Axial flow fan blade for axial flow fan, axial flow fan, motor support, axial flow fan assembly and air conditioner

Abstract

The utility model provides an axial flow fan blade for an axial flow fan, the axial flow fan, a motor support, an axial flow fan assembly and an air conditioner, and belongs to the field of air conditioners. The axial flow fan blade comprises an impeller, the impeller comprises impeller blades, each impeller blade is provided with an inner edge connected with the outer periphery of an impeller hub, an outer edge opposite to the inner edge, a front edge and a tail edge, the front edge and the tail edge are arranged between the inner edge and the outer edge, and the area of each impeller blade is gradually increased from one side of the inner edge to one side of the outer edge. The thicknesses of the impeller blades are gradually reduced from the inner edge side to the outer edge side; at least one convex part and at least one concave part are formed on the tail edge of the impeller blade, the at least one convex part is arranged close to the inner edge of the impeller blade, and the at least one concave part is arranged close to the outer edge of the impeller blade; wherein the protruding parts close to the inner edges of the impeller blades are used for increasing the air flow generated at the inner edge positions of the impeller blades, and the sunken parts close to the outer edges of the impeller blades are used for reducing separation vortexes and wake vortexes generated at the outer edge positions of the impeller blades.

Description

Technical Field

[0001] The utility model relates to the technical field of air conditioners, in particular to an axial flow impeller for an axial flow fan, an axial flow fan, a motor bracket, an axial flow fan assembly and an air conditioner. Background Art

[0002] High temperature weather has swept across the globe, and people's demand for cooling capacity in high temperature weather is increasing day by day, which poses a severe challenge to the efficient operation of air conditioners in high temperature environments.

[0003] However, due to insufficient air volume of the fan in the existing air conditioner, the heat of the condenser in the outdoor unit of the air conditioner cannot be taken away in time, resulting in low energy efficiency of the air conditioner. Summary of the Utility Model

[0004] To overcome the problem that the fan in the air conditioner in the related art cannot take away the heat in the air conditioner in time when operating in a high temperature environment, the embodiments of the present utility model propose an axial flow impeller for an axial flow fan, an axial flow fan, a motor bracket, an axial flow fan assembly, an air conditioner housing and an air conditioner. By improving the structure of the axial flow impeller, a convex portion and a concave portion are provided at the trailing edge position of the impeller blade. The additional convex portion can effectively increase the blade area, improve the work done on the air flow, thereby increasing the air volume. At the same time, the additional concave portion can also reduce the separation vortex and wake vortex generated when the blade rotates, thereby effectively reducing the noise generated when the blade rotates.

[0005] The first aspect of the embodiment of the present utility model proposes an axial flow impeller for an axial flow fan, and the axial flow impeller includes an impeller, and the impeller includes:

[0006] An impeller hub;

[0007] Impeller blades, the impeller blades having an inner edge for connecting with the outer peripheral edge of the impeller hub, an outer edge opposite to the inner edge, and a leading edge and a trailing edge between the inner edge and the outer edge. The inner edge, the leading edge, the outer edge and the trailing edge are sequentially connected to form the outer contour of the impeller blade. The width of the impeller blade gradually increases from the inner edge side to the outer edge side, and the thickness of the impeller blade gradually thins from the inner edge side to the outer edge side;

[0008] At least one convex portion and at least one concave portion are formed on the trailing edge of the impeller blade, wherein at least one convex portion is arranged close to the inner edge of the impeller blade, and at least one concave portion is arranged close to the outer edge of the impeller blade;

[0009] The convex portion arranged close to the inner edge of the impeller blade is used to increase the air flow generated at the inner edge position of the impeller blade, and the concave portion arranged close to the outer edge of the impeller blade is used to reduce the separation vortex and wake vortex generated at the outer edge position of the impeller blade.

[0010] In the above technical solution, two convex portions and one concave portion are formed on the trailing edge of the impeller blade. The two convex portions include a first convex portion disposed near the inner edge side of the impeller blade and a second convex portion disposed near the outer edge side of the impeller blade;

[0011] The concave portion is located between the first convex portion and the second convex portion.

[0012] In the above technical solution, the area of the first convex portion is s1, the area of the second convex portion is s2, and the area of the concave portion is s3. The area s1 of the first convex portion is greater than the area s2 of the second convex portion;

[0013] Where s1 + s2 = k0 * s3, and k0 is a first coefficient with a value between {9 - 11}.

[0014] In the above technical solution, the first convex portion, the concave portion, and the second convex portion can all be configured as at least one of an arc shape, a broken line shape, or a spline curve shape;

[0015] The first convex portion, the concave portion, and the second convex portion are connected in sequence to form the trailing edge of the impeller blade with a convex-concave structure.

