WO2021233482A1 - 轴流叶轮以及具有该轴流叶轮的轴流风机、空调器 - Google Patents

轴流叶轮以及具有该轴流叶轮的轴流风机、空调器 Download PDF

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Publication number
WO2021233482A1
WO2021233482A1 PCT/CN2021/108152 CN2021108152W WO2021233482A1 WO 2021233482 A1 WO2021233482 A1 WO 2021233482A1 CN 2021108152 W CN2021108152 W CN 2021108152W WO 2021233482 A1 WO2021233482 A1 WO 2021233482A1
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Prior art keywords
line
axial flow
flow impeller
arc
edge contour
Prior art date
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PCT/CN2021/108152
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English (en)
French (fr)
Inventor
朱训智
王元
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Qingdao Haier Air Conditioner Gen Corp Ltd
Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
Original Assignee
Qingdao Haier Air Conditioner Gen Corp Ltd
Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
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Publication of WO2021233482A1 publication Critical patent/WO2021233482A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F04D29/384—Blades characterised by form
    • F04D29/386—Skewed blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D19/00—Axial-flow pumps
    • F04D19/002—Axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38—Blades
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

  • the invention belongs to the technical field of axial flow impellers, and specifically provides an axial flow impeller and an axial flow fan and an air conditioner having the axial flow impeller.
  • Axial impellers are widely used due to their simple structure, convenient installation, and large air volume.
  • the fans installed on the walls or roofs of workshops and workshops for indoor ventilation use axial flow impellers.
  • the external units of air conditioners used in homes, offices, shopping malls, etc. use axial flow impellers to quickly perform heat exchangers. Heat exchange and so on.
  • the problem of greater noise in axial flow impellers has been constantly criticized by people.
  • the axial flow impeller includes a hub 1 and three blades 2 uniformly distributed on the outer circumference of the hub 1.
  • the blades 2 have a leading edge 21, a side edge 22 and a trailing edge 23, and a sinusoidal sawtooth structure is provided on the trailing edge 23 230.
  • the efficiency of the fan using the axial flow impeller is improved to a certain extent, the pressure pulsation in the wake area is reduced, and the fundamental frequency and double frequency of the axial flow impeller are suppressed.
  • Low-frequency noise reduces the noise to a certain extent.
  • the noise reduction effect of the axial flow impeller cannot meet higher noise reduction requirements.
  • the present invention provides an axial flow impeller, including a hub and A plurality of blades distributed in the circumferential direction of the hub, in a projection along the axial direction of the hub, the outline of the blade includes a leading edge outline, a trailing edge outline, and a side edge outline, the trailing edge outline It includes a first arc line, a curve, and a second arc line that are connected in sequence.
  • the first arc line and the second arc line are located on the same arc structure line.
  • the points are all located on the side of the arc construction line close to the front edge contour line.
  • the curve is a spline curve defined by N control points K i , wherein the control point K i is determined by the following method: being concentric with the contour circle of the hub and the length of the radius of the arc into a plurality of positioning circle R i formed between the leading edge and the arcuate contour line are configured to L i, each of said control points are located at a K i of the length L i is the arc and the arc is divided into two sections corresponding to the length of the arc segment is formed between the leading edge and the contour of the control point K i l i, the side edge profile
  • N 6, R 1 , R 2 , R 3 , R 4 , R 5 and R 6 decrease in sequence, (L 1 -l 1 ), (L 3 -l 3 ), (L 4 -l 4 ), (L 5 -l 5 ), and (L 6 -l 6 ) are all smaller than (L 2 -l 2 ).
  • the ratio of the radius of the leading edge contour line to the radius of the side edge contour line is 0.585, and/or the radius of the arc structure line and the radius of the side edge contour line are The ratio is 0.68.
  • the number of the blades is three.
  • the axial flow impeller includes a hub and a plurality of blades distributed in the circumferential direction of the hub.
  • the contour of the blade includes the contour line of the leading edge.
  • the trailing edge contour line and the side edge contour line, the trailing edge contour line includes the first circular arc line, the curve and the second circular arc line connected in sequence, the first circular arc line and the second circular arc line are located on the same circular arc structure line
  • the points between the two end points of the curve are all located on the side of the arc construction line close to the front edge contour line.
  • the trailing edge of the blade is set to include a first arc line and a second arc line located on the same arc structure line, and a curve recessed to the front edge between the first arc line and the second arc line, that is,
  • An inner concave notch is formed in the middle area of the trailing edge, and both ends of the inner concave notch form a convex arc-shaped part.
  • the inner concave notch and the convex arc-shaped part cooperate to change the pressure distribution state of the blade and reduce the separation of the surface layer. The vortex generated at the trailing edge is reduced, and the noise generated by the airflow is reduced.
  • the convex arc part ensures the connection strength of the blade and avoids the severe vibration and noise caused by the rotation of the blade due to insufficient strength. Under the condition of the same speed, the air volume of the axial flow impeller remains basically unchanged, which reduces the noise, and reduces the weight of the axial flow impeller, reduces the manufacturing cost, and reduces the driving power of the motor.
