Axial flow fan blade, fan assembly, air conditioner outdoor unit and air conditioner

Abstract

The present invention relates to the technical field of air conditioners, and in particular to an axial flow fan blade, a fan assembly, and an outdoor unit of an air conditioner, wherein the axial flow fan blade comprises a hub and a plurality of blades arranged on the outer side of the hub, wherein the blade comprises a first end face and a second end face arranged in opposite directions, wherein the first end face faces away from the motor connection end of the hub, and the second end face faces the motor connection end of the hub; a plurality of base circles are set with the hub center as the circle center and the radius increases or decreases in sequence, and the first end face and the second end face are respectively formed by fitting the coordinate points of the contour lines on the cross sections of the plurality of base circles. The axial flow fan blade of the present invention can significantly improve the heat exchange efficiency and reduce the noise.

Description

Technical Field

[0001] The invention belongs to the field of air conditioners, and in particular relates to an axial flow fan blade, a fan assembly, an air conditioner outdoor unit and an air conditioner. Background Art

[0002] The fan system is the main component of the outdoor unit of the air conditioner for heat dissipation and air supply. When the fan system is working, the motor drives the motor shaft to rotate and pulls the fan impeller to rotate at high speed, and converts the mechanical energy of the rotating shaft into pressure energy and kinetic energy of the air through the fan system, thereby accelerating the heat dissipation. In the above energy conversion process, there are often mechanical losses, volume losses and flow losses. The efficiency of the fan system is usually measured by the impeller efficiency (that is, the ratio of the actual effective energy obtained by the fan system to the impeller power per unit time). When the axial flow fan rotates at high speed, the aerodynamic noise composed of rotation noise and eddy noise is the main noise source of the air conditioning system. The noise level of the air conditioning system is directly related to the consumer's experience of the product, and low noise is the core competitiveness of air conditioning products. Against the background of the country's continuous improvement in the energy efficiency indicators of air conditioning systems and the increasingly stringent consumer demand for product noise, the design of a fan system with high air volume, high efficiency and low noise is of great significance.

[0003] The air conditioner outdoor unit fan system consists of a motor, a motor bracket, axial flow blades, a guide ring, and a grille. The aerodynamic performance of the axial flow blades, guide ring, and grille directly affects the heat exchange efficiency of the fan system. Based on the idea of ​​aerodynamic noise optimization, there is a lot of room for improvement in the above three components.

[0004] In view of this, the present invention is proposed. Summary of the invention

[0005] The technical problem to be solved by the present invention is to overcome the deficiencies of the prior art and provide an axial flow fan blade, a fan assembly, an outdoor heat exchanger and an air conditioner which can improve heat exchange efficiency and reduce noise.

[0006] To solve the above technical problems, the first object of the present invention is to provide an axial flow fan blade, comprising a hub and a plurality of blades arranged on the outer side of the hub, wherein the blade comprises a first end face and a second end face arranged in opposite directions, wherein the first end face is opposite to the motor connection end of the hub, and the second end face is toward the motor connection end of the hub;

[0007] A plurality of base circles with the hub center as the circle center and radii increasing or decreasing in sequence are set, and the first end face and the second end face are respectively fitted by the coordinate points of the contour lines on the cross sections of the plurality of base circles.

[0008] Further optionally, the coordinate points of the contour lines of the plurality of base circular cross sections on the first end surface satisfy the relationship:

[0009] X=A 1 Y n-1 +A 2 Y n-2 +A 3 Y n-3 +…+A n-1 Y+A n ,

[0010] X = B 1 Z n-1 +B 2 Z n-2 +B 3 Z n-3 +…+B n-1 Z+B n ;

[0011] The spatial rectangular coordinate system of the points of the contour line of the base circular cross section on the second end surface satisfies the relationship:

[0012] X=a 1 Y n-1 +a 2 Y n-2 +a 3 Y n-3 +…+a n-1 Y+a n ,

[0013] X = b 1 Z n-1 +b 2 Z n-2 +b 3 Z n-3 +…+b n-1 Z+b n ;

[0014] A 1 , A 2 , A 3 …A n 、a 1 、a 2 、a 3 …a n、 B 1 , B 2 , B 3 …B n , and b 1 , b 2 , b 3 …b n are coefficients respectively; X, Y, Z are the coordinate points of the contour line of the base circle section.

[0015] Further optionally, a first concave rib and a second concave rib are sequentially formed on the second end surface along the radial direction of the axial flow fan blade, and the first concave rib and the second concave rib are respectively bent in a direction away from the hub.

[0016] Further optionally, the blade includes a blade inner edge and a blade outer edge that are arranged oppositely, the blade inner edge is located at the connection between the blade and the hub, and the blade outer edge is away from the hub; the blade also includes a blade leading edge and a blade trailing edge that are arranged oppositely, the blade leading edge is located on the windward side of the blade, and the blade trailing edge is located on the leeward side of the blade; the distance between the blade outer edge and the center of the hub is set to R, satisfying:

[0017] The radial distance between the boundary of the first concave rib close to the wheel hub and the center of the wheel hub is greater than or equal to 0.3R; the radial distance between the boundary of the first concave rib away from the wheel hub and the center of the wheel hub is less than or equal to 0.54R;

[0018] The angle between the line connecting the boundary of the first concave rib close to the leading edge of the blade and the center of the hub and the line connecting the tip position of the leading edge of the blade and the center of the hub is greater than or equal to 42°; the angle between the line connecting the boundary of the first concave rib away from the leading edge of the blade and the center of the hub and the line connecting the tip position of the leading edge of the blade and the center of the hub is less than or equal to 103°.

[0019] Further optionally, a radial distance between a boundary of the second concave rib close to the hub and the center of the hub is greater than or equal to 0.6R; a radial distance between a boundary of the second concave rib away from the hub and the center of the hub is less than or equal to 0.76R;

[0020] The angle between the boundary of the second concave rib close to the leading edge of the blade and the line connecting the center of the hub, and the angle between the boundary of the second concave rib close to the leading edge of the blade and the line connecting the center of the hub, is greater than or equal to 32°; the angle between the boundary of the first concave rib away from the leading edge of the blade and the line connecting the center of the hub, and the angle between the boundary of the first concave rib away from the leading edge of the blade and the line connecting the center of the hub, is less than or equal to 88°.

[0021] Further optionally, the depth of the first concave rib and the second concave rib is 1.5 mm ~2.0 mm .

[0022] Further optionally, the leading edge of the blade is locally thickened, and the local thickening is smoothly transitioned to the blade through a rounded corner, with a thickness of 1.5 mm ~2 mm .

[0023] Further optionally, a sawtooth structure is formed on part or all of the trailing edges of the blades, and the sawtooth structure is a sinusoidal sawtooth; the radial distance between the end of the sawtooth structure away from the hub and the center of the hub is R s ,satisfy R s ∈[0.75R, 0.9R];

[0024] The radial distance between the end of the sawtooth structure close to the hub and the center of the hub is R e ,satisfy R e ∈[0.2R, 0.35R];

[0025] The tooth height of the sawtooth structure is H ,satisfy H ∈[12,13.5] mm ;

[0026] The tooth pitch of the sawtooth structure is S , S ∈[8,9] mm .

