Cross-flow wind wheel and air conditioner

Abstract

The utility model discloses a cross-flow wind wheel and an air conditioner, the cross-flow wind wheel comprises one impeller middle section or a plurality of impeller middle sections arranged along the axial direction of the cross-flow wind wheel, the impeller middle section comprises a plurality of blades arranged along the circumferential direction of the cross-flow wind wheel at intervals, each blade is provided with an inner end and an outer end, the inner end is the end, close to the rotating axis of the cross-flow wind wheel, of the blade, the outer end is the end, close to the peripheral side of the cross-flow wind wheel, of the blade, a pit is formed in at least one side of the blade in the thickness direction, and the pit is located between the inner end and the outer end. According to the cross-flow wind wheel provided by the embodiment of the utility model, the efficiency and noise of the cross-flow wind wheel are optimized by improving the structure of the cross-flow wind wheel and forming the recess on at least one side of the blade in the thickness direction, and compared with the improvement of a volute structure, the overall performance of the cross-flow wind wheel can be better improved.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning, and in particular to a cross-flow fan and an air conditioner. Background Technology

[0002] In related technologies, cross-flow fans are a commonly used type of fan. As an air supply device, cross-flow fans have the characteristics of large air volume, relatively uniform air distribution, and low noise. Therefore, cross-flow fans are widely used in air conditioning equipment such as air conditioners, for example, they are commonly used in split-type wall-mounted units, floor-standing units, and even some ducted air conditioners. In current air conditioners, fan efficiency and noise are the two most critical product indicators, affecting the overall energy efficiency rating of the unit and the user's comfort experience.

[0003] In optimizing the efficiency and noise of cross-flow fans, common practices include adjusting the volute profile and adding noise-reducing features. However, these techniques primarily target the volute structure, resulting in limited overall performance improvements. Cross-flow impellers in related technologies still offer room for improvement in both noise and efficiency. Utility Model Content

[0004] This invention aims to solve at least one of the technical problems existing in the prior art. Therefore, one objective of this invention is to propose a cross-flow wind turbine that optimizes efficiency and reduces noise by improving the structure of the wind turbine itself, specifically by forming a recess on at least one side of the blades in the thickness direction. Compared to improvements to the volute structure, this allows for a better overall performance enhancement of the cross-flow wind turbine.

[0005] This utility model also proposes an air conditioner that includes the above-mentioned cross-flow fan.

[0006] According to a first aspect of the present invention, a cross-flow wind turbine includes: an impeller middle section, wherein the impeller middle section is one or a plurality of impeller middle sections arranged along the axial direction of the cross-flow wind turbine, the impeller middle section includes a plurality of blades arranged at intervals along the circumference of the cross-flow wind turbine, the blades having an inner end and an outer end, the inner end being one end of the blade near the rotation axis of the cross-flow wind turbine, the outer end being one end of the blade near the outer peripheral side of the cross-flow wind turbine, and at least one side of the blade in the thickness direction having a recess located between the inner end and the outer end.

[0007] According to the cross-flow wind turbine of this utility model embodiment, by forming a recess on at least one side of the blades in the thickness direction, a portion of the airflow can form a vortex near the recess when the cross-flow wind turbine rotates. When the airflow flows past the area near the recess of the blades of the cross-flow wind turbine, the airflow and the vortex experience air-to-air friction. This friction is smaller than the friction between air and blades, resulting in less energy loss. Therefore, the energy loss during the operation of the cross-flow wind turbine can be reduced, and the working efficiency of the cross-flow wind turbine can be improved. Furthermore, due to the smaller friction between the airflow and the vortex, the noise generated during the operation of the cross-flow wind turbine is also smaller, thus reducing the noise of the cross-flow wind turbine. By improving the structure of the cross-flow wind turbine itself, the efficiency and noise of the cross-flow wind turbine can be optimized. Compared with the improvement of the volute structure, the overall performance of the cross-flow wind turbine can be better improved.

[0008] According to some embodiments of this utility model, the blade is a blade of unequal thickness.

[0009] According to some embodiments of the present invention, the thickness of the blade at the recess is less than the thickness of the blade at the inner end; or, the thickness of the blade at the recess is less than the thickness of the blade at the outer end.

[0010] According to some embodiments of the present invention, there are multiple recesses on the same side in the thickness direction of the blade, and the multiple recesses on the same side are spaced apart in the direction from the inner end of the blade to the outer end of the blade.

[0011] According to some embodiments of the present invention, a protrusion exists between two adjacent recesses in a plurality of recesses located on the same side of the blade.

