A method for optimizing the hydraulic performance of the blades of a cold / hot state compensation impeller of a nuclear main pump and a nuclear main pump

Abstract

The application provides a nuclear main pump cold and hot state compensation impeller blade hydraulic optimization method and a nuclear main pump, and comprises the following steps: determining target variables of optimization design; obtaining geometric parameters through an initial cold state hydraulic model; obtaining a cold state efficiency through simulation; defining material properties of a flow part of the hydraulic model, determining a blade surface node coordinate set before fluid-structure thermal coupling according to a grid of the model; obtaining a blade surface node deformation coordinate set after fluid-structure thermal coupling through simulation; adding the blade surface node deformation coordinate set after fluid-structure thermal coupling and the blade surface node coordinate set before fluid-structure thermal coupling to obtain a corrected blade surface node coordinate set; reconstructing the flow part according to the corrected blade surface node coordinate set to obtain a corrected hydraulic model; obtaining a hot state efficiency through flow field simulation of the corrected hydraulic model; and optimizing the nuclear main pump impeller blade under the condition of meeting cold and hot state conversion.

Description

Technical Field

[0001] This invention relates to the field of blade optimization for nuclear main pumps, and particularly to a method for hydraulic optimization of impeller blades for hot and cold compensating conditions in nuclear main pumps, and a nuclear main pump. Background Technology

[0002] In the primary loop system of the nuclear island, the pump used to drive the circulation of coolant within the reactor coolant system is called the reactor coolant main circulation pump (or simply nuclear main pump). The nuclear main pump continuously transfers the heat generated in the reactor core to the feedwater in the secondary loop of the steam generator. Located at the heart of the nuclear island, it pumps cold water into the evaporator to convert heat energy. It is crucial for controlling the water circulation in nuclear power plant operations and is considered a primary piece of equipment. Each steam generator has one nuclear main pump. Because the heat from the nuclear reactor is carried away by the circulation of the primary loop working fluid driven by the nuclear main pump, there are stricter requirements for the safe, stable, and long-term operation of the nuclear main pump.

[0003] Currently, the hydraulic optimization design of nuclear main pumps mostly starts from a cold-state perspective (normal temperature operating conditions), that is, under normal temperature conditions, and then derives the actual operating performance through conversion formulas. According to feedback from power plants, the actual operating conditions of nuclear main pumps are under high temperature and high pressure environments. In particular, the impeller of the nuclear main pump will deform under high temperature, high pressure and centrifugal loads. These deformations will affect the performance of components and deviate from the performance of the design point. Therefore, it is necessary to conduct in-depth research on the hydraulic optimization method of nuclear main pumps under hot conditions (i.e., actual operating conditions). This is one of the difficulties that must be considered in the hydraulic design of nuclear main pump impellers.

[0004] Existing technologies propose a method for rapid conversion between cold and hot states of centrifugal impeller and turbine blade profiles. This method mainly addresses the problem of large computational load on deformation control points of various profile sections during the iteration process. It comprehensively considers aerodynamic load, temperature load, and centrifugal load, and obtains the deformation of each profile section control point through linear interpolation of the mid-arc line. However, it requires a large overall computational resource.

[0005] Existing technologies propose a method for rapid conversion between cold and hot states of turbine blade models. During the blade iteration process, aerodynamic loads, temperature fields, and centrifugal loads are also considered. This overcomes the contradiction between high-precision conversion between cold and hot states and large computational load in existing conventional cold and hot state conversion methods. However, it does not take into account the impact of changes in turbine blade geometry on turbine performance.

[0006] Existing technologies propose a method for optimizing aero-engine blade structures that comprehensively considers the blade shroud amount and the relationship between hot and cold states. This method treats blade shroud amount adjustment and hot-cold state conversion as a complete optimization process, avoiding the problem of significant stress and deformation in the corresponding hot-state blade profile after traditional shroud amount adjustment and hot-cold state conversion procedures. However, this method only addresses the structural aspects of the rotor components and does not delve into the hydraulics of the rotor components.

