An air outlet structure and an air outlet bracket having the same.

Abstract

This invention discloses an air outlet structure and an air outlet bracket having the same, including a hub and blades evenly distributed around the hub. Each blade is formed by an inlet edge, an outlet edge, a blade tip, and a blade root. Both the inlet and outlet edges are S-shaped. The height of the inlet and outlet edges near the blade tip is greater than that of the blade root. The height difference between the top boundary point of the outlet edge and the bottom boundary point of the blade root is 12a to 14a mm, where a is a coefficient and satisfies a > 0. Each blade has at least a first air-cutting section located inside the blade root and a second air-cutting section located outside the blade root. The first and second air-cutting sections arch near the blade tip. The second air-cutting section at least partially extends outside the hub. The air-cutting angle of the blade root curve is greater than that of the blade tip curve and transitions towards the blade tip, improving the air outlet effect.

Description

Technical Field

[0001] This invention relates to the field of fan blade technology, and more specifically to an air outlet structure. Background Technology

[0002] Currently, with the continuous innovation of home appliances and the increasing demand for high-performance products, fan blades, as the core component of fan products, are also facing higher requirements as the overall performance of fans improves. Nowadays, the appearance of household fan blades has remained largely unchanged for decades, typically employing a 3-7 blade structure. The blade surface design is simple, resulting in low airflow efficiency and low fan volume during rotation.

[0003] To address the airflow issue, current technologies still rely on increasing fan speed to achieve a significant increase in airflow. However, high-speed fan rotation inevitably leads to increased noise and power consumption. Therefore, fan blades and components that simultaneously achieve high airflow, low noise, and low power consumption have become a pressing design challenge for household fans.

[0004] In existing technologies, fan noise mainly consists of aerodynamic noise, mechanical noise, and electromagnetic noise. Under normal conditions, mechanical noise and electromagnetic noise are negligible in intensity compared to aerodynamic noise. Aerodynamic noise mainly consists of rotational noise and eddy current noise. Rotational noise is the noise generated by the periodic shearing of the fan blades causing gas pressure pulsations, and its intensity is mainly affected by the rotational speed. Eddy current noise is mainly manifested as broadband noise formed by eddies separating from the fan blade surface, and its intensity is mainly affected by the scale and intensity of the separation between the eddies and the surface during gas flow.

[0005] In current fan designs, increasing airflow and air pressure is mainly achieved by increasing the blade load and blade speed. However, the adverse pressure gradient within the fan blade flow channel makes it easy for low-energy fluids to separate. Further increasing the blade load will exacerbate this phenomenon and may even cause the fan to stall, leading to increased aerodynamic losses, decreased aerodynamic efficiency, increased power consumption, and increased noise.

[0006] As shown in the figure, the design of traditional fan blades is as follows: existing household fans have a small number of blades, and the surface design of the blades is relatively simple. The leading edge curve, trailing edge curve, blade root curve, and blade tip curve are basically single-curve curves. The blade thickness is uniform, which results in a large difference in wind speed between the inner and outer sides of the fan blade when it rotates. The inner side has less air intake and low wind cutting efficiency. This type of fan blade has a high rotation speed during operation, but the output wind speed is low, the wind noise is large, and it also increases energy consumption. In addition, this type of fan blade has low strength and a large amount of deformation under the action of airflow, which further aggravates the noise and the diffusion of airflow.

[0007] In addition, the existing fan blades do not have an air duct to constrain the airflow on the outer side, resulting in the air being diffused after exiting the fan, with a short air delivery distance and low air circulation efficiency. Summary of the Invention

[0008] In view of the shortcomings of the existing technology, the purpose of this invention is to provide an air outlet structure and an air outlet bracket having the same.

[0009] The above-mentioned technical objective of the present invention is achieved through the following technical solution: an air outlet structure, including a hub and blades evenly distributed around the periphery of the hub;

[0010] The blade is formed by an inlet edge, an outlet edge, a blade tip, and a blade root. Both the inlet edge and the outlet edge are S-shaped. The height of the inlet edge and the outlet edge near the blade tip is greater than that of the blade root. The difference in plane height between the top boundary point of the outlet edge and the bottom boundary point of the blade root is 12a~14amm, where a is a coefficient and satisfies a>0.