[0012] According to some embodiments of the present invention, the thickness of the blade at the protrusion is greater than the thickness of the blade at the recess.

[0013] According to some embodiments of this utility model, a plane perpendicular to the rotation axis of the cross-flow wind turbine is a reference plane, and the cross-section obtained by cutting the blade with the reference plane is the blade cross-section. A group of reference rays corresponding to the blade cross-section of a single blade is drawn within the reference plane with the rotation center of the cross-flow wind turbine as its endpoint. The group of reference rays includes multiple reference rays arranged circumferentially along the cross-flow wind turbine. Multiple reference circles with different radii are drawn within the reference plane with the rotation center of the cross-flow wind turbine as their centers. The number of reference circles is the same as the number of reference rays in the group of reference rays. Each reference ray and its corresponding reference circle are located within the blade cross-section. Each reference ray and its corresponding reference circle is a reference point. Multiple reference points are distributed at the inner end, the outer end, the recess, and the protrusion. The reference point distributed at the recess is a recess reference point, and the lowest point of the recess is opposite to the thickness direction of the blade. The reference point distributed at the protrusion is a protrusion reference point, and the highest point of the protrusion is opposite to the thickness direction of the blade.

[0014] According to some embodiments of this utility model, the reference points distributed at the outer end are called outer end reference points, the reference points distributed at the inner end are called inner end reference points, the outer contour line of the blade cross section is called the blade cross section contour line, a first inscribed circle is drawn with the outer end reference point as the center and radius R1, a second inscribed circle is drawn with the inner end reference point as the center and radius R2, a third inscribed circle is drawn with the concave reference point as the center and radius R3, and a fourth inscribed circle is drawn with the convex reference point as the center and radius R4. The first inscribed circle, the second inscribed circle, the third inscribed circle, and the fourth inscribed circle are all tangent to the blade cross section contour line.

[0015] According to some embodiments of this utility model, R3 is less than R4, and R3 is less than R1 or less than R2.

[0016] According to some embodiments of this utility model, the reference ray passing through the inner end reference point is the inner end reference ray, the reference ray passing through the concave reference point is the concave reference ray, the reference ray passing through the convex reference point is the convex reference ray, the included angle between adjacent concave reference rays and convex reference rays is α, and the included angle between the inner end reference ray and adjacent convex reference rays is β, where α > 0.5*β.

[0017] According to some embodiments of this utility model, the reference ray passing through the outer end reference point is the outer end reference ray, the reference ray passing through the concave reference point is the concave reference ray, the reference ray passing through the convex reference point is the convex reference ray, the angle between the outer end reference ray and the adjacent concave reference ray is γ, and the angle between the outer end reference ray and the adjacent convex reference ray is θ, where γ > 0.5*θ.

[0018] According to some embodiments of the present invention, a plurality of the recesses are formed on the pressure surface of the blade.

[0019] An air conditioner according to a second aspect of the present invention includes: a cross-flow fan impeller as described in the first aspect of the present invention.

[0020] The air conditioner according to the embodiments of the present invention, by including the cross-flow fan wheel as described in the first aspect of the present invention, can reduce the energy loss of the cross-flow fan wheel during operation and improve the working efficiency of the air conditioner; furthermore, the noise generated by the cross-flow fan wheel during operation is smaller, which can reduce the noise of the air conditioner.

[0021] 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

[0022] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0023] Figure 1 This is a cross-sectional view of an indoor air conditioner unit according to some embodiments of the present utility model;

[0024] Figure 2 yes Figure 1 A cross-sectional view of the cross-flow wind turbine in the middle;

[0025] Figure 3 yes Figure 2 Enlarged view of point A in the image;

[0026] Figure 4 yes Figure 2 A cross-sectional view of the blades.

[0027] Figure label:

[0028] 100. Air conditioner indoor unit;

[0029] 10. Cross-flow fan; 11. Heat exchanger assembly; 12. Casing; 13. Air inlet; 14. Air outlet;

[0030] 20. Blade; 21. Inner end; 22. Outer end; 23. Pressure surface; 24. Suction surface; 25. Depression; 26. Protrusion; 28. Blade cross-section; 29. ​​Reference ray group; 30. Reference ray; 31. Reference circle; 32. Reference point; 33. Depressed reference point; 34. Protruding reference point; 35. Outer end reference point; 36. Inner end reference point; 37. Blade cross-section outline; 38. First inscribed circle; 39. Second inscribed circle; 40. Third inscribed circle; 41. Fourth inscribed circle; 42. Inner end reference ray; 43. Depressed reference ray; 44. Protruding reference ray; 45. Outer end reference ray. Detailed Implementation

[0031] 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.

