Portable bladeless fan

Abstract

The invention provides a portable bladeless fan which comprises a shell, an air inlet part is arranged on the rear side of the shell, an air outlet part is arranged on the front side of the shell, and the air inlet part and the air outlet part are communicated in the shell; the pressurizing piece is connected with the front side of the shell; the mixed flow fan is located in the shell and connected to the rear side of the pressurizing piece, and the mixed flow fan rotates around a rotating shaft to generate airflow; wherein a pressurization flow guide channel is formed between the mixed flow fan and the shell and between the pressurization piece and the shell, at least part of the surface of the pressurization flow guide channel is provided with a flow guide structure, and airflow flows in a manner of being tightly attached to the flow guide structure so as to reduce differential pressure resistance in the pressurization flow guide channel and enable the airflow to flow quickly; and meanwhile, the flow guide structure increases the roughness of the pressurized flow guide channel to reduce turbulent flow, so that noise is reduced.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of fans, in particular to a portable bladeless fan with large air volume and air pressure and low noise. BACKGROUND

[0002] The portable fan commonly seen in daily life needs to meet the application scenarios of user hand holding, neck hanging, desktop, storage, etc., and therefore has high requirements on the shape, size and weight of the portable fan. It is difficult to realize the structural function of large air volume, large air pressure and low noise in the portable fan which is a super small product compared with the traditional fan. It is difficult to test the air volume and air force, and it is difficult to market.

[0003] Although the Dyson company has developed a new type of fan with good safety performance and beautiful appearance, the bladeless fan of the Dyson company is a product with large volume and heavy weight. Meanwhile, due to technical prejudice, the person skilled in the art believes that a bladeless fan with excellent air outlet effect must correspondingly use a fan assembly with large volume, and the product weight is difficult to reduce. Therefore, there is no portable bladeless fan with small structure, which can meet the air volume, air force and noise in the industry.

[0004] At present, the fan assembly of the handheld bladeless fan on the market is usually arranged in the handheld part to realize "bladeless" by hiding the fan assembly in the handheld part. However, the shape of the handheld part is small, the fan assembly is arranged in the handheld part, the fan rotating noise is large, and the air generated from the handheld part is transmitted to the air outlet part above, the flow path is too long, the air volume is seriously lost, and therefore the air outlet effect is not satisfactory, the market acceptance is low, and the handheld fan has no competitiveness compared with the ordinary axial flow type handheld fan.

[0005] Due to the existence of the above technical problems and technical prejudice, the existing portable fan cannot completely meet the user's use demand. With the improvement of living standards and the richness of fan application scenarios, people's requirements for portable fans are also getting higher and higher. After in-depth research on the above technical problems, technical prejudice, user demand, use safety problem and market product, the present application inventors propose a portable bladeless fan after years of research and experiment, which designs a structure with large air volume, large air pressure and low noise in a small portable fan to solve the above problems in the technical field. SUMMARY

[0006] In view of this, the present application provides a portable bladeless fan with a guide structure arranged on the surface of a pressurized flow channel, and air flow flows close to the guide structure to reduce the pressure difference resistance in the pressurized flow channel. Meanwhile, the guide structure increases the roughness of the pressurized flow channel and reduces turbulence, so as to realize the structural characteristics of small size, easy to carry, large air volume, large air pressure and low noise in the portable bladeless fan.

[0007] The application provides a portable bladeless fan, comprising: a shell, a rear side of which is provided with an air inlet part, and a front side of which is provided with an air outlet part, the air inlet part and the air outlet part being communicated in the shell; a pressurizing part connected to the front side of the shell; a mixed flow fan located in the shell and connected to the rear side of the pressurizing part, the mixed flow fan rotating around a rotation shaft to generate airflow; wherein the mixed flow fan and the pressurizing part form a pressurized airflow channel with the shell, at least part of the surface of the pressurized airflow channel is provided with a flow guide structure, and the airflow flows close to the flow guide structure to reduce the pressure difference resistance in the pressurized airflow channel and make the airflow flow fast; meanwhile, the flow guide structure increases the roughness of the pressurized airflow channel to reduce turbulence and thus reduce noise.

[0008] Further, the mixed flow fan comprises a rotating seat, the rotating seat comprises a wind guide surface which is radially increased at least partially from the air inlet end to the air outlet end, and a plurality of first blades connected to and equidistantly arranged on the wind guide surface; the pressurizing part comprises a pressurizing seat, the pressurizing seat comprises a pressurizing surface which is radially increased at least partially from the air inlet end to the air outlet end, and a plurality of second blades connected to and equidistantly arranged on the pressurizing surface, the plurality of second blades being connected to the shell; the axial length of the rotating seat at the front and rear ends is 1-1.2 times the axial length of the pressurizing seat at the front and rear ends.

[0009] Further, at least part of at least one of the pressurizing surface and the second blades is provided with the flow guide structure towards the pressurized airflow channel to form a pressurized mixed flow sound reduction for the mixed flow fan.

[0010] Further, at least part of the wind guide surface and the pressurizing surface is radially recessed to form a concave surface to absorb part of the noise of the fluid.

