Centrifugal fan wheel, centrifugal fan and air conditioning equipment
By designing a centrifugal impeller with gradually increasing blade chord length, the problem of insufficient work capacity of traditional impellers has been solved, achieving air conditioning equipment performance with larger air volume, lower noise, and higher efficiency.
Patent Information
- Application Number
- CN202521770839.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-08-19
- Publication Date
- 2026-08-25
- Estimated Expiration
- 2035-08-19
AI Technical Summary
Traditional centrifugal impellers have poor working capacity, resulting in low fan efficiency, high noise, and negatively impacting the sound quality of air conditioning equipment and user experience.
Design a centrifugal impeller where the chord length of the blades gradually increases from the annular frame to the central plate. Optimize the connection between the blades and the annular frame and the central plate to reduce the influence of the mold draft angle on the blades and improve the smoothness of the blade surface.
It delivers a larger air volume under the same noise level, reduces noise, improves the comfort and sound quality of air conditioning equipment, increases work efficiency, and reduces the power consumption of the fan system.
Smart Images
Figure CN224679747U_ABST
Abstract
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] Centrifugal fans are commonly used in indoor air conditioning equipment due to their high efficiency and large air volume. As the core moving component, the performance of the centrifugal impeller determines the fan's overall performance and noise level. Traditional centrifugal impellers have poor work capacity, resulting in low fan efficiency and high noise levels, which in turn affects the product's sound quality and the user experience. Utility Model Content
[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a centrifugal impeller with high work capacity, high efficiency, and 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] A centrifugal impeller according to an embodiment of the present invention includes: a central disk; a blade assembly 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; an annular frame spaced apart from the central disk along the axial direction of the centrifugal impeller, the trailing edge of the blade opposite to the central disk being connected to the inner circumferential wall of the annular frame, and on a cross-section perpendicular to the axial direction of the centrifugal impeller, the line connecting the center of the leading edge of the blade and the center of the trailing edge of the blade is a chord length, and the chord length of the blade gradually increases in the direction from the annular frame to the central disk.
[0007] According to the centrifugal impeller of this utility model embodiment, by gradually increasing the chord length of the blades in the direction from the annular frame to the central plate, the centrifugal impeller can deliver a larger air volume under the same noise level, meeting the air conditioning needs of larger spaces. Under the same air volume, it has lower noise, improving the comfort and sound quality of air conditioning equipment using this centrifugal impeller, and has higher work capacity and higher work efficiency for the same air volume, reducing the power of the fan system.
[0008] According to some embodiments of the present invention, the chord length of the blade away from the end of the central plate is b1, and satisfies: 13mm≤b1≤15.5mm; and / or, the chord length of the blade away from the end of the annular frame is b2, and satisfies: 14mm≤b2≤16.5mm.
[0009] According to some embodiments of this utility model, in the direction from the annular frame to the central plate, the ratio γ of the distance L1 between a point on the same straight line as the leading edge of the blade and the axis of the centrifugal impeller and the distance L2 between a point on the same straight line as the trailing edge of the blade and the axis of the centrifugal impeller gradually decreases.
[0010] In some embodiments of this utility model, the diameter ratio of the end of the blade away from the central plate is γ1, and satisfies: 0.78≤γ1≤0.85; and / or, the diameter ratio of the end of the blade away from the annular frame is γ2, and satisfies: 0.75≤γ2≤0.85mm.
[0011] According to some embodiments of the present invention, 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.
[0012] 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.
[0013] 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.
[0014] According to the centrifugal fan of this utility model embodiment, by setting the centrifugal impeller as described above, the chord length of the blades gradually increases in the direction from the annular frame to the central plate. Under the same noise level, the centrifugal impeller can deliver a larger air volume, which can meet the air conditioning needs of larger spaces. Under the same air volume, it has lower noise, improves the comfort and sound quality of the air conditioning equipment using the centrifugal impeller, and has higher work capacity and higher work efficiency for the same air volume, reducing the power of the fan system.
