Cross-flow wind wheel and air conditioner

Abstract

The cross-flow wind wheel comprises blade sets and a plurality of connecting plates, the multiple connecting plates are arranged at intervals in the axial direction of the cross-flow wind wheel, one blade set is connected between every two adjacent connecting plates, each blade set comprises a plurality of blades, the two ends, in the radial direction of the cross-flow wind wheel, of the blades are the windward end and the leeward end respectively, and the windward end and the leeward end are connected through the connecting plates. Relative to the windward end and the leeward end which are adjacent to the central axis of the cross-flow wind wheel, in the axial direction of the cross-flow wind wheel and from one end of each blade to the other end of each blade, the air inlet geometric angle of each blade is firstly reduced and then increased, and on the cross section of the cross-flow wind wheel, the tangent line of the cross section center line of each blade at a first intersection point with the windward end is a first straight line; the connecting line of the first intersection point and the orthographic projection of the central axis of the cross-flow wind wheel is a second straight line, and the air inlet geometric angle is an included angle between the first straight line and the second straight line. Therefore, the air inlet geometric angles of the blades are firstly reduced and then increased from one ends to the other ends of the blades in the axial direction of the cross-flow wind wheel, so that the blades can adapt to a flow field near the connecting plate, the uniformity of the flow field when airflow passes through the cross-flow wind wheel is improved, turbulence noise of the cross-flow wind wheel can be reduced, and the service life of the cross-flow wind wheel is prolonged. And meanwhile, the rotation noise of the cross-flow wind wheel can be reduced.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and more particularly to a cross-flow fan and an air conditioner. Background Technology

[0002] When an air conditioner is running, it generates aerodynamic noise due to the operation of the cross-flow fan. The level of aerodynamic noise is closely related to the user's experience. Therefore, how to reduce the aerodynamic noise generated by the air conditioner has become a matter of great concern.

[0003] In related technologies, the blade shape of the cross-flow fan cannot adapt to the non-uniform distribution of the flow field in the axial direction of the cross-flow fan, which leads to a deterioration in the flow effect of the internal airflow of the cross-flow fan and generates turbulent noise and rotational noise. This results in high noise levels during operation of the cross-flow fan, affecting the user's experience. Summary of the Invention

[0004] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes a cross-flow fan impeller that generates low aerodynamic noise.

[0005] According to an embodiment of the present invention, a cross-flow wind turbine includes: a plurality of connecting plates, the plurality of connecting plates being spaced apart along the axial direction of the cross-flow wind turbine; a blade group, a set of blade groups being connected between two adjacent connecting plates, each set of blade groups including a plurality of blades spaced apart circumferentially along the cross-flow wind turbine, the two ends of the blades in the radial direction of the cross-flow wind turbine being a windward end and a leeward end, respectively. Relative to the windward end, the leeward end is adjacent to the central axis of the cross-flow wind turbine. In the axial direction of the cross-flow wind turbine, from one end of the blade to the other end of the blade, the air intake geometry angle of the blade first decreases and then increases. On the cross-section of the cross-flow wind turbine, the tangent of the center line of the blade cross-section at a first intersection with the windward end is a first straight line, the line connecting the first intersection with the orthographic projection of the central axis of the cross-flow wind turbine is a second straight line, and the air intake geometry angle is the angle between the first straight line and the second straight line.

[0006] According to an embodiment of the present invention, the cross-flow wind turbine makes the air intake geometry angle of the blades decrease first and then increase from one end of the blade to the other in the axial direction of the cross-flow wind turbine. This allows the blades to adapt to the flow field near the connecting plate, improves the flow field uniformity when the airflow passes through the cross-flow wind turbine, and reduces the turbulent noise of the cross-flow wind turbine. At the same time, it helps to reduce the superposition of pressure pulsations generated when the airflow impacts the blades, weakens the high-order harmonics generated by the interaction between the airflow and the blades, and thus reduces the rotational noise of the cross-flow wind turbine. This can reduce the noise generated when the cross-flow wind turbine is working.

[0007] According to some embodiments of the present invention, the blade includes a first section and a second section arranged sequentially along the axial direction of the cross-flow impeller, the air intake geometry angles of the first section and the second section both decreasing in the direction toward each other, each of the first section and the second section includes a first segment and a second segment, the first segment being located between the corresponding connecting plate and the second segment, and the rate of change of the air intake geometry angle of the first segment being greater than the rate of change of the air intake geometry angle of the second segment.

