CN209892505U - Axial fan and air conditioner with same - Google Patents
Axial fan and air conditioner with same Download PDFInfo
- Publication number
- CN209892505U CN209892505U CN201920569425.2U CN201920569425U CN209892505U CN 209892505 U CN209892505 U CN 209892505U CN 201920569425 U CN201920569425 U CN 201920569425U CN 209892505 U CN209892505 U CN 209892505U
- Authority
- CN
- China
- Prior art keywords
- edge
- blade
- equal
- hub portion
- less
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000002093 peripheral effect Effects 0.000 abstract description 5
- 238000000034 method Methods 0.000 description 10
- 230000003068 static effect Effects 0.000 description 8
- 230000002829 reductive effect Effects 0.000 description 7
- 230000008569 process Effects 0.000 description 5
- 210000001367 artery Anatomy 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000002401 inhibitory effect Effects 0.000 description 2
- 230000002452 interceptive effect Effects 0.000 description 2
- 230000000670 limiting effect Effects 0.000 description 2
- 230000036961 partial effect Effects 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- NWGKJDSIEKMTRX-AAZCQSIUSA-N Sorbitan monooleate Chemical compound CCCCCCCC\C=C/CCCCCCCC(=O)OC[C@@H](O)[C@H]1OC[C@H](O)[C@H]1O NWGKJDSIEKMTRX-AAZCQSIUSA-N 0.000 description 1
- IYFATESGLOUGBX-YVNJGZBMSA-N Sorbitan monopalmitate Chemical compound CCCCCCCCCCCCCCCC(=O)OC[C@@H](O)[C@H]1OC[C@H](O)[C@H]1O IYFATESGLOUGBX-YVNJGZBMSA-N 0.000 description 1
- 239000000654 additive Substances 0.000 description 1
- 230000000996 additive effect Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000009510 drug design Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
- 230000009466 transformation Effects 0.000 description 1
Images
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The utility model provides an axial fan and have its air conditioner, this axial flow is including being circular shape wheel hub portion and fixing a plurality of blades on the outer peripheral face of wheel hub portion respectively, and the blade includes first blade district and the second blade district that borders on, and first blade district is located the one end that the blade is close to wheel hub portion, and the one end that the blade kept away from wheel hub portion is located to the second blade district, and first blade district and second blade district distribute on the concentric circle with the center of wheel hub portion as the centre of a circle; the first blade area comprises a first edge and a second edge which are positioned at two sides of the blade, the second blade area 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 bulge along the radial direction, the third edge is protruded relative to the first edge in the radial direction, and the fourth edge and one end of the second edge far away from the hub part form a recess, so that the purpose of reducing the noise of the axial flow fan is achieved.
Description
Technical Field
The utility model relates to a fan field especially relates to an axial fan and have its air conditioner.
Background
As shown in fig. 1, the axial flow fan includes a hub portion 1 ' and blades 2 ' connected to an outer circumferential surface of the hub portion 1 ', and the blades 2 ' are connected to two side edges of the hub portion 1 ', one of the side edges being a continuous arc-shaped recess and the other side edge being a continuous arc-shaped projection. In the process of blade rotation, the farther the blade 2 'is from the radial direction of the hub portion 1', the greater the local rotation speed, the stronger the corresponding blade surface pressure fluctuation intensity, and the greater the noise generated. According to the noise synthesis mechanism, the noise of the axial flow fan mainly contributes to the noise from the region of the blade 2 'where the noise is the largest, so the noise of the axial flow fan in fig. 1 is mainly distributed in the outer ring region of the blade 2', and the noise generated in the outer ring region is large, so the noise of the axial flow fan is also large.
SUMMERY OF THE UTILITY MODEL
The utility model provides an axial fan and have its air conditioner.
Specifically, the utility model discloses a realize through following technical scheme:
according to the utility model discloses a first aspect provides an axial fan, include:
a hub portion, the hub portion being circular; and
the blades comprise a first blade area and a second blade area which are adjacent, wherein the first blade area is arranged at one end, close to the hub portion, of each blade, the second blade area is arranged at one end, far away from the hub portion, of each blade, and the first blade area and the second blade area are distributed on a concentric circle taking the center of the hub portion as the circle center;
the first blade area comprises a first edge and a second edge which are positioned on two sides of the blade, the second blade area comprises a third edge and a fourth edge which are positioned on two sides of the blade, the first edge and the third edge are arranged on the front edge of the blade, and the third edge and the fourth edge are arranged on 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 in the radial direction, and the fourth edge and one end of the second edge far away from the hub portion form a recess.
