CN112699505B - Dynamic stress finite element calculation method for long blade of low-pressure cylinder of nuclear power unit - Google Patents

Dynamic stress finite element calculation method for long blade of low-pressure cylinder of nuclear power unit Download PDF

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CN112699505B
CN112699505B CN202011596317.8A CN202011596317A CN112699505B CN 112699505 B CN112699505 B CN 112699505B CN 202011596317 A CN202011596317 A CN 202011596317A CN 112699505 B CN112699505 B CN 112699505B
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rotor
calculating
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setting
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CN112699505A (en
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李宇峰
管继伟
马义良
潘劭平
关淳
梁天赋
李央
郭魁俊
武芏茳
张迪
王健
潘春雨
赵洪羽
高铁印
徐林峰
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Harbin Turbine Co Ltd
Hadian Power Equipment National Engineering Research Center Co Ltd
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    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/141—Shape, i.e. outer, aerodynamic form
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/147—Construction, i.e. structural features, e.g. of weight-saving hollow blades
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G06F30/28—Design optimisation, verification or simulation using fluid dynamics, e.g. using Navier-Stokes equations or computational fluid dynamics [CFD]
    • G—PHYSICS
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    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2111/00—Details relating to CAD techniques
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    • G06F—ELECTRIC DIGITAL DATA PROCESSING
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    • G06—COMPUTING; CALCULATING OR COUNTING
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    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation

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Abstract

The invention discloses a dynamic stress finite element calculation method for a long blade of a low-pressure cylinder of a nuclear power unit, and relates to a dynamic stress calculation method for a long blade of a low-pressure cylinder. The invention aims to solve the problem of low calculation accuracy of the dynamic stress of the long blade of the conventional nuclear power unit. A dynamic stress finite element calculation method for a long blade of a low-pressure cylinder of a nuclear power unit comprises the following specific processes: the method comprises the following steps: calculating the pressure of the steam on the surface of the blade profile; step two: calculating the dynamic frequency and the resonance danger pitch diameter of the blade based on the first step; step three: and calculating the dynamic stress of the blade based on the first step and the second step. The method is used for the field of the finite element calculation method of the dynamic stress of the long blade of the low-pressure cylinder of the nuclear power unit.