[0016] In the above technical solution, the first convex portion includes a starting end of the first convex portion on the side close to the inner edge of the impeller blade. The starting end of the first convex portion intersects with a first virtual arc, and the first virtual arc is an arc made with a radius of r1 + k1 * Rm, where r1 is the radius of the impeller hub for mating with the impeller blade, Rm is the height of the impeller blade, and k1 is a second coefficient with a value between {0.03 - 0.06};

[0017] The second convex portion includes a terminating end of the second convex portion on the side close to the outer edge of the impeller blade. The terminating end of the second convex portion intersects with a second virtual arc, and the second virtual arc is an arc made with a radius of r1 + k2 * Rm, where r1 is the radius of the impeller hub for mating with the impeller blade, Rm is the height of the impeller blade, and k2 is a third coefficient with a value between {0.9 - 0.97};

[0018] The intersection point of the starting end of the first convex portion and the first virtual arc is point B1, and the intersection point of the terminating end of the second convex portion and the second virtual arc is point B2. The connection line of point B1 and point B2 is L1, and L1 forms at least a part of the outer contour line of the trailing edge of the impeller blade when the first convex portion, the second convex portion, and the concave portion are not provided.

[0019] In the above technical solution, the shortest distance from the highest point Bw1 of the first convex portion to L1 is hw1, and the shortest distance from the highest point Bw1 of the first convex portion to the center of the impeller hub is Rw1;

[0020] The shortest distance from the lowest point Bw2 of the concave part to L1 is hw2, and the shortest distance from the lowest point Bw2 of the concave part to the center of the impeller hub is Rw2;

[0021] The shortest distance from the highest point Bw3 of the second convex part to L1 is hw3, and the shortest distance from the highest point Bw3 of the second convex part to the center of the impeller hub is Rw3;

[0022] Among them;

[0023] hw1 = (0.08 - 0.10) * r2, hw2 = (0.015 - 0.25) * r2, hw3 = (0.02 - 0.03) * r2;

[0024] Rw1 = (0.55 - 0.60) * r2; Rw2 = (0.80 - 0.84) * r2; Rw3 = (0.87 - 0.91) * r2;

[0025] Wherein r2 is the radius of the impeller blade.

[0026] In the above technical solution, in the axial direction of the impeller hub, the maximum distance between the convex part on the trailing edge of the impeller blade and the outer edge of the impeller blade is Hh2, and the maximum distance between the convex part on the trailing edge of the impeller blade and the concave part on the trailing edge of the impeller blade is Hh1;

[0027] Among them, Hh1 = (0.10 - 0.13) * Hh2.

[0028] In the above technical solution, the diameter of the impeller hub is D1, the diameter of the impeller blade is D2, and the height of the impeller blade is Rm, Rm = (D2 - D1) / 2;

[0029] Wherein the ratio between the impeller hub diameter D1 and the impeller blade diameter D2 satisfies: D1 / D2 = (0.285 - 0.305);

[0030] Wherein the area of the virtual circle with diameter D2 is S2, the area of the virtual circle with diameter D1 is S1, S2 - S1 = S3;

[0031] The projected area of the impeller blade in the axial direction of the impeller hub is S4;

[0032] Among them, the ratio of S4 to S3 satisfies: S4 / S3 = (0.170 - 0.210).

[0033] A second aspect of the embodiments of the present utility model provides an axial flow fan, which includes an impeller hub and the above-mentioned axial flow fan blade;

[0034] Among them, the axial flow fan blade includes a plurality of impeller blades, and the plurality of impeller blades are circumferentially distributed along the outer peripheral edge of the impeller hub in the same rotation direction.

[0035] In the third aspect of the embodiment of the present utility model, a motor bracket is proposed, which is used to install the above-mentioned axial-flow impeller or the above-mentioned axial-flow fan, and a guide vane structure is installed on the motor bracket;

[0036] The guide vane structure is arranged at a distance from the intake side of the impeller blades of the axial-flow fan, so as to make the air flow rotate in advance before passing through the impeller blades.

[0037] In the above technical solution, the guide vane structure includes a plurality of guide vane blades distributed in the same rotation direction on the outer circumference of the center of the guide vane structure, and the center of the guide vane structure and the center of the impeller hub arranged on the motor bracket are on the same axis;

[0038] The rotation direction of the guide vane blades is designed to be opposite to the rotation direction of the impeller blades when the impeller blades are arranged on the motor bracket.

[0039] In the above technical solution, among the plurality of circumferentially distributed guide vane blades, the distribution angle between two adjacent guide vane blades is α1, where α1 = 90° ± 20°;

[0040] The outer diameter of the guide vane blade is D0, the thickness of the guide vane blade is hd1, and the diameter of the impeller hub is D1;

[0041] Where D0 = (0.95 - 1) * D1, hd1 = (0.05 - 0.10) * D0.

