Centrifugal fan wheel, centrifugal fan and air conditioning equipment

Abstract

The utility model discloses a centrifugal fan wheel, centrifugal fan and air conditioning equipment, centrifugal fan wheel is integral piece and include: middle disc, blade group, blade group is located in the one side of middle disc along centrifugal fan wheel axial direction, and blade group includes the multiple blades of interval setting along centrifugal fan wheel peripheral direction, and the end face of one end of blade along centrifugal fan wheel axial direction is connected with middle disc, annular border, annular border is spaced apart with middle disc along centrifugal fan wheel axial direction, and the tail edge of one end of blade away from middle disc is connected with the inner peripheral wall of annular border, in the direction from annular border to middle disc, the distance between the tail edge of blade and the axis of centrifugal fan wheel gradually reduces. According to the centrifugal fan wheel of the utility model, can avoid producing the release model muscle, make the surface of blade be the smooth surface, reduce the separation phenomenon in the process of airflow flow, improve the doing function of centrifugal fan wheel, improve the fan efficiency, reduce the noise simultaneously.

Description

Technical Field

[0001] This utility model relates to the field of air handling equipment technology, and in particular to a centrifugal impeller, a centrifugal fan and an air conditioning device. Background Technology

[0002] In related technologies, during the injection molding process of conventional centrifugal fan blades, the mold has a certain draft angle because demolding is required. Due to the existence of the draft angle, the part of the mold corresponding to the blade root is smaller than the part of the blade tip. Therefore, a rib-like demolding rib is generated at the trailing edge of the blade from the blade tip to the blade root. The demolding rib causes severe separation of the airflow flowing over the blade surface at the tail end, resulting in reduced fan efficiency and increased noise. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention proposes a centrifugal impeller that is highly efficient and has low noise.

[0004] This utility model also proposes a centrifugal fan, which includes the centrifugal impeller described above.

[0005] This utility model also proposes an air conditioning device, which includes the centrifugal fan described above.

[0006] According to an embodiment of the present invention, the centrifugal impeller is a single piece and includes: a central disk; a blade assembly, the blade assembly being disposed on one side of the central disk along the axial direction of the centrifugal impeller, the blade assembly including a plurality of blades spaced apart along the circumferential direction of the centrifugal impeller, the end face of one end of the blade along the axial direction of the centrifugal impeller being connected to the central disk; and an annular frame, the annular frame being spaced apart from the central disk along the axial direction of the centrifugal impeller, the trailing edge of the blade away from the central disk being connected to the inner peripheral wall of the annular frame, and the distance between the trailing edge of the blade and the axis of the centrifugal impeller gradually decreasing in the direction from the annular frame to the central disk.

[0007] According to the centrifugal impeller of this utility model embodiment, the end face of one end of the blade along the axial direction of the centrifugal impeller is connected to the middle plate, and the tail edge of the other end is connected to the inner peripheral wall of the annular frame. In the direction from the annular frame to the middle plate, the distance between the tail edge of the blade and the axis of the centrifugal impeller gradually decreases, which can make the change trend of the tail edge of the blade adapt to the draft angle of the mold, and reserve space for the inward shrinkage due to drafting. This allows the areas of both surfaces in the thickness direction of the blade to fit with the mold, thereby avoiding the generation of demolding ribs, making the surface of the blade a smooth surface, reducing the separation phenomenon during airflow, improving the work capacity of the centrifugal impeller, improving the efficiency of the fan, and reducing noise.

[0008] According to some embodiments of the present invention, the two sides of the blade in the thickness direction are a suction surface and a pressure surface, respectively, the leading edge of the blade extends obliquely toward the suction surface, and the connection between the suction surface and the inner peripheral wall of the annular frame has a rounded corner.

[0009] In some embodiments of this utility model, the minimum distance between the rounded corner surface and the axis of the centrifugal impeller is D2, and the distance between the area outside the connection area between the trailing edge of the blade and the annular frame and the axis of the centrifugal impeller along the axial direction of the centrifugal impeller is D3, and satisfies: D3 < D2.

[0010] According to some embodiments of the present invention, the blade has a non-uniform thickness structure in the direction from the trailing edge to the leading edge of the blade.

[0011] In some embodiments of this invention, the thickness of the blade gradually increases and then gradually decreases in the direction from the trailing edge to the leading edge of the blade.