Optionally, a ratio of a difference between a radius of a concentric circle corresponding to the first blade region and a radius of the hub portion to a difference between a radius of a concentric circle corresponding to the second blade region and a radius of the hub portion is greater than 55% and less than 85% and/or an included angle between a connecting line of an innermost side of the first edge and a circle center and a connecting line of an outermost side of the third edge and the circle center is greater than 10 degrees and less than 25 degrees; and/or
And the angle between the connecting line of the outermost side of the second edge and the circle center and the connecting line of the outermost side of the fourth edge is more than 5 degrees and less than 15 degrees.
Optionally, from one end of the blade close to the hub portion to one end of the blade far from the hub portion, a distribution curve of the turning angle of the blade in the radial direction is changed from a straight line segment to a parabolic segment, wherein the straight line segment presents an increasing trend, an opening of a parabola corresponding to the parabolic segment faces downwards, and the parabolic segment comprises an apex of the parabola.
Optionally, the equation of the parabola is:
Y＝A-(X-B)2；
wherein,
x is the normalized radial position of the blade;
Riis the radial position of the blade;
Rhthe radius of a concentric circle corresponding to the second blade area;
Rsis the radius of the hub portion;
and (A, B) is the vertex of the parabola, wherein A is the maximum turning angle of the blade, and B is the radial position of the blade corresponding to the maximum turning angle.
Alternatively, 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 degrees and less than or equal to 15 degrees, wherein C is the turning angle of the blade corresponding to the starting point of the straight line segment.
Optionally, at least one of the third edge and the fourth edge comprises a plurality of consecutive serrations.
Optionally, the shape of the serrations is sinusoidal.
Optionally, the plurality of serrations of the third edge are of equal or unequal amplitude; and/or
The plurality of teeth of the fourth edge are of equal or unequal amplitude.
Optionally, the formula of the sinusoid is as follows:
A′*sin(x/P)；
wherein x is the position of the sawtooth in the radial direction, A' is the amplitude of the sawtooth, and P is the first empirical coefficient.
Optionally, 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.
According to the utility model discloses a second aspect provides an air conditioner, including the outer machine of air conditioner, wherein, the outer machine of air conditioner includes actuating system and the arbitrary any of above-mentioned first aspect axial fan, actuating system is used for the drive axial fan rotates.
According to the technical scheme provided by the embodiment of the utility model, the utility model discloses divide into first blade district (inner circle) and second blade district (outer lane) with the blade, through the blade deflection angle's of first blade district and second blade district reasonable design, improve the atress size in the first blade district of low rotational speed to correspondingly reduce the atress size in the second blade district of high rotational speed, can effectively reduce the pressure pulsation intensity on the whole blade like this, thereby reduced axial fan's noise; and the whole stress of the inner and outer rings of the blade is not affected, the total air quantity of the axial flow fan can be ensured to be unchanged, and the pressure distribution of the inner and outer rings of the blade is more uniform, so that 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
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without inventive effort.
Fig. 1 is a schematic structural view of an axial flow fan in the related art;
fig. 2 is a schematic structural diagram 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 schematic structural diagram of an axial flow fan according to an exemplary embodiment of the present invention;
FIG. 3C is an exploded view of the blade shown in FIG. 3B at the turning angle of the C-C plane;
FIG. 3D is a schematic view of the turning angle of the vane shown in FIG. 3B, from the end close to the hub portion to the end far from the hub portion 1, showing the corresponding radial distribution curve;
fig. 3E is a schematic structural view 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 structural view of an axial flow fan according to an exemplary embodiment of the present invention in another direction;
FIG. 4B is a schematic structural view of a portion A of the axial flow fan of the embodiment shown in FIG. 3A;
FIG. 4C is a schematic structural view 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 graph of the prediction result of noise analysis prediction of the axial flow fan of the present invention and the axial flow fan in the related art based on the Fukano wake vortex noise model;
fig. 6B is a graph comparing the noise test result of the axial flow fan and the noise test result of the axial flow fan in the related art according to an exemplary embodiment of the present invention, and reveals a result graph of the sound pressure level spectrum distribution of the corresponding axial flow fan;
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 the exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements unless otherwise indicated. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with the present invention. Rather, they are merely examples of apparatus and methods consistent with certain aspects of the invention, as detailed in the appended 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 and all possible combinations of one or more of the associated listed items.
