Bladeless fan

Abstract

The application provides a bladeless fan, comprising: a shell provided with a cavity, an air inlet and an air outlet communicating with the cavity; a fan assembly arranged in the cavity and used for sucking air into the cavity from the air inlet and blowing the air out from the air outlet; the shell comprises a first member and a second member, and the first member and the second member form the cavity and the air outlet; wherein the second member comprises a base and a first flow guide part, the base is arranged with the fan assembly, the first flow guide part extends from the base, the first flow guide part is arranged at the radial outer side of the fan assembly, and the angle between the axial direction of the fan assembly and the horizontal direction is less than 60 degrees. The approximately horizontal air inlet / outlet can relatively shorten the airflow path, compared with the vertical air duct which needs to consume wind energy through multiple turning. The air duct structure of the application reduces the resistance loss. Moreover, the axial direction of the fan assembly is arranged in parallel with the horizontal direction, the airflow path is shortened, the gas short circuit and backflow are avoided, and the fan is closer to the user's blowing demand.

Description

Technical Field

[0001] This application relates to the field of fan technology, specifically to a bladeless fan with an optimized air intake and exhaust structure. Background Technology

[0002] Since its inception, bladeless fan technology has rapidly gained market recognition for its unique design concept and superior safety performance. Compared to traditional bladed fans, bladeless fans draw in and accelerate air through a turbine compressor within the base, then expel the high-speed airflow through an annular gap. Utilizing the Coanda effect, the airflow flows along a curved surface and draws in surrounding air, thus achieving an amplified airflow effect. This design eliminates high-speed rotating blades, improving not only operational safety but also producing a more stable and uniform airflow.

[0003] However, existing bladeless fans typically require air to be drawn in from the bottom of the base, accelerated by a turbine, and then transported upwards through an annular channel before finally being discharged through an annular gap. This process involves significant airflow deflection, numerous bends, and an excessively long duct path, leading to airflow separation from the duct walls, generating eddies and turbulence, consuming airflow energy, and reducing the outlet air velocity. Summary of the Invention

[0004] In view of this, this application provides a bladeless fan, in which a first air intake is disposed on the radially outer side of the fan assembly, and the angle between the axial direction of the fan assembly and the horizontal direction is less than 60 degrees. The approximately horizontal air intake / exhaust shortens the airflow path, compared to the need for multiple turns and energy loss in a vertical air duct. Furthermore, the parallel arrangement of the axial and horizontal directions of the fan assembly further shortens the airflow path, preventing short-circuiting and backflow of gas, thus better meeting the user's airflow needs.

[0005] This application provides a bladeless fan, comprising: a housing having a cavity, and an air inlet and an air outlet communicating with the cavity; a fan assembly disposed in the cavity for drawing air into the cavity from the air inlet and blowing it out from the air outlet; the housing includes a first component and a second component, the first component and the second component forming the cavity and the air outlet; wherein, the second component includes a base and a first guide portion, the fan assembly is mounted on the base, the first guide portion extends from the base and is disposed radially outward of the fan assembly, and the angle between the axial direction of the fan assembly and the horizontal direction is less than 60 degrees.

[0006] Furthermore, in the axial direction, the base is located on the front side of the fan assembly, the first drain portion is connected to the base, and the first drain portion extends radially from front to back.

[0007] Furthermore, the fan assembly includes a motor and an impeller, the motor driving the impeller to rotate; axially, the distance from the front end to the rear end of the impeller is defined as the axial length of the impeller, the distance from the front end to the rear end of the first flow guide is defined as the axial length of the first flow guide, and the ratio of the axial length of the first flow guide to the axial length of the impeller is greater than 1 / 2.

[0008] Furthermore, the second component also includes a second drainage portion, which is connected to the first drainage portion and extends radially from back to front, narrowing outwards.

[0009] Furthermore, on the axial section of the second component, both the first drainage portion and the second drainage portion are arranged in an arc shape, and the centroid of the arc of the first drainage portion and the second drainage portion is located on the radial inner side of the first drainage portion.

[0010] Furthermore, on the cross-section of the second component cut axially, the tangent at the rear end of the first drainage portion forms an acute angle with the tangent at the rear end of the second drainage portion.

[0011] Furthermore, the first component, together with the first and second drainage portions, forms an air outlet channel, and the first component and the second drainage portion form the air outlet, which is located at the end of the air outlet channel.

[0012] Furthermore, the maximum distance between the first drainage portion and the second drainage portion is less than 25mm.

[0013] Furthermore, the fan assembly includes a motor and an impeller, the motor driving the impeller to rotate; the impeller includes a hub and multiple blades, the motor is located on a first side of the hub, the multiple blades are connected to a second side of the hub, and the middle part of the hub protrudes towards the second side.

[0014] Furthermore, the air outlet is located on the radial outer side of the fan assembly, and the radial plane containing the air outlet passes through the fan assembly.

[0015] Compared with existing technologies, the bladeless fan of this application has the following advantages: With the first air intake located radially outside the fan assembly, and the angle between the fan assembly's axis and the horizontal direction being less than 60 degrees, the approximately horizontal air intake / exhaust shortens the airflow path. In contrast, vertical air ducts require multiple turns, consuming airflow energy, and the approximately horizontal air intake / exhaust reduces resistance loss. Furthermore, the fan assembly's axis is parallel to the horizontal direction, shortening the airflow path and preventing short-circuiting and backflow of gas, thus better meeting the user's airflow needs. Attached Figure Description

[0016] Figure 1This is a schematic diagram of one direction of the impeller in this application;

[0017] Figure 2 This is a schematic diagram of the impeller in another direction according to this application;

[0018] Figure 3 This is a front view of a bladeless fan according to an embodiment of this application;

[0019] Figure 4 This is a cross-sectional view of a bladeless fan according to an embodiment of this application;

[0020] Figure 5 yes Figure 4 Enlarged view of section D;

[0021] Figure 6 yes Figure 4 A diagram showing the removal of the fan assembly;

[0022] Figure 7 This is a schematic diagram showing the first component with the air intake shroud removed and the structure transparent.

[0023] Figure 8 This is a schematic diagram of the first component of an embodiment of this application;

[0024] Figure 9 This is a cross-sectional view of another embodiment of this application;

[0025] Figure 10 This is a cross-sectional view of another embodiment of this application;

[0026] Figure 11 This is a cross-sectional view of another embodiment of this application;

[0027] Figure 12 This is a cross-sectional view of another embodiment of this application. Detailed Implementation

[0028] To facilitate a better understanding of the purpose, structure, features, and effects of this application, the application will now be further described in conjunction with the accompanying drawings and specific embodiments.