[0008] According to some embodiments of the present invention, the intake geometry angle changes continuously and gradually from one end of the blade to the other end of the blade.

[0009] According to some embodiments of the present invention, the blade includes a first section and a second section arranged sequentially along the axial direction of the cross-flow impeller, wherein the air intake geometry angles of the first section and the second section decrease in the direction toward each other, and the first section and the second section are arranged symmetrically.

[0010] According to some embodiments of the present invention, the intake geometry angle is β, 30°≤β≤60°; and / or, the difference between the maximum and minimum values ​​of the intake geometry angle is less than or equal to 20°.

[0011] According to some embodiments of the present invention, the blade group is multiple groups, including multiple groups of first blade groups and one group of second blade groups. In the axial direction of the cross-flow wind turbine, the lengths of the multiple groups of first blade groups are equal, and the length of the first blade group is greater than the length of the second blade group.

[0012] According to some embodiments of the present invention, there are multiple sets of blades, and a connecting plate connects two adjacent sets of blades. The blades of two adjacent sets of blades are staggered in the circumferential direction of the cross-flow wind turbine.

[0013] According to some embodiments of the present invention, there are three or more connecting plates, and the plurality of connecting plates include two end plates and at least one middle section plate, wherein the middle section plate and the blade assembly on one side thereof are integral or separate parts.

[0014] According to some embodiments of the present invention, along the axial direction of the cross-flow impeller, from one end of the blade to the other end of the blade, the outlet geometry of the blade changes. On the cross-section of the cross-flow impeller, the tangent of the center line of the blade's cross-section at the second intersection with the leeward end is a third straight line, and the line connecting the second intersection with the orthographic projection of the central axis of the cross-flow impeller is a fourth straight line. The outlet geometry is the angle between the third straight line and the fourth straight line.

[0015] According to some embodiments of the present invention, along the axial direction of the cross-flow impeller, from one end of the blade to the other end of the blade, the outlet geometry angle of the blade first decreases and then increases.

[0016] Another object of the present invention is to provide an air conditioner.

[0017] An air conditioner includes the aforementioned cross-flow fan impeller.

[0018] The air conditioner described above has the same advantages as the cross-flow fan mentioned above, which will not be repeated here.

[0019] Additional aspects and advantages of the 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 the present invention 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 schematic diagram of the cross-flow wind turbine according to an embodiment of the present invention;

[0022] Figure 2 This is a cross-sectional view of the cross-flow wind turbine described in an embodiment of the present invention;

[0023] Figure 3 for Figure 2 Enlarged view of point A in the middle;

[0024] Figure 4 This is a schematic diagram of the blade structure according to an embodiment of the present invention;

[0025] Figure 5 This is a schematic diagram showing the variation of the air intake geometry angle of the blade with the axial direction of the cross-flow wind turbine according to an embodiment of the present invention;

[0026] Figure 6 This is a comparison diagram of the simulated streamline cloud map of the cross-flow wind turbine of this application and a conventional cross-flow wind turbine in the same flow channel, wherein B is the simulated flow field cloud map of the conventional cross-flow wind turbine and C is the simulated flow field cloud map of the cross-flow wind turbine of this application embodiment.

[0027] Figure 7 Figure D is a flow field comparison diagram of the cross-flow wind turbine of this application and a conventional cross-flow wind turbine in the axial direction, and Figure E is a flow field diagram of the cross-flow wind turbine of this application.

[0028] Figure label:

[0029] Cross-flow wind turbine 100

[0030] Connecting plate 110, end plate 111, middle section plate 112

[0031] Blade group 120, blade 121, windward end 1211, leeward end 1212, first section 1213, second section 1214, first segment 1215, second segment 1216.

[0032] First blade group 122, second blade group 123

[0033] Intake angle of attack α, intake geometry angle β, exhaust geometry angle γ, first straight line L1, second straight line L2, third straight line L3, fourth straight line L4. Detailed Implementation

[0034] Embodiments of the present invention 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 the present invention, and should not be construed as limiting the present invention.

[0035] In the description of this invention, it should be understood that the terms "center," "length," "width," "thickness," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention 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 the invention. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0036] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" 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 invention based on the specific circumstances.