[0027] Further optionally, a bending structure is formed on the outer edge of the blade, and the bending structure is formed by bending part of the outer edge of the blade toward the second end face, and the first end of the bending structure is separated from the tip position of the leading edge of the blade by a set distance, and the second end of the bending structure extends to the tip position of the trailing edge of the blade.

[0028] Further optionally, the bending degree of the bending structure X satisfy: X ∈[0, 6%]; where the bending degree X = blade tip axial dimension change / hub axial height; the blade tip axial dimension change is the height difference between the first end and the second end of the bending structure;

[0029] The bending radial starting position of the bending structure Y satisfy: Y ∈[0.8R,0.9R]; where the radial starting position of the bend Y = radial position / radius of the axial flow fan blade, the radial position is the radial distance between the bending point of the bending structure and the center of the hub; the radius of the axial flow fan blade is the radial distance between the outer edge of the fan blade and the center of the hub;

[0030] The circumferential starting position of the bending structure Z satisfy: Z ∈[0°, 45°]; wherein the circumferential starting angle of the bend ZIt is the angle between the line connecting the tip position of the leading edge of the blade and the center of the hub and the line connecting the first end of the bending structure and the center of the hub.

[0031] The present invention further provides a fan assembly, which includes the axial flow fan blade described in any one of the above items.

[0032] Further optionally, the fan assembly further includes a guide ring, and the axial flow fan blade is located in the annular space formed by the guide ring; the guide ring includes a collecting part, a throat part and a diffuser part which are sequentially connected along the airflow direction;

[0033] The line shape of the collecting portion in the radial cross section of the guide ring is a circular arc; the line shape of the throat in the radial cross section of the guide ring is a straight line segment, the first end of the throat is connected to the collecting portion, the second end of the throat is connected to the diffuser, and the throat is tangent to the collecting portion and perpendicular to the radius of the guide ring; the line shape of the diffuser in the radial cross section of the guide ring is an oblique line segment.

[0034] Further optionally, the radius of the arc is R d ,satisfy: R d ∈[30,40] mm .

[0035] Further optionally, the gap between the throat and the outer edge of the blade is H d ,satisfy: H d ∈[5,10] mm .

[0036] Further optionally, the distance between the trailing edge of the blade and the second end of the throat at the closest position to the throat is H f ,satisfy: H f ∈[-15,20] mm ;

[0037] when H f When is 0, the trailing edge of the blade is closest to the throat and faces the second end; when H f When it is a negative value, the trailing edge of the blade deviates from the closest position to the throat toward the diffuser. H f When it is a positive value, the trailing edge of the blade deviates toward the collecting portion at the position closest to the throat.

[0038] Further optionally, the angle between the diffuser and the plane where the throat is located is θ ,satisfy θ ∈[6°, 10°].

[0039] The present invention further proposes an outdoor unit of an air conditioner, wherein the air conditioner comprises a shell, and the shell is provided with any one of the above-mentioned fan blades or any one of the above-mentioned fan components.

[0040] Further optionally, a ventilation hole is opened on the shell, the fan assembly is located at the ventilation hole, a grille structure is installed on the ventilation hole, the grille structure includes an outer frame and an inner frame, the outer frame is arranged in an annular shape on the peripheral wall of the ventilation hole, the inner frame is located inside the outer frame, and the area between the outer frame and the inner frame forms an air outlet area of ​​the grille structure;

[0041] The grid structure further includes a plurality of circumferential ribs, which are annularly arranged between the outer frame and the inner frame and are concentric with the outer frame. The radius of the plurality of circumferential ribs decreases from the outer frame to the inner frame, and the spacing between adjacent circumferential ribs is H t ,satisfy: H t ∈[8,12] mm .

[0042] Further optionally, the grid structure further includes a plurality of radial ribs, wherein first ends of the plurality of radial ribs are evenly arranged along the circumference of the inner frame, and second ends of the plurality of radial ribs extend from the inner frame to the outer frame and are connected to the outer frame;

[0043] The angle between the cross section of the radial rib and the plane where the ventilation hole is located is α， satisfy: α = -0.023 L 2 +0.876 L + β ± 0.0185;

[0044] in L is the minimum distance between the grille structure and the blade;

[0045] β is the outlet airflow angle, the outlet airflow angle β It is formed by fitting each radial position of the radial ribs with the corresponding air outlet direction;

[0046] The cross section of the radial ribs is any circumferential cross section between the grille inner frame and the grille outer frame.

[0047] Further optionally, the outlet airflow angleβ satisfy: β =Px 1 2 +Qx 1 -M;

[0048] Where: x 1 is the radial position of the radial rib section, the radial position x 1 = Radius R of the cross-sectional position of the radial rib i / The diameter D, P, Q and M of the outer frame are constants, and the value of P is in the range of -4938.3±5.773, the value of Q is in the range of 3042±3.185, and the value of M is in the range of -391.86±0.844.

[0049] Further optionally, the radial ribs include a straight line segment, a first arc segment and a second arc segment sequentially connected from the inner frame to the outer frame;

[0050] The first end of the straight line segment is connected to the inner frame, the center of the inner frame is located on the extension line of the straight line segment, and the second end of the straight line segment extends to 0.4R in the direction of the outer frame. g Department, R g is the radius of the outer frame;

[0051] The first end of the first arc segment is connected to the second end of the straight segment, and the second end of the first arc segment extends toward the outer frame to 0.8R g , and the first arc segment is tangent to the straight line segment;

[0052] The first end of the second arc segment is connected to the second end of the second arc segment, and the second end of the second arc segment extends toward the outer frame until it is connected to the outer frame; the second arc segment is tangent to the first arc segment; the radius of the first arc segment is set to r 1 , the radius of the second arc segment is r 2 ,satisfy: r 2 =2~3 r 1 .

[0053] The present invention also embodies an air conditioner, which includes the axial flow fan blade described in any one of the above items, or includes the fan assembly described in any one of the above items, or includes the air conditioner outdoor unit described in any one of the above items.

[0054] After adopting the above technical solution, the present invention has the following beneficial effects compared with the prior art:

[0055] 1. The axial flow fan blade proposed in the present invention is designed through parameters such as blade profile and installation angle, so that the fan blade has a higher air volume and aerodynamic efficiency at the design point, and the design of blade top bending and trailing edge serration is simultaneously adopted to effectively reduce the noise of the axial flow fan blade;

[0056] 2. The guide ring proposed in the present invention cooperates with the axial flow fan blade, and the new flow collection and pressure diffusion structure can reduce the impact of the airflow on the fan blade, reduce the leakage of the airflow on the pressure surface of the fan blade, weaken the tip vortex, convert part of the outlet dynamic pressure into static pressure, reduce the wind speed, and improve the heat exchange efficiency of the fan system. At the same time, the noise formed after the blade tip vortex is reduced and it falls off is also optimized;

[0057] 3. The air outlet grille with a gradually inclined angle proposed in the present invention cooperates with the axial flow fan blades to match the air outlet direction of the fan blades at different circumferential positions and the inclination angle of the radial ribs of the grille, and proposes unique radial divergent ribs with a gradually inclined angle. This structure can effectively optimize the air outlet flow field of the fan system, thereby improving the air volume performance of the fan system and optimizing its noise.