[0032] Reference below Figures 1-4 Description of the cross-flow fan 10 according to an embodiment of the present utility model.

[0033] The cross-flow fan 10 according to the first aspect of the present invention includes: an impeller middle section.

[0034] The impeller middle section can be one or multiple sections arranged along the axial direction of the cross-flow wind turbine 10. By including multiple impeller middle sections arranged along the axial direction of the cross-flow wind turbine 10, the axial length of the cross-flow wind turbine 10 can be increased while ensuring the overall strength of the cross-flow wind turbine 10, and avoiding the impeller middle section from being too long and easily bending and damaged.

[0035] The impeller middle section includes a plurality of blades 20 arranged circumferentially along the cross-flow impeller 10. Each blade 20 has an inner end 21 and an outer end 22. The inner end 21 is the end of the blade 20 closest to the rotation axis of the cross-flow impeller 10, and the outer end 22 is the end of the blade 20 closest to the outer periphery of the cross-flow impeller 10. At least one side of the blade 20 in the thickness direction has a recess 25, which is located between the inner end 21 and the outer end 22. By forming a recess 25 on at least one side of the blade 20 in the thickness direction, when the cross-flow impeller 10 rotates, some of the airflow will form vortices near the recess 25. When other airflows flow past the area near the recess 25 of the blade 20 of the cross-flow impeller 10, the airflow flowing past the area near the recess 25 will rub against the airflow that forms the vortex, i.e., friction occurs between airflows, replacing the friction between the airflow and the blade 20 at the corresponding position in the related art. Since the friction between airflows is less than the friction between airflow and blade 20, the energy loss caused by airflow friction during operation of the cross-flow wind turbine 10 can be reduced, thereby improving the working efficiency of the cross-flow wind turbine 10.

[0036] For example, the cross-flow fan 10 can be used in an air conditioner. By forming a recess 25 on at least one side of the blade 20 in the thickness direction of the cross-flow fan 10, the power can be reduced by 5% while keeping the air volume of the air conditioner the same. Furthermore, since the friction between airflows is smaller, the noise generated when the cross-flow fan 10 is working can be reduced, for example, the noise can be reduced by 1 dB while keeping the air volume of the air conditioner the same.

[0037] For example, the two circumferential sides of a single blade 20 are a pressure surface 23 and a suction surface 24, respectively. When the cross-flow impeller 10 rotates, the pressure surface 23 of the single blade 20 faces the wind, and the suction surface 24 is leeward. The overall shape of the blade 20 is a protrusion 26 facing the suction surface 24, and the blade 20 includes multiple recesses 25, all of which are formed on the pressure surface 23.

[0038] According to the cross-flow impeller 10 of this utility model embodiment, by forming a recess 25 on at least one side of the blade 20 in the thickness direction, a portion of the airflow can form a vortex near the recess 25 when the cross-flow impeller 10 rotates. When the airflow flows past the recess 25 of the blade 20 of the cross-flow impeller 10, the airflow and the vortex experience air-to-air friction. This friction is smaller than the friction between air and the blade 20, resulting in less energy loss. Therefore, the energy loss of the cross-flow impeller 10 during operation can be reduced, improving the working efficiency of the cross-flow impeller 10. Furthermore, due to the smaller friction between the airflow and the vortex, the noise generated by the cross-flow impeller 10 during operation is also reduced, thus lowering the noise level of the cross-flow impeller 10. By improving the structure of the cross-flow impeller 10 itself, the efficiency and noise of the cross-flow impeller 10 can be optimized. Compared with the improvement of the volute structure, the overall performance of the cross-flow impeller 10 can be better improved.

[0039] According to some embodiments of this utility model, refer to Figures 2-4 The blades 20 are of unequal thickness. By making the blades 20 of unequal thickness, the concave 25 feature of the blades 20 can be made more obvious, thereby making the vortex formed when the airflow passes through the concave 25 more stable, reducing the energy loss of the cross-flow wind turbine 10 more effectively, and reducing the noise of the cross-flow wind turbine 10. Furthermore, by making the blades 20 of unequal thickness, the concave 25 feature on the pressure side of the blades 20 can be prevented from affecting the suction side, keeping the suction side smooth and reducing drag.

[0040] According to some embodiments of this utility model, refer to Figures 2-4 The thickness of the blade 20 at the recess 25 is less than the thickness of the blade 20 at the inner end 21. By making the thickness of the blade 20 at the recess 25 less than the thickness of the blade 20 at the inner end 21, the blade 20 can maintain a smooth suction side while making the recess 25 more pronounced than the inner end 21, thereby making the vortex formed when the airflow passes through the recess 25 more stable.