[0011] The blade has at least a first wind-cutting portion located inside the blade root and a second wind-cutting portion located outside the blade root. The first and second wind-cutting portions are arched near the blade tip. The second wind-cutting portion extends at least partially outside the hub. The wind-cutting angle of the blade root curve is greater than the wind-cutting angle of the blade tip curve and transitions towards the blade tip.

[0012] Preferably, the number of fan blades is 11.

[0013] Furthermore, the thickness of the leaf root is greater than that of the leaf tip, and the thickness difference is greater than 2:1. The thickness of the air inlet edge and the air outlet edge is less than that of the middle of the blade, and they transition towards the middle of the blade.

[0014] Furthermore, the blade has a root curve, a tip curve, a leading edge curve, and a trailing edge curve;

[0015] The ratio of the curve radius of the leaf root curve to that of the leaf tip curve satisfies: 0.24 to 0.25; the ratio of their maximum arc height satisfies: 0.34 to 0.67; the ratio of their projected dimensions in the direction of the blade axis satisfies: 0.73 to 0.875; and the ratio of their projected dimensions in the plane perpendicular to the blade axis satisfies: 0.30 to 0.34.

[0016] The ratio of the lengths of the leading edge curve and the trailing edge curve satisfies 0.94 to 0.98, and the ratio of their maximum arc height dimensions projected onto the blade axis is 0.51 to 0.66.

[0017] Furthermore, the ratio of the projected distance between the root curve and tip curve of two adjacent blades in a plane perpendicular to the blade axis is 0.08 to 0.125.

[0018] The projection distance between the root curves of two adjacent blades in a plane perpendicular to the blade axis is 2a to 3a mm.

[0019] The distance between the projections of the tip curves of two adjacent blades onto a plane perpendicular to the blade axis is 24a to 25a mm.

[0020] The projection distance between the leading edge curve at a position 0.65 times the blade tip and the trailing edge curve at a position 0.7 times the blade tip in a plane perpendicular to the blade axis is 6.5a to 7.7a ​​mm. The projection distance between the leading edge curve at a position 0.3 times the blade tip and the trailing edge curve at a position 0.3 times the blade tip in a plane perpendicular to the blade axis is 17.8a to 19.2a mm.

[0021] Furthermore, the projection distance between the leading edge curve on the rear side and the trailing edge curve on the front side of two adjacent blades in a plane perpendicular to the blade axis gradually increases from the leaf root to the leaf tip.

[0022] Furthermore, the thickness of the blade at the leading edge is 1.0a to 1.2a mm, the thickness at the trailing edge is 1.1a to 1.3a mm, and the thickness of the blade in the middle region between the leading and trailing edges is 2.0a to 3.5a mm; the outer diameter of the blade is 297.5 to 300a mm, and the outer diameter of the hub is 72a to 74a mm, where a is a coefficient and a is greater than 0.

[0023] Furthermore, the height difference between the top boundary of the trailing edge curve at the blade tip and / or the top plane of the hub portion is 16a to 18a mm; the height of the hub portion is 28a to 30a mm.

[0024] Furthermore, the thickness of the blade decreases towards the leading edge curve and the trailing edge curve.

[0025] Furthermore, the wind-cutting angle of the air inlet end of the blade root curve during rotation is 39a to 41a mm, the wind-cutting angle of the air inlet end of the blade tip curve during rotation is 14a to 16a mm, and the wind-cutting angle of the air inlet end at the middle section of the blade during rotation is 18a to 20a mm.

[0026] As a preferred option, 'a' is a coefficient with a value of 0.9 to 1.

[0027] The blade root curve has a radius of 36a to 37a mm and a maximum arc height of 1.8a to 2.8a mm. The projection size of the blade curve in the direction of the blade axis is 25a to 28a mm, and the projection size of the blade curve in the plane perpendicular to the blade axis is 18.2a to 19.8a mm.

[0028] The blade tip curve has a radius of 148a to 150a mm and a maximum arc height of 4.2a to 5.2a mm. The projected size of the blade tip curve in the direction of the blade axis is 32a to 34a mm, and the projected size of the blade tip curve in a plane perpendicular to the blade axis is 57a to 59.5a mm.

