v =18.83MPa, vibration resistance intensity sigma _a =253.99MPa, allowable safety factor of dynamic strength [ S ] _f ]=2.45, first order vibration frequency f ₁ =123Hz, and n is limited to the highest working rotating speed (1 + 0.01) ₀ Frequency of vibration of time f _d1 =128Hz, n being the lowest (1-0.03) at the operating speed ₀ Time-limited vibration frequency f _d2 =107Hz, m = 6-step diameter vibration frequency f of a full-circle connected long blade _dm =1186Hz and operating speed n of a nuclear turbine ₀ ＝1500r/min＝25Hz。

S502, 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 _σv According to the following formulaCalculating:

in the above formula, σ _a The vibration resistance strength of the moving blade is 253.99MPa, sigma _v The vibration stress of the rotor blade is 18.83MPa, [ S ] _f ]The safety factor of 2.45 is allowed for the dynamic strength of the moving blade.

S503, 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 _d1 And an upper ratio R _u1 Respectively according to the following formula:

in the above formula, f _d1 The vibration frequency of the rotor blade at the highest working rotation speed limit (1 + 0.01) n0 is 128Hz _d2 For the moving blade at the lowest working rotating speed (1-0.03) n ₀ The vibration frequency is 107Hz, K =5 is the rotating speed multiplying factor of the exciting force, n ₀ The working speed of the 1200MW nuclear power turbine is 1500r/min =25Hz.

S504, calculating a second frequency resonance ratio of the moving blade avoiding the high-frequency exciting 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 _h Calculated according to the following formula:

in the above formula, f ₁ Is the first order vibration frequency of the moving blade of 123Hz _n Number of stationary blades 60,n ₀ The working speed of the nuclear power turbine is 1500r/min =25Hz.

And S505, 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.

Third frequency resonance ratio delta f of m-order diameter vibration frequency of full-circle connected long blade avoiding high-frequency exciting force _m Calculated according to the following formula:

in the above formula, f _dm The vibration frequency of m = 6-step diameter 1186Hz, m =6 is the vibration pitch diameter number of the whole circle of the blade, and Z is _n The number of stationary blades is 60.

And S506, optimizing and controlling the dynamic strength of the moving blade.

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

(1) If R is _σv If the dynamic strength of the moving blade of the 1200MW nuclear power turbine is qualified for design and monitoring, the dynamic strength of the moving blade of the 1200MW nuclear power turbine is in a controlled state, the design and monitoring of the vibration strength of the moving blade are finished, and the step S407 is executed.

And S507, the moving blade avoids the optimization control of the low-frequency excitation force frequency resonance.

The method comprises the following steps of carrying out optimization design control on the moving blade of the 1200MW nuclear power turbine by avoiding low-frequency excitation force frequency resonance through an optimization improvement strategy of the moving blade by avoiding the low-frequency excitation force frequency resonance:

(1) If R is _d1 =3.60% > 5% and R _u1 The design and the monitoring of the moving blade of the 1200MW nuclear turbine with the model avoiding the low-frequency exciting force frequency resonance are qualified, and the condition that the moving blade of the 1200MW nuclear turbine avoids the low-frequency exciting force is shownThe frequency resonance is controlled, and the design monitoring of the moving blade avoiding the low-frequency excitation force frequency resonance is finished, and the process proceeds to step S508.

And S508, the moving blade avoids the optimization control of the frequency resonance of the high-frequency exciting force.

Through an optimization and improvement strategy of avoiding high-frequency excitation force frequency resonance by the moving blade, the moving blade of the 1200MW nuclear power turbine of the model avoids the high-frequency excitation force frequency resonance to carry out optimization design control:

(1) If Δ f _h And =91.80% 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 S509 is entered.

And S509, 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 _m And 5%, the design and monitoring that the whole circle of the long blade is connected to avoid the high-frequency excitation force frequency resonance is qualified, which indicates that the whole circle of the long blade is in a controlled state to avoid the high-frequency excitation force frequency resonance, and the design and monitoring that the whole circle of the long blade is connected to avoid the high-frequency excitation force frequency resonance is finished.

The embodiment of the application can accurately monitor the safety of the dynamic strength and the vibration 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. 6 is a flowchart of a method for monitoring reliability of a nuclear turbine according to an embodiment of the present disclosure, and on the basis of the above embodiment, with reference to fig. 6, a torsional vibration safety design monitoring process of a multiple rotor system suffering from a power grid electrical disturbance fault is explained, including the following steps:

s601, acquiring operation state data of the multi-rotor system subjected to the electric disturbance fault of the power grid.

Optionally, based on a component model library server, a load database server and a material database server of the nuclear turbine, design parameters, a three-dimensional mechanical model and material mechanical property data of a multi-rotor system of the nuclear turbine are input, and torsional vibration design monitoring method and subprogram for the multi-rotor system to bear power grid electrical disturbance faults are used for calculating motion state data of the multi-rotor system of the nuclear turbine. Wherein the operating condition data includes a torsional vibration frequency F closest to 45Hz ₁ Torsional vibration frequency F closest to the torsional vibration frequency of 55Hz ₂ And a torsional vibration frequency F closest to 93Hz ₃ A torsional vibration frequency F closest to 108Hz ₄ And the maximum shear stress sigma of the multi-rotor system of the nuclear turbine in the two-phase short circuit _τmax 。

And S602, determining torsional vibration reliability monitoring data according to the running state data of the multi-rotor system.

Optionally, according to the operating state data of the multi-rotor system, a first ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid, a second ratio of the torsional vibration frequency to avoid double working frequencies of the power grid, and a torsional vibration stress ratio of the multi-rotor system during two-phase short circuit are determined, and are used as torsional vibration reliability monitoring data of the multi-rotor system.

In some implementations, the torsional vibration frequency F closest to 45Hz is based on the multi-rotor system ₁ Torsional vibration frequency F closest to torsional vibration frequency of 55Hz ₂ Determining a first ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid, wherein the first ratio of the multi-rotor system comprises a lower limit ratio R of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid _L1 And an upper ratio R _H1 。

Lower limit ratio R of torsional vibration frequency of multi-rotor system of nuclear steam turbine for avoiding power grid working frequency _L1 And an upper ratio R _H1 Respectively according to the following formulas:

wherein, F ₁ A torsional vibration frequency F of approximately 45Hz ₂ The torsional vibration frequency which is closest to the torsional vibration frequency of 55 Hz.

In other implementations, the torsional vibration frequency F closest to 93Hz is based on a multi-rotor system ₃ Torsional vibration frequency F closest to 108Hz ₄ . Determining a second ratio of the double working frequencies of the multi-rotor system when the torsional vibration frequency of the multi-rotor system avoids the power grid, wherein the second ratio of the multi-rotor system comprises a lower limit ratio R of the double working frequencies of the multi-rotor system when the torsional vibration frequency of the multi-rotor system avoids the power grid _L2 And an upper limit ratio R _H2 。

Lower limit ratio R of torsional vibration frequency of multi-rotor system of nuclear steam turbine avoiding double working frequency of power grid _L2 And an upper ratio R _H2 Respectively according to the following formula:

wherein, F ₃ Is the torsional vibration frequency F closest to 93Hz ₄ The torsional vibration frequency closest to 108 Hz.

In other implementations, the maximum shear stress σ of the multi-rotor system is determined based on a two-phase short circuit of the grid _τmax And yield limit of the material at the operating temperature

Determining torsional vibration stress ratio R of multi-rotor system during two-phase short circuit _στ 。

Torsional vibration stress ratio R of nuclear turbine multi-rotor system when two-phase short circuit occurs in electric power system _στ Calculated according to the following formula:

wherein σ _τmax The maximum shearing stress of the multi-rotor system when two phases of the power grid are short-circuited,

is the yield limit of the material at the operating temperature.

And S603, performing design optimization control on the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid according to the first ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid.

In response to a lower ratio R _L1 Less than the set value and the upper limit ratio R _H1 If the frequency is larger than the set value, the design monitoring that the torsional vibration frequency of the multi-rotor system avoids the working frequency of the power grid is determined to be qualified, and the design monitoring is responded to R _L1 Greater than or equal to the set value and/or the upper ratio R _H1 And when the frequency is less than or equal to the set value, determining that the design monitoring of the multi-rotor system torsional vibration frequency avoiding power grid working frequency is not qualified, generating an optimization improvement strategy of the multi-rotor system torsional vibration frequency avoiding power grid working frequency, and performing design optimization control on the multi-rotor system torsional vibration frequency avoiding power grid working frequency based on the optimization improvement strategy.

