A design method of integrated impeller for high-speed centrifugal pump

Abstract

The application provides a high-speed centrifugal pump integrated impeller design method, and belongs to the technical field of centrifugal pump impeller design. The method comprises the following steps: designing an integrated impeller according to the working condition of a high-speed centrifugal pump; using a mesh generation tool to divide the designed integrated impeller into meshes, and performing mesh independence test to obtain integrated impeller meshes; performing numerical simulation according to the integrated impeller meshes to obtain simulation steady data and cavitation data of the integrated impeller; judging whether the simulation steady data and cavitation data of the integrated impeller meet the working condition, if not, optimizing the integrated impeller based on a grey wolf algorithm and using a numerical control programming tool, and then performing mesh division and working condition meeting judgment again, if yes, outputting the integrated impeller to complete the high-speed centrifugal pump integrated impeller design. The application improves the cavitation resistance of the high-speed centrifugal pump and the lift of the high-speed centrifugal pump, and maintains the safe and stable operation of the high-speed centrifugal pump.

Description

Technical Field

[0001] This invention belongs to the field of centrifugal pump impeller design technology, and particularly relates to an integrated impeller design method for high-speed centrifugal pumps. Background Technology

[0002] An integrated impeller is a structural design that combines an inducer impeller and a centrifugal impeller. This design offers significant advantages in improving pump performance and efficiency. First, the integrated impeller design increases the impeller inlet pressure, ensuring higher cavitation resistance. Due to the action of the inducer blades, the fluid is pre-pressurized before entering the centrifugal impeller, which helps improve the overall pump's cavitation resistance. Furthermore, the integrated design avoids the connection and fit issues between traditional separate impellers, reducing energy loss and thus significantly improving impeller efficiency. Second, the integrated impeller has a more compact structure, allowing for a smaller overall pump size, saving space and material costs. Simultaneously, by reducing the number of components, this design also helps lower pump manufacturing and maintenance costs.

[0003] There is a close relationship between cavitation and impeller profile. The design of the impeller profile directly affects the flow state of the fluid within the impeller, thus influencing the occurrence and development of cavitation. The impeller profile design determines the flow path and velocity distribution of the fluid within the impeller. A reasonable profile design can make the fluid flow more smoothly within the impeller, reducing flow separation and vortex phenomena. The geometric parameters of the impeller profile, such as the shape, angle, and number of blades, all affect cavitation characteristics. For example, the blade back slope angle is one of the important parameters affecting cavitation performance. Studies have shown that increasing the blade back slope angle within a certain range can improve the cavitation performance of high-speed centrifugal pumps. This is because increasing the back slope angle can change the flow state at the blade inlet, making the angle of attack when the fluid enters the impeller more reasonable and reducing the occurrence of cavitation. However, when the back slope angle exceeds a certain range, the cavitation performance will decrease. The design of the impeller profile also affects the distribution and development of cavitation phenomena.

[0004] The integrated profile structure helps to reduce the inlet velocity of the fluid, increase the inlet pressure, and enhance the pump's anti-cavitation characteristics. In terms of fluid dynamics performance, the integrated impeller also performs well. Its complex profile design enables multi-stage pressurization of the fluid and stabilizes the flow channel. This design can also effectively reduce the flow loss of the fluid in the impeller and further improve the pump's performance.

[0005] However, existing high-speed centrifugal pump impellers suffer from low cavitation resistance and low head. Therefore, designing a suitable integrated impeller design method is of great significance for the stable operation of high-speed centrifugal pumps against cavitation. Summary of the Invention

[0006] To address the aforementioned shortcomings in existing technologies, this invention provides an integrated impeller design method for high-speed centrifugal pumps, which solves the problems of low cavitation resistance and low head in existing high-speed centrifugal pumps.

[0007] To achieve the above objectives, the technical solution adopted by this invention is: a method for designing an integrated impeller for a high-speed centrifugal pump, comprising the following steps:

[0008] S1. Based on the operating conditions of the high-speed centrifugal pump, a preliminary design of the integrated impeller is carried out;

[0009] S2. Using a mesh generation tool, the designed integrated impeller is meshed, and mesh independence is checked to obtain the integrated impeller mesh.

[0010] S3. Based on the integrated impeller mesh, numerical simulation is performed using fluid dynamics calculation tools to obtain the simulated steady-state data and cavitation data of the integrated impeller;

[0011] S4. Based on the simulated steady-state data and cavitation data of the integrated impeller, determine whether it meets the operating conditions. If not, optimize the integrated impeller using CNC programming tools based on the Grey Wolf algorithm and return to step S2. If yes, output the integrated impeller and complete the design of the high-speed centrifugal pump integrated impeller.