[0029] It should be noted that when a component is considered to be "connected" to another component, it can be directly connected to the other component or there may be an intervening component present.

[0030] In this application, the use of terms such as "first" and "second" is for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated.

[0031] In the description of this application, the terms "front", "rear", "left", "right", "upper", "lower", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying 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, they should not be construed as limitations on this application.

[0032] like Figure 1 , Figure 2 and Figure 4 As shown, this application provides a powerful suction impeller 3. The impeller 3 includes a hub 301 and a plurality of blades 302. The hub 301 includes a first side 35 and a second side 36, which are opposite to each other. The first side 35 of the hub 301 houses a motor 2, and the plurality of blades 302 are connected to the second side 36 of the hub 301. The hub 301 includes a central portion 303, and each blade 302 extends outward from the edge of the central portion 303. The ratio of the radius of the central portion 303 to the radius of the hub 301 is 1 / 10 to 1 / 2. Preferably, the ratio of the radius of the central portion 303 to the radius of the hub 301 is 1 / 5 to 1 / 3. This impeller 3 design can expand the flow channel space at the root of the blades 302, reduce airflow obstruction, and thus improve intake efficiency and air volume. It shortens the gas flow path, reduces frictional loss between the fluid and the surface of the hub 301, and improves energy conversion efficiency. Furthermore, the hub 301 provides a larger support area for the blade 302, making it suitable for high-pressure, high-speed applications. This reduces stress concentration at the root of the blade 302, preventing fatigue fracture. The symmetrical blade design, combined with proportional design, optimizes rotational balance, reduces vibration caused by fluid pulsation or blade 302 deflection, and thus reduces noise.

[0033] The hub 301 protrudes towards the second side 36, and the surface of the second side 36 is arc-shaped. The middle portion 303 also protrudes towards the second side 36, and the axial height of the plurality of blades 302 on the second side 36 is lower than the axial height of the middle portion 303 on the second side 36. The arc-shaped protrusion of the middle portion 303 can guide the fluid to flow along a smooth curve, avoiding turbulence or backflow in the central region of the hub 301 and reducing energy loss. The high point formed by the protrusion of the middle portion 303 can accelerate the convergence of fluid towards the blade 302 region, enhancing the efficiency of fluid kinetic energy conversion into pressure and increasing head or wind pressure.

[0034] Each blade 302 includes a blade root 31 connecting to the hub 301, a blade tip 32 corresponding to the blade root 31, a leading edge 33 connecting the blade root 31 and the blade tip 32, and a trailing edge 34 corresponding to the leading edge 33 and connecting the blade root 31 and the blade tip 32. Each blade 302 extends spirally from the inside to the outside.

[0035] It should be understood that the impeller 3 can be a centrifugal impeller 3, a mixed-flow impeller 3, or an oblique-flow impeller 3.

[0036] like Figure 1 , Figure 2 , Figure 4 and Figure 5 As shown, the impeller 3 is a centrifugal impeller 3. The outer ends of the blade root 31 and the blade tip 32 extend outward beyond the edge of the hub 301, and the trailing edge 34 is located radially outside the hub 301. The trailing edge 34 is parallel to the axial direction, the line connecting the two ends of the blade leading edge 33 is perpendicular to the axial direction, and the angle between the line connecting the two ends of the blade tip 32 and the axial direction is an acute angle. The parallel axial design of the trailing edge 34 ensures that the fluid is thrown out radially when leaving the blade 302, which reduces eddy current losses caused by outflow turbulence and allows the fluid kinetic energy to be converted into static pressure energy more efficiently through the impeller 3. The line connecting the two ends of the blade leading edge 33 is perpendicular to the axial direction, indicating that the inlet of the blade 302 is a standard radial plane air intake. This design is suitable for scenarios with uniform axial air intake and reduces inflow angle of attack deviation. The line connecting the two ends of the blade tip 32 forms an acute angle with the axial direction. Essentially, the blade 302 deflects from the leading edge 33 to the trailing edge 34, which helps to extend the flow channel length and reduce airflow turbulence.

[0037] The blade root 31 and blade tip 32 extend outward beyond the edge of the hub 301, which essentially increases the coverage area of ​​the blade 302 in the radial direction of the hub 301. This design expands the cross-sectional area of ​​the fluid channel, allowing more fluid to fully receive the work done by the blade 302, thereby improving the flow processing capacity.

[0038] In other embodiments, reference is made to Figure 10 The angle between the line connecting the two ends of the leading edge 33 of the blade and the axial direction can be an acute angle or a right angle. Alternatively, refer to... Figure 8 and Figure 9Similarly, this is a centrifugal impeller, but the leading edge 33 of the blade and the middle part 303 are spaced apart, and the line connecting the two ends of the leading edge 33 is parallel to the axial direction. When the line connecting the leading edges 33 forms an acute angle with the axial direction, it essentially introduces a forward-swept design, which can capture the inflow in advance and reduce inlet airflow separation. When the leading edge 33 is completely parallel to the axial direction, the inlet of the blade 302 forms a smooth axial-radial transition flow channel, which is particularly suitable for the needs of some centrifugal impellers 3, reducing inflow deflection losses.

[0039] The hub 301 has an edge diameter of 40-200mm and an axial thickness of 28-35mm. The larger diameter of the hub 301 facilitates the formation of a larger suction surface, enhancing suction capacity. The larger axial thickness of the hub 301 also contributes to its overall structural strength and longer lifespan.

[0040] In one embodiment, the impeller 3 is a centrifugal impeller 3, and the number of blades 302 is 25-45. The spacing between two adjacent blades 302 increases from the inside out, with a minimum spacing of 0.6-3 mm and a maximum spacing of 8-12.5 mm. In high-flow-rate applications, increasing the number of blades 302 can significantly reduce relative vortices within the impeller 3 flow channel, improve the efficiency of gas capture by the blades 302, thereby enhancing theoretical wind pressure output. The high-density blade 302 layout can mitigate uneven velocity distribution in the inlet region. Smaller spacing near the center accelerates fluid entry into the flow channel, avoiding edge separation and vortices caused by insufficient velocity. Larger spacing near the edge stabilizes the outlet velocity, reduces turbulent dissipation of kinetic energy in the impeller 3, and improves stationary blade conversion efficiency.

