Centrifugal wind wheel and air conditioner indoor unit with same

Abstract

The utility model relates to the technical field of air conditioners, in particular to a centrifugal wind wheel and an air conditioner indoor unit with the same. The centrifugal wind wheel aims at solving the problem that an existing centrifugal wind wheel is low in efficiency. Therefore, the inlet edge of any blade is in a winding shape and is in phase difference distribution on the circumference of the centrifugal wind wheel, the outlet edge of any blade is in an arc shape sunken towards the inner side of the centrifugal wind wheel and is also in phase difference distribution on the circumference of the centrifugal wind wheel, and the phase difference of the inlet edge changes the air flowing characteristic at the inlet of the blade; in addition, the phase difference of the inlet edge and the phase difference of the outlet edge are jointly in space, the space distance of airflow of the high kinetic energy outlet and the space distance of airflow of the low kinetic energy outlet are increased, and the efficiency of the centrifugal impeller is improved. And therefore, flow field mixing of blade outlets is inhibited, and the efficiency of the centrifugal wind wheel is further improved. According to the utility model, the technical problems are solved.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning technology, and in particular to a centrifugal impeller and an indoor air conditioning unit having thereon. Background Technology

[0002] With the advancement of modernization, centrifugal wind turbines are being used more and more widely. To achieve energy conservation and emission reduction, various application fields are placing increasing emphasis on improving the efficiency of centrifugal wind turbines. Among these components, the blades are a key part of the centrifugal wind turbine and directly impact its efficiency.

[0003] However, in current technology, due to the influence of the blade structure, the airflow is constrained by the blade as it flows from the inlet edge to the outlet edge of the blade. The kinetic energy of the airflow is dissipated in the form of internal energy and sound pressure, which makes it difficult to further improve the efficiency of centrifugal wind turbines in related technologies. Utility Model Content

[0004] The first aspect of this utility model is to provide a centrifugal impeller with significantly improved efficiency.

[0005] The second aspect of this utility model is to provide an air conditioning indoor unit having the aforementioned centrifugal impeller.

[0006] Specifically, this utility model provides a centrifugal impeller, comprising a disc and a plurality of blades arranged circumferentially along the disc, wherein,

[0007] The inlet edge of any of the blades is meandering, and the outlet edge is an arc shape that is concave towards the inside of the centrifugal impeller.

[0008] Optionally, the inlet edge of the blade includes a first bend, a second bend, and a third bend that are connected sequentially from the end away from the wheel to the end connected to the wheel.

[0009] Optionally, the height of the first bent section on the centrifugal impeller's rotation axis is h1, the height of the second bent section on the centrifugal impeller's rotation axis is h2, the height of the third bent section on the centrifugal impeller's rotation axis is h3, and the height of the blade inlet edge on the centrifugal impeller's rotation axis is H, wherein...

[0010] 0.05H≤h1≤0.15H, 0.35H≤h2≤0.5H, 0.35H≤h2≤0.6H.

[0011] Optionally, h1:h2:h3 = 0.5-1.5:4.5-5.5:3.5-4.5.

[0012] Optionally, the angle between the first bent section and the rotation axis of the centrifugal impeller is θ1, where 65°≤θ1≤90°; and / or,

[0013] The angle between the second bent section and the rotation axis of the centrifugal impeller is θ2, where 10°≤θ2≤40°; and / or,

[0014] The angle between the third bending section and the rotation axis of the centrifugal impeller is θ3, where 0°≤θ3≤30°.

[0015] Optionally, the angle between one end of the blade outlet edge and the rotation axis of the centrifugal impeller is α1, where 30°≤α1≤85°; and / or,

[0016] The angle between the other end of the blade outlet edge and the rotation axis of the centrifugal impeller is α2, where 150°≤α2≤180°.

[0017] Optionally, the angle between the line connecting the two ends of the blade outlet edge and the rotation axis of the centrifugal impeller is β, wherein,

[0018] 0°≤β≤40°.