[0011] Further, the rotating seat and the pressurizing seat are arranged in close proximity in the axial direction, the wind guide surface and the pressurizing surface are arranged in close proximity in the axial direction, and the interval of the rotating seat and the pressurizing seat in the axial direction and the interval of the wind guide surface and the pressurizing surface in the axial direction are both 1-3 mm, so that the airflow generated by the mixed flow fan flows smoothly to the pressurizing surface and the noise generated by turbulence is reduced.

[0012] Further, the outer rotor brushless motor is further included; the mixed flow fan further includes an extension wall connected to the inner wall of the rotating seat and extending forward, the extension wall and the rotating seat jointly define a first cavity with an opening facing forward, the pressurizing seat is concave from back to front to form a second cavity with an opening facing backward, at least part of the extension wall extends into the second cavity forward, so that the first cavity and the second cavity at least partially overlap in the radial direction, and the outer rotor brushless motor is accommodated in the first cavity and the second cavity, the opening of the first cavity and the opening of the second cavity block each other to achieve noise closing processing of the outer rotor brushless motor.

[0013] Further, the line connecting the front and back ends of the air guide surface forms a first angle with the rotating shaft, and the line connecting the front and back ends of the pressurizing surface forms a second angle with the rotating shaft, and the first angle is greater than the second angle, so that the noise of the air outlet is reduced.

[0014] Further, the rear side of the shell is provided with an air inlet plate, the air inlet part is arranged on the air inlet plate, the radial cross-sectional area of the air inlet plate is greater than or equal to the maximum radial cross-sectional area of the rotating seat, and greater than or equal to the maximum radial cross-sectional area of the pressurizing seat, so that the wind at the air inlet end flows more smoothly to the air outlet end, reducing the noise of wind impact.

[0015] Further, a plurality of the flow guide structures are arranged equidistantly along the inner wall of the shell in the circumferential direction, each of the flow guide structures extends longitudinally in the axial direction, and the spacing between adjacent flow guide structures is 0.8-1.5mm, so as to disperse the pressure pulsation generated by the airflow impacting the shell and reduce the aerodynamic noise.

[0016] Further, the front end of the pressurizing part is provided with a front end surface, and the circumferential direction of the pressurizing part is provided with a pressurizing surface, and the front end surface does not protrude forward in the axial direction beyond the front end of the shell; further including a front cover arranged on the front end surface, the surface of the front cover protrudes forward to form a convex surface, and the surface of the front cover is connected to the pressurizing surface, so that the air smoothly transitions from the pressurizing surface to the surface of the front cover.

[0017] Further, the portable bladeless fan is a handheld bladeless fan configured with a handle, a clamping fan configured with a clamp, a versatile fan configured with a curved shaping member for winding, a desktop fan configured with a support, or a floor fan configured with a telescopic support.

[0018] Compared with existing technologies, the portable bladeless fan of the present invention has the following beneficial effects: it directs the airflow near the central shaft to a radially farther position away from the shaft, increasing the air delivery range. The air enters the mixed-flow fan axially from the inlet and then exits obliquely from the outlet, combining the advantages of the large airflow of an axial fan and the high air pressure of a centrifugal fan. Simultaneously, a pressurized flow channel is formed between the mixed-flow fan and the pressurizing component and the housing. At the inlet, the mixed-flow fan draws in air, increasing the airflow, while at the outlet, the pressurizing component compresses the air, increasing the air pressure. Furthermore, the pressurized flow channel is equipped with a guide structure, allowing the airflow to flow closely along the guide structure, reducing pressure resistance within the channel and enabling faster airflow. Simultaneously, the guide structure increases the roughness of the pressurized flow channel to reduce turbulence, thereby reducing noise. The mixed-flow fan directs airflow at an angle, and the pressurizing component increases air pressure and extends the air delivery distance. At the same time, the airflow guiding structure reduces noise. Therefore, a large air volume, high air pressure, and low noise are achieved in a small portable bladeless fan, improving the user experience. Attached Figure Description

[0019] Figure 1 This is a perspective view of the portable bladeless fan of the present invention;

[0020] Figure 2 This is an exploded perspective view of the portable bladeless fan of the present invention from one angle;

[0021] Figure 3 This is an exploded perspective view of the portable bladeless fan of the present invention from another angle;

[0022] Figure 4 This is a partial cross-sectional view of the portable bladeless fan of the present invention from left to right;

[0023] Figure 5 This is a schematic diagram of the portable bladeless fan rotating base and pressurizing base of the present invention;

[0024] Figure 6 This is a left view of the portable bladeless fan of the present invention with the casing transparent and the airflow guiding structure hidden.

[0025] Figure 7 This is a front-to-back sectional view of the portable bladeless fan of the present invention;

[0026] Figure 8 This is a partial rear view of the portable bladeless fan of the present invention with a hidden cover and a transparent housing. Detailed Implementation

[0027] To facilitate a better understanding of the purpose, structure, features, and effects of this invention, the invention will now be further described in conjunction with the accompanying drawings and specific embodiments.