[0041] refer to Figure 11 In one embodiment, the first side 35 of the hub 301 is further provided with an extension wall, which protrudes and forms a receiving portion with the hub 301. The receiving portion houses the motor 2. The inner and / or outer sides of the extension wall are provided with multiple reinforcing ribs, which connect the hub 301 and the extension wall. The second side 36 of the hub 301 protrudes so that the first side 35 houses the motor 2, making reasonable use of space. The multiple reinforcing ribs help to enhance the structural strength.

[0042] like Figures 2 to 5As shown, this application also provides a bladeless fan. The bladeless fan includes a housing 1 and a fan assembly. The housing 1 has a cavity 11, and an air inlet 12 and an air outlet 13 communicating with the cavity 11. The fan assembly is disposed in the cavity 11 and is used to draw air into the cavity 11 from the air inlet 12 and blow it out from the air outlet 13. The fan assembly includes an impeller 3 and a motor 2, and the motor 2 drives the impeller 3 to rotate. The bladeless fan is not completely devoid of blades 302, but rather the blades 302 are hidden inside the housing 1. The core principle is to use the fan assembly to draw in air and then blow the air out through a specially designed air duct. The impeller 3 of the bladeless fan is located inside the housing 1 of the bladeless fan. The housing 1 has an air inlet 12 and an air outlet 13. The interior of the housing 1 is provided with a flow channel. Through the air inlet 12 on the housing 1, air around the housing 1 can be drawn into the interior of the housing 1 through the impeller 3 and transported to the air outlet 13 of the housing 1 through the flow channel inside the housing 1.

[0043] The housing 1 includes a first component 1A and a second component 1B. The first component 1A includes a first guide portion 1011 and a second guide portion 1012. The first guide portion 1011 forms the air inlet 12 corresponding to the impeller 3, and the second guide portion 1012 and the second component 1B form the air outlet 13. It should be understood that the air outlet 13 can be arranged circumferentially, spaced apart along the circumference, or only partially arranged. In this embodiment, the air outlet 13 is arranged circumferentially, which provides a wider air outlet range and increases the air outlet area.

[0044] The first guide portion 1011 tapers radially along the air intake direction, and the air inlet 12 is formed on the radially inner side of the first guide portion 1011 corresponding to the impeller 3. The hub 301 protrudes towards the second side 36; in this embodiment, the hub 301 protrudes towards the air inlet 12. The middle portion 303 protrudes rearward into the air inlet 12. The first guide portion 1011 gradually tapers along the air intake direction, forming a Venturi tube effect, which accelerates the airflow before it enters the impeller 3, reducing inlet turbulence and boundary layer separation. This design improves intake efficiency, especially suitable for high-speed impellers 3, avoiding load fluctuations in the impeller 3 due to uneven intake. The tapered air inlet 12 is directly aligned with the center of the impeller 3, ensuring that the airflow enters the blade 302 with the minimum turning angle, reducing inflow impact loss. The middle portion 303 of the hub 301 protrudes towards the air inlet 12 to form a guide cone, guiding the airflow smoothly along the arc surface of the hub 301 into the blade root 31 region, eliminating the root vortex caused by a traditional flat hub 301. The protruding structure shortens the airflow path from the air inlet 12 to the hub 301, reducing flow resistance and making it suitable for high-flow-rate scenarios.

[0045] At least a portion of the second guide section 1012 is located radially outside the first guide section 1011. The second guide section 1012 and the second component 1B form an air outlet channel 1a, which connects the air outlet of the impeller 3 and the air outlet 13. The cross-sectional area of ​​at least a portion of the air outlet channel 1a decreases along the air outlet direction. The second guide section 1012 is located radially outside the first guide section 1011, making full use of the annular space. The first guide section 1011 is responsible for guiding the airflow, while the second guide section 1012 is responsible for accelerating the airflow, with a clear division of labor to reduce interference. The leading edge 33 of the blade is close to the air inlet 12, and the trailing edge 34 of the blade is close to the air outlet channel 1a. The trailing edge 34 of the blade is directly aligned with the inlet of the tapering air outlet channel 1a, reducing airflow deflection losses. After the high-speed rotating centrifugal impeller 3 throws the airflow radially out, it directly enters the tapering flow channel, avoiding energy dissipation caused by abrupt changes in the flow channel in traditional designs. The leading edge 33 of the blade is close to the air inlet 12, and the trailing edge 34 is adjacent to the inlet of the air outlet channel 1a, shortening the airflow path and reducing flow resistance loss. This design is suitable for miniaturized devices in high-flow-rate scenarios, such as floor fans, desktop fans, and handheld fans. After the airflow is accelerated by the hidden impeller 3, it is discharged through the tapered channel, with no exposed blades 302, completely avoiding the risk of pinching injuries, making it especially suitable for families with children and pets. The efficient pressurization of the tapered channel reduces the fan load, and the power consumption of the motor 2 is reduced for the same airflow.

[0046] like Figures 4 to 6 ,as well as Figures 8 to 10 As shown, the first component 1A includes a third guide portion 1013, which is disposed corresponding to the portion of the blade tip 32. A portion of the second guide portion 1012 is located within the cavity 11, and another portion of the second guide portion 1012 is located outside the cavity 11. The portion of the second guide portion 1012 located within the cavity 11, together with the third guide portion 1013 and the first guide portion 1011, forms the rear cavity 101.

[0047] The first guide section 1011 is disposed corresponding to the air inlet 12, the second guide section 1012 is disposed corresponding to the air outlet 13, and the third guide section 1013 is disposed corresponding to the cavity 11. The third guide section 1013 is disposed on the same edge of multiple blades 302. The first guide section 1011 is connected to the second guide section 1012, and the third guide section 1013 is located between the first guide section 1011 and the second guide section 1012. Specifically, the third guide section 1013 faces multiple blade tips 32. The three guide sections work together to guide the airflow. The converging structure of the first guide section 1011 accelerates the inflow and reduces the risk of inlet airflow separation. The second guide section 1012, in conjunction with the tapered air outlet channel 1a design, converts dynamic pressure into static pressure, increasing the outlet air velocity. The third guide section 1013 guides the airflow at the blade tips 32 to smoothly change direction, avoiding turbulent outflow from the impeller 3 and reducing the turbulence intensity at the impeller 3 outlet. The third guide portion 1013 is spaced apart from the blade tip 32, with a distance of 1.5-3 mm between them. This precise 1.5-3 mm gap between the third guide portion 1013 and the blade tip 32 forms a narrow annular flow channel. This design suppresses eddies and airflow leakage at the blade tip 32, reduces turbulent kinetic energy dissipation, and improves the efficiency of the impeller 3. Too small a gap can easily cause frictional noise, while too large a gap leads to backflow losses. The balanced value of 1.5-3 mm achieves a balance between sealing and safety.

