Industrial fan

Abstract

The invention discloses an industrial fan, belongs to the technical field of fans, and is designed for solving the problems that an existing fan is unreasonable in design and the like. The industrial fan comprises an impeller which comprises a sawtooth-shaped middle disc, the length of a flow channel of the impeller is larger than a set value, and the width of a steady flow area of the impeller is larger than a set value; at least two blades; the impeller and the blades which are assembled are arranged in the machine shell, and the molded line of the inner wall surface of the machine shell is matched with the airflow field of the impeller. The industrial fan comprises the impeller and the machine shell, the impeller comprises the sawtooth-shaped middle disc, airflow distribution at an outlet of the impeller can be improved, the installation angle of the blades can be conveniently designed, impact of gas on blade welding seams can be relieved, axial additional force generated by air pressure difference can be reduced, the service life of a bearing can be prolonged, and rotational inertia can be reduced. The inner wall surface molded line of the casing is matched with the airflow field of the impeller, so that the problem of large energy loss caused by turbulence of the flow field of the existing fan is solved, the flow field of the airflow reaches the optimal state, and the noise is reduced.

Description

Technical Field

[0001] This invention relates to the field of fan technology, and more particularly to industrial fans. Background Technology

[0002] Industrial fans are required to generate airflow in industries such as steel and chemicals. An industrial fan mainly consists of an impeller, blades, and a casing. The blades are mounted on the impeller and rotate synchronously with it. The impeller and blades are housed within the casing, which has an outlet. The airflow generated by the impeller driving the blades to rotate is blown out through the outlet.

[0003] Existing industrial fans have simple structures and unreasonable designs. The blade installation angle is crudely designed, resulting in uneven airflow distribution at the impeller outlet, low matching accuracy between the casing and the impeller, and turbulent flow field leading to large energy losses. Summary of the Invention

[0004] The purpose of this invention is to propose an industrial fan that solves the problem of unreasonable design of existing fans and provides a more uniform distribution of outlet airflow.

[0005] To achieve this objective, the present invention adopts the following technical solution: An industrial fan includes: an impeller with a serrated central disc, the flow channel length of the impeller being greater than a set value, and the width of the flow stabilization zone of the impeller being greater than a set value; at least two blades, all of which are evenly arranged on the outer periphery of the impeller; and a casing, in which the assembled impeller and blades are disposed, the inner wall profile of the casing being adapted to the airflow field of the impeller.

[0006] In one preferred embodiment, the inlet angle of the blade is α1 = arctan(Cm1 / U1) + i, where Cm1 is the radial velocity at the inlet (m / s), calculated based on the flow rate; U1 is the circumferential velocity at the impeller inlet (m / s), U1 = π × D1 × N / 60, N is the rotational speed; i is the angle of attack, ranging from 3° to 8°; D1 is the inner diameter of the blade, D1 = c × D2, c = 0.4-0.9; and D2 is the outer diameter of the blade, D2 = 60 × (Pt / ψρ). 0.5 / π×N, Pt is the target total pressure (Pa), ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient; the outlet angle of the blade α2 = arctan(Cm2 / (U2-C2), where Cm2 is the outlet radial velocity (m / s); C2 is the outlet tangential velocity (m / s); U2 is the impeller outlet circumferential velocity (m / s), U2 = π×D2×N / 60, N is the rotational speed, D2 = 60×(Pt / ψρ) 0.5 / π×N, Pt is the target total pressure (Pa), ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient.

[0007] In one preferred embodiment, the inlet height B1 of the blade is B1 = Q / (π × D1 × ηv × Cm1), where Q is the design flow rate (m³ / s). 3 / s); ηv is the volumetric efficiency, ranging from 0.85 to 0.95; Cm1 is the inlet radial velocity (m / s), ranging from 15m / s to 35m / s; the outlet height of the blade is B2 = Q / (π × D2 × ηv × Cm2), where Q is the design flow rate (m³ / s). 3 / s); ηv is the volumetric efficiency, ranging from 0.85 to 0.95; Cm2 is the outlet radial velocity (m / s), Cm2=(0.8-1.2)×Cm1; impeller inlet height B3=a1×B1+a2×B2, where a1 and a2 are empirical parameters.

[0008] In one preferred embodiment, the inlet diameter of the blade is DL = K × (Q / N). 1 / 3 Where K is the inlet diameter coefficient, with the value of K ranging from 4.5 to 5.0 for backward-curved blades and from 4.0 to 4.5 for forward-curved blades; Q is the design flow rate (m³ / s). 3 / s); N is the rotational speed.