[0007] Existing technology proposes a method and apparatus for calculating the cold and hot states of axial flow blades. It uses finite element analysis to obtain the displacements at the tip, middle, and tail of the blade. It calculates the average translational and torsional errors between the theoretical blade and the current hot blade at the tip and middle sections to obtain correction values. It obtains the coordinate correction values ​​of all blade profile sections by interpolation at the root, middle, and tip. After repeated corrections, it obtains the blade profile of each section of the current conformal blade. However, it cannot effectively and accurately correct the blade profile structure of the more complex twisted blades of nuclear main pump impellers.

[0008] Existing technologies propose a method for transforming structures into hot and cold states. The method designs the structure based on the hot state conditions to obtain the hot state structure; analyzes the deformation of the hot state structure under cold state conditions; and transforms the hot state structure based on the deformation to obtain the cold state structure. However, this method suffers from a contradiction between high-precision transformation between hot and cold states and large computational load. Summary of the Invention

[0009] To address the shortcomings of existing technologies, this invention provides a method for hydraulic optimization of impeller blades under cold and hot conditions in nuclear main pumps, as well as a nuclear main pump itself. This solves the problem that existing hydraulic designs for nuclear main pumps do not consider the impact of impeller blade deformation under cold and hot conditions on the performance of the nuclear main pump.

[0010] The present invention achieves the above-mentioned technical objectives through the following technical means.

[0011] A method for hydraulic optimization of impeller blades under cold and hot conditions in a nuclear main pump includes the following steps:

[0012] S01: The target variables for optimization design are determined as flow rate Q, head H, rotational speed n, and efficiency η; an initial cold-state hydraulic model is obtained through simulation at room temperature. The geometric parameters obtained from the initial cold-state hydraulic model are: impeller outer diameter D2, blade thickness ξ, blade inlet angle β1, blade outlet angle β2, and blade wrap angle.

[0013] S02: Based on geometric parameter modeling and finite element mesh generation, define the material properties of the flow components in the hydraulic model, and obtain the cold efficiency η1 from the flow field simulation; if the cold efficiency η1 < η, then return to S01 and adjust the value of at least one parameter in the geometric parameters.

[0014] S03: When the cold efficiency η1≥η, the hydraulic model based on geometric parameters is the optimal solution;

[0015] S04: Determine the blade surface nodal coordinate set X before fluid-structure-thermal coupling based on the model's mesh. k {N1(x1,y1,z1),N2(x2,y2,z2),…,N k (x k y k , z k)};

[0016] S05: Simulation yields the coordinate set Y of the nodal deformation of the blade surface after fluid-structure-thermal coupling. k {ΔN1(Δx1,Δy1,Δz1),ΔN2(Δx2,Δy2,Δz2),…,ΔN k (Δx k Δy k Δz k )};

[0017] S06: Set the coordinates of nodal deformation on the blade surface after fluid-structure-thermal coupling, Y k The nodal coordinate set X of the blade surface before fluid-structure-thermal coupling k Adding them together, we obtain the corrected set of blade surface nodal coordinates:

[0018] X' k {N'1(x'1,y'1,z'1),N'2(x'2,y'2,z'2),…,N' k (x' k ,y' k ,z' k )},

[0019] Where: N' k (x' k ,y' k ,z' k ) = N k (x k ,y k ,z k )+ΔN k (Δx k ,Δy k ,Δz k );

[0020] S07: Based on the corrected blade surface nodal coordinate set X' k The flow path components are reconstructed to obtain the corrected hydraulic model; the flow field of the corrected hydraulic model is simulated to obtain the thermal efficiency η2;

[0021] S08: If the hot hydraulic efficiency η2 ≥ the cold hydraulic efficiency η1, then the corrected hydraulic model is the optimized hydraulic model; if the hot hydraulic efficiency η2 < the cold hydraulic efficiency η1, then return to S01 and adjust at least one parameter of the geometric parameters, and perform a loop solution.

[0022] Furthermore, the specific nodal points on the blade surface before fluid-structure-thermal coupling were determined as follows:

[0023] The impeller blade profile is divided into several blade sections by several cross sections. Each blade section includes the intersection line between the blade working surface and the blade section and the intersection line between the blade back surface and the blade section; the control point of each intersection line is a node on the blade surface.

[0024] Furthermore, if the cold efficiency η1 < η, then return to S01 and increase or decrease one of the geometric parameters by no more than 5%.

[0025] Furthermore, if the hot hydraulic efficiency η2 < the cold hydraulic efficiency η1, then return to S01 and increase or decrease one of the geometric parameters by no more than 2%.

[0026] Furthermore, if the cold-state efficiency η1 < η or the hot-state hydraulic efficiency η2 < the cold-state hydraulic efficiency η1, then return to S01 to adjust the blade inlet angle β1 and blade outlet angle β2 in the geometric parameters, and satisfy the following relationship: 0.54(β1+Δβ1)≤(β2+Δβ2)<0.65(β1+Δβ1), where Δβ1 is the adjustment amount of the blade inlet angle and Δβ2 is the adjustment amount of the blade outlet angle.

[0027] Furthermore, when the adjusted blade inlet angle β1 and blade outlet angle β2 satisfy the following relationship 0.65(β11+Δβ11)≤(β2+Δβ2)<0.9(β11+Δβ1), the blade wrap angle in the geometric parameters is adjusted. And satisfy the following relationship:

[0028] in This is the adjustment amount for the blade wrap angle.

[0029] A nuclear main pump utilizes a hydraulic optimization method for compensating impeller blades under cold and hot conditions to optimize the blades.

[0030] The beneficial effects of this invention are as follows:

[0031] 1. The cold and hot state compensation impeller blade hydraulic optimization method for nuclear main pumps described in this invention combines cold and hot state impeller hydraulics, comprehensively considering temperature load and centrifugal load, reconstructing the impeller blade surface after hot deformation, obtaining the theoretical impeller deformation, and then performing reverse calculations to finally obtain the optimal hydraulic design scheme. While ensuring the accuracy of the hydraulic design, it improves the hydraulic efficiency of the nuclear main pump and significantly reduces the energy consumption of nuclear power plants. The cold and hot state compensation impeller blade hydraulic optimization method for nuclear main pumps described in this invention solves the problem that existing nuclear main pump hydraulic designs do not consider the impact of impeller blade deformation under cold and hot state transitions on the performance of the nuclear main pump.

[0032] 2. The method for hydraulic optimization of impeller blades for cold and hot state compensation of nuclear main pumps described in this invention provides how to adjust one parameter when the cold state efficiency and hot state efficiency do not meet the conditions respectively; at the same time, it provides the conditions for adjusting three parameters, which can reduce the calculation time of the cycle and obtain the optimized blades more quickly. Attached Figure Description

[0033] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are some embodiments of the present invention. For those skilled in the art, it is obvious that other drawings can be obtained from these drawings without creative effort.

[0034] Figure 1 This is a flowchart of the hydraulic optimization method for cold and hot state compensation of impeller blades in the nuclear main pump described in this invention.

[0035] Figure 2 This is a three-dimensional schematic diagram of the impeller blades of the nuclear main pump of the present invention.

[0036] Figure 3 This is a schematic diagram of the deformation of the back side of the impeller blades of the nuclear main pump in a specific embodiment of the present invention.

[0037] Figure 4 This is a schematic diagram comparing the hydraulic performance of the nuclear main pump impeller under different hot deformation states in a specific embodiment of the present invention. Detailed Implementation

[0038] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0039] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "axial," "radial," "vertical," "horizontal," "inner," and "outer," etc., indicating orientation or positional relationships based on the orientation or positional relationships shown in the accompanying drawings, are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0040] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0041] like Figure 1 As shown, the hydraulic optimization method for cold and hot state compensation of impeller blades of the nuclear main pump according to the present invention includes the following steps:

[0042] S01: The target variables for optimization design are determined as flow rate Q, head H, rotational speed n, and efficiency η; an initial cold-state hydraulic model is obtained through simulation at room temperature. The geometric parameters obtained from the initial cold-state hydraulic model are: impeller outer diameter D2, blade thickness ξ, blade inlet angle β1, blade outlet angle β2, and blade wrap angle.