[0012] The beneficial effects of this invention are as follows: This invention achieves better external characteristics and anti-cavitation characteristics by initially designing a universal integrated impeller and then numerically simulating the initially designed integrated impeller. Furthermore, it quantifies the blade profile and blade length of the integrated impeller, adopts different combination types for different working conditions, and uses mesh independence verification to reduce the amount of calculation, making the calculation of the method of this invention more accurate and faster. This improves the anti-cavitation capability and head of the high-speed centrifugal pump, and maintains the safe and stable operation of the high-speed centrifugal pump.

[0013] Further, S1 includes the following steps:

[0014] S101. Based on the operating conditions of the high-speed centrifugal pump, design the long blades of the integrated impeller, including the inlet flow coefficient, blade tip diameter, inlet liquid flow angle, inlet blade installation angle, outlet blade installation angle, outlet width, number of blades, blade tip wrap angle, and blade thickness, to complete the initial design of the long blades of the integrated impeller.

[0015] S102. Based on the operating conditions of the high-speed centrifugal pump, design an integrated impeller short blade, including the inlet flow angle, inlet installation angle, outlet installation angle, outlet width, and thickness of the short blade, to complete the integrated impeller short blade design.

[0016] S103. Combining the integrated impeller long blade design and the integrated impeller short blade design, a preliminary integrated impeller design is obtained.

[0017] Furthermore, step S101 includes the following steps:

[0018] S1011. Based on the operating conditions of the high-speed centrifugal pump, the inlet flow coefficient of the long blade is obtained using the cavitation coefficient calculation formula, and the blade tip diameter of the long blade is obtained based on the inlet flow coefficient of the long blade.

[0019] S1012. Based on the inlet flow coefficient of the long blade, the variable pitch design method is adopted to design the inlet flow angle, inlet long blade installation angle, outlet long blade installation angle, and outlet width of the long blade.

[0020] S1013. Design the integrated impeller as a conical impeller, set the inlet hub ratio and cone angle of the long blades, select the number of long blades of the integrated impeller based on the inlet hub ratio and cone angle, and obtain the blade density.

[0021] S1014. Calculate the pitch based on the number of long blades and the tip diameter of the long blades, and calculate the outer diameter of the leading edge of the long blade inlet based on the hub ratio of the long blade inlet and the tip diameter of the long blade.

[0022] S1015. Define the leading edge wrap angle of the long blade. Using the integrated impeller blade unfolded length and axial length calculation formula, combined with the blade consistency and pitch, determine the total wrap angle of the long blade and calculate the blade tip wrap angle of the long blade.

[0023] S1016. Set the first thickness of the leading edge of the long blade, and set the second thickness at 30% to 40% of the blade chord length. Based on the first and second thicknesses of the long blade, obtain the thickness of the long blade and complete the initial design of the integrated impeller long blade.

[0024] Furthermore, the formula for calculating the cavitation coefficient of the long blade is as follows:

[0025]

[0026] Where σ represents the cavitation coefficient of long blades, β represents the inlet flow coefficient of the long blade. in Indicates the installation angle of the imported long blade, α in Indicates the angle of attack of the liquid flow at the inlet of the long blade;

[0027] The formula for calculating the exit width of the long blade is as follows:

[0028]

[0029] R = 0.25(1 + R)in )D i

[0030] Among them, b out n represents the exit width of the long blade. s The variable R represents the specific speed of the integrated impeller, H represents the head of the integrated impeller, n represents the rotational speed of the integrated impeller, and R represents the outer diameter of the leading edge of the long blade inlet. in D represents the inlet hub ratio of long blades. i This indicates the diameter of the leaf tip of a long leaf.

[0031] Furthermore, the formula for calculating the total wrap angle of the long blade is as follows:

[0032] θ t =θ-θ q

[0033]

[0034]

[0035] Where, θ t θ represents the leaf tip wrap angle of a long leaf, and θ represents the total wrap angle of a long leaf. q τ represents the leading edge wrap angle of the long blade, τ represents the blade density, t represents the pitch, l represents the unfolded length of the long blade, and D represents the blade width. i The z represents the diameter of the leaf tip of the long blade, and the z represents the number of long blades. It means that β in Indicates the installation angle of the imported long blade, β out The angle of the long blade at the outlet is indicated by L, and the axial length is indicated by L.