It is to be understood that although the terms first, second, third, etc. may be used herein to describe various information, such information should not be limited to these terms. These terms are only used to distinguish one type of information from another. For example, the first information may also be referred to as second information, and similarly, the second information may also be referred to as first information, without departing from the scope of the present invention. The word "if" as used herein may be interpreted as "at … …" or "when … …" or "in response to a determination", depending on the context.
The following describes the axial flow fan and the air conditioner with the same in detail with reference to the accompanying drawings. The features of the following examples and embodiments may be combined with each other without conflict.
With reference 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 portion 1 and a plurality of blades 2, wherein the hub portion 1 is circular, and the blades 2 are respectively fixed on the outer peripheral surface of the hub portion 1. The number of blades 2 can be selected as desired, for example, 3, 4. In the present embodiment, the plurality of blades 2 are provided at intervals on the outer peripheral surface of the hub portion 1.
Referring to fig. 2, the blade 2 may comprise a first blade region 21 (i.e. the root or the inner blade ring) and a second blade region 22 (i.e. the outer blade ring), the first blade region 21 and the second blade region 22 being adjacent, the first blade region 21 being arranged at an end of the blade 2 close to the hub 1 and the second blade region 22 being arranged at an end of the blade 2 remote from the hub 1. In the present embodiment, the first blade regions 21 and the second blade regions 22 are distributed on a concentric circle having the center of the hub portion 1 (i.e., the center of the hub portion 1) as the center. Alternatively, the outer edges of the ends of the blades 2 remote from the hub portion 1 are also distributed on a concentric circle on which the second blade region 22 is located.
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 rear edge of the blade 2 (i.e., an air outlet side of the blade 2), that is, on the same blade 2, a blade side where the first edge 211 and the third edge 221 are located is opposite to a blade side where the second edge 212 and the fourth edge 222 are located. In the embodiment of the present invention, the two sides of the blade 2 refer to two sides of the blade 2 connected to the hub portion 1.
In the present embodiment, the first edge 211 forms a recess along a radial direction (i.e. a radial direction of the blade 2), the second edge 212 forms a protrusion along the radial direction, the third edge 221 protrudes in the radial direction relative to the first edge 211, and the fourth edge 222 forms a recess with an end of the second edge 212 away from the hub portion 1.
The utility model discloses axial fan divides into first blade district 21 (inner circle) and second blade district 22 (outer lane) with blade 2, through the rational design of the blade deflection angle of first blade district 21 and second blade district 22, improves the atress size of first blade district 21 of low rotational speed to correspondingly reduce the atress size of second blade district 22 of high rotational speed (compare axial fan in fig. 1, the utility model discloses axial fan's the total atress size of blade 2 does not change or change less), can effectively reduce the pressure pulsation intensity on the whole blade like this to axial fan's noise has been reduced; and, the whole atress of blade inner and outer lane is not influenced, can guarantee axial fan total amount of wind unchangeable, and blade inner and outer lane pressure distribution is more even, has effectively reduced the pressure artery on whole blade 2 to further improve axial fan efficiency.
The rotation direction (arrow direction in fig. 2) of the axial flow fan 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 rotation 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 of 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 of the second edge 212 to the first edge 211 of the blade 2.
In some embodiments, the difference L between the radius of the concentric circles corresponding to the first blade region 21 and the radius of the hub portion 11(as shown in FIG. 2) the difference L between the radius of the concentric circle corresponding to the second vane region 22 and the radius of the hub portion 10The ratio (as shown in FIG. 2) is greater than 55% and less than 85%, that is, 55%<L1/L0<85%, e.g., L1/L0The amount of the additive can 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 other numerical values greater than 55% and less than 85%.
