CN109915411B - Axial fan and air conditioner with same - Google Patents
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- CN109915411B CN109915411B CN201910336042.5A CN201910336042A CN109915411B CN 109915411 B CN109915411 B CN 109915411B CN 201910336042 A CN201910336042 A CN 201910336042A CN 109915411 B CN109915411 B CN 109915411B
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Abstract
The invention provides an axial flow fan and an air conditioner with the same, wherein the axial flow fan comprises a circular hub part and a plurality of blades respectively fixed on the outer peripheral surface of the hub part, each blade comprises a first blade area and a second blade area which are adjacent, the first blade area is arranged at one end of the blade close to the hub part, the second blade area is arranged at one end of the blade far away from the hub part, and the first blade area and the second blade area are distributed on a concentric circle taking the center of the hub part as the center of a circle; the first blade zone comprises a first edge and a second edge which are positioned at two sides of the blade, the second blade zone comprises a third edge and a fourth edge which are positioned at two sides of the blade, the first edge and the third edge are arranged at the front edge of the blade, and the second edge and the fourth edge are arranged at the tail edge of the blade; the first edge forms a recess along radial direction, the second edge forms a bulge along radial direction, the third edge is protruded at radial direction relative to the first edge, the fourth edge and the second edge form a recess at one end far away from the hub part, so as to achieve the purpose of reducing noise of the axial flow fan.
Description
Technical Field
The invention relates to the field of fans, in particular to an axial flow fan and an air conditioner with the same.
Background
As shown in fig. 1, the axial flow fan includes a hub 1' and blades 2' connected to the outer peripheral surface of the hub 1', wherein one of the two sides of the blade 2' connected to the hub 1' is a continuous arc-shaped recess, and the other side is a continuous arc-shaped protrusion. In the process of rotating the blade, the farther the blade 2 'is from the hub part 1' in the radial direction, the larger the local rotation speed is, the stronger the corresponding blade surface pressure fluctuation intensity is, and the larger the generated noise is. According to the noise synthesis mechanism, the noise of the axial flow fan mainly contributes to the area with the largest noise on the blade 2', so that the noise of the axial flow fan in fig. 1 is mainly distributed in the outer ring area of the blade 2', and the noise generated in the outer ring area is larger, so that the noise of the axial flow fan is also larger.
Disclosure of Invention
The invention provides an axial flow fan and an air conditioner with the same.
Specifically, the invention is realized by the following technical scheme:
according to a first aspect of the present invention, there is provided an axial flow fan comprising:
a hub portion having a circular shape; and
a plurality of blades respectively fixed on the outer peripheral surface of the hub part, wherein the blades comprise a first blade zone and a second blade zone which are adjacent, the first blade zone is arranged at one end of the blade close to the hub part, the second blade zone is arranged at one end of the blade far away from the hub part, and the first blade zone and the second blade zone are distributed on a concentric circle taking the center of the hub part as a circle center;
the first blade zone comprises a first edge and a second edge which are positioned at two sides of the blade, the second blade zone comprises a third edge and a fourth edge which are positioned at two sides of the blade, the first edge and the third edge are arranged at the front edge of the blade, and the third edge and the fourth edge are arranged at the tail edge of the blade; the first edge forms a recess along the radial direction, the second edge forms a protrusion along the radial direction, the third edge protrudes relative to the first edge along the radial direction, and the fourth edge and one end of the second edge far away from the hub part form a recess;
the ratio of the difference between the radius of the concentric circle corresponding to the first blade area and the radius of the hub part to the difference between the radius of the concentric circle corresponding to the second blade area and the radius of the hub part is more than 55% and less than 85% and/or the included angle between the connecting line of the innermost side of the first edge and the center of the circle and the connecting line of the outermost side of the third edge and the center of the circle is more than 10 degrees and less than 25 degrees; and/or
The included angle between the connecting line of the innermost side of the second edge and the center of the circle and the connecting line of the outermost side of the fourth edge is more than 5 degrees and less than 15 degrees;
the method comprises the steps that from one end of a blade close to a hub part to one end of the blade far away from the hub part, a camber angle of the blade changes from a straight line section to a parabolic section along a radial distribution curve, wherein the straight line section is in an increasing trend, a parabolic opening corresponding to the parabolic section faces downwards, and the parabolic section comprises a vertex of the parabola;
the parabolic equation is:
Y＝A-(X-B) 2 ；
wherein,
x is the radial position of the vane after normalization;
R i radial position of the blade;
R h a radius of a concentric circle corresponding to the second blade region;
R s a radius for the hub portion;
(a, B) being the vertex of the parabola, wherein a is the maximum turning angle of the vane, and B is the maximum turning angle corresponding to the radial position of the vane;
a is greater than or equal to 23 ° and less than or equal to 28 °; and/or B is greater than or equal to 6 and less than or equal to 8.