[0019] Optionally, the blade includes a suction surface and a pressure surface, the suction surface and the pressure surface are independently processed and formed, and the blade is formed by splicing the suction surface and the pressure surface together in a relatively fixed manner.

[0020] Optionally, the wheel is provided with a plurality of first blade slots along its circumference for inserting one end of the blade; and

[0021] The centrifugal impeller also includes a wheel cover disposed opposite to the impeller disc. The wheel cover is provided with a plurality of second blade slots along the circumference for the other end of the blade to be inserted. The first blade slot and the second blade slot are opposite to each other.

[0022] According to another aspect of the present invention, an air conditioning indoor unit is also provided, which includes a centrifugal fan as described in any of the preceding claims.

[0023] The centrifugal impeller proposed in this invention includes a disc and multiple blades arranged circumferentially along the disc. The inlet edge of any blade is meandering and exhibits a phase difference distribution on the circumference of the centrifugal impeller, while the outlet edge is an arc-shaped concave shape facing inward towards the centrifugal impeller, also exhibiting a phase difference distribution on the circumference of the centrifugal impeller. The phase difference of the inlet edge changes the airflow characteristics at the blade inlet, suppressing negative impacts such as pressure loss, impact loss, eddies, and noise, and synergistically optimizing the phase state of the flow within the blade passage, changing local pressure accumulation and kinetic energy mixing, thereby optimizing the entire power transmission process and improving the efficiency of the centrifugal impeller. In addition, the phase difference of the inlet edge and the phase difference of the outlet edge together spatially increase the spatial distance between the high and low kinetic energy outlet airflows, thereby suppressing the formation of flow field mixing at the blade outlet, reducing the dissipation of kinetic energy during mixing, and further improving the efficiency of the centrifugal impeller.

[0024] Furthermore, the inlet edge of the blade includes a first bend, a second bend, and a third bend that are sequentially connected from the end furthest from the rotor to the end connected to the rotor. The blade inlet edge is composed of three sections, which improves the efficiency of the centrifugal wind turbine while reducing the processing cost.

[0025] Furthermore, the height of the first bend section on the centrifugal impeller's rotation axis is h1, the height of the second bend section on the centrifugal impeller's rotation axis is h2, the height of the third bend section on the centrifugal impeller's rotation axis is h3, and the height of the blade inlet edge on the centrifugal impeller's rotation axis is H. By ensuring 0.05H≤h1≤0.15H, 0.35H≤h2≤0.5H, and 0.35H≤h3≤0.6H, the ratio of h1:h2:h3 = 0.5-1.5:4.5-5.5:3.5-4.5. The angle between the first bend and the centrifugal impeller's rotation axis is θ1, 65°≤θ1≤90°; and / or, the angle between the second bend and the centrifugal impeller's rotation axis is θ2, 10°≤θ2≤40°; and / or, the angle between the third bend and the centrifugal impeller's rotation axis is θ3, 0°≤θ3≤30°. This allows for precise control of the phase difference distribution at the blade inlet edge, resulting in better suppression of negative effects such as pressure loss, impact loss, eddies, and noise, ensuring the reliability of efficiency improvement. Simultaneously, because a phase difference is formed at the inlet edge according to this ratio, the flow within the blade passage will inevitably form a corresponding phase difference relationship. The airflow within the blade passage is optimized in phase state due to the phase difference, thereby optimizing the entire work process and improving the centrifugal impeller's efficiency.

[0026] Furthermore, the angle between one end of the blade outlet edge and the centrifugal impeller rotation axis is α1, where 30°≤α1≤85°; and / or, the angle between the other end of the blade outlet edge and the centrifugal impeller rotation axis is α2, where 150°≤α2≤180°, and the angle between the line connecting the two ends of the blade outlet edge and the centrifugal impeller rotation axis is β, where 0°≤β≤40°. This allows for accurate control of the phase difference distribution at the blade outlet edge, which, together with the phase difference at the inlet edge, acts spatially to widen the spatial distance between the high and low kinetic energy outlet airflows. This suppresses the mixing of the flow field at the blade outlet, thereby reducing the dissipation of kinetic energy during mixing and further improving the efficiency of the centrifugal impeller.