[0037] The following is for reference. Figures 1-7 A cross-flow fan 100 according to an embodiment of the present invention is described.

[0038] Reference Figure 1According to an embodiment of the present invention, a cross-flow wind turbine 100 includes: a blade assembly 120 and a plurality of connecting plates 110. The plurality of connecting plates 110 are spaced apart along the axial direction of the cross-flow wind turbine 100. A set of blade assemblies 120 is connected between two adjacent connecting plates 110. Each set of blade assemblies 120 includes a plurality of blades 121 spaced apart along the circumferential direction of the cross-flow wind turbine 100.

[0039] Multiple blades 121 are arranged in a ring to form a blade group 120. Each blade group 120 has a connecting plate 110 connected to both ends in the axial direction parallel to the cross-flow wind turbine 100. The connecting plate 110 can serve as the mounting base for the blade group 120. By setting the connecting plate 110, the assembly of multiple blade groups 120 can be facilitated, which in turn facilitates the assembly of the cross-flow wind turbine 100, thereby improving the structural strength and stability of the cross-flow wind turbine 100. By setting multiple blade groups 120, the length of the blades 121 can be reduced, thereby reducing the risk of deformation due to excessive length of the blades 121.

[0040] It should be noted that "the length of blade 121" refers to the dimension of blade 121 extending between the two connecting plates 110 in the axial direction of the cross-flow wind turbine 100.

[0041] Combination Figure 2 and Figure 3 The blade 121 has two ends in the radial direction of the cross-flow wind turbine 100, namely the windward end 1211 and the leeward end 1212. Relative to the windward end 1211, the leeward end 1212 is adjacent to the central axis of the cross-flow wind turbine 100. It can be understood that the radial inner side of the blade 121 is the leeward end 1212, and the radial outer side of the blade 121 is the windward end 1211. The airflow can flow from the windward end 1211 of the blade 121 to the leeward end 1212 of the blade 121.

[0042] Combination Figures 1 to 4 Along the axial direction of the cross-flow impeller 100, from one end of the blade 121 to the other end of the blade 121, the air intake geometry angle β of the blade 121 first decreases and then increases.

[0043] It should be noted that, referring to Figure 3 "The air intake geometry angle β of blade 121" refers to the following: on the cross-section of the cross-flow impeller 100, the tangent of the center line of the cross-section of blade 121 at the first intersection with the windward end 1211 is the first straight line L1, the line connecting the first intersection with the orthographic projection of the central axis of the cross-flow impeller 100 is the second straight line L2, and the air intake geometry angle β is the angle between the first straight line L1 and the second straight line L2.

[0044] Among them, "cross-section of the cross-flow wind turbine 100" refers to the cross-section of the cross-flow wind turbine 100 in the direction perpendicular to its central axis, and the center line of the cross-section of the blade 121 extends along the length of the blade 121.

[0045] Due to the setting of the connecting plate 110, when the airflow passes near the connecting plate 110, a boundary layer vortex will be formed near the wall of the connecting plate 110. The dissipation of the boundary layer vortex will cause uneven flow field distribution in the axial direction of the cross-flow impeller 100 and generate turbulent noise. Studies have found that the reasons for the above problems include that for airflow in a certain direction, when the airflow flows towards the cross-flow impeller 100, the flow field at the tip of the blade 121 is different from the flow field in the middle of the blade 121 due to the setting of the connecting plate 110. Therefore, the angle of attack of the blade tip is also different from that of the middle of the blade 121. The angle of attack of the blade tip is relatively large compared with the inlet geometry β. Therefore, in this embodiment, the air intake geometry angle β of the blade 121 first decreases and then increases from one end of the blade 121 to the other end along the axial direction of the cross-flow impeller 100, so that the air intake geometry angle β at both ends of the blade 121 is relatively large. This makes the change of the air intake geometry angle β match the change of the air intake angle of attack, thereby reducing the variation of the difference between the air intake geometry angle β and the air intake angle of attack α in the axial direction of the blade 121 in the cross-flow impeller 100. This allows the blade 121 to adapt to the flow field near the connecting plate 110, improves the flow field uniformity when the airflow passes through the cross-flow impeller 100, and reduces vortex shedding, thereby reducing the turbulent noise of the cross-flow impeller 100.