[0036] Furthermore, the integrated impeller long blade design specifically includes:

[0037] The inlet flow coefficient of the long blade is 0.05 to 0.1, the tip diameter of the long blade is 40 mm to 72 mm, the inlet flow angle of the long blade is 0° to 5°, the outlet blade installation angle is 40° to 60°, the inlet hub ratio of the long blade is 0.13 to 0.3, the cone angle is 10° to 15°, the number of long blades is selected as 2 or 3, the leading edge wrap angle of the long blade is 40° to 160°, the first thickness of the leading edge of the long blade is 0.3 mm to 0.5 mm, and the second thickness is 1.5 mm to 2.5 mm at 30% to 40% of the blade chord length.

[0038] The integrated impeller short blade design is specifically as follows:

[0039] The short blade inlet flow angle is 5° to 15°, the short blade inlet installation angle is 15° to 25°, the short blade outlet installation angle is 40° to 60°, and the short blade thickness is 1.5mm to 2.5mm.

[0040] The formula for calculating the exit width of the short blade is as follows:

[0041]

[0042] Among them, b out ′ represents the exit width of the short blade, n s The specific speed of the integrated impeller is represented by H, the head of the integrated impeller is represented by n, and the rotational speed of the integrated impeller is represented by n.

[0043] The beneficial effects of the above-mentioned further solutions are as follows: This invention designs a universal integrated impeller design method. By quantifying the blade profile and the length of the blades of the integrated impeller, different combination types are adopted for different working conditions. The important parameters of the blades of the integrated impeller are calculated, and an initial integrated impeller design with improved centrifugal pump efficiency and strong anti-cavitation performance is obtained.

[0044] Furthermore, S3 specifically refers to:

[0045] The integrated impeller mesh was imported into a fluid dynamics calculation tool, and the inlet and outlet boundary conditions of the high-speed centrifugal pump were set using the fluid dynamics calculation tool according to the operating conditions of the high-speed centrifugal pump. Numerical simulation was then performed to obtain the simulated steady-state data and cavitation data of the integrated impeller.

[0046] The beneficial effects of the above-mentioned further solutions are as follows: the present invention uses numerical simulation method to evaluate the external characteristics of the integrated impeller, which facilitates the prediction of the performance of the designed integrated impeller and reduces the workload of experiments.

[0047] Furthermore, in step S4, the specific steps for optimizing the integrated impeller using CNC programming tools are as follows:

[0048] The CNC programming tool is used to edit and obtain multiple tool bodies, which are then grouped into a tool body group. The tool body group is prioritized and marked to obtain a pre-processed tool body group.

[0049] Taking the integrated impeller as the target body, based on the pre-processed tool body group, the target body is surrounded by the pre-processed tool bodies, and iterative optimization is performed to obtain the position vector of each tool body and the position vector of the target body. The distance between the position of each tool body and the position of the target body is calculated.

[0050] In each iteration, the three best tool bodies in the current tool body group are retained as the best tool bodies, and the positions of the tool bodies other than the best tool bodies are updated to obtain the position information of the current candidate tool bodies.

[0051] In response to reaching the maximum number of iterations, the optimal target body is obtained based on the position information of the current candidate tool body, and the optimal integrated impeller is output, thus completing the optimization of the integrated impeller.

[0052] Furthermore, the mathematical model expression for the iterative optimization is as follows:

[0053] X(t+1)=X p (t)-A*D

[0054] D = C * X p (txt)

[0055] A = 2a*r1 - a, C = 2r2

[0056] Where t represents the current iteration number, X(t+1) represents the position vector of the tool body in the (t+1)th iteration, X p X(t) represents the position vector of the target body in the t-th iteration, X(t) represents the position vector of the tool body in the t-th iteration, * represents the Hadamard product, A and C both represent the synergy coefficient vectors, D represents the distance between the tool body position and the target body position, a represents the convergence factor, which linearly decreases from 2 to 0, and r1 and r2 represent random vectors in [0,1].