[0043] S02: Based on geometric parameter modeling and finite element mesh generation, define the material properties of the flow components in the hydraulic model, and obtain the cold efficiency η1 from the flow field simulation; if the cold efficiency η1 < η, then return to S01 to adjust at least one parameter of the geometric parameters; here, prioritize adjusting one parameter, increasing or decreasing one parameter of the geometric parameters by no more than 5%.

[0044] S03: When the cold efficiency η1≥η, the hydraulic model based on geometric parameters is the optimal solution;

[0045] S04: After fluid-structure-thermal coupling calculations, the coordinate set X of the blade surface nodes before fluid-structure-thermal coupling is determined based on the model's mesh.k {N1(x1,y1,z1),N2(x2,y2,z2),…,N k (x k y k , z k )};

[0046] like Figure 2 As shown, the specific details for determining the blade surface nodes before fluid-structure-thermal coupling are as follows: the impeller blade profile is divided into several blade sections by several cross sections, and each blade section includes the intersection line between the blade working surface and the blade section and the intersection line between the blade back surface and the blade section; the control point of each intersection line is a node on the blade surface.

[0047] S05: Simulation yields the coordinate set Y of the nodal deformation of the blade surface after fluid-structure-thermal coupling. k {ΔN1(Δx1,Δy1,Δz1),ΔN2(Δx2,Δy2,Δz2),…,ΔN k (Δx k Δy k Δz k )};

[0048] S06: Set the coordinates of nodal deformation on the blade surface after fluid-structure-thermal coupling, Y k The nodal coordinate set X of the blade surface before fluid-structure-thermal coupling k Adding them together, we obtain the corrected set of blade surface nodal coordinates:

[0049] X' k {N'1(x'1,y'1,z'1),N'2(x'2,y'2,z'2),…,N' k (x' k ,y' k ,z' k )},

[0050] Where: N' k (x' k ,y' k ,z' k ) = N k (x k ,y k ,z k )+ΔN k (Δx k ,Δy k ,Δz k );

[0051] S07: Based on the corrected blade surface nodal coordinate set X' k The flow path components are reconstructed to obtain the corrected hydraulic model; the flow field of the corrected hydraulic model is simulated to obtain the thermal efficiency η2;

[0052] S08: If the hot hydraulic efficiency η2 ≥ the cold hydraulic efficiency η1, then the corrected hydraulic model is the optimized hydraulic model; if the hot hydraulic efficiency η2 < the cold hydraulic efficiency η1, then return to S01 and adjust at least one parameter of the geometric parameters, and perform a loop solution. Generally, adjusting one parameter means increasing or decreasing one parameter of the geometric parameters by no more than 2%.

[0053] However, multiple parameters can also be adjusted: if the hot hydraulic efficiency η2 < the cold hydraulic efficiency η1, then return to S01 to adjust the blade inlet angle β1 and blade outlet angle β2 in the geometric parameters, and satisfy the following relationship: 0.54(β1+Δβ1)≤(β2+Δβ2)<0.65(β1+Δβ1), where Δβ1 is the adjustment amount of the blade inlet angle and Δβ2 is the adjustment amount of the blade outlet angle;

[0054] When the adjusted blade inlet angle β1 and blade outlet angle β2 satisfy the following relationship: 0.65(β1+Δβ1)≤(β2+Δβ2)<0.9(β1+Δβ1), adjust the blade wrap angle in the geometric parameters. And satisfy the following relationship:

[0055] in This is the adjustment amount for the blade wrap angle.

[0056] Example 1

[0057] The design parameters of a certain nuclear main pump model are: flow rate Q = 1049 m³ / s. 3 With a speed of n = 1485 r / min and a head of H = 14.9 m, the impeller hydraulics were optimized to meet the requirements of high temperature and high pressure conditions.