[0027] Furthermore, since the pressure surface and suction surface are two independent structures, and the blade is formed by relatively fixed splicing of the suction surface and the pressure surface, different structural designs can be adopted in various places. The pressure surface and suction surface that make up the blade can adopt different shapes, which can realize more structural possibilities according to design needs. In addition, the blade uses less material, saving material costs.

[0028] Furthermore, the impeller is provided with multiple first blade slots along its circumference for inserting one end of the blade; and the centrifugal impeller also includes a wheel cover disposed opposite to the impeller, the wheel cover being provided with multiple second blade slots along its circumference for inserting the other end of the blade, the first blade slots and the second blade slots being opposite each other, wherein the impeller impeller, wheel cover and blades are separated, reducing the mold cost of the impeller impeller and wheel cover.

[0029] The above description is merely an overview of the technical solution of this utility model. In order to better understand the technical means of this utility model and to implement it in accordance with the contents of the specification, and to make the above and other objects, features and advantages of this utility model more obvious and understandable, specific embodiments of this utility model are given below.

[0030] The above and other objects, advantages and features of this utility model will become more apparent to those skilled in the art from the following detailed description of specific embodiments of this utility model in conjunction with the accompanying drawings. Attached Figure Description

[0031] The following sections will describe some specific embodiments of the present invention in a detailed manner by way of example and not limitation, with reference to the accompanying drawings. The same reference numerals in the drawings denote the same or similar parts or components. Those skilled in the art should understand that these drawings are not necessarily drawn to scale. In the drawings:

[0032] Figure 1 This is a schematic diagram of the overall structure of a centrifugal impeller according to an embodiment of the present invention;

[0033] Figure 2 This is a schematic diagram of the overall structure of a centrifugal impeller according to an embodiment of the present invention;

[0034] Figure 3 yes Figure 1 and Figure 2 The diagram shown is a schematic of the centrifugal fan after the wheel cover has been removed.

[0035] Figure 4 yes Figure 3 A schematic diagram of the inlet side of the centrifugal impeller blades shown;

[0036] Figure 5 yes Figure 3 A schematic diagram of the outlet edge of the centrifugal impeller blades shown;

[0037] Figure 6 yes Figure 1 and Figure 2 A schematic diagram of the wheel cover of the centrifugal impeller shown;

[0038] Figure 7 This is a schematic structural block diagram of an air conditioner indoor unit according to an embodiment of the present utility model.

[0039] Explanation of reference numerals in the attached figures:

[0040] 10. Centrifugal fan;

[0041] 110. Wheel; 111. First blade slot;

[0042] 120. Blade; 121. Inlet edge; 1211. First bend section; 1212. Second bend section; 1213. Third bend section; 122. Outlet edge; 123. Suction surface; 124. Pressure surface;

[0043] 130. Wheel cover; 131. Second blade slot;

[0044] 1. Indoor unit of air conditioner. Detailed Implementation

[0045] The following reference Figures 1 to 7 The present invention describes a centrifugal fan 10 and an indoor air conditioning unit 1 having thereon, according to embodiments of the present invention.

[0046] The terms "top," "upper," and "inner," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this 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. Therefore, they should not be construed as limitations on this utility model.

[0047] The terms "first," "second," and "third," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first," "second," or "third" may explicitly or implicitly include at least one of that feature, that is, include one or more of that feature.

[0048] In the description of this utility model, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified. When a feature "includes or contains" one or more of the features it covers, unless otherwise specifically described, this indicates that other features are not excluded and may be further included.

[0049] In the description of this embodiment, the reference to terms such as "some embodiments," "specific embodiments," etc., means that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments.