[0012] In some embodiments of this utility model, on a cross-section perpendicular to the axial direction of the centrifugal impeller, the blade has a central arc that divides the blade thickness equally. The diameter of the circle whose center is located on the central arc and is inscribed in the two surfaces of the blade thickness direction is the thickness of the blade at the point of tangency. The center of the inscribed circle at the maximum thickness position of the blade is K. The center point of the leading edge of the blade is E, and the center point of the trailing edge of the blade is F, and 0.3≤EK / FK≤0.6 is satisfied.

[0013] In some embodiments of this utility model, the maximum thickness of the blade is Wmax, the minimum thickness of the blade is Wmin, and the following condition is met: 0.3≤Wmin / Wmax≤0.6.

[0014] In some embodiments of this invention, the minimum thickness of the blade is located at the trailing edge of the blade.

[0015] According to some embodiments of the present invention, on a cross-section perpendicular to the axial direction of the centrifugal impeller, the blade has a central arc that divides the blade thickness equally, and the angle between the tangents at both ends of the central arc is the airflow turning angle θ, which satisfies: 94°≤θ≤110°.

[0016] In some embodiments of this utility model, there are two sets of blades, which are respectively located on both sides of the central disk along the axial direction of the centrifugal impeller. There are two annular frames, which are respectively located on both sides of the central disk along the axial direction of the centrifugal impeller and are connected to the two sets of blades in a one-to-one correspondence.

[0017] The centrifugal fan according to an embodiment of the present invention includes: a volute; and the aforementioned centrifugal impeller, wherein the centrifugal impeller is disposed within the volute.

[0018] According to the centrifugal fan of this utility model embodiment, by setting the centrifugal impeller as described above, one end face of the blade along the axial direction of the centrifugal impeller is connected to the middle plate, and the tail edge of the other end is connected to the inner peripheral wall of the annular frame. In the direction from the annular frame to the middle plate, the distance between the tail edge of the blade and the axis of the centrifugal impeller gradually decreases, which can make the change trend of the tail edge of the blade adapt to the draft angle of the mold, and reserve space for the inward shrinkage due to drafting. This allows the areas of both surfaces in the thickness direction of the blade to fit with the mold, thereby avoiding the generation of demolding ribs, making the surface of the blade a smooth surface, reducing the separation phenomenon during the airflow process, improving the work capacity of the centrifugal impeller, improving the efficiency of the fan, and reducing noise.

[0019] In some embodiments of this utility model, the volute has an air outlet diffuser section, one end of which is formed with an air outlet. In the direction toward the air outlet, at least one of the two side walls of the air outlet diffuser section that are opposite each other along the axial direction of the centrifugal impeller are inclined outward.

[0020] In some embodiments of this utility model, the volute has a volute tongue, and the area of ​​the volute tongue opposite to the annular frame has a recessed portion that is recessed toward the outside of the volute.

[0021] The air conditioning equipment according to the present invention includes the centrifugal fan described above.

[0022] According to the air conditioning equipment of this utility model embodiment, by setting the above-mentioned centrifugal fan, including the above-mentioned centrifugal impeller, the end face of one end of the blade along the axial direction of the centrifugal impeller is connected to the middle plate, and the tail edge of the other end is connected to the inner peripheral wall of the annular frame. In the direction from the annular frame to the middle plate, the distance between the tail edge of the blade and the axis of the centrifugal impeller gradually decreases, which can make the change trend of the tail edge of the blade adapt to the draft angle of the mold, and reserve space for the inward shrinkage due to drafting, so that the areas of both surfaces in the thickness direction of the blade can fit with the mold, thereby avoiding the generation of demolding ribs, making the surface of the blade a smooth surface, reducing the separation phenomenon in the airflow process, improving the work capacity of the centrifugal impeller, improving the fan efficiency, and reducing noise.

[0023] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0024] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0025] Figure 1 This is a perspective view of the centrifugal impeller according to an embodiment of the present utility model;

[0026] Figure 2 This is a front view of the centrifugal impeller according to an embodiment of the present utility model;

[0027] Figure 3 This is a top view of the centrifugal impeller according to an embodiment of the present utility model;

[0028] Figure 4 This is a partial cross-sectional view of the centrifugal impeller according to an embodiment of the present utility model;

[0029] Figure 5 yes Figure 4 Enlarged view of point A in the middle;

[0030] Figure 6 This is a partially enlarged view of the connection position between the annular frame and the blades of the centrifugal impeller according to an embodiment of the present utility model;

[0031] Figure 7 This is a partially enlarged view of the connection position of the middle plate and blades of the centrifugal impeller according to an embodiment of the present utility model;

