Axial flow wind wheel, axial flow fan and air conditioner

Abstract

The axial flow wind wheel comprises a hub and a plurality of blades, the blades are connected to the peripheral wall of the hub and are arranged at intervals in the circumferential direction of the hub, notches are formed in the blade tail edges of the blades, the projection of the axial flow wind wheel on a reference plane is the wind wheel projection, and the axial flow wind wheel is connected with the hub. The reference plane is perpendicular to the rotating axis of the axial flow wind wheel, on the wind wheel projection, the intersection point of the blade tail edge and the blade top of the blade is an intersection point Q, the intersection point of the blade tail edge and the blade root of the blade is an intersection point N, the contour line of the notch is a notch contour line, the intersection points of the notch contour line and the blade tail edge are an intersection point P and an intersection point K respectively, and the intersection point P is located on the side, close to the blade top, of the notch. The intersection point K is located on the side, close to the blade root, of the notch, and the distance between the intersection point P and the intersection point Q is smaller than that between the intersection point K and the intersection point N. According to the axial flow wind wheel provided by the embodiment of the utility model, low-efficiency areas in the blade tail edges and the blade tops of the blades can be effectively removed, so that the operation efficiency of the axial flow wind wheel is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of air-conditioning equipment, in particular to an axial flow fan, an axial flow fan and an air conditioner. Background Art

[0002] Axial flow fans are widely used in related technologies, for example, in air conditioning equipment such as air conditioners to drive airflow. However, the blades of these axial flow fans are limited by their structure, resulting in high energy consumption and low operating efficiency. This problem remains to be solved. Utility Model Content

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, one purpose of the present invention is to provide an axial flow wind wheel that, by providing a notch at the trailing edge of the blade, and with the notch being located closer to the blade tip than the blade root, can effectively eliminate the inefficient areas of the blade trailing edge and blade tip that perform negative work, thereby reducing the energy loss caused by the negative work performed in these inefficient areas, thereby effectively improving the operating efficiency of the axial flow wind wheel.

[0004] The utility model provides an axial flow fan comprising the above-mentioned axial flow wind wheel.

[0005] The utility model also provides an air conditioner comprising the axial flow fan.

[0006] According to the embodiment of the first aspect of the present invention, the axial flow wind wheel includes: a hub; a plurality of blades connected to the outer peripheral wall of the hub and arranged at intervals along the circumference of the hub, and a notch is formed on the trailing edge of the blade; wherein, the projection of the axial flow wind wheel on the reference plane is the wind wheel projection, and the reference plane is perpendicular to the rotation axis of the axial flow wind wheel. On the wind wheel projection, the intersection of the trailing edge of the blade and the top of the blade is the intersection Q, and the intersection of the trailing edge of the blade and the root of the blade is the intersection N. The contour line of the notch is the notch contour line, and the intersections of the notch contour line and the trailing edge are intersection P and intersection K respectively. The intersection P is located on the side of the notch close to the blade top, and the intersection K is located on the side of the notch close to the blade root. The distance between the intersection P and the intersection Q is smaller than the distance between the intersection K and the intersection N.

[0007] According to the axial flow wind wheel of the embodiment of the present invention, a notch is provided at the trailing edge of the blade, and the notch is arranged closer to the blade top relative to the blade root. In this way, the inefficient area of ​​the blade trailing edge and blade top that does negative work can be effectively removed, thereby reducing the energy loss caused by the negative work done in this inefficient area, thereby effectively improving the operating efficiency of the axial flow wind wheel.

[0008] According to some embodiments of the present utility model, on the reference plane, a base circle A2 is made with the rotation center of the axial flow impeller as the center of the circle and passing through the intersection point P. The radius of the base circle A2 is R2, and R2 satisfies: 0.75*R1 < R2 < 0.9*R1, where R1 is the maximum radius of the axial flow impeller.

[0009] According to some embodiments of the present utility model, on the reference plane, a straight line M1 is made passing through the intersection point N. The straight line M1 is tangent to the trailing edge of the blade. The point on the notch contour line that is farthest from the straight line M1 is point T. A straight line M2 is made passing through the point T. The straight line M2 is parallel to the straight line M1. The distance between the straight line M2 and the straight line M1 is G1, and G1 satisfies: G1 < 0.3*R1, where R1 is the maximum radius of the axial flow impeller.

[0010] According to some embodiments of the present utility model, on the reference plane, a base circle A2 is made with the rotation center of the axial flow impeller as the center of the circle and passing through the intersection point P. The radius of the base circle A2 is R2. A base circle A3 is made with the rotation center of the axial flow impeller as the center of the circle and passing through the intersection point K. The radius of the base circle A3 is R3. A straight line M1 is made passing through the intersection point N. The straight line M1 is tangent to the trailing edge of the blade. The point on the notch contour line that is farthest from the straight line M1 is point T. On the reference plane, a base circle A4 is made with the rotation center of the axial flow impeller as the center of the circle and passing through the point T. The radius of the base circle A4 is R4. R2, R3, and R4 satisfy: (R2 - R4) < (R4 - R3).

[0011] According to some embodiments of the present utility model, flow guiding ribs are provided on the negative pressure surface of the blade. At least a part of the flow guiding ribs is located between the notch and the blade tip. The flow guiding ribs extend in the direction from the trailing edge of the blade to the leading edge of the blade.

[0012] According to some embodiments of the present utility model, the extending direction of the flow guiding ribs is consistent with the rotation direction of the axial flow impeller.

[0013] According to some embodiments of the present utility model, on the reference plane, the intersection point of the leading edge of the blade and the blade tip is intersection point E1, and the intersection point of the leading edge of the blade and the blade root is intersection point E2. The point on the flow guiding rib that is closest to the intersection point E1 in the circumferential direction of the blade is point F1. A straight line S1 is made passing through the rotation center of the axial flow impeller and the intersection point E1. A straight line S2 is made passing through the rotation center of the axial flow impeller and the intersection point E2. A straight line S3 is made passing through the rotation center of the axial flow impeller and the point F1. The included angle between the straight line S1 and the straight line S2 is V1, and the included angle between the straight line S1 and the straight line S3 is V2. V1 and V2 satisfy: V2 > V1.