[0029] The leading edge curve has a length of 119a to 121a mm, and the maximum arc height of the projection of the leading edge curve onto the blade axis is 10.5a to 12.5a mm.

[0030] The trailing edge curve has a length of 124a to 126a mm, and the maximum arc height of the trailing edge curve projected onto the blade axis is 19a to 20.5a mm.

[0031] The present invention also provides an air outlet bracket, including the above-mentioned air outlet structure, wherein the air outlet structure is arranged inside the air outlet bracket, an air duct is formed inside the air outlet bracket, and the shortest distance between the air duct and the tip of the fan blade is 1a to 8a mm.

[0032] Compared with the prior art, the present invention has the following advantages and beneficial effects: by adopting the air outlet structure of the present invention, 11 blades are evenly distributed on the hub, and the blades are curved. The first air cutting part and the second air cutting part form a blade curved surface with turns and undulations, which reduces the separation of airflow on the blades, thereby improving the air cutting volume and air outlet efficiency. In addition, the blade curved surface has multiple turns, which constrains the airflow and is conducive to air outlet convergence, thereby increasing the air volume and reducing noise under the same fan blade outer diameter.

[0033] The air inlet and outlet edges of the blades are both S-shaped, which makes the airflow velocity relatively stable after it is blown out of the blades and on the inner and outer sides of the blades, reducing the wind speed difference. At the same time, the 11-blade air outlet structure can still achieve higher wind speed under low speed conditions, and the output airflow is natural and continuous.

[0034] The wind shear angle at the blade root is greater than that at the blade tip, and the transition from the blade root to the blade tip is gradual, so that the airflow is turbulent at the blade tip when the blade rotates, which can reduce the noise of the fan blade. Attached Figure Description

[0035] Figure 1 This is a schematic diagram of a duct assembly in the prior art;

[0036] Figure 2 This is a structural diagram of the fan blade of the present invention;

[0037] Figure 3 This is a top view of the fan blade of the present invention;

[0038] Figure 4 This is a front view schematic diagram of the present invention;

[0039] Figure 5 for Figure 4 Enlarged view of point A in the middle;

[0040] Figure 6 This is a curved grille diagram of the fan blade of the present invention;

[0041] Figure 7 This is a schematic diagram of the fan blades and a portion of the hub of the present invention;

[0042] Figure 8 for Figure 7 Cross-sectional view at point AA;

[0043] Figure 9 for Figure 7 Cross-sectional view at point BB;

[0044] Figure 10 for Figure 7 Cross-sectional view at point C;

[0045] Figure 11 for Figure 7 Cross-sectional view at point DD;

[0046] Figure 12 This is a cross-sectional schematic diagram of the air outlet bracket and air outlet structure of the present invention;

[0047] Figure 13 for Figure 12 Enlarged view of point B in the middle;

[0048] Figure 14 This is a schematic diagram of the structure of the middle frame of the present invention;

[0049] Figure 15 This is an exploded view of the present invention;

[0050] Figure 16 This is a cross-sectional schematic diagram of the air guide channel of the present invention;

[0051] In the diagram: 1. Hub; 2. Blades; 2.1. First air-cutting section; 2.2. Second air-cutting section;

[0052] 3. Inlet edge; 4. Outlet edge; 5. Blade tip; 6. Blade root; 7. Leading edge curve; 8. Trailing edge curve;

[0053] 9. Air outlet bracket;

[0054] 9.1 Front frame; 9.2 Middle frame; 9.3 Rear frame; 9.4 Air inlet; 9.5 Air outlet;

[0055] 10. Air guiding section; 10.1. Air inlet section; 10.2. Pressurization section; 10.3. Third boundary;

[0056] 11. Air guide slot; 11.1. First boundary; 11.2. Second boundary; Detailed Implementation

[0057] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0058] It should be understood that although the terms upper, middle, lower, top, one end, etc., appear in this document to describe various elements, these elements are not limited by these terms. These terms are only used to distinguish the elements from each other for ease of understanding, and are not used to define any directional or sequential restrictions.

[0059] like Figure 1-11 As shown, an air outlet structure includes a hub portion 1 and blades 2 evenly distributed around the hub portion 1.