[0057] Furthermore, the mathematical model expression for updating the position of the tool body is as follows:

[0058] X(t+1)=(X1+X2+X3) / 3

[0059] X1 = X α -A1*D α X2 = X β -A2*D β X3 = X δ -A3*D δ

[0060] D α =C1*X α -X,D β =C2*X β -X,D δ =C3*X δ -X

[0061] Where X(t+1) represents the position vector of the tool body in the (t+1)th iteration, X1 represents the position vector of target body 1, X2 represents the position vector of target body 2, X3 represents the position vector of target body 3, and X... α D represents the position vector of the first optimal tool body α. α X represents the distance between the first optimal tool body α and the candidate tool bodies. βD represents the position vector of the second optimal tool body β. β X represents the distance between the second optimal tool body β and the candidate tool bodies. δ D represents the position vector of the third optimal tool body δ. δ Let δ represent the distance between the third optimal tool body and the candidate tool bodies. A1, A2, A3 and C1, C2, C3 all represent the coordination coefficient vectors, and X represents the position vector of the candidate tool body.

[0062] The beneficial effects of the above-mentioned further solutions are as follows: The present invention uses the gray wolf algorithm to optimize the integrated impeller blades, which makes the blade optimization effect better, the optimization speed faster, and the optimization index more directional, resulting in an integrated impeller that improves the anti-cavitation capability and head of the high-speed centrifugal pump, and maintains the safe and stable operation of the high-speed centrifugal pump. Attached Figure Description

[0063] Figure 1 This is a flowchart of the method of the present invention. Detailed Implementation

[0064] The specific embodiments of the present invention are described below to enable those skilled in the art to understand the present invention. However, it should be understood that the present invention is not limited to the scope of the specific embodiments. For those skilled in the art, various changes are obvious as long as they are within the spirit and scope of the present invention as defined and determined by the appended claims. All inventions utilizing the concept of the present invention are protected.

[0065] Before describing this embodiment, the following terms will be explained:

[0066] TurboGrid: A professional software for creating meshes for turbine blade cascade channels;

[0067] CFD: Computational Fluid Dynamics;

[0068] CFX: A software tool for computational fluid dynamics;

[0069] Hadamard product operation: Hadamard product operation.

[0070] Example

[0071] like Figure 1 As shown, this invention provides a method for designing an integrated impeller for a high-speed centrifugal pump, the implementation of which is as follows:

[0072] S1. Based on the operating conditions of the high-speed centrifugal pump, a preliminary design of the integrated impeller is carried out, specifically as follows:

[0073] S101. Based on the operating conditions of the high-speed centrifugal pump, design the integrated impeller long blades, including the inlet flow coefficient, blade tip diameter, inlet flow angle of attack, inlet blade installation angle, outlet blade installation angle, outlet width, number of blades, blade tip wrap angle, and blade thickness. Complete the initial design of the integrated impeller long blades, specifically as follows:

[0074] S1011. Based on the operating conditions of the high-speed centrifugal pump, the inlet flow coefficient of the long blade is obtained using the cavitation coefficient calculation formula, and the blade tip diameter of the long blade is obtained based on the inlet flow coefficient of the long blade.

[0075] S1012. Based on the inlet flow coefficient of the long blade, the variable pitch design method is adopted to design the inlet flow angle, inlet long blade installation angle, outlet long blade installation angle, and outlet width of the long blade.

[0076] S1013. Design the integrated impeller as a conical impeller, set the inlet hub ratio and cone angle of the long blades, select the number of long blades of the integrated impeller based on the inlet hub ratio and cone angle, and obtain the blade density.

[0077] S1014. Calculate the pitch based on the number of long blades and the tip diameter of the long blades, and calculate the outer diameter of the leading edge of the long blade inlet based on the hub ratio of the long blade inlet and the tip diameter of the long blade.

[0078] S1015. Define the leading edge wrap angle of the long blade. Using the integrated impeller blade unfolded length and axial length calculation formula, combined with the blade consistency and pitch, determine the total wrap angle of the long blade and calculate the blade tip wrap angle of the long blade.

[0079] S1016. Set the first thickness of the leading edge of the long blade, and set the second thickness at 30% to 40% of the blade chord length. Based on the first and second thicknesses of the long blade, obtain the thickness of the long blade and complete the initial design of the integrated impeller long blade.

[0080] S102. Based on the operating conditions of the high-speed centrifugal pump, design an integrated impeller short blade, including the inlet flow angle, inlet installation angle, outlet installation angle, outlet width, and thickness of the short blade, to complete the integrated impeller short blade design.

[0081] S103. Combining the integrated impeller long blade design and the integrated impeller short blade design, a preliminary integrated impeller design is obtained.