[0048] like Figures 4 to 6 As shown, in this embodiment, the first guide section 1011, the second guide section 1012, and the third guide section 1013 partially enclose a relatively closed rear cavity 101. This closed structure forces the airflow along a preset path, reducing turbulence loss and increasing the outlet pressure. Furthermore, the rear cavity 101 isolates the high-frequency noise from the motor 2 and the impeller 3; combined with sound-absorbing cotton, noise reduction can be further achieved. The third guide section 1013 corresponds to the blade tip 32 area, and its arc-shaped or planar design guides the airflow at the blade tip 32 smoothly into the outlet duct, preventing vortex separation.

[0049] refer to Figures 9 to 11 In other embodiments, the first guide portion 1011, the second guide portion 1012, and the third guide portion 1013 form an open rear cavity 101. The first guide portion 1011, the second guide portion 1012, and the third guide portion 1013 can be interconnected, or the third guide portion 1013 can be connected only to the first guide portion 1011, or the third guide portion 1013 can be not directly connected to either the first guide portion 1011 or the second guide portion 1012. This open structure also provides the capability for voltage boosting and noise reduction.

[0050] like Figures 4 to 6 ,as well as Figures 9 to 11As shown, multiple leading edges 33 of the blades are positioned close to the center of the impeller 3, and these multiple leading edges 33 correspond to the air inlet 12. Multiple trailing edges 34 of the blades are positioned away from the center of the impeller 3, and these trailing edges 34 correspond to the air outlet 1a. The leading edges 33 are concentrated close to the center of the impeller 3, allowing the airflow to enter the blade 302 flow channel with the minimum turning angle, reducing inflow impact loss. The trailing edges 34 extend outward to the outer edge of the hub 301, precisely connecting with the gradually narrowing inlet of the air outlet 1a, ensuring that the high-speed airflow is directly thrown into the pressurization flow channel after radial ejection, reducing kinetic energy dissipation. The third guide portion 1013 is annular and extends to the air outlet 1a. The annular third guide 1013 covers the blade tip 32 region and extends to the air outlet 1a, guiding the airflow at the blade tip 32 to a smooth direction and preventing high-speed airflow from impacting the inner wall of the second guide 1012 and generating separation vortices. It also constrains the airflow to enter the narrowing air outlet 1a along a predetermined path, enhancing the Venturi effect and significantly increasing the wind speed at the air outlet 13. The annular structure wraps around the blade tip 32 region, blocking the outward propagation of noise from vortex shedding at the blade tip 32, effectively suppressing noise.

[0051] The shape of a portion of the hub 301 is adapted to the shape of a portion of the third guide 1013. The axial projections of the third guide 1013 and the hub 301 overlap, and / or the radial projections of the third guide 1013 and the hub 301 overlap. The contours of the hub 301 and the third guide 1013 match, forming a smoothly transitioned flow channel surface, significantly reducing the separation vortices between the hub 301 and the third guide 1013, and reducing turbulent kinetic energy dissipation. The overlap of axial and radial projections makes the third guide 1013 an extension of the hub 301, jointly constraining the airflow path in the blade 302 region. A portion of the blade tip 32 is exposed at the air inlet 12, forming a larger suction surface and shortening the local airflow path, thus enhancing flow efficiency.

[0052] like Figures 4 to 8As shown, the air outlet 13 is located at one end of the air outlet channel 1a, and multiple guide vanes 15 are spaced apart at the air outlet channel 1a. At least a portion of the multiple blades 302 extend spirally along a first direction, and at least a portion of the multiple guide vanes 15 extend spirally along a second direction opposite to the first direction. The spiral extension of the blades 302 along the first direction gives the airflow initial rotational kinetic energy; while the spiral extension of the guide vanes 15 along the second direction forms a reverse swirling flow field. This design can counteract the rotational component of the airflow at the outlet of the impeller 3, reduce turbulent kinetic energy dissipation, and improve static pressure conversion efficiency. The reverse spiral structure of the guide vanes 15 forces the airflow to undergo secondary rectification within the air outlet channel 1a, converting disordered vortices into axial flow, reducing velocity fluctuations at the air outlet 13, and improving the consistency of the air delivery distance. The guide vanes 15 are spaced apart in the tapering air outlet channel 1a, and combined with the reverse spiral extension of the guide vanes 15, further accelerate the airflow and enhance the Coanda effect. When the high-speed airflow adheres to the curved surface of the guide vanes 15, turbulence is reduced. The spaced guide vanes 15 divide the air outlet channel 1a into multiple sub-channels, forcing the airflow to be evenly distributed. Combined with the reverse spiral guide, it eliminates the jet deflection phenomenon caused by local high-speed areas, resulting in a wider air outlet coverage.

[0053] like Figures 4 to 6 ,as well as Figures 9 to 11 As shown, the second component 1B includes a first flow guide 1031 and a second flow guide 1032. The first flow guide 1031 is located inside the cavity 11, and the second flow guide 1032 is located outside the cavity 11. The second guide 1012, the first flow guide 1031, and the second flow guide 1032 together form the air outlet channel 1a and the air outlet 13. The second guide 1012, the first flow guide 1031, and the second flow guide 1032 together constitute the main body of the air outlet channel 1a. The three components work together to form a narrowing flow channel, which accelerates the airflow and reduces turbulence losses. The first flow guide 1031 optimizes the internal flow field, and the second flow guide 1032 and the second guide 1012 control the airflow diffusion direction, avoid airflow scattering, and improve the directionality of the airflow.

[0054] refer to Figure 7 and Figure 8Multiple guide vanes 15 are formed on the second guide portion 1012, or multiple guide vanes 15 are formed on the second component 1B. Alternatively, multiple guide vanes 15 are formed individually, and multiple guide vanes 15 simultaneously contact the first component 1A and the second component 1B, with the connection between the first guide portion 1031 and the second guide portion 1032 abutting against multiple guide vanes 15. Multiple guide vanes 15 form recesses 151 corresponding to the second component 1B, and multiple recesses 151 accommodate the connection between the first guide portion 1031 and the second guide portion 1032. The guide vanes 15 pre-formed recesses 151 corresponding to the second component 1B to accommodate the connection between the first guide portion 1031 and the second guide portion 1032, forming a mechanical interlock. Furthermore, this design can reduce the distance between the first component 1A and the second component 1B, which is beneficial for forming a tapered air outlet channel 1a, thereby enhancing wind pressure and increasing the air delivery distance.