Optionally, at least one of the third edge and the fourth edge comprises a plurality of continuous serrations.
Optionally, the saw tooth is sinusoidal in shape.
Optionally, the plurality of serrations of the third edge are of equal or unequal amplitude; and/or
The plurality of serrations of the fourth edge are of equal or unequal amplitude.
Optionally, the formula of the sinusoid is as follows:
A′*sin(x/P)；
where x is the radial position of the serration, a' is the amplitude of the serration, and P is the first tested coefficient.
Optionally, for the serrations of the third edge, a' is greater than or equal to 4mm and less than or equal to 8mm, p is greater than or equal to 0.6 and less than or equal to 1.2; and/or
For the serrations of the fourth edge, A' is greater than or equal to 2mm and less than or equal to 6mm and P is greater than or equal to 0.8 and less than or equal to 1.4.
According to a second aspect of the present invention, there is provided an air conditioner comprising an air conditioner external unit, wherein the air conditioner external unit comprises a drive system and the axial flow fan according to any one of the first aspect, and the drive system is used for driving the axial flow fan to rotate.
According to the technical scheme provided by the embodiment of the invention, the blades are divided into the first blade area (the inner ring) and the second blade area (the outer ring), the stress of the first blade area with low rotation speed is improved through reasonable design of the blade folding angles of the first blade area and the second blade area, and the stress of the second blade area with high rotation speed is correspondingly reduced, so that the pressure pulsation intensity on the whole blade can be effectively reduced, and the noise of the axial flow fan is reduced; and moreover, the whole stress of the inner ring and the outer ring of the blade is not influenced, so that the total air quantity of the axial flow fan is unchanged, the pressure distribution of the inner ring and the outer ring of the blade is more uniform, and the efficiency of the axial flow fan is further improved.
It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the invention as claimed.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments consistent with the invention and together with the description, serve to explain the principles of the invention.
Fig. 1 is a schematic structural view of an axial flow fan in the related art;
fig. 2 is a schematic structural view of an axial flow fan according to an exemplary embodiment of the present invention;
fig. 3A is a perspective view of an axial flow fan according to an exemplary embodiment of the present invention;
fig. 3B is another structural schematic view of an axial flow fan according to an exemplary embodiment of the present invention;
FIG. 3C is an exploded view of the turning angle of the blade shown in FIG. 3B at the C-C plane;
FIG. 3D is a schematic diagram showing radial distribution curves of turning angles of the blade shown in FIG. 3B from one end close to the hub portion to one end far from the hub portion 1;
fig. 3E is a schematic view illustrating a structure of an axial flow fan in another direction according to an exemplary embodiment of the present invention;
FIG. 3F is an enlarged view of a portion of FIG. 3E;
fig. 4A is a schematic view showing a structure of an axial flow fan in still another direction according to an exemplary embodiment of the present invention;
FIG. 4B is a schematic view of the structure of the portion A of the axial flow fan of the embodiment shown in FIG. 3A;
FIG. 4C is a schematic view showing the structure of a portion B of the axial flow fan of the embodiment shown in FIG. 3A;
fig. 5 is a perspective view of an axial flow fan according to an exemplary embodiment of the present invention;
FIG. 6A is a comparison chart of prediction results of noise analysis and prediction of the axial flow fan of the invention and the axial flow fan in the related art based on a Fukano wake vortex noise model;
FIG. 6B is a graph showing a comparison of the noise test results of an axial flow fan with those of an axial flow fan according to the related art, revealing a spectrum distribution result graph of sound pressure levels of the corresponding axial flow fan according to an exemplary embodiment of the present invention;
fig. 6C is a partial schematic view of fig. 6B.
Reference numerals:
1: a hub portion; 2: a blade; 21: a first blade region; 211: a first edge; 212: a second edge; 22: a second blade region; 221: a third edge; 222: and a fourth edge.
Detailed Description
Reference will now be made in detail to exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, the same numbers in different drawings refer to the same or similar elements, unless otherwise indicated. The implementations described in the following exemplary examples do not represent all implementations consistent with the invention. Rather, they are merely examples of apparatus and methods consistent with aspects of the invention as detailed in the accompanying claims.
The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used in this specification and the appended claims, the singular forms "a," "an," and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It should also be understood that the term "and/or" as used herein refers to and encompasses any or all possible combinations of one or more of the associated listed items.
It should be understood that although the terms first, second, third, etc. may be used herein to describe various information, these information should not be limited by these terms. These terms are only used to distinguish one type of information from another. For example, first information may also be referred to as second information, and similarly, second information may also be referred to as first information, without departing from the scope of the invention. The word "if" as used herein may be interpreted as "at … …" or "at … …" or "responsive to a determination", depending on the context.
The axial flow fan and the air conditioner having the same according to the present invention will be described in detail with reference to the accompanying drawings. The features of the examples and embodiments described below may be combined with each other without conflict.
Referring to fig. 2, 3A-3B, 3E, 4A and 5, an embodiment of the present invention provides an axial flow fan, which may include a hub 1 and a plurality of blades 2, wherein the hub 1 is circular, and the plurality of blades 2 are respectively fixed to the plurality of blades 2 on an outer circumferential surface of the hub 1. The number of blades 2 may be selected as desired, for example 3, 4. In the present embodiment, a plurality of blades 2 are provided on the outer peripheral surface of the hub portion 1 at intervals.
Referring to fig. 2, the blade 2 may include a first blade section 21 (i.e., a root or blade inner ring) and a second blade section 22 (i.e., a blade outer ring), the first blade section 21 and the second blade section 22 being contiguous, the first blade section 21 being provided at an end of the blade 2 near the hub portion 1, and the second blade section 22 being provided at an end of the blade 2 remote from the hub portion 1. In the present embodiment, the first blade area 21 and the second blade area 22 are distributed on a concentric circle centered on the center of the hub portion 1 (i.e., the center of the hub portion 1). Optionally, the outer edges of the end of the blade 2 remote from the hub portion 1 are also distributed on a concentric circle with the second blade area 22.
Further, referring to fig. 2 again, the first blade area 21 may include a first edge 211 and a second edge 212 located at two sides of the blade 2, the second blade area 22 includes a third edge 221 and a fourth edge 222 located at two sides of the blade 2, the first edge 211 and the third edge 221 are disposed at a front edge of the blade 2 (i.e. an air inlet side of the blade 2), the second edge 212 and the fourth edge 222 are disposed at a tail edge of the blade 2 (i.e. an air outlet side of the blade 2), that is, on the same blade 2, a side of the blade where the first edge 211 and the third edge 221 are disposed opposite to a side of the blade where the second edge 212 and the fourth edge 222 are disposed. In the embodiment of the present invention, the two sides of the blade 2 are two sides of the blade 2 connected to the hub 1.
In this embodiment, the first edge 211 forms a recess along the radial direction (i.e. the radial direction of the blade 2), the second edge 212 forms a protrusion along the radial direction, the third edge 221 protrudes radially opposite to the first edge 211, and the fourth edge 222 and the second edge 212 form a recess at an end far from the hub 1.