[0015] 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.
[0016] 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.
[0017] The air conditioning equipment according to the present invention includes the centrifugal fan described above.
[0018] According to the embodiment of the present invention, the air conditioning equipment, by setting the centrifugal fan as described above, including the centrifugal impeller, gradually increases the chord length of the blades in the direction from the annular frame to the central plate. Under the same noise level, the centrifugal impeller can deliver a larger air volume, satisfying the air conditioning needs of larger spaces. Under the same air volume, it has lower noise, improving the comfort and sound quality of the air conditioning equipment using the centrifugal impeller. It also has higher work capacity and higher work efficiency for the same air volume, reducing the power of the fan system.
[0019] 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
[0020] 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:
[0021] Figure 1 This is a perspective view of the centrifugal impeller according to an embodiment of the present utility model;
[0022] Figure 2 This is a top view of a centrifugal fan according to an embodiment of the present utility model;
[0023] Figure 3 This is a front view of a centrifugal fan according to an embodiment of the present utility model;
[0024] Figure 4 It is along Figure 3 Sectional view of line AA in the middle;
[0025] Figure 5 This is a schematic diagram of a centrifugal impeller according to an embodiment of the present invention, wherein only one blade is shown;
[0026] Figure 6 yes Figure 5 Enlarged view of point B in the middle;
[0027] Figure 7 This is a top view of the blades of a centrifugal impeller according to an embodiment of the present utility model;
[0028] Figure 8 This is a front view of the blades of a centrifugal impeller according to an embodiment of the present utility model;
[0029] Figure 9 This is a perspective view of a centrifugal fan according to an embodiment of the present utility model;
[0030] Figure 10 This is a front view of a centrifugal fan according to an embodiment of the present utility model;
[0031] Figure 11 This is a top view of a centrifugal fan according to an embodiment of the present utility model;
[0032] Figure 12 It is along Figure 11 A cross-sectional view of the CC line.
[0033] Figure label:
[0034] 100. Centrifugal fan;
[0035] 10. Centrifugal fan;
[0036] 1. Mid-game;
[0037] 2. Leaf group; 21. Leaf blade; 211. Leading edge; 212. Tail edge; 216. Leaf apex; 217. Leaf root;
[0038] 3. Circular border;
[0039] 20. Snail shell;
[0040] 201. Main body section; 2011. Air inlet; 202. Air outlet diffuser section; 2021. Air outlet; 203. Volute tongue; 2031. Recessed part. Detailed Implementation
[0041] 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.
[0042] 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.
[0043] 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.
[0044] The centrifugal impeller 10 according to an embodiment of the present invention is described below with reference to the accompanying drawings.
[0045] like Figures 1-4 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.
[0046] Specifically, the centrifugal impeller 10 can be 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.
[0047] like Figure 1 and Figure 2 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.
[0048] like Figures 1-4As 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.
[0049] like Figures 1-3 As shown, the annular frame 3 and the central disk 1 are spaced apart along the axial direction of the centrifugal impeller 10, and the trailing edge 212 of the blade 21 at the end opposite to 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 along the radial direction is the leading edge 211, and the end of the blade 21 further away from the axis of the centrifugal impeller 10 along the radial 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 of the annular frame 3. This not only fixes the blade 21 through the annular frame 3, but also prevents the annular frame 3 from blocking the mold used to form multiple blades 21 in the center of the centrifugal impeller 10 during injection molding. This facilitates the demolding of the mold used to form multiple blades 21 in the center of the centrifugal impeller 10 from the inner space of the annular frame 3, thus facilitating the injection molding process of the centrifugal impeller 10.