[0014] According to some embodiments of the present invention, on the reference surface, a straight line M1 is drawn through the intersection N, the straight line M1 is tangent to the trailing edge of the blade, the point on the notch contour line farthest from the straight line M1 is point T, the intersection of the leading edge of the blade and the blade top is intersection E1, the point of the guide rib farthest from the intersection E1 in the circumferential direction of the blade is point F2, a straight line S1 is drawn through the rotation center of the axial flow wind wheel and through the intersection E1, a straight line S4 is drawn through the rotation center of the axial flow wind wheel and through the intersection T, a straight line S5 is drawn through the rotation center of the axial flow wind wheel and through the intersection F2, the angle between the straight line S1 and the straight line S4 is V3, the angle between the straight line S1 and the straight line S5 is V4, and V3 and V4 satisfy: V3≤V4.

[0015] According to some embodiments of the present invention, on the reference surface, the point of the guide rib closest to the rotation center of the axial flow wind wheel in the radial direction of the axial flow wind wheel is point F3, and a base circle A5 is formed with the rotation center of the axial flow wind wheel as the center and passing through the intersection F3, and the radius of the base circle A5 is R5. On the reference surface, a base circle A2 is formed with the rotation center of the axial flow wind wheel as the center and passing through the intersection P, and the radius of the base circle A2 is R2, and R5 and R2 satisfy: R5≥R2.

[0016] According to some embodiments of the present invention, R5 and R2 further satisfy: (R5-R2)≤0.05*R1.

[0017] According to some embodiments of the present invention, the protruding height of the guide rib relative to the negative pressure surface is H1, and H1 is ≥ 1 mm.

[0018] According to some embodiments of the present invention, the cross section of the guide rib is a guide rib cross section, and the width of the guide rib cross section at the junction of the negative pressure surface is W1, 2mm≤W1≤8mm.

[0019] According to some embodiments of the present invention, the cross section of the guide rib is a guide rib cross section, and the width of the guide rib cross section decreases in the convex direction of the guide rib relative to the negative pressure surface.

[0020] According to some embodiments of the present invention, there are multiple guide ribs, and the multiple guide ribs are arranged at intervals along the radial direction of the axial flow wind wheel.

[0021] According to some embodiments of the present invention, the spacing between adjacent guide ribs is G2, and G2 ≥ 2 mm.

[0022] The axial flow fan according to the embodiment of the second aspect of the present invention includes: the axial flow wind wheel according to the embodiment of the first aspect of the present invention.

[0023] According to the axial flow fan of the embodiment of the present invention, the above-mentioned axial flow wind wheel is provided, and a notch is provided at the trailing edge of the blade of the axial flow wind wheel, and the notch is provided closer to the blade top relative to the blade root. In this way, the inefficient area of ​​the blade trailing edge and blade top that does negative work can be effectively removed, thereby reducing the energy loss caused by the negative work done in this inefficient area, thereby effectively improving the operating efficiency of the axial flow wind wheel, which is beneficial to improving the operating efficiency of the axial flow fan.

[0024] An air conditioner according to an embodiment of the third aspect of the present invention includes: an axial flow fan according to the embodiment of the second aspect of the present invention.

[0025] According to the air conditioner of the embodiment of the present invention, the above-mentioned axial flow fan is provided, and the axial flow fan includes an axial flow wind wheel. By providing a notch at the trailing edge of the blade of the axial flow wind wheel, and the notch is arranged closer to the blade top relative to the blade root, the inefficient area of ​​the blade trailing edge and blade top that does negative work can be effectively removed, thereby reducing the energy loss caused by the negative work done in this inefficient area, thereby effectively improving the operating efficiency of the axial flow wind wheel, which is beneficial to improving the overall operating efficiency of the air conditioner.

[0026] Additional aspects and advantages of the present invention will be given in part in the following description and will become apparent from the following description or learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] 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:

[0028] Figure 1 This is a three-dimensional schematic diagram of an axial flow wind wheel according to some embodiments of the present invention. Figure 1 ;

[0029] Figure 2 yes Figure 1 Three-dimensional diagram of the axial flow wind wheel in Figure 2 ;

[0030] Figure 3 yes Figure 1 Three-dimensional diagram of the axial flow wind wheel in Figure 3 ;

[0031] Figure 4 yes Figure 1 Three-dimensional diagram of the axial flow wind wheel in Figure 4 ;

[0032] Figure 5 yes Figure 1 Three-dimensional diagram of the axial flow wind wheel in Figure 5 ;

[0033] Figure 6 yes Figure 4 A three-dimensional schematic diagram of a partial structure of an axial flow wind wheel;

[0034] Figure 7 yes Figure 6 Schematic diagram of part of the mechanism of the axial flow wind wheel;

[0035] Figure 8 yes Figure 7 Enlarged view of point A in the middle;

[0036] Figure 9 is a schematic diagram of a portion of the mechanism of an axial flow wind wheel according to other embodiments of the present invention;

[0037] Figure 10 yes Figure 6 A cross-sectional view of a partial structure of a blade of an axial flow wind wheel;

[0038] Figure 11 is a cross-sectional view of a partial structure of a blade of an axial flow wind wheel according to some other embodiments of the present invention;

[0039] Reference numerals:

[0040] 100. Axial flow fan;

[0041] 1. Wheel hub;

[0042] 2. Blade; 21. Trailing edge of blade; 211. Notch; 22. Leading edge of blade; 23. Blade root; 24. Blade top; 25. Negative pressure surface; 251. Guide rib; 26. Positive pressure surface. DETAILED DESCRIPTION

[0043] The following describes embodiments of the present invention in detail. Examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended only to explain the present invention and are not to be construed as limiting the present invention.

[0044] In the related art, the applicant discovered that there is an inefficient area at the connection between the trailing edge 21 and the blade top 24 of the blade 2. This inefficient area performs negative work, affecting the efficient operation of the axial flow wind wheel 100, thereby causing a large energy loss in the axial flow wind wheel 100 and affecting the overall operating efficiency of the axial flow wind wheel 100.

[0045] Based on this, the applicant has proposed an axial flow wind rotor 100 comprising a hub 1 and a plurality of blades 2. The plurality of blades 2 are connected to the outer peripheral wall of the hub 1 and are spaced apart along the circumference of the hub 1. The trailing edges 21 of the blades 2 are formed with notches 211. Providing the notches 211 on the trailing edges 21 of the blades 2 of the axial flow wind rotor 100 eliminates inefficient regions, thereby reducing energy loss caused by negative work performed in these inefficient regions, thereby effectively improving the operating efficiency of the axial flow wind rotor 100.