[0032] Figure 8 This is a schematic diagram of the blades of a centrifugal impeller according to an embodiment of the present utility model;

[0033] Figure 9 This is a schematic diagram of the blades of a centrifugal impeller according to an embodiment of the present invention, showing the inscribed circles at different positions of the blades;

[0034] Figure 10 This is a schematic diagram of the blades of a centrifugal impeller according to an embodiment of the present invention, showing the airflow deflection angle of the blades;

[0035] Figure 11 This is a perspective view of a centrifugal fan according to an embodiment of the present utility model;

[0036] Figure 12 This is a front view of a centrifugal fan according to an embodiment of the present utility model;

[0037] Figure 13 This is a top view of a centrifugal fan according to an embodiment of the present utility model;

[0038] Figure 14 It is along Figure 13 A cross-sectional view along the BB line.

[0039] Figure label:

[0040] 100. Centrifugal fan;

[0041] 10. Centrifugal fan;

[0042] 1. Mid-game;

[0043] 2. Blade assembly; 21. Blade; 211. Leading edge; 212. Trailing edge; 213. Suction surface; 214. Pressure surface; 215. Rounded corner surface; 216. Blade tip; 217. Blade root; 218. Mid-curve;

[0044] 3. Circular border;

[0045] 20. Snail shell;

[0046] 201. Main body section; 2011. Air inlet; 202. Air outlet diffuser section; 2021. Air outlet; 203. Volute tongue; 2031. Recessed part. Detailed Implementation

[0047] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0048] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this utility model 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, and therefore should not be construed as a limitation of this utility model. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0049] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0050] The centrifugal impeller 10 according to an embodiment of the present invention is described below with reference to the accompanying drawings.

[0051] like Figures 1-3 As shown, the centrifugal impeller 10 according to an embodiment of the present invention includes a central disk 1, a blade assembly 2, and an annular frame 3.

[0052] Specifically, the centrifugal impeller 10 is a single piece, which can be a single injection molded part. This simplifies the assembly process of the centrifugal impeller 10 and improves the reliability of the connection between the various components of the centrifugal impeller 10.

[0053] like Figure 1 and Figure 3 As shown, the middle plate 1 can be a disc-shaped structure, specifically a circular disc-shaped structure. The middle plate 1 can be perpendicular to the axis of the centrifugal impeller 10, that is, the thickness direction of the middle plate 1 can be the same as the axis direction of the centrifugal impeller 10.

[0054] like Figure 1 and Figure 2 As shown, the blade assembly 2 is located on one side of the central disk 1 along the axial direction of the centrifugal impeller 10. The blade assembly 2 includes a plurality of blades 21 spaced apart along the circumferential direction of the centrifugal impeller 10. The end face of one end of the blade 21 along the axial direction of the centrifugal impeller 10 is connected to the surface of the central disk 1 along the axial direction of the centrifugal impeller 10. The central disk 1 can connect the plurality of blades 21 together, and along the circumferential direction of the centrifugal impeller 10, the central disk 1 can fix the plurality of blades 21 at a predetermined distance and angle, so that the blades 21 can better drive the airflow.

[0055] like Figures 1-3 As shown, for reference Figure 4The annular frame 3 and the central disk 1 are spaced apart along the axial direction of the centrifugal impeller 10. The trailing edge 212 of the blade 21, which is away from the central disk 1, is connected to the inner peripheral wall of the annular frame 3. Specifically, the end of the blade 21 closer to the axis of the centrifugal impeller 10 in the width direction is the leading edge 211, and the end of the blade 21 further away from the axis of the centrifugal impeller 10 in the width direction is the trailing edge 212. The annular frame 3 is circular, and the blade 21 is located radially inside the annular frame 3 with its trailing edge 212 connected to the inner peripheral wall. This not only fixes the blade 21 through the annular frame 3, but also prevents the annular frame 3 from obstructing the mold used to form multiple blades 21 at the center of the centrifugal impeller 10 during injection molding. This facilitates the demolding of the mold used to form multiple blades 21 from the inner space of the annular frame 3, thus facilitating the injection molding process of the centrifugal impeller 10.