[0050] In addition, such as Figures 5-8 As shown, in the cross-section of blade 21 perpendicular to the axial direction of centrifugal impeller 10, the line connecting the center of the leading edge 211 of blade 21 and the center of the trailing edge 212 of blade 21 is the chord length b. The chord length b of blade 21 gradually increases in the direction from the annular frame 3 to the central disk 1. The end of blade 21 connected to the central disk 1 is the blade root 217, and the end of blade 21 connected to the annular frame 3 is the blade tip 216. That is, the chord length of blade 21 gradually increases in the direction from the blade tip 216 to the blade root 217.
[0051] Therefore, under the same noise level, the centrifugal impeller 10 can deliver a larger air volume, meeting the air conditioning needs of larger spaces. Under the same air volume, it has lower noise, improving the comfort and sound quality of air conditioning equipment using the centrifugal impeller 10. It also has higher work capacity and higher work efficiency for the same air volume, reducing the power of the fan system.
[0052] According to the centrifugal impeller 10 of this utility model embodiment, by gradually increasing the chord length of the blades 21 in the direction from the annular frame 3 to the central plate 1, the centrifugal impeller 10 can deliver a larger air volume under the same noise level, satisfying the air conditioning needs of larger spaces. Under the same air volume, it has lower noise, improving the comfort and sound quality of air conditioning equipment using the centrifugal impeller 10, and has higher work capacity and higher work efficiency for the same air volume, reducing the power of the fan system.
[0053] In some embodiments of this utility model, such as Figure 5 and Figure 6 As shown, the chord length of the end of blade 21 facing away from the central disk 1 is b1, and satisfies: 13mm ≤ b1 ≤ 15.5mm, that is, the chord length of the blade tip 216 is b1, and satisfies: 13mm ≤ b1 ≤ 15.5mm. For example, the chord length b1 of the end of blade 21 facing away from the central disk 1, i.e., the blade tip 216, can be 13mm, 13.3mm, 13.5mm, 13.7mm, 14mm, 14.3mm, 14.5mm, 14.7mm, 15mm, 15.3mm, or 15.5mm, etc. This allows the centrifugal impeller 10 to achieve better results in both increasing air volume and reducing noise, improving the work capacity of the centrifugal impeller 10, increasing the efficiency of the centrifugal fan 100, and simultaneously reducing noise.
[0054] In some embodiments of this utility model, such as Figure 5 and Figure 6 As shown, the chord length of the end of blade 21 facing away from the annular frame 3 is b2, and satisfies: 14mm ≤ b2 ≤ 16.5mm. That is, the chord length of blade root 217 is b2, and satisfies: 14mm ≤ b2 ≤ 16.5mm. For example, the chord length b2 of the end of blade 21 facing away from the annular frame 3, i.e., blade root 217, can be 14mm, 14.3mm, 14.5mm, 14.7mm, 15mm, 15.3mm, 15.5mm, 15.7mm, 16mm, 16.3mm, or 16.5mm, etc. This allows the centrifugal impeller 10 to achieve better results in both increasing airflow and reducing noise, improving the work capacity of the centrifugal impeller 10, increasing the efficiency of the centrifugal fan 100, and simultaneously reducing noise.
[0055] In a specific example of this utility model, the chord length b1 of the blade 21 at the end away from the central plate 1, i.e., the blade tip 216, can be 14 mm, and the chord length b2 of the blade 21 at the end away from the annular frame 3, i.e., the blade root 217, can be 15.1 mm. The chord length of the blade 21 at the blade tip 216 is less than the chord length of the blade 21 at the blade root 217.
[0056] In some embodiments of this utility model, such as Figure 4As shown, in the direction from the annular frame 3 to the central disk 1, the ratio γ of the distance L1 between a point on the same straight line as the leading edge 211 of blade 21 and the axis of centrifugal impeller 10 and the distance L2 between a point on the same straight line as the trailing edge 212 of blade 21 and the axis of centrifugal impeller 10 gradually decreases. It can be understood that in a cross-section perpendicular to the axial direction of centrifugal impeller 10, the leading edge 211 of blade 21 has a leading edge point, the distance between the leading edge point and the axis of centrifugal impeller 10 is L1, and the trailing edge 212 of blade 21 has a trailing edge point, the distance between the trailing edge point and the axis of centrifugal impeller 10 is L2, and the wheel diameter ratio is γ, where γ = L1 / L2. In the direction from the annular frame 3 to the central disk 1, the wheel diameter ratio γ gradually decreases, and multiple leading edge points and multiple trailing edge points are located on the same straight line.
