Fan assembly, purification fan head, and purification fan

Abstract

The embodiment of the present application provides a fan assembly, a purification fan head and a purification fan. The fan assembly comprises a shell, an axial flow fan and a pressurizing assembly. The shell has an air inlet end and an air outlet end at two axial ends thereof respectively; the axial flow fan is rotatably installed inside the shell; the pressurizing assembly is installed inside the shell and located at a side of the axial flow fan close to the air outlet end, and the pressurizing assembly and the axial flow fan together cooperate with the inner wall of the shell to form a pressurizing air duct which communicates the air inlet end and the air outlet end. The pressurizing assembly comprises a primary guide vane structure and a secondary guide vane structure. The primary guide vane structure is located at a side close to the axial flow fan inside the shell; the secondary guide vane structure is located at a side close to the air outlet end inside the shell; and the primary guide vane structure is configured to adjust the airflow blown out by the axial flow fan to be axial, and the secondary guide vane structure is configured to accelerate the axial airflow to be blown out.

Description

Technical Field

[0001] This application relates to the field of air conditioning equipment technology, and more specifically, to a fan assembly, a purification fan head, and a purification fan. Background Technology

[0002] In the relevant technical field, in order to enable fans to purify the air while delivering air, a structure with a filter installed at the air inlet of the fan is usually chosen.

[0003] However, adding a filter to the fan's inlet directly affects the airflow, significantly increasing air resistance and causing a substantial decrease in airflow speed and volume, thus impacting basic air delivery functionality. Using a simple filter, on the other hand, cannot effectively purify the air. Therefore, air purification fans generally suffer from low airflow and speed, resulting in poor purification performance. Summary of the Invention

[0004] This application provides a fan assembly, a purification fan head, and a purification fan, which aims to adjust the oblique airflow blown out by the oblique flow fan to the axial direction through a first-stage guide vane structure, and then accelerate the axial airflow through a second-stage guide vane structure, thereby achieving a blowing effect that enhances suction, increases wind speed, and increases wind distance.

[0005] This application provides a fan assembly, including: a housing, a diagonal-flow fan, and a pressurizing assembly. The housing has an inlet end and an outlet end at its two axial ends, respectively; the diagonal-flow fan is rotatably mounted inside the housing; the pressurizing assembly is mounted inside the housing and located on the side of the diagonal-flow fan near the outlet end, and the pressurizing assembly and the diagonal-flow fan together cooperate with the inner wall of the housing to form a pressurizing duct communicating with the inlet end and the outlet end; wherein, the pressurizing assembly includes: a primary guide vane structure and a secondary guide vane structure. The primary guide vane structure is located inside the housing and is positioned behind the diagonal-flow fan along the airflow direction; the secondary guide vane structure is located inside the housing and is positioned behind the primary guide vane structure along the airflow direction; and the primary guide vane structure is configured to adjust the airflow blown by the diagonal-flow fan to tend towards the axial direction, and the secondary guide vane structure is configured to accelerate the axial airflow.

[0006] In some embodiments, the first-stage guide vane structure includes: a guide seat and a first blade, wherein a plurality of first blades are circumferentially arranged along the outer surface of the guide seat; wherein the first blade has a guide surface disposed opposite to each other in the thickness direction, a plane perpendicular to the axial direction is defined as a reference plane, the angle between the guide surface and the reference plane gradually increases in the direction from the air inlet to the air outlet, the angle between the trailing edge of the guide surface and the reference plane is not less than 70° and not greater than 90°; and / or, the thickness of the first blade gradually decreases in the direction from the air inlet to the air outlet.

[0007] In some embodiments, each of the first blades is twisted; wherein, a sub-duct is formed between two adjacent first blades, the centerline of the sub-duct being curved to guide the airflow blown by the oblique flow fan to be adjusted to axial airflow.

[0008] In some embodiments, the secondary guide vane structure includes: a connecting seat and a plurality of second blades, the plurality of second blades being arranged circumferentially along the outer surface of the connecting seat; wherein, along the airflow direction, the thickness of the second blades near the air outlet end is greater than its thickness near the air inlet end.

[0009] In some embodiments, the first blade is larger than the second blade along the axial direction of the housing.

[0010] In some embodiments, the arrangement density of the second blade along the circumference of the connector is greater than the arrangement density of the first blade along the circumference of the guide seat.

[0011] In some embodiments, along the axial direction of the housing, the distance between the end of the first blade near the air outlet and the end of the second blade near the air inlet is not less than 1 mm and not more than 9 mm.

[0012] In some embodiments, the diagonal flow fan includes a rotating base and a plurality of diagonal flow blades, the plurality of diagonal flow blades being evenly distributed on the surface of the rotating base around the rotation axis of the diagonal flow fan; wherein, along the axial direction of the housing, the size of the diagonal flow blades is larger than the size of the first blade.

[0013] In some embodiments, along the axial direction of the housing, the distance between the end of the oblique flow blade near the air outlet and the end of the first blade near the air inlet is not less than 1 mm and not more than 9 mm.

[0014] In some embodiments, the fan assembly further includes a motor mount disposed on the air guide seat and located on the side of the air guide seat opposite to the first blade, for mounting a motor.

[0015] In some embodiments, the fan assembly further includes an air intake grille. The air intake grille is detachably mounted to the air intake end; wherein the center of the air intake grille protrudes axially away from the air intake end.

[0016] In some embodiments, the fan assembly further includes a control panel disposed on the side of the connector opposite to the second blade.

[0017] In some embodiments, the housing includes: an outer shell, a duct shell, a flow guide shell, and a pressurization shell; the duct shell, the flow guide shell, and the pressurization shell are sequentially arranged inside the outer shell, wherein the flow guide shell is disposed around the periphery of the primary guide vane structure; the pressurization shell is disposed around the periphery of the secondary guide vane structure; and / or, the outer shell, the duct shell, the flow guide shell, and the pressurization shell are integrally formed; and / or, the flow guide shell and the primary guide vane structure are integrally formed; and / or, the pressurization shell and the secondary guide vane structure are integrally formed; and / or, the outer shell and the secondary guide vane structure are integrally formed.

[0018] This application embodiment also provides a purification fan head, including: the fan assembly and the air purification assembly; the air purification assembly is installed at the air inlet end of the fan assembly; wherein the air purification assembly and the fan assembly are detachably connected.