In some embodiments, the line connecting the innermost side of the first edge 211 and the center of the circle makes an angle θ with the line connecting the outermost side of the third edge 221 and the center of the circle1(as shown in FIG. 2) greater than 10 degrees and less than 25 degrees, e.g., θ1The angle may 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, or may be other values greater than 10 degrees and less than 25 degrees, and may be specifically selected according to actual requirements.
In some embodiments, the angle θ between the line connecting the outermost side of the second edge 212 and the center of the circle and the line connecting the outermost side of the fourth edge 2222Greater than 5 degrees and less than 15 degrees, e.g. theta2The angle may be 6 degrees, 7 degrees, 8 degrees, 9 degrees, 10 degrees, 11 degrees, 12 degrees, 13 degrees, or 14 degrees, or may be other values greater than 5 degrees and less than 15 degrees, and may be specifically selected according to actual requirements.
Optionally, the first edge 211 is curved and/or the second edge 212 is curved, the curved edges further reducing noise. As a possible implementation, in conjunction with fig. 2, 3A, 4A, and 5, the first edge 211 and the second edge 212 are both curved.
Further, the blades 2 of the present embodiment are not entirely in the same plane.
Specifically, referring to fig. 3A to 3F, the distribution curve of the turning angle of the blade 2 in the radial direction changes from a straight line segment to a parabolic segment from one end of the blade 2 close to the hub portion 1 to one end of the blade 2 away from the hub portion 1. The straight line segment is in an increasing trend (as shown in fig. 3F), the opening of the parabola corresponding to the parabolic segment faces downward, and the parabolic segment includes the vertex of the parabola. Optionally, the parabola corresponding to the parabola segment is a symmetric structure.
In the embodiment of the present invention, for the same circumference C-C, the intersection point of the leading edge of the C-C and the blade 2 is Le, the intersection point of the leading edge of the blade 2 is Te, and fig. 3B can be understood as the orthogonal cylindrical plane formed by the circumference surface corresponding to the C-C after orthogonal transformation, wherein the included angle β between the Le end and the C-CLeThe included angle beta between the Te end and C-CTeThe difference of two (β)Le-βTe) This is understood as the angle of deflection Te at the trailing edge of the C-C face of the blade 2 relative to Le at the leading edge. Note that the turning angle Y of the blade 2 according to the embodiment of the present invention is also a deflection angle of the trailing edge Te with respect to the leading edge Le of the C-C surface of the blade 2. It should be noted that, in the embodiment of the present invention, the parabolic segment may include a curved shape with a small deviation from the parabolic shape (smaller than a preset deviation threshold), and may also include a curved shape with a superposed parabolic shape.
As a possible implementation, the equation of the parabola can be the following equation:
Y＝A-(X-B)2 (1)
in the formula (1), the first and second groups,
x is the normalized radial position of the blade;
Riis the radial position of the blade;
Rhthe radius of a concentric circle corresponding to the second blade area;
Rsis the radius of the hub portion;
and (A, B) is the vertex of the parabola, wherein A is the maximum turning angle of the blade, and B is the radial position of the blade corresponding to the maximum turning angle.
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 ° (units of angle, degrees) and less than or equal to 28 °, e.g., a can be 23 °, 23.5 °, 24 °, 24.5 °, 25 °, 25.5 °, 26 °, 26.5 °, 27 °, 27.5 °, 28 °. Of course, a can be other degrees greater than 23 ° and less than 28 °.
Optionally, 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 have other values between 6 and 8.
Optionally, in some embodiments, C is greater than or equal to 10 ° and less than or equal to 15 °, where C is a 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 degree magnitudes between greater than 10 ° and less than 15 °.
It is to be understood that the parabolic equation is not limited to the above equation (1), but may be a variation of equation (1), or other parabolic equations.
Referring to fig. 2, fig. 3A, fig. 4A to fig. 4B and fig. 5 again, 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 serrations, wherein the serrations of the third edge 221 may inhibit the blade 2 from moving and static interfering with other static components during the rotation process, for example, the axial flow fan is applied to an air conditioner, and the serrations of the third edge 221 may inhibit the blade 2 from moving and static interfering with static components in the air conditioner during the rotation process; the serration of the fourth edge 222 may ensure good sound quality characteristics.