[0060] The blade 2 is formed by an air inlet edge 3, an air outlet edge 4, a blade tip portion 5, and a blade root portion 6, and both the air inlet edge 3 and the air outlet edge 4 are S-shaped.

[0061] The height of the air inlet edge 3 and the air outlet edge 4 near the blade tip 5 is greater than that of the blade root 6, giving the blade 2 a tendency to extend relative to the hub 1 or the air outlet direction, thereby constraining the output airflow.

[0062] Among them, the blade 2 has a curved surface, specifically a three-dimensional shape formed by multiple large bends and turns. Combined with the S-shaped blade 2 design, the airflow is relatively stable after it is blown out of the blade 2, as well as the wind speed values ​​on the inner and outer sides of the blade 2, reducing the wind speed difference and constraining the airflow, thus reducing the airflow diffusion.

[0063] The blade 2 has at least a first air-cutting portion 2.1 located inside the blade root portion 6 and a second air-cutting portion 2.2 located outside the blade root portion 6. The first air-cutting portion 2.1 and the second air-cutting portion 2.2 are arched near the blade tip portion 5, and the second air-cutting portion 2.2 extends at least partially outside the hub portion 1. Through the above improvements, the portion of the blade 2 extending outside the hub portion 1 can restrict the output airflow, which is conducive to forming a straight output airflow, increasing the air delivery distance, and thus improving the air circulation effect.

[0064] Furthermore, the wind shear angle of the blade root curve is greater than that of the blade tip curve and transitions towards the blade tip, so that the airflow is turbulent at the blade tip when the blade 2 rotates, which can reduce the noise of the fan blade.

[0065] Preferably, the number of fan blades is 11, which makes the airflow delivered by the fan blades more natural and continuous.

[0066] like Figure 5 As shown, as a further embodiment of the first and second air-cutting sections, the first and second air-cutting sections are divided about the left and right sides of the blade root portion 6, and the first and second air-cutting sections form the curved surface of the blade 2 with its twists and turns. The air inlet edge 3 is formed on the first air-cutting section, the air outlet edge 4 is provided on the second air-cutting section, and the first air-cutting section has a tendency to guide towards the second air-cutting section, while the second air-cutting section has a tendency to converge towards the axial direction.

[0067] Among them, the cross section of the blade root part 6 is an arc surface that is close to the axial direction. The arc surface protrudes towards the air inlet side, and the arc surface is close to the central axis at the air inlet end, while the arc surface is far away from the central axis at the air outlet end. The cross section of the blade tip part 5 is flatter than that of the blade root part 6. It is an arc surface that forms an angle with the end face of the hub part 1. The arc surface protrudes towards the air inlet side, and the projection of the middle part of the blade tip part 5 near the end face of the hub part 1 and the outer end of the air outlet of the blade root part 6 on the axial direction intersects. The cross section of the blade tip part 5 also passes through the axis of the hub part 1.

[0068] In this embodiment, to ensure the strength and airflow cut of the blade 2, the thickness of the blade root portion 6 is greater than that of the blade tip portion 5, and the thickness difference is greater than 2:1. The thickness of the air inlet edge 3 and the air outlet edge 4 is less than that of the middle portion of the blade 2 and transitions towards the middle portion of the blade 2. This thickness design, which is thin on both sides and thick in the middle, is also reflected in the blade root portion 6 and the blade tip portion 5. By setting the blade 2 to a gradual thickness, the middle portion of the blade 2 has sufficient strength, thereby reducing the deformation of the blade 2 during rotation and forming an airflow cut arc surface on the surface of the blade 2. This is beneficial for forming turbulence at the blade tip portion 5, reducing the noise of the fan blade, and avoiding the noise generated by the separation of vortex-shaped airflow on the surface of the blade 2.

[0069] like Figure 6 and Figure 7As shown, specifically, the blade 2 has a root curve, a tip curve, a leading edge curve 7, and a trailing edge curve 8;

[0070] The ratio of the curve radius of the leaf root curve to that of the leaf tip curve satisfies: 0.24 to 0.25; the ratio of their maximum arc height satisfies: 0.34 to 0.67; the ratio of their projected dimensions in the direction of the blade axis 2 satisfies: 0.73 to 0.875; and the ratio of their projected dimensions in the plane perpendicular to the blade axis 2 is 0.30 to 0.34.