According to the axial flow fan disclosed by the embodiment of the invention, the blades 2 are divided into the first blade area 21 (the inner ring) and the second blade area 22 (the outer ring), the stress of the first blade area 21 with low rotation speed is improved through reasonable design of the blade folding angles of the first blade area 21 and the second blade area 22, and the stress of the second blade area 22 with high rotation speed is correspondingly reduced (compared with the axial flow fan in fig. 1, the total stress of the blades 2 of the axial flow fan disclosed by the embodiment of the invention is unchanged or is less changed), so that the pressure pulsation intensity on the whole blades can be effectively reduced, and the noise of the axial flow fan is reduced; and moreover, the whole stress of the inner ring and the outer ring of the blade is not influenced, so that the total air volume of the axial flow fan is unchanged, the pressure distribution of the inner ring and the outer ring of the blade is more uniform, the pressure artery on the whole blade 2 is effectively reduced, and the efficiency of the axial flow fan is further improved.
The rotational direction of the axial flow fan (arrow direction in fig. 2) of the present embodiment is the arrangement direction of the fourth edge 222 to the third edge 221 of the blade 2, that is, the rotational direction of the axial flow fan is along the arrangement direction of the fourth edge 222 to the third edge 221 of the blade 2; or the rotation direction of the axial flow fan is the arrangement direction from the second edge 212 to the first edge 211 of the blade 2, that is, the rotation direction of the axial flow fan is along the arrangement direction from the second edge 212 to the first edge 211 of the blade 2.
In certain embodiments, the first blade zone 21 corresponds to a difference L between the radius of the concentric circle and the radius of the hub portion 1 1 (as shown in FIG. 2) the difference L between the radius of the concentric circle corresponding to the second blade zone 22 and the radius of the hub portion 1 0 The ratio (as shown in FIG. 2) is greater than 55% and less than 85%, i.e., 55%<L 1 /L 0 <85%, e.g. L 1 /L 0 May be 56%, 57%, 58%, 59%, 60%, 61%, 62%, 63%, 64%, 65%, 66%, 67%, 68%, 69%, 70%, 71%, 72%, 73%, 74%, 75%, 76%, 77%, 78%, 79%, 80%, 81%, 82%, 83% or 84%, or may be other numerical values greater than 55% and less than 85%.
In some embodiments, the angle θ between the line connecting the innermost side of the first edge 211 and the center and the line connecting the outermost side of the third edge 221 and the center 1 (as shown in FIG. 2) greater than 10 degrees and less than 25 degrees, e.g., θ 1 The numerical values can be 11 degrees, 12 degrees, 13 degrees, 14 degrees, 15 degrees, 16 degrees, 17 degrees, 18 degrees, 19 degrees, 20 degrees, 21 degrees, 22 degrees, 23 degrees or 24 degrees, and can be other numerical values which are larger than 10 degrees and smaller than 25 degrees, and can be specifically selected according to actual requirements.
In some embodiments, the angle θ between the innermost and center lines of the second edge 212 and the outermost line of the fourth edge 222 2 Greater than 5 degrees and less than 15 degrees, e.g., θ 2 Can be 6 degrees, 7 degrees, 8 degrees, 9 degrees, 10 degrees, 11 degrees, 12 degrees, 13 degrees or 14 degrees, or can be the sameThe numerical value of the three-dimensional coordinate system is larger than 5 degrees and smaller than 15 degrees, and the numerical value can be specifically selected according to actual requirements.
Optionally, the first edge 211 is curved and/or the second edge 212 is curved, which curved edges can further reduce noise. As a possible implementation, and in combination with fig. 2, 3A, 4A and 5, the first edge 211 and the second edge 212 are each curved.
Further, the blades 2 of the embodiment of the present invention are not entirely in the same plane.
Specifically, with reference to fig. 3A to 3F, the radial distribution curve of the camber angle of the blade 2 changes from a straight line segment to a parabolic segment from the end of the blade 2 near the hub 1 to the end of the blade 2 far from the hub 1. The straight line segment is in an increasing trend (as shown in fig. 3F), the parabolic segment corresponds to the parabolic opening facing downwards, and the parabolic segment comprises the vertex of the parabolic curve. Optionally, the parabola corresponding to the parabola section is of a symmetrical structure.