[0057] For example, on a cross-section perpendicular to the axial direction of the centrifugal impeller 10, the point where the distance between the leading edge 211 of the blade 21 and the axis of the centrifugal impeller 10 is minimized can be defined as the leading edge point, and the point where the distance between the trailing edge 212 of the blade 21 and the axis of the centrifugal impeller 10 is maximized can be defined as the trailing edge point. The distance between the leading edge point and the axis of the centrifugal impeller 10 is L1, and the distance between the trailing edge point and the axis of the centrifugal impeller 10 is L2. The wheel diameter ratio is γ, where γ = L1 / L2. In the direction from the annular frame 3 to the middle disk 1, the wheel diameter ratio γ gradually decreases. It can be understood that in the direction from the annular frame 3 to the middle disk 1, when the maximum distance between the trailing edge 212 of the blade 21 and the axis of the centrifugal impeller 10 remains constant, the minimum distance between the leading edge 211 of the blade 21 and the axis of the centrifugal impeller 10 gradually decreases, and the chord length of the blade 21 gradually increases.
[0058] Therefore, under the same noise level, the centrifugal impeller 10 can deliver a larger air volume, meeting the air conditioning needs of larger spaces. Under the same air volume, it has lower noise, improving the comfort and sound quality of air conditioning equipment using the centrifugal impeller 10. It also has higher work capacity and higher work efficiency for the same air volume, reducing the power of the fan system.
[0059] In some embodiments of this utility model, the diameter ratio of the end of the blade 21 facing away from the central disk 1 is γ1, and satisfies: 0.78≤γ1≤0.85. For example, the diameter ratio γ1 of the end of the blade 21 facing away from the central disk 1 can be 0.79, 0.8, 0.81, 0.82, 0.83, 0.84, or 0.85. This allows the centrifugal impeller 10 to achieve better results in both increasing airflow and reducing noise, improving the work capacity of the centrifugal impeller 10, increasing the efficiency of the centrifugal fan 100, and simultaneously reducing noise.
[0060] In some embodiments of this utility model, the diameter ratio of the end of the blade 21 facing away from the annular frame 3 is γ2, and satisfies: 0.75≤γ2≤0.85mm. For example, the diameter γ2 of the end of the blade 21 facing away from the annular frame 3 can be 0.75, 0.76, 0.77, 0.78, 0.79, 0.8, 0.81, 0.82, 0.83, 0.84, or 0.85, etc. This allows the centrifugal impeller 10 to achieve better results in both increasing air volume and reducing noise, improving the work capacity of the centrifugal impeller 10, increasing the efficiency of the centrifugal fan 100, and simultaneously reducing noise.
[0061] In a specific example of this utility model, the wheel diameter ratio γ1 of the end of the blade 21 facing away from the central disk 1 is 0.834, and the wheel diameter ratio γ2 of the end of the blade 21 facing away from the annular frame 3 is 0.813.
[0062] 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.
[0063] It should be noted that the outer diameter of blade 21 is twice the maximum distance between the outermost contour of blade 21, i.e., the trailing edge 212 of blade 21, and the axis of centrifugal impeller 10.
[0064] In some embodiments of this utility model, in the direction from the annular frame 3 to the middle 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 middle 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 position 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 due to drafting, so that the areas of both surfaces of the blade 21 in the thickness direction can fit with the mold, thereby avoiding the formation of demolding ribs, making the surface of the blade 21 a smooth surface, reducing separation during airflow, improving the work capacity of the centrifugal impeller 10, improving the efficiency of the centrifugal fan 100, and reducing noise.