[0041] According to some embodiments of this utility model, refer to Figures 2-4 The thickness of the blade 20 at the recess 25 is less than the thickness of the blade 20 at the outer end 22. By making the thickness of the blade 20 at the recess 25 less than the thickness of the blade 20 at the outer end 22, the blade 20 can maintain a smooth suction side while making the recess 25 more pronounced than the recess 25 at the outer end 22, thereby making the vortex formed when the airflow passes through the recess 25 more stable.

[0042] According to some embodiments of this utility model, refer to Figures 2-4 Multiple recesses 25 are located on the same side of the blade 20 in the thickness direction, and these multiple recesses 25 on the same side are spaced apart in the direction from the inner end 21 to the outer end 22 of the blade 20. By having multiple recesses 25 on the same side of the blade 20 in the thickness direction, multiple standing waves can be formed when the airflow passes through the blade 20. By having multiple recesses 25 on the same side spaced apart in the direction from the inner end 21 to the outer end 22 of the blade 20, the formed standing waves can be spaced apart in the direction from the inner end 21 to the outer end 22 of the blade 20. The standing waves act like rolling bearings on the airflow, which can more effectively reduce the friction force of the cross-flow wind turbine 10 during operation, more effectively reduce the energy loss of the cross-flow wind turbine 10 during operation, and more effectively reduce noise.

[0043] For example, the indentation 25 formed by the blade 20 on the pressure surface 23 can be two, three, four, etc.

[0044] According to some embodiments of this utility model, refer to Figures 2-4 A protrusion 26 is provided between two adjacent recesses 25 on the same side of the blade 20. By providing a protrusion 26 between two adjacent recesses 25 on the same side of the blade 20, the protrusion 26 can separate the two adjacent recesses 25, so that when the airflow flows through the recesses 25 of the blade 20, a vortex can be formed at one recess 25, thus reducing the energy loss of the cross-flow wind turbine 10 during operation.

[0045] According to some embodiments of this utility model, refer to Figures 2-4 The thickness of the blade 20 at the protrusion 26 is greater than the thickness of the blade 20 at the depression 25. By making the thickness of the blade 20 at the protrusion 26 greater than the thickness of the blade 20 at the depression 25, the protrusion 26 can be made more prominent than the depression 25 while keeping the suction side smooth, and the protrusion 26 can more significantly separate two adjacent depressions 25.

[0046] According to some embodiments of this utility model, refer to Figure 3 A plane perpendicular to the rotation axis of the cross-flow impeller 10 is used as a reference plane. The cross section obtained by cutting the blade 20 from the reference plane is the blade 20 cross section. A set of reference rays 29, corresponding to the blade 20 cross section of a single blade 20, is drawn within the reference plane with the rotation center of the cross-flow impeller 10 as the endpoint. The set of reference rays 29 includes multiple reference rays 30 arranged circumferentially along the cross-flow impeller 10. A set of reference circles 31 with different radii are drawn within the reference plane with the rotation center of the cross-flow impeller 10 as the center. The number of reference circles 31 is the same as the number of reference rays 30 in the set of reference rays 29 and they correspond one-to-one. The intersection points of the reference ray 30 and the corresponding reference circle 31 are all located within the cross-section of the blade 20. Each intersection point of the reference ray 30 and the corresponding reference circle 31 is a reference point 32. Multiple reference points 32 are distributed at the inner end 21, outer end 22, recess 25, and protrusion 26. The reference point 32 located at the recess 25 is a recessed reference point 32, and its lowest point is opposite to the lowest point of the recess 25 in the thickness direction of the blade 20. The reference point 32 located at the protrusion 26 is a protrusion reference point 32, and its highest point is opposite to the highest point of the protrusion 26 in the thickness direction of the blade 20. By aligning the recessed reference point 32 with the lowest point of the recess 25 in the thickness direction of the blade 20, and the protrusion reference point 32 with the highest point of the protrusion 26 in the thickness direction of the blade 20, the shape and structure of the blade 20 can be simplified, facilitating design and manufacturing.