[0055] like Figures 4 to 6 ,as well as Figures 9 to 11 As shown, the air outlet channel 1a is curved, and the airflow in the air outlet channel 1a flows both axially and radially. Axially, the airflow flows backward first and then forward, while radially, the airflow flows outward. The curved design of the air outlet channel 1a allows the airflow to undergo a combined axial and radial motion. This structure, through the synergistic effect of centrifugal force and the Coanda effect, facilitates the formation of negative pressure, attracting more external air in. Furthermore, the curved air outlet channel 1a makes full use of the radial space, which is beneficial for forming a larger air outlet surface and reducing product thickness. The axial backward-forward flow path extends the sound wave propagation path, canceling out specific frequency noise through phase interference. The guide vane 15 and the blade 302 are spaced apart axially and radially. The axial spacing avoids wake interference between the blade 302 and the guide vane 15, reducing periodic vortex shedding; the radial spacing expands the flow channel expansion space, matching the radial acceleration process of the airflow and avoiding noise caused by local overspeed. At least a portion of the air outlet channel 1a is located radially outside the impeller 3.

[0056] The air outlet duct 1a is located radially outside the impeller 3, forming a double-ring structure. The impeller 3 in the inner ring focuses on kinetic energy input, while the guide vanes 15 in the outer ring are responsible for flow field rectification. This clear division of labor reduces mutual vibration interference. From back to front, at least a portion of the plurality of blades 302 extends spirally in a clockwise direction, and at least a portion of the plurality of guide vanes 15 extends spirally in a counterclockwise direction. The counterclockwise spiral extension of the guide vanes 15 optimizes the airflow angle of attack and reduces energy loss from impact with the wake of the impeller 3. Alternatively, from back to front, at least a portion of the plurality of blades 302 can extend spirally in a counterclockwise direction, and at least a portion of the plurality of guide vanes 15 can extend spirally in a clockwise direction.

[0057] At least a portion of the radially inner surface of the first guide section 1031 faces the air outlet channel 1a, and at least a portion of the radially outer surface of the second guide section 1032 faces the air outlet channel 1a. The air outlet channel 1a is radially bent, and the turning point is located at the connection between the first guide section 1031 and the second guide section 1032, resulting in a contraction of the flow channel cross-sectional area, accelerated airflow jetting, and increased outlet wind speed. On the axially cut section of the second component 1B, the tangent at the rear end of the first guide section 1031 forms an acute angle with the tangent at the rear end of the second guide section 1032. This acute angle between the tangents at the rear ends of the first guide section 1031 and the second guide section 1032 prevents airflow separation vortices and ensures a smooth flow transition.

[0058] The second component 1B further includes a base 1035, which is connected to the front end of the first guide portion 1031, and the motor 2 is fixed to the base 1035. The axial length of the first guide portion 1031 is greater than the axial length of the trailing edge 34 of the blade. The first guide portion 1031 extends rearward from the base 1035 and extends rearward beyond the rear end of the trailing edge 34. The first guide portion 1031 is arranged radially outside the trailing edge 34, and the radial distance between the first guide portion 1031 and the trailing edge 34 increases from front to back. The first guide portion 1031 extends rearward beyond the trailing edge 34 to directly capture the high-speed airflow ejected by the impeller 3, reducing energy loss; the second guide portion 1032 extends forward to form a guide nozzle, constraining the axial jet direction of the airflow and increasing the air delivery distance.

[0059] like Figures 4 to 6 As shown, the first drainage portion 1031 is connected to the base 1035 and extends rearward from the base 1035. The second drainage portion 1032 is connected to the first drainage portion 1031 and extends forward from the first drainage portion 1031.

[0060] The first drainage portion 1031 and the second drainage portion 1032 are arranged radially inward and outward, and are connected. At least a portion of the first drainage portion 1031 extends radially from front to back, increasing in size, and at least a portion of the second drainage portion 1032 extends radially from back to front, decreasing in size. In a cross-section axially cut by the second member 1B, the tangent at the rear end of the first drainage portion 1031 forms an acute angle with the tangent at the rear end of the second drainage portion 1032.

[0061] At least a portion of the first flow guide 1031 extends radially, increasing in size from front to back, while at least a portion of the second flow guide 1032 extends radially, decreasing in size from back to front. The air outlet channel 1a is radially bent, with the bend corresponding to the connection point of the first flow guide 1031 and the second flow guide 1032. The radially increased size of the first flow guide 1031 adapts to the diffusion of airflow at the impeller 3 outlet, while the radially reduced size of the second flow guide 1032 focuses the kinetic energy of the airflow, achieving synergistic flow guidance. The bent air outlet channel 1a and the segmented flow guide structure facilitate acceleration and pressurization, while the sharp-angle connection suppresses vortices. The base 1035 integrates vibration resistance, and the bent nodes enhance rigidity.

[0062] In the axial direction, the distance from the front end to the rear end of the impeller 3 is defined as the axial length of the impeller 3, and the distance from the front end to the rear end of the first guide section 1031 is defined as the axial length of the first guide section 1031. The ratio of the axial length of the first guide section 1031 to the axial length of the impeller 3 is greater than 1 / 2. The axial length of the first guide section 1031 is less than the axial length of the fan assembly. The high-speed airflow ejected by the impeller 3 has a certain distribution range in both the axial and radial directions. The relatively long first guide section 1031 ensures that its flow channel can completely cover and receive all the airflow swept out by the trailing edge 34 of the blade, avoiding some high-energy airflow from directly leaking into the ineffective area and causing energy loss. The main function of the first guide section 1031 is to decelerate and pressurize the high-speed airflow. This physical process requires sufficient length to complete. A sufficiently long outlet channel 1a helps to stabilize the flow field, weaken the backflow phenomenon caused by pressure pulsation, and ensure that the airflow moves stably towards the outlet.