[0042] In the fourth aspect of the embodiment of the present utility model, an axial-flow fan assembly is proposed, which includes the above-mentioned axial-flow fan and / or the above-mentioned motor bracket.

[0043] In the fifth aspect of the embodiment of the present utility model, an air conditioner is proposed. The air conditioner includes an indoor unit and an outdoor unit. The outdoor unit includes an air conditioner housing. The outdoor unit includes the above-mentioned axial-flow fan, or the outdoor unit includes the above-mentioned axial-flow fan assembly, or the above-mentioned motor bracket is integrally formed on the air conditioner housing:

[0044] The axial-flow fan is used to cool the condenser in the outdoor unit.

[0045] After adopting the above technical solution, the present utility model has the following beneficial effects compared with the prior art:

[0046] In the embodiment of the present utility model, by improving the structure of the axial-flow impeller, a raised portion and a recessed portion are arranged at the trailing edge position of the impeller blades. The added raised portion can effectively increase the blade area, improve the work done on the air flow, thereby increasing the air volume. At the same time, the added recessed portion can also reduce the separation vortex and wake vortex generated when the blade rotates, thereby effectively reducing the noise generated when the blade rotates. Description of the Drawings

[0047] The accompanying drawings here are incorporated into the specification and form a part of this specification, showing embodiments consistent with the present utility model, and are used together with the specification to explain the principles of the present utility model.

[0048] Figure 1 It is a three-dimensional structure schematic diagram of an axial flow fan embodiment of the present utility model;

[0049] Figure 2 It is a front view structure schematic diagram of an axial flow fan embodiment of the present utility model;

[0050] Figure 3 It is a three-dimensional structure schematic diagram of an impeller in an axial flow fan embodiment of the present utility model;

[0051] Figure 4 It is a front view structure schematic of an impeller in an axial flow fan embodiment of the present utility model Figure 1 ;

[0052] Figure 5 It is a front view structure schematic of an impeller in an axial flow fan embodiment of the present utility model Figure 2 ;

[0053] Figure 6 It is a front view structure schematic diagram of an impeller blade in an axial flow fan embodiment of the present utility model;

[0054] Figure 7 It is a comparison chart of air volume - noise data between the axial flow fan in the embodiment of this aspect and the axial flow fan in the prior art.

[0055] Wherein: 1 - impeller hub; 2 - impeller blade; 2a - inner edge; 2b - outer edge; 2c - leading edge; 2d - trailing edge; 21 - first protrusion; 22 - second protrusion; 23 - depression; 3 - motor bracket; 4 - motor; 5 - guide vane blade. Detailed implementation manners

[0056] Here, the exemplary embodiments will be described in detail, and the examples are shown in the accompanying drawings. When the following description refers to the accompanying drawings, unless otherwise indicated, the same numbers in different drawings represent the same or similar elements. The implementation manners described in the following exemplary embodiments do not represent all implementation manners consistent with the present utility model. On the contrary, they are merely examples of devices and methods consistent with some aspects of the present utility model as detailed in the appended claims.

[0057] When the existing air conditioner operates in a high-temperature environment, the fan cannot timely take away the heat in the air conditioner. In view of the above problems, the embodiment of the present utility model provides an axial-flow impeller, an axial-flow fan, a motor bracket, an axial-flow fan assembly and an air conditioner. By improving the structure of the axial-flow impeller, a convex portion and a concave portion are arranged at the trailing edge of the impeller blade. The added convex portion can effectively increase the blade area, improve the work done on the air flow, thereby increasing the air volume. At the same time, the added concave portion can also reduce the separation vortex and wake vortex generated when the blade rotates, thereby effectively reducing the noise generated when the blade rotates.

[0058] The following will Figure 1 - be Figure 7 elaborate on the technical solutions of this embodiment in detail. Without conflict, the following embodiments and examples can be combined with each other.

[0059] Embodiment

[0060] As Figures 1 - 7 shown, in the first aspect of the embodiment of the present utility model, an axial-flow impeller for an axial-flow fan is provided. The axial-flow impeller includes an impeller, and the impeller includes:

[0061] Impeller blades 2, the impeller blades 2 have an inner edge 2a for connecting with the outer peripheral edge of the impeller hub 1, an outer edge opposite to the inner edge 2a, and a leading edge 2c and a trailing edge 2d between the inner edge 2a and the outer edge 2b. The inner edge 2a, the leading edge 2c, the outer edge 2b and the trailing edge 2d are sequentially connected to form the outer contour of the impeller blade 2. The width of the impeller blade 2 gradually increases from the inner edge 2a side to the outer edge 2b side, and the thickness of the impeller blade 2 gradually thins from the inner edge 2a side to the outer edge 2b side;