[0046] Reference below Figures 1-11 An axial flow wind wheel 100 according to an embodiment of the present invention is described.

[0047] Reference Figure 1 、 Figure 4 and Figure 6 According to the first embodiment of the present invention, an axial flow wind turbine 100 includes a hub 1 and a plurality of blades 2. The blades 2 are connected to the outer peripheral wall of the hub 1 and are spaced apart along the circumference of the hub 1. The trailing edges 21 of the blades 2 are formed with notches 211. The hub 1 secures and supports the blades 2. Rotation of the hub 1 drives the blades 2 to rotate. For example, a motor is fixedly connected to the hub 1. The motor can be a DC motor or an AC motor.

[0048] Multiple blades 2 are provided on the outer peripheral wall of the hub 1 and are spaced apart from one another along the circumferential direction of the hub 1. Preferably, the multiple blades 2 are evenly spaced along the circumferential direction of the hub 1, and each blade 2 has the same shape. This makes the structure of the axial flow rotor 100 more uniform and the rotation of the axial flow rotor 100 more stable. Notches 211 are formed through the trailing edges 21 of the blades 2, and the notches 211 can change the flow path of the airflow at the trailing edges 21.

[0049] It should be explained that the contour edge of the blade 2 includes a leading edge 22, a blade top 24, a trailing edge 21 and a blade root 23 connected end to end in sequence. The blade root 23 is connected to the hub 1. In the rotation direction of the hub 1, the leading edge 22 is located in front of the trailing edge 21.

[0050] When the axial flow impeller 100 is operating, air flows in from the leading edge 22 and out from the trailing edge 21. That is, the airflow first contacts the blade 2 at the leading edge 22, and the airflow last exits the blade 2 at the trailing edge 21. The inlet direction refers to the incoming direction of the airflow, and the outlet direction refers to the outgoing direction of the airflow. The blade tip 24 refers to the radial boundary of the blade 2 away from the hub 1. The positive pressure surface 26 is the side of the blade 2 facing the outlet direction, and the negative pressure surface 25 is the side of the blade 2 facing the inlet direction. The negative pressure surface 25 is located upstream of the positive pressure surface 26.

[0051] Among them, the projection of the axial flow wind wheel 100 on the reference plane is the wind wheel projection, and the reference plane is perpendicular to the rotation axis of the axial flow wind wheel 100. On the wind wheel projection, the intersection of the blade trailing edge 21 and the blade top 24 of the blade 2 is the intersection Q, the intersection of the blade trailing edge 21 and the blade root 23 of the blade 2 is the intersection N, the contour line of the notch 211 is the notch contour line, and the intersection points of the notch contour line and the blade trailing edge 21 are intersection P and intersection K respectively. The intersection P is located on the side of the notch 211 close to the blade top 24, and the intersection K is located on the side of the notch 211 close to the blade root 23. The distance between the intersection P and the intersection Q is smaller than the distance between the intersection K and the intersection N. The distance between the intersection P and the intersection Q is smaller than the distance between the intersection K and the intersection N, indicating that the distance between the side of the notch contour line close to the blade top 24 and the blade top 24 is smaller than the distance between the side of the notch contour line close to the blade root 23 and the blade root 23. This ensures that the notch 211 is closer to the blade top 24 relative to the blade root 23, thereby effectively removing the inefficient area on the blade 2 and avoiding the inefficient area doing negative work to consume the positive work done by the adjacent high-efficiency blade top 24 and blade trailing edge 21. That is, by removing the inefficient area to reduce the negative work done by the blade 2, the impact of the negative work done by the inefficient area on the adjacent high-efficiency area can be effectively reduced, thereby improving the operating efficiency of the axial flow wind wheel 100.

[0052] Among them, the inefficient area refers to the area of ​​the blade 2 close to the trailing edge 21 and the blade top 24, where vortices and backflows may occur. This area will produce a negative pressure area, thereby doing negative work, consuming the positive work done by the blade top 24 and the trailing edge 21, and increasing the energy loss of the blade 2.

[0053] In the description of the present invention, “plurality” means two or more.

[0054] According to the axial flow wind wheel 100 of the embodiment of the present invention, a notch 211 is provided at the trailing edge 21 of the blade 2 of the axial flow wind wheel 100, and the notch 211 is provided closer to the blade top 24 relative to the blade root 23. In this way, the inefficient area of ​​the trailing edge 21 and the blade top 24 of the blade 2 that does negative work can be effectively removed, thereby reducing the energy loss caused by the negative work done in this inefficient area, thereby effectively improving the operating efficiency of the axial flow wind wheel 100.

[0055] Reference Figure 6-Figure 8, according to some embodiments of the present utility model, on the reference plane, with the rotation center O of the axial flow impeller 100 as the center of the circle and passing through the intersection point P, a base circle A2 is made. The radius of the base circle A2 is R2, and R2 satisfies: 0.75*R1 < R2 < 0.9*R1, where R1 is the maximum radius of the axial flow impeller 100. For example, R2 can be 0.78R1, 0.82R1, 0.85R1, 0.86R1, 0.89R1, etc. By R2 not being less than 0.75R1, it can be shown that the distance between the side of the notch 211 close to the blade tip 24 and the blade root 23 is large enough to ensure that this part of the notch 211 can effectively eliminate the negative work done by this part of the inefficient area, and thus can effectively improve the overall operating efficiency of the axial flow impeller 100; by R2 not being greater than 0.9R1, it can be avoided that the distance between the side of the notch 211 close to the blade tip 24 and the blade tip 24 is too small, reducing the air volume of the axial flow impeller 100.

[0056] By 0.75*R1 < R2 < 0.9*R1, the air volume of the axial flow impeller 100 and the energy loss of the axial flow impeller 100 can be better balanced.

[0057] Refer to Figure 6-Figure 8 , according to some embodiments of the present utility model, on the reference plane, a straight line M1 is made passing through the intersection point N. The straight line M1 is tangent to the trailing edge 21 of the blade. The point on the notch contour line farthest from the straight line M1 is point T. A straight line M2 is made passing through point T. The straight line M2 is parallel to the straight line M1. The distance between the straight line M2 and the straight line M1 is G1, and G1 satisfies: G1 < 0.3*R1, where R1 is the maximum radius of the axial flow impeller 100. For example, G1 can be 0.1*R1, 0.15*R1, 0.2*R1, 0.22*R1, 0.25*R1, etc. By G1 < 0.3*R1, the depth of the notch 211 can be restricted to better balance the air volume, noise, structural strength and energy loss of the blade 2, avoid that the notch 211 opens too deep towards the leading edge 22 of the blade, affecting the air volume of the blade 2 and increasing the noise during air flow, and also make the influence of the notch 211 on the structural strength of the blade 2 smaller.