  • the curve control points by N K i defined spline is formed, the control point K i is determined by: the hub contour circle concentric circle having a radius R i of the plurality of locating the leading edge contour and the arc length of the arc formed between the construction line L i, respectively, each control point K i are located on a length L i and the circular arc corresponding to an arc divided into two sections, the leading edge contour
  • the length of the arc segment formed with the control point K i is l i
  • the radius of the side edge contour line is R
  • the shape of the curve is related to the size of the front edge contour line, so that the blade maintains a specific shape and size between the front edge and the rear edge, which can reduce noise and weaken the recessed gap at the rear edge.
  • the influence on the air volume ensures the air volume of the axial flow impeller.
  • N 6, R 1 , R 2 , R 3 , R 4 , R 5 and R 6 decrease in sequence, (L 1 -l 1 ), (L 3 -l 3 ), (L 4 -l 4 ), (L 5 -l 5 ), and (L 6 -l 6 ) are all smaller than (L 2 -l 2 ). That is to say, among the six control points, the arc distance between the control point K 2 and the trailing edge contour line is the largest, and the indentation gap is more concave near the outer edge contour line. Because along the radial direction of the blade, the closer to the contour line of the outer edge, the greater the relative flow velocity of the airflow, and the more likely it is to separate the surface layer. Through the above arrangement, it is possible to more effectively reduce the separation of the surface layer, reduce eddy currents, and reduce noise.
  • the present invention also provides an axial flow fan, which includes the axial flow impeller according to any one of the above technical solutions.
  • the present invention also provides an air conditioner, which includes the axial flow impeller according to any one of the above technical solutions. It should be noted that the axial flow fan and the air conditioner have all the technical effects of the above axial flow impeller, which will not be repeated here.
  • Fig. 1 is a structural diagram of an axial flow impeller of an existing air conditioner
  • Figure 2 is a structural diagram of an axial flow impeller of an air conditioner according to an embodiment of the present invention
  • Figure 3 is an axial projection view of an axial flow impeller of an air conditioner according to an embodiment of the present invention.
  • FIG. 4 is a graph showing the relationship between noise and rotational speed of an axial flow impeller of an air conditioner according to an embodiment of the present invention and an axial flow impeller of an existing air conditioner;
  • Fig. 5 is a graph showing the relationship between power and air volume of an axial flow impeller of an air conditioner according to an embodiment of the present invention and an axial flow impeller of an existing air conditioner.
  • connection can also be a detachable connection or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or a connection between two components.
  • connection can also be a detachable connection or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or a connection between two components.
  • the present invention provides an axial flow impeller.
  • the contour of the blade includes a leading edge contour line, a trailing edge contour line, and a side contour line.
  • the trailing edge contour line includes a first arc line, a curve, and a second circle connected in sequence
  • the arc, the first arc line and the second arc line are located on the same arc structure line, and the points between the two end points of the curve are all located on the side of the arc structure line close to the front edge contour line.
  • the trailing edge of the blade is set to include the first arc line and the second arc line located on the same arc structure line, and the forward edge recessed between the first arc line and the second arc line
  • the middle area of the trailing edge forms an inner concave notch, and the two ends of the inner concave notch form a convex arc part.
  • the inner concave notch and the convex arc part cooperate to change the pressure distribution state of the blade and reduce the surface layer Separation, thereby reducing the vortex generated at the trailing edge and reducing the noise generated by the airflow.
  • the convex arc-shaped part of the trailing edge ensures the connection strength of the blade and avoids the severe vibration and noise caused by the blade rotation due to insufficient strength. Under the condition of the same speed, the air volume of the axial flow impeller remains basically unchanged, which reduces the noise, and reduces the weight of the axial flow impeller, and reduces the power of the motor.
  • FIGS. 2 to 5 is a structural diagram of an axial flow impeller of an air conditioner according to an embodiment of the present invention
  • FIG. 3 is a projection view of an axial flow impeller of an air conditioner according to an embodiment of the present invention
  • FIG. 5 is an axial flow impeller of an air conditioner and an existing air conditioner according to an embodiment of the present invention The graph of the relationship between the power of the axial flow impeller and the air volume.
  • the axial flow impeller of the air conditioner includes a hub 1 and three blades 2 distributed on the outer periphery of the hub 1.
  • the contour of the blade 2 in the projection along the axial direction of the hub 1, includes a leading edge contour line 211, a side edge contour line 221, and a trailing edge contour line 231.
  • the end of the edge contour line 211 away from the hub 1 is connected to the end of the trailing edge contour line 231 away from the hub 1, the other end of the front edge contour line 211 is connected to the contour circle 11 of the hub 1, and the other end of the trailing edge contour line 231 is connected to the hub 1.
  • the contour circles 11 are connected.
  • the trailing edge contour line 231 includes a first circular arc line 2311, a curve 2312, and a second circular arc line 2313 connected in sequence.