In the embodiment of the present invention, for the same circumference C-C, the intersection point of C-C and the front edge of the blade 2 is Le, the intersection point of C-C and the rear edge of the blade 2 is Te, and FIG. 3B can be understood as an orthogonal cylindrical plane formed by orthogonally transforming the circumference corresponding to C-C, where the included angle beta between the Le end and C-C Le Included angle beta between Te end and C-C T e difference (beta) L e-β T e) The angle of deflection of Te at the trailing edge of the C-C face of the blade 2 relative to Le at the leading edge can be understood. It should be noted that, the camber angle Y of the blade 2 according to the embodiment of the present invention, that is, the deflection angle of Te at the trailing edge of the C-C surface of the blade 2 with respect to Le at the leading edge. In addition, it should be noted that in the embodiment of the present invention, the parabolic segment may include a curve shape with a smaller deviation from the parabolic shape (less than the preset deviation threshold value), and may also include a curve shape with a coincident parabolic shape.
As a possible implementation, the parabolic equation may be the following:
Y＝A-(X-B) 2 (1)
in the formula (1),
x is the radial position of the vane after normalization;
ri is the radial position of the blade;
rh is the radius of the concentric circle corresponding to the second blade area;
rs is the radius of the hub portion;
(A, B) is the vertex of the parabola, wherein A is the maximum turning angle of the blade, and B is the maximum turning angle corresponding to the radial position of the blade.
Wherein a is greater than or equal to 23 ° and less than or equal to 28 °, and/or B is greater than or equal to 6 and less than or equal to 8, and/or C is greater than or equal to 10 ° and less than or equal to 15 °.
Alternatively, in certain embodiments, a is greater than or equal to 23 ° (angular units, degrees) and less than or equal to 28 °, e.g., a may be 23 °, 23.5 °, 24 °, 24.5 °, 25 °, 25.5 °, 26 °, 26.5 °, 27 °, 27.5 °, 28 °. Of course, a may be other degrees between greater than 23 ° and less than 28 °.
Alternatively, in certain embodiments, B is greater than or equal to 6 and less than or equal to 8, e.g., B can be 6, 6.5, 7, 7.5, 8. Of course, B may be any other value greater than 6 and less than 8.
Optionally, in some embodiments, C is greater than or equal to 10 ° and less than or equal to 15 °, where C is the turning angle of the blade corresponding to the start of the straight line segment. For example, C may be 10, 10.5, 11, 11.5, 12, 12.5, 13, 13.5, 14, 14.5, 15, or other degrees between greater than 10 and less than 15.
It will be appreciated that the parabolic equation is not limited to equation (1) above, but may be a variation of equation (1), or other parabolic equation.
Referring again to fig. 2, 3A, 4A-4B, and 5, at least one of the third edge 221 and the fourth edge 222 includes a plurality of continuous serrations. Optionally, the third edge 221 and the fourth edge 222 respectively include a plurality of continuous saw teeth, where the saw teeth of the third edge 221 can inhibit dynamic and static interference with other static components during the rotation of the blade 2, for example, the axial flow fan is applied to an air conditioner, and the saw teeth of the third edge 221 can inhibit dynamic and static interference with static components in the air conditioner during the rotation of the blade 2; the serrations of the fourth edge 222 may ensure good sound quality characteristics.
In the following embodiment, the third edge 221 and the fourth edge 222 each include a plurality of continuous serrations.
The shape of the serrations may be designed as desired, for example, in some embodiments, as shown in fig. 4B and 4C, the serrations may be sinusoidal in shape that reduces the amount of stress on the second blade region 22 to reduce noise in the second blade region 22. It should be noted that, in the embodiment of the present invention, the sinusoidal curve may include a curve shape with a smaller deviation from the sinusoidal curve shape (less than a preset deviation threshold value), and may also include a curve shape with a sinusoidal curve overlapping.
Optionally, the plurality of saw teeth of the third edge 221 have a constant amplitude, and the structural design is simple; optionally, the plurality of saw teeth of the third edge 221 have non-uniform amplitude, for example, the amplitude of the saw teeth at two ends of the third edge 221 is smaller than the amplitude of the saw teeth at the middle of the third edge 221, which is beneficial to inhibiting dynamic and static interference with other static components in the rotation process of the blade 2 and reducing the stress of the third edge 221.
Optionally, the plurality of saw teeth of the third edge 221 have a constant amplitude, and the structural design is simple; optionally, the plurality of saw teeth of the third edge 221 have non-uniform amplitude, for example, the saw teeth at two ends of the fourth edge 222 have smaller amplitude than the saw teeth at the middle of the fourth edge 222, which is beneficial to inhibiting dynamic and static interference with other static components during rotation of the blade 2 and reducing the stress of the fourth edge 222.
As a possible implementation, the amplitude of the serrations at both ends of the third edge 221 is smaller than the amplitude of the serrations at the middle of the third edge 221, and the amplitude of the serrations at both ends of the fourth edge 222 is smaller than the amplitude of the serrations at the middle of the fourth edge 222.
Alternatively, the formula for the sinusoid is as follows:
A′*sin(x/P)(2)；
in formula (2), x is the radial position of the serration, a' is the amplitude of the serration, and P is the first tested coefficient.
In certain embodiments, for serrations of the third edge 221, a 'is greater than or equal to 4mm and less than or equal to 8mm, p is greater than or equal to 0.6 and less than or equal to 1.2, e.g., a' may include 4mm, 4.5mm, 5mm, 5.5mm, 6mm, 6.5mm, 7mm, 7.5mm, 8mm, and may include other values greater than 4mm and less than 8 mm; p may include 0.6, 0.65, 0.7, 0.75, 0.8, 0.85, 0.9, 0.95, 1, 1.05, 1.1, 1.15, 1.2, and may include other values greater than 0.6 and less than 1.2.
In certain embodiments, for serrations of fourth edge 222, A 'is greater than or equal to 2mm and less than or equal to 6mm, P is greater than or equal to 0.8 and less than or equal to 1.4, e.g., A' may include 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, 5.5mm, 6mm, and may include other values greater than 2mm and less than 6 mm; p may include 0.8, 0.85, 0.9, 0.95, 1, 1.05, 1.1, 1.15, 1.2, 1.25, 1.3, 1.35, 1.4, and may include other values greater than 0.8 and less than 1.4.
In certain embodiments, for the serrations of the third edge 221, a' is greater than or equal to 4mm and less than or equal to 8mm, p is greater than or equal to 0.6 and less than or equal to 1.2; and for the serrations of the fourth edge 222, a' is greater than or equal to 2mm and less than or equal to 6mm, and p is greater than or equal to 0.8 and less than or equal to 1.4.
It will be appreciated that the sinusoid is not limited to equation (1), but may be other, such as variations of equation (1).
Of course, the shape of the serrations is not limited to sinusoidal, but may be other arcuate or non-arcuate shapes.
FIG. 6A is a comparison chart of the prediction results of the noise analysis and prediction of the axial flow fan of the present invention and the axial flow fan (the axial flow fan with the structural shape shown in FIG. 1) in the related art based on the Fukano wake vortex noise model; fig. 6B is a graph showing a comparison of a noise test result (curve 10 in fig. 6B) of an axial flow fan and a noise test result (curve 10' in fig. 6B) of an axial flow fan in the related art according to an exemplary embodiment of the present invention, that is, fig. 6B is a graph showing a comparison of noise test results determined by an actual test; fig. 6C is a partial schematic view of fig. 6B.
Specifically, the noise of the axial flow fan according to the embodiment of the present invention and the noise of the axial flow fan in the related art are analyzed by using the Fukano wake vortex noise model as formula (3), and the Fukano wake vortex noise model is as follows:
in the formula (3), E is noise power, and the unit is W;
ρ 0 the density of the medium is that the medium corresponding to the fan is air, and the unit is kg/m3;
c 0 sound velocity in m/s;
i is the number of blades 2, and the axial flow fan in the embodiment of the invention and the axial flow fan in the related technology both comprise 3 blades;
r is the radius, and the unit is m;
r h the radius of the first blade area of the blade 2 is given by m;
r t the radius of the second blade area of the blade 2 is given by m;
d is wake vortex width, and the unit is m;
w is wake vortex relative speed, and the unit is m/s;
l is the position of the distance fan, and the unit is m;
p is the acoustic pressure of the blade 2 according to the embodiment of the present invention, and can be determined according to the first two formulas in the formula (3);
p 0 the sound pressure is an acoustic reference sound pressure, and the size is 2e-5Pa;
SPL is the noise sound pressure level magnitude, i.e., the ordinate of fig. 6A, in dB.
For the axial flow fan in the related art and the axial flow fan of the embodiment of the present invention, the following operations are performed:
the blade is divided into 5 parts in the radial direction from the outer peripheral surface close to the hub part to the outer peripheral surface far away from the hub part, wherein the parts are respectively a Span 0-20%, a Span 20-40%, a Span 40-60%, a Span 60-80% and a Span 80-100%.
In each portion in fig. 6A, the left square column is used to indicate the noise prediction result of the corresponding portion of the axial flow fan in the related art, and the right square column is used to indicate the noise prediction result of the corresponding portion of the axial flow fan in the embodiment of the present invention.
As shown in fig. 6A, compared with the axial flow fan in the related art, the area noise value of the span of the axial flow fan in the embodiment of the invention is properly increased, the area noise of the span of 80% -100% is greatly reduced, and the noise distribution of different blade 2 parts of the axial flow fan is more reasonable; the total noise of the axial flow fan in the related technology is 71.7dB, the total noise of the axial flow fan in the embodiment of the invention is 70.0dB, and the total noise of the axial flow fan in the embodiment of the invention is reduced by 1.7dB.
Further, the axial flow fans in the related art and the axial flow fans in the embodiments of the present invention are respectively installed on the whole machine (air conditioning system) for testing, and the test results can be seen in fig. 6B and 6C, wherein a curve 10' is a sound pressure level curve of the axial flow fans (conventional design) in the related art at different frequencies, a curve 10 is a sound pressure level curve of the axial flow fans (hybrid design) in the embodiments of the present invention at different frequencies, and the ordinate of fig. 6B and 6C is the noise sound pressure level SPL in dBA; the abscissa is the sound frequency in Hz. As can be seen from fig. 6B and 6C, the noise of the axial flow fan in the embodiment of the invention is reduced obviously in the low frequency range. In the 200-600 Hz range of FIG. 6C, the sound pressure level at the blade pass frequency is reduced by 5-10 dB. Compared with the axial flow fan in the related art, the axial flow fan in the embodiment of the invention has better sound quality, and finally the noise of the whole machine is reduced by 1dBA.
Therefore, the axial flow fan reduces the noise of the axial flow fan through the reasonable design of the edge shapes of the first blade area 21 and the second blade area 22; and moreover, the total air quantity of the axial flow fan is unchanged, and the pressure artery on the whole blade 2 is effectively reduced, so that the efficiency of the axial flow fan is improved.
It is worth mentioning that the axial flow fan of the embodiment of the invention can be applied to air conditioners and other devices requiring fans.
The embodiment of the invention also provides an air conditioner, which comprises an air conditioner external unit, wherein the air conditioner external unit comprises a driving system and the axial flow fan of the embodiment, and the driving system is used for driving the axial flow fan to rotate.
Optionally, the driving system comprises a motor, and a main shaft of the motor is connected with the hub part 1 of the axial flow fan to drive the axial flow fan to rotate. Of course, the drive system may alternatively be other power systems, not limited to an electric motor.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather to enable any modification, equivalent replacement, improvement or the like to be made within the spirit and principles of the invention.