Alternatively, the set value is 1, in response to R _L1 < 1 and R _H1 And if the frequency is higher than 1, the design monitoring of avoiding the working frequency of the power grid by the torsional vibration frequency of the multi-rotor system of the nuclear turbine is qualified, which indicates that the frequency avoiding the working frequency of the power grid by the torsional vibration frequency of the multi-rotor system is in a controlled state, and the design monitoring of avoiding the working frequency of the power grid by the torsional vibration frequency of the multi-rotor system is finished.

In response to R _L1 Not less than 1 and/or R _H1 Less than or equal to 1, the torsional vibration frequency of the nuclear steam turbine multi-rotor system avoids the design monitoring of the working frequency of the power grid, and is unqualified, which indicates that the structure of the rotor or the coupling needs to be optimized and improved in the design stage, and the yield is changed into the yieldThe material with better strength or the structural geometric dimension of the multi-rotor system is optimized, so that the nuclear turbine is optimally controlled, and the running state data of the multi-rotor system bearing the power grid electrical disturbance fault is re-detected until R _L1 < 1 and R _H1 And > 1, ending optimization or executing the next safety monitoring flow.

S604, according to a second ratio of the torsional vibration frequency of the multi-rotor system to avoid the doubled working frequency of the power grid, design optimization control is carried out on the torsional vibration frequency of the multi-rotor system to avoid the doubled working frequency of the power grid.

In response to the lower ratio R _L2 Less than the set value and the upper limit ratio R _H2 If the frequency is larger than the set value, the design monitoring that the torsional vibration frequency of the multi-rotor system avoids the working frequency of the power grid is determined to be qualified, and the design monitoring is responded to R _L2 Greater than or equal to the set value and/or the upper ratio R _H2 And when the frequency is smaller than or equal to the set value, determining that the design monitoring of the multi-rotor system torsional vibration frequency avoiding the power grid working frequency is unqualified, generating an optimization improvement strategy of the multi-rotor system torsional vibration frequency avoiding the power grid double working frequency, and performing design optimization control on the multi-rotor system torsional vibration frequency avoiding the power grid double working frequency based on the optimization improvement strategy.

In response to R _L2 < 1 and R _H2 The design monitoring that the torsional vibration frequency of the multi-rotor system of the nuclear turbine avoids the double working frequency of the power grid is qualified, the fact that the torsional vibration frequency of the multi-rotor system avoids the double working frequency of the power grid is indicated to be in a controlled state, the design monitoring that the torsional vibration frequency of the multi-rotor system avoids the double working frequency of the power grid is finished, and the monitoring can be finished or the next monitoring process can be started.

In response to R _L2 Not less than 1 or R _H2 Less than or equal to 1, the torsional vibration frequency of the multi-rotor system of the nuclear turbine avoids the design monitoring of the double working frequency of the power grid, the design monitoring is unqualified, the structure of a rotor or a coupler needs to be optimized and improved in the design stage, a material with better yield strength is used instead, or the structural geometric dimension of the multi-rotor system is optimized, so that the nuclear turbine is optimized and controlled, the running state data of the multi-rotor system bearing the electric disturbance fault of the power grid is detected again until R _L2 < 1 and R _H2 If the safety monitoring process is finished, the optimization is finished, or the next safety monitoring process is executed.

And S605, optimally controlling the torsional vibration stress of the multi-rotor system when the two-phase short circuit occurs according to the torsional vibration stress ratio of the multi-rotor system when the two-phase short circuit occurs.

In response to torsional stress ratio R _στ Less than the set value, determining that the torsional stress design of the multi-rotor system is qualified, responding to the torsional stress ratio R _στ And if the design monitoring result is less than the set value, determining that the design monitoring of the torsional vibration stress of the multi-rotor system is not qualified, generating an optimization improvement strategy of the torsional vibration stress of the multi-rotor system, and performing design optimization control on the torsional vibration stress of the multi-rotor system based on the optimization improvement strategy.

In response to R _στ And (3) less than 1, the torsional vibration stress of the multi-rotor system of the nuclear turbine is qualified in design monitoring when the two-phase short circuit occurs, the torsional vibration stress of the multi-rotor system is in a controlled state, the design monitoring of the torsional vibration stress of the multi-rotor system is finished, or the next monitoring flow is entered.

In response to R _στ Not less than 1, the torsional vibration stress of the multi-rotor system of the nuclear turbine is unqualified in design monitoring when two-phase short circuit occurs, the structure of a rotor or a coupling needs to be optimized and improved in the design stage, a material with better yield strength is used instead, or the structural geometric size of the multi-rotor system is optimized, so that the nuclear turbine is optimized and controlled, the operation state data of the multi-rotor system bearing the power grid electrical disturbance fault is re-detected until R _στ < 1, either the optimization is ended or the next safety monitoring procedure is executed.

In the embodiment of the application, the nuclear turbine is optimally controlled according to a first ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid, a second ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid twice and a torsional vibration stress ratio of the multi-rotor system during two-phase short circuit. The embodiment of the application can accurately monitor the torsional vibration safety design condition of the multi-rotor system of the nuclear turbine, which bears the electrical disturbance fault of a power grid, so that the nuclear turbine can be optimally controlled, the service life of the nuclear turbine is prolonged, and the long-period safe operation of the nuclear turbine is ensured.

FIG. 7 is a flowchart of a torsional vibration safety monitoring method for a multiple rotor system of a specific type of nuclear turbine subject to a grid electrical disturbance fault according to an embodiment of the present application, as shown in FIG. 7, the method includes the following steps:

and S701, calculating the running state data of the multi-rotor system subjected to the electric disturbance fault of the power grid.

Inputting design parameters, three-dimensional mechanical models and material mechanical property data of a multi-rotor system of the 1200MW nuclear turbine based on a component model library server 1, a load database server 2 and a material database server 3 of the nuclear turbine, and calculating the running state data of the multi-rotor system of the 1200MW nuclear turbine bearing the electric disturbance fault of the power grid by using a torsional vibration design monitoring method and a subprogram of the multi-rotor system bearing the electric disturbance fault of the power grid, wherein the running state data comprises a torsional vibration frequency F closest to 45Hz ₁ Torsional vibration frequency F of =15.58Hz, nearest 55Hz ₂ Torsional vibration frequency F of =15.58Hz, closest to 93Hz ₃ Torsional vibration frequency F of =90.51Hz and closest to 108Hz ₄ =172.14Hz and maximum shear stress sigma of multi-rotor system of nuclear turbine in two-phase short circuit _τmax ＝275.83MPa。

S702, calculating a first ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid.

The model 1200MW nuclear steam turbine multi-rotor system torsional vibration frequency avoids first ratio of power grid working frequency, wherein the first ratio comprises a lower limit ratio R of the rotor system torsional vibration frequency avoiding the power grid working frequency _L1 And an upper ratio R _H1 Respectively according to the following formula:

in the above formula, F ₁ The torsional vibration frequency of 15.58Hz, F is closest to 45Hz ₂ The torsional vibration frequency, which is the torsional vibration frequency closest to 55Hz, is 87.61Hz.

Determining the lower limit ratio R of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid _L1 And an upper ratio R _H1 Thereafter, step S605 may be executed, i.e. according to the lower limit ratio R _L1 And an upper ratio R _H1 And carrying out design optimization control on the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid.

And S703, calculating a second ratio of the torsional vibration frequency of the multi-rotor system to avoid the doubled working frequency of the power grid.

The torsional vibration frequency of the multi-rotor system of the 1200MW nuclear steam turbine avoids a second ratio of twice the working frequency of the power grid, wherein the second ratio comprises a lower limit ratio R of twice the working frequency of the multi-rotor system torsional vibration frequency avoiding the power grid _L2 And an upper ratio R _H2 Respectively according to the following formula:

in the above formula, F ₃ The torsional vibration frequency is 90.51Hz, F which is closest to 93Hz ₄ The torsional vibration frequency of 172.14Hz which is closest to 108 Hz;

determining the lower limit ratio R of the double working frequency of the multi-rotor system avoiding the power grid by the torsional vibration frequency _L2 And an upper ratio R _H2 Thereafter, step S606 can be performed, i.e. according to the lower ratio R _L2 And an upper ratio R _H2 And optimally controlling the design of the torsional vibration frequency of the multi-rotor system to avoid twice the working frequency of the power grid.

S704, calculating the torsional vibration stress ratio of the multi-rotor system when the two phases are short-circuited.