Description

Dynamic stress finite element calculation method for long blade of low-pressure cylinder of nuclear power unit
Technical Field
The invention relates to a dynamic stress calculation method of a low-pressure long blade.
Background
The blades are the heart of the turbine and are the most important part of the turbine, and 70% of turbine accidents are caused by blade damage. The nuclear power unit has high power, and the low-voltage blade has long length to cause rigidity reduction, so that the capability of resisting dynamic stress of the blade is reduced, and the blade damage accident is easy to happen. With the continuous increase of nuclear power generating units in recent years, the dynamic stress calculation requirement of low-pressure long blades of the nuclear power generating units is more and more urgent.
Disclosure of Invention
The invention aims to solve the problem of low accuracy of calculation of the dynamic stress of a long blade of an existing nuclear power unit, and provides a finite element calculation method of the dynamic stress of a long blade of a low-pressure cylinder of the nuclear power unit.
A dynamic stress finite element calculation method for a long blade of a low-pressure cylinder of a nuclear power unit comprises the following specific processes:
the method comprises the following steps: calculating the pressure of the steam on the surface of the blade profile;
step two: calculating the dynamic frequency and the resonance danger pitch diameter of the blade based on the first step;
step three: and calculating the dynamic stress of the blade based on the first step and the second step.
Calculating the steam pressure of the blade profile surface in the first step; the specific process is as follows:
the method comprises the following steps: acquiring x, y and z coordinate data points of the blade according to the low-pressure cylinder flow pattern and the molded line of the blade, and establishing a blade geometric model according to the x, y and z coordinate data points of the blade;
the first step is: importing x, y and z coordinate data points of the established blade geometric model into fluid calculation software to form a flow channel model, and dividing the flow channel model to generate a flow field grid;
step one is three: calculating the flow field grid generated in the first step and the second step by using fluid calculation software according to the thermal data of the unit to obtain the steam pressure of each part of the blade-shaped surface under the conventional working condition;
in the second step, the dynamic frequency and the resonance danger pitch diameter of the blade are calculated based on the first step; the specific process is as follows:
step two, firstly: establishing a low-pressure cylinder long blade geometric model for the low-pressure cylinder long blade by using geometric modeling software based on the shroud band, the blade root and the tie bar size data of the blade and the molded line of the blade;
according to the low-pressure cylinder flow graph and the size of a blade root, establishing a rotor geometric model for a rotor corresponding to a long blade of a low-pressure cylinder by using geometric modeling software;
step two: meshing the established low-pressure cylinder long blade geometric model and the established rotor geometric model by using meshing software to generate meshes; the specific process is as follows:
the contact part of the rotor and the blade root uses hexahedral mesh, the rest parts use tetrahedron, pentahedron or hexahedron for smooth transition, the mesh length of the blade profile part is as follows: width: the height is 2.
Step two and step three: calculating the dynamic frequency and the resonance danger pitch diameter of the blade under the condition of the working rotating speed of the blade by using finite element software based on the working temperature of the unit, the working rotating speed and the material data of the blade and the rotor; the specific process is as follows:
importing the grid generated in the second step into finite element software, and setting the contact surfaces of the blade and the rotor and the friction coefficient; setting a rotational speed load applied to the whole of the blade and the rotor; setting a steam pressure load applied to the airfoil surface; setting temperature loads of the blade and the rotor, and setting material properties of the blade and the rotor;
calculating to obtain the dynamic frequency and the resonance dangerous pitch diameter under the condition of the working rotating speed of the blade;
the steam pressure is calculated in the first step;
calculating the dynamic stress of the blade based on the first step and the second step in the third step; the specific process is as follows:
step three, firstly: taking 4% of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one, wherein the upper limit of the steam pressure distribution of the blade-shaped surface under the dangerous working condition is 4% of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one, and the lower limit of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one is-4%;
step two, calculating the dynamic stress of the blade by using finite element software based on the working temperature and the rotating speed of the unit, the material data of the blade and the rotor and the resonance dangerous pitch diameter data obtained in the step two;
the specific process is as follows:
importing the grid generated in the second step into finite element software, and setting the contact surfaces of the blade and the rotor and the friction coefficient; setting the rotating speed load applied to the whole of the blade and the rotor; setting steam pressure load applied to the blade profile surface; setting resonance dangerous pitch diameter data, setting temperature loads of the blades and the rotor, and setting material properties of the blades and the rotor;
calculating to obtain the dynamic stress of the blade;
the steam pressure is the upper limit and the lower limit of the distribution of the steam pressure of the blade surface under the dangerous working condition obtained in the third step;
and the resonance dangerous nodal diameter data are resonance dangerous nodal diameters obtained in the second step.
The invention has the beneficial effects that:
the invention uses three-dimensional fluid calculation software to divide the flow field grid for calculation, and can calculate the steam pressure of the blade surface more accurately compared with the traditional calculation method. The finite element method is used for calculating the dynamic frequency and the resonance danger pitch diameter of the blade, and the calculation precision is higher. The dynamic stress of the blade calculated through the data is more accurate, and the method can be used for design and check of the long blade of the low-pressure cylinder of the nuclear power unit.
The calculation process of the invention can be standardized, engineers can use a large-scale computer for calculation, and the result can be obtained in a short time, thereby greatly improving the working efficiency. The method improves the calculation accuracy of the dynamic stress of the long blade of the nuclear power unit, and solves the problem of low calculation accuracy of the dynamic stress of the long blade of the existing nuclear power unit.
Drawings
FIG. 1 is a geometric schematic of a single stage blade and corresponding rotor section;
FIG. 2 is a schematic diagram of a blade interface defined in finite element software;
FIG. 3 is a schematic view of a rotor interface defined in the finite element software.
Detailed Description
The first embodiment is as follows: the method for calculating the dynamic stress finite element of the long blade of the low-pressure cylinder of the nuclear power unit comprises the following specific steps:
the method comprises the following steps: calculating the pressure of the steam on the surface of the blade profile;
step two: calculating the dynamic frequency and the resonance danger pitch diameter of the blade based on the first step;
step three: and calculating the dynamic stress of the blade based on the first step and the second step.
The second embodiment is as follows: the difference between the first embodiment and the first embodiment is that the pressure of the blade-shaped surface steam is calculated in the first step; the specific process is as follows:
the method comprises the following steps: acquiring x, y and z coordinate data points (a plurality of points) of the blade according to the low-pressure cylinder flow-through diagram and the molded line of the blade, and establishing a blade geometric model according to the x, y and z coordinate data points of the blade;
the first step is: importing x, y and z coordinate data points of the established blade geometric model into fluid calculation software (existing software) to form a flow channel model, and dividing the flow channel model to generate a flow field grid;
step one, three: according to the thermodynamic data (total temperature of an inlet and an outlet of a blade, total pressure of the inlet and the outlet of the blade, static pressure of an outlet and the like) of the unit, simulating and calculating the flow field grid generated in the first step and the second step by using fluid calculation software (existing software) to obtain the steam pressure of each part of the surface of the blade profile under the conventional working condition (all data are under the normal condition);
other steps and parameters are the same as those in the first embodiment.
The third concrete implementation mode: the second embodiment is different from the first or second embodiment in that the blade dynamic frequency and the resonance danger nodal diameter are calculated in the first step; the specific process is as follows:
step two, firstly: establishing a low-pressure cylinder long blade geometric model for the low-pressure cylinder long blade by using geometric modeling software (existing software) based on shroud band, blade root and tie bar size data of the blade and molded lines of the blade;
according to the low-pressure cylinder flow diagram and the size of a blade root, geometric modeling software (existing software) is used for establishing a rotor geometric model for a rotor 2 corresponding to a long blade 1 of a low-pressure cylinder, and the model schematic diagram is shown in figure 1;
step two: meshing the established low-pressure cylinder long blade geometric model and the established rotor geometric model by using meshing software (existing software) to generate meshes; the specific process is as follows:
the contact part of the rotor and the blade root uses hexahedral mesh, the rest part uses tetrahedron, pentahedron or hexahedron for smooth transition, the mesh length of the blade profile part is as follows: width: height is about 2.
Step two and step three: calculating the dynamic frequency and the resonance dangerous nodal diameter (the resonance dangerous nodal diameter is the closest resonance point to the rotating speed) under the condition of the working rotating speed of the blade by using finite element software (the existing software) based on the working temperature of the unit, the working rotating speed, the material data (the material used by the blade and the rotor and the characteristics of the material pair, such as the density) of the blade and the rotor and the like; the specific process is as follows:
importing the grid generated in the second step into finite element software (existing software), and setting the contact surfaces of the blade and the rotor and the friction coefficient; setting a rotational speed load applied to the whole of the blade and the rotor; setting a steam pressure load applied to the airfoil surface; setting temperature loads of the blades and the rotor, and setting material properties of the blades and the rotor (the temperature loads of the blades and the rotor are the unit working temperature of the second step and the third step, the material properties of the blades and the rotor are the material data of the blades and the rotor of the second step and the third step, and setting the rotating speed load applied to the whole of the blades and the rotor as the working rotating speed of the second step and the third step);
calculating to obtain the dynamic frequency and the resonance dangerous pitch diameter (the resonance dangerous pitch diameter is the closest resonance point to the rotating speed) under the condition of the working rotating speed of the blade;
the steam pressure is the steam pressure calculated in the first step.
Other steps and parameters are the same as those in the first or second embodiment.
The fourth concrete implementation mode: the difference between the present embodiment and one of the first to third embodiments is that in the third step, the dynamic stress of the blade is calculated based on the first step and the second step;
step three, firstly: taking 4% of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one, wherein the upper limit of the steam pressure distribution of the blade-shaped surface under the dangerous working condition is 4% of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one, and the lower limit of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one is-4%;
step two, calculating the dynamic stress of the blade by using finite element software (existing software) based on the data of the material data (the material and the material pair used by the blade and the rotor, such as density) of the blade and the rotor, the resonance dangerous pitch diameter and the like obtained in the step two, and the working temperature and the rotating speed of the unit;
the specific process is as follows:
importing the grid generated in the second step into finite element software, and setting the contact surface of the blade and the rotor and the friction coefficient; setting the rotating speed load applied to the whole of the blade and the rotor; setting steam pressure load applied to the blade profile surface; setting resonance dangerous pitch diameter data, setting temperature loads of the blades and the rotor, and setting material properties of the blades and the rotor;
calculating to obtain the dynamic stress of the blade;
the steam pressure is the upper limit and the lower limit of the distribution of the steam pressure of the blade surface under the dangerous working condition obtained in the third step;
and the resonance dangerous nodal diameter data are resonance dangerous nodal diameters obtained in the second step.
The blade contact surface is shown in FIG. 2 and the rotor contact surface is shown in FIG. 3, with a coefficient of friction set at 0.2.
Other steps and parameters are the same as those in one of the first to third embodiments.
The present invention may be embodied in other specific forms without departing from the spirit or essential attributes thereof, and it is therefore intended that all such changes and modifications be considered as within the spirit and scope of the appended claims.