[0050] Unless otherwise specified, all terms (including technical and scientific terms) used in the description of the embodiments of this utility model shall have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains.

[0051] Figure 1 This is a schematic diagram of the overall structure of the centrifugal impeller 10 according to an embodiment of the present utility model;

[0052] Figure 2 This is a schematic diagram of the overall structure of the centrifugal impeller 10 according to an embodiment of the present utility model;

[0053] Figure 3 yes Figure 1 and Figure 2 The diagram shows the centrifugal impeller 10 after the wheel cover 130 has been removed.

[0054] See Figure 1-3 As shown, this utility model proposes a centrifugal impeller 10, which includes a disc 110, a plurality of blades 120 arranged circumferentially along the disc 110, and a wheel cover 130 disposed on the top of the plurality of blades 120 opposite to the disc 110. The inlet edge 121 of any blade 120 is meandering and zigzag, resembling a lightning bolt, and the outlet edge 122 is an arc-shaped concave towards the inner side of the centrifugal impeller 10, resembling a large C.

[0055] Among them, the inlet side 121 of the blade 120 is the side closer to the wind turbine rotation axis, and the outlet side 122 of the blade 120 is the side farther away from the wind turbine rotation axis.

[0056] The inlet edge 121 of the blade 120 is used to guide air into the wind turbine, and the outlet edge 122 of the blade 120 is used to guide the airflow out.

[0057] In this embodiment of the invention, the inlet edge 121 of any blade 120 is meandering and exhibits a phase difference distribution on the circumference of the centrifugal impeller 10. The outlet edge 122 is an arc-shaped concave shape facing the inner side of the centrifugal impeller 10, also exhibiting a phase difference distribution on the circumference of the centrifugal impeller 10. The phase difference of the inlet edge 121 changes the airflow characteristics at the inlet of the blade 120, forming an airflow angle of attack phase difference, suppressing negative impacts such as pressure loss, impact loss, eddies, and noise, and synergistically optimizing the phase state of the flow in the blade passage, changing local pressure accumulation and kinetic energy mixing, thereby optimizing the entire power process and improving the efficiency of the centrifugal impeller. In addition, the phase difference of the inlet edge 121 and the phase difference of the outlet edge 122 together spatially widen the spatial distance between the high and low kinetic energy outlet airflows, thereby suppressing the flow field mixing at the outlet of the blade 120, thereby reducing the dissipation of kinetic energy during the mixing process and further improving the efficiency of the centrifugal impeller 10.

[0058] Figure 4 yes Figure 3A schematic diagram of the inlet edge 121 of the blades of the centrifugal impeller 10 shown. Figure 4 The straight line between point A and point B is the first bend segment 1211, the straight line between point B and point C is the second bend segment 1212, and the straight line between point C and point D is the third bend segment 1213.

[0059] See Figure 3 and Figure 4 As shown, in some preferred or alternative embodiments of the present invention, the inlet edge 121 of the blade 120 includes a first bent section 1211, a second bent section 1212 and a third bent section 1213 connected sequentially from one end away from the wheel 110 to the end connected to the wheel 110.

[0060] Among them, the first bend segment 1211, the second bend segment 1212 and the third bend segment 1213 are all straight segments.

[0061] It should be noted that the number of bent sections included in the inlet edge 121 of the blade 120 can be determined according to the actual situation, and this utility model does not impose too many restrictions on it.

[0062] Those skilled in the art will understand that the blade inlet edge 121 is composed of three sections, which improves the efficiency of the centrifugal impeller 10 while reducing processing costs.

[0063] See Figure 4 As shown, in some preferred or alternative embodiments of the present invention, the height of the first bent section 1211 on the rotation axis of the centrifugal impeller 10 is h1, the height of the second bent section 1212 on the rotation axis of the centrifugal impeller 10 is h2, the height of the third bent section 1213 on the rotation axis of the centrifugal impeller 10 is h3, and the height of the blade inlet edge 121 on the rotation axis of the centrifugal impeller 10 is H, wherein 0.05H≤h1≤0.15H, 0.35H≤h2≤0.5H, and 0.35H≤h3≤0.6H.