[0019] In some embodiments, the air purification component has a rotating buckle at one end facing the fan component, and the air purification component is detachably connected to the fan component via the rotating buckle.

[0020] In some embodiments, the air purification assembly includes: a rear screen, a first filter, and / or a second filter; the rear screen has a receiving cavity inside and is detachably installed at the air inlet end of the fan assembly; the first filter is installed in the receiving cavity and is disposed around the inner wall of the rear screen; the first filter has a channel that extends radially through it; the second filter is installed at the end of the channel away from the fan assembly.

[0021] This application also provides a purification fan, including: a base, a bracket, and the purification fan head. The purification fan head is mounted on the bracket. The purification fan head is rotatable relative to the bracket.

[0022] Based on the fan assembly of this application embodiment, a pressurized air duct is constructed inside the housing. The diagonal-flow fan first draws air into the pressurized air duct by rotation, generating a large flow rate and a certain directional angle of diagonal airflow. Subsequently, the diagonal airflow enters the first-stage guide vane structure, guiding the diagonal airflow to change its direction of motion, adjusting the diagonal airflow into an airflow that flows substantially along the axial direction of the housing. Finally, the adjusted airflow, tending towards the axial direction, enters the second-stage guide vane structure. The second-stage guide vane structure converges and accelerates the airflow, further increasing the dynamic pressure and velocity at the airflow outlet.

[0023] Thus, the air purifier fan head using the fan assembly of this application overcomes the problem of significant reduction in airflow and speed after adding a filter, improving air delivery efficiency while ensuring purification effect. This allows the solution to function as both a fan and an air circulation and purification device, improving indoor air quality and comfort, while also enhancing the functional integration of home appliances and providing users with a superior user experience. Attached Figure Description

[0024] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0025] Figure 1 This is a cross-sectional structural diagram of the fan assembly in this application; Figure 2 This is a schematic diagram of the airflow direction in this application; Figure 3 This is a schematic diagram of the first-stage guide vane structure in this application; Figure 4 for Figure 3 Enlarged structural diagram of region A in the middle; Figure 5 This is a schematic diagram of the secondary guide vane structure in this application; Figure 6 This is a schematic diagram of the structure of the diagonal flow fan in this application; Figure 7 This is a cross-sectional structural diagram of the diagonal flow fan in this application; Figure 8 This is a schematic diagram of the shell structure in this application; Figure 9 This is a schematic diagram of the structure of the purification fan head in this application; Figure 10 This is a cross-sectional structural diagram of the purification fan head in this application; Figure 11 This is a schematic diagram of the structure of the purification fan in this application.

[0026] Explanation of icon numbers: 1. Fan assembly; 10. Housing; 101. Air inlet; 102. Air outlet; 11. Diagonal flow fan; 12. Pressurization assembly; 121. First-stage guide vane structure; 122. Second-stage guide vane structure; 13. Pressurization duct; 1210. Flow guide seat; 1211. First blade; 131. Sub-duct; 1220. Connecting seat; 1221. Second blade; 110. Rotating seat; 111. Diagonal flow blade; 14. Motor seat; 15. Motor; 16. Air inlet grille; 17. Control panel; 103. Housing; 104. Duct housing; 105. Flow guide housing; 106. Pressurization housing; 2. Air purification assembly; 20. Rear screen; 21. First filter; 22. Second filter; 3. Purification fan head; 4. Purification fan; 40. Base; 41. Bracket; S. Reference plane; L. Axial direction.

[0027] The realization of the purpose, functional features and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0028] To make the objectives, technical solutions, and advantages of this application clearer, the embodiments of this application will be described in further detail below with reference to the accompanying drawings.

[0029] Where the following description relates to the accompanying drawings, unless otherwise indicated, the same numbers in different drawings denote the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this application as detailed in the appended claims.

[0030] In the description of this application, it should be understood that the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances. Furthermore, in the description of this application, unless otherwise stated, "multiple" refers to two or more. "And / or" describes the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship.

[0031] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of this application. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0032] A fan, as a device that propels airflow through a rotating impeller, works by converting the mechanical energy of an electric motor into the kinetic energy of the air. Air purifiers, building upon this principle, integrate filter materials into the airflow path to remove particulate pollutants. Existing air purifiers generally use traditional axial fans as their power source. Axial fans are characterized by airflow parallel to the rotation axis, resulting in relatively low air pressure but a large flow rate. In this design, filter components (such as screens) are typically placed simply on the fan's inlet or outlet side. As airflow passes through the filter material, the air is purified, but the filter material also creates significant resistance to the airflow.

[0033] The aforementioned traditional technical solutions suffer from the following main problems: First, the low air pressure characteristic of axial fans makes them insufficient to overcome the additional air resistance introduced by filters, resulting in a significant decrease in the overall airflow and velocity after adding filters, a substantial reduction in air delivery distance, and impacting basic ventilation circulation functions. Second, the simple duct design cannot effectively organize and optimize airflow, leading to turbulent airflow, significant energy loss, and low efficiency. Finally, to accommodate fan performance, filters are often made thin and simple, with limited filtration area and dust holding capacity, resulting in unsatisfactory purification effects and lifespan.

[0034] Based on the problems existing in the current technology, such as Figure 1 As shown, this application embodiment provides a fan assembly 1, including a housing 10, a diagonal flow fan 11, and a pressurizing assembly 12. Understandably, the housing 10 has an air inlet 101 and an air outlet 102 at its two ends along the axial direction L, respectively. The air inlet 101 is an opening for air to enter, and the air outlet 102 is an opening for air to exit. The diagonal flow fan 11 is rotatably mounted inside the housing 10. The pressurizing assembly 12 is a static component assembly for handling airflow. The pressurizing assembly 12 is mounted inside the housing 10 and located on the side of the diagonal flow fan 11 near the air outlet 102. The pressurizing assembly 12 and the diagonal flow fan 11 together cooperate with the inner wall of the housing 10 to form a pressurizing duct 13 communicating with the air inlet 101 and the air outlet 102. The pressurizing duct 13 refers to the spatial path enclosed by the surface of the components through which the airflow flows from the air inlet 101 to the air outlet 102.