Electric power systemTorsional vibration stress ratio R of multi-rotor system of nuclear turbine in two-phase short circuit _στ Calculated according to the following formula:

in the above formula, σ _τmax The maximum shear stress of the multi-rotor system is 275.83MPa when two phases of the power grid are short-circuited,

is the yield limit of the material at the working temperature of 630MPa;

after the ratio of the torsional vibration stress of the multi-rotor system during the two-phase short circuit is determined, step S607 may be executed, that is, the torsional vibration stress of the multi-rotor system during the two-phase short circuit is optimally designed and controlled according to the ratio of the torsional vibration stress of the multi-rotor system during the two-phase short circuit.

And S705, optimally controlling the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid.

For the torsional vibration frequency of the multi-rotor system of the 1200MW nuclear power turbine, the optimal design control is carried out by avoiding the working frequency of a power grid:

in response to R _L1 =0.35 < 1 and R _H1 And if the torsional vibration frequency of the multi-rotor system of the 1200MW nuclear power turbine is qualified for design monitoring of avoiding the working frequency of the power grid, the condition that the torsional vibration frequency of the multi-rotor system is in a controlled state avoiding the working frequency of the power grid is indicated, and the design monitoring of avoiding the working frequency of the power grid by the torsional vibration frequency of the multi-rotor system is finished or a next safety monitoring process is started.

And S706, optimally controlling the torsional vibration frequency of the multi-rotor system to avoid the doubled working frequency of the power grid.

The torsional vibration frequency of the multi-rotor system of the 1200MW nuclear power turbine avoids twice the working frequency of a power grid to carry out optimization design control:

in response to R _L2 =0.97 < 1 and R _H2 The torsional vibration frequency of the multi-rotor system of the 1200MW nuclear power turbine is qualified by design monitoring for avoiding twice working frequency of a power grid when the number is =1.59 > 1, which shows thatThe multi-rotor system torsional vibration frequency avoids the twice working frequency of the power grid and is in a controlled state, the design monitoring of the multi-rotor system torsional vibration frequency avoids the twice working frequency of the power grid is finished, or the next safety monitoring process is started.

And S707, carrying out design optimization control on the torsional vibration stress of the multi-rotor system when two-phase short circuit occurs.

Optimally designing and controlling the torsional vibration stress of the multi-rotor system of the 1200MW nuclear turbine when two-phase short circuit occurs:

in response to R _στ And if the torsional vibration stress of the multi-rotor system of the 1200MW nuclear power turbine is qualified in design and monitoring when the two-phase short circuit occurs, the torsional vibration stress of the multi-rotor system is in a controlled state, the design and monitoring of the torsional vibration stress of the multi-rotor system are finished, or the next safety monitoring process is started.

Fig. 8 is a flowchart of a method for monitoring reliability of a nuclear turbine according to an embodiment of the present disclosure, and with reference to fig. 8, a process for monitoring a shafting vibration safety design in which a rotor and a bearing system are subjected to forced vibration and self-excited vibration is explained, including the following steps:

s801, acquiring running state data of a rotor and a bearing system under the action of forced vibration and self-excited vibration;

s802, determining the vibration reliability monitoring data of the first shaft system of the rotor and bearing system under the action of forced vibration and self-excited vibration according to the operation state data of the rotor and bearing system.

Optionally, according to the operating state data of the rotor and the bearing system, a critical rotating speed ratio of the rotor and the bearing system, a destabilizing rotating speed ratio of the rotor and the bearing system, a logarithmic decrement ratio of the rotor and the bearing system, a first unbalanced response ratio of the rotor and the bearing system at the operating rotating speed, and a second unbalanced response ratio of the rotor and the bearing system at the critical rotating speed are determined, and the critical rotating speed ratio, the destabilizing rotating speed ratio, the logarithmic decrement ratio, the first unbalanced response ratio and the second unbalanced response ratio are determined as the first shaft system vibration reliability monitoring data.

In some implementations, the operating speed n is based on a nuclear turbine ₀ Critical speed n of the rotor and bearing system of a nuclear turbine closest to the operating speed _c Determining the critical speed ratio R of the rotor and the bearing system of the nuclear turbine _nc 。

Critical speed ratio R of nuclear turbine rotor to bearing system _nc Calculated according to the following formula:

wherein n is ₀ For the operating speed, n, of a nuclear turbine _c The critical rotating speed of the nuclear turbine rotor and the bearing system which is closest to the working rotating speed is obtained.

In other implementations, the minimum destabilized speed n is based on the rotor and bearing system _st And the operating speed n of the nuclear turbine ₀ Determining the ratio R of the unstable rotation speed of the rotor and the bearing system _nst 。

Unstable rotating speed ratio R of rotor and bearing system of nuclear turbine considering different bearing loads _nst Calculated according to the following formula:

wherein n is _st Is the minimum unstable speed of the rotor and bearing system.

In other implementations, the rotor-to-bearing system logarithmic decay rate ratio is determined based on the minimum logarithmic decay rate δ of the rotor-to-bearing system.

Logarithmic decrement ratio R of rotor and bearing system of nuclear turbine considering different bearing loads _δ Calculated according to the following formula:

wherein, delta is the minimum logarithmic decrement of the rotor and the bearing system of the nuclear turbine;

in other implementations, the journal maximum imbalance response A is based on the operating speed of the rotor and bearing system _p-p0 Determining the imbalance response ratio R of the rotor and bearing system at the operating speed _p-p0 。

Maximum unbalance response ratio R of shaft neck of nuclear turbine rotor and bearing system at working rotating speed _p-p0 Calculated according to the following formula:

wherein, A _p-p0 The maximum journal imbalance response at operating speed.

In other implementations, the response A is based on the maximum journal imbalance at the critical rotational speed for the rotor and bearing system _p-pc Determining the imbalance response ratio R of the rotor to the bearing system at the critical speed _p-pc 。

Maximum unbalance response ratio R of shaft neck of nuclear turbine rotor and bearing system at critical rotating speed _p-pc Calculated according to the following formula:

wherein A is _p-pc The maximum imbalance response of the journal at the critical rotational speed.

And S803, optimally designing and controlling the critical rotating speed of the rotor and the bearing system to avoid the working rotating speed according to the critical rotating speed ratio of the rotor and the bearing system.

In response to the critical speed ratio R _nc The critical rotating speed of the nuclear turbine rotor and the bearing system is qualified when the critical rotating speed is larger than a preset critical rotating speed ratio threshold value, and the critical rotating speed of the nuclear turbine rotor and the bearing system is qualified in design and monitoring and responds to a critical rotating speed ratio R _nc The critical rotating speed is less than or equal to a preset critical rotating speed ratio threshold value, the critical rotating speed design monitoring of the nuclear turbine rotor and the bearing system is not qualified, and the design monitoring needs to be carried outAnd generating an optimization and improvement strategy for avoiding the working speed of the critical rotating speed of the rotor and bearing system, and performing optimization design control on the avoiding of the working speed of the critical rotating speed of the rotor and bearing system according to the optimization and improvement strategy.

Optionally, the preset threshold value of the critical rotation speed ratio is 10%, if R _nc And if the critical rotating speed of the rotor and the bearing system of the nuclear turbine is higher than 10%, the critical rotating speed design monitoring is qualified, the critical rotating speed of the rotor and the bearing system is in a controlled state, the critical rotating speed design monitoring of the rotor and the bearing system is finished, or the next safety monitoring process is started.

If R is _nc Less than or equal to 10 percent, the critical rotating speed of the rotor and the bearing system of the nuclear power turbine is designed and monitored unqualifiedly, the bearing form or the rotor structure needs to be optimized and improved at the design stage, the bearing with better stability is used instead, or the geometric dimension of the rotor structure is optimized, so that the design optimization is carried out on the nuclear power turbine, the running state data of the forced vibration and the self-excited vibration action borne by the rotor and the bearing system is re-detected until R _nc And ending the optimization when the rate is less than or equal to 10 percent, or executing the next safety monitoring process.

And S804, optimally designing and controlling the stability of the rotor and the bearing system according to the instability rotating speed ratio of the rotor and the bearing system.

Responsive to a destabilized speed ratio R _nst The stability of the nuclear turbine rotor and the bearing system is qualified by design and monitoring when the value is larger than a preset instability rotating speed ratio threshold value and responds to a critical rotating speed ratio R _nst And if the value is less than or equal to the instability rotating speed ratio threshold, the stability design monitoring of the rotor and the bearing system of the nuclear turbine is not qualified, an optimization improvement strategy of the instability rotating speed of the rotor and the bearing system needs to be generated, and the optimization design control is carried out on the instability rotating speed of the rotor and the bearing system according to the optimization improvement strategy.