[0064] The height of the first bending segment 1211 can be selected as 0.05H, 0.1H, or 0.15H; the height of the second bending segment 1212 can be selected as 0.35H, 0.4H, or 0.5H; and the height of the third bending segment 1213 can be selected as 0.35H, 0.5H, or 0.6H.

[0065] See also Figure 4 As shown, in some preferred or alternative embodiments according to the present invention, h1:h2:h3 = 0.5-1.5:4.5-5.5:3.5-4.5.

[0066] In one specific embodiment, h1:h2:h3 = 1:5:4.

[0067] See also Figure 4 As shown, in some preferred or alternative embodiments according to the present invention, the angle between the first bent section 1211 and the rotation axis of the centrifugal impeller 10 is θ1, 65°≤θ1≤90°; and / or,

[0068] The angle between the second bending segment 1212 and the rotation axis of the centrifugal impeller 10 is θ2, 10°≤θ2≤40°; and / or,

[0069] The angle between the third bend segment 1213 and the rotation axis of the centrifugal impeller 10 is θ3, where 0°≤θ3≤30°.

[0070] In one specific embodiment, 65°≤θ1≤90°, 10°≤θ2≤40°, and 0°≤θ3≤30°.

[0071] The included angle θ1 of the first bending segment 1211 can be 65°, 85°, or 90°; the included angle θ2 of the second bending segment 1212 can be 10°, 30°, or 40°; and the included angle θ3 of the third bending segment 1213 can be 0°, 15°, or 30°.

[0072] In one specific embodiment, θ1 = 85°, θ2 = 30°, and θ3 = 15°.

[0073] Those skilled in the art will understand that by ensuring 0.05H≤h1≤0.15H, 0.35H≤h2≤0.5H, 0.35H≤h3≤0.6H, h1:h2:h3=0.5-1.5:4.5-5.5:3.5-4.5, 65°≤θ1≤90°; and / or, 10°≤θ2≤40°; and / or, 0°≤θ3≤30°, the phase difference distribution at the blade inlet edge 121 can be accurately controlled, thereby accurately controlling the phase difference of the airflow angle of attack at the inlet edge. This achieves better suppression of negative effects such as pressure loss, impact loss, eddies, and noise, ensuring the reliability of efficiency improvement. Simultaneously, since a phase difference is formed at the inlet edge 121 according to this ratio, the flow within the blade passage will inevitably form a corresponding phase difference relationship. The airflow within the blade passage is optimized by the phase difference, thereby optimizing the entire work process and improving the efficiency of the centrifugal impeller 10.

[0074] Figure 5 yes Figure 3 A schematic diagram of the outlet edge 122 of the centrifugal impeller 10 blades. Figure 5 The straight line between points E and F is the exit edge 122, and points E and F are the two ends of the exit edge 122.

[0075] See Figure 5As shown, in some preferred or alternative embodiments according to the present invention, the angle between one end of the blade outlet edge 122 and the rotation axis of the centrifugal impeller 10 is α1, 30°≤α1≤85°; and / or,

[0076] The angle between the other end of the blade outlet edge 122 and the rotation axis of the centrifugal impeller 10 is α2, where 150°≤α2≤180°.

[0077] Among them, α1 can be selected from 30°, 45°, and 85°, and α2 can be selected from 150°, 175°, and 180°.

[0078] In one specific embodiment, a1 = 45° and a2 = 175°.

[0079] See also Figure 5 As shown, in some preferred or alternative embodiments according to the present invention, the angle between the line connecting the two ends of the blade outlet edge 122 and the rotation axis of the centrifugal impeller 10 is β, where 0°≤β≤40°

[0080] β can be selected as 0°, 25°, or 40°.