  • the first circular arc line 2311 and the second circular arc line 2313 are located on the same circular arc structure line.
  • the points between the two end points of the curve 2312 are all located on the side of the arc structure line 3 close to the front edge contour line 211.
  • the curve 2312 is a spline curve defined by six control points K 1 , K 2 , K 3 , K 4 , K 5 , and K 6.
  • the control points K 1 , K 2 , K 3 , K 4 , K 5 , and K 6 are determined as follows: they are concentric with the contour circle 11 of the hub 1 and have radii R 1 , R 2 , R 3 , R 4 ,
  • the lengths of the arc formed by the six positioning circles of R 5 and R 6 between the leading edge contour line 211 and the arc structure line 3 are respectively L 1 , L 2 , L 3 , L 4 , L 5 , L 6 .
  • the control points K 1 , K 2 , K 3 , K 4 , K 5 , and K 6 are respectively located on the arcs with lengths L 1 , L 2 , L 3 , L 4 , L 5 , and L 6 and correspond to the circles
  • the arc is divided into two segments.
  • the lengths of the arc segments between the leading edge contour line 211 and the control points K 1 , K 2 , K 3 , K 4 , K 5 , and K 6 are l 1 , l 2 , l 3 , l 4 , l 5 , l 6 .
  • the radius of the side contour line is R, R 1 /R, l 1 /L 1 , R 2 /R, l 2 /L 2 , R 3 /R, l 3 /L 3 , R 4 /R, l 4 / L 4 , R 5 /R, l 5 /L 5 , R 6 /R, and l 6 /L 6 meet the preset conditions.
  • the trailing edge contour line 231 of the blade 2 By setting the trailing edge contour line 231 of the blade 2 to include a first circular arc line 2311 and a second circular arc line 2313 on the same circular arc structure line 3, and a first circular arc line 2311 and a second circular arc line 2313
  • the concave curve 2312 between the front edge, the middle area of the rear edge 22 forms an inner concave notch, and the two end regions of the inner concave notch form a convex arc-shaped part.
  • the inner concave notch and the convex arc-shaped part cooperate to change
  • the pressure distribution state of the blade 2 is reduced, the separation of the boundary layer is reduced, the vortex generated at the trailing edge is reduced, and the noise generated by the air flow is reduced.
  • the convex arc part ensures the connection strength of the blade, and avoids the severe vibration and noise caused by the blade rotation due to insufficient strength.
  • the curve 2312 is a spline curve defined by six control points, and the positions of the six control points are related to the radii of the leading edge contour line and the side edge contour line, so that the blade maintains a specific distance between the leading edge and the trailing edge.
  • the shape and size can not only reduce the noise, but also weaken the influence of the recessed notch at the rear edge on the air volume, and ensure the air volume of the axial flow impeller.
  • R 1 , R 2 , R 3 , R 4 , R 5 and R 6 decrease in sequence, (L 1 -l 1 ), (L 3 -l 3 ), (L 4 -l 4 ), (L 5 -l 5 ) and (L 6 -l 6 ) are both smaller than (L 2 -l 2 ). That is to say, among the six control points, the arc distance between the control point K2 and the trailing edge contour line is the largest, and the inner concave notch is more concave near the outer edge contour line. Because along the radial direction of the blade, the closer to the contour line of the outer edge, the greater the relative flow velocity of the airflow, and the more likely it is to separate the surface layer. Through this arrangement, it is possible to more effectively reduce the separation of the surface layer, reduce eddy currents, and reduce noise.
  • the end of the curve 2312 close to the outer contour line 221 to the end close to the hub 1 first bends in the direction close to the front contour line 211, and then slowly bends away from the front contour line 211.
  • This shape The inner recessed notch greatly reduces the turbulence, reduces the noise, and makes the trailing edge 23 change slowly near the hub 1, so that the air pressure distribution is more uniform, and the resistance to the air flow is reduced.
  • the number of control points is six is also a preferred setting method. Those skilled in the art can adjust the number of control points according to the actual situation. For example, the number of control points can be three, five, seven or more. Wait.
  • the curve 2312 can also be a wavy curve or a curve of other shapes, as long as the points between the two end points of the curve are located on the arc structure line 3 close to the front edge contour line 211. Just side.
  • the ratio of the radius of the leading edge contour line 211 to the radius of the side edge contour line 221 is 0.585, and the ratio of the radius of the arc structure line 3 to the side edge contour line 221 is 0.68.
  • the ratio of the radius of the leading edge contour 211 to the radius of the side contour 221 may be 0.585, and the ratio of the radius of the arc structure line 3 to the side contour 221 is not limited. It is also possible to only set the ratio of the radius of the arc structure line 3 to the side edge contour line 221 to be 0.68, and the ratio of the radius of the leading edge contour line 211 to the radius of the side edge contour line 221 is not limited.