[0082] In this embodiment, based on the existing operating conditions of high-speed centrifugal pumps, a preliminary design of the integrated impeller is carried out, adopting a design of 3 long blades + 3 short blades or 2 long blades + 4 short blades, as detailed below:

[0083] Integrated impeller with long blade design: To ensure good cavitation performance of the integrated impeller, the cavitation coefficient σ of the long blades should be taken as a small value. Therefore, according to the calculation formula of the cavitation coefficient of the long blades, the inlet flow coefficient of the long blades is taken as... And based on the inlet flow coefficient of the long blade The diameter of the leaf tip of the long leaf is D. i =40mm~72mm;

[0084] The formula for calculating the cavitation coefficient of the long blade is as follows:

[0085]

[0086] Where σ represents the cavitation coefficient of long blades, β represents the inlet flow coefficient of the long blade. in Indicates the installation angle of the imported long blade, α in Indicates the angle of attack of the liquid flow at the inlet of the long blade;

[0087] The long blades employ a variable pitch design, with an inlet flow angle α of 200°. in =0°~5°, installation angle β of imported long blades in Based on the formula and the inlet flow coefficient of the long blade, the outlet long blade installation angle is 40°≤β. out ≤60°, long blade exit width b out It is calculated based on the specific speed of the integrated impeller, the specific speed of the integrated impeller, and the speed of the integrated impeller.

[0088] The formula for calculating the exit width of the long blade is as follows:

[0089]

[0090] Among them, b out n represents the exit width of the long blade. s The specific speed of the integrated impeller is represented by H, the head of the integrated impeller is represented by n, and the rotational speed of the integrated impeller is represented by n.

[0091] The integrated impeller is designed as a conical impeller with long blades and an inlet hub ratio R. in =0.13~0.3, cone angle γ is 10°~15°; when 2 long blades are selected for the integrated impeller, the blade density τ=2; when 3 long blades are selected for the integrated impeller, the blade density τ=3; leading edge wrap angle θ of the long blade q=40°~160°, the total wrap angle of the long blades of the integrated impeller is calculated by the formula of the blade unfolded length and axial length of the integrated impeller, combined with the blade density and pitch. The first thickness of the leading edge of the long blade is 0.3mm~0.5mm, and the second thickness of 1.5mm~2.5mm is set at 30%~40% of the blade chord length.

[0092] The formula for calculating the outer diameter of the leading edge of the long blade inlet is as follows:

[0093] R = 0.25(1 + R) in )D i

[0094] R represents the outer diameter of the leading edge of the long blade inlet. in D represents the inlet hub ratio of long blades. i Indicates the diameter of the leaf tip of a long leaf;

[0095] The formula for calculating the total wrap angle of the long blade is as follows:

[0096] θ t =θ-θ q

[0097]

[0098] Where, θ t θ represents the leaf tip wrap angle of a long leaf, and θ represents the total wrap angle of a long leaf. q τ represents the leading edge wrap angle of the long blade, τ represents the blade density, t represents the pitch, l represents the unfolded length of the long blade, and D represents the blade width. i The z represents the diameter of the leaf tip of the long blade, and the z represents the number of long blades. It means that β in Indicates the installation angle of the imported long blade, β out The angle of the long blade at the outlet is indicated, and L represents the axial length.

[0099] In this embodiment, the integrated impeller short blade design is as follows:

[0100] The short blade inlet flow angle is 5° to 15°, the short blade inlet installation angle is 15° to 25°, the short blade outlet installation angle is 40° to 60°, and the short blade thickness is 1.5mm to 2.5mm.

[0101] The formula for calculating the exit width of the short blade is as follows:

[0102]

[0103] Among them, b out ′ represents the exit width of the short blade, n s The specific speed of the integrated impeller is represented by H, the head of the integrated impeller is represented by n, and the rotational speed of the integrated impeller is represented by n.

[0104] S2. Using a mesh generation tool, the designed integrated impeller is meshed, and mesh independence is checked to obtain the integrated impeller mesh.

[0105] In this embodiment, the TurboGrid mesh generation tool is used to divide the designed integrated impeller into a mesh and perform a mesh independence test to obtain the integrated impeller mesh.

[0106] S3. Based on the integrated impeller mesh, numerical simulation is performed using fluid dynamics calculation tools to obtain the simulated steady-state data and cavitation data of the integrated impeller, specifically:

[0107] The integrated impeller mesh was imported into a fluid dynamics calculation tool, and the inlet and outlet boundary conditions of the high-speed centrifugal pump were set using the fluid dynamics calculation tool according to the operating conditions of the high-speed centrifugal pump. Numerical simulation was then performed to obtain the simulated steady-state data and cavitation data of the integrated impeller.