[0062] At least one convex portion and at least one concave portion are formed on the trailing edge 2d of the impeller blade 2, wherein at least one convex portion is arranged close to the inner edge 2a of the impeller blade 2, and at least one concave portion is arranged close to the outer edge 2b of the impeller blade 2;

[0063] The convex portion arranged close to the inner edge 2a of the impeller blade 2 is used to increase the air flow generated at the inner edge 2a position of the impeller blade, and the concave portion arranged close to the outer edge 2b of the impeller blade 2 is used to reduce the separation vortex and wake vortex generated at the outer edge 2b position of the impeller blade.

[0064] In the embodiment of the present utility model, by arranging a convex portion and a concave portion at the trailing edge 2d position of the impeller blade 2 of the axial-flow fan, the added convex portion can effectively increase the blade area, improve the work done on the air flow, thereby increasing the air volume. At the same time, the added concave portion can reduce the separation vortex and wake vortex generated when the impeller blade 2 rotates, thereby effectively reducing the noise generated when the impeller blade 2 rotates.

[0065] Specifically, since the area of the inner edge 2a of the impeller blade 2 is smaller than that of the outer edge 2b, the air volume here is small. By setting a convex portion here, the blade area here can be effectively increased, thereby enhancing the work done on the air flow and then increasing the air volume. Since the outer edge 2b of the impeller blade is thinner than the inner edge 2a, separation vortices and wake vortices are likely to occur at the position of the impeller blade 2 near the outer edge 2b, which will increase the noise during the rotation of the impeller blade 2. By setting a concave portion here, the separation vortices and wake vortices can be reduced, thereby effectively reducing the noise.

[0066] It should be noted that, as Figure 4 and Figure 5 shown, in this embodiment, the "width of the impeller blade" mentioned above is the distance from one side of the leading edge 2c of the impeller blade to the trailing edge 2d. As can be seen from Figure 4 and Figure 5 , the width of the impeller blade 2 gradually increases from the inner edge 2a side to the outer edge 2b side.

[0067] Furthermore, as Figure 6 shown, two convex portions and a concave portion 23 are formed on the trailing edge of the impeller blade 2. The two convex portions include a first convex portion 21 disposed near the inner edge 2a side of the impeller blade 2 and a second convex portion 22 disposed near the outer edge 2b side of the impeller blade 2;

[0068] wherein the concave portion 23 is located between the first convex portion 21 and the second convex portion 22.

[0069] In the embodiment of the present invention, by setting two convex portions and a concave portion on the trailing edge 2d of the impeller blade 2 and arranging the concave portion between the two convex portions, a balance can be achieved between the effect of increasing the air volume and the effect of reducing the noise.

[0070] Preferably, the area of the first convex portion 21 is s1, the area of the second convex portion 22 is s2, and the area of the concave portion 23 is s3. The area s1 of the first convex portion 21 is greater than the area s2 of the second convex portion 22;

[0071] where s1 + s2 = k0 * s3, and k0 is a first coefficient with a value in the range of {9 - 11}. Preferably, k0 is taken as 10.

[0072] It should be noted that the area s1 of the first convex portion 21 and the area s2 of the second convex portion 22 are separated at 3 / 4 to 11 / 12 of the blade height, so as to effectively balance the air volume and noise generated during the rotation of the impeller. As shown in Figure 4 and Figure 5 , the blade height in this embodiment is the height of the impeller, that is, the maximum distance from the inner edge 2a of the impeller to the outer edge 2b of the impeller.

[0073] It should be noted that when the areas of the first convex portion 21, the second convex portion 22, and the concave portion 23 satisfy the above formula, the impeller blade 2 has the best operating effect at this time, that is, the above-mentioned balance can be achieved between the effect of increasing the air volume and the effect of reducing noise.

[0074] In any of the above embodiments, as Figure 6 shown, the first convex portion 21, the concave portion 23, and the second convex portion 22 can all be configured as at least one of an arc shape, a broken line shape, or a spline curve shape;

[0075] When the first convex portion 21, the concave portion 23, and the second convex portion 22 are all configured as arcs, the arc length of the first convex portion 21 is greater than the arc length of the second convex portion 22, the arc length of the second convex portion is equal to the arc length of the concave portion 23, the radian of the first convex portion 21 is less than the radian of the second convex portion 22, and the radian of the second convex portion 22 is equal to the radian of the concave portion 23;

[0076] Among them, the first convex portion 21, the concave portion 23, and the second convex portion 23 are connected in sequence to form the trailing edge of the impeller blade with a convex-concave structure.