[0063] like Figures 9 to 11As shown, in another embodiment, portions of the first drainage portion 1031 and the second drainage portion 1032 overlap, while portions of the first drainage portion 1031 and the second drainage portion 1032 are spaced apart. Specifically, the forward portion of the first drainage portion 1031 and the forward portion of the second drainage portion 1032 overlap, while the rearward portion of the first drainage portion 1031 and the rearward portion of the second drainage portion 1032 are spaced apart. The end of the rearward portion of the first drainage portion 1031 forms a first lug 1033, and the end of the rearward portion of the second drainage portion 1032 forms a second lug 1034. The first drainage portion 1031 includes the first lug 1033, and the second drainage portion 1032 includes the second lug 1034, with the first lug 1033 and the second lug 1034 spaced apart. The first lug 1033, the second lug 1034, and portions of the second drainage portion 1032 together form an open sound-absorbing cavity. The first lug 1033 and the second lug 1034 are spaced apart, forming a V-shaped guide ridge on the surface of the second drainage portion 1032. This guides the airflow to smoothly change direction along the sidewall of the lug, avoiding separation vortices caused by abrupt changes in the flow channel. The open cavity formed by the first lug 1033, the second lug 1034, and the second drainage portion 1032 constitutes a Helmholtz resonator, achieving sound energy absorption. The inner shell of the sound-absorbing cavity is further equipped with a sound-absorbing structure to further absorb noise.

[0064] like Figures 4 to 6 ,as well as Figures 9 to 11 As shown, the first component 1A and the second component 1B are coaxially arranged. On a cross-section taken along the axial direction of the first component 1A and the second component 1B, both the first component 1A and the second component 1B have arc-shaped structures, with the arc-shaped structure of the second component 1B extending into the arc-shaped structure of the first component 1A. The arc-shaped structure of the first component 1A includes a first guide portion 1011 and a second guide portion 1012. The first guide portion 1011 extends forward and radially narrows to form the air inlet 12. The arc-shaped structure of the second component 1B extends into the first component 1A, forming a nested flow channel. The inner layer guides the core airflow, while the outer layer constrains the peripheral airflow, reducing boundary layer separation losses. The coaxial arc-shaped structure ensures that the airflow smoothly changes direction along a predetermined path, avoiding vortices caused by abrupt changes.

[0065] The second guide portion 1012 and at least a portion of the second component 1B are arranged radially inward and outward, and the radial plane of the front end of the second guide portion 1012 passes through the impeller 3. The front end of the second guide portion 1012 is the air outlet 13, and the radial plane of the front end of the second guide portion 1012 passes through the impeller 3, so that the air outlet position is approximately radially matched with the position of the impeller 3, which is beneficial to the overall structural stability.

[0066] like Figures 4 to 6 As shown, the second guide portion 1012 extends radially from front to back, and then extends radially from back to front. The first guide portion 1011 is connected to the middle region of the second guide portion 1012. The arc-shaped structure of the second component 1B includes a first guide portion 1031 and a second guide portion 1032, which extend into the second guide portion 1012. Regions are provided radially inside and outside the first component 1A and the second component 1B, and from the outside in, the following are sequentially arranged: the radially increasing portion of the second guide portion 1012 from back to front, the second guide portion 1032, the first guide portion 1031, and the radially increasing portion of the second guide portion 1012 from front to back. The radially increasing section of the second guide portion 1012 from front to back cooperates with the first guide portion 1031 to form a diffuser section, which decelerates and pressurizes the airflow, reducing turbulent kinetic energy dissipation. The second guide section 1012, with its radially increasing section from rear to front, cooperates with the second guide section 1032 to form a secondary contraction and diffusion section. The airflow is decelerated and pressurized again before flowing out, avoiding separation vortices caused by sudden changes in flow velocity and increasing the air delivery distance. The first component 1A and the second component 1B adopt an arc-shaped structure design to disperse periodic vortices and reduce high-frequency noise.

[0067] like Figures 4 to 6 ,as well as Figures 9 to 11 As shown, a portion of the second flow guide 1032 is disposed inside and outside at least a portion of the first component 1A, with a portion of the second flow guide 1032 exposed outwards. The axial length of the outwardly exposed portion of the second flow guide 1032 is greater than the axial length of the portion of the second flow guide 1032 disposed inside and outside the first component 1A. The outwardly exposed portion of the second flow guide 1032 includes a guiding arc surface 103, which is radially tapered from back to front. The radially tapering guiding arc surface 103 of the exposed portion of the second flow guide 1032 forms a tapering flow surface, guiding the fluid to slightly contract inwards. Simultaneously, the guiding arc surface 103 guides the fluid to smoothly change direction, reducing turbulence and energy loss. Furthermore, according to the Coanda effect, the convex arc shape of the guiding arc surface 103 allows for the additional forward delivery of airflow from the external space, resulting in a larger air multiplication area.

[0068] The first air intake 1031 extends from the base 1035 and is located radially outward of the fan assembly. The angle between the axial direction and the horizontal direction of the fan assembly is less than 60 degrees. The airflow is relatively concentrated in the axial direction, allowing for more applications such as floor fans, desktop fans, and handheld fans. In other words, the fan assembly's shaft is approximately horizontal, and the fan assembly delivers air approximately horizontally. The main human activity area is concentrated at heights of 0.8-1.5 meters when seated and 1.5-1.8 meters when standing. Horizontal airflow can directly cover this range, avoiding temperature stratification caused by vertical airflow needing to traverse the entire height of the space. Furthermore, compared to bladeless fans with bottom air intake in existing technologies, which are prone to drawing in just-exhausted airflow and creating airflow short-circuiting, the approximately horizontal air intake / exhaust design, through spatial separation, blocks the return path and improves the effective airflow utilization rate. A roughly horizontal air intake / exhaust system can relatively shorten the airflow path, compared to a vertical air duct that requires multiple turns—such as bottom intake, vertical flow into the top exhaust, annular flow channel at the exhaust, and horizontal exhaust at the top. A roughly horizontal air intake / exhaust system reduces resistance loss. In this embodiment, the fan assembly is arranged with its axis parallel to the horizontal direction, shortening the airflow path, preventing short-circuit backflow of gas, and better meeting the user's airflow needs.