[0058] For example, if G1 > 0.3*R1, it indicates that the notch 211 opens too deep towards the leading edge 22 of the blade, resulting in excessive cutting of the blade 2. Excessive cutting of the blade 2 easily causes the air volume of the blade 2 to decrease at the same rotational speed, and further reduces the work capacity of the wind wheel at the rated rotational speed, and also causes an increase in noise at the notch 211 at the same air volume. By G1 < 0.3*R1, while forming a notch 211 on the blade 2 to effectively reduce the energy loss of the blade 2, the influence of the notch 211 on the work capacity of the axial flow impeller 100 is small, the noise during air flow can be reduced or avoided due to the notch 211, and the influence of the notch 211 on the structural strength of the blade 2 can also be made smaller.

[0059] Refer to Figure 6-Figure 8 According to some embodiments of the present invention, on the reference surface, a base circle A2 is formed with the rotation center of the axial flow wind wheel 100 as the center O and passing through the intersection point P, and the radius of the base circle A2 is R2. A base circle A3 is formed with the rotation center of the axial flow wind wheel 100 as the center O and passing through the intersection point K, and the radius of the base circle A3 is R3. A straight line M1 is formed through the intersection point N, and the straight line M1 is tangent to the blade trailing edge 21. The point on the notch contour line farthest from the straight line M1 is point T. On the reference surface, a base circle A4 is formed with the rotation center of the axial flow wind wheel 100 as the center O and passing through point T, and the base circle A5 is formed. The radius of circle A4 is R4, and R2, R3, and R4 satisfy: (R2-R4)<(R4-R3), indicating that the distance between the deepest point of the notch 211 and the side of the notch 211 close to the blade top 24 is smaller than the distance between the deepest point of the notch 211 and the side of the notch 211 close to the blade root 23. This ensures that the deepest point of the notch 211 is biased toward the blade top 24, thereby ensuring that this part of the notch 211 can effectively eliminate the negative work done by this part of the inefficient area, thereby effectively improving the overall operating efficiency of the axial flow wind wheel 100.

[0060] Reference Figure 7-Figure 9 According to some embodiments of the present invention, a guide rib 251 is provided on the suction surface 25 of the blade 2. At least a portion of the guide rib 251 is located between the notch 211 and the blade tip 24. The guide rib 251 extends from the trailing edge 21 to the leading edge 22 of the blade 2. The guide rib 251 can enhance the overall structural strength of the blade 2 to a certain extent. The guide rib 251 can also eliminate vortex shedding generated at the blade tip 24 during rotation of the blade 2 and reduce the amount of airflow flowing back from the pressure surface 26 to the suction surface 25. The fact that at least a portion of the guide rib 251 is located between the notch 211 and the blade tip 24 can include the following situations: for example, a portion of the guide rib 251 can be located between the notch 211 and the blade tip 24; or, for another example, the entire guide rib 251 can be located between the notch 211 and the blade tip 24.

[0061] For example, while air on the surface of blade 2 moves circumferentially along blade 2, it also moves toward blade tip 24 due to centrifugal force. When air reaches blade tip 24, due to the pressure difference between negative pressure surface 25 and positive pressure surface 26, the airflow with this pressure difference after leaving blade tip 24 rotates and forms vortices upon encountering each other. These vortices then leave blade 2 and shed. Vortex shedding increases power consumption and noise, and may also cause abnormal sound issues. In the connection area between the trailing edge 21 and blade tip 24—that is, the area of ​​high negative pressure on the negative pressure surface 25 of blade 2—at least a portion of the guide rib 251 is located between the notch 211 and the blade tip 24. The guide rib 251 guides the airflow, directing it from the trailing edge 21 and inhibiting it from leaving the blade tip 24. This reduces or prevents the possibility of vortex shedding at the blade tip 24 due to airflow leaving the blade tip 24.

[0062] Optionally, the entire guide rib 251 may be in contact with the blade trailing edge 21 , or part of the guide rib 251 may be in contact with part of the blade trailing edge 21 , or the guide rib 251 may be close to the blade trailing edge 21 but not in contact with the blade trailing edge 21 .

[0063] Optionally, the material of the guide rib 251 can be consistent with that of the blade 2. In this case, the guide rib 251 can be integrally formed with the blade 2. The material of the guide rib 251 can also be inconsistent with that of the blade 2. The guide rib 251 can also be fixed to the negative pressure surface 25 by welding or other methods.

[0064] Reference Figure 7-Figure 9 According to some embodiments of the present invention, the extension direction of the guide rib 251 is consistent with the rotation direction of the axial flow wind wheel 100, so that the guide rib 251 is arc-shaped, specifically, it can be circular arc-shaped, so that the friction of the airflow when passing through the guide rib 251 is small, and thus the noise is also small.

[0065] Reference Figure 7-Figure 9 According to some embodiments of the present invention, on the reference plane, the intersection of the leading edge 22 and the blade top 24 of the blade 2 is the intersection E1, the intersection of the leading edge 22 and the blade root 23 is the intersection E2, the point of the guide rib 251 closest to the intersection E1 in the circumferential direction of the blade 2 is the point F1, a straight line S1 is drawn through the rotation center O of the axial flow wind wheel 100 and through the intersection E1, a straight line S2 is drawn through the rotation center O of the axial flow wind wheel 100 and through the intersection E2, a straight line S3 is drawn through the rotation center O of the axial flow wind wheel 100 and through the point F1, the angle between the straight line S1 and the straight line S2 is V1, the angle between the straight line S1 and the straight line S3 is V2, and V1 and V2 satisfy: V2>V1. In this way, the distance between the guide rib 251 and the intersection of the leading edge 22 and the blade top 24 in the circumferential direction of the blade 2 can be limited. While the guide rib 251 guides the airflow on the negative pressure surface 25, it can prevent the guide member from excessively extending to the leading edge. If the guide rib 251 extends excessively to the leading edge 22, this will cause excessive resistance to the airflow on the negative pressure surface 25, thereby resulting in a decrease in air volume and an increase in noise.