[0058] S01: Determine the target variable for the optimization design as flow rate Q = 1049 m³ / s. 3 The impeller has a head of H = 14.9 m, a rotational speed of n = 1485 r / min, and an efficiency of η = 81%. An initial cold-state hydraulic model was obtained through simulation at room temperature. The geometric parameters obtained from this model are: impeller outer diameter D2 = 278 mm, blade thickness ξ = 4 mm, blade inlet angle β1 = 54.8°, blade outlet angle β2 = 20°, and blade wrap angle.

[0059] S02: Based on geometric parameter modeling and finite element mesh generation, define the material properties of the flow components in the hydraulic model, and obtain the cold efficiency η1 = 82% from CFD flow field simulation;

[0060] S03: When the cold efficiency η1≥η, the hydraulic model based on geometric parameters is the optimal solution;

[0061] S04: After fluid-structure-thermal coupling calculations, the coordinate set X of the blade surface nodes before fluid-structure-thermal coupling is determined based on the model's mesh. k {N1(x1,y1,z1),N2(x2,y2,z2),…,N k (x k y k , z k )};

[0062] S05: Simulation yields the coordinate set Y of the nodal deformation of the blade surface after fluid-structure-thermal coupling. k {ΔN1(Δx1,Δy1,Δz1),ΔN2(Δx2,Δy2,Δz2),…,ΔN k (Δx k Δy k Δz k )};

[0063] S06: Set the coordinates of nodal deformation on the blade surface after fluid-structure-thermal coupling, Y k The nodal coordinate set X of the blade surface before fluid-structure-thermal coupling k Adding them together yields the corrected set of blade surface nodal coordinates X'. k ;

[0064] S07: Based on the corrected blade surface nodal coordinate set X' k The flow components were reconstructed to obtain a corrected hydraulic model; flow field simulation of the corrected hydraulic model yielded a thermal efficiency η2 = 85%;

[0065] like Figure 4 As shown, since the hot efficiency η2 is greater than the cold efficiency η1, the current scheme is the final model, that is, the efficiency of the cold model is improved in actual operation. Therefore, the geometric parameters of the cold model are output.

[0066] Example 2

[0067] The design parameters of a certain nuclear main pump model are: flow rate Q = 1049 m³ / s. 3 With a speed of n = 1485 r / min and a head of H = 14.9 m, the impeller hydraulics were optimized to meet the requirements of high temperature and high pressure conditions.

[0068] S01: Determine the target variable for the optimization design as flow rate Q = 1049 m³ / s. 3 The impeller has a head of H = 14.9 m, a rotational speed of n = 1485 r / min, and an efficiency of η = 81%. An initial cold-state hydraulic model was obtained through simulation at room temperature. The geometric parameters obtained from this model are: impeller outer diameter D2 = 278 mm, blade thickness ξ = 4 mm, blade inlet angle β1 = 24°, blade outlet angle β2 = 16°, and blade wrap angle.

[0069] S02: Based on geometric parameter modeling and finite element mesh generation, the cold efficiency η1 = 78% is obtained by CFD flow field simulation; if the cold efficiency η1 < η, then return to S01 to adjust the blade inlet angle β1 and blade outlet angle β2 in the geometric parameters.

[0070] If Δβ1 is -1.5 and Δβ2 is 1, then the adjusted blade inlet angle β1' = 22.5° and the adjusted blade outlet angle β2' = 17°. Since 0.65β1′ < β2′ < 0.9β1′, then... The value is 5, which satisfies the condition. The adjusted blade wrap angle φ = 105°;

[0071] S03: Recalculate the cold efficiency η1 = 81.5% > η = 81%, then the hydraulic model based on geometric parameters is the optimal solution;

[0072] S04: Define the material properties of the flow components in the hydraulic model, and determine the nodal coordinate set X of the blade surface before fluid-structure-thermal coupling based on the model's mesh. k {N1(x1,y1,z1),N2(x2,y2,z2),…,N k (x k y k , z k )};

[0073] S05: Simulation yields the coordinate set Y of the nodal deformation of the blade surface after fluid-structure-thermal coupling. k {ΔN1(Δx1,Δy1,Δz1),ΔN2(Δx2,Δy2,Δz2),…,ΔN k (Δx k Δy k Δz k )};