[0069] Axially, the base 1035 is located at the front of the fan assembly. The first airflow guide 1031 is connected to the base 1035 and extends radially from front to back. The first airflow guide 1031 is located radially outside the fan assembly, forming an annular airflow guide cavity. The inner layer of the fan assembly accelerates the core airflow, while the outer layer of the air outlet channel 1a constrains the peripheral airflow, preventing boundary layer separation. The base 1035 is located at the front of the fan assembly, which facilitates the formation of the air outlet channel 1a, which extends backward and then forward, resulting in a reasonable structural arrangement. The fan assembly is mounted on the base 1035, with the first airflow guide 1031 facing the air outlet channel 1a. The diameter of the base 1035 is larger than the diameter of the fan assembly. The first airflow guide 1031 is connected to the base 1035 and extends rearward from the base 1035, circling the radially outside of the fan assembly. The first drainage portion 1031 extends radially backward from the base 1035, and during this extension, at least a portion of the slope of the first drainage portion 1031 decreases. The motor 2 is disposed between the base 1035 and the hub 301. The minimum distance between the base 1035 and the hub 301 is 2-4 mm.

[0070] On the axial section of the second component 1B, both the first guide section 1031 and the second guide section 1032 are arranged in an arc shape, and the centroids of the arcs of the first guide section 1031 and the second guide section 1032 are located radially inside the first guide section 1031. The arc design of both the first guide section 1031 and the second guide section 1032 forms a smoothly transitioned flow channel surface, reducing airflow separation and turbulence intensity. The arc-shaped flow channel guides the airflow to move laminarly along a preset path, reducing kinetic energy dissipation. The centroids of both guide sections are located radially inside the first guide section 1031, forming a centripetal converging flow field, enhancing the axial acceleration effect of the core airflow, and increasing the outlet velocity. The centroids of both guide sections are biased towards the inside of the first guide section 1031, forming a mechanical lever effect. The first guide section 1031 bears the main airflow impact force, while the second guide section 1032 provides a reverse supporting torque, dispersing stress concentration points.

[0071] The first component 1A, together with the first guide portion 1031 and the second guide portion 1032, forms an air outlet channel 1a. The first component 1A and the second guide portion 1032 form the air outlet 13, which is located at the end of the air outlet channel 1a. The maximum distance between the first guide portion 1031 and the second guide portion 1032 is less than 25mm, reducing the overall cross-sectional area. The air outlet 13 is located on the radially outer side of the fan assembly, and the radial plane containing the air outlet 13 passes through the fan assembly. The inner fan assembly accelerates the core airflow, while the outer air outlet channel 1a guides the high-speed airflow ejected from the impeller 3.

[0072] The bladeless fan also includes an air inlet shroud 102, which is located upstream of the air inlet 12. The maximum diameter of the air inlet shroud 102 is greater than or equal to the diameter of the air inlet 12. The first component 1A includes a first guide portion 1011, which tapers radially from back to front. The front end of the first guide portion 1011 forms the air inlet 12, and the radial plane of the front end of the first guide portion 1011 passes through the hub 301. The large-diameter air inlet shroud 102 expands the ambient air capture range, achieving low-turbulence air intake and reducing energy loss. The radial plane of the front end of the first guide portion 1011 passes through the hub 301, ensuring that the airflow in the central region of the impeller 3 is directly guided, avoiding vortex separation caused by inflow deflection.

[0073] like Figure 4 and Figure 6As shown, the air inlet shroud 102 protrudes rearward axially, forming a larger air intake surface. The air inlet shroud 102 is sheet-like, with multiple ventilation openings 1021 penetrating its surface, each ventilation opening 1021 connecting to the air inlet 12. The air inlet shroud 102 also includes a ring-shaped structure with multiple ventilation openings 1021 penetrating it, each ventilation opening 1021 connecting to the air inlet 12. In another embodiment, as... Figures 9 to 11 As shown, the air inlet hood 102 is a cover plate structure. The air inlet hood 102 and the first component 1A are spaced apart to form a ventilation opening 1021, which connects to the air inlet 12. The cover plate and the first component 1A are spaced apart to form the ventilation opening 1021. By adjusting the spacing, the airflow cross-sectional area is controlled to balance the flow velocity and resistance, preventing hair or large foreign objects from directly entering. The air inlet hood 102 is connected to the first component 1A. At the connection point between the air inlet hood 102 and the first component 1A, near the connection point between the first guide portion 1011 and the second guide portion 1012, a triangular support frame is formed to improve the overall deformation resistance.

[0074] like Figures 4 to 6 , Figures 9 to 12 As shown, the second component 1B has a flow guide 16 on its front side, and there is a gap between the flow guide 16 and the base 1035. The flow guide 16 is recessed rearward corresponding to the position of the base 1035. A front cavity 104 is formed between the flow guide 16 and the base 1035, and the front cavity 104 is used to accommodate the component.

[0075] The second component 1B and the air guide 16 together are roughly in the shape of a double-layered bowl. The second component 1B mainly forms the bottom wall of the inner dish and part of the side wall of the outer dish, while the air guide 16 mainly forms the bottom wall of the outer dish and part of the side wall of the outer dish. The second component 1B includes a guiding arc surface 103, and the air guide 16 includes a guiding surface 161. The guiding arc surface 103 and the guiding surface 161 are connected to guide the airflow along the wall. The fan assembly is installed on the part of the second component 1B facing the cavity 11. A front cavity 104 is formed between the inner and outer dishes, which can be used to house electronic components. For example, the front cavity 104 houses the display component 6, thereby displaying the operating parameters of the bladeless fan to the outside of the air guide 16. The operating parameters include, but are not limited to, the operating mode, current wind speed, and current battery level. It should be understood that the display component 6 may include touch screen operation functionality, allowing the user to adjust the bladeless fan through touch sensing. In addition, the front cavity 104 also has the function of absorbing vibration and noise. Of course, the outer disc bottom of the air guide 16 can be recessed in the air inlet direction; it can also be protruding in the air outlet direction; or it can be partially recessed in the air inlet direction and partially protruding in the air outlet direction; or it can be neither recessed nor protruding. In other embodiments, the front cavity 104 can also be used to set up lights, contain trend images, etc.

[0076] It should be understood that Figures 4 to 6 as well as Figures 9 to 12 The bladeless fan shown may further include a base 4. The base 4 is located below the housing 1. The third component 1C connects the base 4 and the first component 1A, or the third component 1C connects the base 4 and the second component 1B, making the overall structure more stable. A power supply component 5 is provided inside the base 4. The power supply component 5 is electrically connected to the motor 2 via wires, providing power to drive the motor 2 and ensuring the normal operation of the bladeless fan. A rotating structure may also be provided between the third component 1C and the base 4, allowing the third component 1C to rotate horizontally relative to the base 4. This means the air outlet of the bladeless fan can oscillate horizontally relative to the base 4, preventing the air outlet from blowing directly on the user for extended periods.

[0077] In one embodiment, the display component 6 is housed within the base 4 of this application, thereby displaying the operating parameters of the bladeless fan outwards on a portion of the base 4. These operating parameters include, but are not limited to, operating mode, current wind speed, and current battery level. It should be understood that the display component 6 may include touchscreen functionality, allowing users to adjust the bladeless fan via touch sensing.

[0078] In one embodiment, the motor 2 described in this application is a three-phase high-speed motor 2, which can stably and continuously provide a high speed of 12000 R / min or higher. In actual use, the user places the bladeless fan in a suitable location, and after connecting the power supply, the three-phase high-speed motor 2 drives the impeller 3 to rotate. Air flows according to the designed airflow channel, blowing a strong, uniform, and comfortable breeze from the air outlet 13. Through the optimized design of the structure of each component and the airflow channel of the bladeless fan, the performance and usage effect of the product are effectively improved.

[0079] In one embodiment, such as Figure 12 As shown, the housing 1 further includes a third component 1C, which is located radially outside the first component 1A and the second component 1B. In this embodiment, the outer wall portion of the housing 1 forming the air outlet 13 is a portion of the first component 1A, and the outer wall portion of the housing 1 forming the air outlet 13 increases radially from back to front. An air inlet 14 is formed between the first component 1A and the third component 1C, and the air inlet 14 draws airflow through quickly, thereby increasing the air volume. In other embodiments, the outer wall portion of the housing 1 forming the air outlet 13 may also be a portion of the second component 1B. Furthermore, in other embodiments, the outer wall portion of the housing 1 forming the air outlet 13 may also decrease radially from back to front.

[0080] By incorporating the third component 1C, external airflow is drawn into the radially inner side of the third component 1C, thereby increasing airflow and blowing range, and enhancing the user experience. According to the Venturi effect, low pressure is generated near a high-speed flowing fluid, resulting in adsorption. In this embodiment, the third component 1C is arranged radially outside the first component 1A and the second component 1B, thus forming an air-enhancing ring using the Venturi effect, significantly increasing the airflow. Of course, in other embodiments, the third component 1C may also be arranged circumferentially along the first component 1A and the second component 1B, or only partially.

[0081] Axially, the rear end of the third component 1C is located behind the air outlet 13, and the front end of the third component 1C is located in front of the air outlet 13. The third component 1C is an annular structure, fitted radially outside the first component 1A and the second component 1B. An air intake channel 1b is formed between the third component 1C and the first component 1A, and the air intake channel 1b connects to the air outlet 14. An air gathering channel 1c is formed between the second component 1B and the third component 1C. The rear end of the third component 1C covers the rear side of the air outlet 13, forcing the airflow to adhere to its surface and extending the Coanda effect distance. From back to front, the cross-sectional area of ​​the air intake channel 1b gradually decreases, while the cross-sectional area of ​​the air gathering channel 1c gradually increases. The decreasing cross-sectional area of ​​the air intake channel 1b forms a converging flow channel, increasing airflow velocity and reducing static pressure, significantly enhancing low-pressure adsorption and improving external air entrainment. Furthermore, the converging structure constrains airflow diffusion and reduces turbulence. The increased cross-sectional area of ​​the air-gathering channel 1c forms an expanding flow channel, converting high-speed air kinetic energy into static pressure energy, thereby increasing wind pressure and extending the air delivery distance. The air-gathering channel 1c connects the air outlet channel 1a and the air intake channel 1b, forming an integrated path of "acceleration-stabilization-pressurization".

[0082] The above detailed description is only an illustration of the preferred embodiment of this application and is not intended to limit the patent scope of this application. Therefore, all equivalent technical changes made using the content of this invention's specification and illustrations are included within the patent scope of this invention.

Claims

1. A bladeless fan, characterized in that, include: The housing has a cavity, and an air inlet and an air outlet communicating with the cavity; A fan assembly, disposed in the cavity, is used to draw air into the cavity from the air inlet and blow it out from the air outlet; The housing includes a first component and a second component, the first component and the second component forming the cavity and the air outlet; The second component includes a base and a first drain portion. The fan assembly is mounted on the base. The first drain portion extends from the base and is located on the radially outer side of the fan assembly. The angle between the axial direction and the horizontal direction of the fan assembly is less than 60 degrees.

2. The bladeless fan as described in claim 1, characterized in that: In the axial direction, the base is located on the front side of the fan assembly, the first drain portion is connected to the base, and the first drain portion extends radially from front to back.

3. The bladeless fan as described in claim 2, characterized in that: The fan assembly includes a motor and an impeller, the motor driving the impeller to rotate; in the axial direction, the distance from the front end to the rear end of the impeller is defined as the axial length of the impeller, the distance from the front end to the rear end of the first flow guide is defined as the axial length of the first flow guide, and the ratio of the axial length of the first flow guide to the axial length of the impeller is greater than 1 / 2.

4. The bladeless fan as described in claim 2, characterized in that: The second component further includes a second drainage portion, which is connected to the first drainage portion and extends radially from back to front, tapering outwards.

5. The bladeless fan as described in claim 4, characterized in that: On the axial section of the second component, both the first drainage portion and the second drainage portion are arranged in an arc shape, and the centroid of the arc of the first drainage portion and the second drainage portion is located on the radial inner side of the first drainage portion.

6. The bladeless fan as described in claim 4, characterized in that: On the cross-section of the second component cut axially, the tangent at the rear end of the first drainage part forms an acute angle with the tangent at the rear end of the second drainage part.

7. The bladeless fan as described in claim 4, characterized in that: The first component, together with the first and second drainage portions, forms an air outlet channel, and the first component and the second drainage portion form the air outlet, which is located at the end of the air outlet channel.

8. The bladeless fan as described in claim 4, characterized in that: The maximum distance between the first drainage section and the second drainage section is less than 25 mm.

9. The bladeless fan as described in claim 1, characterized in that: The fan assembly includes a motor and an impeller, the motor drives the impeller to rotate; the impeller includes a hub and multiple blades, the motor is located on a first side of the hub, the multiple blades are connected to a second side of the hub, and the middle part of the hub protrudes towards the second side.

10. The bladeless fan as described in claim 1, characterized in that: The air outlet is located on the radial outer side of the fan assembly, and the radial plane containing the air outlet passes through the fan assembly.

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