[0009] In one preferred embodiment, the leading disk arc of the blade is r = R × e(θtanβ), where R is the inlet radius (m); β is the average blade tilt angle, taken as β = (β1 + β2) / 2, β1 is the inlet installation angle, and β2 is the outlet installation angle; the value of θ ranges from 0 to γ, γ is the wrap angle, γ = 180° / π × ln(D2 / D1)cot((β1 + β2) / 2), D1 is the blade inner diameter, D1 = c × D2, c = 0.4-0.9, D2 is the blade outer diameter, D2 = 60 × (Pt / ψρ)0.5 / π × N, Pt is the target total pressure (Pa), and ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient; the number of blades on the impeller is Z=2π×sinβ / ln(D2 / D1)×k1, where K1 is the correction coefficient.

[0010] In one preferred embodiment, the inlet radius of the housing is R = R1e tanf(φ，A，C,) R1 is the inlet radius correction factor.

[0011] In one preferred embodiment, the industrial fan further includes: a machine vision inspection component, including an image acquisition device, the machine vision inspection component being used to inspect the production process through machine vision to automatically identify production process steps; and a control module, connected to the machine vision inspection component to receive image information, the control module being able to construct an interlocking control model between the industrial fan and the production process through a built-in AI model, predicting the operating conditions and load of the industrial fan in advance, so as to automatically adjust the production process steps.

[0012] In one preferred embodiment, the industrial fan has a frequency conversion function.

[0013] In one preferred embodiment, the industrial fan further includes a noise monitoring device connected to the control module. The noise monitoring device is used to monitor the noise spectrum of the industrial fan in real time and send the monitoring results to the control module. The control module is used to dynamically adjust the operating parameters of the industrial fan or activate the silencing device based on the monitoring results.

[0014] In one preferred embodiment, the industrial fan further includes a control module and a parameter detection component. The control module includes: a sensing layer connected to the parameter detection component, which detects at least the airflow, pressure, temperature, vibration, rotational speed, and current of the industrial fan, and all detection results are sent to the sensing layer; a transmission layer for receiving and sending the detection results from the sensing layer; a processing layer with data storage, processing, and analysis capabilities, which receives the detection results from the transmission layer, converts the data into identification information, and stores the identification information; and an application layer for applying the identification information analyzed by the processing layer to the operation and maintenance management of the industrial fan to monitor, diagnose, and manage its operating status.

[0015] The industrial fan of this invention includes an impeller and a casing. The impeller includes a serrated central disc, which improves the airflow distribution at the impeller outlet, facilitates the design of the blade installation angle, reduces the impact of gas on the blade welds, reduces the axial additional force caused by air pressure differences, extends the bearing service life, and reduces the moment of inertia. The inner wall profile of the casing is adapted to the airflow field of the impeller, solving the problem of large energy loss caused by turbulent flow field in existing fans, optimizing the airflow field, and reducing noise. Attached Figure Description

[0016] Figure 1 This is one of the schematic diagrams of the combined structure of the impeller and blades provided in a specific embodiment of the present invention; Figure 2This is the second schematic diagram of the combined structure of the impeller and blades provided in a specific embodiment of the present invention; Figure 3 This is a schematic diagram of the casing provided in a specific embodiment of the present invention; Figure 4 This is a schematic diagram of the control module provided in a specific embodiment of the present invention; Figure 5 This is a schematic diagram of the working principle of the control module provided in a specific embodiment of the present invention.

[0017] In the picture: 1. Impeller; 2. Blades; 3. Casing. Detailed Implementation

[0018] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0019] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this 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. Therefore, they should not be construed as limitations on this invention.

[0020] 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 as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0021] 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 part; 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; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0022] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0023] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0024] This embodiment discloses an industrial fan, such as... Figures 1 to 3 As shown, the industrial fan includes an impeller 1, at least two blades 2, and a casing 3. All blades 2 are evenly arranged on the outer periphery of the impeller 1, and the assembled impeller 1 and blades 2 are disposed in the casing 3.

[0025] Impeller 1 includes a serrated central disk. The flow channel length and the width of the steady flow zone of impeller 1 are both greater than a set value. This improves the airflow distribution at the outlet of impeller 1, facilitates the design of the blade 2's installation angle, reduces the impact of gas on the weld seam of blade 2, reduces the axial additional force caused by the pressure difference, extends the bearing's service life, and reduces the moment of inertia. The specific values ​​corresponding to the flow channel length and the width of the steady flow zone are not limited and can be determined according to actual usage requirements.

[0026] The inner wall profile of the casing 3 is adapted to the airflow field of the impeller 1. Specifically, the profile center structure of the casing 3 and the streamlined air collector are precisely matched with the impeller 1, which solves the problem of large energy loss caused by the turbulent flow field of existing fans, so as to achieve the optimal flow field and reduce noise.

[0027] To achieve a good match between impeller 1 and casing 3, it is necessary to optimize key parameters such as impeller arc, number of blades, and casing profile. The specific matching calculation and design formulas and methods are as follows.

[0028] The inlet angle of blade 2 is α1 = arctan(Cm1 / U1) + i, where Cm1 is the radial velocity at the inlet (m / s), calculated based on the flow rate; U1 is the circumferential velocity at the impeller inlet (m / s), U1 = π × D1 × N / 60, N is the rotational speed; i is the angle of attack, ranging from 3° to 8°; D1 is the inner diameter of the blade, D1 = c × D2, c is an empirical parameter value (in this embodiment, c = 0.4-0.9); and D2 is the outer diameter of the blade, D2 = 60 × (Pt / ψρ). 0.5 / π×N, Pt is the target total pressure (Pa), ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient. ψ is an empirical value; for backward-curved blades, the value of ψ ranges from 0.8 to 1.2; for forward-curved blades, the value of ψ ranges from 1.5 to –2.5.

[0029] The exit angle α2 of blade 2 is α2 = arctan(Cm2 / (U2-C2), where Cm2 is the radial velocity at the exit (m / s); C2 is the tangential velocity at the exit (m / s); U2 is the circumferential velocity at the impeller exit (m / s), U2 = π × D2 × N / 60, N is the rotational speed, and D2 = 60 × (Pt / ψρ). 0.5 / π×N, Pt is the target total pressure (Pa), ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient.

[0030] By rationally designing the installation angle of blade 2, the vortex and resistance formed during air intake are reduced, thereby improving aerodynamic performance.

[0031] The inlet height B1 of blade 2 is calculated as B1 = Q / (π × D1 × ηv × Cm1), where Q is the design flow rate (m³ / s). 3 / s); ηv is the volumetric efficiency, ranging from 0.85 to 0.95; Cm1 is the inlet radial velocity (m / s), ranging from 15m / s to 35m / s.

[0032] The outlet height B2 of blade 2 is calculated as B2 = Q / (π × D2 × ηv × Cm2), where Q is the design flow rate (m³ / s). 3 / s); ηv is the volumetric efficiency, ranging from 0.85 to 0.95; Cm2 is the outlet radial velocity (m / s), Cm2=(0.8-1.2)×Cm1.

[0033] The impeller inlet height B3 = a1 × B1 + a2 × B2, where a1 and a2 are empirical parameters.

[0034] The inlet diameter of blade 2 is DL = K × (Q / N). 1 / 3 Where K is the inlet diameter coefficient, with the value of K ranging from 4.5 to 5.0 for backward-curved blades and from 4.0 to 4.5 for forward-curved blades; Q is the design flow rate (m³ / s). 3 / s); N is the rotational speed.

[0035] The leading disk arc r of blade 2 is given by: r = R × e(θtanβ), where R is the inlet radius (m); β is the average blade tilt angle, taken as β = (β1 + β2) / 2, where β1 is the inlet installation angle and β2 is the outlet installation angle; θ ranges from 0 to γ, where γ is the wrap angle, γ = 180° / π × ln(D2 / D1)cot((β1 + β2) / 2), D1 is the blade inner diameter, D1 = c × D2, c = 0.4-0.9, and D2 is the blade outer diameter, D2 = 60 × (Pt / ψρ). 0.5 / π×N, Pt is the target total pressure (Pa), ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient; The number of blades 2 on impeller 1 is Z = 2π × sinβ / ln(D2 / D1) × k1, where K1 is a correction coefficient. The specific value of K1 is not limited and can be determined according to actual usage requirements.

[0036] The inlet radius of casing 3 is R = R1e tanf(φ，A，C,) R1 is the inlet radius correction factor, C is the outlet diameter of housing 3, and A is the horizontal distance between the starting point of the inner profile of housing 3 and the wall of housing 3.

[0037] Through the aforementioned design and calculation methods, this industrial fan ensures that the impeller 1, casing 3, and internal flow field structure all meet the requirements of actual operating conditions, thereby improving the operating efficiency of the industrial fan and achieving energy conservation and consumption reduction without affecting process production needs. Equipping the fan with a suitable high-efficiency industrial fan according to production process requirements improves energy utilization, ensures high operating efficiency, and avoids the situation of oversized fans being insufficient for the needs of existing industrial fans, thus saving energy and reducing consumption.

[0038] By automatically optimizing the design of parameters such as the profile of the casing, the arc of the impeller, and the number of blades, a "tailor-made" design is achieved, reducing gas eddy and turbulence losses, resulting in high efficiency, light weight, compact structure, and easy transportation, installation, and testing and maintenance.

[0039] It is understandable that the above calculation formula can also be obtained using computational fluid dynamics (CFD) simulation optimization methods; the industrial fan can also adopt a split blade design, which can also optimize airflow distribution and reduce weld impact; using a specific airfoil blade section instead of simply relying on installation angle adjustment can also achieve better aerodynamic performance and flow stabilization effect.

[0040] Based on the above structure, industrial fans also include a control module and parameter detection components, such as... Figure 4 As shown, the control module includes a perception layer, a transmission layer, a processing layer, and an application layer connected in sequence. The transmission layer can receive the detection results sent by the perception layer and send them to the processing layer.

[0041] The sensing layer connects to the parameter detection component, which mainly includes detection sensors and cameras. The parameter detection component can detect at least several parameters of the industrial fan, such as airflow, pressure, temperature, vibration, speed, and current, and all detection results can be sent to the sensing layer.

[0042] The transport layer connects to structures such as routers, gateways, advanced controllers, industrial control computers, and servers, and its function is simply to transmit information.

[0043] The processing layer possesses data storage, processing, and analysis capabilities. It receives detection results from the transmission layer and transforms the raw detection data into identification information, which is then stored in a database for processing and analysis of equipment operation. The processing layer supports AI model algorithms, equipment access, equipment management, data management, big data analysis, and production process matching, expanding the industrial fan's applicability and enhancing its competitiveness.

[0044] The application layer is used to feed back the identification information obtained from the processing layer to the operation and maintenance management of industrial fans. The fans can be digitally and intelligently monitored, diagnosed and managed to improve the reliability and production efficiency of the equipment, and realize data visualization and data export.

[0045] Based on the above structure, the industrial fan includes a machine vision inspection component and a control module. The machine vision inspection component includes an image acquisition device, and the intelligent control module is connected to the machine vision inspection component to receive image information.

[0046] like Figure 5 As shown, the machine vision inspection component is used to inspect the production process using machine vision, automatically identifying production process steps, especially key production process links that affect the operation of the industrial fan. Specifically, by obtaining information about the fan's operation through machine vision, an interlocking control model between the industrial fan and the production process can be implemented.

[0047] The control module uses a built-in AI model to build interlocking control between the industrial fan and the production process. It predicts the operating conditions and load of the industrial fan in advance and uses the AI ​​model to make predictive adjustments to automatically regulate production process steps. Specifically, it monitors the industrial fan's operating data in real time, including airflow, air pressure, speed, current, power, temperature, vibration, and power consumption, making predictive adjustments in advance. By building an AI model and algorithms, it correlates the equipment monitoring data with the health status of the industrial fan, automatically identifying the equipment's health status and fault types.

[0048] In this embodiment, the control module can be a centralized or distributed controller. For example, the controller can be a single microcontroller or a combination of multiple distributed microcontrollers. The microcontroller can run a control program to control the machine vision inspection component to achieve its function.

[0049] This industrial fan establishes an interlocking control model between the fan and the production process. By employing machine vision and dynamic control algorithms, AI learns the production process conditions and matches the fan's operation status to construct an interlocking control model between the fan equipment and the production process. This enables automatic identification of production process steps and automatic speed adjustment of the industrial fan, thereby enhancing the intelligence level of the industrial fan.

[0050] This industrial fan has changed the existing fixed-speed operation mode of fans by exploring the linkage mechanism between fan start-up and shutdown, equipment operating parameter adjustment and process status, effectively reducing the fan's energy consumption.

[0051] This industrial fan can automatically adjust its operating conditions according to the production process. Through the learning of the production process and the fan's operating conditions by the AI ​​model, it can predict the fan load and the production process, adjust the fan load in advance and respond in a timely manner to achieve the best energy-saving effect and a good user experience.

[0052] It is understandable that the technical solution for machine vision inspection of process steps can be replaced by other methods. In this embodiment, pressure, flow, position, or temperature sensors are installed at key nodes of the production equipment (such as valves, conveyor belts, heaters, etc.). By analyzing the temporal characteristics and correlations of these sensor data, the production process steps and load requirements are indirectly inferred, thereby predicting the operating condition of the industrial fan. Alternatively, production plans, work order statuses, and equipment start / stop signals provided by the factory manufacturing execution system (MES) or programmable logic controller (PLC) can be used as inputs to directly determine the current process status and expected load, driving the regulation of the industrial fan.

[0053] AI models used for load forecasting and regulation (such as deep learning neural networks) can be replaced by mathematical models based on physical mechanisms (such as fan characteristic curve fitting models and thermodynamic models) combined with time series prediction algorithms for forecasting and regulation. The technical solution of building an interlocking model between the fan and the production process to achieve automatic speed regulation can be replaced by time program-based control (adjusting the fan speed according to the preset production schedule) or direct linkage control based on the status of key equipment (such as main motor current and valve opening threshold) (without the need for complex step recognition models).

[0054] The specific structure of the industrial fan is not limited; in this embodiment, the industrial fan is a variable frequency fan. By utilizing the fan's variable frequency function, an interlocking control model between the fan equipment and the production process is constructed, enabling automatic identification of production process steps and automatic speed adjustment of the fan. During production, the industrial fan can operate at high speed according to actual needs; while in non-production states, the industrial fan can automatically reduce speed or even stop.

[0055] To extend the service life of the industrial fan, an anti-corrosion coating is sprayed onto its outer surface. In this embodiment, a plasma spraying nano-coating method is used to form the anti-corrosion coating, which has high processing efficiency and good anti-corrosion effect. This industrial fan can be used in harsh environments such as oceans and swamps, and has a wide range of applications.

[0056] Based on the above structure, the industrial fan also includes a noise monitoring device connected to the control module. The noise monitoring device is used to monitor the noise spectrum of the industrial fan in real time and send the monitoring results to the control module. The control module is used to dynamically adjust the operating parameters of the industrial fan (which can be, but is not limited to, speed) or activate the silencing device according to the monitoring results to achieve adaptive noise reduction.

[0057] The specific structure of the noise reduction device is not limited, as long as it can effectively reduce noise. In this embodiment, the resonator is installed at the volute of the casing 3, which consumes sound energy through friction and damping, thus significantly reducing noise in a specific frequency band. Alternatively, sound-absorbing and insulating material can be wrapped around the outer perimeter of the industrial fan, a silencer can be installed at the exhaust, and rubber or springs can be installed at the base to reduce mechanical vibration during fan operation and reduce noise transmission.

[0058] Note that the above description is merely a preferred embodiment of the present invention and the technical principles employed. Those skilled in the art will understand that the present invention is not limited to the specific embodiments described herein, and various obvious changes, readjustments, and substitutions can be made without departing from the scope of protection of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments, and may include many other equivalent embodiments without departing from the concept of the present invention, the scope of which is determined by the scope of the appended claims.

Claims

1. An industrial fan, characterized in that, include: Impeller (1), including a sawtooth-shaped central disk, the flow channel length of the impeller (1) is greater than a set value, and the width of the steady flow zone of the impeller (1) is greater than a set value; At least two blades (2), all of which are evenly arranged on the outer periphery of the impeller (1); and, The casing (3) contains the assembled impeller (1) and blades (2), and the inner wall profile of the casing (3) is adapted to the airflow field of the impeller (1).

2. The industrial fan according to claim 1, characterized in that, The inlet angle of the blade (2) is α1=arctan(Cm1 / U1)+i, where Cm1 is the radial velocity at the inlet (m / s), calculated based on the flow rate; U1 is the circumferential velocity at the impeller inlet (m / s), U1=π×D1×N / 60, N is the rotational speed; i is the angle of attack, ranging from 3° to 8°; D1 is the inner diameter of the blade, D1=c×D2, c=0.4-0.9; D2 is the outer diameter of the blade, D2=60×(Pt / ψρ) 0.5 / π×N, Pt is the target total pressure (Pa), ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient; The exit angle α2 of the blade (2) is α2 = arctan(Cm2 / (U2-C2)), where Cm2 is the radial velocity at the exit (m / s); C2 is the tangential velocity at the exit (m / s); U2 is the circumferential velocity at the impeller exit (m / s), U2 = π × D2 × N / 60, N is the rotational speed, and D2 = 60 × (Pt / ψρ). 0.5 / π×N, Pt is the target total pressure (Pa), ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient.

3. The industrial fan according to claim 2, characterized in that, The inlet height B1 of the blade (2) is B1 = Q / (π × D1 × ηv × Cm1), where Q is the design flow rate (m³ / s). 3 / s); ηv is the volumetric efficiency, ranging from 0.85 to 0.95; Cm1 is the inlet radial velocity (m / s), ranging from 15m / s to 35m / s; The outlet height B2 of the blade (2) is B2 = Q / (π × D2 × ηv × Cm2), where Q is the design flow rate (m³ / m²). 3 / s); ηv is the volumetric efficiency, ranging from 0.85 to 0.95; Cm2 is the outlet radial velocity (m / s), Cm2=(0.8-1.2)×Cm1; The impeller inlet height B3 = a1 × B1 + a2 × B2, where a1 and a2 are empirical parameters.

4. The industrial fan according to claim 1, characterized in that, The inlet diameter of the blade (2) is DL = K × (Q / N). 1 / 3 Where K is the inlet diameter coefficient, with the value of K ranging from 4.5 to 5.0 for backward-curved blades and from 4.0 to 4.5 for forward-curved blades; Q is the design flow rate (m³ / s). 3 / s); N is the rotational speed.

5. The industrial fan according to claim 1, characterized in that, The leading disk arc of the blade (2) is r = R × e(θtanβ), where R is the inlet radius (m); β is the average blade tilt angle, taken as β = (β1 + β2) / 2, β1 is the inlet installation angle, and β2 is the outlet installation angle; the value of θ is between 0 and γ, γ is the wrap angle, γ = 180° / π × ln(D2 / D1)cot((β1 + β2) / 2), D1 is the blade inner diameter, D1 = c × D2, c = 0.4-0.9, D2 is the blade outer diameter, D2 = 60 × (Pt / ψρ) 0.5 / π×N, Pt is the target total pressure (Pa), ρ is the gas density (kg / m³). 3 ), where ψ is the pressure coefficient; The number of blades (2) set on the impeller (1) is Z = 2π × sinβ / ln(D2 / D1) × k1, where K1 is a correction coefficient.

6. The industrial fan according to claim 1, characterized in that, The inlet radius R of the casing (3) is R1e tanf (φ，A，C,) R1 is the inlet radius correction factor.

7. The industrial fan according to any one of claims 1 to 6, characterized in that, The industrial fan also includes: A machine vision inspection component, including an image acquisition device, is used to inspect the production process using machine vision to automatically identify production process steps; and... The control module is connected to the machine vision detection component to receive image information. The control module can construct an interlock control model between the industrial fan and the production process through the built-in AI model, predict the operating conditions and load of the industrial fan in advance, and automatically adjust the production process steps.

8. The industrial fan according to claim 7, characterized in that, The industrial fan has a frequency conversion function.

9. The industrial fan according to claim 7, characterized in that, The industrial fan also includes a noise monitoring device connected to the control module. The noise monitoring device is used to monitor the noise spectrum of the industrial fan in real time and send the monitoring results to the control module. The control module is used to dynamically adjust the operating parameters of the industrial fan or activate the silencing device according to the monitoring results.

10. The industrial fan according to any one of claims 1 to 6, characterized in that, The industrial fan also includes a control module and a parameter detection component. The control module includes: A sensing layer is connected to the parameter detection component, which is used to detect at least the air volume, pressure, temperature, vibration, speed and current of the industrial fan, and all detection results can be sent to the sensing layer. The transport layer is used to receive the detection results sent by the perception layer and to send the detection results back. The processing layer, possessing data storage, data processing, and data analysis capabilities, is used to receive the detection results sent by the transmission layer, convert the data into identification information, and store the identification information; and, The application layer is used to feed back the identification information obtained from the analysis of the processing layer to the operation and maintenance management of the industrial fan, so as to monitor, diagnose and manage the operating status of the industrial fan.

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