  • the number of blades 2 of the axial flow impeller is three, which can not only meet the conventional air output requirement, but also reduce the weight of the impeller, and avoid excessive power of the driving motor required.
  • the number of blades 2 of the axial flow impeller is three, which is only a preferred embodiment, and those skilled in the art can adjust it according to the actual situation to adapt to specific applications. For situations where the air supply volume is required to be large, the number of blades in the axial flow impeller can be increased.
  • the number of blades can be four, five, six, seven, eight, etc., preferably an odd number Blades to avoid resonance when an even number of blades rotate.
  • the radius of the contour circle of the hub 1 is 85mm
  • the radius of the leading edge contour line 211 is 160mm
  • the radius of the arc structure line 3 is 186mm
  • the radius R of the line 221 is 273 mm.
  • the radii R 1 , R 2 , R 3 , R 4 , R 5 , and R 6 of the positioning circle corresponding to the control points K 1 , K 2 , K 3 , K 4 , K 5 , and K 6 are 253mm, 222mm, 195mm, respectively , 172mm, 151mm, 126mm.
  • Concentric with the contour circle 11 of the hub 1 and the radii are R 1 , R 2 , R 3 , R 4 , R 5 , R 6 and the positioning circle formed between the front edge contour line 211 and the arc structure line 3
  • the lengths L 1 , L 2 , L 3 , L 4 , L 5 , and L 6 are 447mm, 389mm, 341mm, 299mm, 261mm, and 218mm, respectively, which are concentric with the contour circle 11 of the hub 1, and the radii are R 1 and R 2 respectively.
  • the axial flow impeller of the above-mentioned shape and size of the present invention and the existing axial flow impeller with a sinusoidal sawtooth structure set on the trailing edge are compared and tested with the driving motor respectively. After the test, the parameters of the two are obtained as shown in Table 1 As shown in Table 2:
  • the noise of the axial flow impeller of the present invention is reduced by 1.3-1.8 dB compared with the noise of the existing axial flow impeller, which significantly reduces the noise of the impeller.
  • the impeller of the present invention consumes less power than the conventional impeller when the air output is the same. It is 6-22w smaller, and the power consumption is reduced by 6-12%. It can be seen from Table 2 that when the speed is the same, the air volume basically remains unchanged. That is to say, compared with the existing axial flow impeller, the axial flow impeller of the present invention not only reduces noise when it is driven at the same speed by the drive motor, but also meets the higher noise reduction requirements, while ensuring the air output, and at the same time. On this basis, the power consumption of the drive motor is reduced.
  • the axial flow impeller of the present invention has lower noise, can meet higher noise reduction requirements, and meets the consumption of the same air output.
  • the power is lower, and it has better energy saving and emission reduction advantages.
  • the present invention also provides an axial flow fan, which includes the axial flow impeller of any one of the above embodiments.
  • the present invention also provides an air conditioner, which includes the axial flow impeller of any one of the above embodiments.
  • the air conditioner can be a window type air conditioner, a wall-mounted air conditioner, a cabinet type air conditioner, a ceiling type air conditioner, and the like.
  • the axial flow impeller includes a hub and a plurality of blades distributed in the circumferential direction of the hub.
  • the trailing edge contour line includes a first circular arc line, a curve and a second circular arc line connected in sequence, and the first circular arc line and the second circular arc line are located on the same circular arc structure line, The points between the two end points of the curve are all located on the side of the arc construction line close to the front edge contour line.
  • the trailing edge of the blade By setting the trailing edge of the blade to include a first circular arc line and a second circular arc line located on the same circular arc structure line, and a curved line recessed to the front edge between the first circular arc line and the second circular arc line, That is, an inner concave notch is formed in the middle area of the trailing edge, and the two ends of the inner concave notch form a convex arc part.
  • the inner concave notch and the convex arc part cooperate to change the pressure distribution state of the blade and reduce the separation of the surface layer. , Thereby reducing the vortex generated at the trailing edge and reducing the noise generated by the airflow.
  • the air volume remains basically unchanged, which reduces the size of the noise, and reduces the weight of the axial flow impeller, and reduces the power of the motor.
  • the convex arc part ensures the connection strength of the blade, and avoids the vibration and noise caused by the rotation of the blade due to insufficient strength.