Claims (1)

1. A dynamic stress finite element calculation method for a long blade of a low-pressure cylinder of a nuclear power unit is characterized by comprising the following steps of: the method comprises the following specific processes:
the method comprises the following steps: calculating the pressure of the steam on the surface of the blade profile;
step two: calculating the dynamic frequency and the resonance danger pitch diameter of the blade based on the first step;
step three: calculating the dynamic stress of the blade based on the first step and the second step;
calculating the steam pressure of the blade profile surface in the first step; the specific process is as follows:
the method comprises the following steps: acquiring x, y and z coordinate data points of the blade according to the low-pressure cylinder flow-through diagram and the molded line of the blade, and establishing a blade geometric model according to the x, y and z coordinate data points of the blade;
the first step is: introducing x, y and z coordinate data points of the established blade geometric model into fluid calculation software to form a flow channel model, and dividing the flow channel model to generate a flow field grid;
step one, three: calculating the flow field grid generated in the first step and the second step by using fluid calculation software according to the thermal data of the unit to obtain the steam pressure of each part of the blade-shaped surface under the conventional working condition;
in the second step, the dynamic frequency and the resonance danger pitch diameter of the blade are calculated based on the first step; the specific process is as follows:
step two, firstly: establishing a low-pressure cylinder long blade geometric model for the low-pressure cylinder long blade by using geometric modeling software based on the shroud band, the blade root and the tie bar size data of the blade and the molded line of the blade;
according to the low-pressure cylinder flow diagram and the size of the blade root, establishing a rotor geometric model for the rotor corresponding to the low-pressure cylinder long blade by using geometric modeling software;
step two: meshing the established low-pressure cylinder long blade geometric model and the rotor geometric model by using meshing software to generate meshes; the specific process is as follows:
the contact part of the rotor and the blade root uses hexahedral mesh, the rest part uses tetrahedron, pentahedron or hexahedron for smooth transition, the mesh length of the blade profile part is as follows: width: the height is 2;
step two and step three: calculating the dynamic frequency and the resonance danger pitch diameter of the blade under the condition of the working rotating speed of the blade by using finite element software based on the working temperature of the unit, the working rotating speed and the material data of the blade and the rotor; the specific process is as follows:
importing the grid generated in the second step into finite element software, and setting the contact surfaces of the blade and the rotor and the friction coefficient; setting a rotational speed load applied to the whole of the blade and the rotor; setting a steam pressure load applied to the airfoil surface; setting temperature loads of the blades and the rotor, and setting material properties of the blades and the rotor;
calculating to obtain the dynamic frequency and the resonance dangerous pitch diameter under the condition of the working rotating speed of the blade;
the steam pressure is calculated in the first step;
calculating the dynamic stress of the blade based on the first step and the second step in the third step; the specific process is as follows:
step three, first: taking 4% of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one, wherein the upper limit of the steam pressure distribution of the blade-shaped surface under the dangerous working condition is 4% of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one, and the lower limit of the steam pressure data of each part of the blade-shaped surface under the normal working condition calculated in the step one is-4%;
step two, calculating the dynamic stress of the blade by using finite element software based on the working temperature and the rotating speed of the unit, the material data of the blade and the rotor and the resonance dangerous pitch diameter data obtained in the step two;
the specific process is as follows:
importing the grid generated in the second step into finite element software, and setting the contact surfaces of the blade and the rotor and the friction coefficient; setting the rotating speed load applied to the whole of the blade and the rotor; setting steam pressure load applied to the blade profile surface; setting resonance dangerous pitch diameter data, setting temperature loads of the blades and the rotor, and setting material properties of the blades and the rotor;
calculating to obtain the dynamic stress of the blade;
the steam pressure is the upper limit and the lower limit of the distribution of the steam pressure of the blade-shaped surface under the dangerous working condition obtained in the step three;
and the resonance dangerous pitch diameter data is the resonance dangerous pitch diameter obtained in the step two.
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