[0074] S06: Set the coordinates of nodal deformation on the blade surface after fluid-structure-thermal coupling, Y k The nodal coordinate set X of the blade surface before fluid-structure-thermal coupling k Adding them together yields the corrected set of blade surface nodal coordinates X'. k ;

[0075] S07: Based on the corrected blade surface nodal coordinate set X' k The flow components were reconstructed to obtain a corrected hydraulic model; flow field simulation of the corrected hydraulic model yielded a thermal efficiency η2 = 80%;

[0076] S08: Since the hot hydraulic efficiency η2 = 80% < the cold hydraulic efficiency η1 = 81.5%, return to S01 to readjust the geometric parameters and perform a loop solution; readjust the blade inlet angle β1 and blade outlet angle β2 in the geometric parameters again;

[0077] If Δβ1 is -2.2 and Δβ2 is 1, then the adjusted blade inlet angle β1' = 20.3° and the adjusted blade outlet angle β2' = 18°. Since 0.65β1′ < β2′ < 0.9β1′, then... The value is 5, which satisfies the condition. The adjusted blade wrap angle φ = 105°;

[0078] S09: Based on geometric parameter modeling and finite element mesh generation, the calculated cold efficiency η1 = 85% > η = 81% obtained by CFD flow field simulation is the optimal solution;

[0079] Repeat: S04~S06.

[0080] S10: Based on the corrected blade surface nodal coordinate set X' k The flow path components were reconstructed to obtain the corrected hydraulic model; the flow field simulation of the corrected hydraulic model yielded a thermal efficiency η2 = 85.5%;

[0081] Since the hot efficiency η2 is greater than the cold efficiency η1, the current scheme is the final model. That is, the efficiency of the cold model is improved in actual operation, so the geometric parameters of the cold model are output.

[0082] A nuclear main pump, wherein the impeller blades are optimized using the aforementioned nuclear main pump cold and hot state compensation impeller blade hydraulic optimization method.

[0083] A nuclear main pump cold / hot state compensation impeller blade hydraulic optimization system includes a storage medium; the storage medium stores a program written using the nuclear main pump cold / hot state compensation impeller blade hydraulic optimization method described in this invention. The storage medium includes a hard disk, CD-ROM, optical storage device, magnetic storage device, or a combination thereof. Those skilled in the art will understand that the various features described herein can be implemented by methods, data processing systems, or computer program products. Therefore, these features can be implemented entirely in hardware, entirely in software, or in a combination of hardware and software. Furthermore, the above features can also be implemented as a computer program product stored on one or more computer-readable storage media, which contains computer-readable program code segments or instructions stored in the storage medium. Any usable computer-readable storage medium can be used, including hard disks, CD-ROMs, optical storage devices, magnetic storage devices, and / or combinations thereof.

[0084] It should be understood that although this specification is described according to various embodiments, not every embodiment contains only one independent technical solution. This way of describing the specification is only for clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment can also be appropriately combined to form other implementation methods that can be understood by those skilled in the art.

[0085] The detailed descriptions listed above are merely specific illustrations of feasible embodiments of the present invention and are not intended to limit the scope of protection of the present invention. All equivalent embodiments or modifications made without departing from the spirit of the present invention should be included within the scope of protection of the present invention.