Optionally, the predetermined threshold for the destabilized speed ratio is 1.25 if R _nst If the stability of the rotor and the bearing system is higher than 1.25, the stability design monitoring of the rotor and the bearing system is qualified, the stability of the rotor and the bearing system is in a controlled state, the stability design monitoring of the rotor and the bearing system is finished, or the process enters the processAnd the next safety monitoring process.

If R is _ns Less than or equal to 1.25, the stability design monitoring of the rotor and the bearing system is not qualified, the bearing form or the rotor structure needs to be optimized and improved in the design stage, a bearing with better stability is used instead, or the geometric dimension of the rotor structure is optimized, so that the design optimization is carried out on the nuclear power steam turbine, and the running state data of the forced vibration and the self-excited vibration of the rotor and the bearing system are re-detected until R _nst If the safety monitoring process is more than 1.25, the optimization is finished or the next safety monitoring process is executed.

And S805, optimally designing and controlling the logarithmic attenuation rate of the rotor and the bearing system according to the logarithmic attenuation rate ratio of the rotor and the bearing system.

In response to the logarithmic decay rate ratio R _δ The logarithmic attenuation rate of the rotor and the bearing system is qualified by design monitoring when the logarithmic attenuation rate ratio is larger than a preset logarithmic attenuation rate ratio threshold value and responds to the logarithmic attenuation rate ratio R _δ And if the logarithmic attenuation rate is smaller than or equal to the logarithmic attenuation rate ratio threshold value, the design and monitoring of the logarithmic attenuation rates of the rotor and the bearing system are not qualified, an optimization and improvement strategy of the logarithmic attenuation rates of the rotor and the bearing system needs to be generated, and the optimization, design and control of the logarithmic attenuation rates of the rotor and the bearing system are carried out according to the optimization and improvement strategy.

Optionally, the predetermined logarithmic decrement ratio threshold is 1 if R _δ And if the logarithmic attenuation rate of the rotor and the bearing system is qualified, the logarithmic attenuation rate of the rotor and the bearing system is in a controlled state, the design monitoring of the logarithmic attenuation rate of the rotor and the bearing system is finished, or the next safety monitoring flow is entered.

If R is _δ Less than or equal to 1, the logarithmic decrement design and monitoring of the rotor and the bearing system are unqualified, the bearing form or the rotor structure needs to be optimized and improved at the design stage, a bearing with better stability is used instead, or the geometric dimension of the rotor structure is optimized, so that the design optimization of the nuclear power steam turbine is carried out, and the running state data of the rotor and the bearing system under the action of forced vibration and self-excited vibration is detected again until R _δ If the optimization is finished, or the next safety monitoring flow is executed。

And S806, performing optimal design control on the unbalance response of the rotor and the bearing system at the working rotating speed according to the first unbalance response ratio of the rotor and the bearing system at the working rotating speed.

In response to the first imbalance response ratio R _p-p0 Less than the set value, the rotor and bearing system is qualified in unbalance response design monitoring at the working rotating speed and responds to the first unbalance response ratio R _p-p0 And if the unbalance response of the rotor and the bearing system is greater than or equal to the set value, the unbalance response design monitoring of the rotor and the bearing system is not qualified at the working rotating speed, an optimization improvement strategy of the unbalance response of the rotor and the bearing system at the working rotating speed needs to be generated, and the optimization design control is carried out on the unbalance response of the rotor and the bearing system at the working rotating speed according to the optimization improvement strategy.

Alternatively, the value is set to 1 if R _p-p0 If the number of the rotor and the bearing system is less than 1, the design monitoring of the unbalance response at the working rotating speed of the rotor and the bearing system is qualified, the unbalance response at the working rotating speed of the rotor and the bearing system is in a controlled state, the design monitoring of the unbalance response at the working rotating speed of the rotor and the bearing system is finished, or the next safety monitoring process is started.

If R is _p-p0 Not less than 1, the unbalance response design monitoring is not qualified under the working rotating speed of the rotor and bearing system, the bearing form or the rotor structure needs to be optimized and improved in the design stage, a bearing with better stability is used instead, or the geometric dimension of the rotor structure is optimized, so that the nuclear power steam turbine is designed and optimized, and the running state data of the rotor and the bearing system under the action of forced vibration and self-excited vibration is re-detected until R is reached _p-p0 < 1, ending the optimization, or executing the next safety monitoring process.

And S807, optimally designing and controlling the unbalance response of the rotor and the bearing system at the critical rotating speed according to the second unbalance response ratio of the rotor and the bearing system at the critical rotating speed.

In response to the second imbalance response ratio R _p-pc Less than the set value, the rotor and bearing system are designed and monitored to be qualified in response to the unbalance response at the critical rotating speed and respond to the second failureEquilibrium response ratio R _p-pc And if the unbalance response of the rotor and the bearing system at the critical rotating speed is larger than or equal to the set value, the unbalance response design monitoring of the rotor and the bearing system at the critical rotating speed is not qualified, an optimization improvement strategy of the unbalance response of the rotor and the bearing system at the critical rotating speed needs to be generated, and the optimization design control is carried out on the unbalance response of the rotor and the bearing system at the critical rotating speed according to the optimization improvement strategy.

Alternatively, the value is set to 1 if R _p-pc And (3) being less than 1, the design monitoring of the unbalance response at the critical rotating speed of the rotor and the bearing system is qualified, the unbalance response at the critical rotating speed of the rotor and the bearing system is in a controlled state, and the design monitoring of the unbalance response at the critical rotating speed of the rotor and the bearing system is finished or the next safety monitoring process is started.

If R is _p-pc Not less than 1, the unbalance response design monitoring is not qualified under the critical rotating speed of the rotor and the bearing system, the bearing form or the rotor structure needs to be optimized and improved in the design stage, a bearing with better stability is used instead, or the geometric dimension of the rotor structure is optimized, so that the design optimization of the nuclear power turbine is carried out, and the running state data of the rotor and the bearing system under the action of forced vibration and self-excited vibration is detected again until R is reached _p-pc < 1, ending the optimization, or executing the next safety monitoring process.

In the embodiment of the application, the nuclear power turbine is optimally controlled according to the critical rotating speed ratio of the rotor to the bearing system, the instability rotating speed ratio of the rotor to the bearing system, the logarithmic decrement ratio of the rotor to the bearing system, the first unbalance response ratio of the rotor to the bearing system at the working rotating speed and the second unbalance response ratio of the rotor to the bearing system at the critical rotating speed. The safe design condition of the shaft system vibration of the rotor and the bearing system of the nuclear power steam turbine under the action of forced vibration and self-excited vibration can be accurately monitored, so that the nuclear power steam turbine can be optimally controlled, the service life of the nuclear power steam turbine is prolonged, and the long-period safe operation of the nuclear power steam turbine is guaranteed.

Fig. 9 is a flowchart of a shafting vibration safety monitoring method for a rotor and bearing system of a nuclear turbine of a specific type subject to forced vibration and self-excited vibration according to an embodiment of the present application, and as shown in fig. 9, the method includes the following steps:

and S901, calculating the running state data of the rotor and bearing system under the action of forced vibration and self-excited vibration.

Based on a component model library server 1, a load database server 2 and a material database server 3 of a nuclear turbine, design parameters and a three-dimensional mechanical model of a 1200MW nuclear turbine rotor and bearing system, a rigidity coefficient and a damping coefficient of a bearing oil film and material mechanical property data are input, and operating state data of the rotor and the bearing system under the action of forced vibration and self-excited vibration is calculated by using a method for monitoring shafting vibration design of the rotor and the bearing system, wherein the operating state data comprises critical rotating speed n closest to the working rotating speed _c =1248r/min, minimum instability speed n of 1200MW nuclear power turbine rotor and bearing system considering different bearing loads _st =2090r/min, minimum axial logarithmic decrement δ =0.122, maximum journal imbalance response A at operating speed _p-p0 =42.7 μm, maximum journal imbalance response A at critical rotational speed _p-pc ＝172μm。

And S902, calculating the ratio of the critical rotating speed of the rotor to the critical rotating speed of the bearing system.