[0028] To facilitate understanding of the technical solution of this invention, the X-axis in the three-dimensional coordinate system of the accompanying drawings is defined as the left-right direction, the Y-axis as the front-back direction, and the Z-axis as the up-down direction. In this application, air, wind, airflow, and fluid all refer to gases.

[0029] refer to Figures 1 to 3 , Figure 1 This is a perspective view of the portable bladeless fan 100 of the present invention. Figure 2 and Figure 3 These are two exploded views of the portable bladeless fan 100 of the present invention from two different angles. In this embodiment, the portable bladeless fan 100 is a handheld bladeless fan equipped with a handle (not shown, the same below), allowing the user to carry the portable bladeless fan 100 with them. Of course, the portable bladeless fan 100 can also be a clamping fan equipped with a clip, a versatile fan equipped with a bending shaping component for winding, a desktop fan equipped with a stand, or a floor fan equipped with a telescopic stand, and is not limited thereto. A semiconductor cooling element (not shown, the same below) can be provided on the handle, allowing the user to carry the portable bladeless fan 100 with them. At the same time, the semiconductor cooling element can automatically adjust the cooling temperature according to the temperature of the part in contact with the user, improving the user's carrying comfort. It should be understood that the portable bladeless fan 100 is used for heat dissipation and cooling, and a semiconductor cooling component is provided on it to improve the user's carrying comfort; of course, if a heating element (not shown) is added to the portable bladeless fan 100, it can also be used for heat preservation and warmth, and a warming component (not shown) can be provided on it to automatically adjust the temperature of the part in contact with the human body to warm the part in contact with the human body and improve the user's carrying comfort.

[0030] Combination Figure 2 and Figure 3 In this embodiment, the handle can accommodate a battery (not labeled, the same below), and a switch button (not labeled, the same below) and a charging port (not shown, the same below) can be exposed on the handle. The battery powers the portable bladeless fan 100, the switch button is used to adjust the wind speed and turn the fan on and off, and the charging port is used to charge the battery by connecting to an external power source. When the portable bladeless fan 100 is a different type of fan (such as the aforementioned clamp fan, multi-functional fan, desktop fan, etc.), the positions of the battery, switch button, and charging port can be adjusted accordingly. Of course, to achieve a smaller size, the portable bladeless fan 100 may not have a battery inside, and can still be portable by connecting to an external power source through an interface (not shown).

[0031] refer to Figures 1 to 4The portable bladeless fan 100 includes a housing 1, a pressurizing component 3, and a mixed-flow fan 2. The radial cross-sectional outlines of the housing 1, the pressurizing component 3, and the mixed-flow fan 2 are generally circular. However, the housing 1, the pressurizing component 3, and the mixed-flow fan 2 can also have other shapes, and are not limited thereto. The pressurizing component 3 is connected to the front side of the housing 1, and the pressurizing component 3 and the housing 1 are integrally formed. Alternatively, the pressurizing component 3 and the housing 1 can be separately formed, with the pressurizing component 3 mounted on the housing 1, and are not limited thereto. The mixed-flow fan 2 is connected to the rear side of the pressurizing component 3 and is located inside the housing 1. The mixed-flow fan 2 rotates around a rotating shaft 24 to generate airflow. The air inlet R of the portable bladeless fan 100 is located at the rear end, and the air outlet F is located at the front end. The direction of extension perpendicular to and passing through the rotating shaft 24 is radial, and the direction parallel to the rotating shaft 24 is axial.

[0032] refer to Figure 2 , Figure 3 , Figure 4 and Figure 6 An air inlet plate 13 is provided on the rear side of the housing 1, and an air inlet portion 14 is provided on the air inlet plate 13. The pressurizing member 3 is connected to the front side of the housing 1. An air outlet portion 15 is formed between the pressurizing member 3 and the housing 1 in the radial direction near the air outlet end F. The air inlet portion 14 and the air outlet portion 15 are connected within the housing 1. A cover plate 16 is fixed on the rear side of the air inlet plate 13. The cover plate 16 is provided with an air hole 161. The size of the air hole 161 is smaller than the size of the air inlet portion 14 to prevent fingers or other foreign objects from entering the housing 1 through the air inlet portion 14, thereby improving the safety of use. There is a distance between the surface of the cover plate 16 and the surface of the air intake plate 13. This increases the radial air intake path between the air intake plate 13 and the cover plate 16, even when the size of the air holes 161 on the cover plate 16 is small. Meanwhile, the air intake part 14 is relatively large, so the airflow is not affected by the cover plate 16 with its smaller air holes 161. The housing 1 is further divided into a first housing 11 and a second housing 12 that fit together front and rear. The first housing 11 and the second housing 12 are fixed to each other by a fixing structure. Most of the mixed-flow fan 2 is radially disposed within the first housing 11, and the pressure member 3 is radially disposed within the second housing 12. The ratio of the lengths of the front and rear ends of the first housing 11 to the lengths of the front and rear ends of the second housing 12 is 1-1.2, which achieves a reasonable balance between airflow and air pressure while realizing miniaturization, and the ratio is close to 1:1, making the first housing 11 and the second housing 12 more aesthetically pleasing.