[0058] The specific implementation modes of the present invention are further described in detail below in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0059] The accompanying drawings are part of the present invention and are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention, but do not constitute an improper limitation of the present invention. Obviously, the drawings described below are only some embodiments. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work. In the accompanying drawings:

[0060] Figure 1 : is a schematic diagram of the axial flow fan blade structure of an embodiment of the present invention.

[0061] Figure 2 : is a three-dimensional diagram of an axial flow fan blade according to an embodiment of the present invention.

[0062] Figure 3 : is the projection surface of the blade profile contour line of the axial flow fan blade according to the embodiment of the present invention

[0063] Figure 4 : is a schematic diagram of the blade profile outline of an embodiment of the present invention.

[0064] Figure 5 : This is a characteristic diagram of the concave ribs of an embodiment of the present invention.

[0065] Figure 6 : is a stereoscopic diagram of the axial flow fan blade from another perspective of an embodiment of the present invention.

[0066] Figure 7: A schematic diagram of the blade serration structure characteristics of an embodiment of the present invention.

[0067] Figure 8 : It is a characteristic schematic diagram of the blade bending structure of an embodiment of the present invention.

[0068] Fig. 9 : is a characteristic diagram of blade tip size variation of a blade according to an embodiment of the present invention;

[0069] Fig.10 : It is a schematic diagram of the assembly of the guide ring and the axial flow fan blade according to an embodiment of the present invention.

[0070] Fig.11 :for Fig.10 DD view.

[0071] Fig.12 :for Fig.11 An enlarged view of detail view C in FIG.

[0072] Fig.13 : A schematic diagram of the cutout structure of the current collecting portion according to an embodiment of the present invention;

[0073] Fig.14 : is a schematic diagram of the structure of the guide ring of an embodiment of the present invention.

[0074] Fig.15 : It is a schematic diagram of the grille structure and axial flow fan blade assembly according to an embodiment of the present invention.

[0075] Fig.16 :for Fig.15 Side view of.

[0076] Fig.17 : is a schematic diagram of the angle between the cross section of the radial ribs of the grille structure of an embodiment of the present invention and the plane where the ventilation holes are located.

[0077] Fig.18 : is a schematic diagram of the radial ribs of the grille structure of an embodiment of the present invention.

[0078] Fig.19 : is the appearance diagram of the air conditioner outdoor unit according to an embodiment of the present invention.

[0079] Fig. 20 : is an exploded view of the outdoor unit of the air conditioner according to an embodiment of the present invention.

[0080] Fig.21 : It is the power comparison curve of the original fan system and the fan system of this embodiment under the same air volume.

[0081] Fig. 22 : is a noise comparison curve between the original fan system and the fan system of this embodiment under the same air volume.

[0082] Among them: 1-axial flow fan blade; 2-guide ring; 3-grid structure; 4-motor; 5-motor bracket; 6-condenser; 7-housing; 8-blade; 9-hub; 10-blade leading edge; 11-blade trailing edge; 12-blade outer edge; 13-blade inner edge; 14-first end face; 15-second end face; 16-serrated structure; 17-bending structure; 151-first concave rib; 152-second concave rib; 101-partial thickening of blade; 18-collecting part; 181-incision; 19-throat; 20-diffuser; 21-outer frame; 22-inner frame; 23-circumferential ribs; 24-radial ribs.

[0083] It should be noted that these drawings and textual descriptions are not intended to limit the conceptual scope of the present invention in any way, but are intended to illustrate the concept of the present invention for those skilled in the art by referring to specific embodiments. DETAILED DESCRIPTION

[0084] In the description of the present invention, it should be noted that the terms "inside", "outside", etc. 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, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0085] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "contacted", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0086] Example 1

[0087] This embodiment proposes an axial flow fan blade, such as Figure 1-Figure 9 As shown, it includes a hub 9 and a plurality of blades 8 arranged on the outer side of the hub 9. The plurality of blades 8 are evenly distributed on the outer side of the hub 9 at a certain installation angle. The plurality of blades 8 rotate within a circumference with the center of the hub 9 as the center and the length of the blade 8 as the radius. The rotation direction is as shown in FIG. Figure 1 The direction indicated by the arrow. Set the radius of the circle to R, optional R=576 mm ;like Figure 2 As shown, the thickness of the axial flow fan blade 1 is set to H. Optionally, the thickness of the blade 8 is H =203 mmThe blade 8 includes a first end face 14 and a second end face 15 which are arranged in opposite directions. The first end face 14 faces away from the motor 4 connection end of the hub 9, and the second end face 15 faces the motor 4 connection end of the hub 9. The first end face 14 is the pressure surface of the blade 8, and the second end face 15 is the suction surface of the blade 8. A plurality of base circles with the center of the hub 9 as the circle center and the radius increasing or decreasing in sequence are set, and the spacing between adjacent base circles is equal. The first end face 14 and the second end face 15 are respectively fitted by the coordinate points of the contour lines on the cross sections of the plurality of base circles.

[0088] The coordinate points of the contour lines of the plurality of base circular cross sections on the first end surface 14 satisfy the relationship: X=A 1 Y n-1 +A 2 Y n-2 +A 3 Y n-3 +…+A n-1 Y+A n , X = B 1 Z n-1 +B 2 Z n-2 +B 3 Z n-3 +…+B n-1 Z+B n ;

[0089] The spatial rectangular coordinate system of the points of the contour line of the base circular cross section on the second end surface 15 satisfies the relationship:

[0090] X=a 1 Y n-1 +a 2 Y n-2 +a 3 Y n-3 +…+a n-1 Y+a n , X = b 1 Z n-1 +b 2 Z n-2 +b 3 Z n-3 +…+b n-1 Z+b n ;

[0091] A 1 , A 2 , A 3 …A n 、a 1 、a 2 、a 3 …a n、 B 1 , B 2 , B 3 …B n, and b 1 、b 2 、b 3 …b n are coefficients respectively; X, Y, Z are the coordinate points of the contour line of the base circle section.