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  • General Engineering & Computer Science (AREA)
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Abstract

轴流叶轮、轴流风机和空调器。轴流叶轮包括轮毂（1）和分布在轮毂（1）周向的多个叶片（2），在沿轮毂（1）轴向的投影中，叶片（2）的后缘轮廓线（231）包括第一圆弧线（2311）、曲线（2312）以及第二圆弧线（2313），第一圆弧线（2311）和第二圆弧线（2313）位于同一圆弧构造线（3）上，曲线（2312）位于圆弧构造线（3）靠近前缘轮廓线（211）的一侧。该轴流叶轮改变了叶片的压力分布状态，减少了附面层分离，降低了噪音。

Description

轴流叶轮以及具有该轴流叶轮的轴流风机、空调器 技术领域
本发明属于轴流叶轮技术领域，具体提供一种轴流叶轮以及具有该轴流叶轮的轴流风机、空调器。
背景技术
轴流叶轮由于结构简单、安装方便、风量大等优点而被广泛应用。例如，车间厂房的墙壁或屋顶安装的用于对室内换气的风机采用轴流叶轮，目前家庭、办公场所、商场等使用的空调器的外机中采用轴流叶轮来对换热器进行快速换热等。随着人们对产品品质的要求越来越高，轴流叶轮存在的噪音较大的问题被人们不断诟病。
鉴于此，市场上出现了一种新的轴流叶轮。如图1所示，轴流叶轮包括轮毂1以及在轮毂1外周均布的三个叶片2，叶片2具有前缘21、侧缘22和后缘23，后缘23上设置有正弦形锯齿结构230。通过在后缘23上设置正弦形锯齿结构230，在一定程度上提高了采用该轴流叶轮的风机的效率，减弱了尾迹区压力脉动，抑制了轴流叶轮转动时基频和二倍频的低频噪音，在一定程度上降低了噪音。不过，该轴流叶轮的降噪效果并不能满足更高的降噪要求。
因此，本领域需要一种新的技术方案来解决上述问题。
发明内容
为了解决现有技术中的上述问题，即为了解决现有的轴流叶轮的降噪效果不能够满足更高的降噪要求的问题，一方面本发明提供了一种轴流叶轮，包括轮毂和分布在所述轮毂周向的多个叶片，在沿所述轮毂轴向的投影中，所述叶片的轮廓包括前缘轮廓线、后缘轮廓线和侧缘轮廓线，所述后缘轮廓线包括依次连接的第一圆弧线、曲线以及第二圆弧线，所述第一圆弧线和所述第二圆弧线位于同一圆弧构造线上，所述曲线的两端点之间的点均位于所述圆弧构造线靠近所述前缘轮廓线的一侧。
在上述轴流叶轮的优选技术方案中，所述曲线为由N个控制点K i限定形成的样条曲线，其中所述控制点K i通过如下方式确定：与所述轮毂的轮廓圆同心且半径为R i的多个定位圆在所述前缘轮廓线与所述圆弧构造线之间形成的圆弧的长度分别为L i，每个所述控制点K i分别位于一个所述长度为L i的圆弧上并将对应的圆弧分为两段，在所述前缘轮廓线与所述控制点K i之间形成的圆弧段的长度为l i，所述侧缘轮廓线的半径为R，并且R i/R和l i/L i满足预设条件，其中，i＝1-N。
在上述轴流叶轮的优选技术方案中，N＝6，R 1、R 2、R 3、R 4、R 5以及R 6依次减小，(L 1-l 1)、(L 3-l 3)、(L 4-l 4)、(L 5-l 5)以及(L 6-l 6)均小于(L 2-l 2)。
在上述轴流叶轮的优选技术方案中，R 2/R＝0.78～0.84，l 2/L 2＝0.881。
在上述轴流叶轮的优选技术方案中，R 1/R＝0.9～0.96，l 1/L 1＝1，R 3/R＝0.69～0.74，l 3/L 3＝0.886，R 4/R＝0.6～0.67，l 4/L 4＝0.916，R 5/R＝0.52～0.58，l 5/L 5＝0.943，R 6/R＝0.43～0.49，l 6/L 6＝1。
在上述轴流叶轮的优选技术方案中，所述R i/R满足以下条件的至少一个：R 1/R＝0.93；R 2/R＝0.81；R 3/R＝0.71；R 4/R＝0.63；R 5/R＝0.55；R 6/R＝0.46。
在上述轴流叶轮的优选技术方案中，所述前缘轮廓线的半径与侧缘轮廓线的半径的比值为0.585，并且/或者所述圆弧构造线的半径与侧缘轮廓线的半径的比值为0.68。
在上述轴流叶轮的优选技术方案中，所述叶片的数量为三个。
本领域技术人员能够理解的是，在本发明的技术方案中，轴流叶轮包括轮毂和分布在轮毂周向的多个叶片，在沿轮毂轴向的投影中，叶片的轮廓包括前缘轮廓线、后缘轮廓线和侧缘轮廓线，后缘轮廓线包括依次连接的第一圆弧线、曲线以及第二圆弧线，第一圆弧线和第二圆弧线位于同一圆弧构造线上，曲线的两端点之间的点均位于圆弧构造线靠近前缘轮廓线的一侧。叶片后缘设置成包括位于同一圆弧构造线上的第一圆弧线和第二圆弧线以及位于第一圆弧线和第二圆弧线之间的向前缘凹陷的曲线，即在后缘中部区域形成内凹缺口，内凹缺口的两端区域 形成外凸的弧状部分，内凹缺口和外凸的弧状部分配合，改变了叶片的压力分布状态，减少了附面层分离，从而减少了后缘部位产生的涡流，降低了气流产生的噪音。外凸的弧状部分，保证了叶片的连接强度，避免了叶片由于强度不够导致转动时剧烈振动产生噪音。在相同转速的条件下，轴流叶轮的风量基本保持不变，降低了噪音，并且减小了轴流叶轮的重量，降低了制造成本，降低了电机的驱动功率。
优选地，曲线为由N个控制点K i限定形成的样条曲线，控制点K i通过如下方式确定：与轮毂的轮廓圆同心且半径为R i的多个定位圆在前缘轮廓线与圆弧构造线之间形成的圆弧的长度分别为L i，每个控制点K i分别位于一个长度为L i的圆弧上并将对应的圆弧分为两段，在前缘轮廓线与控制点K i之间形成的圆弧段的长度为l i，侧缘轮廓线的半径为R，曲线为由K 1、K 2、…、K 6六个控制点限定形成的样条曲线，并且R i/R和l i/L i满足预设条件，其中，i＝1-N。通过这样的设置，曲线的形状与前缘轮廓线的尺寸相关联，使叶片在前缘后后缘之间保持特定的形状尺寸，既能够降低噪音，又能够消弱后缘处的内凹缺口对风量的影响，保证轴流叶轮的风量。
优选地，N＝6，R 1、R 2、R 3、R 4、R 5以及R 6依次减小，(L 1-l 1)、(L 3-l 3)、(L 4-l 4)、(L 5-l 5)以及(L 6-l 6)均小于(L 2-l 2)。也就是说，在六个控制点中，控制点K 2与后缘轮廓线的圆弧距离最大，内凹缺口在靠近外缘轮廓线处内凹程度较大。由于沿叶片的径向，越靠近外缘轮廓线，气流的相对流速越大，更容易出现附面层分离。通过上述设置，能够更加有效地降低附面层分离，减少涡流，降低噪音。
另一方面，本发明还提供了一种轴流风机，所述风机包括上述技术方案中任一项所述的轴流叶轮。
此外，本发明还提供了一种空调器，所述空调器包括上述技术方案中任一项所述的轴流叶轮。需要说明的是，该轴流风机和空调器具有上述轴流叶轮的全部技术效果，在此不再赘述。
附图说明
下面参照附图来描述本发明的优选实施方式，附图中：
图1是现有空调器的一种轴流叶轮的结构图；
图2是本发明一种实施例的空调器的轴流叶轮的结构图；
图3是本发明一种实施例的空调器的轴流叶轮沿轴向的投影图；
图4是本发明一种实施例的空调器的轴流叶轮和现有空调器的轴流叶轮的噪音与转速的关系曲线图；
图5是本发明一种实施例的空调器的轴流叶轮和现有空调器的轴流叶轮的功率与风量的关系曲线图。
附图标记列表：
1、轮毂；11、轮廓圆；2、叶片；21、前缘；211、前缘轮廓线；22、侧缘；221、侧缘轮廓线；23、后缘；230、正弦形锯齿结构；231、后缘轮廓线；2311、第一圆弧线；2312、曲线；2313、第二圆弧线；3、圆弧构造线。
具体实施方式
首先，本领域技术人员应当理解的是，下面描述的实施方式仅仅用于解释本发明的技术原理，并非旨在限制本发明的保护范围。例如，虽然本发明是结合空调器的轴流叶轮来进行介绍，但是这并不能对本发明的保护范围构成限制，本领域技术人员可以根据需要对其作出调整，以便适应具体的应用场合，如本发明的轴流叶轮适用于电机散热风扇、换气风机等。显然，调整后的技术方案仍将落入本发明的保护范围。
需要说明的是，在本发明的描述中，术语“前”、“后”、“内”、“外”等指示方向或位置关系的术语是基于附图所示的方向或位置关系，这仅仅是为了便于描述，而不是指示或暗示所述装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性。
此外，还需要说明的是，在本发明的描述中，除非另有明确的规定和限定，术语“安装”、“设置”、“相连”、“连接”应作广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，还可以是两个元件内部的连通。对于本领域技术人员而言，可根据具体情况理解上述术语在本发明中的具体含义。
基于背景技术指出的现有的轴流叶轮的降噪效果不能够满足更高的降噪要求的问题，本发明提供了一种轴流叶轮，轴流叶轮包括轮毂和分布在轮毂周向的多个叶片，在沿轮毂轴向的投影中，叶片的轮廓包括前缘轮廓线、后缘轮廓线和侧缘轮廓线，后缘轮廓线包括依次连接的第一圆弧线、曲线以及第二圆弧线，第一圆弧线和第二圆弧线位于同一圆弧构造线上，曲线的两端点之间的点均位于圆弧构造线靠近前缘轮廓线的一侧。