[0066] Reference Figure 7-Figure 9According to some embodiments of the present invention, on a reference surface, a straight line M1 is drawn through the intersection N, the straight line M1 is tangent to the blade trailing edge 21, the point on the notch contour line farthest from the straight line M1 is point T, the intersection of the leading edge 22 of the blade 2 and the blade top 24 is the intersection E1, the point of the guide rib 251 farthest from the intersection E1 in the circumferential direction of the blade 2 is point F2, a straight line S1 is drawn through the rotation center O of the axial flow wind wheel 100 and through the intersection E1, a straight line S4 is drawn through the rotation center O of the axial flow wind wheel 100 and through the intersection T, a straight line S5 is drawn through the rotation center O of the axial flow wind wheel 100 and through the intersection F2, the angle between the straight line S1 and the straight line S4 is V3, the angle between the straight line S1 and the straight line S5 is V4, and V3 and V4 satisfy: V3≤V4. Relative to the leading edge 22 of the blade, the guide rib 251 is made closer to the trailing edge 21 of the blade, and the deepest part of the notch 211 is used as the boundary, which can ensure that the deepest part of the notch 211 and the boundary determined by the rotation center of the axial flow wind wheel are within the boundary determined by the point of the guide rib 251 farthest from the leading edge 22 and the blade top 24 in the circumferential direction of the blade 2 and the rotation center O of the axial flow wind wheel 100. In this way, the guiding effect of the guide rib 251 on the airflow can be ensured, and the airflow turbulence caused by the irregular trailing edge 21 of the blade at the notch 211 can be effectively suppressed, thereby reducing noise.

[0067] Reference Figure 9 According to other embodiments of the present invention, on the rotor projection, the intersection of the trailing edge 21 and the blade top 24 of the blade 2 is the intersection point Q. On the reference surface, a straight line M1 is drawn through the intersection point N. The straight line M1 is tangent to the trailing edge 21. The point on the notch contour line farthest from the straight line M1 is point T. The intersection of the leading edge 22 of the blade 2 and the blade top 24 is the intersection point E1. The point of the guide rib 251 farthest from the intersection point E1 in the circumferential direction of the blade 2 is point F2. The rotation center O of the axial flow rotor 100 is passed through the straight line M1. A straight line S1 is drawn through the intersection E1, a straight line S4 is drawn through the rotation center of the axial flow wind wheel 100 and through the intersection T, a straight line S5 is drawn through the rotation center O of the axial flow wind wheel 100 and through the intersection F2, a straight line S6 is drawn through the rotation center O of the axial flow wind wheel 100 and through the intersection Q, the angle between the straight line S1 and the straight line S4 is V3, the angle between the straight line S1 and the straight line S5 is V4, and the angle between the straight line S1 and the straight line S6 is V5, and V3, V4, and V5 satisfy: V3≤V4≤V5. At this time, the point F2 of the guide rib 251 that is farthest from the intersection E1 in the circumferential direction of the blade 2 does not coincide with the intersection Q of the blade trailing edge 21 and the blade top 24. By V3≤V4≤V5, it can be ensured that the boundary determined by the point F2 of the guide rib 251 that is farthest from the intersection E1 in the circumferential direction of the blade 2 and the rotation center O of the axial flow wind wheel 100 is located within the boundary determined by the intersection Q of the blade trailing edge 21 and the blade top 24 and the rotation center O of the axial flow wind wheel 100, thereby avoiding an increase in the resistance to airflow due to the guide rib 251 exceeding the blade trailing edge 21.

[0068] Reference Figure 7-Figure 9According to some embodiments of the present invention, on the reference surface, the point of the guide rib 251 closest to the rotation center of the axial flow wind wheel 100 in the radial direction of the axial flow wind wheel 100 is point F3, and the rotation center of the axial flow wind wheel 100 is taken as the center O and passes through the intersection F3 to make a base circle A5, and the radius of the base circle A5 is R5. On the reference surface, the rotation center of the axial flow wind wheel 100 is taken as the center O and passes through the intersection P to make a base circle A2, and the radius of the base circle A2 is R2. R5 and R2 satisfy: R5≥R2. In the radial direction of the axial flow wind wheel 100, the guide rib 251 is located between the notch 211 and the blade top 24. In this way, the guide rib 251 can reduce the possibility of vortex shedding at the blade top 24, and can also reduce the possibility of vortex shedding at the notch 211 due to the pressure difference between the negative pressure surface 25 and the positive pressure surface 26 at the notch 211.

[0069] Reference Figure 7-Figure 9 According to some embodiments of the present invention, R5 and R2 further satisfy: (R5-R2)≤0.05*R1. In the radial direction of the axial flow wind wheel 100, the guide rib 251 is located between the notch 211 and the blade top 24 and the distance between the guide rib 251 and the notch 211 is small, ensuring that the guide rib 251 can effectively reduce the possibility of vortex shedding at the notch 211 due to the pressure difference between the negative pressure surface 25 and the positive pressure surface 26 at the notch 211, thereby reducing the noise generated by the turbulent airflow at the notch 211 caused by the irregular blade trailing edge 21.

[0070] Reference Figure 10-11 According to some embodiments of the present invention, the protrusion height of the guide rib 251 relative to the negative pressure surface 25 is H1, and H1 is ≥ 1 mm. For example, H1 can be 1 mm, 2 mm, 4 mm, 5 mm, 7 mm, etc. When H1 is ≥ 1 mm, the guide rib 251 can ensure that it guides the airflow, causing minimal turbulence on the negative pressure surface 25 to attract air to conform to the negative pressure surface 25. The guide rib also constrains the radial movement of the airflow along the blade 2, causing it to flow out through the trailing edge 21, thereby reducing the possibility of vortex shedding at the blade tip 24.

[0071] Reference Figure 10-11According to some embodiments of the present invention, the cross-section of the guide rib 251 is the guide rib cross-section, and the width of the guide rib cross-section at the intersection with the negative pressure surface 25 is W1, 2mm≤W1≤8mm. For example, W1 can be 2mm, 4mm, 5mm, 7mm, 8mm, etc. By ensuring that W1 is not less than 2mm, it can be ensured that the width of the guide rib cross-section is sufficient to ensure that the guide rib 251 has a strong structural strength; by ensuring that W1 is not greater than 8mm, it can be ensured that the guide rib 251 guides the airflow, allowing the airflow to flow as much as possible along the axial direction of the blade 2, reducing or avoiding the possibility of a second suction surface being formed at the top of the guide rib 251 in the direction of protrusion relative to the negative pressure surface 25 due to the excessive width of the guide rib 251, resulting in radial movement of the airflow at the top of the guide rib 251 in the direction of protrusion relative to the negative pressure surface 25.