[0071] The ratio of the lengths of the leading edge curve 7 and the trailing edge curve 8 is 0.94 to 0.98, and the ratio of their maximum arc height dimensions projected onto the axis of blade 2 is 0.51 to 0.66.

[0072] Specifically, the ratio of the projection distance between the root curve and the tip curve of two adjacent blades 2 in a plane perpendicular to the axis of the blade 2 is 0.08 to 0.125.

[0073] As a further embodiment of blade profile 2:

[0074] The leaf root curve has a radius of 36a to 37a mm and a maximum arc height of 1.8a to 2.8a mm. The projection size of the blade 2 curve in the direction of the blade 2 axis is 25a to 28a mm, and the projection size of the blade 2 curve in the plane perpendicular to the blade 2 axis is 18.2a to 19.8a mm.

[0075] The blade tip curve has a radius of 148a to 150a mm and a maximum arc height of 4.2a to 5.2a mm. The projected size of the blade tip curve in the direction of the blade 2 axis is 32a to 34a mm, and the projected size of the blade tip curve in the plane perpendicular to the blade 2 axis is 57a to 59.5a mm.

[0076] The leading edge curve 7 has a length of 119a to 121a mm, and the maximum arc height of the projection of the leading edge curve 7 onto the axis of the blade 2 is 10.5a to 12.5a mm.

[0077] The trailing edge curve 8 has a length of 124a to 126a mm, and the maximum arc height of the projection of the trailing edge curve 8 onto the axis of the blade 2 is 19a to 20.5a mm.

[0078] Regarding the projection of blade 2 in a plane perpendicular to the axis of blade 2:

[0079] The projection distance between the root curves of two adjacent blades 2 in a plane perpendicular to the axis of blade 2 is 2a to 3a mm.

[0080] The distance between the projections of the tip curves of two adjacent blades 2 onto a plane perpendicular to the axis of the blade 2 is 24a to 25a mm.

[0081] The projection distance between the leading edge curve 7 at a position 0.65 times the distance of the blade tip 5 and the trailing edge curve 8 at a position 0.7 times the distance of the blade tip 5, in a plane perpendicular to the axis of blade 2, is 6.5a to 7.7a ​​mm. The projection distance between the leading edge curve 7 at a position 0.3 times the distance of the blade tip 5 and the trailing edge curve 8 at a position 0.3 times the distance of the blade tip 5, in a plane perpendicular to the axis of blade 2, is 17.8a to 19.2a mm.

[0082] Specifically, the thickness of the blade 2 at the leading edge is 1.0a to 1.2a mm, the thickness at the trailing edge is 1.1a to 1.3a mm, and the thickness of the blade 2 in the middle region between the leading and trailing edges is 2.0a to 3.5a mm; the outer diameter of the blade 2 is 297.5 to 300a mm, and the outer diameter of the hub portion 1 is 72a to 74a mm, where a is a coefficient and a is greater than 0.

[0083] Specifically, the thickness of the blade 2 decreases toward the leading edge curve 7 and the trailing edge curve 8, that is, the blade 2 has the maximum thickness value in the middle and decreases toward the leading edge curve 7 and the trailing edge curve to form a thinner wind-cutting position.

[0084] Furthermore, the projection distance between the leading edge curve 7 on the rear side and the trailing edge curve 8 on the front side of two adjacent blades 2 in a plane perpendicular to the axis of the blade 2 gradually increases from the root of the blade to the tip of the blade.

[0085] Specifically, the wind-cutting angle of the air inlet end of the blade root curve during rotation is 39a to 41a mm, the wind-cutting angle of the air inlet end of the blade tip curve during rotation is 14a to 16a mm, and the wind-cutting angle of the air inlet end at the middle section of the blade 2 during rotation is 18a to 20a mm.

[0086] By restricting the blade profile and edge as described above, the curved surface structure of blade 2 is optimized, reducing the airflow difference between the inside and outside of the airflow, making the airflow straighter, reducing diffusion, increasing airflow and reducing noise under the same blade outer diameter.

[0087] As a further embodiment of the leading edge curve 7 and trailing edge curve 8 of the blade 2 relative to the hub portion 1, the trailing edge curve 8 at the blade tip portion 5, and / or the top boundary of the middle part of the trailing edge curve 8, has a height difference of 16a to 18a mm with the plane of the top of the hub portion 1.