[0047] According to some embodiments of this utility model, refer to Figure 3The reference point 32 distributed at the outer end 22 is the outer end reference point 32, the reference point 32 distributed at the inner end 21 is the inner end reference point 32, the outer contour line of the blade 20 section is the blade 20 section contour line, the outer end reference point 32 is the center and the first inscribed circle 38 is the radius R1, the inner end reference point 32 is the center and the second inscribed circle 39 is the radius R2, the concave reference point 32 is the center and the third inscribed circle 40 is the radius R3, and the convex reference point 32 is the center and the fourth inscribed circle 41 is the radius R4. The first inscribed circle 38, the second inscribed circle 39, the third inscribed circle 40 and the fourth inscribed circle 41 are all tangent to the blade 20 section contour line. By making the first inscribed circle 38, the second inscribed circle 39, the third inscribed circle 40, and the fourth inscribed circle 41 tangent to the cross-sectional profile of the blade 20, the cross-sectional profile of the blade 20 can be made smoother. When the cross-flow impeller 10 is running, the friction between the cross-sectional profile of the blade 20 and the airflow can be reduced, reducing the energy loss caused by friction and improving the efficiency of the cross-flow impeller 10. Furthermore, since the friction between the blade 20 and the airflow is reduced, the noise generated when the cross-flow impeller 10 is running is reduced, thus reducing the noise of the cross-flow impeller 10 and improving the user experience.

[0048] According to some embodiments of this utility model, refer to Figure 3 R3 is less than R4, and R3 is less than R1 or less than R2. By making R3 less than R4, the indentation 25 of the blade 20 near the concave reference point 32 can be stronger than that of the blade 20 near the convex reference point 32, resulting in a more stable vortex near the concave reference point 32 when the cross-flow impeller 10 is operating. By making R3 less than R1 or less than R2, the indentation 25 of the blade 20 near the concave reference point 32 can be stronger than that of the outer or inner reference point 32, resulting in a more stable vortex near the concave reference point 32 when the cross-flow impeller 10 is operating. When the airflow passes through, the friction between the vortex formed near the concave reference point 32 and the airflow can more fully replace the friction between the airflow and the blade 20 at the same position, reducing energy loss caused by friction and improving the efficiency of the cross-flow impeller 10. Furthermore, by reducing the friction between the blade 20 and the airflow, the noise generated during the operation of the cross-flow impeller 10 is reduced, improving the user experience.

[0049] For example, R3 is less than R4, and R3 is less than R1.

[0050] For example, R3 is less than R4, and R3 is less than R2.

[0051] For example, R3 is less than R4, and R3 is less than R1, and R3 is less than R2.

[0052] According to some embodiments of this utility model, refer to Figure 3The reference ray 30 passing through the inner end reference point 32 is the inner end reference ray 42, the reference ray 30 passing through the concave reference point 32 is the concave 25 reference ray 30, and the reference ray 30 passing through the convex reference point 32 is the convex reference ray 44. The angle between adjacent concave 25 reference rays 30 and convex reference rays 44 is α, and the angle between the inner end reference ray 42 and adjacent convex reference rays 44 is β, where α > 0.5*β. For example, the value of α can be 0.55β, 0.6β, 0.65β, 0.68β, 0.7β, etc. By making α > 0.5*β, the profile of the blade 20 near the concave reference point 32 can be made more concave than the adjacent convex reference point 32, which can make the stagnant vortex formed by the airflow at this point more stable. When the cross-flow impeller 10 is running, a more stable stagnant vortex can be formed near the concave reference point 32. When the airflow passes through, the friction between the vortex formed near the concave reference point 32 and the airflow can be used more fully to replace the friction between the airflow and the blade 20 at the same position, reducing the energy loss caused by friction and improving the efficiency of the cross-flow fan 10. Furthermore, since the friction between the blade 20 and the airflow is reduced, the noise generated when the cross-flow fan 10 is operated is reduced, improving the user experience.

[0053] According to some embodiments of this utility model, refer to Figure 3 The reference ray 30 passing through the outer end reference point 32 is the outer end reference ray 45, the reference ray 30 passing through the concave reference point 32 is the concave 25 reference ray 30, and the reference ray 30 passing through the convex reference point 32 is the convex reference ray 44. The angle between the outer end reference ray 45 and the adjacent concave 25 reference ray 30 is γ, and the angle between the outer end reference ray 45 and the adjacent convex reference ray 44 is θ, where γ > 0.5*θ. For example, the value of γ can be 0.55θ, 0.6θ, 0.65θ, 0.68θ, 0.7θ, etc. By making γ > 0.5*θ, the profile of the blade 20 near the concave reference point 32 can be made more concave than the adjacent convex reference point 32, which can make the vortex formed by the airflow at this point more stable. When the cross-flow impeller 10 is running, a more stable vortex can be formed near the concave reference point 32. When the airflow passes through, the friction between the vortex formed near the concave reference point 32 and the airflow can be used more fully to replace the friction between the airflow and the blade 20 at the same position, reducing the energy loss caused by friction and improving the efficiency of the cross-flow fan 10. Furthermore, since the friction between the blade 20 and the airflow is reduced, the noise generated when the cross-flow fan 10 is operated is reduced, improving the user experience.