[0033] refer to Figure 2 , Figure 4 ,Figure 7 and Figure 8 The mixed-flow fan 2 includes a rotating base 21 and a plurality of first blades 22. The rotating base 21 includes a guide surface 211 that increases radially from the air inlet end R to the air outlet end F. The plurality of first blades 22 are connected and equidistantly arranged on the guide surface 211. Each blade includes a first blade root 221 connected to the guide surface 211 and a first blade tip 222 away from the guide surface 211. The first blades 22 extend spirally from the air inlet end R to the air outlet end F and along the circumference of the guide surface 211 at a predetermined angle. Viewed from the air inlet end R to the air outlet end F, any two adjacent first blades 22 have a first interval J1 at the air inlet end R and a second interval J2 at the air outlet end F. The ratio of the first interval J1 to the second interval J2 is in the range of 0.4-0.8, which is beneficial for increasing the air intake volume. (Refer to reference) Figure 3 The rotating seat 21 is generally truncated cone-shaped. The radial cross-sectional area of ​​the rotating seat 21 at the air inlet R is smaller than the radial cross-sectional area of ​​the rotating seat 21 at the air outlet F. The rotating seat 21 has a relatively large radial cross-section at the air outlet F. The mixed-flow fan 2 also includes an extension wall 26 that connects to the inner wall of the rotating seat 21 and extends forward. The extension wall 26 and the rotating seat 21 together form a first cavity 23 with a forward opening at the air outlet F.

[0034] refer to Figure 2 , Figure 4 and Figure 6 The air intake plate 13 and the rear end of the rotating base 21 have a safe pressure distance D1 to allow the air intake plate 13 to undergo maximum compressive deformation within the pressure range permitted by the material properties. The distance between the air intake plate 13 and the rear end of the rotating base 21 is 12.4-12.9 mm (millimeters, the same below) to provide space at the air intake end R for a large air volume to enter, and also to allow the air intake plate 13 to undergo maximum compressive deformation when subjected to a large air volume. (Refer to reference...) Figure 8 The radial cross-sectional area of ​​the air intake plate 13 is greater than or equal to the maximum radial cross-sectional area of ​​the rotating seat 21 to ensure sufficient air intake and achieve noise reduction, converting sharp noise into a low-pitched sound. In this embodiment, the radial cross-sectional radius of the air intake plate 13 is 25.9 mm, and the radial cross-sectional radius of the rear end of the rotating seat 21 is 8.0 mm, but this is not a limitation. Furthermore, the radial cross-sectional area of ​​the air intake plate 13 is greater than or equal to the radial cross-sectional area of ​​the pressurizing seat 31 at the air outlet F, so that the air from the air intake end R flows more smoothly to the air outlet F, reducing the noise from wind impact. At the air intake end R, the tip 222 of the first blade is closer to the air intake plate 13 than the root 221 of the first blade to enhance the suction capacity of the mixing fan 2.

[0035] refer to Figure 4 and Figure 5 At least a portion of the air guide surface 211 is recessed toward the rotating shaft 24. It should be understood that at least a portion of the air guide surface 211 may be recessed toward the rotating shaft 24 to allow the mixing fan 2 to concentrate and expand the airflow and create high air pressure. Of course, the air guide surface 211 may also be an inclined plane, or it may at least partially bulge away from the rotating shaft 24, and this is not a limitation.

[0036] refer to Figure 2 , Figure 4 , Figure 5 and Figure 6 The pressurizing component 3 includes a pressurizing base 31 and a plurality of second blades 32. The pressurizing base 31 includes a pressurizing surface 311 that increases radially from the air inlet R to the air outlet F. The plurality of second blades 32 are connected and equidistantly arranged on the pressurizing surface 311. Each second blade 32 includes a second blade root 321 connected to the pressurizing surface 311 and a second blade tip 322 away from the pressurizing surface 311. The second blades 32 extend forward in a substantially axial direction. The oblique flow air generated by the mixed-flow fan 2 is combed and transformed by the second blades 32 to form a direct flow airflow parallel to the rotating shaft 24, thereby increasing the blowing distance and reducing turbulence, noise, and vibration. This reduces the noise generated by turbulent crosstalk, achieving noise reduction and converting sharp noise into low-pitched sound, thus reducing the noise of the mixed-flow air generated by the mixed-flow fan 2. It also greatly improves the static pressure, reduces energy consumption, and strengthens the concentration of the airflow from the mixed-flow fan 2. The second blades 32 even out the airflow generated by the mixed-flow fan 2 and increase the air pressure. The second blade tip 322 is connected to the housing 1, the rotating base 21 is connected to the pressurizing base 31 through a fixed fitting structure, and the mixed-flow fan 2 is relatively fixed inside the housing 1 by the pressurizing component 3. The pressurizing component 3 has a radius of 25.3-25.7 mm at its maximum diameter at the air outlet F, ensuring sufficient airflow and pressure while facilitating portability.