Claims

1. A method for hydraulic optimization of impeller blades under cold and hot conditions in a nuclear main pump, characterized in that, Includes the following steps: S01: The target variables for optimization design are determined as flow rate Q, head H, rotational speed n, and efficiency η; an initial cold-state hydraulic model is obtained through simulation at room temperature. The geometric parameters obtained from the initial cold-state hydraulic model are: impeller outer diameter D2, blade thickness ξ, blade inlet angle β1, blade outlet angle β2, and blade wrap angle. S02: Based on geometric parameter modeling and finite element mesh generation, define the material properties of the flow components in the hydraulic model, and obtain the cold efficiency η1 from the flow field simulation; if the cold efficiency η1 < η, then return to S01 and adjust the value of at least one parameter in the geometric parameters. S03: When the cold efficiency η1≥η, the hydraulic model based on geometric parameters is the optimal solution; S04: determining a blade surface node coordinate set X before fluid-structure-thermal coupling according to a grid of the model k {N1(x1, y1, z1), N2(x2, y2, z2), …, N k (x k , y k , z k )}; S05: Simulation yields the coordinate set Y of the nodal deformation of the blade surface after fluid-structure-thermal coupling. k {△N1(△x1, △y1, △z1), △N2(△x2, △y2, △z2), ..., △N k (△x k , △y k , △z k )}; S06: Set the coordinates of nodal deformation on the blade surface after fluid-structure-thermal coupling, Y k The nodal coordinate set X of the blade surface before fluid-structure-thermal coupling k Adding them together, we obtain the corrected set of blade surface nodal coordinates: X′ k {N′1(x′1,y′1,z′1),N′2(x′2,y′2,z′2),…,N′ k (x′ k ,y′ k ,z′ k )}, wherein: N′ k (x′ k , y′ k , z′ k )=N k (x k , y k , z k )+△N k (△x k , △y k , △z k ); S07: Based on the corrected blade surface nodal coordinate set X′ k The flow path components are reconstructed to obtain the corrected hydraulic model; the flow field of the corrected hydraulic model is simulated to obtain the thermal efficiency η2; S08: If the hot hydraulic efficiency η2 ≥ the cold hydraulic efficiency η1, then the corrected hydraulic model is the optimized hydraulic model; if the hot hydraulic efficiency η2 < the cold hydraulic efficiency η1, then return to S01 and adjust at least one parameter of the geometric parameters, and perform a loop solution.

2. The method for hydraulic optimization of impeller blades under cold and hot conditions for nuclear main pumps according to claim 1, characterized in that, The specific details of the blade surface nodes before fluid-structure-thermal coupling are as follows: The impeller blade profile is divided into several blade sections by several cross sections. Each blade section includes the intersection line between the blade working surface and the blade section and the intersection line between the blade back surface and the blade section; the control point of each intersection line is a node on the blade surface.

3. The method for hydraulic optimization of impeller blades under cold and hot conditions for nuclear main pumps according to claim 1, characterized in that, If the cold efficiency η1 < η, then return to S01 and increase or decrease one of the geometric parameters by no more than 5%.

4. The method for hydraulic optimization of impeller blades under cold and hot conditions for nuclear main pumps according to claim 1, characterized in that, If the hot hydraulic efficiency η2 < the cold hydraulic efficiency η1, then return to S01 and increase or decrease one of the geometric parameters by no more than 2%.

5. The method for hydraulic optimization of impeller blades under cold and hot conditions for nuclear main pumps according to claim 1, characterized in that, If the cold-state efficiency η1 < η or the hot-state hydraulic efficiency η2 < the cold-state hydraulic efficiency η1, then return to S01 to adjust the blade inlet angle β1 and blade outlet angle β2 in the geometric parameters, and satisfy the following relationship: 0.54(β1+△β1)≤(β2+△β2)<0.65(β1+△β1), where △β1 is the adjustment amount of the blade inlet angle and △β2 is the adjustment amount of the blade outlet angle.

6. The method for hydraulic optimization of impeller blades under cold and hot conditions for nuclear main pumps according to claim 5, characterized in that, When the adjusted blade inlet angle β1 and blade outlet angle β2 satisfy the following relationship: 0.65(β1+△β1)≤(β2+△β2)<0.9(β1+△β1), adjust the blade wrap angle in the geometric parameters. And satisfy the following relationship: in This is the adjustment amount for the blade wrap angle.

7. A nuclear main pump, characterized in that, The impeller blades of the nuclear main pump are optimized using the hydraulic optimization method for cold and hot state compensation according to any one of claims 1-6.

8. A hydraulic optimization system for compensating for cold and hot conditions of a nuclear main pump impeller blade, characterized in that, Includes a storage medium; the storage medium stores a program written using the hydraulic optimization method for cold and hot state compensation of impeller blades of the nuclear main pump according to any one of claims 1-6.

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