[0077] Preferably, the first convex portion 21, the concave portion 23, and the second convex portion 22 are all configured as arcs.

[0078] In any of the above embodiments, as Figure 4 and Figure 5 shown, the first convex portion 21 includes a starting end of the first convex portion close to one side of the inner edge 2a of the impeller blade. The starting end of the first convex portion intersects with a first virtual arc, and the first virtual arc is an arc made with a radius of r1 + k1 * Rm, where r1 is the hub radius, Rm is the height of the impeller blade 2, and k1 is a second coefficient with a value in the range of {0.03 to 0.06}; preferably, k1 takes a value of 0.05, that is, the first convex portion 21 is arranged near the impeller hub 1, and the gas flow velocity near the impeller hub 1 is small, and the influence on the impeller flow rate and noise is small;

[0079] The second convex portion 22 includes a terminating end of the second convex portion close to one side of the outer edge 2b of the impeller blade. The terminating end of the second convex portion intersects with a second virtual arc, and the second virtual arc is an arc made with a radius of r1 + k2 * Rm, where r1 is the hub radius, Rm is the height of the impeller blade 2, and k2 is a third coefficient with a value in the range of {0.9 to 0.97}; preferably, k2 takes a value of 0.95; that is, the second convex portion 22 is arranged close to the outer edge 2b of the impeller blade 2, but due to the light-weight treatment at the position of the outer edge 2b of the impeller blade 2, the setting position of the second convex portion 22 needs to be at a certain distance from the outer edge 2b of the impeller blade 2.

[0080] The intersection point of the starting end of the first convex portion and the first virtual arc is point B1. The first virtual arc intersects the leading edge 2c of the impeller blade 2 at point A1. The intersection point of the terminating end of the second convex portion and the second virtual arc is point B2. The second virtual arc intersects the leading edge of the impeller blade 2 at point A2. The line connecting point B1 and point B2 is L1. L1 forms at least a part of the outer contour line of the trailing edge of the impeller blade 2 when the first convex portion 21, the second convex portion 22, and the recessed portion 23 are not provided, as Figure 5 and Figure 6 shown. With the line L1 connecting point B1 and point B2 as the reference, the portion protruding away from the leading edge 2c is the convex portion, and the recessed portion recessed toward the leading edge 2c.

[0081] Furthermore, as Figure 4 and Figure 5 shown, the shortest distance from the highest point Bw1 of the first convex portion 21 to L1 is hw1, and the shortest distance from the highest point Bw1 of the first convex portion 21 to the center of the impeller hub 1 is Rw1;

[0082] The shortest distance from the lowest point Bw2 of the recessed portion 23 to L1 is hw2, and the shortest distance from the lowest point Bw2 of the recessed portion 23 to the center of the impeller hub 1 is Rw2;

[0083] The shortest distance from the highest point Bw3 of the second convex portion 22 to L1 is hw3, and the shortest distance from the highest point Bw3 of the second convex portion 22 to the center of the impeller hub 1 is Rw3;

[0084] wherein;

[0085] hw1 = (0.08 - 0.10) * r2, hw2 = (0.015 - 0.25) * r2, hw3 = (0.02 - 0.03) * r2;

[0086] Rw1 = (0.55 - 0.60) * r2; Rw2 = (0.80 - 0.84) * r2; Rw3 = (0.87 - 0.91) * r2;

[0087] where r2 is the radius of the impeller blade 2.

[0088] In the embodiment of the present utility model, by limiting the above parameters, the convex sizes of the first convex portion 21 and the second convex portion 22 can be controlled, so as to avoid generating relatively large noise while increasing the air volume.

[0089] In any of the above embodiments, as Figure 4 and Figure 5As shown, in the axial direction of the axis of the impeller hub 1, the maximum distance between the raised portion on the trailing edge 2d of the impeller blade and the outer edge 2b of the impeller blade is Hh2, and the maximum distance between the raised portion on the trailing edge 2d of the impeller blade and the recessed portion on the trailing edge of the impeller blade is Hh1; where Hh1 = (0.10 - 0.13) * Hh2. In the embodiment of the present invention, by defining the above parameters, the recessed size of the recessed portion 23 can be controlled, thereby reducing noise while avoiding affecting the air volume.

[0090] In any of the above embodiments, as Figure 4 and Figure 5 shown, the diameter of the impeller hub 1 is D1, the diameter of the impeller blade 2 is D2, and the height of the impeller blade 2 is Rm, Rm = (D2 - D1) / 2;

[0091] where the ratio between the diameter D1 of the impeller hub 1 and the diameter D2 of the impeller blade 2 satisfies: D1 / D2 = (0.285 - 0.305);

[0092] where the virtual circle area with diameter D2 is S2, the virtual circle area with diameter D1 is S1, and S2 - S1 = S3;

[0093] The projected area of the impeller blade 2 in the axial direction of the axis of the impeller hub 1 is S4;

[0094] where the ratio between S4 and S3 satisfies: S4 / S3 = (0.170 - 0.210). In the embodiment of the present invention, by defining the above parameters, the effective area of the impeller during rotation can be controlled, thereby improving the working efficiency of the impeller.