[0072] By ensuring that 2mm≤W1≤8mm, the guide rib 251 has a relatively strong structural strength and can guide the airflow, so that the airflow flows as much as possible along the axial direction of the blade 2 .

[0073] Reference Figure 10-11 According to some embodiments of the present invention, the cross-section of the guide rib 251 is a guide rib cross-section, and the width of the guide rib cross-section decreases in the direction in which the guide rib 251 bulges out from the negative pressure surface 25. This reduces the area of ​​the airflow blocked by the guide rib 251 in the direction in which the guide rib 251 bulges out from the negative pressure surface 25. This reduces resistance to airflow and the degree of collision between the guide rib 251 and the airflow, allowing the airflow to flow more smoothly toward the trailing edge 21.

[0074] Optionally, the shapes of the cross sections of the guide ribs 251 may be equal or unequal. For example, there are three guide ribs 251, namely the first guide rib 251, the second guide rib 251 and the third guide rib 251. The cross section of the first guide rib 251 may be trapezoidal, the cross section of the second guide rib 251 may be triangular, the cross section of the third guide rib 251 may be circular, etc. Of course, there are many other optional combinations of the shapes of the cross sections of the guide ribs 251, which are not listed here one by one.

[0075] Reference Figure 6 、 Figure 9 and Figure 11 According to some embodiments of the present invention, a plurality of guide ribs 251 are provided, and the plurality of guide ribs 251 are arranged at intervals along the radial direction of the axial flow impeller 100. The plurality of guide ribs 251 can further enhance the overall structural strength of the blade 2 and can enhance the airflow guidance effect of the guide ribs 251, thereby further reducing the possibility of vortex shedding at the blade tip 24.

[0076] Preferably, multiple guide ribs 251 can be evenly arranged at radial intervals along the axial flow wind wheel 100, and the length of each guide rib 251 is equal. The equally distributed arc guide ribs 251 make the turbulence formed between each arc guide rib 251 have roughly the same guiding effect on the air on the negative pressure surface 25, thereby making the airflow flow smoother.

[0077] Reference Figure 10-11 According to some embodiments of the present invention, the spacing between adjacent guide ribs 251 is G2, where G2 is ≥ 2 mm. For example, G2 can be 2 mm, 3 mm, 5 mm, 7 mm, 10 mm, etc. By ensuring that G2 is ≥ 2 mm, the guide ribs 251 can ensure that the airflow is guided by the guide ribs 251, so that the airflow flows as much as possible along the axial direction of the blade 2. This reduces or avoids the possibility that a second suction surface may form at the top of the adjacent guide ribs 251 that protrudes relative to the negative pressure surface 25 due to the small distance between adjacent guide ribs 251, resulting in radial movement of the airflow at the top of the adjacent guide ribs 251 that protrude relative to the negative pressure surface 25.

[0078] Refer to the following Figures 1-11 An axial flow wind wheel 100 according to an embodiment of the present invention is described.

[0079] Reference Figure 2 、 Figure 5 and Figure 6 In this embodiment, the axial flow rotor 100 includes a hub 1 and a plurality of blades 2. The blades 2 are connected to the outer peripheral wall of the hub 1 and are spaced apart along the circumference of the hub 1. The contour edge of the blade 2 includes a leading edge 22, a blade tip 24, a trailing edge 21, and a blade root 23, which are connected end to end. The blade root 23 is connected to the hub 1. In the rotation direction of the hub 1, the leading edge 22 is located in front of the trailing edge 21. The trailing edge 21 of the blade 2 is formed with a notch 211.

[0080] A guide rib 251 is provided on the suction surface 25 of the blade 2. At least a portion of the guide rib 251 is located between the notch 211 and the blade tip 24. The guide rib 251 extends from the trailing edge 21 to the leading edge 22 of the blade 2. The extension direction of the guide rib 251 is consistent with the rotation direction of the axial flow rotor 100. There are multiple guide ribs 251, which are arranged at intervals along the radial direction of the axial flow rotor 100.

[0081] Among them, the projection of the axial flow impeller 100 on the reference plane is the impeller projection. The reference plane is perpendicular to the rotation axis of the axial flow impeller 100. On the impeller projection, the intersection point of the trailing edge 21 of the blade and the tip 24 of the blade 2 is the intersection point Q, and the intersection point of the trailing edge 21 of the blade and the root 23 of the blade 2 is the intersection point N. The contour line of the notch 211 is the notch contour line. The intersection points of the notch contour line and the trailing edge 21 are the intersection points P and K respectively. The intersection point P is located on the side of the notch 211 close to the tip 24, and the intersection point K is located on the side of the notch 211 close to the root 23. The distance between the intersection point P and the intersection point Q is less than the distance between the intersection point K and the intersection point N.

[0082] On the reference plane, a base circle A2 is made with the rotation center of the axial flow impeller 100 as the center and passing through the intersection point P. The radius of the base circle A2 is R2, and R2 satisfies: 0.75*R1 < R2 < 0.9*R1, where R1 is the maximum radius of the axial flow impeller 100.

[0083] A straight line M1 is made through the intersection point N. The straight line M1 is tangent to the trailing edge 21. The point on the notch contour line farthest from the straight line M1 is the point T. A straight line M2 is made through the point T. The straight line M2 is parallel to the straight line M1. The distance between the straight line M2 and the straight line M1 is G1, and G1 satisfies: G1 < 0.3*R1.

[0084] A base circle A2 is made with the rotation center of the axial flow impeller 100 as the center and passing through the intersection point P. The radius of the base circle A2 is R2. A base circle A3 is made with the rotation center of the axial flow impeller 100 as the center and passing through the intersection point K. The radius of the base circle A3 is R3. A straight line M1 is made through the intersection point N. The straight line M1 is tangent to the trailing edge 21. The point on the notch contour line farthest from the straight line M1 is the point T. On the reference plane, a base circle A4 is made with the rotation center of the axial flow impeller 100 as the center and passing through the point T. The radius of the base circle A4 is R4. R2, R3, and R4 satisfy: (R2 - R4) < (R4 - R3).