[0046] Meanwhile, the above-mentioned arrangement allows the windward end 1211 of the blade 121 to extend in a curved manner along the axial direction of the cross-flow impeller 100. This helps prevent the airflow flowing towards the cross-flow impeller 100 from simultaneously impacting different positions of the windward end 1211 of the blade 121 in the axial direction of the cross-flow impeller 100. This makes the impact of the airflow on different positions of the windward end 1211 asynchronous, thereby reducing the superposition of pressure pulsations generated when the airflow impacts the blade 121 on the blade 121. This weakens the high-order harmonics generated by the interaction between the airflow and the blade 121, thereby reducing the rotational noise of the cross-flow impeller 100.

[0047] It should be noted that "the air intake angle α of blade 121" refers to the angle between the flow direction of the airflow towards the cross-flow impeller 100 and the first straight line L1.

[0048] In related technologies, the air intake geometry angle of the blades is constant from one end to the other in the axial direction of the cross-flow impeller. This cannot adapt to the non-uniform distribution of the flow field in the axial direction of the cross-flow impeller, resulting in a deterioration in the internal airflow of the cross-flow impeller. Furthermore, the shedding of vortices at the connecting plate will lead to greater turbulent noise. At the same time, when the cross-flow impeller rotates, the airflow flowing through different positions of the blades will simultaneously impact the blades, causing the pressure pulsations generated when the airflow impacts the blades to superimpose on each other, resulting in high rotational noise of the cross-flow impeller.

[0049] Combination Figures 1 to 4as well as Figure 7 This application achieves a reduction in the air intake geometry angle β of the blade 121 from one end of the blade 121 to the other end along the axial direction of the cross-flow impeller 100. This allows the blade 121 to adapt to the flow field near the connecting plate 110, improving the flow field uniformity when the airflow passes through the cross-flow impeller 100 and reducing the turbulent noise of the cross-flow impeller 100. It also helps to reduce the superposition of pressure pulsations generated when the airflow impacts the blade 121, weakening the high-order harmonics generated by the interaction between the airflow and the blade 121, thereby reducing the rotational noise of the cross-flow impeller 100. This reduces the noise generated when the cross-flow impeller 100 is working.

[0050] Table 1 shows the airflow and noise test results of a conventional cross-flow fan and the cross-flow fan 100 of this application embodiment under the same airflow duct. The specifications of both the conventional cross-flow fan and the cross-flow fan 100 of this application embodiment are 120mm (diameter) * 620mm (axial length). The actual measurement results show that, at the same rotation speed, the cross-flow fan 100 of this application embodiment has a higher airflow and lower noise compared to the conventional cross-flow fan.

[0051] Table 1

[0052]

[0053] Figure 6 For conventional cross-flow wind turbines of the same specifications and the cross-flow wind turbine 100 of this application embodiment, both are located in the same air duct and rotate at 1000 r / min. The flow field cloud diagrams are taken at a cross-sectional location 3 mm away from one of the multiple connecting plates 110. According to... Figure 6 It can be seen that the influence range of the eccentric vortex inside the cross-flow wind turbine 100 of this application is smaller, and the blocking effect of the eccentric vortex on the flow field inside the cross-flow wind turbine 100 is smaller, which is conducive to the airflow passing through the cross-flow wind turbine 100.

[0054] In some embodiments of the present invention, the intake geometry angle β changes continuously and gradually from one end of the blade 121 to the other end of the blade 121. This helps to prevent airflows flowing through different positions of the blade 121 from impacting the blade 121 at the same time, thereby reducing the high-order harmonics generated by the interaction between the airflow and the blade 121, thereby reducing the rotational noise of the cross-flow impeller 100, and facilitating the processing and forming of the blade 121.

[0055] Reference Figure 4 In some embodiments of the present invention, the blade 121 includes a first section 1213 and a second section 1214 arranged sequentially along the axial direction of the cross-flow impeller 100, and the air intake geometry β of the first section 1213 and the second section 1214 both decrease in the direction toward each other.

[0056] Combination Figure 1 and Figure 4 One end of the first segment 1213 can be connected to one of the two adjacent connecting plates 110, and the other end of the first segment 1213 is connected to the second segment 1214. The end of the second segment 1214 away from the first segment 1213 can be connected to the other of the two adjacent connecting plates 110. The end of the first segment 1213 that is relatively close to the connecting plate 110 it is connected to is relatively close to the central axis of the cross-flow impeller 100. In the direction in which the first segment 1213 extends toward the second segment 1214, the first segment 1213 extends away from the central axis of the cross-flow impeller 100 along the radial direction of the cross-flow impeller 100, so that the air intake geometry angle β of the first segment 1213 decreases in the direction toward the second segment 1214.

[0057] Similarly, combining Figure 1 and Figure 4 The second segment 1214 is positioned relatively close to the connecting plate 110 connected to it, and is positioned relatively close to the central axis of the cross-flow impeller 100. In the direction in which the second segment 1214 extends toward the first segment 1213, the second segment 1214 extends in the radial direction of the cross-flow impeller 100 away from the central axis of the cross-flow impeller 100, so that the air intake geometry angle β of the second segment 1214 decreases toward the first segment 1213.

[0058] Thus, in the axial direction of the cross-flow impeller 100, from one end of the blade 121 to the other end, the air intake geometry angle β of the blade 121 first decreases and then increases, so that the blade 121 can adapt to the flow field near the connecting plate 110, improve the flow field uniformity when the airflow passes through the cross-flow impeller 100, and reduce the turbulent noise of the cross-flow impeller 100. At the same time, it helps to reduce the superposition of pressure pulsation generated when the airflow impacts the blade 121 on the blade 121, thereby reducing the rotational noise of the cross-flow impeller 100.

[0059] Optionally, from one end of the blade 121 to the other end, the intake geometry angle β can change continuously or in a stepwise manner, which helps to prevent airflows flowing through different positions of the blade 121 from impacting the blade 121 at the same time, thereby reducing the high-order harmonics generated by the interaction between the airflow and the blade 121, and thus reducing the rotational noise of the cross-flow wind turbine 100.

[0060] Furthermore, since the first segment 1213 and the second segment 1214 are symmetrically arranged, the air intake geometric angle β at both ends of the blade 121 length is equal. The first segment 1213 and the second segment 1214 have the same length. The position with the smallest air intake geometric angle β on the blade 121 is located in the middle of the blade 121 length. This is beneficial to improving the processing convenience of the blade 121 and the uniformity of the air guiding effect of the blade 121, thereby improving the uniformity of the flow field of the cross-flow impeller 100.

[0061] Combination Figure 2 and Figure 3 In some embodiments of the present invention, the intake geometry angle β is β, 30°≤β≤60°, which is beneficial to reduce the difference between the intake geometry angle β of the blade 121 and the airflow angle (or intake angle of attack), which is beneficial to ensure the intake effect of the cross-flow impeller 100 and to improve the flow field uniformity of the cross-flow impeller 100.

[0062] It is understandable that the specific angle setting of the intake geometry angle β can be determined according to actual production requirements, and no specific limit is made here. For example, the maximum value of the intake geometry angle β of blade 121 shall not exceed 60° and the minimum value shall not be lower than 30°.

[0063] like Figure 5 As shown, in some examples, the difference between the maximum and minimum values ​​of the inlet geometry angle β is less than or equal to 20°. The inlet geometry angle β may be different at different positions on the blade 121. Therefore, the inlet geometry angle β has a maximum and a minimum value. By making the difference between the maximum and minimum values ​​of the inlet geometry angle β less than or equal to 20°, specifically 10°, 15° or 17°, etc., and the inlet angle of attack is usually within a certain range, that is, the cross-flow impeller 100 can be adapted to the airflow with the inlet angle of attack within a certain range. This is beneficial to reduce the axial fluctuation of the difference between the inlet geometry angle β of the blade 121 and the airflow angle, and to improve the flow field uniformity of the cross-flow impeller 100.

[0064] It is understandable that the specific setting of the difference between the maximum and minimum values ​​of the intake geometry angle β, Δβ, can be determined according to actual production requirements, and no specific limitation is made here.

[0065] Optionally, the inlet geometry angle β can simultaneously satisfy 30°≤β≤60° and the difference between its maximum and minimum values ​​Δβ is less than or equal to 20°, which is beneficial to further reduce the difference between the inlet geometry angle β of the blade 121 and the airflow angle, and to improve the flow field uniformity of the cross-flow impeller 100.

[0066] like Figure 1As shown, in some embodiments of the present invention, the blade group 120 is multiple groups, and the multiple blade groups 120 include multiple first blade groups 122 and a second blade group 123. In the axial direction of the cross-flow wind turbine 100, the lengths of the multiple first blade groups 122 are equal, and the length of the first blade group 122 is greater than the length of the second blade group 123.

[0067] The first blade group 122 and the second blade group 123 are arranged at intervals in the axial direction of the cross-flow impeller 100. By making the lengths of the multiple first blade groups 122 equal, it is beneficial to improve the processing convenience of the first blade groups 122. The multiple first blade groups 122 have a certain degree of versatility. In order to make the length of the cross-flow impeller 100 adaptable to the usage requirements, the length of the second blade group 123 is adjusted to be smaller than the length of the first blade group 122, so as to facilitate the adjustment of the length of the cross-flow impeller 100, thereby making the length of the cross-flow impeller 100 adaptable to the usage requirements.

[0068] Therefore, the length of the cross-flow wind turbine 100 can be adjusted by adjusting the length of the second blade group 123, which helps to improve the production convenience and production efficiency of the cross-flow wind turbine 100.

[0069] Reference Figure 1 In some embodiments of the present invention, there are multiple sets of blade groups 120, and a connecting plate 110 connects two adjacent sets of blade groups 120. The blades 121 of two adjacent sets of blade groups 120 are staggered in the circumferential direction of the cross-flow impeller 100. That is, in the axial direction of the cross-flow impeller 100, the frontal projection planes of the blades 121 of two adjacent sets of blade groups 120 do not completely overlap. This is beneficial to reduce the airflow from simultaneously impacting the blades 121 of different sets of blade groups 120, thereby reducing the superposition of pressure pulsations generated by the airflow impacting the blades 121 of different sets of blade groups 120, and reducing the rotational noise of the cross-flow impeller 100.

[0070] In some embodiments of the present invention, the blade 121 is a lightweight high-strength material component, which includes at least one of thermoplastic resin and composite material.

[0071] For example, specific types of thermoplastic resins can be AS materials (AS material is short for styrene-acrylonitrile copolymer) or ABS materials (ABS material is specifically a terpolymer of three monomers: acrylonitrile (A), butadiene (B) and styrene (S)).

[0072] Composite materials can be high-strength composites made of PP plastic and glass fiber, where PP plastic refers to polypropylene.

[0073] The material components formed by the above materials have the characteristics of high strength and light weight, which can realize the lightweight design of the cross-flow wind turbine 100 and help ensure the structural strength of the blade 121 and reduce the risk of deformation of the blade 121.

[0074] It should be noted that the blade 121 can be made of a single material, which is beneficial to improving the processing convenience of the blade 121. Alternatively, the blade 121 can be made of thermoplastic resin and composite material through physical connection, or a new material can be made by chemical formulation. The specific material forming the blade 121 can be determined according to the actual production requirements, and no specific limitation is made here, as long as the strength and quality of the blade 121 can meet the production requirements.

[0075] Reference Figure 1 In some embodiments of the present invention, there are three or more connecting plates 110, and the multiple connecting plates 110 include two end plates 111 and at least one middle section plate 112.

[0076] For example, the multiple blade groups 120 may include a first blade group 122 and a second blade group 123 arranged along the axial direction of the cross-flow impeller 100. The length of the first blade group 122 is greater than the length of the second blade group 123, and the second blade group 123 may be disposed on one of the two end plates 111. The first blade group 122 is disposed on the side of the middle section plate 112 away from the second blade group 123 and is connected to the middle section plate 112. The other of the two end plates 111 is disposed on the side of the first blade group 122 away from the second blade group 123. Of course, when there are multiple first blade groups 122, the axial arrangement of the multiple first blade groups 122 and second blade groups 123 can be set according to requirements. For example, the second blade group 123 may be located on one side of the axial direction of all the first blade groups 122.

[0077] The specific number of the middle section plate 112 can be determined according to the actual size requirements of the cross-flow impeller 100, and is not specifically limited here.

[0078] Optionally, the middle section plate 112 and the blade group 120 on one side can be an integral part or separate parts. That is, according to the above example, the middle section plate 112 can be an integral part with the first blade group 122 to facilitate the production and assembly of the cross-flow wind turbine 100, or the middle section plate 112 can be separately set from the first blade group 122 to facilitate the disassembly and maintenance of the cross-flow wind turbine 100.

[0079] It is understandable that the specific arrangement of the middle section plate 112 and the blade group 120 on one side can be determined according to actual production requirements, and no specific limitation is made here.

[0080] Combination Figure 4 and Figure 5 In some embodiments of the present invention, the blade 121 includes a first segment 1213 and a second segment 1214 arranged sequentially along the axial direction of the cross-flow impeller 100. The air intake geometry angle β of the first segment 1213 and the second segment 1214 decreases in the direction toward each other. Each of the first segment 1213 and the second segment 1214 includes a first section 1215 and a second section 1216. The first section 1215 is located between the corresponding connecting plate 110 and the second section 1216. The rate of change of the air intake geometry angle β of the first section 1215 is greater than the rate of change of the air intake geometry angle β of the second section 1216. That is, for each of the first segment 1213 and the second segment 1214, the rate of change of the air intake geometry angle β at the position closer to the connecting plate 110 is greater than the rate of change of the air intake geometry angle β at the position farther from the connecting plate 110. The rate of change of the air intake geometry angle β can be understood as the amount of change of the air intake geometry angle β per unit length of the blade 121 along the axial direction of the cross-flow impeller 100.

[0081] For example, the first segment 1213 and the second segment 1214 are respectively connected to two adjacent connecting plates 110. The position where the first segment 1213 and the second segment 1214 are close to each other is defined as the second section 1216, and the position where the first segment 1213 and the second segment 1214 are relatively close to the connecting plate 110 is defined as the first section 1215. Considering the boundary layer eddies and eddy shedding near the connecting plate 110, by making the rate of change of the air intake geometry angle β of the first section 1215 greater than the rate of change of the air intake geometry angle β of the second section 1216, it is beneficial to improve the flow field uniformity when the airflow passes through the cross-flow impeller 100, and to reduce the turbulent noise caused by eddy shedding in the cross-flow impeller 100.

[0082] Combination Figure 2 and Figure 3 In some embodiments of the present invention, along the axial direction of the cross-flow impeller 100, from one end of the blade 121 to the other end of the blade 121, the exhaust geometry angle γ of the blade 121 changes. On the cross-section of the cross-flow impeller 100, the tangent of the center line of the cross-section of the blade 121 at the second intersection with the leeward end 1212 is the third straight line L3, and the line connecting the second intersection with the orthographic projection of the central axis of the cross-flow impeller 100 is the fourth straight line L4. The exhaust geometry angle γ is the angle between the third straight line L3 and the fourth straight line L4.

[0083] By changing the exhaust geometry angle γ of the blade 121, the blade 121 can adapt to the flow field near the connecting plate 110, extend the flow path of the airflow on the blade 121, improve the separation of the airflow from the blade 121, and thus help reduce turbulent noise.

[0084] Preferably, along the axial direction of the cross-flow impeller 100, from one end of the blade 121 to the other end of the blade 121, the outlet geometric angle γ of the blade 121 can be decreased first and then increased. This is beneficial to improving the adaptability of the blade 121 to the flow field near the connecting plate 110, thereby extending the flow path of the airflow on the blade 121 and thus reducing turbulent noise.

[0085] It is understood that the specific variation of the outlet geometric angle γ of the blade 121 can be determined according to the actual production requirements of the cross-flow impeller 100, and is not specifically limited here, as long as the outlet geometric angle γ of the blade 121 varies in the axial direction of the cross-flow impeller 100. The air conditioner according to an embodiment of the present invention includes the aforementioned cross-flow impeller 100.

[0086] Since the air conditioner is equipped with the aforementioned cross-flow impeller 100, by making the air intake geometry angle β of the blade 121 first decrease and then increase from one end of the blade 121 to the other end along the axial direction of the cross-flow impeller 100, the blade 121 can adapt to the flow field near the connecting plate 110, improve the flow field uniformity when the airflow passes through the cross-flow impeller 100, and reduce the turbulent noise of the cross-flow impeller 100. At the same time, it helps to reduce the superposition of pressure pulsations generated when the airflow impacts the blade 121 on the blade 121, weaken the high-order harmonics generated by the interaction between the airflow and the blade 121, and thus reduce the rotational noise of the cross-flow impeller 100. This can reduce the noise generated when the cross-flow impeller 100 is working.

[0087] The changes in the air intake geometry angle β and air outlet geometry angle γ of the blade 121, the number of blades 121, and the shape of the blades 121 can all be aerodynamically coupled according to the air intake grille, evaporator layout, duct profile, air outlet shape, louvers, and air guide plate of the air conditioner, so that the blades 121 can be adapted to the flow field of the cross-flow impeller 100 and reduce the aerodynamic noise of the cross-flow impeller 100.

[0088] 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 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.

[0089] Although embodiments of the 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 invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A cross-flow impeller, characterized in that, include: Multiple connecting plates are spaced apart along the axial direction of the cross-flow impeller; A blade assembly is connected between two adjacent connecting plates. Each blade assembly includes multiple blades spaced circumferentially along the cross-flow impeller. The two ends of the blades in the radial direction of the cross-flow impeller are the windward end and the leeward end, respectively. Relative to the windward end, the leeward end is adjacent to the central axis of the cross-flow impeller. In the axial direction of the cross-flow impeller, from one end of the blade to the other end, the air intake geometry angle of the blade first decreases and then increases. On the cross-section of the cross-flow impeller, the tangent of the center line of the blade's cross-section at the first intersection with the windward end is a first straight line, and the line connecting the first intersection point and the orthographic projection of the central axis of the cross-flow impeller is a second straight line. The air intake geometry angle is the angle between the first straight line and the second straight line.

2. The cross-flow impeller according to claim 1, characterized in that, The blade includes a first segment and a second segment arranged sequentially at intervals along the axial direction of the cross-flow impeller. The air intake geometry angles of the first segment and the second segment decrease in the direction toward each other. Each of the first segment and the second segment includes a first section and a second section. The first section is located between the corresponding connecting plate and the second section. The rate of change of the air intake geometry angle of the first section is greater than the rate of change of the air intake geometry angle of the second section.

3. The cross-flow impeller according to claim 1, characterized in that, The intake geometry angle changes continuously and gradually from one end of the blade to the other end.

4. The cross-flow wind turbine according to claim 1, characterized in that, The blade includes a first section and a second section arranged sequentially along the axial direction of the cross-flow impeller. The air intake geometry angles of the first section and the second section decrease in the direction toward each other, and the first section and the second section are arranged symmetrically.

5. The cross-flow wind turbine according to claim 1, characterized in that, The intake geometry angle is β, where 30°≤β≤60°; and / or, The difference between the maximum and minimum values ​​of the intake geometry angle is less than or equal to 20°.

6. The cross-flow wind turbine according to claim 1, characterized in that, The blade group consists of multiple groups, including multiple first blade groups and one second blade group. Along the axial direction of the cross-flow wind turbine, the lengths of the multiple first blade groups are equal, and the length of the first blade group is greater than the length of the second blade group.

7. The cross-flow wind turbine according to claim 1, characterized in that, The blade assembly consists of multiple sets, with a connecting plate connecting adjacent sets of blades. The blades of adjacent sets of blades are staggered in the circumferential direction of the cross-flow wind turbine.

8. The cross-flow wind turbine according to claim 1, characterized in that, There are three or more connecting plates, and the multiple connecting plates include two end plates and at least one middle section plate. The middle section plate and the blade assembly on one side are either integral or separate parts.

9. The cross-flow wind turbine according to any one of claims 1-8, characterized in that, Along the axial direction of the cross-flow impeller, from one end of the blade to the other end, the air outlet geometry angle of the blade changes. On the cross-section of the cross-flow impeller, the tangent to the center line of the blade's cross-section at the second intersection with the leeward end is the third straight line, and the line connecting the second intersection point and the orthographic projection of the central axis of the cross-flow impeller is the fourth straight line. The air outlet geometry angle is the angle between the third straight line and the fourth straight line.

10. The cross-flow wind turbine according to claim 9, characterized in that, Along the axial direction of the cross-flow impeller, from one end of the blade to the other end, the outlet geometry angle of the blade first decreases and then increases.

11. An air conditioner, characterized in that, Includes the cross-flow wind turbine according to any one of claims 1-10.

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