[0056] In related technologies, the blades of conventional centrifugal fans have the same outer diameter from the blade root to the blade tip. That is, from the blade root to the blade tip, the distance between the trailing edge of the blade and the axis of the centrifugal fan is equal. During the injection molding process, the mold has a certain draft angle because demolding is required. Due to the existence of the draft angle, the part of the mold corresponding to the blade root is smaller than the part of the blade tip. Therefore, a rib-like demolding rib will be generated on the trailing edge of the blade from the blade tip to the blade root, which deviates from the design shape. The demolding rib causes the airflow flowing over the blade surface to be severely separated at the tail end, resulting in a decrease in fan efficiency and an increase in noise.

[0057] It should be noted that the outer diameter of the blade 21 is twice the maximum distance between the outermost contour of the blade 21, i.e., the trailing edge 212 of the blade 21, and the axis of the centrifugal impeller 10. The end of the blade 21 connected to the central disk 1 is the blade root 217, and the end of the blade 21 connected to the annular frame 3 is the blade tip 216.

[0058] In this invention, in the direction from the annular frame 3 to the central plate 1, that is, in the direction from the blade tip 216 to the blade root 217 of the blade 21, the distance between the trailing edge 212 of the blade 21 and the axis of the centrifugal impeller 10 gradually decreases. It can be understood that in the direction from the annular frame 3 to the central plate 1, that is, in the direction from the blade tip 216 to the blade root 217 of the blade 21, the outer diameter of the blade 21 gradually decreases, and the outer diameter of the area on the blade 21 other than the connection point with the annular frame 3 is smaller than the outer diameter of the area where the blade 21 connects with the annular frame 3. This allows the changing trend of the trailing edge 212 of the blade 21 to adapt to the draft angle of the mold, reserving space for inward contraction during drafting. This ensures that the areas of both surfaces of the blade 21 in the thickness direction can fit snugly against the mold, thereby avoiding the formation of release ribs, making the surface of the blade 21 smooth, reducing separation during airflow, improving the work capacity of the centrifugal impeller 10, increasing fan efficiency, and reducing noise.

[0059] Additionally, it is understood that, at least in the region between the annular frame 3 and the central disk 1, in the direction from the annular frame 3 to the central disk 1, the outer diameter of the centrifugal impeller 10 gradually decreases as the maximum distance between the trailing edge 212 of the blade 21 and the axis of the centrifugal impeller 10 gradually decreases.

[0060] According to the centrifugal impeller 10 of this utility model embodiment, the end face of one end of the blade 21 along the axial direction of the centrifugal impeller 10 is connected to the middle disk 1, and the tail edge 212 of the other end is connected to the inner peripheral wall of the annular frame 3. In the direction from the annular frame 3 to the middle disk 1, the distance between the tail edge 212 of the blade 21 and the axis of the centrifugal impeller 10 gradually decreases. This allows the changing trend of the tail edge 212 of the blade 21 to adapt to the draft angle of the mold, and reserves space for the inward shrinkage due to drafting. This allows the areas of both surfaces of the blade 21 in the thickness direction to fit with the mold, thereby avoiding the generation of demolding ribs, making the surface of the blade 21 a smooth surface, reducing the separation phenomenon during the airflow process, improving the work capacity of the centrifugal impeller 10, improving the efficiency of the fan, and reducing noise.

[0061] In some embodiments of this utility model, such as Figures 4-6 As shown, the two sides of the blade 21 in the thickness direction are the suction surface 213 and the pressure surface 214, respectively. The leading edge 211 of the blade 21 extends obliquely towards the suction surface 213, and the connection between the suction surface 213 and the inner peripheral wall of the annular frame 3 has a rounded corner surface 215. It can be understood that the acute angle where the blade 21 connects to the annular frame 3 is rounded. This rounded corner treatment between the blade 21 and the annular frame 3 increases the contact area between them, also increases the material thickness, and improves the structural strength of the centrifugal impeller 10, thereby improving the reliability of the centrifugal impeller 10.

[0062] Optionally, such as Figure 5 As shown, the rounded corner surface 215 includes a single arc surface or multiple arc surfaces connected in sequence. When the rounded corner surface 215 includes multiple arc surfaces connected in sequence, the radii of the multiple arc surfaces may be the same or different.

[0063] In some embodiments of this utility model, the minimum distance between the rounded corner surface 215 and the axis of the centrifugal impeller 10 is D2. Along the axial direction of the centrifugal impeller 10, the distance between the area outside the connection region between the trailing edge 212 of the blade 21 and the annular frame 3 and the axis of the centrifugal impeller 10 is D3, and D3 < D2. This avoids the rounded corner surface 215 obstructing the mold at the center of the centrifugal impeller 10 used to form multiple blades 21, facilitating the demolding of the mold at the center of the centrifugal impeller 10 from the inner space of the annular frame 3, and facilitating the injection molding process of the centrifugal impeller 10.

[0064] In some examples of this invention, along the axial direction of the centrifugal impeller 10, the maximum distance between the area outside the connection region between the trailing edge 212 of the blade 21 and the annular frame 3 and the axis of the centrifugal impeller 10 is D3, and satisfies: D3 < D2. This avoids the rounded corner surface 215 obstructing the mold at the center of the centrifugal impeller 10 used to form multiple blades 21, facilitating the demolding of the mold at the center of the centrifugal impeller 10 from the inner space of the annular frame 3, and facilitating the injection molding process of the centrifugal impeller 10.

[0065] In some embodiments of this utility model, such as Figure 7 As shown, at the blade root 217 of blade 21, the position where the distance between the trailing edge 212 of blade 21 and the axis of centrifugal impeller 10 is greatest is flush with the outer peripheral wall of the central disk 1. That is, at the blade root 217 of blade 21, the maximum distance between the trailing edge 212 of blade 21 and the axis of centrifugal impeller 10 is equal to the radius of the central disk 1. This facilitates the injection molding of centrifugal impeller 10, and also facilitates the centrifugal impeller 10 in driving airflow, resulting in better aerodynamic noise and higher efficiency of centrifugal impeller 10.

[0066] In some embodiments of this utility model, such as Figure 8 As shown, in the direction from the trailing edge 212 to the leading edge 211 of blade 21, blade 21 has a non-uniform thickness structure. It can be understood that, in this direction, there are at least two points on blade 21 where the thickness differs. Specifically, in this direction, the thickness of blade 21 can first increase and then decrease, or first decrease and then increase, or gradually decrease or gradually increase, etc. Therefore, aerodynamic performance can be improved through thickness gradient optimization, thereby increasing efficiency. Furthermore, it can also achieve enhanced structural strength, extended fatigue life, and improved process adaptability.

[0067] In addition, the thickness is the same at the same position on any two cross sections perpendicular to the axis of the centrifugal impeller 10.

[0068] In some embodiments of this utility model, such as Figure 8 and Figure 9 As shown, in the direction from the trailing edge 212 to the leading edge 211 of blade 21, the thickness of blade 21 first gradually increases and then gradually decreases. It can be understood that, in the direction from the trailing edge 212 to the leading edge 211, the thickness of blade 21 is greatest in the middle region of blade 21, and gradually decreases from the middle region towards the leading edge 211 and trailing edge 212. This improves airflow guidance and pressure distribution, adapts to different operating conditions, improves aerodynamic performance, and increases the structural strength of blade 21. Furthermore, it reduces aerodynamic noise, suppresses self-excited vibration, reduces flow losses, improves efficiency, and reduces energy consumption.

[0069] Furthermore, such as Figure 8 and Figure 9 As shown, in a cross-section perpendicular to the axial direction of the centrifugal impeller 10, the blade 21 has a central arc 218 that equally divides the thickness of the blade 21. The diameter of the circle centered on the central arc 218 and inscribed in the two surfaces of the blade 21 in the thickness direction is the thickness of the blade 21 at the point of tangency. The center of the inscribed circle at the position of maximum thickness of the blade 21 is K. The center point of the leading edge 211 of the blade 21 is E, and the center point of the trailing edge 212 of the blade 21 is F, satisfying 0.3≤EK / FK≤0.6, where EK is the straight-line distance between points E and K, and FK is the straight-line distance between points F and K. It can be understood that from point K towards the leading edge 211 and trailing edge 212 of the blade 21, the thickness of the blade 21 gradually decreases, and the distance between the position of maximum thickness of the blade 21 and the leading edge 211 is less than the distance between the position of maximum thickness of the blade 21 and the trailing edge 212. For example, EK / FK can be 0.3, 0.35, 0.4, 0.45, 0.5, 0.55 or 0.6.

[0070] This can improve airflow guidance and pressure distribution, adapt to different operating conditions, improve aerodynamic performance, and increase the structural strength of blade 21. In addition, it can reduce aerodynamic noise, suppress self-excited vibration, reduce flow loss, improve efficiency, and reduce energy consumption.

[0071] Preferably, the straight-line distance EK between point E and point K and the straight-line distance FK between point F and point K satisfy: EK / FK = 0.4.

[0072] In some embodiments of this utility model, such as Figure 8 and Figure 9As shown, the maximum thickness of blade 21 is Wmax, and the minimum thickness of blade 21 is Wmin, satisfying the condition: 0.3 ≤ Wmin / Wmax ≤ 0.6. For example, Wmin / Wmax can be 0.3, 0.35, 0.4, 0.45, 0.5, 0.55, or 0.6, etc. This can improve airflow guidance and pressure distribution, adapt to different operating conditions, improve aerodynamic performance, and increase the structural strength of blade 21. In addition, it can reduce aerodynamic noise, suppress self-excited vibration, reduce flow losses, improve efficiency, and reduce energy consumption.

[0073] Preferably, the maximum thickness of blade 21, Wmax, and the minimum thickness of blade 21, Wmin, satisfy: Wmin / Wmax = 0.44.

[0074] In some embodiments of this utility model, such as Figure 9 As shown, combined with Figure 4 The minimum thickness of blade 21 is located at its trailing edge 212. It can be understood that the thickness of blade 21 is smallest at its trailing edge 212 in the direction from the trailing edge 212 to the leading edge 211. This reduces trailing edge vortex and pressure drag, improves outlet airflow uniformity, enhances aerodynamic performance, and increases the structural strength of blade 21. Furthermore, it reduces aerodynamic noise, suppresses self-excited vibration, improves efficiency, and reduces energy consumption.

[0075] In some embodiments of this utility model, such as Figure 10 As shown, in a cross-section perpendicular to the axial direction of the centrifugal impeller 10, the blade 21 has a central arc 218 that equally divides the thickness of the blade 21. The angle between the tangents at both ends of the central arc 218 is the airflow turning angle θ, which satisfies: 94°≤θ≤110°. It can be understood that the angle between the tangents at point E and point F of the central arc 218 is θ. For example, the angle between the tangents at both ends of the central arc 218 is the airflow turning angle θ, which can be 94°, 95°, 96°, 97°, 98°, 99°, 100°, 101°, 102°, 103°, 104°, 105°, 106°, 107°, 108°, 109°, or 110°, etc.

[0076] This allows the blades 21 to guide the airflow in a more fluid dynamic manner, increasing the lift coefficient while preventing airflow separation due to excessive angles, reducing flow losses, and thus improving the working efficiency of the centrifugal impeller 10. Furthermore, it balances efficiency and pressure stability, adapting to different operating conditions, and reduces noise and vibration while improving structural reliability, achieving a comprehensive improvement in the performance of the centrifugal impeller 10.

[0077] Preferably, the angle θ between the tangents at both ends of the middle arc 218 is 104°.

[0078] In some embodiments of this utility model, such as Figure 1 and Figure 2 As shown, there are two sets of blades 2, located on both sides of the central disk 1 along the axial direction of the centrifugal impeller 10. There are also two annular frames 3, each located on one side of the central disk 1 along the axial direction of the centrifugal impeller 10 and connected to one of the two sets of blades 2. This increases the flow rate and pressure coefficient of the centrifugal impeller 10, and the two sets of blades 2 balance the pressure distribution on both sides of the central disk 1, suppressing vortex generation and improving airflow uniformity, thereby optimizing aerodynamic performance. Furthermore, it improves the structural strength of the centrifugal impeller 10, reduces aerodynamic noise, increases efficiency, reduces energy consumption, and allows it to be adapted to more applications.

[0079] Furthermore, such as Figure 1 and Figure 2 As shown, along the circumferential direction of the centrifugal impeller 10, multiple blades 21 of the two sets of blade groups 2 are alternately arranged, which can better improve the flow rate and pressure coefficient of the centrifugal impeller 10, improve airflow uniformity, and thus optimize aerodynamic performance. In addition, it can improve the structural strength of the centrifugal impeller 10, reduce aerodynamic noise, improve efficiency, reduce energy consumption, and adapt to more applications.

[0080] The following is for reference. Figures 11-14 A centrifugal fan 100 according to an embodiment of the present utility model is described.

[0081] like Figures 11-14 As shown, the centrifugal fan 100 according to an embodiment of the present invention includes a volute 20 and the centrifugal impeller 10 described above.

[0082] Specifically, the centrifugal impeller 10 is housed within the volute 20, which includes a main body section 201 and an outlet diffuser section 202. The main body section 201 is generally cylindrical, and the centrifugal impeller 10 is housed within it. The volute 20 has an air inlet 2011 and an air outlet 2021. At least one side of the volute 20 along the axial direction of the centrifugal impeller 10 may have an air inlet 2011, which is located on the main body section 201. One end of the outlet diffuser section 202 is connected to the peripheral wall of the main body section 201, and the other end forms the air outlet 2021. Under the action of the centrifugal impeller 10, airflow enters the volute 20 through the air inlet 2011 along the axial direction of the centrifugal impeller 10, then flows radially out to the air outlet 2021, and finally exits the volute 20.