[0092] The number of base circles can be adjusted according to actual needs. In this embodiment, six base circles are used to describe the blade 8 of this embodiment in detail. Figure 3 and Figure 4 As shown, the first end surface 14 is formed by the six base circular sections. S 1 ~S 6 The coordinate points of the upper contour line are fitted. Figure 4 middle, is the cylindrical coordinate of the contour line of the base circular section on the first end face, The cylindrical coordinates of the contour line of the base circular section on the second end face. The spatial rectangular coordinate system of the points on the contour line of the base circular section satisfies the relationship: X = A 1 Y 5 +A 2 Y 4 +A 3 Y 3 +A 4 Y 2 +A 5 Y+A 6 , X = B 1 Z 5 +B 2 Z 4 +B 3 Z 3 +B 4 Z 2 +B 5 Z+B 6 , the optional values ​​of the coefficients in the equation are shown in Table 1:

[0093] Table 1:

[0094]

[0095] Table 2:

[0096]

[0097] The second end surface 15 of the blade 8 is also formed by the six base circle sections. S 1 ~S 6 The coordinate points of the upper contour line are fitted, and the spatial rectangular coordinate system of the points on the contour line of the base circle section satisfies the relationship: X=a 1 Y 5 +a2 Y 4 +a 3 Y 3 +a 4 Y 2 +a 5 Y+a 6 , X = b 1 Z 5 +b 2 Z 4 +b 3 Z 3 +b 4 Z 2 +b 5 Z+b 6 The optional values ​​of the coefficients in the equation are shown in Table 3 and Table 4.

[0098] Table 3:

[0099]

[0100] Table 4:

[0101]

[0102] Further optionally, if Figure 2 and Figure 5 As shown, the second end surface 15 is sequentially formed with a first concave rib 151 and a second concave rib 152 along the radial direction of the axial flow fan blade 1, and the first concave rib 151 and the second concave rib 152 are respectively bent in the direction away from the hub 9. The structures of the first concave rib 151 and the second concave rib 152 are respectively to add full fillets at both ends of a sector-shaped circular ring. The main function of this embodiment by setting the first concave rib 151 and the second concave rib 152 on the second end surface 15, that is, the suction surface, is to improve the surface load distribution, improve the blade's work capacity, remove part of the material, reduce the cost, improve the flow separation near the wall, reduce drag and increase efficiency, and reduce noise.

[0103] Further optionally, if Figure 1 , Figure 5 and Figure 6 As shown, the blade 8 includes a blade inner edge 13 and a blade outer edge 12 which are arranged oppositely, the blade inner edge 13 is located at the connection between the blade 8 and the hub 9, and the blade outer edge 12 is far away from the hub 9; the blade 8 also includes a blade leading edge 10 and a blade trailing edge 11 which are arranged oppositely, the blade leading edge 10 is located on the windward side of the blade 8, and the blade trailing edge 11 is located on the leeward side of the blade 8; the distance between the blade outer edge 12 and the center of the hub 9 is set to R, which meets the following requirements:

[0104] like Figure 5As shown, the radial distance between the boundary of the first concave rib 151 close to the hub 9 and the center of the hub 9 is greater than or equal to 0.3R; the radial distance between the boundary of the first concave rib 151 away from the hub 9 and the center of the hub 9 is less than or equal to 0.54R;

[0105] The angle between the line connecting the boundary of the first concave rib 151 close to the blade leading edge 10 and the center of the hub 9 and the line connecting the tip of the blade leading edge 10 and the center of the hub 9 is greater than or equal to 42°; the angle between the line connecting the boundary of the first concave rib 151 away from the blade leading edge 10 and the center of the hub 9 and the line connecting the tip of the blade leading edge 10 and the center of the hub 9 is less than or equal to 103°.

[0106] Further optionally, if Figure 5 As shown, the radial distance between the boundary of the second concave rib 152 close to the hub 9 and the center of the hub 9 is greater than or equal to 0.6R; the radial distance between the boundary of the second concave rib 152 away from the hub 9 and the center of the hub 9 is less than or equal to 0.76R;

[0107] The angle between the boundary of the second concave rib 152 close to the blade leading edge 10 and the line connecting the center of the hub 9, and the angle between the boundary of the blade leading edge 10 and the line connecting the center of the hub 9, and the angle between the boundary of the first concave rib 151 away from ... is less than or equal to 88°.

[0108] Further optionally, the depth of the first concave rib 151 and the second concave rib 152 is 1.5 mm ~2 mm .

[0109] Further optionally, if Figure 1 , Figure 5-Figure 8 As shown, the leading edge 10 of the blade is the end of the blade 8 separating the inlet airflow, and forms a structural feature of "blunt head and pointed tail" with the trailing edge 11 of the blade, that is, a local thickening 101 of the blade is designed at the leading edge 10 of the blade, the thickness of the blade 8 at the leading edge 10 of the blade is greater than the thickness of the blade 8 at the trailing edge 11 of the blade, and the local thickening 101 and the blade 8 are smoothly transitioned through a rounded corner, and the thickness of the local thickening 101 is 1.5 mm ~2 mm The structure complies with the low-speed aerodynamic characteristics, can increase the strength of blade 8 and suppress the leading edge separation vortex, and reduce the flutter of the blade tip.

[0110] Further optionally, if Figure 1-Figure 3 , Figure 5-Figure 9As shown, a sawtooth structure 16 is formed on part or all of the trailing edge 11 of the blade, and the sawtooth structure 16 is a sinusoidal sawtooth. In this embodiment, by providing a sawtooth structure 16 on the trailing edge 11 of the blade, the low-frequency, large-scale trailing edge shedding vortex can be reduced to a high-frequency, small-scale vortex structure, and the scattering of noise can be enhanced, thereby achieving a noise reduction effect. Compared with other types of sawtooth structures 16, the sinusoidal sawtooth has a higher improvement in the heat exchange efficiency of the blade 8, and the sinusoidal sawtooth has a higher fit with the fan blade, and the noise is significantly improved when the air volume loss is small.

[0111] Further optionally, if Figure 7 As shown, the radial distance between the end of the sawtooth structure 16 away from the hub 9 and the center of the hub 9 is R s ,satisfy R s ∈[0.75R, 0.9R], preferred R s =0.8R; the radial distance from the end of the sawtooth structure 16 close to the hub 9 to the center of the hub 9 is Re ,satisfy R e ∈[0.2R, 0.35R], preferably R e =0.25R; the tooth height of the sawtooth structure 16 is H ,satisfy H ∈[12,13.5] mm , preferably H =13.5 mm ; The pitch of the sawtooth structure 16 is S , S ∈[8,9] mm , preferably S =9 mm Each characteristic parameter within the above range can achieve better noise reduction effect.

[0112] Further optionally, if Figure 7-Figure 9 As shown, a bending structure 17 is formed on the outer edge 12 of the blade. The bending structure 17 is formed by bending a portion of the outer edge 12 of the blade toward the second end surface 15. The first end of the bending structure 17 is separated from the tip of the leading edge 10 of the blade by a set distance, and the second end of the bending structure 17 extends to the tip of the trailing edge 11 of the blade. The characteristics of the bending structure 17 are determined by the degree of bending. X , bending radial starting position Y , Bending circumferential starting position Z Determine the bending degree of the bending structure 17 X satisfy: X ∈[0, 6%], preferred X =6%; among which, the bending degree X= blade tip axial dimension change / hub axial height; blade tip axial dimension change is the height difference between the first end and the second end of the bending structure 17; bending radial starting position of the bending structure 17 Y satisfy: Y ∈[0.8R,0.9R], preferably Y=0.8R; where the radial starting position of the bend Y = radial position / radius of the axial flow fan blade 1, where the radial position is the radial distance between the bending point of the bending structure 17 and the center of the hub 9; the radius of the axial flow fan blade 1 is the radial distance between the outer edge of the fan blade and the center of the hub 9; the circumferential starting position of the bending structure 17 Z satisfy: Z ∈[0°, 45°], preferred Z =10°; where the bending circumferential starting angle Z It is the angle between the line connecting the tip of the leading edge 10 of the blade and the center of the hub 9 and the line connecting the first end of the bending structure 17 and the center of the hub 9 .