也就是说，将叶片后缘设置成包括位于同一圆弧构造线上的第一圆弧线和第二圆弧线以及位于第一圆弧线和第二圆弧线之间的向前缘凹陷的曲线，后缘中部区域形成内凹缺口，内凹缺口的两端区域形成外凸的弧状部分，内凹缺口和外凸的弧状部分配合，改变了叶片的压力分布状态，减少了附面层分离，从而减少了后缘部位产生的涡流，降低了气流产生的噪音。后缘外凸的弧状部分，保证了叶片的连接强度，避免了叶片由于强度不够导致转动时剧烈振动产生噪音。在相同转速的条件下，轴流叶轮的风量基本保持不变，降低了噪音，并且减小了轴流叶轮的重量，降低了电机的功率。
下面参照图2至图5，来对本发明的一种优选的实施例进行详细介绍。其中，图2是本发明一种实施例的空调器的轴流叶轮的结构图，图3是本发明一种实施例的空调器的轴流叶轮沿轴向的投影图，图4是本发明一种实施例的空调器的轴流叶轮和现有空调器的轴流叶轮的噪音与转速的关系曲线图，图5是本发明一种实施例的空调器的轴流叶轮和现有空调器的轴流叶轮的功率与风量的关系曲线图。
如图2所示，空调器的轴流叶轮包括轮毂1以及分布于轮毂1的外周的三个叶片2。如图3所示，在沿轮毂1轴向的投影中，叶片2的轮廓包括前缘轮廓线211、侧缘轮廓线221和后缘轮廓线231，侧缘轮廓线221的两端分别与前缘轮廓线211远离轮毂1的一端和后缘轮廓线231远离轮毂1的一端连接，前缘轮廓线211的另一端与轮毂1的轮廓圆11相连，后缘轮廓线231的另一端与轮毂1的轮廓圆11相连。
继续参照图3，后缘轮廓线231包括依次连接的第一圆弧线2311、曲线2312以及第二圆弧线2313，第一圆弧线2311和第二圆弧线2313位于同一圆弧构造线3上，曲线2312的两端点之间的点均位于圆弧 构造线3靠近前缘轮廓线211的一侧。曲线2312为由K 1、K 2、K 3、K 4、K 5、K 6六个控制点限定形成的样条曲线。控制点K 1、K 2、K 3、K 4、K 5、K 6是通过如下方式确定的：与轮毂1的轮廓圆11同心且半径分别为R 1、R 2、R 3、R 4、R 5、R 6的六个定位圆在在前缘轮廓线211和圆弧构造线3之间形成的圆弧的长度分别为L 1、L 2、L 3、L 4、L 5、L 6，控制点K 1、K 2、K 3、K 4、K 5、K 6分别位于长度分别为L 1、L 2、L 3、L 4、L 5、L 6的圆弧上并将对应圆弧分成两段，在前缘轮廓线211与控制点K 1、K 2、K 3、K 4、K 5、K 6之间的圆弧段的长度分别为l 1、l 2、l 3、l 4、l 5、l 6。侧缘轮廓线的半径为R，R 1/R、l 1/L 1、R 2/R、l 2/L 2、R 3/R、l 3/L 3、R 4/R、l 4/L 4、R 5/R、l 5/L 5、R 6/R、l 6/L 6满足预设条件。
通过将叶片2的后缘轮廓线231设置成包括位于同一圆弧构造线3上的第一圆弧线2311和第二圆弧线2313以及位于第一圆弧线2311和第二圆弧线2313之间的向前缘凹陷的曲线2312，后缘22的中部区域形成了内凹缺口，并且内凹缺口的两端区域形成外凸的弧状部分，内凹缺口和外凸的弧状部分配合，改变了叶片2的压力分布状态，减少了附面层分离，从而减少了后缘部位产生的涡流，降低了气流产生的噪音。同时，外凸的弧状部分，保证了叶片的连接强度，避免了叶片由于强度不够导致转动时剧烈振动产生噪音。
曲线2312为由六个控制点限定形成的样条曲线，并且六个控制点的位置与前缘轮廓线和侧缘轮廓线的半径相关联，使叶片在前缘后后缘之间保持特定的形状尺寸，既能够降低噪音，又能够消弱后缘处的内凹缺口对风量的影响，保证轴流叶轮的风量。
优选地，R 1、R 2、R 3、R 4、R 5以及R 6依次减小，(L 1-l 1)、(L 3-l 3)、(L 4-l 4)、(L 5-l 5)以及(L 6-l 6)均小于(L 2-l 2)。也就是说，在六个控制点中，控制点K2与后缘轮廓线的圆弧距离最大，内凹缺口在靠近外缘轮廓线处内凹程度较大。由于沿叶片的径向，越靠近外缘轮廓线，气流的相对流速越大，更容易出现附面层分离。通过这样的设置，能够更加有效地降低附面层分离，减少涡流，降低噪音。优选地，R 2/R＝0.78～0.84，l 2/L 2＝0.881。