In the following embodiments, the third edge 221 and the fourth edge 222 respectively include a plurality of continuous serrations.
The shape of the serrations may be designed as desired, for example, in some embodiments, as shown in FIGS. 4B and 4C, the serrations are shaped as sinusoids that reduce the amount of force applied to the second blade region 22 to reduce the noise of 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 (smaller than a preset deviation threshold) than the sinusoidal curve shape, and may also include a curve shape with a sinusoidal curve coinciding with the sinusoidal curve.
Optionally, the plurality of sawteeth of the third edge 221 have the same amplitude, and the structural design is simple; optionally, the plurality of sawteeth of the third edge 221 are of unequal amplitude, for example, the amplitude of the sawteeth located at the two ends of the third edge 221 is smaller than the amplitude of the sawteeth located at the middle of the third edge 221, which is beneficial to inhibiting dynamic and static interference with other static components during the rotation process of the blade 2, and reducing the magnitude of the stress on the third edge 221.
Optionally, the plurality of sawteeth of the third edge 221 have the same amplitude, and the structural design is simple; optionally, the plurality of sawteeth of the third edge 221 are of unequal amplitude, for example, the amplitude of the sawteeth located at the two ends of the fourth edge 222 is smaller than the amplitude of the sawteeth located in the middle of the fourth edge 222, which is beneficial to inhibiting the blade 2 from moving and static interference with other static components during the rotation process, and reducing the stress magnitude of the fourth edge 222.
As a possible implementation, the amplitude of the saw teeth at the two ends of the third edge 221 is smaller than the amplitude of the saw teeth at the middle of the third edge 221, and the amplitude of the saw teeth at the two ends of the fourth edge 222 is smaller than the amplitude of the saw teeth at the middle of the fourth edge 222.
Alternatively, the formula of the sinusoid is as follows:
A′*sin(x/P) (2)；
in formula (2), x is the position of the sawtooth in the radial direction, a' is the amplitude of the sawtooth, and P is the first empirical coefficient.
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 and 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 also 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 also include other values greater than 0.6 and less than 1.2.
In some embodiments, for 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, e.g., a' may include 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, 5.5mm, 6mm, and may also 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 also 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 is understood that the sinusoidal curve is not limited to equation (1), but may be other, such as a variation of equation (1).
Of course, the shape of the saw teeth is not limited to a sinusoidal shape, and may be other curved or non-curved shapes.
Fig. 6A is a comparison graph of the prediction result of noise analysis prediction of the axial flow fan of the present invention and the axial flow fan in the related art (the axial flow fan having the structural shape shown in fig. 1) based on the Fukano wake vortex noise model; fig. 6B is a comparison graph 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 according to the related art according to an exemplary embodiment of the present invention, that is, fig. 6B is a comparison graph of a noise test result determined by an actual test; fig. 6C is a partial schematic view of fig. 6B.
Specifically, adopt the Fukano wake vortex noise model analysis as in equation (3) the utility model discloses axial fan's in the noise and the correlation technique of axial fan's noise, Fukano wake vortex noise model is as follows:
in formula (3), E is the noise power in W;
ρ0the medium density is that the medium corresponding to the fan of the utility model is air, the unit is kg/m 3;
c0is the sound velocity, in m/s;
i is the number of the fan blades of the blade 2, and the axial flow fan in the embodiment of the utility model and the axial flow fan in the related technology both comprise 3 blades;
r is the radius in m;
rhis the radius of the first blade zone of the blade 2, in m;
rtis the radius of the second blade region of the blade 2, in m;
d is the wake vortex width in m;
w is the wake vortex relative speed, and the unit is m/s;
l is the position from the fan and the unit is m;
p0the acoustic reference sound pressure is 2e-5 Pa;
SPL is the noise sound pressure level magnitude, i.e., ordinate of FIG. 6A, in dB.