[0037] refer to Figures 2 to 6The pressure seat 31 is recessed from back to front to form a second cavity 34 with a rearward opening. At least a portion of the extension wall 26 extends forward into the second cavity 34, so that the first cavity 23 and the second cavity 34 at least partially overlap radially, reducing the space occupied. The mixed-flow fan 2 uses an external rotor brushless motor 25 housed within the first cavity 23 and the second cavity 34. The openings of the first cavity 23 and the second cavity 34 mutually block each other to reduce the noise of the external rotor brushless motor 25, converting sharp noise into a low-pitched sound. This also achieves independent isolation between the rotating seat 21 and the pressure member 3. Simultaneously, the connection structure between the mixed-flow fan 2 and the pressure member 3 is also accommodated in the first cavity 23, making excellent use of space. The rotating shaft 24 protrudes forward from the rear wall of the first cavity 23, and the rear side of the pressure member 3 protrudes rearward to form a protruding post 33. The rotating shaft 24 is fixed to the protruding post 33. The external rotor brushless motor 25 has a service life of up to 15,000 hours and eliminates the electrical sparks generated during the operation of brushed motors, greatly reducing interference from electrical sparks to remote control wireless equipment. The brushless operation significantly reduces friction, resulting in smoother operation and better noise reduction. Noise and wind noise from the external rotor brushless motor 25 are effectively eliminated.

[0038] refer to Figure 3 , Figure 4 , Figure 5 and Figure 6 The pressurizing seat 31 is also approximately truncated conical in shape. The radial cross-sectional area of ​​the pressurizing seat 31 at the air inlet R is smaller than that at the air outlet F. The pressurizing seat 31 has a relatively large radial cross-section at the air outlet F. Simultaneously, the pressurizing seat 31 and the housing 1 form the air outlet 15 at the air outlet F. The pressurizing seat 31 has a large radial cross-section at the air outlet F, and an acute angle is formed between the line connecting the front and rear ends of the second blade root 321 and the line connecting the front and rear ends of the second blade tip 322. This means that the housing 1 and the pressurizing surface 311 extend forward while simultaneously moving closer to each other. Air is pressurized and expelled from the gap between the pressurizing seat 31 and the housing 1 at the air outlet F, which helps to increase wind force, wind pressure, and air delivery distance.

[0039] refer to Figure 3 , Figure 4 , Figure 5 and Figure 6At least a portion of the pressurizing surface 311 increases radially from the air inlet end R to the air outlet end F. Simultaneously, at least a portion of the pressurizing surface 311 is concave towards the rotating shaft. The air guide surface 211 and the radial concavity of at least a portion of the pressurizing surface 311 form a concave surface to absorb some of the fluid noise. Specifically, the pressurizing surface 311 generally increases radially from the air inlet end R to the air outlet end F. However, in other embodiments, the pressurizing surface 311 may first extend forward parallel to the rotating shaft 24 and then increase radially, or first increase radially and then extend forward parallel to the rotating shaft 24, or the overall radial direction may remain unchanged, or at least a portion of the radial direction may decrease; this is not a limitation.

[0040] refer to Figure 2 , Figure 4 and Figure 6 The pressurizing component 3 and the mixed-flow fan 2 form a pressurized flow channel T between themselves and the housing 1. The radial cross-sectional area of ​​the pressurized flow channel T at the air inlet R is larger than that at the air outlet F. Air enters the pressurized flow channel T from the air inlet 14, forms a pressurized mixed flow in the pressurized flow channel T, and then exits from the air outlet 15. After the air enters the mixed-flow fan 2 axially from the air inlet R, it leaves obliquely from the air outlet F. The mixed-flow fan 2 combines the advantages of large air volume of an axial flow fan and high air pressure of a centrifugal fan. At the same time, the pressurized flow channel T formed between the mixed-flow fan 2 and the pressurizing component 3 and the housing 1 has a large radial cross-sectional area at the air inlet R, which is conducive to absorbing air and increasing air volume; and a small radial cross-sectional area at the air outlet F, which is conducive to compressing air and increasing air pressure. The oblique airflow characteristic of the mixed-flow fan 2 further increases the air pressure and the air delivery distance, thereby achieving large air volume and high air pressure in the relatively small portable bladeless fan 100, achieving rapid cooling and improving the user experience.

[0041] refer to Figures 2 to 4Meanwhile, at least a portion of the surface of the pressurized flow channel T is provided with a flow guide structure 4, allowing the airflow to flow closely along the flow guide structure 4 to reduce the pressure difference resistance within the pressurized flow channel T and increase airflow speed. Simultaneously, the flow guide structure 4 increases the roughness of the pressurized flow channel T to reduce turbulence and thus lower noise. Specifically, in this embodiment, multiple flow guide structures 4 are arranged equidistantly along the circumferential direction of the inner wall of the housing 1, with each flow guide structure 4 extending longitudinally in the axial direction. The interval between adjacent flow guide structures 4 is 0.8-1.5 mm to disperse the pressure pulsations generated by the airflow impacting the housing 1 and reduce aerodynamic noise. Of course, the number of flow guide structures 4, the extension direction of the flow guide structures 4, and the interval between adjacent flow guide structures 4 are not limited by these. Furthermore, at least a portion of at least one of the pressurized surface 311 and the second blade 32 faces the pressurized flow channel T and is provided with the flow guide structure 4 to reduce noise from the pressurized mixed flow generated by the mixed-flow fan 2. It should be understood that the airflow guiding structure 4 can be provided on various structural surfaces within the pressurized airflow guiding channel T, such as the airflow guiding surface 211, the first blade 22, etc., as long as the noise of the portable bladeless fan 100 can be reduced to an acceptable level for the user. Specifically, the airflow guiding structure 4 is a recessed structure. The recessed structure can reduce wind resistance and turbulence, thereby increasing wind speed and reducing airflow loss. Of course, the shape of the airflow guiding structure 4 is not limited to this.

[0042] refer to Figure 4 , Figure 5 and Figure 6The mixing fan 2 and the pressurizing component 3 are arranged close to each other in the axial direction, that is, the rotating seat 21 and the pressurizing seat 31 are arranged close to each other in the axial direction. At the same time, the radial cross-section of the rotating seat 21 at the air outlet F and the radial cross-section of the pressurizing seat 31 at the air inlet R are both circular, and the difference between their radii is very small. In this embodiment, the difference between their radii is less than 1 mm. Of course, this is not a limitation, as long as the pressurizing surface 311 and the air guiding surface 211 are also arranged close to each other in the axial direction to block the wind from entering. The equivalent seamless connection interval D2 between the rotating seat 21 and the pressurizing seat 31 prevents airflow that would otherwise be blocked from entering the equivalent seamless connection interval D2. Instead, the airflow from the mixing fan 2 at the rear is blown directly forward, allowing the air to flow more smoothly from the portion of the pressurizing guide channel T between the air guide surface 211 and the housing 1 into the portion of the pressurizing guide channel T between the pressurizing surface 311 and the housing 1. This reduces eddy current losses and minimizes turbulent crosstalk noise. Specifically, the equivalent seamless connection interval D2 between the rotating seat 21 and the pressurizing seat 31 in the axial direction is 1-3 mm to ensure smooth airflow from the mixing fan 2 to the pressurizing component 3, reducing noise generated by turbulence. However, this is not a limitation; any measure that minimizes airflow entering the equivalent seamless connection interval D2 between the rotating seat 21 and the pressurizing seat 31 is acceptable.

[0043] refer to Figure 5 The air guide surface 211 includes a first extension 2111 adjacent to one end of the pressurizing surface 311, and the pressurizing surface 311 includes a second extension 312 adjacent to one end of the air guide surface 211. The first extension 2111 and the second extension 312 extend in the same direction, so as to make the connection between the air guide surface 211 and the pressurizing surface 311 smoother.

[0044] refer to Figure 6 The first blade 22 and the second blade 32 are axially adjacent and spaced apart to form an equivalent partition gap D3. The minimum equivalent partition gap D3 between the first blade 22 and the second blade 32 is 1-3 mm. This is to prevent the airflow generated by the mixed-flow fan 2 at the air outlet F from flowing back to the air inlet R along the gap between the first blade 22 and the second blade 32, and to prevent crossflow between two adjacent second blades 32, thereby streamlining the airflow and increasing air pressure, achieving the effects of air guidance and noise reduction. Of course, the minimum equivalent partition gap D3 between the first blade 22 and the second blade 32 is not limited to this, as long as the airflow between the first blades 22 can flow smoothly to the space between the second blades 32, reducing backflow loss.

[0045] refer to Figure 2 and Figure 8In this embodiment, the number of the first blades 22 is 6 and the number of the second blades 32 is 8. In other embodiments, the ratio of the number of the first blades 22 to the number of the second blades 32 can be in the range of 1 / 2-1. Of course, this is not a limitation, as long as the portable bladeless fan 100 can have a good suction capacity and a good pressurization capacity.

[0046] refer to Figures 4 to 6 From the air inlet R to the air outlet F, the mixing fan 2 and the pressurizing base 31 are radially enlarged to form a trumpet shape, creating an outwardly expanding pressurizing slope M. Specifically, the rotating base 21 and the pressurizing base 31 are radially enlarged to form a trumpet shape, creating an outwardly expanding pressurizing slope M. The pressurizing slope M increases the pressurization stroke of the airflow. The pressurizing slope M includes the air guide surface 211 and the pressurizing surface 311, providing two-stage pressurization with increased pressurization strokes in both stages, resulting in a better pressurization effect.

[0047] refer to Figure 3 , Figure 4 , Figure 5 and Figure 6 The axial lengths of the front and rear ends of the rotating base 21 are 1-1.2 times the axial lengths of the front and rear ends of the pressurizing base 31. This ensures that after the airflow is concentrated under high pressure by the first blade 22, it is effectively combed through the second blade 32, ensuring the maximum usable airflow constructed by the high-pressure airflow generated by the pressurizing component 3 and the external negative pressure airflow, as well as the aggregated airflow distance of the maximum usable airflow. It should be understood that the high air pressure of the final airflow generated by the pressurizing component 3 can drive the negative pressure air near the outside of the housing 1, thereby further increasing the airflow. Preferably, the axial lengths of the front and rear ends of the mixed-flow fan 2 and the pressurizing component 3 are in a 1:1 ratio, which can meet the high airflow requirements of the portable bladeless fan 100 in various usage scenarios and also allows for product miniaturization.

[0048] refer to Figure 4 , Figure 5 and Figure 6 The pressurizing inclined surface M and the housing 1 form the pressurizing guide channel T. The pressurizing inclined surface M includes the air guide surface 211 and the pressurizing surface 311. The cooperation between the pressurizing inclined surface M and the housing 1 achieves noise reduction, converting sharp noise into low-pitched sound. The pressurizing guide channel T includes a first channel T1 and a second channel T2 connected to each other. The first channel T1 is formed radially between the air guide surface 211 of the mixed-flow fan 2 and the first housing 11, and the second channel T2 is formed radially between the pressurizing surface 311 of the pressurizing seat 31 and the second housing 12. The minimum radial cross-sectional area of ​​the first channel T1 is greater than or equal to the maximum cross-sectional area of ​​the second channel T2.

[0049] refer to Figure 4 , Figure 5 and Figure 6 In the radial direction, the first housing 11 includes a first drainage surface 111 facing the air guide surface 211. Both the air guide surface 211 and the first drainage surface 111 are annular. At least a portion of the air guide surface 211 is radially concave to form a concave surface. The first drainage surface 111 increases radially from the air inlet end R to the air outlet end F, and at least a portion of the first drainage surface 111 is radially convex to form a convex surface, so that the structure of the first channel T1 can concentrate and form a large air volume while being pressurized. Of course, this is only one form of the air guide surface 211 and the first drainage surface 111, and is not a limitation thereof.

[0050] refer to Figure 4 , Figure 5 and Figure 6 In the radial direction, the second housing 12 includes a second airflow guiding surface 121 facing the pressurizing surface 311. Both the pressurizing surface 311 and the second airflow guiding surface 121 are annular. At least a portion of the pressurizing surface 311 is radially enlarged and radially concave to form a concave surface. The second airflow guiding surface 121 is radially reduced from the air inlet end R to the air outlet end F, and at least a portion of the second airflow guiding surface 121 is radially convex to form a convex surface. This allows the structure of the second channel T2 to further and rapidly pressurize the large volume and high pressure airflow generated behind it to form high pressure airflow. Of course, this is only one form of the pressurizing surface 311 and the second airflow guiding surface 121, and is not a limitation thereof.

[0051] Both the first air-guiding surface 111 and the second air-guiding surface 121 are radially protruding convex surfaces. Furthermore, the first air-guiding surface 111 and the second air-guiding surface 121 form a smooth and complete arc surface by first increasing radially and then decreasing radially from the air inlet end R to the air outlet end F. The first air-guiding surface 111 and the second air-guiding surface 121 not only increase air volume and air pressure but also improve the aesthetics of the housing 1. The radial distance between the second air-guiding surface 121 at the air outlet end F and the rotating shaft 24 is greater than the radial distance between the first air-guiding surface 111 at the air inlet end R and the rotating shaft 24. This facilitates blowing the airflow from the rotating shaft 24, which is closer to the center, towards a position radially away from the rotating shaft 24, thereby increasing the air delivery distance.

[0052] refer to Figures 4 to 5The axial airflow at the air inlet R is redirected to flow obliquely forward along the air guide surface 211, allowing airflow closer to the axial direction to flow outward at an oblique angle. The oblique airflow at the air outlet F of the mixed-flow fan 2 is redirected to flow obliquely forward along the pressure surface 311, and further obliquely outward, providing sufficient space near the axis of the pressure component 3 for housing the external rotor brushless motor 25. The line connecting the front and rear ends of the air guide surface 211 forms a first angle α with the rotating shaft 24, and the line connecting the front and rear ends of the pressure surface 311 forms a second angle b with the rotating shaft 24. The first angle α is greater than the second angle b, increasing air pressure while reducing airflow loss and lowering exhaust noise. The first angle α ranges from 30 to 45 degrees, and the second angle b ranges from 0.5 to 5 degrees. The air guide surface 211 is at least partially concave towards the rotating shaft 24, allowing the axial airflow at the air inlet R to flow along the air guide surface 211 with its rapidly increasing slope for rapid pressurization. The pressurizing surface 311 increases radially from the air inlet R to the air outlet F. The airflow generated by the mixed-flow fan 2 is further pressurized along the pressurizing surface 311, which has a smaller slope. The airflow is rapidly pressurized by the air guide surface 211 and then by the secondary pressurization of the pressurizing surface 311, forming high-pressure airflow, resulting in good blowing effect and long air delivery distance. At the same time, the two inclined structures also have the effects of air guiding and noise reduction.

[0053] refer to Figure 4 , Figure 6 and Figure 7 From the air inlet R to the air outlet F, at least a portion of the air guide surface 211 is recessed toward the rotating shaft 24, so that the mixing fan 2 concentrates airflow and forms a first high air pressure; as Figure 4 Viewed from left to right, the distance between the top of the first blade 222 and the radial gap of the housing 1 decreases from the air inlet R to the air outlet F, but combined with Figure 7 The distance between the tip 222 of the first blade and the housing 1 is maintained within the error range of the equivalent isolation distance D4, so as to block the airflow generated by the mixed flow fan 2 at the air outlet F from flowing back to the mixed flow fan 2 at the air inlet R around the minimum radial gap, thereby increasing the second high wind pressure and reducing the noise of turbulent crosstalk; the distance between any two adjacent first blades 22 gradually increases from the air inlet R to the air outlet F, so as to increase the third high wind pressure; the second blade 32 equalizes the airflow formed by the mixed flow fan 2 and increases the fourth high wind pressure.

[0054] The first high air pressure is formed on the basis of the large air volume gathered at the air inlet R, and the second, third and fourth high air pressures are increased at the same time. The mixed flow fan 2 has the ability to form a large air volume and high air pressure, so as to generate a large air volume and high air pressure in the small portable bladeless fan 100, and increase the air delivery distance, which perfectly meets the needs of users.

[0055] refer to Figure 3 , Figure 4 and Figure 6 The pressurizing component 3 has a front end face 313 and a circumferential pressurizing surface 311. The front end face 313 does not extend forward beyond the front end of the housing 1 in the axial direction, which is beneficial for forming a negative pressure zone between the front end face 313 and the front end of the housing 1. It also includes a front cover 35 disposed on the front end face 313. The surface of the front cover 35 protrudes forward to form a convex surface, and the surface of the front cover 35 connects to the pressurizing surface 311, allowing air to smoothly transition from the pressurizing surface 311 to the surface of the front cover 35. In other embodiments, the front cover 35 can also be a replaceable IP character item. The front cover 35 can be exposed or covered by at least partially transparent material to enhance user interaction with the IP character item. By making it replaceable, different partners need to customize different molds; one mold can be used for multiple IP partners, reducing IP partner production costs by about 40%. The exposed IP character item increases user direct contact with the IP character item, changing the traditional user experience. The front cover 35 can also be used to set up an aromatherapy component, a component that combines humidification and aromatherapy, a USB cable harness, or a mirror for LED lights, etc., and is not limited thereto.

[0056] The above detailed description is only an illustration of a preferred embodiment of the present invention and is not intended to limit the patent scope of the present invention. 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 portable bladeless fan, characterized in that, include: The housing has an air inlet and an air outlet, which are connected within the housing. The pressure member is connected to the front side of the housing; A mixed-flow fan is located inside the housing and connected to the rear side of the pressurizing member. The mixed-flow fan rotates around a pivot to generate airflow. The housing includes a first airflow guiding surface and a second airflow guiding surface. The first airflow guiding surface is disposed towards the mixed-flow fan, and the second airflow guiding surface is disposed towards the pressurizing component. The radial distance between the second airflow guiding surface at the air outlet end and the rotating shaft is greater than the radial distance between the first airflow guiding surface at the air inlet end and the rotating shaft.

2. The portable bladeless fan according to claim 1, characterized in that: At least a portion of the first air-draining surface increases radially from the air inlet end to the air outlet end.

3. The portable bladeless fan according to claim 1, characterized in that: At least a portion of the second airflow surface decreases radially from the air inlet end to the air outlet end.

4. The portable bladeless fan according to claim 1, characterized in that: Both the first drainage surface and the second drainage surface are annular.

5. The portable bladeless fan according to claim 1, characterized in that: At least a portion of the first drainage surface protrudes radially, and / or at least a portion of the second drainage surface protrudes radially.

6. The portable bladeless fan according to claim 1, characterized in that: The mixed-flow fan and the pressurizing component together form a pressurized flow channel with the housing. The mixed-flow fan includes a rotating base and a plurality of first blades. The rotating base includes a guide surface. The pressurizing component includes a pressurizing base and a plurality of second blades. The pressurizing base includes a pressurizing surface. A first channel is formed between the guide surface and the housing, and a second channel is formed between the pressurizing surface and the housing.

7. The portable bladeless fan according to claim 6, characterized in that: At least a portion of the air guiding surface increases radially from the air inlet end to the air outlet end, and at least a portion of the pressurizing surface increases radially from the air inlet end to the air outlet end.

8. The portable bladeless fan according to claim 6, characterized in that: The minimum radial cross-sectional area of ​​the first channel is greater than or equal to the maximum cross-sectional area of ​​the second channel.

9. The portable bladeless fan according to claim 6, characterized in that: The pressurizing seat has a front cover fixed on the air outlet side.

10. The portable bladeless fan according to claim 9, characterized in that: The surface of the front cover protrudes in the direction of air outlet to form a convex surface, and the end of the convex surface on the air outlet side does not extend beyond the end of the second air outlet surface.

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