[0083] In addition, the centrifugal fan 100 may also include a drive motor, which is mounted on the volute 20. The output shaft of the drive motor is connected to the centrifugal impeller 10, specifically to the central plate 1 of the centrifugal impeller 10, for driving the centrifugal impeller 10 to rotate.

[0084] Furthermore, the centrifugal fan 100 may also include a motor bracket, which may be located at one end of the volute 20 along the axial direction of the centrifugal impeller 10, and the drive motor may be fixed to the motor bracket. Of course, the centrifugal fan 100 may also include a motor cover, which is connected to the motor bracket, and the drive motor is fixed within the space defined between the motor bracket and the motor cover.

[0085] According to the centrifugal fan 100 of this utility model embodiment, by setting the centrifugal impeller 10 as described above, the end face of one end of the blade 21 along the axial direction of the centrifugal impeller 10 is connected to the middle plate 1, and the tail edge 212 of the other end is connected to the inner peripheral wall of the annular frame 3. In the direction from the annular frame 3 to the middle plate 1, the distance between the tail edge 212 of the blade 21 and the axis of the centrifugal impeller 10 gradually decreases. This allows the changing trend of the tail edge 212 of the blade 21 to adapt to the draft angle of the mold, reserving space for the inward shrinkage due to drafting. This allows the areas of both surfaces of the blade 21 in the thickness direction to fit with the mold, thereby avoiding the generation of demolding ribs, making the surface of the blade 21 a smooth surface, reducing the separation phenomenon during the airflow process, improving the work capacity of the centrifugal impeller 10, improving the fan efficiency, and reducing noise.

[0086] In some embodiments of this utility model, such as Figures 11-14 As shown, the volute 20 has an air outlet diffuser section 202, one end of which forms an air outlet 2021. Inside the volute 20, in the direction facing the air outlet 2021, at least one of the opposite side walls of the air outlet diffuser section 202 in the axial direction of the centrifugal impeller 10 is inclined outward. For example, in Figures 11-14 In the example shown, in the direction of the air outlet 2021 inside the volute 20, the two opposite side walls of the air outlet diffuser section 202 along the axial direction of the centrifugal impeller 10 are inclined towards the outside of the volute 20, that is, the two opposite side walls of the air outlet diffuser section 202 along the axial direction of the centrifugal impeller 10 are inclined in a direction away from each other.

[0087] This can improve the static pressure efficiency of the centrifugal fan 100, optimize the airflow direction, reduce airflow loss, reduce noise, and improve operational stability.

[0088] In some embodiments of this utility model, such as Figure 13 and Figure 14As shown, the volute 20 has a volute tongue 203, and the area of ​​the volute tongue 203 opposite to the annular frame 3 has a recess 2031 that is recessed towards the outside of the volute 20. The annular frame 3 protrudes further outward toward the centrifugal impeller 10 relative to the blades 21. When the recess 2031 is not provided on the volute tongue 203, the distance between the annular frame 3 and other areas of the centrifugal impeller 10 is closer to the volute tongue 203. Providing the recess 2031 on the volute tongue 203 at the position opposite to the annular frame 3 can increase the distance between the annular frame 3 and the volute tongue 203, preventing the annular frame 3 from colliding with the volute tongue 203 when the centrifugal fan 100 falls, thus preventing damage to the volute 20 and the centrifugal impeller 10. In addition, increasing the gap between the annular frame 3 and the volute tongue 203 can also improve airflow performance and reduce aerodynamic noise.

[0089] The following describes an air conditioning device according to an embodiment of the present invention.

[0090] The air conditioning equipment according to the present utility model includes the centrifugal fan 100 described above.

[0091] According to the air conditioning equipment of this utility model embodiment, by setting the centrifugal fan 100, including the centrifugal impeller 10, one end face of the blade 21 along the axial direction of the centrifugal impeller 10 is connected to the middle plate 1, and the tail edge 212 of the other end is connected to the inner peripheral wall of the annular frame 3. In the direction from the annular frame 3 to the middle plate 1, the distance between the tail edge 212 of the blade 21 and the axis of the centrifugal impeller 10 gradually decreases. This allows the changing trend of the tail edge 212 of the blade 21 to adapt to the draft angle of the mold, reserving space for the inward shrinkage due to drafting. This allows the areas of both surfaces of the blade 21 in the thickness direction to fit with the mold, thereby avoiding the generation of demolding ribs, making the surface of the blade 21 a smooth surface, reducing the separation phenomenon during airflow, improving the work capacity of the centrifugal impeller 10, improving the fan efficiency, and reducing noise.