The critical rotation speed ratio R of the rotor and the bearing system of the 1200MW nuclear steam turbine _nc Calculated according to the following formula:

in the above formula, n ₀ The working speed n of the 1200MW nuclear power turbine ₀ ＝1500r/min，n _c The critical rotating speed 1248r/min of the model 1200MW nuclear steam turbine rotor and bearing system closest to the working rotating speed.

And S903, calculating the instability rotating speed ratio of the rotor and the bearing system.

Rotor and bearing of 1200MW nuclear power steam turbine with different bearing loads consideredDestabilizing speed ratio R of system _nst Calculated according to the following formula:

in the above formula, n _st The minimum instability rotating speed of the rotor and the bearing system is 2090r/min;

and S904, calculating the logarithmic decrement ratio of the rotor and the bearing system.

Logarithmic decrement ratio R of rotor and bearing system of 1200MW nuclear power turbine considering different bearing loads _δ Calculated according to the following formula:

in the above formula, δ is the minimum logarithmic decrement of 0.122 of the rotor and bearing system of the 1200MW nuclear steam turbine;

s905, calculating the unbalance response ratio of the rotor and the bearing system at the working rotating speed.

The maximum unbalance response ratio R of the shaft neck of the 1200MW nuclear power turbine rotor and bearing system at the working rotating speed _p-p0 Calculated according to the following formula:

in the above formula, A _p-p0 The maximum journal imbalance response is 42.7 μm at operating speed.

And S906, calculating the unbalance response ratio of the rotor and the bearing system at the critical rotating speed.

The maximum unbalance response ratio R of the shaft neck of the 1200MW nuclear power turbine rotor and bearing system at the critical rotating speed _p-pc Calculated according to the following formula:

in the above formula, A _p-pc A journal maximum imbalance response of 172 μm at the critical rotational speed;

and S907, optimally controlling the critical rotating speed of the rotor and bearing system to avoid the working rotating speed.

The critical rotating speed of the rotor and the bearing system of the 1200MW nuclear power turbine is optimally designed and controlled by avoiding the working rotating speed:

(1) Due to R _nc =16.8% > 10%, the critical rotational speed design monitoring of the rotor and bearing system of the 1200MW nuclear turbine is qualified, which indicates that the critical rotational speed of the rotor and bearing system is in a controlled state, and the critical rotational speed design monitoring of the rotor and bearing system is finished, and then the process goes to step 1108;

and S908, optimally controlling the instability rotating speed of the rotor and the bearing system.

The stability of the rotor and the bearing system of the 1200MW nuclear power turbine is optimally designed and controlled:

(1) In view of R _nst And (5) the stability of the rotor and the bearing system of the 1200MW nuclear turbine is qualified in design and monitoring, which indicates that the stability of the rotor and the bearing system is in a controlled state, and the design and monitoring of the stability of the rotor and the bearing system are finished or the next safety monitoring process is started.

And S909, carrying out optimized control on the logarithmic decrement of the rotor and bearing system.

The logarithmic decrement of the rotor and the bearing system of the 1200MW nuclear power turbine is optimally designed and controlled:

(1) Due to R _δ And if the logarithmic attenuation rate of the rotor and the bearing system of the 1200MW nuclear steam turbine is qualified in design and monitoring, the logarithmic attenuation rate of the rotor and the bearing system is in a controlled state, the design and monitoring of the logarithmic attenuation rate of the rotor and the bearing system are finished, or the next safety monitoring process is started.

S910, optimizing and controlling the unbalance response of the rotor and the bearing system at the working rotating speed:

the unbalanced response of the rotor and the bearing system of the 1200MW nuclear power turbine is optimized, designed and controlled at the working rotating speed:

(1)R _p-p0 and if the unbalance response of the rotor and the bearing system of the 1200MW nuclear turbine is qualified in design monitoring under the working rotating speed, the unbalance response of the rotor and the bearing system is in a controlled state under the working rotating speed, the design monitoring of the unbalance response of the rotor and the bearing system under the working rotating speed is finished, or the next monitoring process is entered.

S911, the rotor and the bearing system are subjected to the optimized control of the unbalance response at the critical rotating speed:

the unbalanced response of the rotor and the bearing system of the 1200MW nuclear power turbine is optimized, designed and controlled at the critical rotating speed:

(1) In view of R _p-pc And if the unbalance response of the rotor and the bearing system of the 1200MW nuclear turbine is qualified in design monitoring under the critical rotating speed, the unbalance response of the rotor and the bearing system is in a controlled state under the critical rotating speed, the design monitoring of the unbalance response of the rotor and the bearing system under the critical rotating speed is finished, or the next safety monitoring process is entered.

Fig. 10 is a flowchart of a method for monitoring reliability of a nuclear turbine according to an embodiment of the present disclosure, and with reference to fig. 10, a process for monitoring safe operation of shaft system vibration when a rotor and a bearing system are subjected to forced vibration and self-excited vibration is explained, which includes the following steps:

s1001, acquiring shafting vibration online monitoring data of a rotor and bearing system under the action of forced vibration and self-excited vibration.

A method and a subprogram for monitoring the vibration operation of a shaft system based on a component model library server, a load database server and a material database server of a nuclear turbine and the action of forced vibration and self-excited vibration borne by a rotor and bearing system are input into a shaft neck of a nuclear turbine rotor to monitor the peak value D of the relative displacement peak of shaft vibration on line _p-pr (mum) and bearing on-line monitoring tile vibration displacement peak value D _p-pb And (mum) monitoring the reliability of the running vibration.

S1002, determining second shaft system vibration reliability monitoring data according to the shaft system vibration on-line monitoring data.

And determining the ratio of the shaft vibration relative displacement of the rotor journal and the ratio of the bearing vibration displacement of the bearing on-line monitoring according to the on-line monitoring data of the vibration of the shafting, and determining the ratio of the shaft vibration relative displacement and the ratio of the bearing vibration displacement as the monitoring data of the vibration reliability of the second shafting.

In some implementations, the shaft vibration relative displacement ratio R is monitored online by a nuclear steam turbine rotor journal _p-pr And, calculating according to the following formula:

wherein D is _p-pr Monitoring the peak value (mum) of the shaft vibration relative displacement peak on line for the shaft neck of the nuclear power steam turbine rotor;

on-line monitoring tile vibration displacement ratio R of nuclear turbine bearing _p-pb Calculated according to the following formula:

wherein D is _p-pb And monitoring the peak value (mum) of the vibration displacement peak of the tile on line for the bearing.

And S1003, performing operation optimization control on the rotor shaft neck by monitoring the shaft vibration relative displacement on line according to the ratio of the shaft vibration relative displacement.

Ratio R in response to relative displacement of shaft vibration _p-pr When the value is smaller than a preset shaft vibration relative displacement ratio threshold value, determining that the operation monitoring of the rotor shaft neck on-line monitoring shaft vibration relative displacement is qualified; ratio R in response to relative displacement of shaft vibration _p-pr And if the value is larger than or equal to the preset shaft vibration relative displacement ratio threshold value, determining that the operation monitoring of the shaft vibration relative displacement of the rotor shaft neck on-line monitoring is not qualified, generating an optimization improvement strategy of the shaft vibration relative displacement, and performing operation optimization control on the shaft vibration relative displacement of the rotor shaft neck on-line monitoring by the optimization improvement strategy of the shaft vibration relative displacement.

Optionally preset shaft vibrationThe relative displacement ratio threshold may be 1, i.e. if R is _p-pr If R is less than 1, the operation monitoring of the shaft vibration relative displacement of the shaft neck of the nuclear power turbine rotor on line monitoring is qualified, which shows that the shaft vibration relative displacement of the nuclear power turbine rotor shaft neck on line monitoring is in a controlled state, if R is not qualified _p-pr And (2) not less than 1, the shaft vibration relative displacement operation monitoring of the shaft neck of the nuclear power steam turbine rotor is unqualified, the condition that the steam turbine rotor and the bearing need to be overhauled in the use stage is indicated, the cause of overlarge vibration of the rotor and the bearing is searched and improved, the operation of the nuclear power steam turbine is optimally controlled, and the optimization is finished until the ratio of the shaft vibration relative displacement is smaller than a preset shaft vibration relative displacement ratio threshold value, or the next safety monitoring flow is started.

And S1004, performing operation optimization control on the bearing on-line monitoring tile vibration displacement according to the ratio of the tile vibration displacement.