[0035] Furthermore, the pressurization assembly 12 includes a first-stage guide vane structure 121 and a second-stage guide vane structure 122. The first-stage guide vane structure 121 is located inside the housing 10 and is positioned behind the diagonal flow fan 11 along the airflow direction. The second-stage guide vane structure 122 is located inside the housing 10 and is positioned behind the first-stage guide vane structure 121 along the airflow direction. The first-stage guide vane structure 121 is configured to adjust the airflow blown by the diagonal flow fan 11 to tend towards the axial direction L, and the second-stage guide vane structure 122 is configured to accelerate the axial L airflow, with the airflow direction as shown in the figure. Figure 2 As indicated by the middle arrow. Understandably, the airflow tending towards the axial direction L refers to the airflow adjusted by the first-stage guide vane structure 121, whose flow direction gradually adjusts towards the axial direction L until it is basically parallel to the axial direction L and blows towards the second-stage guide vane structure 122.

[0036] In other words, fan assembly 1 constructs an efficient airflow processing path. The diagonal-flow fan 11 first draws in air through rotation, generating a high-flow-rate airflow with a specific directional angle. Subsequently, the airflow enters the first-stage guide vane structure 121. As a stationary guiding component, the first-stage guide vane structure 121 guides the diagonal airflow to change its direction of motion through its specific blade shape, adjusting the diagonal airflow into an airflow that flows substantially along the axial direction L of the housing 10. Finally, the adjusted axial airflow enters the second-stage guide vane structure 122. The second-stage guide vane structure 122, through the contraction and guiding action of the pressurized air duct 13, converges and further accelerates the airflow, further increasing the dynamic pressure and velocity at the airflow outlet.

[0037] In this way, through the coordinated work of the diagonal flow fan 11 and the pressurizing component 12, the airflow in the pressurizing duct 13 can eventually be blown out along the axis at a greater speed, so that the fan component 1 can output a stronger, more concentrated, and longer-range airflow than a traditional single fan, thereby achieving the blowing effect of enhanced suction, increased wind speed, and increased wind distance.

[0038] In one embodiment, such as Figure 3 As shown, the first-stage guide vane structure 121 includes a guide seat 1210 and a plurality of first blades 1211. A partial pressurized air duct 13 is formed between the guide seat 1210 and the inner wall of the housing 10. The plurality of first blades 1211 are located between the guide seat 1210 and the inner wall surface of the housing 10, and are arranged circumferentially along the outer surface of the guide seat 1210. The first blades 1211 have guide surfaces arranged opposite to each other in the thickness direction. A plane perpendicular to the axial direction L is defined as the reference plane S. The angle between the guide surface and the reference plane S gradually increases in the direction from the air inlet end 101 to the air outlet end 102. The angle between the trailing edge of the guide surface and the reference plane S is not less than 70° and not greater than 90°. The thickness of the first blades 1211 gradually decreases in the direction from the air inlet end 101 to the air outlet end 102.

[0039] In other words, the first blade 1211 has a leading edge and a trailing edge. The leading edge is the end of the first blade 1211 closer to the inlet end 101, and the trailing edge is the end of the first blade 1211 closer to the outlet end 102. The thickness of the leading edge of the first blade 1211 can be designed to be greater than the thickness of the trailing edge, forming a cross-section with unequal thickness. For example, the leading edge can be a smooth, large radius of curvature, while the trailing edge can gradually thin. It should be noted that the thickness here refers to the distance between the two guide surfaces of the first blade 1211 that are circumferentially opposite to each other.

[0040] like Figure 3 As shown, the angle α2 between the trailing edge of the first blade 1211 and the reference plane S is not less than 70° and not greater than 90°. This angle is preferably between 80° and 90°, so that the airflow at the blade outlet is as close as possible to the axial direction L. The acute angle between the leading edge of the first blade 1211 and the reference plane S is the front inlet angle α1, which can range from 30° to 50°.

[0041] Understandably, the first blade 1211 adopts a gradually widening installation angle design. Looking from the inlet end 101 to the outlet end 102, the blades of the diagonal flow fan 11 are arranged in the opposite direction to the first blade 1211. At the leading edge of the first blade 1211, the smaller installation angle helps to smoothly receive the airflow with a certain tangential component from the diagonal flow fan 11. When the diagonal flow fan 11 rotates, it drives the airflow, resulting in an angle between the direction of airflow exiting the diagonal flow fan 11 and the direction of rotation of the diagonal flow fan 11. The design of the inlet angle α1 at the leading edge of the first blade 1211 matches this angle with the angle of the diagonal airflow blown out by the diagonal flow fan 11. This matching design allows the airflow to smoothly enter the flow channel between the first blades 1211, avoiding kinetic energy loss and additional flow resistance caused by abrupt changes in airflow direction, thus helping to maintain high aerodynamic efficiency. Simultaneously, the first blade 1211 adopts a non-uniform thickness design with a thicker leading edge and a thinner trailing edge. The thicker and smoother leading edge can better guide and divide the airflow, reducing the possibility of airflow separation and the generation of large-scale vortices at the leading edge of the first blade 1211.

[0042] In this way, the optimized design of the first blade 1211 improves the airflow state when entering the first-stage guide vane structure 121, further reducing aerodynamic noise caused by flow instability and improving the overall noise reduction performance and energy efficiency. At the same time, the smooth, gradual guiding process effectively reduces separation and vortex phenomena during airflow turning, reducing aerodynamic noise and improving guiding efficiency.

[0043] In one embodiment, such as Figure 3 and Figure 4As shown, each first blade 1211 is twisted. Twisting refers to the variation in the airfoil or installation angle of the blade along the height direction of the first blade 1211 (from the root to the tip). Specifically, the angle between the first blade 1211 and the axial direction L gradually increases from the root to the tip, i.e., b2 > b1. A sub-channel 131 is formed between two adjacent first blades 1211. The sub-channel 131 is the airflow passage between adjacent blades. The centerline of the sub-channel 131 is curved to guide the airflow blown by the oblique flow fan 11 to adjust the airflow to the axial direction L. The shape of the curve can be matched to the twisting pattern of the blades.

[0044] Understandably, since the airflow velocity and direction angle differ at different radii of the diagonal flow fan 11, designing the first blade 1211 as twisted allows the installation angle of the first blade 1211 at different heights to better match the diagonal airflow conditions blown by the diagonal flow fan 11, achieving more precise airflow guidance. The curved sub-duct 131 formed by the twisted blades provides a smooth transition path for the airflow, guiding the airflow to naturally and continuously transform from the diagonal flow at the inlet to the axial L-flow at the outlet.