[0081] Those skilled in the art will understand that by ensuring 30°≤ɑ1≤85°; and / or 150°≤ɑ2≤180°, 0°≤β≤40°, the phase difference distribution at the blade outlet edge 122 can be accurately controlled. This phase difference, together with the phase difference at the inlet edge 121, acts spatially to widen the spatial distance between the high and low kinetic energy outlet airflows, thereby suppressing the mixing of the flow field at the blade 120 outlet, reducing the dissipation of kinetic energy during mixing, and further improving the efficiency of the centrifugal impeller 10.

[0082] See Figure 3 As shown, in some preferred or alternative embodiments of the present invention, the blade 120 includes a suction surface 123 and a pressure surface 124, which are independently processed and formed, and the blade 120 is formed by relatively fixed splicing the suction surface 123 and the pressure surface 124.

[0083] Among them, the pressure surface 124 refers to the side of the blade 120 where the fluid flow is subjected to pressure, and the suction surface 123 refers to the side of the blade 120 where the fluid flow is subjected to suction.

[0084] As those skilled in the art will understand, since the pressure surface 124 and the suction surface 123 are two independent structures, the pressure surface 124 and the suction surface 123 can adopt different structural designs in different places. The pressure surface 124 and the suction surface 123 that make up the blade 120 can adopt different shapes, which can realize more structural possibilities according to design needs. In addition, the blade 120 uses less material, saving material costs.

[0085] Figure 6 yes Figure 1 and Figure 2 A schematic diagram of the wheel cover 130 of the centrifugal impeller 10 shown.

[0086] See Figure 2 and Figure 6 As shown, in some preferred or alternative embodiments according to the present invention, the wheel 110 is provided with a plurality of first blade slots 111 along the circumference for inserting one end of the blade 120; and

[0087] The centrifugal impeller 10 also includes a wheel cover 130 disposed opposite to the impeller 110. The wheel cover 130 is provided with a plurality of second blade slots 131 for inserting the other end of the blade 120 along the circumferential direction. The first blade slots 111 and the second blade slots 131 are opposite to each other.

[0088] The number of first blade slots 111 and second blade slots 131 is equal to the number of blades. The first blade slots 111 and second blade slots 131 are elongated grooves that are adapted to the two ends of the blades 120 respectively.

[0089] The first blade slot 111 can be used to install and fix one end of the blade 120, and the second blade slot 131 can be used to install and fix the other end of the blade 120. The blade 120 can be placed between the chassis and the wheel cover 130 through the first blade slot 111 and the second blade slot 131, and an air outlet is formed between two adjacent blades 120 to realize the outflow of air.

[0090] Those skilled in the art will understand that separating the wind turbine's disc 110, cover 130, and blades 120 reduces the mold cost of the disc 110 and cover 130.

[0091] Figure 7 This is a schematic structural block diagram of an air conditioner indoor unit 1 according to an embodiment of the present utility model.

[0092] See Figure 7 As shown, based on the same inventive concept, this utility model also proposes an air conditioning indoor unit 1, which includes a centrifugal fan 10 as in any of the above embodiments.

[0093] The indoor unit 1 of the air conditioner can be one of the following: ceiling-mounted indoor unit, wall-mounted indoor unit, or cabinet air conditioner.

[0094] Centrifugal fan 10 is installed in the indoor unit 1 of the air conditioner to quickly and evenly deliver treated air (such as cooling, heating, humidifying, dehumidifying, etc.) to every corner of the room, ensuring uniform distribution of indoor temperature and humidity.

[0095] The centrifugal impeller 10 proposed in this utility model includes a disc 110 and multiple blades 120 arranged circumferentially along the disc 110. The inlet edge 121 of any blade 120 is meandering and exhibits a phase difference distribution on the circumference of the centrifugal impeller 10. The outlet edge 122 is an arc-shaped concave shape facing the inner side of the centrifugal impeller 10, also exhibiting a phase difference distribution on the circumference of the centrifugal impeller 10. The phase difference of the inlet edge 121 changes the airflow characteristics at the inlet of the blade 120, suppressing negative impacts such as pressure loss, impact loss, eddies, and noise, and synergistically optimizing the phase state of the flow in the blade passage, changing local pressure accumulation and kinetic energy mixing, thereby optimizing the entire power process and improving the efficiency of the centrifugal impeller. In addition, the phase difference of the inlet edge 121 and the phase difference of the outlet edge 122 together spatially widen the spatial distance between the high and low kinetic energy outlet airflows, thereby suppressing the flow field mixing at the outlet of the blade 120, reducing the dissipation of kinetic energy during the mixing process, and further improving the efficiency of the centrifugal impeller 10.

[0096] Furthermore, the inlet edge 121 of the blade 120 includes a first bent section 1211, a second bent section 1212, and a third bent section 1213 connected sequentially from the end away from the impeller 110 to the end connected to the impeller 110. The inlet edge 121 of the blade 120 is composed of three sections, which improves the efficiency of the centrifugal impeller 10 while reducing the processing cost.

[0097] Furthermore, the height of the first bent section 1211 on the rotation axis of the centrifugal impeller 10 is h1, the height of the second bent section 1212 on the rotation axis of the centrifugal impeller 10 is h2, the height of the third bent section 1213 on the rotation axis of the centrifugal impeller 10 is h3, and the height of the blade inlet edge 121 on the rotation axis of the centrifugal impeller 10 is H. By ensuring that 0.05H≤h1≤0.15H, 0.35H≤h2≤0.5H, and 0.35H≤h3≤0.6H, the ratio of h1:h2:h3 = 0.5-1.5:4.5-5.5:3.5-4.5 The angle between the first bend section 1211 and the rotation axis of the centrifugal impeller 10 is θ1, 65°≤θ1≤90°; and / or, the angle between the second bend section 1212 and the rotation axis of the centrifugal impeller 10 is θ2, 10°≤θ2≤40°; and / or, the angle between the third bend section 1213 and the rotation axis of the centrifugal impeller 10 is θ3, 0°≤θ3≤30°. This allows for accurate control of the phase difference distribution at the blade inlet edge 121, resulting in better suppression of negative effects such as pressure loss, impact loss, eddies, and noise, ensuring the reliability of efficiency improvement. Simultaneously, because a phase difference is formed at the inlet edge 121 according to this ratio, the flow within the blade passage will also necessarily form a corresponding phase difference relationship. The airflow within the blade passage is optimized in phase state due to the phase difference, thereby optimizing the entire work process and improving the efficiency of the centrifugal impeller 10.

[0098] Furthermore, the angle between one end of the blade outlet edge 122 and the rotation axis of the centrifugal impeller 10 is α1, where 30°≤α1≤85°; and / or, the angle between the other end of the blade outlet edge 122 and the rotation axis of the centrifugal impeller 10 is α2, where 150°≤α2≤180°, and the angle between the line connecting the two ends of the blade outlet edge 122 and the rotation axis of the centrifugal impeller 10 is β, where 0°≤β≤40°. This allows for accurate control of the phase difference distribution at the blade outlet edge 122, which, together with the phase difference at the inlet edge 121, acts spatially to widen the spatial distance between the high and low kinetic energy outlet airflows. This suppresses the mixing of the flow field at the blade 120 outlet, thereby reducing the dissipation of kinetic energy during mixing and further improving the efficiency of the centrifugal impeller 10.

[0099] Furthermore, since the pressure surface 124 and the suction surface 123 are two independent structures, and the blade 120 is formed by relatively fixed splicing of the suction surface 123 and the pressure surface 124, the pressure surface 124 and the suction surface 123 can adopt different structural designs in various places. The pressure surface 124 and the suction surface 123 that make up the blade 120 can adopt different shapes, which can realize more structural possibilities according to design needs. In addition, the blade 120 uses less material, saving material costs.

[0100] Furthermore, the impeller 110 is provided with a plurality of first blade slots 111 for inserting one end of the blade 120 around its circumference; and the centrifugal impeller 10 also includes a wheel cover 130 disposed opposite to the impeller 110, the wheel cover 130 being provided with a plurality of second blade slots 131 for inserting the other end of the blade 120 around its circumference, the first blade slots 111 and the second blade slots 131 being opposite each other, wherein the impeller 110, the wheel cover 130 and the blades are separated, reducing the mold cost of the impeller 110 and the wheel cover 130.

[0101] Therefore, those skilled in the art should recognize that although many exemplary embodiments of the present invention have been shown and described in detail herein, many other variations or modifications conforming to the principles of the present invention can be directly determined or derived from the disclosure of the present invention without departing from the spirit and scope of the present invention. Therefore, the scope of the present invention should be understood and recognized as covering all such other variations or modifications.

Claims

1. A centrifugal fan wheel comprising a wheel disc and a plurality of blades arranged circumferentially along the wheel disc, characterized in that, an inlet edge of any of the blades is in a meandering shape, and an outlet edge of the blade is in an arc shape concave towards an inner side of the centrifugal fan wheel. 2.The centrifugal fan wheel according to claim 1, characterized in that, the inlet edge of the blade comprises a first bending section, a second bending section and a third bending section sequentially connected from an end away from the wheel disc to an end connected with the wheel disc. 3.The centrifugal fan wheel according to claim 2, characterized in that, a height of the first bending section on an axis of rotation of the centrifugal fan wheel is h1, a height of the second bending section on the axis of rotation of the centrifugal fan wheel is h2, a height of the third bending section on the axis of rotation of the centrifugal fan wheel is h3, and a height of the inlet edge of the blade on the axis of rotation of the centrifugal fan wheel is H, wherein, 0.05H≤h1≤0.15H, 0.35H≤h2≤0.5H, 0.35H≤h2≤0.6H. 4.The centrifugal fan wheel according to claim 3, characterized in that, h1:h2:h3=0.5-1.5:4.5-5.5:3.5-4.

5. 5.The centrifugal fan wheel according to claim 2, characterized in that, an angle between the first bending section and the axis of rotation of the centrifugal fan wheel is θ1, and 65°≤θ1≤90°; and / or, an angle between the second bending section and the axis of rotation of the centrifugal fan wheel is θ2, and 10°≤θ2≤40°; and / or, an angle between the third bending section and the axis of rotation of the centrifugal fan wheel is θ3, and 0°≤θ3≤30°. 6.The centrifugal fan wheel according to claim 1, characterized in that, an angle between an end of the outlet edge of the blade and the axis of rotation of the centrifugal fan wheel is α1, and 30°≤α1≤85°; and / or, an angle between another end of the outlet edge of the blade and the axis of rotation of the centrifugal fan wheel is α2, and 150°≤α2≤180°. 7.The centrifugal fan wheel according to claim 1, characterized in that, an angle between a line connecting the two ends of the outlet edge of the blade and the axis of rotation of the centrifugal fan wheel is β, wherein, 0°≤β≤40°。 8.The centrifugal fan wheel according to claim 1, characterized in that, the blade comprises a suction surface and a pressure surface, the suction surface and the pressure surface are independently processed and formed, and the blade is formed by relatively fixing and splicing the suction surface and the pressure surface. 9.The centrifugal fan wheel according to claim 1, characterized in that, the wheel disc is provided with a plurality of first blade insertion slots circumferentially for inserting one end of the blade; and the centrifugal fan wheel further comprises a wheel cover arranged opposite to the wheel disc, the wheel cover is provided with a plurality of second blade insertion slots circumferentially for inserting another end of the blade, and the first blade insertion slots and the second blade insertion slots are in one-to-one correspondence. 10.An air conditioner indoor unit, characterized in that, comprising the centrifugal fan wheel according to any one of claims 1-9.

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