[0113] The benefit of setting a bending structure 17 on the outer edge 12 of the blade in this embodiment is that the blade tip leakage vortex and the blade tip vortex are weakened; the size parameters of the bending structure 17 are subjected to multiple rounds of iterative optimization design to obtain a preferred range of bending parameters that can achieve optimized blade performance, while also taking into account the errors caused by production and assembly differences. The key point is that the bending degree, the radial starting position of the bend, and the circumferential starting position of the bend must all meet the range at the same time to achieve the performance optimization effect of the axial flow blade 1.

[0114] Since the impeller is the core component of the outdoor axial flow fan system of the air conditioner, it is usually composed of a hub 9 and blades 8, among which the design and optimization of the blades 8 are the main contents of the fan system design. The three-dimensional curved blade 8 of this embodiment is usually formed by lofting a plurality of blade profiles with different chord lengths, curvatures, relative thicknesses (the above three are blade profile geometric parameters) and installation angles. During the design process, after determining the number of blades 8, hub 9 ratio and other parameters, it is usually necessary to use computational fluid dynamics combined with experimental measurement methods to carefully design the blade profile geometric parameters and installation angles at different positions of the fan blades. Well-designed blades 8 usually have a smaller flow separation near the design point and have higher aerodynamic efficiency while meeting performance requirements such as flow and pressure. At the same time, in order to further reduce the aerodynamic noise of blade 8 and improve efficiency, blade 8 is usually partially optimized for aerodynamic modification, such as locally thickening the leading edge to increase strength and suppress the leading edge separation vortex and reduce tip flutter; bending the blade tip to weaken the tip leakage vortex and tip vortex; applying sawtooth to the trailing edge to reduce the low-frequency and large-scale trailing edge shedding vortex to a high-frequency and small-scale vortex structure and enhance noise scattering. The application of the above noise reduction design means and parameter optimization usually need to be matched with the design conditions of blade 8, and the optimal solution can be obtained through repeated iterations.

[0115] Example 2

[0116] This embodiment also provides a fan assembly, which includes the axial flow fan blade 1 of the above embodiment 1. Figure 10-Figure 14 As shown, the fan assembly of this embodiment includes a guide ring 2, and the axial flow fan blade 1 is located in the annular space formed by the guide ring 2; Fig.12 As shown, the guide ring 2 includes a collecting portion 18, a throat portion 19 and a diffuser 20 which are sequentially connected along the airflow direction; the guide ring 2 is a semi-closed guide ring 2, that is, the guide ring 2 only covers a part of the axial flow fan blade 1, and the airflow direction flows from the collecting portion 18 to the diffuser 20; the design of the guide ring 2 structure complies with the air outlet velocity streamline result obtained by simulation, and the collecting portion 18 is the air inlet, where the airflow velocity direction changes, and the transition through the arc segment can attenuate the air reflux and improve the flow field.

[0117] like Fig.12 As shown, the line shape of the collector 18 in the radial section of the guide ring 2 is an arc; the line shape of the throat 19 in the radial section of the guide ring 2 is a straight line segment, the first end of the throat 19 is connected to the collector 18, the second end of the throat 19 is connected to the diffuser 20, and the throat 19 is tangent to the collector 18 and perpendicular to the radius of the guide ring 2; the line shape of the diffuser 20 in the radial section of the guide ring 2 is an oblique line segment. The contact position between the collector 18 and the throat 19 is designed to be tangent, which can effectively reduce the intake resistance and optimize its intake aerodynamic performance.

[0118] Further optionally, if Fig.12 As shown, the rear end of the diffuser 20 is a folded edge, which is designed with a snap-fit ​​and screw hole structure, and is fixedly connected to the housing 7 through the structure.

[0119] Further optionally, in order to meet the installation size and match the condenser 6 and the middle partition, the guide ring 2 is closely fitted with the middle partition and the condenser 6 to ensure that the fan system has smooth air intake without backflow and vortex, and the fan inlet area is increased to the maximum extent, and symmetrical cutouts 181 are set at the air inlet end of the collector 18, such as Fig.13 and Fig.14 shown.

[0120] Further optionally, if Fig.12 As shown, the radius of the arc is R d ,satisfy: R d ∈[30,40] mm , preferably R d =40 mm The arc radius in this range has a good flow collection effect, can optimize the flow field, and achieve the optimization of the aerodynamic performance of the guide ring 2.

[0121] Further optionally, if Fig.10 As shown, the gap between the throat 19 and the outer edge 12 of the blade is H d ,satisfy: H d ∈[5,10] mm , preferably H d =8 mm Theoretical tip clearance H d The smaller the gap, the more beneficial it is to reduce the leakage of airflow on the pressure surface. However, there will be tolerances in the manufacture of the fan blades and the assembly of the system. If the blade tip gap is small, it may increase the difficulty of production and assembly. Therefore, it is limited by the actual production accuracy limit and the deformation of the blade 8 when it rotates at high speed. The blade tip gap can be moderate. The specific situation is determined by the actual fan blade material and size used. The blade tip gap selected in this embodiment is the optimal size that meets the above-mentioned strength requirements. On the premise of ensuring the performance of the fan blade, the blade tip gap is relaxed as much as possible to increase the operating space for production and assembly.

[0122] Further optionally, if Fig.11 As shown, the distance between the blade trailing edge 11 and the second end of the throat 19 at the position closest to the throat 19 is H f ,satisfy: H f ∈[-15,20] mm , preferably H f = 10 mm ;when H f When it is 0, the blade trailing edge 11 is closest to the throat 19 and faces the second end; H f When the value is negative, the blade trailing edge 11 deviates from the throat 19 to the diffuser 20. H f When it is a positive value, the blade trailing edge 11 deviates toward the collecting portion 18 at the position closest to the throat 19 .

[0123] The axial position relationship between the throat 19 and the axial flow fan blade 1 is as follows: Fig.11 As shown, the distance between the highest position of the trailing edge of the fan blade and the rear end of the throat is H f , H f ∈[-15,20] mm , preferably H f = 10 mmThis position is also limited by the distance between the leading edge of the blade tip and the rear end of the motor 4. H s In order to prevent the fan blades from interfering with the bracket after high-speed rotation and deformation, H s ≥ 10 mm , that is, in satisfying H s On the premise of H f You can select any value within the range. H f The simulation results of size changes are shown in Table 5. H f When the value is negative, the blade trailing edge 11 deviates from the throat 19 to the diffuser 20. H f When is a positive value, the blade trailing edge 11 deviates from the collector 18 at the position closest to the throat 19. H f When it is a negative value, the air volume of the fan system is greatly attenuated and the efficiency is low, so H f The verification results are shown in Table 6. The air volume of the fan system is not much different, but the noise level has advantages and disadvantages. H f = 10 mm The effect is best when

[0124] Table 5: Simulation results of different distances Hf between the trailing edge of the blade and the rear end of the throat

[0125]

[0126] Table 6 Test results of different distances Hf between the trailing edge of the blade and the rear end of the throat

[0127]

[0128] Further optionally, the angle between the diffuser 20 and the plane where the throat 19 is located is θ ,satisfy θ ∈[6°, 10°].

[0129] The guide ring 2 is one of the core components of the air conditioner outdoor unit fan system. It is usually composed of a collector 18, a throat 19, and a diffuser. Its function is to moderate the wind speed of the fan blades, block the leakage of air outflow from the blade surface, limit the development of blade tip vortices and reduce the outlet wind speed. Its structural form and the coordination relationship with the fan blades will directly affect the air volume and noise of the fan system, and thus determine the heat exchange efficiency of the unit and the after-sales sound quality experience.

[0130] Example 3

[0131] The third object of this embodiment also provides an air conditioner outdoor unit, such as Figure 18-Figure 20 As shown, the air conditioner includes a housing 7, and the fan assembly of Example 2 is arranged inside the housing 7.

[0132] The air conditioner outdoor unit of this embodiment includes an axial flow fan blade 1, a guide ring 2, a grille, a motor 4, a motor bracket 5, a condenser 6, and a shell 7. The axial flow fan blade 1 is mounted on the motor 4, the motor 4 is mounted on the motor bracket 5, the motor bracket 5 is connected and fixed to the condenser 6 and the shell 7, the guide ring 2 is mounted inside the shell 7, coaxial with the axial flow fan blade 1, and the grille is mounted outside the shell 7, coaxial with the axial flow fan blade 1;

[0133] Further optionally, a ventilation hole is opened on the housing 7, the fan assembly is located at the ventilation hole, and a grille structure 3 is installed on the ventilation hole, such as Fig.15 Fig.18 As shown, the grille structure 3 includes an outer frame 21 and an inner frame 22. The outer frame 21 is arranged in an annular shape on the peripheral wall of the ventilation hole, and the inner frame 22 is located inside the outer frame 21. The area between the outer frame 21 and the inner frame 22 forms the air outlet area of ​​the grille structure 3.

[0134] like Fig.15 As shown, the grid structure 3 further includes a plurality of circumferential ribs 23, which are arranged in a ring shape concentric with the outer frame 21 between the outer frame 21 and the inner frame 22, and the radius of the plurality of circumferential ribs 23 decreases from the outer frame 21 to the inner frame 22, and the spacing between adjacent circumferential ribs 23 is H t ,satisfy: H t ∈[8,12] mm , preferably H t =9.8 mm .H t Determined by actual needs, in order to reduce wind resistance and under the premise of meeting safety regulations, the thickness of the circumferential ribs 23 should be as small as possible and the spacing should be as large as possible.

[0135] Further optionally, if Fig.15 As shown, the grille structure 3 further includes a plurality of radial ribs 24, the first ends of which are evenly arranged along the circumference of the inner frame 22, and the second ends of which extend from the inner frame 22 to the outer frame 21 and are connected to the outer frame 21; the angle between the cross section of the radial rib 24 and the plane where the ventilation hole is located is α ,like Fig.17 As shown, the radial ribs 24 are formed by scanning the cross-section sketch according to the guide line sketch, wherein the inclination angle of the cross-section sketch is α That is, the angle between the cross section of the radial rib 24 and the plane where the ventilation hole is located.α ;satisfy: α = -0.023 L 2 + 0.876 L + β ± 0.0185; where L is the minimum distance between the grille structure 3 and the blade 8, such as Fig.16 As shown; β is the outlet airflow angle, outlet airflow angle β The radial positions of the radial ribs 24 are fitted with the corresponding air outlet directions; the cross section of the radial ribs 24 is any circular cross section between the inner frame and the outer frame of the grille. β satisfy: β =Px 1 2 +Qx 1 -M; where: x 1 is the radial position of the radial rib 24, and the radial position x 1 = Radius of the cross-sectional position of the radial rib 24 Ri / The diameter D, P, Q and M of the outer frame 21 are constants, and the value of P is within the range of -4938.3±5.773, the value of Q is within the range of 3042±3.185, and the value of M is within the range of -391.86±0.844.

[0136] Several groups of inclination angles of this embodiment are obtained by calculation, and the air volume and total pressure efficiency data are compared by simulation calculation. α The simulation results are shown in Table 7. The radial rib 24 has an inclination angle of α The test data is shown in Table 8. It can be seen from Table 8 that at the design speed point, the air volume and efficiency are improved after the angle is changed to a variable inclination angle. The better unit solution is taken for verification. For the fan system described in this embodiment, the grille inclination angle α for G The noise and air volume optimization effect is most obvious when the grille angle is 56-66 (the inner frame of the grille is 56°, the middle is 66°, and the outer frame is 56°). Compared with G59 (the original grille angle is 59°), the air volume is increased by 20% at the same speed. m 3 / h , the noise is reduced by 0.94 dB(A) .

[0137] Table 7: Inclination angle of radial rib 24 α Simulation Results

[0138]

[0139] Table 8: Inclination angle of radial rib 24 α Test Data

[0140]

[0141] Further optionally, if Fig.18 As shown, the radial rib 24 includes a straight line segment, a first arc segment and a second arc segment connected in sequence from the inner frame 22 to the outer frame 21; the first end of the straight line segment is connected to the inner frame 22, the center of the inner frame 22 is located on the extension line of the straight line segment, and the second end of the straight line segment extends to 0.4 R g Department, R g The first end of the first arc segment is connected to the second end of the straight line segment, and the second end of the first arc segment extends toward the outer frame 21 to 0.8 R g The first arc segment is tangent to the straight line segment; the first end of the second arc segment is connected to the second end of the second arc segment, and the second end of the second arc segment extends toward the outer frame 21 until it is connected to the outer frame 21; the second arc segment is tangent to the first arc segment; the radius of the first arc segment is set to r 1 , the radius of the second arc segment is r 2 ,satisfy: r 2 =2~3 r 1 .

[0142] The structure of the divergent ribs of this embodiment is obtained by simulating velocity streamlines to obtain the rotation direction and approximate profile of the air outlet. Based on the profile and experimental verification, the optimal divergent rib structure can be obtained.

[0143] Further optionally, the front end of the outer frame 21 is a folded edge, which is designed with a buckle and screw hole structure, and is fixedly connected to the shell 7 through the structure.

[0144] The grille structure 3 serves to separate the fan from the outside and guide the air flow. However, the existence of the grille structure 3 will seriously affect the wind resistance of the system, resulting in a problem of reduced air volume and increased noise. Tests have found that the use of the grille structure 3 reduces the air volume of the fan system by 7% to 8% and increases the noise by about 3%. dB(A), among which the rib structure setting of the grille structure 3 is an important factor affecting the noise and air volume of the fan system. Through research, it is found that the air outlet direction after passing through the rotating fan blades is spirally divergent. In order to meet the smoothness of the air outlet, most designs of the grille structure 3 abandon the original square horizontal and vertical air outlet grilles, and all adopt circular ring-shaped air outlet grilles with divergent ribs. This rib structure can optimize the flow field of the fan system's air outlet to a certain extent, but the inclination angle of the divergent ribs also has a decisive influence on the air outlet flow field. Based on the simulation study of the air outlet speed of the fan system, we obtained that the air outlet direction after passing through the rotating axial flow fan blades 1 is spirally divergent, and from the center of the fan to the top of the blade, the direction of the air outlet speed will also change with the change of the circumferential position.

[0145] The matching scheme of the fan blade, the guide ring 2, and the grille structure 3 in the outdoor unit of the air conditioner of this embodiment can obtain a fan system with obvious aerodynamic performance advantages. The test data of the original fan system are shown in Table 9, and the test data of the fan system of the embodiment are shown in Table 10. The power comparison curve of the original fan system and the fan system of this embodiment under the same air volume is shown in Fig.21 As shown, the noise comparison curve of the original fan system and the fan system of this embodiment under the same air volume is as follows Fig. 22 shown.

[0146] Table 9 Original fan system test data

[0147]

[0148] Table 10 Test data of fan system in the embodiment

[0149]

[0150] From the experimental data in Tables 9 and 10, and Fig.21 and Fig. 22 The comparison curve shows that the fan system performance of this embodiment is 50-75% lower than the input power value of the motor 4 of the original fan system under the same air volume. W Under the same air volume conditions, the fan system described in the embodiment reduces the noise value by 1~1.5 compared with the original fan system. dB (A). The implementation data show that the fan system of this embodiment has the benefit of significantly improving the heat exchange efficiency of the air conditioner and reducing the noise of the whole machine, and can effectively solve the problem of large air volume attenuation and high noise of the original fan system.

[0151] Example 4

[0152] This embodiment also embodies an air conditioner, which includes the axial flow fan blade 1 of embodiment 1, or includes the fan assembly of embodiment 2, or the air conditioner outdoor unit of embodiment 3.

[0153] The above is only a preferred embodiment of the present invention, and does not limit the present invention in any form. Although the present invention has been disclosed as a preferred embodiment, it is not used to limit the present invention. Any technician familiar with this patent can make some changes or modify the technical contents suggested above into equivalent embodiments without departing from the scope of the technical solution of the present invention. However, any simple modification, equivalent change and modification made to the above embodiments according to the technical essence of the present invention without departing from the content of the technical solution of the present invention still fall within the scope of the solution of the present invention.

Claims

1. An axial flow fan blade, It is characterized in that It comprises a hub and a plurality of blades arranged on the outer side of the hub, wherein the blade comprises a first end face and a second end face arranged in opposite directions, the first end face is opposite to the motor connection end of the hub, and the second end face is toward the motor connection end of the hub; A plurality of base circles with the hub center as the circle center and radii increasing or decreasing in sequence are set, and the first end surface and the second end surface are respectively formed by fitting the coordinate points of the contour lines on the cross sections of the plurality of base circles; The coordinate points of the contour lines of the plurality of base circular cross sections on the first end surface satisfy the relationship: X=A 1 Y n-1 +A 2 Y n-2 +A 3 Y n-3 +…+A n-1 Y+A n ,X=B 1 Z n-1 +B 2 Z n-2 +B 3 Z n-3 +…+B n-1 Z+B n ; The spatial rectangular coordinate system of the points of the contour line of the base circular cross section on the second end surface satisfies the relationship: X=a 1 AND n-1 +a 2 AND n-2 +a 3 AND n-3 +…+a n-1 And+a n , X= b 1 Z n-1 +b 2 Z n-2 +b 3 Z n-3 +…+b n-1 Z+b n ; A 1 , A 2 , A 3 …A n 、a 1 、a 2 、a 3 …a n、 B 1 , B 2 , B 3 …B n , and b 1 、b 2 、b 3 …b n are coefficients respectively; X, Y, Z are the coordinate points of the contour line of the base circle section.

2. An axial flow fan blade according to claim 1, It is characterized in that The second end surface is sequentially formed with a first concave rib and a second concave rib along the radial direction of the axial flow fan blade, and the first concave rib and the second concave rib are respectively bent in a direction away from the hub.

3. An axial flow fan blade according to claim 2, It is characterized in that The blade comprises an inner edge and an outer edge of the blade which are arranged opposite to each other, wherein the inner edge of the blade is located at the connection between the blade and the hub, and the outer edge of the blade is away from the hub; the blade further comprises a leading edge and a trailing edge of the blade which are arranged opposite to each other, wherein the leading edge of the blade is located at the windward side of the blade, and the trailing edge of the blade is located at the leeward side of the blade; and the distance between the outer edge of the blade and the center of the hub is set to R, satisfying: The radial distance between the boundary of the first concave rib close to the wheel hub and the center of the wheel hub is greater than or equal to 0.3R; the radial distance between the boundary of the first concave rib away from the wheel hub and the center of the wheel hub is less than or equal to 0.54R; The angle between the line connecting the boundary of the first concave rib close to the leading edge of the blade and the center of the hub and the line connecting the tip position of the leading edge of the blade and the center of the hub is greater than or equal to 42°; the angle between the line connecting the boundary of the first concave rib away from the leading edge of the blade and the center of the hub and the line connecting the tip position of the leading edge of the blade and the center of the hub is less than or equal to 103°.

4. An axial flow fan blade according to claim 3, It is characterized in that The radial distance between the boundary of the second concave rib close to the wheel hub and the center of the wheel hub is greater than or equal to 0.6R; the radial distance between the boundary of the second concave rib away from the wheel hub and the center of the wheel hub is less than or equal to 0.76R; The angle between the boundary of the second concave rib close to the leading edge of the blade and the line connecting the center of the hub, and the angle between the boundary of the second concave rib close to the leading edge of the blade and the line connecting the center of the hub, is greater than or equal to 32°; the angle between the boundary of the first concave rib away from the leading edge of the blade and the line connecting the center of the hub, and the angle between the boundary of the first concave rib away from the leading edge of the blade and the line connecting the center of the hub, is less than or equal to 88°.

5. An axial flow fan blade according to claim 3, It is characterized in that The depth of the first concave rib and the second concave rib is 1.5 mm ~2.0 mm .