[0092] Other components and operations of the air conditioning equipment according to the embodiments of this utility model are known to those skilled in the art and will not be described in detail here.

[0093] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0094] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A centrifugal impeller, characterized in that, The centrifugal impeller is a single piece and includes: Mid-game; A blade assembly is disposed on one side of the central disk along the axial direction of the centrifugal impeller. The blade assembly includes a plurality of blades spaced apart along the circumferential direction of the centrifugal impeller. The end face of one end of the blade along the axial direction of the centrifugal impeller is connected to the central disk. An annular frame is provided, which is spaced apart from the central disk along the axial direction of the centrifugal impeller. The trailing edge of the blade at the end opposite to the central disk is connected to the inner peripheral wall of the annular frame. In the direction from the annular frame to the central disk, the distance between the trailing edge of the blade and the axis of the centrifugal impeller gradually decreases.

2. The centrifugal impeller according to claim 1, characterized in that, The two sides of the blade in the thickness direction are the suction surface and the pressure surface, respectively. The leading edge of the blade extends obliquely toward the suction surface. The suction surface has a rounded corner at the connection with the inner peripheral wall of the annular frame.

3. The centrifugal impeller according to claim 2, characterized in that, The minimum distance between the rounded corner surface and the axis of the centrifugal impeller is D2. Along the axial direction of the centrifugal impeller, the distance between the area outside the connection region between the trailing edge of the blade and the annular frame and the axis of the centrifugal impeller is D3, and D3 < D2.

4. The centrifugal impeller according to claim 1, characterized in that, The blade has a non-uniform thickness structure in the direction from the trailing edge to the leading edge of the blade.

5. The centrifugal impeller according to claim 4, characterized in that, In the direction from the trailing edge to the leading edge of the blade, the thickness of the blade first gradually increases and then gradually decreases.

6. The centrifugal impeller according to claim 5, characterized in that, On a cross-section perpendicular to the axial direction of the centrifugal impeller, the blade has a central arc that divides the blade thickness equally. The diameter of the circle whose center is located on the central arc and is inscribed in the two surfaces of the blade thickness direction is the thickness of the blade at the point of tangency. The center of the inscribed circle at the maximum thickness position of the blade is K. The center point of the leading edge of the blade is E, and the center point of the trailing edge of the blade is F, and 0.3≤EK / FK≤0.6 is satisfied.

7. The centrifugal impeller according to claim 5, characterized in that, The maximum thickness of the blade is Wmax, and the minimum thickness of the blade is Wmin, and the following condition is met: 0.3≤Wmin / Wmax≤0.

6.

8. The centrifugal impeller according to claim 5, characterized in that, The minimum thickness of the blade is located at the trailing edge of the blade.

9. The centrifugal impeller according to claim 1, characterized in that, On a cross-section perpendicular to the axial direction of the centrifugal impeller, the blade has a central arc that divides the blade thickness equally. The angle between the tangents at both ends of the central arc is the airflow turning angle θ, and satisfies: 94°≤θ≤110°.

10. The centrifugal impeller according to any one of claims 1-9, characterized in that, The blade assembly consists of two sets, located on both sides of the central disk along the axial direction of the centrifugal impeller. There are two annular frames, located on both sides of the central disk along the axial direction of the centrifugal impeller and connected to the two sets of blade assemblies in a one-to-one correspondence.

11. A centrifugal fan, characterized in that, include: Snail shell; The centrifugal impeller according to any one of claims 1-10 is disposed within the volute.

12. The centrifugal fan according to claim 11, characterized in that, The volute has an air outlet diffuser section, one end of which forms an air outlet. In the direction toward the air outlet, at least one of the two side walls of the air outlet diffuser section that are opposite each other along the axial direction of the centrifugal impeller are inclined outward.

13. The centrifugal fan according to claim 11, characterized in that, The volute has a volute tongue, and the area of ​​the volute tongue opposite to the annular frame has a recess that is recessed toward the outside of the volute.

14. An air conditioning device, characterized in that, Includes the centrifugal fan according to any one of claims 11-13.

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