To axial fan among the correlation technique with the utility model discloses axial fan, all carry out following operation:
the blade is equally divided into 5 parts along the radial direction, and the parts are respectively 0-20% of Span, 20-40% of Span, 40-60% of Span, 60-80% of Span and 80-100% of Span from the outer peripheral surface close to the hub part to the direction far away from the outer peripheral surface of the hub part.
In every part in fig. 6A, the left square column is used for instructing the noise prediction result of the corresponding part of the axial flow fan in the related art, and the right square column is used for instructing the noise prediction result of the corresponding part of the axial flow fan in the embodiment of the present invention.
As can be seen from fig. 6A, compared with the axial flow fan in the related art, the axial flow fan span 40% -80% of the area noise value of the embodiment of the present invention is properly increased, the span 80% -100% of the area noise is greatly reduced, and the noise distribution of the different blade 2 parts of the axial flow fan is more reasonable; axial fan's among the correlation technique total noise size is 71.7dB, the utility model discloses axial fan's total noise size is 70.0dB, the utility model discloses axial fan's total noise descends 1.7 dB.
Further, install axial fan among the relevant art and the axial fan of the embodiment of the utility model on complete machine (air conditioning system) respectively and test, the test result can refer to fig. 6B and fig. 6C, wherein, curve 10' is the sound pressure level curve of axial fan (conventional design) among the relevant art under different frequencies, curve 10 is the sound pressure level curve of axial fan (hybrid design) of the embodiment of the utility model under different frequencies, the ordinate of fig. 6B and fig. 6C is noise sound pressure level size SPL, the unit is 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 according to the embodiment of the present invention is significantly reduced in the low frequency range. In the range of 200-600 Hz in FIG. 6C, the sound pressure level at the passing frequency of the blade is reduced by 5-10 dB. Compare the axial fan of correlation technique, the utility model discloses axial fan's sound quality is better, and final complete machine noise descends ~ 1 dBA.
Therefore, the axial flow fan provided by the embodiment of the invention 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; in addition, the total air volume of the axial flow fan can be ensured to be 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 utility model discloses axial fan can use on the air conditioner, also can use on other equipment that need the fan.
The embodiment of the utility model provides an air conditioner is still provided, including the outer machine of air conditioner, wherein, the outer machine of air conditioner includes actuating system and the axial fan of above-mentioned embodiment, and actuating system is used for driving axial fan and rotates.
Optionally, the driving system includes a motor, and a main shaft of the motor is connected to the hub portion 1 of the axial flow fan to drive the axial flow fan to rotate. Of course, the driving system can also select other power systems and is not limited to the motor.
The above description is only a preferred embodiment of the present invention, and should not be taken as limiting the invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. An axial flow fan, comprising:
a hub portion, the hub portion being circular; and
the blades comprise a first blade area and a second blade area which are adjacent, wherein the first blade area is arranged at one end, close to the hub portion, of each blade, the second blade area is arranged at one end, far away from the hub portion, of each blade, and the first blade area and the second blade area are distributed on a concentric circle taking the center of the hub portion as the circle center;
the first blade area comprises a first edge and a second edge which are positioned on two sides of the blade, the second blade area comprises a third edge and a fourth edge which are positioned on two sides of the blade, the first edge and the third edge are arranged on the front edge of the blade, and the second edge and the fourth edge are arranged on 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 in the radial direction, and the fourth edge and one end of the second edge far away from the hub portion form a recess.
2. The axial flow fan of claim 1, wherein a ratio of a difference between a radius of a concentric circle corresponding to the first blade region and a radius of the hub portion to a difference between a radius of a concentric circle corresponding to the second blade region and a radius of the hub portion is greater than 55% and less than 85%; and/or the presence of a gas in the gas,
the included angle between the connecting line of the innermost side of the first edge and the circle center and the connecting line of the outermost side of the third edge and the circle center is more than 10 degrees and less than 25 degrees; and/or
And the angle between the connecting line of the outermost side of the second edge and the circle center and the connecting line of the outermost side of the fourth edge is more than 5 degrees and less than 15 degrees.
3. The axial flow fan according to claim 1, wherein a profile of a camber angle of the blade in a radial direction changes from a straight line segment to a parabolic segment from an end of the blade close to the hub portion to an end of the blade far from the hub portion, wherein the straight line segment exhibits an increasing trend, an opening of a parabola corresponding to the parabolic segment faces downward, and the parabolic segment includes an apex of the parabola.