[0045] In this way, the twisted first blade 1211 structure design further optimizes the uniformity and efficiency of airflow adjustment, and reduces the additional drag loss and noise caused by flow mismatch.

[0046] In one embodiment, such as Figure 1 and Figure 5 As shown, the secondary guide vane structure 122 includes a connecting seat 1220 and a plurality of second blades 1221. A partial pressurized air duct 13 is formed between the connecting seat 1220 and the inner wall of the housing 10. The plurality of second blades 1221 are located between the connecting seat 1220 and the inner wall surface of the housing 10, and are arranged circumferentially along the outer surface of the connecting seat 1220. In the airflow direction, the thickness of the second blades 1221 near the air outlet 102 is greater than the thickness near the air inlet 101.

[0047] Specifically, the second blade 1221 has two sides that are circumferentially opposite to each other, and at least one of the sides is curved. That is, the second blade 1221 can have an arc shape, with a D-shaped cross-section. A D-shaped cross-section refers to a cross-section resembling the letter "D," with one side being a plane or slightly convex surface and the other a significantly curved surface. A curved side refers to a surface profile that is a smooth curve, such as a circular arc, parabola, or spline curve.

[0048] Understandably, the second blade 1221 adopts an arc shape and a D-shaped cross-section design, and the thickness of the second blade 1221 near the outlet end 102 is set to be greater than its thickness near the inlet end 101, so that the flow channel between two adjacent second blades 1221 forms a channel with a gradually changing cross-section along the airflow direction. When the airflow, which tends towards the axial direction L after being regulated by the first-stage guide vane structure 121, enters this region, the flow channel cross-section contracts. According to Bernoulli's principle, in the steady flow of an incompressible fluid, the static pressure of the fluid decreases where the flow velocity increases. Therefore, in this contracting flow channel, the airflow velocity is increased, and the static pressure decreases accordingly. The arc-shaped blade side can smoothly guide and constrain the airflow.

[0049] Similarly, the cross-section of the second blade 1221 can also be set as trapezoidal, in which case the second blade 1221 can also play the role of smoothly guiding and constraining the airflow.

[0050] In this way, by rationally designing the variation of the second blade thickness along the airflow direction, energy conversion efficiency is optimized, resulting in low energy loss and aerodynamic noise. Simultaneously, the smooth, curved shape avoids sharp angles, reducing the possibility of airflow separation and vortex generation on the blade surface. This achieves airflow acceleration while suppressing turbulent energy dissipation, helping to reduce aerodynamic noise that may be exacerbated by increased flow velocity, and improving the quality of high-speed airflow and overall system efficiency.

[0051] In one embodiment, the arrangement density of the second blades 1221 along the circumference of the connecting seat 1220 is greater than the arrangement density of the first blades 1211 along the circumference of the guide seat 1210. Understandably, the more blades arranged circumferentially, the smaller the angle between the lines connecting the roots to the center of two adjacent blades; that is, the greater the arrangement density, the smaller the angle. Therefore, the angle between the lines connecting the roots of two adjacent second blades 1221 to the center of the connecting seat 1220 is smaller than the angle between the lines connecting the roots of two adjacent first blades 1211 to the center of the guide seat 1210.

[0052] In this way, the airflow blown out from the first-stage guide vane structure 121 enters the second-stage guide vane structure 122 and can be diverted by more second blades 1221, so that the airflow at each angle can be fully accelerated.

[0053] In one embodiment, such as Figure 3 and Figure 5 As shown, the axial dimension of the first blade 1211 is greater than the axial dimension of the second blade 1221. The axial dimension refers to the length or depth of the component in the direction parallel to the fan axis. Specifically, the axial dimension of the first blade 1211 is L2, and the axial dimension of the second blade 1221 is L3, and the ratio between them satisfies: 1.5 ≤ L2 / L3 ≤ 3.

[0054] Understandably, the first-stage guide vane structure 121 undertakes the main and significant task of adjusting the airflow direction, thus requiring a longer flow path length (i.e., a larger axial dimension) to allow the airflow to be smoothly and fully redirected, in order to avoid significant flow losses and noise. The second-stage guide vane structure 122 mainly undertakes the tasks of acceleration and flow convergence, and its airflow adjustment range is relatively small, so a shorter axial dimension L can be used to achieve its function.

[0055] Furthermore, the wind speed and noise of the fan assembly were tested based on different ratios of L2 and L3. Referring to the national standard "AC Fans and Speed ​​Regulators" (GB / T 13380-2018), the specified measurement method is as follows: The fan assembly 1 is installed at one end of the test chamber. Several test planes are selected along the axial direction L in front of the air outlet of the fan assembly 1. Multiple concentric rings are set around the fan axis in each test plane, with four wind speed measurement points arranged on each ring, two symmetrically arranged in the horizontal and two symmetrically arranged in the vertical directions. An impeller-type anemometer with a nominal diameter not exceeding 100 mm and a sensitivity not less than 0.15 m / s is used. The anemometer is moved sequentially to each measurement point to collect wind speed data. During measurement, starting approximately 40 mm from the fan axis, the measurement is moved horizontally in increments of 80 mm to both sides until the measured average wind speed drops below 9 m / min. Meanwhile, during the operation of fan assembly 1, a microphone is used to measure at least 4 points around the fan assembly and the average value is taken.

[0056] The above measurements show that when the ratio of L2 to L3 is 2.5, the wind speed of fan assembly 1 can reach 304 m / min, and the noise generated by fan assembly 1 during operation can be controlled below 60 dB. When the ratio is 0.5, the wind speed at the air outlet 102 is only 275 m / min, and the noise generated by the fan assembly 1 during operation exceeds 60 dB. When the ratio is 4, the wind speed at the air outlet 102 is only 281 m / min, and the noise generated by the fan assembly 1 during operation exceeds 60 dB. Therefore, when the ratio is below 1.5, the depth of the first blade 1211 may be insufficient, resulting in inadequate airflow adjustment. A significant amount of turbulent tangential component still enters the second blade 1221, affecting acceleration and potentially increasing noise. When the ratio is higher than 3, the first-stage guide vane structure 121 may be too long, which will increase unnecessary wind resistance and material costs, making the axial dimension of the product too large. Not only will the wind speed increase effect be poor, but the noise generated by the fan assembly will also increase.