Ratio R in response to buffeting displacement _p-pb When the bearing vibration displacement ratio is smaller than a preset bearing vibration displacement ratio threshold value, the bearing vibration displacement operation monitoring is determined to be qualified; ratio R in response to buffeting displacement _p-pb And if the bearing vibration displacement ratio is larger than or equal to the preset bearing vibration displacement ratio threshold value, determining that the bearing vibration displacement on-line monitoring operation monitoring is not qualified, generating an optimization improvement strategy for the bearing vibration displacement on-line monitoring, and performing operation optimization control on the bearing vibration displacement on-line monitoring of the rotor journal by the optimization improvement strategy for the bearing vibration displacement.

Optionally, the predetermined watt-to-vibration displacement ratio threshold is set to 1, i.e., if R _p-pb Less than 1, the operation monitoring of the on-line monitoring tile vibration displacement of the nuclear turbine bearing is qualified, which indicates that the on-line monitoring tile vibration displacement of the nuclear turbine bearing is in a controlled state, if R is _p-pb Not less than 1, the on-line monitoring of the bearing vibration displacement operation of the nuclear turbine bearing is unqualified, which indicates that the turbine rotor and the bearing need to be overhauled in the use stage, the reason for the overlarge vibration of the rotor and the bearing is searched and improved, so that the operation of the nuclear turbine is optimally controlled until R _p-pb And (5) ending the optimization or entering the next safety monitoring flow.

In the embodiment of the application, the shaft vibration relative displacement peak value and the bearing vibration displacement peak value which are monitored on line by the rotor shaft neck of the rotor and bearing system bearing the action of forced vibration and self-excited vibration are obtained and used as the shaft vibration on-line monitoring data, so that the on-line reliability monitoring data of the shaft vibration is determined, and the operation optimization control is carried out on the nuclear power turbine. The embodiment of the application can accurately monitor the safety of the shaft system vibration of the rotor and the bearing system of the nuclear turbine and optimally control the operation of the nuclear turbine, thereby prolonging the service life of the nuclear turbine and ensuring the long-period safe operation of the nuclear turbine.

Fig. 11 is a flowchart of a shafting vibration safety monitoring method for monitoring the forced vibration and self-excited vibration of a rotor and bearing system of a nuclear turbine of a specific type according to an embodiment of the present application, and as shown in fig. 11, the method includes the following steps:

step 1101, acquiring shafting vibration online monitoring data of the rotor and bearing system under the action of forced vibration and self-excited vibration.

Based on a component model library server 1, a load database server 2 and a material database server 3 of the nuclear power turbine, a shafting vibration operation monitoring method chart of a rotor and bearing system bearing the action of forced vibration and self-excited vibration is input into a shaft neck on-line monitoring shaft vibration relative displacement peak value D of a rotor shaft neck of a 1200MW nuclear power turbine of the model _p-pr =100 μm and bearing on-line monitoring tile vibration displacement peak value D _p-pb And the vibration monitoring data is 70 μm and is used as the online monitoring data of the shafting vibration of the rotor and bearing system under the action of forced vibration and self-excited vibration so as to monitor the reliability of the operation vibration.

And S1102, calculating the ratio of the shaft vibration relative displacement of the rotor shaft neck on line monitoring.

The shaft vibration relative displacement ratio R of the rotor journal of the 1200MW nuclear power steam turbine is monitored on line _p-pr Calculated according to the following formula:

in the above formula, D _p-pr Is 1200MW nuclear power of the modelThe shaft neck of the steam turbine rotor monitors the peak value of the shaft vibration relative displacement peak 100 mu m on line;

and S1103, calculating the ratio of the vibration displacement of the bearing on-line monitoring tile.

The bearing of the 1200MW nuclear power steam turbine monitors the bearing vibration displacement ratio R on line _p-pb Calculated according to the following formula:

in the above formula, D _p-pb The peak value of the vibration displacement peak of the bearing is monitored by 70 μm on line.

And S1104, carrying out operation optimization control on the rotor journal on-line monitoring of the shaft vibration relative displacement.

The shaft vibration relative displacement is monitored on line for the shaft neck of the rotor of the 1200MW nuclear steam turbine to carry out optimization control:

due to R _p-pr And (5) keeping the shaft vibration relative displacement on-line monitoring of the rotor journal of the 1200MW nuclear steam turbine to be qualified in operation monitoring, which indicates that the shaft vibration relative displacement on-line monitoring of the rotor journal of the nuclear steam turbine is in a controlled state or enters the next safety monitoring process.

And S1105, carrying out operation optimization control on the bearing on-line monitoring tile vibration displacement.

Carrying out optimization design control on the bearing on-line monitoring tile vibration displacement of the 1200MW nuclear power turbine:

in view of R _p-pb And if the bearing vibration displacement is monitored on line by the 1200MW nuclear turbine bearing, the condition that the bearing vibration displacement is monitored on line by the nuclear turbine bearing is controlled or the next safety monitoring process is started is indicated that the bearing vibration displacement is monitored on line by the nuclear turbine bearing, wherein the condition is that the bearing vibration displacement is monitored on line by the model is 0.737 < 1.

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, the optimization method also can comprise information such as an optimization result of the nuclear turbine.

Fig. 12 is a structural diagram of a multidimensional reliability monitoring apparatus of a nuclear power turbine according to an embodiment of the present disclosure, and as shown in fig. 12, the multidimensional reliability monitoring apparatus 1200 of the nuclear power turbine includes:

the first acquisition module 1210 is used for acquiring the monitoring data of the dynamic strength and the vibration reliability of the moving blade of the nuclear turbine under the action of centrifugal force, low-frequency excitation force and high-frequency excitation force;

a second obtaining module 1220, configured to obtain torsional vibration reliability monitoring data of a multiple rotor system of the nuclear turbine that suffers from a power grid electrical disturbance fault;

a third obtaining module 1230, configured to obtain first shaft system vibration reliability monitoring data and second shaft system vibration reliability monitoring data of the rotor and bearing system of the nuclear turbine, where the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data are subjected to the forced vibration and self-excited vibration;

a generation obtaining module 1240, configured to generate an optimization improvement policy of the nuclear turbine according to at least one abnormal reliability monitoring data of the dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first axis system vibration reliability monitoring data, and the second axis system vibration reliability monitoring data;

and the optimizing module 1250 is configured to perform optimization control on the nuclear turbine according to the optimization improvement strategy.

In the method, the high reliability of the nuclear turbine is realized by performing design monitoring on the dynamic strength and vibration of the moving blade bearing the centrifugal force, the low-frequency exciting force and the high-frequency exciting force in a design stage, performing design monitoring on the torsional vibration of a multi-rotor system bearing the electric disturbance fault of a power grid, performing design monitoring on the shafting vibration of a rotor and a bearing system bearing the forced vibration and the self-excited vibration, and performing safe operation monitoring on the shafting vibration of the rotor and the bearing system bearing the forced vibration and the self-excited vibration in an operation stage, so that the aims of long service life, high safety guarantee and high reliable operation of the nuclear turbine are fulfilled.

It should be noted that the explanation of the foregoing embodiment of the multidimensional reliability monitoring method for a nuclear turbine is also applicable to the multidimensional reliability monitoring device for a nuclear turbine of this embodiment, and details are not repeated here.

Further, in a possible implementation manner of the embodiment of the present disclosure, the first obtaining module 1210 is further configured to: acquiring running state data of the moving blade under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force; and determining the dynamic intensity and vibration reliability monitoring data according to the running state data of the movable blades.

Further, in a possible implementation manner of the embodiment of the present disclosure, the first obtaining module 1210 is further configured to: determining the safety ratio of the dynamic strength of the moving blade according to the running state data of the moving blade; determining a first frequency resonance ratio of the moving blade avoiding a low-frequency exciting force according to the running state data of the moving blade; determining a second frequency resonance ratio of the moving blade avoiding the high-frequency excitation force according to the operation state data of the moving blade; determining a third frequency resonance ratio of m-order diameter vibration frequency of the whole circle of connected long blades to avoid a high-frequency exciting force according to the running state data of the moving blades; 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 determined dynamic intensity and vibration reliability monitoring data.

Further, in a possible implementation manner of the embodiment of the present disclosure, the second obtaining module 1220 is further configured to: acquiring running state data of the multi-rotor system subjected to the electrical disturbance fault of the power grid; and determining the torsional vibration reliability monitoring data according to the operation state data of the multi-rotor system.

Further, in a possible implementation manner of the embodiment of the present disclosure, the second obtaining module 1220 is further configured to: determining a first ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of a power grid according to the running state data of the multi-rotor system; determining a second ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of the power grid by two times according to the running state data of the multi-rotor system; determining the torsional vibration stress ratio of the multi-rotor system when two phases are short-circuited according to the running state data of the multi-rotor system; and determining the first ratio, the second ratio and the torsional stress ratio as the torsional vibration reliability monitoring data.

Further, in a possible implementation manner of the embodiment of the present disclosure, the third obtaining module 1230 is further configured to: acquiring running state data of the rotor and the bearing system under the action of forced vibration and self-excited vibration; and determining the vibration reliability monitoring data of the first shaft system according to the operating state data of the multi-rotor system of the rotor and bearing system.

Further, in a possible implementation manner of the embodiment of the present disclosure, the third obtaining module 1230 is further configured to: determining the critical rotating speed ratio of the rotor and the bearing system according to the operating state data of the rotor and the bearing system; determining the instability rotating speed ratio of the rotor and the bearing system according to the running state data of the rotor and the bearing system; determining a logarithmic decrement ratio of the rotor to the bearing system according to the operating state data of the rotor to the bearing system; determining a first imbalance response ratio of the rotor and bearing system at a working rotational speed according to the operating state data of the rotor and bearing system; determining a second imbalance response ratio of the rotor and the bearing system at a critical rotation speed according to the operating state data of the rotor and the bearing system; and determining the critical rotating speed ratio, the instability rotating speed ratio, the logarithmic decrement ratio, the first unbalance response ratio and the second unbalance response ratio as the first shaft system vibration reliability monitoring data.

Further, in a possible implementation manner of the embodiment of the present disclosure, the third obtaining module 1230 is further configured to: acquiring shafting vibration online monitoring data of the rotor and bearing system under the action of forced vibration and self-excited vibration; and determining the second shaft system vibration reliability monitoring data according to the shaft system vibration online monitoring data.

Further, in a possible implementation manner of the embodiment of the present disclosure, the third obtaining module 1230 is further configured to: determining the ratio of the shaft journal on-line monitoring shaft vibration relative displacement and the ratio of the bearing on-line monitoring tile vibration displacement according to the shafting vibration on-line monitoring data; and determining the ratio of the shaft vibration relative displacement and the ratio of the bearing vibration displacement as the second shafting vibration reliability monitoring data.

Further, in a possible implementation manner of the embodiment of the present disclosure, the generating module 1240 is further configured to: judging whether the nuclear turbine meets monitoring qualified conditions or not according to at least one abnormal reliability monitoring data of the dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data; and if one of the reliability monitoring data does not meet the qualified monitoring condition, generating an optimization improvement strategy of the nuclear turbine based on the abnormal reliability monitoring data which does not meet the qualified monitoring condition.

Further, in a possible implementation manner of the embodiment of the present disclosure, the generating module 1240 is further configured to: acquiring a part to which the abnormal reliability monitoring data belongs, and calling an optimization model of the nuclear turbine based on the part to which the abnormal reliability monitoring data belongs; and generating an optimization improvement strategy of the nuclear turbine based on the optimization model.

Further, in a possible implementation manner of the embodiment of the present disclosure, the optimizing module 1250 is further configured to: acquiring an adjusting component of the nuclear turbine according to the optimization and improvement strategy; and optimizing the adjusting part according to the adjusting parameters of the adjusting part in the optimization improvement strategy.

Further, in a possible implementation manner of the embodiment of the present disclosure, the optimizing module 1250 is further configured to: and continuing to monitor the abnormal reliability monitoring data which do not meet the monitoring qualified conditions, if the newly acquired reliability monitoring data still do not meet the monitoring qualified conditions, updating the optimization improvement strategy, and continuing to optimize the adjusting component based on the updated optimization improvement strategy.

The present disclosure also provides an electronic device, a readable storage medium, and a computer program product according to embodiments of the present disclosure.

FIG. 13 shows a schematic block diagram of an example electronic device 130 that may be used to implement embodiments of the present disclosure. Electronic devices are intended to represent various forms of digital computers, such as laptops, desktops, workstations, personal digital assistants, servers, blade servers, mainframes, and other appropriate computers. Electronic devices may also represent various forms of mobile devices, such as personal digital processors, cellular telephones, smart phones, wearable devices, and other similar computing devices. The components shown herein, their connections and relationships, and their functions, are meant to be exemplary only, and are not meant to limit implementations of the disclosure described and/or claimed herein.

As shown in fig. 13, the system includes a memory 131, a processor 132, and a computer program stored in the memory 131 and executable on the processor 132, and when the processor 132 executes the program, the foregoing multidimensional reliability monitoring method for a nuclear turbine is implemented.

In the context of this disclosure, a machine-readable medium may be a tangible medium that can contain, or store a program for use by or in connection with an instruction execution system, apparatus, or device. The machine-readable medium may be a machine-readable signal medium or a machine-readable storage medium. A machine-readable medium may include, but is not limited to, an electronic, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, or device, or any suitable combination of the foregoing. More specific examples of a machine-readable storage medium would include an electrical connection based on one or more wires, a portable computer diskette, a hard disk, a Random Access Memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a compact disc read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the foregoing.

To provide for interaction with a user, the systems and techniques described here can be implemented on a computer having: a display device (e.g., a CRT (cathode ray tube) or LCD (liquid crystal display) monitor) for displaying information to a user; and a keyboard and a pointing device (e.g., a mouse or a trackball) by which a user may provide input to the computer. Other kinds of devices may also be used to provide for interaction with a user; for example, feedback provided to the user can be any form of sensory feedback (e.g., visual feedback, auditory feedback, or tactile feedback); and input from the user can be received in any form, including acoustic, speech, or tactile input.

The systems and techniques described here can be implemented in a computing system that includes a back-end component (e.g., as a data server), or that includes a middleware component (e.g., an application server), or that includes a front-end component (e.g., a user computer having a graphical user interface or a web browser through which a user can interact with an implementation of the systems and techniques described here), or any combination of such back-end, middleware, or front-end components. The components of the system can be interconnected by any form or medium of digital data communication (e.g., a communication network). Examples of communication networks include: local Area Networks (LANs), wide Area Networks (WANs), and the Internet.

The computer system may include clients and servers. A client and server are generally remote from each other and typically interact through a communication network. The relationship of client and server arises by virtue of computer programs running on the respective computers and having a client-server relationship to each other. The server may be a cloud server, a server of a distributed system, or a server combining a blockchain.

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 to implicitly indicate 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 invention, "a plurality" means two or more unless specifically defined otherwise.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Moreover, various embodiments or examples and features of various embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims

1. A multidimensional reliability monitoring method for a nuclear turbine is characterized by comprising the following steps:

acquiring monitoring data of dynamic strength and vibration reliability of a moving blade of a nuclear turbine under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force;

acquiring torsional vibration reliability monitoring data of a multi-rotor system of the nuclear turbine subjected to power grid electrical disturbance fault;

acquiring first shaft system vibration reliability monitoring data and second shaft system vibration reliability monitoring data of a rotor and bearing system of the nuclear turbine under the action of forced vibration and self-excited vibration; wherein the first shafting vibration reliability monitoring data comprises: the critical rotating speed ratio of the rotor to the bearing system, the unstable rotating speed ratio of the rotor to the bearing system, the logarithmic decrement ratio of the rotor to the bearing system, a first unbalance response ratio of the rotor to the bearing system at the working rotating speed and a second unbalance response ratio of the rotor to the bearing system at the critical rotating speed; the second shaft system vibration reliability monitoring data includes: the rotor shaft neck on-line monitoring shaft vibration relative displacement ratio and the bearing on-line monitoring tile vibration displacement ratio;

generating an optimization improvement strategy of the nuclear turbine according to at least one abnormal reliability monitoring data of the dynamic intensity and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data;

and performing optimization control on the nuclear turbine according to the optimization improvement strategy.

2. The method of claim 1, wherein the obtaining of the dynamic strength and vibration reliability monitoring data of the action of centrifugal force, low-frequency exciting force and high-frequency exciting force on the moving blade of the nuclear turbine comprises:

acquiring running state data of the moving blade under the action of centrifugal force, low-frequency exciting force and high-frequency exciting force;

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

3. The method of claim 2, wherein said determining said dynamic intensity and vibration reliability monitoring data from said operational status data comprises:

determining the safety ratio of the dynamic strength of the moving blade according to the running state data of the moving blade;

determining a first frequency resonance ratio of the moving blade avoiding a low-frequency excitation force according to the running state data of the moving blade;

determining a second frequency resonance ratio of the moving blade avoiding the high-frequency exciting force according to the running state data of the moving blade;

determining a third frequency resonance ratio of m-step diameter vibration frequency of the whole circle of connected long blades to avoid high-frequency exciting force according to the running state data of the moving blades;

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 determined dynamic intensity and vibration reliability monitoring data.