[0065] 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.
[0066] In some embodiments of this utility model, such as Figure 1 and Figure 3 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.
[0067] 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.
[0068] The following is for reference. Figures 9-12 A centrifugal fan 100 according to an embodiment of the present utility model is described.
[0069] like Figures 9-12 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.
[0070] 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.
[0071] 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.
[0072] 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.
[0073] According to the centrifugal fan 100 of this utility model embodiment, by setting the centrifugal impeller 10 as described above, the chord length of the blades 21 gradually increases in the direction from the annular frame 3 to the central plate 1. Under the same noise level, the centrifugal impeller 10 can deliver a larger air volume, which can meet the air conditioning needs of larger spaces. Under the same air volume, it has lower noise, improves the comfort and sound quality of the air conditioning equipment using the centrifugal impeller 10, and has higher work capacity and higher work efficiency for the same air volume, reducing the power of the fan system.
[0074] In some embodiments of this utility model, such as Figures 9-12 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 9-12 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.
[0075] 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.
[0076] In some embodiments of this utility model, such as Figure 11 and Figure 12As 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.
[0077] The following describes an air conditioning device according to an embodiment of the present invention.
[0078] The air conditioning equipment according to the present utility model includes the centrifugal fan 100 described above.
[0079] According to the embodiment of the present invention, the air conditioning equipment, by setting the centrifugal fan 100, including the centrifugal impeller 10, in the direction from the annular frame 3 to the central plate 1, makes the chord length of the blades 21 gradually increase. Under the same noise, the centrifugal impeller 10 can deliver a larger air volume, which can meet the air conditioning needs of a larger space. Under the same air volume, it has lower noise, improves the comfort and sound quality of the air conditioning equipment using the centrifugal impeller 10, and has higher work capacity and higher work efficiency for the same air volume, reducing the power of the fan system.
[0080] 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.
[0081] 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.
[0082] 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, include: Mid-game; A blade assembly is provided 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. On the cross-section of the blade in the direction perpendicular to the axial direction of the centrifugal impeller, the line connecting the center of the leading edge of the blade and the center of the trailing edge of the blade is the chord length, and the chord length of the blade gradually increases in the direction from the annular frame to the central disk.
2. The centrifugal impeller according to claim 1, characterized in that, The chord length of the blade opposite to the middle disk is b1, and satisfies: 13mm≤b1≤15.5mm; And / or, the chord length of the blade away from the annular frame is b2, and satisfies: 14mm≤b2≤16.5mm.
3. The centrifugal impeller according to claim 1, characterized in that, In the direction from the annular frame to the central disk, the ratio γ of the distance L1 between a point on the same straight line as the leading edge of the blade and the axis of the centrifugal impeller and the distance L2 between a point on the same straight line as the trailing edge of the blade and the axis of the centrifugal impeller gradually decreases.
4. The centrifugal impeller according to claim 3, characterized in that, The diameter ratio of the end of the blade away from the central disk is γ1, and satisfies: 0.78≤γ1≤0.85; And / or, the diameter ratio of the blade at the end opposite to the annular frame is γ2, and satisfies: 0.75≤γ2≤0.85mm.
5. The centrifugal impeller according to claim 1, characterized in that, 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.
6. The centrifugal impeller according to any one of claims 1-5, 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.
7. A centrifugal fan, characterized in that, include: Snail shell; The centrifugal impeller according to any one of claims 1-6, wherein the centrifugal impeller is disposed within the volute.
8. The centrifugal fan according to claim 7, 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 opposing side walls of the air outlet diffuser section is inclined outward along the axial direction of the centrifugal impeller.
9. The centrifugal fan according to claim 7, 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.
10. An air conditioning device, characterized in that, Includes the centrifugal fan according to any one of claims 7-9.