[0057] Therefore, limiting the ratio of L2 to L3 to between 1.5 and 3 ensures that noise is kept within a small range even when the wind speed is high enough, thus achieving a reasonable allocation of functions and an optimized balance of structure.

[0058] In this way, by limiting the axial dimensions of the first blade 1211 and the second blade 1221, it is ensured that the first-stage guide vane structure 121 can effectively regulate the airflow within a limited space, while the second-stage guide vane structure 122 can efficiently accelerate the airflow. Ultimately, the overall performance goals of high air volume, high wind speed and low noise are achieved in synergy.

[0059] In one embodiment, such as Figure 1 As shown, along the axial direction of the housing 10, the distance between the end of the first blade 1211 near the air outlet 102 and the end of the second blade 1221 near the air inlet 101 is e2, where e2 is less than 1 mm and not greater than 9 mm. This distance e2 is preferably in the range of 2 mm to 8 mm.

[0060] Understandably, a gap is maintained between the first blade 1211 and the second blade 1221 along the axial direction L of the housing 10. This small gap prevents large-scale backflow or vortices from forming in the cavity between the two guide vanes, thus avoiding unnecessary pressure loss and noise generation. At the same time, this gap provides the necessary tolerances for manufacturing and assembly.

[0061] This achieves a good balance between suppressing the adverse effects of gap flow and ensuring manufacturability, thus ensuring the efficient transfer of airflow energy from the first-stage guide vane structure 121 to the second-stage guide vane structure 122.

[0062] In one embodiment, such as Figure 6 and Figure 7 As shown, the diagonal flow fan 11 includes a rotating base 110 and multiple diagonal flow blades 111. The rotating base 110 is a hub for connecting the motor drive shaft and mounting the blades. The multiple diagonal flow blades 111 are the core components for generating air pressure, and the multiple diagonal flow blades 111 are evenly distributed on the surface of the rotating base 110 around the rotation axis of the diagonal flow fan 11. The axial dimension of the diagonal flow blades 111 is larger than the axial dimension of the first blade 1211.

[0063] Specifically, the diameter of the front root of the oblique flow blade 111 is defined as D1, the diameter of the front tip of the oblique flow blade 111 is defined as D2, the diameter of the rear root of the oblique flow blade 111 is defined as D3, and the diameter of the rear tip of the oblique flow blade 111 is defined as D4. These diameters satisfy the proportional relationship: 2≤D1 / D3≤3.5, and 1.3≤D2 / D4≤2.5.

[0064] Furthermore, the front end of the oblique flow blade 111 adopts a concave design with a concave depth of L4; the rear end of the oblique flow blade 111 adopts a swept-back oblique cut design with a cut depth of L5. Both the concave depth L4 and the oblique cut depth L5 satisfy the relationship with the rotor depth L1: L4, L5 = (0.05 ~ 0.25) L1.

[0065] Define the number of blades of the diagonal flow blade 111 as N1 and the number of blades of the first-stage guide vane as N2. The two numbers satisfy the relationship: 0.5 ≤ N1 / N2 ≤ 2.

[0066] Define the axial dimension of the oblique flow blade 111 as L1 and the axial dimension of the first blade 1211 as L2. The depths of the two blades satisfy the relationship: 1.5≤L1 / L2≤3.

[0067] Understandably, the larger axial dimension of the diagonal-flow fan 11, as the core power source, provides the necessary flow channel length for sufficient air acceleration and pressurization. The ratio of D1 / D3 to D2 / D4 defines the blade shape. A larger ratio (e.g., D1 significantly greater than D3) means that the inlet area of ​​the airflow channel from the root to the tip of the blade is significantly larger than the outlet area. This is beneficial for continuously pressurizing the air during rotation, improving the fan's static pressure capability, and thus better overcoming the resistance from the filter and pressurization duct 13. The specific value range of L4 and L5 (0.05~0.25*L1) ensures a balance between the structural strength and aerodynamic effect of the concave and oblique front ends. The concave front end increases the actual air intake area and reduces the inlet velocity, which helps reduce intake noise and improve performance under high flow rates; the oblique front end weakens the vortex intensity generated at the tip of the blade during rotation, further reducing aerodynamic noise.

[0068] The ratio of N1 to N2 (0.5 ≤ N1 / N2 ≤ 2) avoids resonance at the blade passing frequency or the generation of strong discrete noise. For example, when the ratio of N1 to N2 is 0.2, the noise generated during the operation of fan assembly 1 increases; while when the ratio of N1 to N2 is 3, the noise generated during the operation of fan assembly 1 not only increases but also generates resonance noise. Therefore, the ratio of N1 to N2 ensures good aerodynamic interference matching between the power component and the stationary guide component, allowing the airflow to be smoothly transmitted from the rotating impeller to the stationary guide vanes.

[0069] The ratio of L1 / L2 (1.5≤L1 / L2≤3) reflects the functional division and length matching between the power section and the guide section. The longer depth L1 of the diagonal flow fan 11 ensures sufficient energy input, while the relatively short but functionally sufficient axial dimension L2 of the first blade 1211 enables efficient steering.

[0070] Specifically, based on different L1 / L2 ratios, the above-mentioned method for measuring wind speed is used, combined with the method specified in Appendix A or Appendix B of the national standard "AC Electric Fans and Speed ​​Regulators" (GB / T 13380-2018) to calculate the average wind speed of each ring, and then calculate the volume of air (air volume) delivered by the fan per unit time. During the test, the input power of the motor is measured synchronously using a power meter, and finally the actual energy efficiency is calculated by dividing the measured air volume by the measured motor input power.

[0071] The above measurements show that when the ratio of L1 to L2 is 2, the airflow reaches 310 m³ / min, with an energy efficiency of 16.8. However, when the ratio of L1 to L2 is 0.5, the airflow only reaches 277 m³ / min, with an energy efficiency of only 15.4. Therefore, the L1 / L2 ratio satisfies 1.5 ≤ L1 / L2 ≤ 3, which both improves the airflow of fan assembly 1 and optimizes its energy efficiency.

[0072] In this way, by optimizing and constraining the geometric parameter relationship of the diagonal flow fan 11, it is ensured that the diagonal flow fan 11 can generate high air pressure under large air volume, while efficiently coupling with the first-stage guide vane structure 121, providing a stable and high-quality airflow input for the subsequent second-stage acceleration, fundamentally improving the overall performance of the entire fan assembly 1.