[0054] According to some embodiments of this utility model, refer to Figure 4Multiple recesses 25 are formed on the pressure surface 23 of the blade 20. Since the pressure surface 23 of the blade 20 faces the wind, the friction between the pressure surface 23 and the air is higher than that between the suction surface 24 and the blade 20. By forming multiple recesses 25 on the pressure surface 23 of the blade 20, multiple vortices can be formed on the pressure surface 23 of the blade 20 when the cross-flow impeller 10 rotates. These vortices create a rolling bearing-like effect on the flowing airflow, which can more effectively reduce frictional losses caused by the airflow passing through the blade 20, thereby improving the efficiency of the cross-flow impeller 10. Furthermore, by significantly reducing the friction between the blade 20 and the airflow, the noise generated during the operation of the cross-flow impeller 10 is reduced, improving the user experience.

[0055] For example, multiple indentations 25 are formed on the pressure surface 23 of the blade 20, while no indentations 25 are formed on the suction surface 24 of the blade 20. Since the pressure surface 23 of the blade 20 faces the wind, the friction between the pressure surface 23 and the air is higher than that between the suction surface 24 and the blade 20. By forming multiple indentations 25 on the pressure surface 23 of the blade 20, multiple vortices can be formed on the pressure surface 23 of the blade 20 when the cross-flow impeller 10 rotates. These vortices create a rolling bearing-like effect on the flowing airflow, further reducing frictional losses from the airflow passing through the blade 20 and thus improving the efficiency of the cross-flow impeller 10. Furthermore, by significantly reducing friction between the blade 20 and the airflow, the noise generated during the operation of the cross-flow impeller 10 is reduced, improving the user experience. By not forming indentations 25 on the suction surface 24 of the blade 20, the suction surface 24 of the blade 20 can be made smoother, further reducing friction between the blade 20 and the airflow.

[0056] An air conditioner according to a second aspect embodiment of the present invention, referring to... Figure 1 This includes: a cross-flow fan 10 according to the first aspect of the present invention.

[0057] For example, the air conditioner is a split-type air conditioner, which is divided into an outdoor unit and an indoor unit 100. The indoor unit 100 includes a cross-flow fan 10 according to the first aspect of the present invention.

[0058] For example, the air conditioner indoor unit 100 also includes a housing 12, a heat exchanger assembly 11, and a fan assembly. The fan assembly includes a cross-flow fan wheel 10 according to the first aspect of the present invention. The housing 12 is provided with an air inlet 13 and an air outlet 14. When the air conditioner is working, the cross-flow fan wheel 10 rotates, driving the airflow to enter the air conditioner indoor unit 100 from the air inlet 13. After the airflow exchanges heat with the heat exchanger assembly 11, it enters the vicinity of the cross-flow fan wheel 10 from the fan assembly. Because the blades 20 of the cross-flow fan 10 have a recess 25 on at least one side in the thickness direction, when the airflow passes through the blades 20, a vortex can be formed near the recess 25 of the blade 20. This causes the flowing airflow to rub against the vortex, replacing the friction between the airflow and the blades 20. Since the friction between airflows is less than the friction between the airflow and the blades 20, the friction loss generated by the airflow passing through the blades 20 can be reduced, thereby improving the efficiency of the cross-flow fan 10. Furthermore, by significantly reducing the friction between the blades 20 and the airflow, the noise generated during the operation of the cross-flow fan 10 is reduced, which can reduce the noise of the air conditioner and improve the user experience. By eliminating the recess 25 on the suction surface 24 of the blades 20, the suction surface 24 of the blades 20 can be made smoother, further reducing the friction between the blades 20 and the airflow.

[0059] According to the embodiments of the present invention, the air conditioner includes a cross-flow fan 10 according to the first aspect of the present invention, which can reduce the energy loss of the cross-flow fan 10 during operation and improve the working efficiency of the air conditioner; and the cross-flow fan 10 generates less noise during operation, which can reduce the noise of the air conditioner.

[0060] Reference below Figures 1-4 Description of the cross-flow fan 10 according to an embodiment of the present utility model.

[0061] In this embodiment, the cross-flow impeller 10 includes an impeller middle section.