4. The method of claim 1, wherein the obtaining torsional vibration reliability monitoring data of the multiple rotor system of the nuclear turbine subject to the grid electrical disturbance fault comprises:

acquiring running state data of the multi-rotor system subjected to the electrical disturbance fault of the power grid;

and determining the torsional vibration reliability monitoring data according to the running state data of the multi-rotor system.

5. The method of claim 4, wherein determining the torsional vibration reliability monitoring data from the operating state data of the multi-rotor system comprises:

determining a first ratio of the torsional vibration frequency of the multi-rotor system to avoid the working frequency of a power grid according to the running state data of the multi-rotor system;

determining a second ratio of the torsional vibration frequency of the multi-rotor system to avoid the double working frequency of the power grid according to the running state data of the multi-rotor system;

determining the torsional vibration stress ratio of the multi-rotor system when two phases are short-circuited according to the running state data of the multi-rotor system;

and determining the first ratio, the second ratio and the torsional vibration stress ratio as the torsional vibration reliability monitoring data.

6. The method of claim 1, wherein the obtaining the first shaft system vibration reliability monitoring data of the rotor and bearing system of the nuclear turbine subjected to the forced vibration and the self-excited vibration comprises:

acquiring running state data of the rotor and bearing system under the action of forced vibration and self-excited vibration;

and determining the vibration reliability monitoring data of the first shaft system according to the running state data of the rotor and the bearing system.

7. The method of claim 6, wherein determining the first shaft system vibration reliability monitoring data from the operating condition data of the rotor and bearing system comprises:

determining the critical rotating speed ratio of the rotor and the bearing system according to the running state data of the rotor and the bearing system;

determining the instability rotating speed ratio of the rotor and the bearing system according to the running state data of the rotor and the bearing system;

determining the logarithmic decrement ratio of the rotor and the bearing system according to the running state data of the rotor and the bearing system;

determining a first unbalance response ratio of the rotor and the bearing system at a working rotating speed according to the running state data of the rotor and the bearing system;

and determining a second imbalance response ratio of the rotor and the bearing system at the critical rotating speed according to the operating state data of the rotor and the bearing system.

8. The method of claim 1, wherein obtaining second shaft system vibration reliability monitoring data of the rotor and bearing system of the nuclear turbine subject to the forced vibration and the self-excited vibration comprises:

acquiring shafting vibration online monitoring data of the rotor and bearing system under the action of forced vibration and self-excited vibration;

and determining the second shaft system vibration reliability monitoring data according to the shaft system vibration online monitoring data.

9. The method of claim 8, wherein said determining said second shafting vibration reliability monitoring data from said shafting vibration online monitoring data comprises:

and determining the ratio of the shaft vibration relative displacement of the rotor journal on-line monitoring and the ratio of the bearing vibration displacement of the bearing on-line monitoring according to the shafting vibration on-line monitoring data.

10. The method according to any one of claims 1 to 9, wherein generating an optimization improvement strategy for the nuclear power turbine based on at least one anomaly reliability monitoring data of the dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data, and the second shaft system vibration reliability monitoring data comprises:

judging whether the nuclear turbine meets monitoring qualified conditions or not according to at least one abnormal reliability monitoring data of the dynamic strength and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data;

and if one piece of reliability monitoring data does not meet the monitoring qualified condition, generating an optimization improvement strategy of the nuclear turbine based on the abnormal reliability monitoring data which does not meet the monitoring qualified condition.

11. The method of claim 10, wherein generating an optimization improvement strategy for the nuclear turbine based on the unrequired monitored qualifying condition exceptional reliability monitoring data comprises:

acquiring a component to which the abnormal reliability monitoring data belongs, and calling an optimization model of the nuclear turbine based on the component to which the abnormal reliability monitoring data belongs;

and generating an optimization improvement strategy of the nuclear turbine based on the optimization model.

12. The method of claim 11, wherein said optimizing control of said nuclear power turbine in accordance with said optimization improvement strategy comprises:

acquiring an adjusting part of the nuclear turbine according to the optimization and improvement strategy;

and optimizing the adjusting component according to the adjusting parameter of the adjusting component in the optimization and improvement strategy.

13. The method according to claim 12, wherein after optimizing the adjusting component according to the adjusting parameters of the adjusting component in the optimization improvement strategy, the method further comprises:

and continuously monitoring the abnormal reliability monitoring data which do not meet the monitoring qualified conditions, if the newly acquired reliability monitoring data still do not meet the monitoring qualified conditions, updating the optimization improvement strategy, and continuously optimizing the adjusting component based on the updated optimization improvement strategy.

14. A multi-dimensional reliability monitoring device of a nuclear turbine is characterized by comprising:

the second acquisition module is used for acquiring torsional vibration reliability monitoring data of a multi-rotor system of the nuclear turbine, which bear power grid electrical disturbance faults;

the third acquisition module is used for acquiring the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data of the rotor and bearing system of the nuclear turbine under the action of forced vibration and self-excited vibration; wherein the first shafting vibration reliability monitoring data comprises: the critical rotating speed ratio of the rotor to the bearing system, the unstable rotating speed ratio of the rotor to the bearing system, the logarithmic decrement ratio of the rotor to the bearing system, a first unbalance response ratio of the rotor to the bearing system at the working rotating speed and a second unbalance response ratio of the rotor to the bearing system at the critical rotating speed; the second shaft system vibration reliability monitoring data includes: the rotor shaft neck on-line monitoring shaft vibration relative displacement ratio and the bearing on-line monitoring tile vibration displacement ratio;

the generating module is used for generating an optimization improvement strategy of the nuclear turbine according to at least one abnormal reliability monitoring data in the dynamic intensity and vibration reliability monitoring data, the torsional vibration reliability monitoring data, the first shaft system vibration reliability monitoring data and the second shaft system vibration reliability monitoring data;

and the optimization module is used for carrying out optimization control on the nuclear turbine according to the optimization improvement strategy.

15. The apparatus of claim 14, wherein the first obtaining module is further configured to:

16. The apparatus of claim 15, wherein the first obtaining module is further configured to:

determining a first frequency resonance ratio of the moving blade avoiding low-frequency exciting force according to the running state data of the moving blade;

determining a second frequency resonance ratio of the moving blade avoiding the high-frequency excitation force according to the operation state data of the moving blade;

17. The apparatus of claim 14, wherein the second obtaining module is further configured to:

18. The apparatus of claim 17, wherein the second obtaining module is further configured to:

19. The apparatus of claim 14, wherein the third obtaining module is further configured to:

and determining the vibration reliability monitoring data of the first shaft system according to the operating state data of the multi-rotor system of the rotor and bearing system.

20. The apparatus of claim 19, wherein the third obtaining module is further configured to:

determining the logarithmic decrement ratio of the rotor and the bearing system according to the operating state data of the rotor and the bearing system;

and determining a second unbalance response ratio of the rotor and the bearing system at the critical rotating speed according to the operating state data of the rotor and the bearing system.

21. The apparatus of claim 14, wherein the third obtaining module is further configured to:

22. The apparatus of claim 21, wherein the third obtaining module is further configured to:

23. The apparatus according to any one of claims 14-22, wherein the generating module is further configured to:

24. The apparatus of claim 23, wherein the generating module is further configured to:

acquiring a part to which the abnormal reliability monitoring data belongs, and calling an optimization model of the nuclear turbine based on the part to which the abnormal reliability monitoring data belongs;

25. The apparatus of claim 24, wherein the optimization module is further configured to:

and optimizing the adjusting component according to the adjusting parameters of the adjusting component in the optimization improvement strategy.

26. The apparatus of claim 25, wherein the optimization module is further configured to:

and continuing to monitor the abnormal reliability monitoring data which do not meet the monitoring qualified conditions, if the newly acquired reliability monitoring data still do not meet the monitoring qualified conditions, updating the optimization improvement strategy, and continuing to optimize the adjusting component based on the updated optimization improvement strategy.

27. An electronic device comprising a memory, a processor;

wherein the processor runs a program corresponding to the executable program code by reading the executable program code stored in the memory for implementing the method according to any one of claims 1 to 13.

28. A computer-readable storage medium, on which a computer program is stored which, when being executed by a processor, carries out the method according to any one of claims 1-13.