[0088] The height difference between the top boundary point of the air outlet edge 4 and the bottom boundary point of the blade root part 6 is 12a~14amm.

[0089] The height of the hub portion 1 is 28a~30a mm. The blade root curve is located on the outer wall surface of the hub portion 1 at one end near the air inlet side of the blade 2, so that the hub portion 1 guides the wind passing through the blade 2 when the blade 2 rotates. Here, a is a coefficient and satisfies a>0.

[0090] According to one embodiment of the present invention, the height of the hub portion 1 is 28a to 30a mm, and the blade root curve is located on the outer wall surface of the hub portion 1 at one end near the air inlet side of the blade 2. The hub portion 1 with this structure can guide the wind passing through the blade 2 when the blade 2 rotates.

[0091] According to one embodiment of the present invention, the angle between the leading edge curve 7 of the blade and the outer wall of the hub portion 1 near the blade root portion 6 is 69.5°a to 71.5°a mm. This structural design makes it easier for wind to flow from the inside to the outside on the surface of the blade 2 in the design of blades with large slopes.

[0092] According to one embodiment of the present invention, the middle part of the trailing edge curve 8 near the blade tip is 16a-18amm higher than the top surface of the hub, and the height of the trailing edge curve 8 gradually increases towards the blade tip 5. The middle section of the trailing edge curve 8 near the blade root 6 and the top surface of the hub 1 are basically the same height. This structural design can make the wind speed difference between the inside and outside of the blade 2 smaller when cutting the wind.

[0093] According to an embodiment of the present invention, the S-shaped blade 2 is designed with a curved surface shape. The leading edge curve 7 of the structure design has two main wind-cutting areas: an inner arched area and an outer area near the blade tip 5, namely the first wind-cutting area 2.1 and the second wind-cutting area 2.2. This makes the wind more even on the inner and outer sides when it passes over the blade 2, and the actual difference in wind speed between the inner and outer sides is ≤1m / s.

[0094] According to one embodiment of the present invention, the blade 2 adopts an architecture design with 11 blades 2. This architecture design makes the wind cutting efficiency of the blade 2 higher. Under the same blade area and the same rotation speed, the wind cutting efficiency is 20% to 50% higher than that of the 7-blade and 9-blade architectures.

[0095] According to one embodiment of the present invention, the hub portion 1 is a hollow cylinder with an opening facing the air inlet side of the blade 2, and the side wall thickness is 2a to 2.7a mm. The design of the wall thickness of the hub portion 1 to be 2.0a to 2.7a mm is sufficient to meet the requirements of hub strength.

[0096] According to one embodiment of the present invention, a positioning rib is provided on the inner wall of the cylindrical hub 1. The drive shaft of the motor can be installed in the opening of the cylinder and positioned by the positioning pin. Eleven reinforcing ribs are evenly distributed along the axis of the inner wall of the hub 1 at the corresponding position of the root of each blade 2 to improve the overall strength of the blade 2 and avoid hub deformation.

[0097] According to one embodiment of the present invention, a is a coefficient value between 0.9 and 1. The blade 2 supported by the coefficient within this range is smaller in size and meets the requirements of low speed, high wind speed and low noise in the fan, and can be better applied to the fan.

[0098] When a equals 1:

[0099] Existing technology fan blades 800 4.9m / s 52dB Fan blade of the present invention 800 5.6m / s 51dB

[0100] Preferably, the blade 2 has a forward-convex outer side near the blade tip that is much higher than the inner side of the blade 2 at the blade root. During operation, the blade 2 rotates at a low speed and generates high wind speed. The setting of 11 blades 2 can improve wind cutting efficiency and achieve higher wind speed at a lower speed. More specifically, by adopting the air outlet structure of the present invention, higher wind speed can be provided at the same speed, and the same wind speed can be achieved at a lower speed, thereby reducing motor energy consumption.

[0101] In this invention, the wind-cutting angle at the root is larger than that at the blade tip 5 compared to existing products. The blade 2 has a complex profile, and the edges of the air inlet (leading edge curve 7) and air outlet (tailing edge curve 8) are designed to be S-shaped. The leading edge surface and the trailing edge curve 8 are higher near the blade tip than at the root, so that the blade 2 can take in more air and has a higher wind-cutting efficiency when rotating.

[0102] like Figures 12 to 16 As shown, the present invention also provides an air outlet bracket 9, including the above-mentioned air outlet structure, the air outlet structure being arranged inside the air outlet bracket 9, an air duct being formed inside the air outlet bracket 9, and the shortest distance between the air duct and the blade tip portion 5 being 1a to 8a mm.

[0103] By controlling the distance between the outer boundary of blade 2 and the air duct, it is beneficial to provide a converging effect on the airflow, so that the airflow is output within the expected air outlet area and the air outlet distance is increased.

[0104] Specifically, the air duct assembly includes a front frame 9.1, a middle frame 9.2, and a rear frame 9.3 for forming the air duct. The rear frame 9.3 forms an air inlet 9.4 on one side of the middle frame 9.2, and the front frame 9.1 forms an air outlet 9.5 on the other side of the middle frame 9.2. The middle frame 9.2 is enclosed around the air duct, thereby forming a complete annular air cavity. During operation, the blades 2 rotate to cut the air, thereby forming an airflow path. When the airflow passes through the middle frame 9.2, it is pressurized, accelerated, and guided, and finally ejected from the air outlet 9.5 of the front frame 9.1.

[0105] Optionally, the middle frame 9.2 may be integrally formed on the peripheral boundary of the rear frame 9.3.

[0106] As a further embodiment of the middle frame 9.2, the middle frame 9.2 has a funnel-shaped air guide portion 10 corresponding to the air inlet 9.4. The funnel-shaped air guide portion 10 creates a Venturi effect at the air inlet 9.4, causing the airflow to be accelerated and pressurized after passing through the middle frame 9.2. In addition, the air guide portion 10 has multiple air guide grooves 11 circumferentially opened. The air guide grooves 11 are arranged with respect to the airflow path and have a certain length with respect to the airflow direction. Thus, the airflow is sorted and guided by the air guide grooves 11, giving the surface airflow of the inner wall of the middle frame 9.2 a directionality towards the air outlet 9.5, and the guiding direction is consistent, thereby reducing the diffusion of airflow. At the same time, the regular airflow also reduces wind noise and fan vibration during operation.

[0107] like Figure 14 As shown, specifically, the air guide section 10 includes an air inlet section 10.1 and a pressurization section 10.2. The air inlet section 10.1 is flared outward toward the air inlet 9.4, and the pressurization section 10.2 is connected to the constricted end of the air inlet section 10.1 and is flared outward toward the air outlet 9.5. The flared air inlet section 10.1 creates a Venturi effect, thereby increasing the wind speed. After passing through the air inlet section 10.1, the airflow is pressurized in the pressurization section 10.2, so that the air guide section 10 and the air guide groove 11 define the airflow path in the air duct and constrict the airflow at the air outlet 9.5.

[0108] Optionally, the pressurization section 10.2 also tends to narrow towards the air outlet 9.5 to further improve the airflow convergence and pressurization effect.

[0109] As a further embodiment of the air guide duct 11, the air guide duct 11 includes a first boundary 11.1 and a second boundary 11.2 set with respect to the air outlet direction. A third boundary 10.3, consistent with the air inlet section 10.1, is also present between the air guide ducts 11. The first boundary 11.1 and the second boundary 11.2 tend to expand outwards with respect to the third boundary 10.3. The first boundary 11.1 is approximately parallel to the pressurization section 10.2 and connects to the air inlet section 10.1. The second boundary 11.2 is widened towards the air inlet 9.4, and its narrowing point connects to the pressurization section 10.2. Through these improvements, the second boundary 11.2 further pressurizes the surface airflow, and the first boundary 11.1 and the third boundary 10.3 guide and organize the main airflow and the surface airflow. Furthermore, both the second boundary 11.2 and the air inlet section 10.1 tend to converge towards the air outlet 9.5, thereby converging the airflow and preventing airflow diffusion within the duct.

[0110] In this embodiment, the air guide 11 is connected from the air inlet section 10.1 to the pressurization section 10.2. The air guide 11 interrupts the airflow vortex and reduces the noise of the airflow in this part.