Claims (6)
1. An axial flow fan, comprising:
a hub portion having a circular shape; and
a plurality of blades respectively fixed on the outer peripheral surface of the hub part, wherein the blades comprise a first blade zone and a second blade zone which are adjacent, the first blade zone is arranged at one end of the blade close to the hub part, the second blade zone is arranged at one end of the blade far away from the hub part, and the first blade zone and the second blade zone are distributed on a concentric circle taking the center of the hub part as a circle center;
the first blade zone comprises a first edge and a second edge which are positioned at two sides of the blade, the second blade zone comprises a third edge and a fourth edge which are positioned at two sides of the blade, the first edge and the third edge are arranged at the front edge of the blade, and the second edge and the fourth edge are arranged at the tail edge of the blade;
the first edge forms a recess along the radial direction, the second edge forms a protrusion along the radial direction, the third edge protrudes relative to the first edge along the radial direction, and the fourth edge and one end of the second edge far away from the hub part form a recess;
the ratio of the difference between the radius of the concentric circle corresponding to the first blade region and the radius of the hub part to the difference between the radius of the concentric circle corresponding to the second blade region and the radius of the hub part is more than 55% and less than 85%; and/or the number of the groups of groups,
the included angle between the connecting line of the innermost side of the first edge and the center of the circle and the connecting line of the outermost side of the third edge and the center of the circle is more than 10 degrees and less than 25 degrees; and/or
The included angle between the connecting line of the innermost side of the second edge and the center of the circle and the connecting line of the outermost side of the fourth edge is more than 5 degrees and less than 15 degrees;
the method comprises the steps that from one end of a blade close to a hub part to one end of the blade far away from the hub part, a camber angle of the blade changes from a straight line section to a parabolic section along a radial distribution curve, wherein the straight line section is in an increasing trend, a parabolic opening corresponding to the parabolic section faces downwards, and the parabolic section comprises a vertex of the parabola;
the parabolic equation is:
Y＝A-(X-B) 2 ；
wherein,
x is the radial position of the vane after normalization;
R i radial position of the blade;
R h a radius of a concentric circle corresponding to the second blade region;
R s a radius for the hub portion;
(a, B) being the vertex of the parabola, wherein a is the maximum turning angle of the vane, and B is the maximum turning angle corresponding to the radial position of the vane;
a is greater than or equal to 23 ° and less than or equal to 28 °; and/or
B is greater than or equal to 6 and less than or equal to 8.
2. The axial flow fan of claim 1, wherein at least one of the third edge and the fourth edge includes a plurality of continuous serrations.
3. The axial flow fan according to claim 2, wherein the saw tooth is sinusoidal in shape.
4. The axial flow fan of claim 3, wherein the sinusoidal curve is formulated as follows:
A′*sin(x/P)；
where x is the radial position of the serration, a' is the amplitude of the serration, and P is the first tested coefficient.
5. The axial flow fan according to claim 4, wherein for the serrations of the third edge, a' is greater than or equal to 4mm and less than or equal to 8mm, and p is greater than or equal to 0.6 and less than or equal to 1.2; and/or
For the serrations of the fourth edge, A' is greater than or equal to 2mm and less than or equal to 6mm and P is greater than or equal to 0.8 and less than or equal to 1.4.
6. An air conditioner, comprising an air conditioner external unit, wherein the air conditioner external unit comprises a driving system and the axial flow fan according to any one of claims 1 to 5, and the driving system is used for driving the axial flow fan to rotate.
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| CN201910336042.5A CN109915411B (en) | 2019-04-24 | 2019-04-24 | Axial fan and air conditioner with same |
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| CN201910336042.5A CN109915411B (en) | 2019-04-24 | 2019-04-24 | Axial fan and air conditioner with same |
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| CN110345106A (en) * | 2019-07-31 | 2019-10-18 | 广东美的制冷设备有限公司 | Axial-flow leaf, axial flow blower and air conditioner |
| JP7165433B2 (en) * | 2021-03-17 | 2022-11-04 | シロカ株式会社 | Propeller Fans, Fans, and Circulators |
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| CN209892505U (en) * | 2019-04-24 | 2020-01-03 | 特灵空调系统(中国)有限公司 | Axial fan and air conditioner with same |
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| KR20010026488A (en) * | 1999-09-07 | 2001-04-06 | 구자홍 | Out door unit axial flow fan for airconditioner |
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