[0073] In one embodiment, such as Figure 1 As shown, along the axial direction L of the housing 10, the distance between the end of the oblique flow blade 111 near the air outlet 102 and the end of the first blade 1211 near the air inlet 101 is e1. The value of e1 is not less than 1 mm and not greater than 9 mm. The preferred range of this distance e1 is 2 mm to 8 mm.

[0074] Understandably, a gap is also maintained between the diagonal flow fan 11 and the first blade 1211 along the axial direction L of the housing 10. This gap is designed to minimize the ineffective flow space between the airflow outlet of the diagonal flow fan 11 and the airflow inlet of the first-stage guide vane structure 121. After the airflow exits the rotating diagonal flow fan 11, it enters the stationary first-stage guide vane structure 121 almost immediately, without sufficient space and time to form large-scale vortices or flow separation.

[0075] This reduces aerodynamic interference losses between the diagonal flow fan 11 and the first-stage guide vane structure 121, improves the aerodynamic efficiency of the entire flow channel, and helps reduce noise generated by gap vortices.

[0076] In one embodiment, such as Figure 1 and Figure 3As shown, the fan assembly 1 also includes a motor mount 14. The motor mount 14 is a structural component for mounting and securing the drive motor 15, disposed on the guide vane 1210, and located on the side of the guide vane 1210 opposite to the first blade 1211. The motor mount 14 and the guide vane 1210 are integrally formed. Integral forming means that two components are made into a single, indivisible integral part through injection molding, die casting, or machining. Understandably, the integral forming of the motor mount 14 and the guide vane 1210 combines the mounting base of the motor 15 with the support structure of the first-stage guide vane structure 1211 into one unit. The rotating shaft of the motor 15 is coaxially connected to the diagonal flow fan 11, thereby driving the diagonal flow fan 11 to rotate.

[0077] This eliminates the assembly interface between the motor mount 14 and the air guide 1210, improving the rigidity and coaxiality of the entire assembly structure. It helps suppress vibration transmission during motor 15 operation, reducing noise. Better coaxiality ensures alignment of the center lines of the motor shaft, the diagonal-flow fan 11, and the air guide 1210, reducing mechanical friction and airflow pulsation caused by misalignment, thereby improving the smoothness, reliability, and efficiency of fan operation.

[0078] In one embodiment, such as Figure 1 As shown, the fan assembly 1 also includes an air inlet grille 16. The air inlet grille 16 is a grid-like or mesh-like component with filtering and protective functions, which is detachably installed at the air inlet end of the housing. Detachable installation means that it is connected by means of clips, screws, magnets, etc., allowing users or maintenance personnel to install and remove it.

[0079] Understandably, the air intake grille 16 is installed at the airflow inlet to perform preliminary filtration of the air entering the pressurized air duct 13, blocking larger dust particles, hair, and other debris, and protecting the internal oblique flow fan 11 and guide vanes from contamination or blockage. The removable design allows users to regularly clean or replace the grille, maintaining unobstructed airflow and hygiene.

[0080] Furthermore, the center of the air inlet grille 16 protrudes along the axial direction L away from the air inlet end 102, increasing the distance between the air inlet grille 16 and the diagonal flow fan 11. During the rotation of the diagonal flow fan 11, the air inlet grille 16 is less likely to collide with the diagonal flow fan 11 and generate noise. At the same time, during the use of the fan assembly 1, the user is less likely to come into direct contact with the diagonal flow fan 11, thus protecting the user's safety during use.

[0081] In this way, by setting the air inlet grille 16 at the air inlet end 101, basic protection functions are achieved while also taking into account the maintainability of the product and the user experience.

[0082] In one embodiment, such as Figure 8As shown, the housing 10 includes an outer shell 103, a duct shell 104, a guide shell 105, and a pressurization shell 106. The duct shell 104, guide shell 105, and pressurization shell 106 are functional sections within the housing 10, arranged sequentially along the airflow direction. The guide shell 105 surrounds and encloses the periphery of the first-stage guide vane structure 121. The pressurization shell 106 surrounds and encloses the periphery of the second-stage guide vane structure 122. The outer shell 103 is the outermost integral structural component. In other words, the radial dimension of the rotating seat 110 gradually increases along the axial direction L of the housing 10, extends to the guide seat 1210, and is smoothly connected to the guide seat 1210. The radial dimension of the guide seat 1210 gradually increases along the axial direction L of the housing 10, extends to the connecting seat 1220, and is smoothly connected to the connecting seat 1220. They are arranged sequentially along the airflow direction, corresponding to the air duct housing 104, the guide housing 105, and the pressurizing housing 106, and together form a pressurizing air duct 13 whose radial dimension gradually decreases along the airflow direction.

[0083] Understandably, these shell segments collectively enclose and form a pressurized air duct 13 connecting the inlet end 101 and the outlet end 102. The radial dimension of the pressurized air duct 13 gradually decreases along the airflow direction (from the inlet end to the outlet end). Specifically, the characteristic dimension of the cross-section of the pressurized air duct 13 near the inlet end 101 can be defined as h1, the characteristic dimension after passing through the first-stage guide vane region along the airflow direction can be defined as h2, the characteristic dimension after passing through the second-stage guide vane region can be defined as h3, and the characteristic dimension at the outlet end 102 can be defined as h4. These dimensions satisfy the relationship: h1>h2>h3>h4, that is, the cross-sectional area of ​​the air duct continuously shrinks. The ratio of the inlet end dimension h1 to the outlet end dimension h4 satisfies: 1.4 ≤ h1 / h4 ≤ 2.5.

[0084] According to the principle of continuity, for incompressible fluids, the mass flow rate is conserved across different cross-sections. Therefore, when the cross-sectional area of ​​the flow channel decreases, the fluid velocity must increase. In this embodiment, the design of h1 > h4 forces the airflow to accelerate from the inlet to the outlet. Bernoulli's principle further states that in a horizontal flow channel, an increase in velocity will lead to a decrease in the static pressure of the fluid. Therefore, the pressurized duct 13 not only increases the velocity of the outlet airflow but also helps to form a pressure gradient within the duct that is conducive to airflow stability. Limiting the contraction ratio (h1 / h4) to between 1.4 and 2.5 is an optimal choice for engineering.

[0085] If the ratio is too small (less than 1.4), the acceleration effect will be limited and it will be difficult to significantly increase the wind speed; if the ratio is too large (greater than 2.5), it may cause severe flow separation in the contraction section, generate strong eddies and large local drag loss, which will reduce efficiency and increase noise.

[0086] The gradual decrease from h1 to h4 (h1>h2>h3>h4) constitutes a smooth, multi-stage contraction process, further reducing turbulence generation and aerodynamic losses. The variable-diameter pressurized air duct 13, working in conjunction with the diagonal-flow fan 11 and the two-stage guide vanes, achieves efficient airflow guidance, smooth acceleration, and energy conversion, which is a key structural feature for improving the overall unit's wind speed, wind pressure, and energy efficiency.

[0087] Furthermore, this embodiment also provides a variety of feasible manufacturing and assembly solutions for the housing 10 and its internal structure. These solutions can be selected individually or in combination according to production needs, cost control, and performance objectives.

[0088] The first option is to manufacture the four parts—outer shell 103, air duct shell 104, air guide shell 105, and pressurization shell 106—into a single, indivisible integral part through injection molding, die casting, or other molding processes, i.e., integral molding.

[0089] The second option is to combine the guide shell 105 and the first-stage guide vane structure 121 into a single integral part using a one-piece molding technology.

[0090] The third option is to combine the pressure shell 106 and the secondary guide vane structure 122 into a single integral part using a one-piece molding technology.

[0091] The fourth option is to combine the outer shell 103 and the secondary guide vane structure 122 into a single integral part using a one-piece molding technology.

[0092] These solutions can be implemented independently, for example, by using only the guide shell 105 and the first-stage guide vane structure 121 as an integral part, while the other parts are manufactured separately; or they can be implemented in combination, for example, by using the outer shell 103, the air duct shell 104, the guide shell 105, and the pressurization shell 106 as an integral part, and the guide shell 105 and the first-stage guide vane structure 121 are also integrally formed.

[0093] In other words, this embodiment provides highly flexible design and manufacturing possibilities for the housing 10 and its internal structure. Dividing the housing into multiple functional segments (air duct housing 104, air guide housing 105, pressurization housing 106) facilitates modular design, separate manufacturing, and assembly, which is advantageous in scenarios involving small batches or frequent maintenance and replacement of specific components. Furthermore, the use of one-piece molding technology, whether integrating multiple housing segments 103 or integrating the housing 103 with the internal guide vane structure, significantly reduces the number of individual parts, simplifies the assembly process, and thus lowers production costs and improves production efficiency. Moreover, one-piece molding eliminates steps, gaps, or discontinuities caused by assembly seams between separate parts. This allows the pressurization air duct 13 to form a smooth, continuous, and well-sealed inner wall surface, effectively reducing frictional losses between the airflow and the wall. Together, these factors improve the overall aerodynamic efficiency of the air duct, contributing to higher airflow and velocity output and lower operating noise, ultimately improving the product's energy efficiency and performance.

[0094] In one embodiment, such as Figure 8 and Figure 9 As shown, the fan assembly 1 also includes a control panel 17. The control panel 17 is installed on the side of the connector 1220 away from the second blade 1221. That is, the second blade 1221 is arranged around the control panel 17. The control panel 17 faces the air outlet 102. The user can operate the control panel 17 directly at the air outlet 102 to control the working state of the fan assembly 1.

[0095] like Figure 9 As shown, this application also provides a purification fan head 3, including a fan assembly 1 and an air purification assembly 2. The air purification assembly 2 is a filter unit for removing pollutants from the air and is installed upstream of the air inlet end 101 of the fan assembly 1. The air purification assembly 2 and the fan assembly 1 are detachably connected. Detachable connection means that the two can be connected and separated by means of clips, threads, quick-release interfaces, etc.

[0096] Understandably, the air purification fan head 3 integrates efficient air delivery and air purification functions into one unit. The air purification component 2 is located upstream of the air inlet 101 of the fan component 1, so that all the air drawn in is first purified before being accelerated and blown out by the fan component 1, realizing the process of "purification before air delivery".

[0097] In this way, the air can be purified while the fan is in use, providing users with a good user experience. At the same time, the detachable connection design allows users to easily remove the air purification component 2 for cleaning or filter replacement, greatly improving the practicality and maintenance convenience of the product. It also allows for the selection of filter components with different purification capabilities according to different needs.

[0098] In one embodiment, such as Figure 10 As shown, the air purification assembly 2 includes a rear screen 20, a first filter 21, and a second filter 22. The rear screen 20 is a frame with a supporting structure and an internal receiving cavity, detachably mounted to the air inlet end 101 of the fan assembly 1. The first filter 21 is a barrel-shaped or annular filter, installed within the receiving cavity and surrounding the inner wall of the rear screen 20. The first filter 21 has a channel extending radially through it. The second filter 22 is a disc-shaped or tray-shaped filter, installed at the end of the first filter 21 away from the channel of the fan assembly 1.

[0099] In other words, the air purification component 2 employs a composite filtration design. The first filter 21 filters the air passing through the annular side of the rear filter 20, while the second filter 22 filters the air passing through the end face of the channel. This creates a multi-stage, multi-directional filtration surface, increasing the effective filtration area, reducing wind resistance, and enabling it to handle pollutants of different particle sizes. The combination of the first filter 21 and the second filter 22 allows the purification component to achieve maximum filter media loading within a limited space, thereby improving dust holding capacity and purification lifespan, ensuring long-lasting high purification efficiency even under high-volume fan operation.

[0100] like Figure 11 As shown, this application also provides a purification fan 4, including a base 40, a bracket 41, and a purification fan head 3. The base 40 is a stable base placed on the ground. The bracket 41 is a support frame connecting the base and the purification fan head 3. The purification fan head 3 is mounted on the bracket.

[0101] Understandably, the purifying fan 4 constitutes a complete indoor air conditioning product. The base 40 provides stability, and the bracket 41 supports the purifying fan head 3 at a suitable height. The head, which integrates efficient air delivery and purification functions, can circulate and purify indoor air.

[0102] This allows the purifying fan 4 to function as both a fan and an air circulation and purification device, improving indoor air quality and comfort while enhancing the functional integration of home appliances and providing users with a better user experience.