6. An axial flow fan blade according to claim 3, It is characterized in that The leading edge of the blade is locally thickened, and the local thickening is smoothly transitioned to the blade through a rounded corner, with a thickness of 1.5 mm ~2 mm .

7. An axial flow fan blade according to claim 6, It is characterized in that A sawtooth structure is formed on part or all of the trailing edges of the blades, and the sawtooth structure is a sinusoidal sawtooth; the radial distance between the end of the sawtooth structure away from the hub and the center of the hub is R s ,satisfy R s ∈[0.75R, 0.9R]; The radial distance between the end of the sawtooth structure close to the hub and the center of the hub is R e ,satisfy R e ∈[0.2R, 0.35R]; The tooth height of the sawtooth structure is H ,satisfy H ∈[12,13.5] mm ; The tooth pitch of the sawtooth structure is S , S ∈[8,9] mm .

8. An axial flow fan blade according to claim 3, It is characterized in that A bending structure is formed on the outer edge of the blade, and the bending structure is formed by bending part of the outer edge of the blade toward the second end face. The first end of the bending structure is separated from the tip position of the leading edge of the blade by a set distance, and the second end of the bending structure extends to the tip position of the trailing edge of the blade.

9. An axial flow fan blade according to claim 8, It is characterized in that The bending degree X of the bending structure satisfies: X ∈[0, 6%]; where the bending degree X = blade tip axial dimension change / hub axial height; the blade tip axial dimension change is the height difference between the first end and the second end of the bending structure; The bending radial starting position Y of the bending structure satisfies: Y ∈[0.8R,0.9R]; where the radial starting position of the bend Y = radial position / radius of the axial flow fan blade, the radial position is the radial distance between the bending point of the bending structure and the center of the hub; the radius of the axial flow fan blade is the radial distance between the outer edge of the fan blade and the center of the hub; The circumferential starting position Z of the bending structure satisfies: Z ∈[0°, 45°]; wherein the circumferential starting angle Z of the bending is the angle between a line connecting the tip position of the leading edge of the blade and the center of the hub and a line connecting the first end of the bending structure and the center of the hub.

10. A fan assembly, It is characterized in that The fan assembly includes the axial flow fan blade according to any one of claims 1-9.

11. A fan assembly according to claim 10, It is characterized in that The fan assembly further includes a guide ring, and the axial flow fan blade is located in the annular space formed by the guide ring; the guide ring includes a collector, a throat and a diffuser connected in sequence along the airflow direction; The line shape of the collecting portion in the radial cross section of the guide ring is a circular arc; the line shape of the throat in the radial cross section of the guide ring is a straight line segment, the first end of the throat is connected to the collecting portion, the second end of the throat is connected to the diffuser, and the throat is tangent to the collecting portion and perpendicular to the radius of the guide ring; the line shape of the diffuser in the radial cross section of the guide ring is an oblique line segment.

12. A fan assembly according to claim 11, It is characterized in that The radius of the arc is R d ,satisfy: R d ∈[30,40] mm .

13. A fan assembly according to claim 12, It is characterized in that The gap between the throat and the outer edge of the blade is H d ,satisfy: H d ∈[5,10] mm .

14. A fan assembly according to claim 13, It is characterized in that The distance between the trailing edge of the blade and the second end of the throat at the closest position to the throat is H f ,satisfy: H f ∈[-15,20] mm ; when H f When is 0, the trailing edge of the blade is closest to the throat and faces the second end; when H f When it is a negative value, the trailing edge of the blade deviates from the closest position to the throat toward the diffuser. H f When it is a positive value, the trailing edge of the blade deviates toward the collecting portion at the position closest to the throat.

15. A fan assembly according to claim 14, It is characterized in that The angle between the diffuser and the plane where the throat is located is θ ,satisfy θ ∈[6°, 10°].

16. An outdoor unit of an air conditioner, It is characterized in that The air conditioner comprises a shell, in which the axial flow fan blade according to any one of claims 1 to 9 or the fan assembly according to any one of claims 10 to 15 is arranged.

17. An air conditioner outdoor unit according to claim 16, It is characterized in that The housing is provided with a ventilation hole, the fan assembly is located at the ventilation hole, a grille structure is installed on the ventilation hole, the grille structure includes an outer frame and an inner frame, the outer frame is arranged in an annular shape on the peripheral wall of the ventilation hole, the inner frame is located inside the outer frame, and the area between the outer frame and the inner frame forms an air outlet area of ​​the grille structure; The grid structure further includes a plurality of circumferential ribs, which are annularly arranged between the outer frame and the inner frame and are concentric with the outer frame. The radius of the plurality of circumferential ribs decreases from the outer frame to the inner frame, and the spacing between adjacent circumferential ribs is H t ,satisfy: H t ∈[8,12] mm .

18. An air conditioner outdoor unit according to claim 17, It is characterized in that The grid structure further includes a plurality of radial ribs, wherein first ends of the plurality of radial ribs are evenly arranged along the circumference of the inner frame, and second ends of the plurality of radial ribs extend from the inner frame to the outer frame and are connected to the outer frame; The angle between the cross section of the radial rib and the plane where the ventilation hole is located is α， satisfy: α = -0.023 L 2 +0.876 L + β ± 0.0185; in L is the minimum distance between the grille structure and the blade; β is the outlet airflow angle, the outlet airflow angle β It is formed by fitting each radial position of the radial ribs with the corresponding air outlet direction; The cross section of the radial ribs is any circumferential cross section between the grille inner frame and the grille outer frame.

19. An air conditioner outdoor unit according to claim 18, It is characterized in that The outlet airflow angle β satisfy: β =Px 1 2 +Qx 1 -M; Where: x 1 is the radial position of the radial rib section, the radial position x 1 = Radius R of the cross-sectional position of the radial rib i / The diameter D, P, Q and M of the outer frame are constants, and the value of P is in the range of -4938.3±5.773, the value of Q is in the range of 3042±3.185, and the value of M is in the range of -391.86±0.

844.

20. An air conditioner outdoor unit according to claim 19, It is characterized in that The radial ribs include a straight line segment, a first arc segment and a second arc segment sequentially connected from the inner frame to the outer frame; The first end of the straight line segment is connected to the inner frame, the center of the inner frame is located on the extension line of the straight line segment, and the second end of the straight line segment extends to 0.4 R g Department, R g is the radius of the outer frame; The first end of the first arc segment is connected to the second end of the straight line segment, and the second end of the first arc segment extends toward the outer frame to 0.8 R g , and the first arc segment is tangent to the straight line segment; The first end of the second arc segment is connected to the second end of the second arc segment, and the second end of the second arc segment extends toward the outer frame until it is connected to the outer frame; the second arc segment is tangent to the first arc segment; the radius of the first arc segment is set to r 1 , the radius of the second arc segment is r 2 ,satisfy: r 2 =2~3 r 1 .

21. An air conditioner, It is characterized in that It includes the axial flow fan blade described in any one of claims 1-9, or the fan assembly described in any one of claims 10-15, or the air conditioner outdoor unit described in any one of claims 16-20.

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