[0062] The impeller middle section is one or multiple blades arranged along the axial direction of the cross-flow wind turbine 10. The impeller middle section includes multiple blades 20 arranged circumferentially at intervals along the cross-flow wind turbine 10. Each blade 20 has an inner end 21 and an outer end 22. The inner end 21 is the end of the blade 20 closest to the rotation axis of the cross-flow wind turbine 10, and the outer end 22 is the end of the blade 20 closest to the outer peripheral side of the cross-flow wind turbine 10. At least one side of the blade 20 in the thickness direction has a recess 25, which is located between the inner end 21 and the outer end 22.

[0063] The blade 20 is of unequal thickness. The thickness of the blade 20 at the recess 25 is less than the thickness of the blade 20 at the inner end 21, and the thickness of the blade 20 at the recess 25 is less than the thickness of the blade 20 at the outer end 22. Multiple recesses 25 are located on the same side of the thickness direction of the blade 20, and these multiple recesses 25 are spaced apart in the direction from the inner end 21 to the outer end 22 of the blade 20. A protrusion 26 is provided between adjacent recesses 25 on the same side of the blade 20, and the thickness of the blade 20 at the protrusion 26 is greater than the thickness of the blade 20 at the recess 25. Multiple recesses 25 are formed on the pressure surface 23 of the blade 20.

[0064] A plane perpendicular to the rotation axis of the cross-flow impeller 10 is used as a reference plane. The cross-section of the blade 20 obtained by cutting the blade 20 from the reference plane is the blade 20 cross-section. A set of reference rays 29, corresponding to the blade 20 cross-section of a single blade 20, is drawn within the reference plane with the rotation center of the cross-flow impeller 10 as its endpoint. The set of reference rays 29 includes multiple reference rays 30 arranged circumferentially along the cross-flow impeller 10. Multiple reference circles 31 with different radii are drawn within the reference plane with the rotation center of the cross-flow impeller 10 as their center. The number of reference circles 31 is the same as the number of reference rays 30 in the set of reference rays 29, and they correspond one-to-one. Each reference circle 31... The intersection of the reference ray 30 and the corresponding reference circle 31 is located within the cross section of the blade 20. The intersection of each reference ray 30 and the corresponding reference circle 31 is a reference point 32. Multiple reference points 32 are distributed at the inner end 21, the outer end 22, the depression 25, and the protrusion 26, respectively. The reference point 32 distributed at the depression 25 is the depression reference point 32. The depression reference point 32 and the lowest point of the depression 25 are opposite to each other in the thickness direction of the blade 20. The reference point 32 distributed at the protrusion 26 is the protrusion reference point 32. The protrusion reference point 32 and the highest point of the protrusion 26 are opposite to each other in the thickness direction of the blade 20. Reference points 32 distributed at the outer end 22 are designated as outer end reference points 32, and reference points 32 distributed at the inner end 21 are designated as inner end reference points 32. The outer contour line of the blade 20 cross section is designated as the blade 20 cross section contour line. A first inscribed circle 38 is drawn with the outer end reference point 32 as the center and radius R1, a second inscribed circle 39 is drawn with the inner end reference point 32 as the center and radius R2, a third inscribed circle 40 is drawn with the concave reference point 32 as the center and radius R3, and a fourth inscribed circle 41 is drawn with the convex reference point 32 as the center and radius R4. The first inscribed circle 38, the second inscribed circle 39, the third inscribed circle 40, and the fourth inscribed circle 41 are all tangent to the blade 20 cross section contour line. R3 is less than R4, and R3 is less than R1 and R3 is less than R2.

[0065] Reference ray 30 passing through inner end reference point 32 is inner end reference ray 42; reference ray 30 passing through concave reference point 32 is concave 25 reference ray 30; reference ray 30 passing through convex reference point 32 is convex reference ray 44; the angle between adjacent concave 25 reference ray 30 and convex reference ray 44 is α; the angle between inner end reference ray 42 and adjacent convex reference ray 44 is β, where α > 0.5*β. Reference ray 30 passing through outer end reference point 32 is outer end reference ray 45; reference ray 30 passing through concave reference point 32 is concave 25 reference ray 30; reference ray 30 passing through convex reference point 32 is convex reference ray 44; the angle between outer end reference ray 45 and adjacent concave 25 reference ray 30 is γ; the angle between outer end reference ray 45 and adjacent convex reference ray 44 is θ, where γ > 0.5*θ.

[0066] 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", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to 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.

[0067] In the description of this utility model, "first feature" and "second feature" may include one or more of the features.

[0068] In the description of this utility model, "multiple" means two or more.

[0069] In the description of this utility model, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or it may include the first and second features not being in direct contact but being in contact through another feature between them.