[0108] In this embodiment, CFD flow field numerical simulation is performed. The integrated impeller mesh is imported into the fluid dynamics calculation tool, CFX software. Based on the operating conditions of the high-speed centrifugal pump, the inlet and outlet boundary conditions of the high-speed centrifugal pump are set using the fluid dynamics calculation tool CFX software to complete the numerical simulation and obtain the simulated steady-state data and cavitation data of the integrated impeller.

[0109] S4. Based on the simulated steady-state data and cavitation data of the integrated impeller, determine whether it meets the operating conditions. If not, optimize the integrated impeller using CNC programming tools based on the Grey Wolf algorithm and return to step S2. If yes, output the integrated impeller and complete the design of the high-speed centrifugal pump integrated impeller.

[0110] The specific steps for optimizing the integrated impeller using CNC programming tools are as follows:

[0111] The CNC programming tool is used to edit and obtain multiple tool bodies, which are then grouped into a tool body group. The tool body group is prioritized and marked to obtain a pre-processed tool body group.

[0112] Taking the integrated impeller as the target body, based on the pre-processed tool body group, the target body is surrounded by the pre-processed tool bodies, and iterative optimization is performed to obtain the position vector of each tool body and the position vector of the target body. The distance between the position of each tool body and the position of the target body is calculated.

[0113] In each iteration, the three best tool bodies in the current tool body group are retained as the best tool bodies, and the positions of the tool bodies other than the best tool bodies are updated to obtain the position information of the current candidate tool bodies.

[0114] In response to reaching the maximum number of iterations, the optimal target body is obtained based on the position information of the current candidate tool body, and the optimal integrated impeller is output, thus completing the optimization of the integrated impeller.

[0115] In this embodiment, based on the simulated steady-state data and cavitation data of the integrated impeller, it is determined whether the operating conditions are met. If not, the integrated impeller is optimized using a CNC programming tool based on the Grey Wolf algorithm, and the process returns to step S2. If yes, the integrated impeller is output, and the design of the integrated impeller for the high-speed centrifugal pump is completed.

[0116] Integrated impeller optimization process:

[0117] Multiple tool bodies are obtained through editing using CNC programming tools and grouped into a tool body group. The tool bodies are then prioritized and labeled α, β, δ, and ω from top to bottom. α represents the optimal tool body, followed by β and δ tool bodies, with ω being the least preferred. The optimization process is guided by tool bodies α, β, and δ, while ω only follows the instructions of other higher-level tool bodies, resulting in a pre-processed tool body group.

[0118] Taking the integrated impeller as the target body, iterative optimization is performed by surrounding the target body with tool body. The mathematical model expression of the iterative optimization is as follows:

[0119] X(t+1)=X p (t)-A*D

[0120] D = C * X p (txt)

[0121] A = 2a*r1 - a

[0122] C = 2r²

[0123] Where t represents the current iteration number, X(t+1) represents the position vector of the tool body in the (t+1)th iteration, X p X(t) represents the position vector of the target body in the t-th iteration, X(t) represents the position vector of the tool body in the t-th iteration, * represents the Hadamard product operation, A and C both represent the coordination coefficient vectors, D represents the distance between the tool body position and the target body position, a represents the convergence factor, and r1 and r2 represent random vectors in [0,1]. During the construction of the optimization target body, the decrease in the value of a will cause the value of A to fluctuate accordingly; where a decreases linearly from 2 to 0 during the iteration process.

[0124] In each iteration, the three best tool bodies in the current tool body group are retained: the first best tool body α1, the second best tool body β1, and the third best tool body δ1. The positions of the tool bodies other than the best tool bodies are updated to obtain the position information of the current candidate tool bodies.

[0125] In response to reaching the maximum number of iterations, the optimal target body is obtained based on the position information of the current candidate tool body, and the optimal integrated impeller is output, thus completing the optimization of the integrated impeller;

[0126] The mathematical model expression for updating the position of the tool body is as follows:

[0127] X(t+1)=(X1+X2+X3) / 3

[0128] X1 = X α -A1*D α X2 = X β -A2*D β X3 = X δ -A3*D δ

[0129] D α =C1*X α -X,D β =C2*X β -X,D δ =C3*X δ -X

[0130] Where X(t+1) represents the position vector of the tool body in the (t+1)th iteration, X1 represents the position vector of target body 1, X2 represents the position vector of target body 2, X3 represents the position vector of target body 3, and X... α D represents the position vector of the tool body α. α X represents the distance between tool body α and the optimal tool body. β D represents the position vector of the tool body β. β X represents the distance between tool body β and the optimal tool body. δ D represents the position vector of the tool body δ. δ Let δ represent the distance between the tool body and the optimal tool body, and let A1, A2, A3, C1, C2, C3 all represent the coordination coefficient vectors, and let X represent the position vector of the candidate tool body;

[0131] When |A|>1, the tool bodies are distributed as widely as possible across different regions to search for the target body. When |A|<1, the tool bodies will focus on searching for the target body in one or more regions. When A is in the interval [-1,1], the next position of the search agent can be anywhere between the current tool body and the target body.

[0132] In this embodiment, the integrated induced impeller designed by the present invention has significant advantages in improving pump efficiency, cavitation resistance, structural compactness, and machining accuracy. It is a high-efficiency pump impeller design that is worth promoting.

Claims

1. A method for designing an integrated impeller for a high-speed centrifugal pump, characterized in that, Includes the following steps: S1. Based on the operating conditions of the high-speed centrifugal pump, a preliminary design of the integrated impeller is carried out. The specific steps are as follows: S101. Based on the operating conditions of the high-speed centrifugal pump, design the long blades of the integrated impeller. Design the inlet flow coefficient, blade tip diameter, inlet flow angle, inlet blade installation angle, outlet blade installation angle, outlet width, number of blades, blade tip wrap angle, and blade thickness of the long blades to complete the initial design of the long blades of the integrated impeller. The specific steps are as follows: S1011. Based on the operating conditions of the high-speed centrifugal pump, the inlet flow coefficient of the long blade is obtained using the cavitation coefficient calculation formula, and the blade tip diameter of the long blade is obtained based on the inlet flow coefficient of the long blade. S1012. Based on the inlet flow coefficient of the long blade, the variable pitch design method is adopted to design the inlet flow angle, inlet long blade installation angle, outlet long blade installation angle, and outlet width of the long blade. S1013. Design the integrated impeller as a conical impeller, set the inlet hub ratio and cone angle of the long blades, select the number of long blades of the integrated impeller based on the inlet hub ratio and cone angle, and obtain the blade density. S1014. Calculate the pitch based on the number of long blades and the tip diameter of the long blades, and calculate the outer diameter of the leading edge of the long blade inlet based on the hub ratio of the long blade inlet and the tip diameter of the long blade. S1015. Define the leading edge wrap angle of the long blade. Using the integrated impeller blade unfolded length and axial length calculation formula, combined with the blade consistency and pitch, determine the total wrap angle of the long blade and calculate the blade tip wrap angle of the long blade. S1016. Set the first thickness of the leading edge of the long blade, and set the second thickness at 30%~40% of the blade chord length. Based on the first and second thicknesses of the long blade, obtain the thickness of the long blade and complete the initial design of the long blade of the integrated impeller. S102. Based on the operating conditions of the high-speed centrifugal pump, design an integrated impeller short blade, including the inlet flow angle, inlet installation angle, outlet installation angle, outlet width, and thickness of the short blade, to complete the integrated impeller short blade design. S103. Combining the integrated impeller long blade design and the integrated impeller short blade design, a preliminary integrated impeller design is obtained; S2. Using a mesh generation tool, the designed integrated impeller is meshed, and mesh independence is checked to obtain the integrated impeller mesh. S3. Based on the integrated impeller mesh, numerical simulation is performed using fluid dynamics calculation tools to obtain the simulated steady-state data and cavitation data of the integrated impeller; S4. Based on the simulated steady-state data and cavitation data of the integrated impeller, determine whether it meets the operating conditions. If not, optimize the integrated impeller using CNC programming tools based on the Grey Wolf algorithm and return to step S2. If yes, output the integrated impeller and complete the design of the high-speed centrifugal pump integrated impeller.

2. The integrated impeller design method for high-speed centrifugal pumps according to claim 1, characterized in that, The formula for calculating the cavitation coefficient of the long blade is as follows: in, This represents the cavitation coefficient of long blades. This represents the inlet flow rate coefficient for long blades. Indicates the installation angle of the imported long blades. Indicates the angle of attack of the liquid flow at the inlet of the long blade; The formula for calculating the exit width of the long blade is as follows: in, Indicates the width of the long blade exit. This indicates the specific speed of the integrated impeller. Indicates the head of the integrated impeller. This indicates the rotational speed of the integrated impeller. Indicates the outer diameter of the leading edge of the long blade inlet. Indicates the inlet hub ratio of long blades. This indicates the diameter of the leaf tip of a long leaf.

3. The integrated impeller design method for high-speed centrifugal pumps according to claim 2, characterized in that, The formula for calculating the total wrap angle of the long blade is as follows: ， in, Indicates the leaf tip wrap angle of long leaves. Indicates the total wrap angle of the long blade. Indicates the leading edge wrap angle of long blades. Indicates the density of sage. Indicates pitch, Indicates the unfolded length of the long blade. Indicates the diameter of the leaf tip of a long leaf. Indicates the number of long blades. express, Indicates the installation angle of the imported long blades. Indicates the installation angle of the long blade at the outlet. Indicates axial length.

4. The integrated impeller design method for high-speed centrifugal pumps according to claim 1, characterized in that, The integrated impeller long blade design is specifically as follows: The inlet flow coefficient of the long blade is 0.05~0.1, the blade tip diameter is 40mm~72mm, and the inlet flow angle of the long blade is... The installation angle of the long blade at the outlet is The inlet hub ratio for long blades is 0.13~0.3, and the cone angle is... The number of long leaves should be 2 or 3, and the leading edge of the long leaves should have an angle of [missing information]. The first thickness of the leading edge of the long blade is 0.3mm~0.5mm, and the second thickness is 1.5mm~2.5mm at 30%~40% of the blade chord length; The integrated impeller short blade design is specifically as follows: The angle of attack of the short blade inlet fluid flow is The short blade inlet installation angle is The short blade outlet installation angle is The thickness of the short blades is 1.5mm~2.5mm; The formula for calculating the exit width of the short blade is as follows: in, Indicates the exit width of the short blade. This indicates the specific speed of the integrated impeller. Indicates the head of the integrated impeller. This indicates the rotational speed of the integrated impeller.

5. The integrated impeller design method for high-speed centrifugal pumps according to claim 1, characterized in that, Specifically, S3 is: The integrated impeller mesh was imported into a fluid dynamics calculation tool, and the inlet and outlet boundary conditions of the high-speed centrifugal pump were set using the fluid dynamics calculation tool according to the operating conditions of the high-speed centrifugal pump. Numerical simulation was then performed to obtain the simulated steady-state data and cavitation data of the integrated impeller.

6. The integrated impeller design method for high-speed centrifugal pumps according to claim 1, characterized in that, In step S4, the specific steps for optimizing the integrated impeller using CNC programming tools are as follows: The CNC programming tool is used to edit and obtain multiple tool bodies, which are then grouped into a tool body group. The tool body group is prioritized and marked to obtain a pre-processed tool body group. Taking the integrated impeller as the target body, based on the pre-processed tool body group, the target body is surrounded by the pre-processed tool bodies, and iterative optimization is performed to obtain the position vector of each tool body and the position vector of the target body. The distance between the position of each tool body and the position of the target body is calculated. In each iteration, the three best tool bodies in the current tool body group are retained as the best tool bodies, and the positions of the tool bodies other than the best tool bodies are updated to obtain the position information of the current candidate tool bodies. In response to reaching the maximum number of iterations, the optimal target body is obtained based on the position information of the current candidate tool body, and the optimal integrated impeller is output, thus completing the optimization of the integrated impeller.

7. The integrated impeller design method for high-speed centrifugal pumps according to claim 6, characterized in that, The mathematical model expression for the iterative optimization is as follows: ， in, Indicates the current iteration number. Indicates the first The position vector of the tool body in the next iteration. Indicates the first The position vector of the target body in the next iteration. Indicates the first The position vector of the tool body in the next iteration. It represents the Hadamah accumulation. and Both represent the vector of synergy coefficients. This indicates the distance between the tool's position and the target's position. This represents the convergence factor, which decreases linearly from 2 to 0. and express Random vectors in.

8. The integrated impeller design method for high-speed centrifugal pumps according to claim 6, characterized in that, The mathematical model expression for updating the position of the tool body is as follows: ， ， ， ， in, Indicates the first The position vector of the tool body in the next iteration. This represents the position vector of target body 1. This represents the position vector of target body 2. This represents the position vector of target body 3. Represents the first optimal tool body The position vector, Represents the first optimal tool body Distance between the candidate tool body Indicates the second optimal tool body The position vector, Indicates the second optimal tool body Distance between the candidate tool body Represents the third optimal tool body The position vector, Represents the third optimal tool body Distance between the candidate tool body , , as well as , , Both represent the vector of synergy coefficients. This represents the position vector of the candidate tool body.

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