[0085] The intersection point of the leading edge 22 of the blade 2 and the tip 24 is the intersection point E1, and the intersection point of the leading edge 22 of the blade 2 and the root 23 is the intersection point E2. The point on the guide rib 251 closest to the intersection point E1 in the circumferential direction of the blade 2 is the point F1. A straight line S1 is made through the rotation center of the axial flow impeller 100 and through the intersection point E1. A straight line S2 is made through the rotation center of the axial flow impeller 100 and through the intersection point E2. A straight line S3 is made through the rotation center of the axial flow impeller 100 and through the point F1. The included angle between the straight line S1 and the straight line S2 is V1, and the included angle between the straight line S1 and the straight line S3 is V2. V1 and V2 satisfy: V2 > V1.

[0086] A straight line M1 is drawn through the intersection N, and the straight line M1 is tangent to the blade trailing edge 21. The point on the notch contour line farthest from the straight line M1 is point T. The intersection of the leading edge 22 of the blade 2 and the blade top 24 is the intersection E1. The point of the guide rib 251 farthest from the intersection E1 in the circumferential direction of the blade 2 is point F2. A straight line S1 is drawn through the rotation center of the axial flow wind wheel 100 and through the intersection E1. A straight line S4 is drawn through the rotation center of the axial flow wind wheel 100 and through the intersection T. A straight line S5 is drawn through the rotation center of the axial flow wind wheel 100 and through the intersection F2. The angle between the straight line S1 and the straight line S4 is V3, and the angle between the straight line S1 and the straight line S5 is V4. V3 and V4 satisfy: V3≤V4.

[0087] The point of the guide rib 251 closest to the rotation center of the axial flow wind wheel 100 in the radial direction of the axial flow wind wheel 100 is point F3, and a base circle A5 is made with the rotation center of the axial flow wind wheel 100 as the center and passing through the intersection F3. The radius of the base circle A5 is R5. On the reference surface, a base circle A2 is made with the rotation center of the axial flow wind wheel 100 as the center and passing through the intersection P. The radius of the base circle A2 is R2. R5 and R2 satisfy: R5>R2, and R5 and R2 further satisfy: (R5-R2)≤0.05*R1.

[0088] The protrusion height of the guide rib 251 relative to the negative pressure surface 25 is H1, where H1 ≥ 1 mm. The cross-section of the guide rib 251 is the guide rib cross section. The width of the guide rib cross section at the intersection with the negative pressure surface 25 is W1, where 2 mm ≤ W1 ≤ 8 mm. The width of the guide rib cross section decreases in the direction in which the guide rib 251 protrudes relative to the negative pressure surface 25. The spacing between adjacent guide ribs 251 is G2, where G2 ≥ 2 mm.

[0089] When the axial flow wind wheel 100 is working, the air flow flows in from the leading edge 22 of the blade and flows out from the trailing edge 21 of the blade. A notch 211 is provided in the area where the trailing edge 21 of the blade connects with the blade top 24. The inefficient area doing negative work in the area of ​​the trailing edge 21 and the blade top 24 can be removed, thereby reducing the energy loss caused by the negative work done in this inefficient area, thereby effectively improving the operating efficiency of the axial flow wind wheel 100; and in the radial direction of the axial flow wind wheel 100, a plurality of guide ribs 251 arranged at intervals are provided between the notch 211 and the blade top 24, which can reduce the possibility of vortex shedding at the blade top 24, and can also reduce the possibility of vortex shedding at the notch 211 due to the pressure difference between the negative pressure surface 25 and the positive pressure surface 26 at the notch 211, thereby reducing noise.

[0090] Reference Figure 2 、 Figure 4 and Figure 5 The axial flow fan according to the second embodiment of the present invention includes the axial flow fan wheel 100 according to the first embodiment of the present invention. For example, the axial flow fan includes the axial flow fan wheel 100 and a motor, and the motor is used to drive the axial flow fan wheel 100 to rotate.

[0091] According to the axial flow fan of the embodiment of the present invention, the above-mentioned axial flow wind wheel 100 is provided, and a notch 211 is provided on the trailing edge 21 of the blade 2 of the axial flow wind wheel 100, and the notch 211 is provided closer to the blade top 24 relative to the blade root 23. In this way, the inefficient area doing negative work in the trailing edge 21 and the blade top 24 of the blade 2 can be effectively removed, thereby reducing the energy loss caused by the negative work done in this inefficient area, thereby effectively improving the operating efficiency of the axial flow wind wheel 100, which is beneficial to improving the operating efficiency of the axial flow fan.

[0092] Reference Figure 2 、 Figure 4 and Figure 5 According to an embodiment of the third aspect of the present invention, an air conditioner includes an axial flow fan according to the embodiment of the second aspect of the present invention. For example, the air conditioner includes a housing assembly, an air duct assembly, and a heat exchanger assembly. The air duct assembly includes an air duct volute and the axial flow fan. The housing is formed with an air inlet and an air outlet. The air duct volute forms an air duct. The heat exchanger is disposed in the air duct. The axial flow impeller 100 is used to drive airflow from the air inlet into the housing so that the airflow exchanges heat with the heat exchanger. The airflow after heat exchange is blown toward the air outlet into the room to cool / heat the room.

[0093] According to the air conditioner of the embodiment of the present invention, the above-mentioned axial flow fan is provided, and the axial flow fan includes an axial flow wind wheel 100. A notch 211 is provided at the trailing edge 21 of the blade 2 of the axial flow wind wheel 100, and the notch 211 is provided closer to the blade top 24 relative to the blade root 23. In this way, the inefficient area doing negative work in the trailing edge 21 and the blade top 24 of the blade 2 can be effectively removed, thereby reducing the energy loss caused by the negative work done in this inefficient area, thereby effectively improving the operating efficiency of the axial flow wind wheel 100, which is beneficial to improving the overall operating efficiency of the air conditioner.

[0094] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation to the present invention.

[0095] In the description of the present invention, "first feature" and "second feature" may include one or more such features.

[0096] In the description of the present invention, a first feature being “above” or “below” a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact via another feature therebetween.

[0097] In the description of the present invention, a first feature “above”, “above” and “above” a second feature includes the first feature being directly above and obliquely above the second feature, or simply means that the first feature is horizontally higher than the second feature.

[0098] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that the specific features, structures, materials, or characteristics described in conjunction with that embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the illustrative use of the above terms does 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 any one or more embodiments or examples.

[0099] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and purpose of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. An axial flow wind wheel, characterized in that: Comprising: A hub; A plurality of blades, connected to the outer peripheral wall of the hub and arranged at intervals in the circumferential direction of the hub, and a notch is formed at the trailing edge of the blade; Wherein, the projection of the axial flow wind turbine on the reference plane is the wind turbine projection, the reference plane is perpendicular to the rotation axis of the axial flow wind turbine, on the wind turbine projection, the intersection point of the trailing edge and the tip of the blade is intersection point Q, the intersection point of the trailing edge and the root of the blade is intersection point N, the contour line of the notch is the notch contour line, the intersection points of the notch contour line and the trailing edge are intersection points P and K respectively, the intersection point P is located on the side of the notch close to the tip, the intersection point K is located on the side of the notch close to the root, and the distance between the intersection point P and the intersection point Q is less than the distance between the intersection point K and the intersection point N.

2. The axial flow wind wheel according to claim 1, characterized in that: On the reference plane, a base circle A2 is made with the rotation center of the axial flow wind turbine as the center and passing through the intersection point P, the radius of the base circle A2 is R2, and R2 satisfies: 0.75*R1 < R2 < 0.9*R1, where R1 is the maximum radius of the axial flow wind turbine.

3. The axial flow wind wheel according to claim 1, characterized in that: On the reference plane, a straight line M1 is made passing through the intersection point N, the straight line M1 is tangent to the trailing edge, the point on the notch contour line farthest from the straight line M1 is point T, a straight line M2 is made passing through the point T, the straight line M2 is parallel to the straight line M1, and the distance between the straight line M2 and the straight line M1 is G1, and G1 satisfies: G1 < 0.3*R1, where R1 is the maximum radius of the axial flow wind turbine.

4. The axial flow wind wheel according to claim 1, characterized in that: On the reference plane, a base circle A2 is made with the rotation center of the axial flow wind turbine as the center and passing through the intersection point P, the radius of the base circle A2 is R2, a base circle A3 is made with the rotation center of the axial flow wind turbine as the center and passing through the intersection point K, the radius of the base circle A3 is R3, a straight line M1 is made passing through the intersection point N, the straight line M1 is tangent to the trailing edge, the point on the notch contour line farthest from the straight line M1 is point T, on the reference plane, a base circle A4 is made with the rotation center of the axial flow wind turbine as the center and passing through the point T, the radius of the base circle A4 is R4, and R2, R3, and R4 satisfy: (R2 - R4) < (R4 - R3).

5. The axial flow wind wheel according to claim 1, characterized in that: A flow guiding rib is provided on the negative pressure surface of the blade, at least part of the flow guiding rib is located between the notch and the tip, and the flow guiding rib extends in the direction from the trailing edge to the leading edge of the blade.

6. The axial flow wind wheel according to claim 5, characterized in that: The extending direction of the flow guiding rib is the same as the rotation direction of the axial flow wind turbine.

7. The axial flow wind wheel according to claim 5, characterized in that: On the reference plane, the intersection point of the leading edge and the tip of the blade is intersection point E1, the intersection point of the leading edge and the root of the blade is intersection point E2, the point on the flow guiding rib closest to the intersection point E1 in the circumferential direction of the blade is point F1. A straight line S1 is made passing through the rotation center of the axial flow wind turbine and passing through the intersection point E1, a straight line S2 is made passing through the rotation center of the axial flow wind turbine and passing through the intersection point E2, a straight line S3 is made passing through the rotation center of the axial flow wind turbine and passing through the point F1, the included angle between the straight line S1 and the straight line S2 is V1, the included angle between the straight line S1 and the straight line S3 is V2, and V1 and V2 satisfy: V2 > V1.

8. The axial flow wind wheel according to claim 5, characterized in that: On the reference surface, a straight line M1 is drawn through the intersection point N. The straight line M1 is tangent to the trailing edge of the blade. The point on the notch contour line farthest from the straight line M1 is point T. The intersection of the leading edge of the blade and the blade top is intersection point E1. The point of the guide rib farthest from the intersection point E1 in the circumferential direction of the blade is point F2. A straight line S1 is drawn through the rotation center of the axial flow wind wheel and the intersection E1, a straight line S4 is drawn through the rotation center of the axial flow wind wheel and the intersection T, and a straight line S5 is drawn through the rotation center of the axial flow wind wheel and the intersection F2. The angle between the straight line S1 and the straight line S4 is V3, and the angle between the straight line S1 and the straight line S5 is V4. V3 and V4 satisfy: V3≤V4.

9. The axial flow wind wheel according to claim 5, characterized in that: On the reference surface, the point of the guide rib closest to the rotation center of the axial flow wind wheel in the radial direction of the axial flow wind wheel is point F3, and a base circle A5 is made with the rotation center of the axial flow wind wheel as the center and passing through the intersection F3, and the radius of the base circle A5 is R5. On the reference surface, a base circle A2 is made with the rotation center of the axial flow wind wheel as the center and passing through the intersection P, and the radius of the base circle A2 is R2, and R5 and R2 satisfy: R5≥R2.

10. The axial flow wind wheel according to claim 9, characterized in that: R5 and R2 further satisfy: (R5-R2)≤0.05*R1.

11. The axial flow wind wheel according to any one of claims 5 to 10, characterized in that: The protruding height of the guide rib relative to the negative pressure surface is H1, and H1 is ≥ 1 mm.

12. The axial flow wind wheel according to any one of claims 5 to 10, characterized in that: The cross section of the guide rib is the guide rib cross section, and the width of the guide rib cross section at the junction of the negative pressure surface is W1, 2mm≤W1≤8mm.

13. The axial flow wind wheel according to any one of claims 5 to 10, characterized in that: The cross section of the guide rib is the guide rib cross section, and the width of the guide rib cross section decreases in the convex direction of the guide rib relative to the negative pressure surface.

14. The axial flow wind wheel according to any one of claims 5 to 10, characterized in that: There are multiple guide ribs, and the multiple guide ribs are arranged at intervals along the radial direction of the axial flow wind wheel.

15. The axial flow wind wheel according to claim 14, characterized in that: The distance between adjacent guide ribs is G2, and G2≥2mm.

16. An axial flow fan, characterized in that: include: An axial flow wind wheel according to any one of claims 1 to 15.

17. An air conditioner, characterized in that: include: The axial flow fan according to claim 16.

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