[0070] In the description of this utility model, the terms "above", "over" and "on top" for the first feature and the second feature include the first feature being directly above or diagonally above the second feature, or simply indicate that the first feature is at a higher horizontal level than the second feature.

[0071] 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.

[0072] 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 cross-flow impeller, characterized in that, include: The impeller middle section is one or multiple impeller middle sections arranged along the axial direction of the cross-flow wind turbine. The impeller middle section includes multiple blades arranged at intervals along the circumference of the cross-flow wind turbine. Each blade has an inner end and an outer end. The inner end is the end of the blade closest to the rotation axis of the cross-flow wind turbine, and the outer end is the end of the blade closest to the outer peripheral side of the cross-flow wind turbine. At least one side of the blade in the thickness direction has a recess, which is located between the inner end and the outer end.

2. The cross-flow impeller according to claim 1, characterized in that, The blades are blades of unequal thickness.

3. The cross-flow impeller according to claim 1, characterized in that, The thickness of the blade at the recess is less than the thickness of the blade at the inner end; or, the thickness of the blade at the recess is less than the thickness of the blade at the outer end.

4. The cross-flow wind turbine according to claim 1, characterized in that, The recesses located on the same side in the thickness direction of the blade are multiple, and the multiple recesses located on the same side are spaced apart in the direction from the inner end of the blade to the outer end of the blade.

5. The cross-flow impeller according to claim 4, characterized in that, A protrusion exists between two adjacent recesses in a plurality of recesses located on the same side of the blade.

6. The cross-flow wind turbine according to claim 5, characterized in that, The thickness of the blade at the protrusion is greater than the thickness of the blade at the depression.

7. The cross-flow wind turbine according to claim 5, characterized in that, A plane perpendicular to the rotation axis of the cross-flow wind turbine is designated as a reference plane. The cross-section obtained by cutting the blade with the reference plane is called the blade cross-section. A set of reference rays, corresponding to the blade cross-section of a single blade, is drawn within the reference plane with the rotation center of the cross-flow wind turbine as its endpoint. This set of reference rays includes multiple reference rays arranged circumferentially along the cross-flow wind turbine. Multiple reference circles of different radii are drawn within the reference plane with the rotation center of the cross-flow wind turbine as their centers. The number of reference circles is the same as the number of reference rays in the set of reference rays, and they correspond one-to-one. The intersection points of each reference ray and the corresponding reference circle are all located within the blade cross-section. Each intersection point of the reference ray and the corresponding reference circle is a reference point. Multiple reference points are distributed at the inner end, the outer end, the recess, and the protrusion. The reference points distributed at the recess are recess reference points, and the lowest point of the recess is opposite to the thickness direction of the blade. The reference points distributed at the protrusion are protrusion reference points, and the highest point of the protrusion is opposite to the thickness direction of the blade.

8. The cross-flow wind turbine according to claim 7, characterized in that, The reference points distributed at the outer end are called outer end reference points, and the reference points distributed at the inner end are called inner end reference points. The outer contour line of the blade cross section is called the blade cross section contour line. A first inscribed circle is drawn with the outer end reference point as the center and radius R1, a second inscribed circle is drawn with the inner end reference point as the center and radius R2, a third inscribed circle is drawn with the concave reference point as the center and radius R3, and a fourth inscribed circle is drawn with the convex reference point as the center and radius R4. The first inscribed circle, the second inscribed circle, the third inscribed circle, and the fourth inscribed circle are all tangent to the blade cross section contour line.

9. The cross-flow wind turbine according to claim 8, characterized in that, R3 is less than R4, and R3 is less than R1 or less than R2.

10. The cross-flow wind turbine according to claim 7, characterized in that, The reference ray passing through the inner end reference point is the inner end reference ray, the reference ray passing through the concave reference point is the concave reference ray, and the reference ray passing through the convex reference point is the convex reference ray. The angle between adjacent concave reference rays and convex reference rays is α, and the angle between the inner end reference ray and adjacent convex reference rays is β, where α > 0.5*β.

11. The cross-flow wind turbine according to claim 7, characterized in that, The reference ray passing through the outer end reference point is the outer end reference ray, the reference ray passing through the concave reference point is the concave reference ray, and the reference ray passing through the convex reference point is the convex reference ray. The angle between the outer end reference ray and the adjacent concave reference ray is γ, and the angle between the outer end reference ray and the adjacent convex reference ray is θ, where γ > 0.5*θ.

12. The cross-flow wind turbine according to any one of claims 4-11, characterized in that, Multiple of the aforementioned recesses are formed on the pressure surface of the blade.

13. An air conditioner, characterized in that, include: The cross-flow wind turbine according to any one of claims 1-12.

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