4. The axial fan of claim 3, wherein the equation of the parabola is:
Y＝A-(X-B)2；
wherein,
x is the normalized radial position of the blade;
Riis the radial position of the blade;
Rhis a concentric circle corresponding to the second blade regionThe radius of (a);
Rsis the radius of the hub portion;
and (A, B) is the vertex of the parabola, wherein A is the maximum turning angle of the blade, and B is the radial position of the blade corresponding to the maximum turning angle.
5. The axial fan according to claim 4, characterized in that 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 degrees and less than or equal to 15 degrees, wherein C is the turning angle of the blade corresponding to the starting point of the straight line segment.
6. The axial fan of claim 1, wherein at least one of the third edge and the fourth edge includes a plurality of continuous serrations.
7. The axial fan of claim 6, wherein the saw-tooth shape is sinusoidal.
8. The axial fan of claim 7, wherein the formula of the sinusoid is as follows:
A′*sin(x/P)；
wherein x is the position of the sawtooth in the radial direction, A' is the amplitude of the sawtooth, and P is the first empirical coefficient.
9. The axial fan according to claim 8, wherein 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.
10. An air conditioner, characterized by comprising an air conditioner outdoor unit, wherein the air conditioner outdoor unit comprises a driving system and the axial flow fan as claimed in any one of claims 1 to 9, and the driving system is used for driving the axial flow fan to rotate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920569425.2U CN209892505U (en) | 2019-04-24 | 2019-04-24 | Axial fan and air conditioner with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920569425.2U CN209892505U (en) | 2019-04-24 | 2019-04-24 | Axial fan and air conditioner with same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN209892505U true CN209892505U (en) | 2020-01-03 |
Family
ID=69019819
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920569425.2U Active CN209892505U (en) | 2019-04-24 | 2019-04-24 | Axial fan and air conditioner with same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN209892505U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109915411A (en) * | 2019-04-24 | 2019-06-21 | 特灵空调***(中国)有限公司 | Axial flow blower and air-conditioning with it |
-
2019
- 2019-04-24 CN CN201920569425.2U patent/CN209892505U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109915411A (en) * | 2019-04-24 | 2019-06-21 | 特灵空调***(中国)有限公司 | Axial flow blower and air-conditioning with it |
| CN109915411B (en) * | 2019-04-24 | 2024-03-22 | 特灵空调***(中国)有限公司 | Axial fan and air conditioner with same |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP1862675B1 (en) | Axial fan assembly | |
| US5611667A (en) | Transverse fan | |
| US20040136830A1 (en) | Fan | |
| US20110023526A1 (en) | Centrifugal fan | |
| EP1797334A1 (en) | High efficiency axial fan | |
| WO2011062062A1 (en) | Multi-blade fan for centrifugal blower | |
| JPH03253794A (en) | Fluid circulator and its manufacture | |
| WO2005081979A2 (en) | Fan assembly and method | |
| EP1792085A1 (en) | Axial impeller with enhanced flow | |
| AU2012203104B2 (en) | Axial fan assembly | |
| US7794198B2 (en) | Centrifugal fan and apparatus using the same | |
| CN109915411B (en) | Axial fan and air conditioner with same | |
| US9523370B2 (en) | Blower with curved blades | |
| CN209892505U (en) | Axial fan and air conditioner with same | |
| JP2018141371A (en) | Axial blower impeller and axial blower | |
| JP3137897B2 (en) | Once-through fan | |
| US6712584B2 (en) | Fan blade | |
| JPH08200283A (en) | Cross-flow fan and air conditioner provided with it | |
| JPH09100795A (en) | Air conditioner | |
| JP2004100663A (en) | Air conditioner | |
| US20050123404A1 (en) | Fan blade | |
| CN110566500A (en) | Impeller of centrifugal ventilator | |
| CN207814038U (en) | Cross-flow fan blade, cross-flow fan blade, indoor unit and air conditioner | |
| CN113404711B (en) | Barrel-type axial flow fan | |
| CN105240316A (en) | Axial flow fan blade, axial flow fan and air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |