Multi-blade centrifugal fan design method and system based on flow control

Abstract

The invention discloses a multi-blade centrifugal fan design method and system based on flow control, and relates to the technical field of centrifugal fan design. The method comprises the following steps that structural parameters of a centrifugal fan are obtained; modeling an impeller of the centrifugal fan according to the structural parameters to obtain flow velocity distribution; and determining the blade profile of the centrifugal fan according to the flow velocity distribution. According to the method, the design structure parameters of the centrifugal fan are determined, the working data of the impeller of the centrifugal fan are calculated according to the structure parameters, flow velocity distribution modeling is conducted on the impeller part of the centrifugal fan, and after flow velocity distribution is obtained, the optimal blade molded line is selected to conduct optimization design on the centrifugal fan; it is guaranteed that gas efficiently flows in the impeller of the centrifugal fan, and the operation performance of the centrifugal fan is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of centrifugal fan design, and in particular to a multi-blade centrifugal fan design method and system based on flow control. Background Art

[0002] Multi-blade centrifugal fans are widely used in various industries due to their high number of blades, compact size, high pressure coefficient, large flow coefficient, and low noise. However, their impellers, characterized by a large impeller diameter ratio, short flow passages, wide blades, and large blade outlet angles and curvatures, can easily lead to complex flow phenomena such as separation flow, resulting in poor performance.

[0003] Due to the complex impeller structure of the multi-blade centrifugal fan, the existing improvement on flow separation is to optimize the design of the acceleration channel or volute for one blade type, and lacks the selection and optimization design of the blade profile of the multi-blade centrifugal fan. Summary of the Invention

[0004] The purpose of the present invention is to provide a multi-blade centrifugal fan design method and system based on flow control. The present invention determines the structural parameters of the centrifugal fan design, calculates the working data at the centrifugal fan impeller according to the structural parameters, models the flow velocity distribution of the impeller part of the centrifugal fan, and after obtaining the flow velocity distribution, selects the optimal blade profile to optimize the design of the centrifugal fan, thereby ensuring that the gas flows efficiently in the centrifugal fan impeller and improving the operating performance of the centrifugal fan.

[0005] The purpose of the present invention is achieved by the following technical means: In a first aspect, the present invention provides a method for designing a multi-blade centrifugal fan based on flow control, comprising the following steps: Obtain the structural parameters of the centrifugal fan; Modeling the impeller of the centrifugal fan according to the structural parameters to obtain a flow velocity distribution; According to the flow velocity distribution, the blade profile of the centrifugal fan is determined.

[0006] Preferably, the structural parameters include: rotational speed, flow rate, blade thickness, number of blades, inlet airflow direction angle, outlet airflow direction angle, inlet diameter, outlet diameter, inlet width and outlet width.

[0007] Preferably, the modeling of the impeller of the centrifugal fan according to the structural parameters to obtain the flow velocity distribution comprises the following steps: Calculating the relative flow velocity at the impeller inlet and the relative flow velocity at the impeller outlet according to the structural parameters; Calculating the maximum speed-increasing relative flow velocity of the impeller according to the structural parameters, the inlet relative flow velocity, and the outlet relative flow velocity; Calculating the unknown coefficient of the flow velocity distribution according to the inlet relative flow velocity, the outlet relative flow velocity and the maximum speed-increasing relative flow velocity; The calculation formula of the flow velocity distribution is expressed as follows: , in, is the flow velocity distribution, , , is the undetermined coefficient, is the radial position coordinate of the impeller.

[0008] Preferably, the calculation formula of the inlet relative flow rate is expressed as follows: , in, is the relative flow velocity at the inlet, is the rotation speed, For traffic, is the inlet velocity coefficient, is the inlet meridian velocity, is the inlet airflow direction angle, , , is the unknown coefficient, is the radial position coordinate at the inlet; The calculation formula of the outlet relative flow rate is expressed as follows: , in, is the relative flow velocity at the outlet, is the exit meridian velocity, is the outlet airflow direction angle, , , is the unknown coefficient, is the radial position coordinate at the exit; The calculation formula of meridian velocity is as follows: , in, is the radial position coordinate of the impeller The meridian velocity, For traffic, is the radial position coordinate of the impeller The diameter of is the radial position coordinate of the impeller The width, is the radial position coordinate of the impeller The flow rate coefficient.

[0009] Preferably, the calculating of the maximum speed-increasing relative flow velocity of the impeller according to the structural parameters, the inlet relative flow velocity and the outlet relative flow velocity comprises the following steps: Calculating an acceleration rate according to the inlet relative flow velocity and the outlet relative flow velocity; Calculate the average of the inlet diameter and outlet diameter to obtain the radial position coordinates of the maximum speed increase; Calculating a maximum speed-increasing ratio according to the radial position coordinates of the maximum speed-increasing point and the speed-increasing rate; Calculating a maximum speed-up relative flow velocity according to the maximum speed-up ratio and the inlet relative flow velocity; The calculation formula of the growth rate is as follows: , in, is the growth rate, is the relative flow velocity at the outlet, is the inlet relative flow velocity; The calculation formula of the maximum speed-increasing relative flow rate is as follows: , in, is the relative flow velocity with maximum acceleration, is the maximum speed-up ratio, is the relative flow velocity at the inlet, is the radial position coordinate of the maximum speed increase point.

[0010] Preferably, determining the blade profile of the centrifugal fan according to the flow velocity distribution comprises the following steps: Calculating the airflow direction angle according to the flow velocity distribution; Determining the blade profile of the centrifugal fan according to the airflow direction angle; The calculation formula of the airflow direction angle is expressed as follows: , in, is the radial position coordinate of the impeller The airflow direction angle, is the radial position coordinate of the impeller The meridian velocity, is the radial position coordinate of the impeller The relative flow rate, is the leaf thickness, is the number of leaves, is the radial position coordinate of the impeller diameter.

[0011] In some embodiments, determining the blade profile of the centrifugal fan according to the flow velocity distribution further includes the following steps: Calculating a boundary layer thickness based on the blade profile and the flow velocity distribution of the centrifugal fan; Comparing the boundary layer thicknesses and selecting the blade profile corresponding to the minimum boundary layer; determining whether boundary layer separation occurs in the minimum boundary layer; When boundary layer separation occurs in the minimum boundary layer, removing the blade profile corresponding to the minimum boundary layer and reselecting the minimum boundary layer; When boundary layer separation does not occur in the minimum boundary layer, the blade profile corresponding to the minimum boundary layer is selected.

[0012] In a second aspect, the present invention provides a multi-blade centrifugal fan design system based on flow control, which applies the above-mentioned multi-blade centrifugal fan design method based on flow control, including: a structural parameter acquisition module, a flow velocity distribution modeling module and a blade profile determination module; The structural parameter acquisition module acquires the structural parameters of the centrifugal fan; The flow velocity distribution modeling module models the impeller of the centrifugal fan according to the structural parameters to obtain the flow velocity distribution; The blade profile determination module determines the blade profile of the centrifugal fan according to the flow velocity distribution.

[0013] In a third aspect, the present invention provides an electronic device comprising a processor and a memory, wherein the memory is used to store computer program code, and the computer program code comprises computer instructions. When the processor executes the computer instructions, the electronic device executes the above-mentioned multi-blade centrifugal fan design method based on flow control.

[0014] In a fourth aspect, the present invention provides a computer-readable storage medium, in which a computer program is stored. The computer program includes program instructions, and when the program instructions are executed by a processor of an electronic device, the processor executes the above-mentioned multi-blade centrifugal fan design method based on flow control.

[0015] Compared with the prior art, the present invention has the following beneficial effects: The present invention determines the structural parameters of the centrifugal fan design, calculates the working data of the centrifugal fan impeller according to the structural parameters, models the flow velocity distribution of the impeller part of the centrifugal fan, selects the optimal blade profile after obtaining the flow velocity distribution, optimizes the design of the centrifugal fan, ensures that the gas flows efficiently in the centrifugal fan impeller, and improves the operating performance of the centrifugal fan. The present invention calculates the relative flow velocity at the impeller inlet, the relative flow velocity at the impeller outlet, and the relative flow velocity at the impeller's maximum speed increase, and models the flow velocity distribution based on the calculated relative flow velocity data, thereby improving the accuracy of the flow velocity distribution modeling and providing a data basis for subsequent centrifugal fan design. The present invention unifies the radial position coordinates of the maximum speed-increasing position of various centrifugal fans, simplifies the impeller flow path of the centrifugal fan, calculates the radial position coordinates of the maximum speed-increasing position based on the inlet diameter and outlet diameter, and thus calculates the maximum speed-increasing relative flow velocity, thereby reducing the difficulty of flow velocity distribution modeling and providing a data basis for subsequent flow velocity distribution modeling. The present invention calculates the airflow direction angle at each impeller position based on the flow velocity distribution, converts the airflow direction angle to obtain the blade profile, and obtains the optimal blade profile in a specific acceleration flow channel, thereby ensuring that the gas flows efficiently in the centrifugal fan impeller and improving the operating performance of the centrifugal fan. The present invention selects the blade profile according to the thickness of the boundary layer, and at the same time, performs boundary layer separation detection on the blade profile to select the optimal blade profile that meets the design, thereby ensuring high-efficiency flow of gas in the centrifugal fan impeller and improving the operating performance of the centrifugal fan. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and, together with the description, serve to explain the principles of the invention.

[0017] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, for ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative labor.

[0018] Figure 1 A schematic flow chart of a multi-blade centrifugal fan design method based on flow control provided in this embodiment; Figure 2 In step S2 provided in this embodiment, the impeller of the centrifugal fan is modeled according to the structural parameters to obtain a flow diagram of the flow velocity distribution; Figure 3 Step S22 provided in this embodiment is a flow chart of calculating the maximum speed-increasing relative flow velocity of the impeller based on the structural parameters, the inlet relative flow velocity, and the outlet relative flow velocity; Figure 4 Step S3 of this embodiment provides a flow chart of determining the blade profile of the centrifugal fan according to the flow velocity distribution; Figure 5A schematic structural diagram of a multi-blade centrifugal fan design system based on flow control provided in this embodiment; Figure 6 This is a schematic structural diagram of an electronic device provided in this embodiment. DETAILED DESCRIPTION

[0019] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. All other embodiments obtained by ordinary technicians in this field based on the embodiments of the present invention without making any creative efforts shall fall within the scope of protection of the present invention.

[0020] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative position relationship and movement status of various components in a certain specific posture. If the specific posture changes, the directional indication will also change accordingly.

[0021] In addition, the descriptions of "first", "second", etc. in the present invention are for descriptive purposes only and should not be understood as indicating or implying their relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" or "second" may explicitly or implicitly include at least one of such features. In addition, the technical solutions between the various embodiments can be combined with each other, but this must be based on the fact that they can be implemented by ordinary technicians in this field. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0022] Example 1 This embodiment provides a multi-blade centrifugal fan design method based on flow control, such as Figure 1 As shown, the following steps are included: S1, obtaining the structural parameters of the centrifugal fan; S2, model the impeller of the centrifugal fan according to the structural parameters to obtain the flow velocity distribution; S3. Determine the blade profile of the centrifugal fan based on the flow velocity distribution.

[0023] It should be noted that when designing a multi-blade centrifugal fan, it is necessary to determine the fan's structural parameters. Based on these parameters, the fan's acceleration flow path and blade profile are designed. Structural parameters are the primary parameters of the centrifugal fan and the impeller. In some embodiments, these parameters include: rotational speed, flow rate, blade thickness, number of blades, inlet airflow direction angle, outlet airflow direction angle, inlet diameter, outlet diameter, inlet width, and outlet width. The values ​​of a centrifugal fan's structural parameters must satisfy multiple constraints. In this embodiment, after determining the range of values ​​for the structural parameters and obtaining multiple sets of structural parameters, the multi-blade centrifugal fan is optimized based on these parameters. The blade profile refers to the cross-sectional shape of the blades in a centrifugal fan, which determines the flow characteristics of gas passing through the blades. Optimizing the blade profile design helps improve energy conversion efficiency and enhance the efficiency of the multi-blade centrifugal fan. Therefore, this embodiment designs the blade profile of the centrifugal fan based on the flow of gas in the impeller.

[0024] In this embodiment, by determining the structural parameters of the centrifugal fan design, calculating the working data at the centrifugal fan impeller based on the structural parameters, the flow velocity distribution of the impeller part of the centrifugal fan is modeled, and after obtaining the flow velocity distribution, the optimal blade profile is selected to optimize the design of the centrifugal fan, thereby ensuring that the gas flows efficiently in the centrifugal fan impeller and improving the operating performance of the centrifugal fan.

[0025] In some embodiments, in step S2, the impeller of the centrifugal fan is modeled according to the structural parameters to obtain the flow velocity distribution, such as Figure 2 As shown, the following steps are included: S21, calculating the relative flow velocity at the impeller inlet and the relative flow velocity at the impeller outlet according to the structural parameters; S22, calculating the maximum speed-increasing relative velocity of the impeller according to the structural parameters, the inlet relative velocity, and the outlet relative velocity; S23, calculating the unknown coefficient of the velocity distribution according to the inlet relative velocity, the outlet relative velocity, and the maximum speed-increasing relative velocity; The calculation formula of flow velocity distribution is as follows: , in, is the flow velocity distribution, , , is the unknown coefficient, is the radial position coordinate of the impeller.

[0026] In some embodiments, the calculation formula of the inlet relative flow rate is expressed as follows: , in, is the relative flow velocity at the inlet, is the rotation speed, For traffic, is the inlet velocity coefficient, is the inlet meridian velocity, is the inlet airflow direction angle, , , is the unknown coefficient, is the radial position coordinate at the inlet; The calculation formula of the relative flow rate at the outlet is as follows: , in, is the relative flow velocity at the outlet, is the exit meridian velocity, is the outlet airflow direction angle, , , is the undetermined coefficient, is the radial position coordinate at the exit; The calculation formula of the meridian velocity is as follows: , in, is the radial position coordinate of the impeller The meridian velocity, For traffic, is the radial position coordinate of the impeller The diameter of is the radial position coordinate of the impeller The width, is the radial position coordinate of the impeller The flow rate coefficient.

[0027] It should be noted that the velocity modeling of the impeller's acceleration channel is performed using a polynomial curve. This polynomial curve involves a total of three unknowns of the highest binary value, and therefore requires three independent equations to calculate the unknown coefficients. This embodiment solves the problem by calculating the relative flow velocity at the inlet, the relative flow velocity at the outlet, and the relative flow velocity at the radial position coordinate at the point of maximum acceleration.

[0028] Specifically, the inlet flow velocity coefficient is calculated based on the inlet diameter, number of blades, blade thickness and inlet airflow direction angle; the inlet meridional velocity is calculated based on the flow rate, inlet diameter, inlet width and inlet flow velocity coefficient; and the inlet relative flow velocity is calculated based on the rotational speed, flow rate, inlet flow velocity coefficient, inlet meridional velocity and inlet gas direction angle.

[0029] The outlet flow velocity coefficient is calculated based on the outlet diameter, number of blades, blade thickness and outlet airflow direction angle. The outlet meridional velocity is calculated based on the flow rate, outlet diameter, outlet width and outlet flow velocity coefficient. The outlet relative flow velocity is calculated based on the outlet meridional velocity and outlet gas direction angle.

[0030] In this embodiment, by calculating the relative flow velocity at the impeller inlet, the relative flow velocity at the impeller outlet and the relative flow velocity at the maximum speed increase of the impeller, the flow velocity distribution is modeled according to the calculated relative flow velocity data, thereby improving the accuracy of the flow velocity distribution modeling and providing a data basis for subsequent centrifugal fan design.

[0031] In some embodiments, step S22 calculates the maximum speed-increasing relative velocity of the impeller according to the structural parameters, the inlet relative velocity and the outlet relative velocity, such as Figure 3 As shown, the following steps are included: S221, calculating the growth rate according to the inlet relative flow velocity and the outlet relative flow velocity; S222, calculating the average of the inlet diameter and the outlet diameter to obtain the radial position coordinates of the maximum speed increase point; S223, calculating the maximum speed-increasing ratio according to the radial position coordinates and the speed-increasing rate at the maximum speed-increasing point; S224, calculating the maximum speed-up relative flow velocity based on the maximum speed-up ratio and the inlet relative flow velocity; The calculation formula of the growth rate is as follows: , in, is the growth rate, is the relative flow velocity at the outlet, is the inlet relative flow velocity; The calculation formula of the maximum speed increase relative to the flow velocity is as follows: , in, is the relative flow velocity with maximum acceleration, is the maximum speed-up ratio, is the relative flow velocity at the inlet, is the radial position coordinate of the maximum speed increase point.

[0032] It should be noted that, in addition to optimizing the blade profile according to different structural parameters, this embodiment can also optimize the blade profiles of different acceleration channel types with the same structural parameters. Taking into account the multiple structural parameters and multiple acceleration channels, the impeller structure needs to be simplified. Therefore, the median of the inlet diameter and the outlet diameter is uniformly used as the radial position coordinate of the maximum speed increase point. By calculating the speed increase rate and the radial position coordinate of the maximum speed increase point, the speed increase rate and the radial position coordinate of the maximum speed increase point are input into the preset acceleration channel type for machine calculation to obtain the maximum speed increase ratio under the acceleration channel type, thereby calculating the maximum speed increase relative flow rate.

[0033] In this embodiment, by unifying the radial position coordinates of the maximum speed increase points of various centrifugal fans, simplifying the impeller flow path of the centrifugal fan, and calculating the radial position coordinates of the maximum speed increase point based on the inlet diameter and outlet diameter, the relative flow velocity of the maximum speed increase is calculated, thereby reducing the difficulty of flow velocity distribution modeling and providing a data basis for subsequent flow velocity distribution modeling.

[0034] In some embodiments, step S3, based on the flow velocity distribution, the blade profile of the centrifugal fan is determined, such as Figure 4 As shown, the following steps are included: S31, calculating the airflow direction angle according to the flow velocity distribution; S32, determining a blade profile of the centrifugal fan according to the airflow direction angle; The calculation formula of the airflow direction angle is as follows: , in, is the radial position coordinate of the impeller The airflow direction angle, is the radial position coordinate of the impeller The meridian velocity, is the radial position coordinate of the impeller The relative flow rate, is the leaf thickness, is the number of leaves, is the radial position coordinate of the impeller diameter.

[0035] It should be noted that the velocity distribution can be used to obtain the relative velocity at a specific location in the impeller, and the airflow direction angle at a specific location can be inferred based on the velocity triangle. Specifically, the diameter of the location where the airflow direction angle is to be calculated is obtained, and the relative flow velocity at the location to be calculated is calculated based on the velocity distribution and the diameter of the location to be calculated. The meridional velocity at the location to be calculated is calculated based on the flow rate, the diameter of the location to be calculated, and the width of the location to be calculated. The airflow direction angle at the location to be calculated is calculated based on the meridional velocity at the location to be calculated, the relative flow velocity at the location to be calculated, the blade thickness, the number of blades, and the diameter of the location to be calculated. After obtaining the airflow direction angles at all locations, the airflow direction angles are converted to obtain the blade profile of the centrifugal fan.

[0036] In this embodiment, the airflow direction angle at each position of the impeller is calculated based on the flow velocity distribution, and the airflow direction angle is converted to obtain the blade profile, so as to obtain the optimal blade profile in a specific acceleration flow channel, thereby ensuring that the gas flows efficiently in the centrifugal fan impeller and improving the operating performance of the centrifugal fan.

[0037] In some embodiments, step S3, based on the flow velocity distribution, the blade profile of the centrifugal fan is determined, such as Figure 4 As shown, the following steps are also included: S33, calculating the boundary layer thickness based on the blade profile and flow velocity distribution of the centrifugal fan; S34, comparing the boundary layer thicknesses and selecting the blade profile corresponding to the minimum boundary layer; S35, determining whether boundary layer separation occurs in the minimum boundary layer; S36, when boundary layer separation occurs in the minimum boundary layer, remove the blade profile corresponding to the minimum boundary layer and reselect the minimum boundary layer; S37, when the minimum boundary layer does not undergo boundary layer separation, selecting a blade profile corresponding to the minimum boundary layer.

[0038] It should be noted that this embodiment optimizes the blade profile design for different acceleration channel types with the same structural parameters. The goal is to select the optimal acceleration channel and blade profile for that acceleration channel. Under the same structural parameters, different acceleration channel types will result in different flow velocity distributions and blade profiles. Therefore, it is necessary to evaluate the blade profile and select the appropriate blade profile. The boundary layer refers to a thin layer formed by viscosity when gas flows adjacent to the impeller blade surface. The gas velocity within the boundary layer gradually increases from zero velocity at the contact point with the blade surface to the velocity in the outer mainstream area. The thickness of the boundary layer affects the state and efficiency of the gas flow. An excessively thick boundary layer can cause flow separation, thereby reducing the efficiency and performance of the centrifugal fan. Therefore, this embodiment calculates the boundary layer thickness based on the blade profile and flow velocity distribution, and evaluates the blade profile based on the boundary layer thickness. Specifically, the boundary layer thickness is calculated based on the blade profile and flow velocity distribution calculated for different preset acceleration channel types, and the blade profile with the smallest boundary layer thickness is selected. This calculation process is conventional and will not be described in detail here. The minimum boundary layer is tested for boundary layer separation. If boundary layer separation occurs, the blade profile data is removed and a new minimum boundary layer is selected from the remaining blade profiles. If boundary layer separation does not occur, the blade profile is selected for centrifugal fan design. In certain embodiments, the friction coefficient and momentum thickness of the centrifugal fan can be calculated based on the boundary layer thickness and the Reynolds number. When the friction coefficient is very low and close to zero and the momentum thickness of the boundary layer is very large and exceeds a preset threshold, it can be determined that boundary layer separation has occurred.

[0039] In this embodiment, the blade profile is selected according to the size of the boundary layer thickness. At the same time, the boundary layer separation detection is performed on the blade profile to select the optimal blade profile that meets the design, thereby ensuring that the gas flows efficiently in the centrifugal fan impeller and improving the operating performance of the centrifugal fan.

[0040] Example 2 This embodiment provides a multi-blade centrifugal fan design system based on flow control, which applies the above-mentioned multi-blade centrifugal fan design method based on flow control, such as Figure 5 As shown, it includes: a structural parameter acquisition module, a flow velocity distribution modeling module and a blade profile determination module; A structural parameter acquisition module is used to obtain the structural parameters of the centrifugal fan; The flow velocity distribution modeling module is used to model the impeller of the centrifugal fan according to the structural parameters to obtain the flow velocity distribution; The blade profile determination module is used to determine the blade profile of the centrifugal fan according to the flow velocity distribution.

[0041] In this embodiment, by determining the structural parameters of the centrifugal fan design, calculating the working data at the centrifugal fan impeller based on the structural parameters, the flow velocity distribution of the impeller part of the centrifugal fan is modeled, and after obtaining the flow velocity distribution, the optimal blade profile is selected to optimize the design of the centrifugal fan, thereby ensuring that the gas flows efficiently in the centrifugal fan impeller and improving the operating performance of the centrifugal fan.

[0042] It should be understood that the disclosed system can be implemented in other ways. For example, the system embodiments described above are merely illustrative. For example, the division of the above modules is merely a logical functional division. In actual implementation, there may be other division methods. For example, multiple modules or components may be combined or integrated into another system, or some features may be ignored or not executed. In addition, each functional module may be integrated into a processing module, or each module may exist physically separately, or two or more modules may be integrated into one module. The above-mentioned integrated modules may be implemented in the form of hardware or in the form of software functional modules.

[0043] Example 3 This embodiment provides an electronic device 2, such as Figure 6 As shown, a processor 21 and a memory 22, the memory 22 is used to store computer program code, the computer program code includes computer instructions, when the processor 21 executes the computer instructions, the electronic device executes the above-mentioned multi-blade centrifugal fan design method based on flow control.

[0044] The electronic device 2 includes a processor 21, a memory 22, an output device 23, and an input device 24. The processor 21, memory 22, output device 23, and input device 24 are coupled via a connector, which may include various interfaces, transmission lines, or buses, etc., although this is not limited in the present embodiment. It should be understood that in various embodiments of the present invention, coupling refers to interconnection in a specific manner, including direct connection or indirect connection through other devices, such as various interfaces, transmission lines, buses, etc.

[0045] The processor 21 may be one or more graphics processing units (GPUs). If the processor 21 is a GPU, the GPU may be a single-core GPU or a multi-core GPU. Alternatively, the processor 21 may be a processor group consisting of multiple GPUs, with the multiple processors coupled to each other via one or more buses. Alternatively, the processor 21 may be other types of processors, and the embodiments of the present invention are not limited thereto.

[0046] The memory 22 can be used to store computer program instructions and various computer program codes, including program codes for executing the solutions of the present invention. Optionally, the memory 22 includes, but is not limited to, random access memory (RAM), read-only memory (ROM), erasable programmable read-only memory (EPROM), or compact disc read-only memory (CD-ROM). The memory 22 is used for related instructions and data.

[0047] The input device 24 is used to input data and / or signals, and the output device 23 is used to output data and / or signals. The output device 23 and the input device 24 can be independent devices or an integrated device.

[0048] This embodiment provides a computer-readable storage medium, in which a computer program is stored. The computer program includes program instructions. When the program instructions are executed by a processor of an electronic device, the processor executes the above-mentioned multi-blade centrifugal fan design method based on flow control.

[0049] The foregoing description is intended only to provide specific embodiments of the present invention, which will enable those skilled in the art to understand and implement the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not intended to be limited to the embodiments shown herein, but is intended to be accorded the widest scope consistent with the principles and novel features claimed herein.

Claims

1. A multi-blade centrifugal fan design method based on flow control, characterized in that: The following steps are involved: Obtain the structural parameters of the centrifugal fan; Modeling the impeller of the centrifugal fan according to the structural parameters to obtain a flow velocity distribution; determining a blade profile of the centrifugal fan according to the flow velocity distribution; The impeller of the centrifugal fan is modeled according to the structural parameters to obtain a flow velocity distribution, comprising the following steps: Calculating the relative flow velocity at the impeller inlet and the relative flow velocity at the impeller outlet according to the structural parameters; Calculating the maximum speed-increasing relative flow velocity of the impeller according to the structural parameters, the inlet relative flow velocity, and the outlet relative flow velocity; The undetermined coefficient of the flow velocity distribution is calculated according to the inlet relative flow velocity, the outlet relative flow velocity and the maximum speed-increasing relative flow velocity.

2. The method for designing a multi-blade centrifugal fan based on flow control according to claim 1, characterized in that: The structural parameters include: rotation speed, flow rate, blade thickness, number of blades, inlet airflow direction angle, outlet airflow direction angle, inlet diameter, outlet diameter, inlet width and outlet width.

3. The method for designing a multi-blade centrifugal fan based on flow control according to claim 1, characterized in that: The calculation formula of the flow velocity distribution is expressed as follows: ， in, is the flow velocity distribution, , , is the unknown coefficient, is the radial position coordinate of the impeller, that is, the radial distance from the center of the impeller.

4. The method for designing a multi-blade centrifugal fan based on flow control according to claim 3, characterized in that: The calculation formula of the inlet relative flow rate is expressed as follows: ， in, is the relative flow velocity at the inlet, is the rotation speed, For traffic, is the inlet velocity coefficient, is the inlet meridian velocity, is the inlet airflow direction angle, , , is the undetermined coefficient, is the radial position coordinate at the inlet; The calculation formula of the outlet relative flow rate is expressed as follows: ， in, is the relative flow velocity at the outlet, is the exit meridian velocity, is the outlet airflow direction angle, , , is the undetermined coefficient, is the radial position coordinate at the exit; The calculation formula of the meridian velocity is as follows: ， in, is the radial position coordinate of the impeller The meridian velocity, For traffic, is the radial position coordinate of the impeller The diameter of is the radial position coordinate of the impeller The width, is the radial position coordinate of the impeller The flow rate coefficient.

5. The method for designing a multi-blade centrifugal fan based on flow control according to claim 3, characterized in that: Calculating the maximum speed-increasing relative flow velocity of the impeller according to the structural parameters, the inlet relative flow velocity, and the outlet relative flow velocity comprises the following steps: Calculating an acceleration rate according to the inlet relative flow velocity and the outlet relative flow velocity; Calculate the average of the inlet diameter and outlet diameter to obtain the radial position coordinates of the maximum speed increase; Calculating a maximum speed-increasing ratio according to the radial position coordinates of the maximum speed-increasing point and the speed-increasing rate; Calculating a maximum speed-up relative flow velocity according to the maximum speed-up ratio and the inlet relative flow velocity; The calculation formula of the growth rate is as follows: ， in, is the growth rate, is the relative flow velocity at the outlet, is the inlet relative flow velocity; The calculation formula of the maximum speed-increasing relative flow rate is as follows: ， in, is the relative flow velocity with maximum acceleration, is the maximum speed-up ratio, is the relative flow velocity at the inlet, is the radial position coordinate of the maximum speed increase point.

6. The method for designing a multi-blade centrifugal fan based on flow control according to claim 1, characterized in that: Determining the blade profile of the centrifugal fan according to the flow velocity distribution includes the following steps: Calculating the airflow direction angle according to the flow velocity distribution; Determining the blade profile of the centrifugal fan according to the airflow direction angle; The calculation formula of the airflow direction angle is expressed as follows: ， in, is the radial position coordinate of the impeller The airflow direction angle, is the radial position coordinate of the impeller The meridian velocity, is the radial position coordinate of the impeller The relative flow rate, is the leaf thickness, is the number of leaves, is the radial position coordinate of the impeller diameter.

7. The method for designing a multi-blade centrifugal fan based on flow control according to claim 1, characterized in that: Determining the blade profile of the centrifugal fan according to the flow velocity distribution further includes the following steps: Calculating a boundary layer thickness based on the blade profile and the flow velocity distribution of the centrifugal fan; Comparing the boundary layer thicknesses and selecting the blade profile corresponding to the minimum boundary layer; determining whether boundary layer separation occurs in the minimum boundary layer; When boundary layer separation occurs in the minimum boundary layer, removing the blade profile corresponding to the minimum boundary layer and reselecting the minimum boundary layer; When boundary layer separation does not occur in the minimum boundary layer, the blade profile corresponding to the minimum boundary layer is selected.

8. A multi-blade centrifugal fan design system based on flow control, applying a multi-blade centrifugal fan design method based on flow control according to any one of claims 1 to 7, characterized in that: include: Structural parameter acquisition module, velocity distribution modeling module and blade profile determination module; The structural parameter acquisition module acquires the structural parameters of the centrifugal fan; The flow velocity distribution modeling module models the impeller of the centrifugal fan according to the structural parameters to obtain the flow velocity distribution; The blade profile determination module determines the blade profile of the centrifugal fan according to the flow velocity distribution.

9. An electronic device, characterized in that: The electronic device comprises a processor and a memory, wherein the memory is used to store computer program code, and the computer program code comprises computer instructions. When the processor executes the computer instructions, the electronic device executes a multi-blade centrifugal fan design method based on flow control as described in any one of claims 1 to 7.

10. A computer-readable storage medium, characterized in that The computer-readable storage medium stores a computer program, which includes program instructions. When the program instructions are executed by a processor of an electronic device, the processor executes a multi-blade centrifugal fan design method based on flow control as described in any one of claims 1 to 7.

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