[0095] In summary, in the embodiment of the present invention, by defining the above parameters to design the setting position and size of the raised portion and the recessed portion, as well as the sizes of the impeller blade and the impeller hub, the designed impeller can achieve a balance between the effects of increasing the air volume and reducing the noise, so as to improve the working efficiency of the impeller.

[0096] As Figures 1 - 5 shown, in the second aspect of the embodiment of the present invention, an axial flow fan is further provided, which includes an impeller hub 1 and the above-mentioned axial flow fan blade;

[0097] where the axial flow fan blade includes a plurality of impeller blades 2, and the plurality of impeller blades 2 are circumferentially distributed along the outer peripheral edge of the impeller hub 1 in the same rotation direction.

[0098] Preferably, the plurality of impeller blades 2 are circumferentially and uniformly distributed along the outer peripheral edge of the impeller hub 1 in the same rotation direction.

[0099] In summary, as Figure 7As shown, in the embodiment of the present utility model, compared with the existing impeller, for the improved impeller, at the same noise level, its air volume has increased by 379 - 472 m3 / h, with an increase of 11% - 13%.

[0100] The third aspect of the embodiment of the present utility model also provides a motor bracket as shown in Figure 1 and Figure 2 for installing the above-mentioned axial-flow fan blade or the above-mentioned axial-flow fan. The axial-flow fan further includes a motor 4, the motor 4 is fixedly installed on the motor bracket 3, the output shaft end of the motor 4 is in transmission connection with the impeller blade 2, and a guide vane structure is installed on the motor bracket 3;

[0101] The guide vane structure is arranged at a distance from the intake side of the impeller blade 2 of the axial-flow fan to pre-rotate the air flow before the air flow passes through the impeller blade 2.

[0102] In the embodiment of the present utility model, by arranging the guide vane structure on the motor bracket 3, the air flow before entering the impeller can be pre-rotated. The pre-rotated air flow enters the impeller at a certain attack angle, which can improve the intake efficiency of the impeller and thus increase the air volume.

[0103] Furthermore, the guide vane structure includes a plurality of guide vane blades 5 distributed in the same rotation direction on the outer circumference of the center of the guide vane structure. The center of the guide vane structure and the center of the impeller hub 1 arranged on the motor bracket 3 are on the same axis;

[0104] The rotation direction of the guide vane blade 5 is designed such that when the impeller blade 2 is arranged on the motor bracket 3, the rotation direction of the guide vane blade 5 is opposite to that of the impeller blade 2.

[0105] In the embodiment of the present utility model, by setting the rotation direction of the guide vane blade 5 to be opposite to that of the impeller blade 2, the air flow can enter the impeller blade 2 more smoothly from the guide vane blade 5.

[0106] Specifically, among the plurality of circumferentially distributed guide vane blades 5, the distribution angle between two adjacent guide vane blades 5 is α1, where α1 = 90° ± 20°;

[0107] The outer diameter of the guide vane blade 5 is D0, the thickness of the guide vane blade 5 is hd1, and the diameter of the impeller hub 1 is D1;

[0108] Where D0 = (0.95 - 1) * D1, hd1 = (0.05 - 0.10) * D0. In the embodiment of the present utility model, through the above parameter settings, as much as possible of the air entering the impeller can pass through the guide vane blade 5 for pre-rotation.

[0109] The fourth aspect of the embodiment of the present utility model also provides a kind of as shown in Figure 1 and Figure 2The axial flow fan assembly shown includes the axial flow fan provided in the second aspect of the embodiment of the present invention and the motor bracket provided in the third aspect of the embodiment of the present invention.

[0110] The fifth aspect of the embodiment of the present invention further provides an air conditioner, which includes an indoor unit and an outdoor unit. The outdoor unit includes an air conditioner housing. The outdoor unit includes the axial flow fan provided in the second aspect of the embodiment of the present invention, or the outdoor unit includes the axial flow fan assembly provided in the fourth aspect of the embodiment of the present invention, or the motor bracket provided in the third aspect of the embodiment of the present invention is integrally formed on the air conditioner housing.

[0111] The axial flow fan is used to cool the condenser in the outdoor unit.

[0112] When the axial flow fan in the embodiment of the present invention is adopted by the air conditioner, it can effectively dissipate the heat of the condenser in the outdoor unit, avoiding the problem of low air conditioner energy efficiency caused by insufficient air volume of the outdoor unit and the inability to take away the heat of the condenser in time under high temperature conditions.

[0113] Those skilled in the art will readily conceive of other embodiments of the present invention after considering the specification and practicing the embodiments disclosed herein. This application is intended to cover any variations, uses, or adaptations of the present invention, which follow the general principles of the present invention and include known common knowledge or conventional technical means in the technical field not disclosed by the present invention. The specification and examples are only illustrative, and the true scope and spirit of the present invention are pointed out by the following claims.

[0114] It should be understood that the present invention is not limited to the exact structures described above and shown in the drawings, and various modifications and changes can be made without departing from its scope. The scope of the present invention is only limited by the appended claims.

Claims

1. An axial flow fan blade for an axial flow fan, characterized in that: The axial flow fan blade comprises an impeller, and the impeller comprises: An impeller blade (2), the impeller blade (2) comprising an inner edge (2a) for connecting to the outer peripheral edge of an impeller hub (1), an outer edge (2b) opposite to the inner edge (2a), and a leading edge (2c) and a trailing edge (2d) between the inner edge (2a) and the outer edge (2b), the inner edge (2a), the leading edge (2c), the outer edge (2b) and the trailing edge (2d) being sequentially connected to form an outer contour of the impeller blade (2), the width of the impeller blade (2) gradually increasing from the inner edge (2a) side to the outer edge (2b) side, and the thickness of the impeller blade (2) gradually decreasing from the inner edge (2a) side to the outer edge (2b) side; At least one protrusion and at least one recess are formed on the trailing edge (2d) of the impeller blade (2), wherein at least one protrusion is arranged close to the inner edge (2a) of the impeller blade (2), and at least one recess is arranged close to the outer edge (2b) of the impeller blade (2); The raised portion arranged close to the inner edge (2a) of the impeller blade (2) is used to increase the airflow rate generated at the inner edge (2a) of the impeller blade, and the recessed portion arranged close to the outer edge (2b) of the impeller blade (2) is used to reduce the separation vortex and the wake vortex generated at the outer edge of the impeller blade.

2. The axial flow fan blade according to claim 1, characterized in that: Two raised portions and a recessed portion (23) are formed on the trailing edge of the impeller blade (2), the two raised portions comprising a first raised portion (21) arranged close to the inner edge (2a) of the impeller blade (2) and a second raised portion (22) arranged close to the outer edge (2b) of the impeller blade (2); The recessed portion (23) is located between the first raised portion (21) and the second raised portion (22).

3. The axial flow fan blade according to claim 2, characterized in that: The area of ​​the first raised portion (21) is s1, the area of ​​the second raised portion (22) is s2, and the area of ​​the recessed portion (23) is s3, and the area s1 of the first raised portion (21) is greater than the area s2 of the second raised portion (22); Wherein s1+s2=k0*s3, k0 is the first coefficient whose value is between {9-11}.

4. The axial flow fan blade according to claim 2, characterized in that: The first protruding portion (21), the recessed portion (23) and the second protruding portion (22) are all configured to be at least one of an arc shape, a broken line shape or a spline curve shape; When the first protruding portion (21), the recessed portion (23) and the second protruding portion (22) are all configured to be arc-shaped, the arc length of the first protruding portion (21) is greater than the arc length of the second protruding portion (22), the arc length of the second protruding portion is equal to the arc length of the recessed portion (23), the curvature of the first protruding portion (21) is smaller than the curvature of the second protruding portion (22), and the curvature of the second protruding portion (22) is equal to the curvature of the recessed portion (23); The first raised portion (21), the recessed portion (23) and the second raised portion (22) are sequentially connected to form the impeller blade trailing edge having a convex-concave structure.

5. The axial flow fan blade according to claim 2, characterized in that: The first protrusion (21) comprises a first protrusion starting end close to the inner edge (2a) of the impeller blade, the first protrusion starting end intersecting with a first virtual arc, the first virtual arc being an arc with a radius of r1+k1*Rm, wherein r1 is the radius of the impeller hub used to cooperate with the impeller blade, Rm is the height of the impeller blade (2), and k1 is a second coefficient with a value between {0.03 and 0.06}; The second protrusion (22) comprises a second protrusion terminal end close to the outer edge (2b) of the impeller blade, the second protrusion terminal end intersects with a second virtual arc, the second virtual arc is an arc with a radius of r1+k2*Rm, wherein r1 is the radius of the impeller hub used to match the impeller blade, Rm is the height of the impeller blade, and k2 is a third coefficient with a value between {0.9 and 0.97}; The intersection point of the starting end of the first raised portion and the first virtual arc is point B1, the intersection point of the terminating end of the second raised portion and the second virtual arc is point B2, the line connecting point B1 and point B2 is L1, and L1 constitutes at least part of the outer contour line of the trailing edge of the impeller blade (2) when the first raised portion (21), the second raised portion (22) and the recessed portion (23) are not provided.

6. The axial flow fan blade according to claim 5, characterized in that: The shortest distance from the highest point Bw1 of the first protrusion (21) to L1 is hw1, and the shortest distance from the highest point Bw1 of the first protrusion (21) to the center of the impeller hub (1) is Rw1; The shortest distance from the lowest point Bw2 of the recessed portion (23) to L1 is hw2, and the shortest distance from the lowest point Bw2 of the recessed portion (23) to the center of the impeller hub (1) is Rw2; The shortest distance from the highest point Bw3 of the second protrusion (22) to L1 is hw3, and the shortest distance from the highest point Bw3 of the second protrusion (22) to the center of the impeller hub (1) is Rw3; in; hw1=(0.08~0.10)*r2, hw2=(0.015~0.25)*r2, hw3=(0.02~0.03)*r2; Rw1=(0.55~0.60)*r2; Rw2=(0.80~0.84)*r2; Rw3=(0.87~0.91)*r2; Wherein r2 is the radius of the impeller blade (2).

7. The axial flow fan blade according to claim 1, characterized in that: In the axial direction of the impeller hub (1), the maximum distance between the protrusion on the trailing edge (2d) of the impeller blade and the outer edge (2b) of the impeller blade is Hh2, and the maximum distance between the protrusion on the trailing edge (2d) of the impeller blade and the recessed portion on the trailing edge of the impeller blade is Hh1; Where Hh1 = (0.10 ~ 0.13) * Hh2.

8. The axial flow fan blade according to claim 1, characterized in that: The diameter of the impeller hub (1) is D1, the diameter of the impeller blade (2) is D2, the height of the impeller blade (2) is Rm, and Rm=(D2-D1) / 2; The ratio between the diameter D1 of the impeller hub (1) and the diameter D2 of the impeller blades (2) satisfies: D1 / D2=(0.285-0.305); The area of ​​the virtual circle with diameter D2 is S2, the area of ​​the virtual circle with diameter D1 is S1, S2-S1=S3; The projection area of ​​the impeller blade (2) in the axial direction of the impeller hub (1) is S4; The ratio of S4 to S3 satisfies: S4 / S3=(0.170-0.210).

9. An axial flow fan, characterized in that: It comprises an impeller hub (1) and an axial flow fan blade according to any one of claims 1 to 8; The axial flow fan blade comprises a plurality of impeller blades (2), and the plurality of impeller blades (2) are circumferentially distributed along the outer periphery of the impeller hub (1) in the same rotation direction.

10. A motor bracket, characterized in that: Used for installing the axial flow fan blades described in any one of claims 1 to 8 or the axial flow fan described in claim 9, the motor bracket (3) being provided with a guide vane structure; The guide vane structure is used to be arranged at a distance from the air inlet side of the impeller blades (2) of the axial flow fan, so as to pre-rotate the airflow before the airflow passes through the impeller blades (2).

11. The motor bracket according to claim 10, characterized in that: The guide vane structure comprises a plurality of guide vane blades (5) distributed in the same rotation direction on the periphery of the guide vane structure center, and the center of the guide vane structure and the center of the impeller hub (1) provided on the motor bracket (3) are located on the same axis; The rotation direction of the guide vane blade (5) is designed such that when the impeller blade (2) is arranged on the motor bracket (3), the rotation direction of the guide vane blade (5) is opposite to the rotation direction of the impeller blade (2).

12. The motor bracket according to claim 11, characterized in that: Among the plurality of guide vane blades (5) distributed in the circumferential direction, the distribution angle between two adjacent guide vane blades (5) is α1, wherein α1=90°±20°; The outer diameter of the guide vane blade (5) is D0, the thickness of the guide vane blade (5) is hd1, and the diameter of the impeller hub (1) is D1; Wherein D0=(0.95~1)*D1, hd1=(0.05~0.10)*D0.

13. An axial flow fan assembly, characterized in that: It comprises the axial flow fan described in claim 9 and / or the motor bracket described in any one of claims 10-12.

14. An air conditioner, characterized in that: The air conditioner comprises an indoor unit and an outdoor unit, the outdoor unit comprises an air conditioner housing, the outdoor unit comprises the axial flow fan according to any one of claims 1 to 9, or the outdoor unit comprises the axial flow fan assembly according to claim 13, or the air conditioner housing is integrally formed with a motor bracket according to any one of claims 10 to 12: The axial flow fan is used to cool the condenser in the outdoor unit.

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