[0111] This specific embodiment is merely an explanation of the present invention and is not intended to limit the invention. After reading this specification, those skilled in the art can make modifications to this embodiment without contributing any inventive step, but such modifications are protected by patent law as long as they are within the scope of the claims of the present invention.

Claims

1. An air outlet structure, comprising a hub (1) and blades (2) evenly distributed around the hub (1), wherein the blades (2) are formed by an air inlet edge (3), an air outlet edge (4), a blade tip portion (5) and a blade root portion (6), wherein the air inlet edge (3) has a leading edge curve (7), the air outlet edge (4) has a trailing edge curve (8), the blade tip portion (5) has a blade tip curve, and the blade root portion (6) has a blade root curve; Its features are: Furthermore, both the air inlet edge (3) and the air outlet edge (4) are S-shaped. The height of the air inlet edge (3) and the air outlet edge (4) near the blade tip (5) is greater than that of the blade root (6). The difference in plane height between the top boundary point of the air outlet edge (4) and the bottom boundary point of the blade root (6) is 12a~14amm, where a is a coefficient and satisfies a>0. The blade (2) has at least a first wind-cutting portion (2.1) located inside the blade root portion (6) and a second wind-cutting portion (2.2) located outside the blade root portion (6). The first wind-cutting portion (2.1) and the second wind-cutting portion (2.2) are arched near the blade tip portion (5). The second wind-cutting portion (2.2) extends at least partially outside the hub portion (1). The wind-cutting angle of the blade root curve is greater than the wind-cutting angle of the blade tip curve and transitions toward the blade tip portion (5). The blade (2) has a root curve, a tip curve, a leading edge curve (7) and a trailing edge curve (8); The ratio of the curve radius of the leaf root curve to that of the leaf tip curve satisfies: 0.24 to 0.25, the ratio of their maximum arc height satisfies: 0.34 to 0.67, the ratio of their projected dimensions in the direction of the blade (2) axis satisfies: 0.73 to 0.875, and the ratio of their projected dimensions in the plane perpendicular to the blade (2) axis is 0.30 to 0.

34. The ratio of the lengths of the leading edge curve (7) and the trailing edge curve (8) is 0.94 to 0.98, and the ratio of the maximum arc height dimensions projected onto the blade (2) axis is 0.51 to 0.

66. The ratio of the projection distance between the root curve and tip curve of two adjacent blades (2) in a plane perpendicular to the axis of the blade (2) is 0.08 to 0.

125. The projection distance between the leading edge curve (7) at a position 0.65 times the distance of the leaf tip (5) and the trailing edge curve (8) at a position 0.7 times the distance of the leaf tip (5) in the plane perpendicular to the axis of the blade (2) is 6.5a to 7.7a ​​mm. The projection distance between the leading edge curve (7) at a position 0.3 times the distance of the leaf tip (5) and the trailing edge curve (8) at a position 0.3 times the distance of the leaf tip (5) in the plane perpendicular to the axis of the blade (2) is 17.8a to 19.2a mm. The trailing edge curve (8) at the blade tip portion (5), and / or the top boundary of the middle part of the trailing edge curve (8) has a plane height difference of 16a to 18a mm with the top of the hub portion (1); the height of the hub portion (1) is 28a to 30a mm.

2. The air outlet structure according to claim 1, characterized in that: The thickness of the leaf root (6) is greater than that of the leaf tip (5), and the thickness difference is greater than 2:

1. The thickness of the leaf blade (2) decreases toward the leading edge curve (7) and the trailing edge curve (8).

3. The air outlet structure according to claim 1, characterized in that: The projection distance between the leading edge curve (7) on the rear side and the trailing edge curve (8) on the front side of two adjacent blades (2) in a plane perpendicular to the axis of the blade (2) gradually increases from the root of the blade to the tip of the blade.

4. An air outlet structure according to any one of claims 1-3, characterized in that: 'a' is a coefficient with a value ranging from 0.9 to 1.

5. An air outlet bracket, characterized in that: The air outlet structure includes any one of claims 1 to 3, wherein the air outlet structure is arranged in the air outlet bracket (9), the air outlet bracket (9) forms an air duct, and the shortest distance between the air duct and the blade tip (5) of the blade (2) is 1a to 8a mm.

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