[0103] In one embodiment, the air purifier fan head 3 can rotate relative to the bracket 41. The rotational connection can be achieved by a rotary joint, bearing, or motor-driven oscillating mechanism.

[0104] In other words, the air purifier fan head 3 can rotate relative to the bracket 41, allowing the airflow direction to be adjusted horizontally or vertically. Users can direct the clean airflow to different areas of the room as needed, achieving faster and more uniform air circulation and purification, and avoiding dead zones. The oscillating design greatly enhances the product's practicality and user experience, enabling it to meet a wider range of scenario needs.

[0105] In the accompanying drawings of this embodiment, the same or similar reference numerals correspond to the same or similar components. In the description of this application, it should be understood that if terms such as "upper," "lower," "left," "right," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, they are only for the convenience of describing this application 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, the terms used to describe positional relationships in the drawings are only for illustrative purposes and should not be construed as limiting this application. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

[0106] The above are merely preferred embodiments of this application and are not intended to limit this application. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A fan assembly, characterized in that, include: The housing has an air inlet and an air outlet at its two axial ends, respectively; A diagonal-flow fan is rotatably mounted inside the housing; as well as A pressurizing component is installed inside the housing and located on the side of the diagonal flow fan near the air outlet. The pressurizing component and the diagonal flow fan together cooperate with the inner wall of the housing to form a pressurizing air duct that connects the air inlet and the air outlet. The pressurization component includes: A first-stage guide vane structure is located inside the housing and positioned behind the diagonal-flow fan along the airflow direction; and The second-stage guide vane structure is located inside the housing and is positioned behind the first-stage guide vane structure along the airflow direction; Furthermore, the first-stage guide vane structure is configured to adjust the airflow blown out by the oblique flow fan to tend towards the axial direction, and the second-stage guide vane structure is configured to accelerate the airflow.

2. The fan assembly as claimed in claim 1, characterized in that, The first-stage guide vane structure includes: a guide seat and a first blade, wherein a plurality of the first blades are arranged circumferentially along the outer surface of the guide seat; The first blade has a guide surface that is relatively arranged in the thickness direction. A plane perpendicular to the axial direction is defined as a reference surface. The angle between the guide surface and the reference surface gradually increases in the direction from the air inlet to the air outlet. The angle between the trailing edge of the guide surface and the reference surface is not less than 70° and not greater than 90°. And / or, the thickness of the first blade gradually decreases in the direction from the air inlet to the air outlet.

3. The fan assembly as claimed in claim 2, characterized in that, Each of the first blades is twisted; wherein, a sub-channel is formed between two adjacent first blades, and the centerline of the sub-channel is curved to guide the airflow blown by the oblique flow fan to be adjusted to tend towards the axial direction.

4. The fan assembly as claimed in claim 2, characterized in that, The secondary guide vane structure includes: a connecting seat and a plurality of second blades, wherein the plurality of second blades are arranged circumferentially along the outer surface of the connecting seat; Wherein, along the airflow direction, the thickness of the second blade near the air outlet is greater than its thickness near the air inlet.

5. The fan assembly as claimed in claim 4, characterized in that, Along the axial direction of the housing, the size of the first blade is larger than the size of the second blade.

6. The fan assembly as claimed in claim 4, characterized in that, The arrangement density of the second blade along the circumference of the connecting seat is greater than the arrangement density of the first blade along the circumference of the guide seat.

7. The fan assembly as claimed in claim 4, characterized in that, Along the axial direction of the housing, the distance between the end of the first blade near the air outlet and the end of the second blade near the air inlet (101) is not less than 1 mm and not more than 9 mm.

8. The fan assembly as claimed in claim 4, characterized in that, The oblique flow fan includes a rotating base and multiple oblique flow blades, the multiple oblique flow blades being evenly distributed on the surface of the rotating base around the rotation axis of the oblique flow fan; Along the axial direction of the housing, the size of the oblique flow blade is larger than the size of the first blade.

9. The fan assembly as claimed in claim 8, characterized in that, Along the axial direction of the housing, the distance between the end of the oblique flow blade near the air outlet and the end of the first blade near the air inlet is not less than 1 mm and not more than 9 mm.

10. The fan assembly as claimed in claim 2, characterized in that, It also includes a motor mount, which is disposed on the guide seat and located on the side of the guide seat away from the first blade, for mounting the motor.

11. The fan assembly as claimed in claim 1, characterized in that, It also includes an air intake grille, which is detachably mounted to the air intake end; The center of the air inlet grid protrudes axially away from the air inlet end.

12. The fan assembly as claimed in claim 4, characterized in that, It also includes a control panel, which is located on the side of the connector opposite to the second blade.

13. The fan assembly as claimed in any one of claims 1 to 12, characterized in that, The housing includes: an outer shell, a duct shell, a flow guide shell, and a pressurization shell; the duct shell, the flow guide shell, and the pressurization shell are arranged sequentially inside the outer shell; The guide shell is arranged around the periphery of the first-stage guide vane structure; the pressurization shell is arranged around the periphery of the second-stage guide vane structure. And / or, the outer shell, the air duct shell, the air guide shell, and the pressurization shell are integrally formed; And / or, the guide shell and the first-stage guide vane structure are integrally formed; And / or, the pressurized shell and the secondary guide vane structure are integrally formed; And / or, the outer shell and the secondary guide vane structure are integrally formed.

14. A purification fan head, characterized in that, include: The fan assembly as described in any one of claims 1 to 12; and An air purification component is installed at the air inlet end of the fan assembly; The air purification component and the fan component are detachably connected.

15. The purification fan head as described in claim 14, characterized in that, The air purification component has a rotating buckle at one end facing the fan component, and the air purification component is detachably connected to the fan component through the rotating buckle.

16. The air purification fan head as described in claim 14, wherein the air purification component comprises: The rear grille, having an internal cavity, is detachably mounted to the air inlet end of the fan assembly; A first filter screen is installed within the receiving cavity and is disposed around the inner wall of the rear screen; the first filter screen has a channel extending radially through it; and / or The second filter is installed at the end of the channel away from the fan assembly.

17. A purification fan, characterized in that, include: Base; The bracket is connected to the base; as well as The purification fan head as described in claim 13 is mounted on the bracket and is rotatable relative to the bracket.

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