进一步优选地，R 1/R＝0.9～0.96，l 1/L 1＝1，R 3/R＝0.69～0.74，l 3/L 3＝0.886，R 4/R＝0.6～0.67，l 4/L 4＝0.916，R 5/R＝0.52～0.58，l 5/L 5＝0.943，R 6/R＝0.43～0.49，l 6/L 6＝1。
通过这样的设置，曲线2312靠近外缘轮廓线221的一端向靠近轮毂1的一端，先向靠近前缘轮廓线211的方向弯曲，然后缓慢向远离前缘轮廓线211的方向弯曲，这种形状的内凹缺口在很大程度上减少了涡流，降低了噪音，并且使后缘23在靠近轮毂1的部位缓慢变化，气流压力分布更加均匀，减少了气流流动的阻力。
本领域技术人员可以理解的是，上述参数的限定，仅是一种较为优选的设置方式，本领域技术人员也可以根据需要对其作出调整，如在另一种可行的实施方式中，R 1、R 2、R 3、R 4、R 5、R 6分别为0.97、0.86、0.8、0.7、0.6、0.5，l 1/L 1＝1，l 2/L 2＝0.9，l 3/L 3＝0.92，l 4/L 4＝0.93，l 5/L 5＝0.94，l 6/L 6＝1，也可以设置成其他数值，只要R 1、R 2、R 3、R 4、R 5以及R 6依次减小，(L 1-l 1)、(L 3-l 3)、(L 4-l 4)、(L 5-l 5)以及(L 6-l 6)均小于(L 2-l 2)即可。另外，控制点的数量为六个也是一种较为优选的设置方式，本领域技术人员可以根据实际情况调整控制点的数量，如控制点的数量可以是三个、五个、七个或者更多个等。此外，在另外一种可行的设置方式中，曲线2312也可以是波浪形曲线或者其他形状的曲线，只要曲线的两端点之间的点均位于圆弧构造线3靠近前缘轮廓线211的一侧即可。
优选地，R 1/R＝0.93，R 2/R＝0.81，R 3/R＝0.71，R 4/R＝0.63，R 5/R＝0.55，R 6/R＝0.46。通过对六个控制点K 1、K 2、K 3、K 4、K 5、K 6的进一步优化，气流流经后缘22产生涡流的风险进一步降低，降噪效果得到进一步提升。本领域技术人员可以理解的是，在另外的一种可行的实施方式中，叶片2的参数可以仅满足R 1/R＝0.93，R 2/R＝0.81，R 3/R＝0.71，R 4/R＝0.63，R 5/R＝0.55，R 6/R＝0.46中的一个，也可以满足其中的多个组合。此外，R 1/R、R 2/R、R 3/R、R 4/R、R 5/R、R 6/R的具体数值也可以根据实际情况进行调整，如R 1/R＝0.91、0.94或者0.95等，R 2/R＝0.79、0.80或者0.83等，R 3/R＝0.70、0.72或者0.74等，R 4/R＝0.61、0.65或者0.67等，R 5/R＝0.53、0.56或者0.57等，R 6/R＝0.44、0.47或者0.48等。
优选地，前缘轮廓线211的半径与侧缘轮廓线221的半径的比值为0.585，并且圆弧构造线3与侧缘轮廓线221的半径的比值为0.68。 通过这样的优化，在保证叶轮的降噪效果的同时，保证了叶片2的有效出风量。本领域技术人员可以理解的是，可以仅使前缘轮廓线211的半径与侧缘轮廓线221的半径的比值为0.585，对于圆弧构造线3与侧缘轮廓线221的半径的比值不作限定，也可以仅使圆弧构造线3与侧缘轮廓线221的半径的比值为0.68，对于前缘轮廓线211的半径与侧缘轮廓线221的半径的比值不作限定。
在上述实施例中，轴流叶轮的叶片2的数量为三个，既能够满足常规的出风量需求，又能够减少叶轮的重量，避免所需的驱动电机的功率过大。本领域技术人员可以理解的是，轴流叶轮的叶片2的数量为三个，仅是一种较为优选的实施方式，本领域技术人员可以根据实际情况对其作出调整，以便适应具体的应用场合，如对于送风量要求较大的场合，可以增大轴流叶轮中的叶片的数量，叶片的数量可以是四个、五个、六个、七个、八个等，优选地选用奇数个叶片，避免偶数个叶片在转动时产生共振。
如图4和图5所示，经过大量的实验，根据实验结果绘制出了本发明空调器优选的空调器的轴流叶轮和现有空调器的轴流叶轮的噪音与转速的关系曲线图以及本发明优选的空调器的轴流叶轮和现有空调器的轴流叶轮的功率与风量的关系曲线图。其中，现有叶轮的后缘处设置有正弦形锯齿结构，本发明叶轮与现有叶轮的区别仅在于叶片的后缘形状尺寸不同。
一种具体规格的轴流叶轮沿轮毂1的轴线方向的投影中，轮毂1的轮廓圆半径为85mm，前缘轮廓线211的半径为160mm，圆弧构造线3的半径为186mm，侧缘轮廓线221的半径R为273mm。控制点K 1、K 2、K 3、K 4、K 5、K 6分别对应的定位圆的半径R 1、R 2、R 3、R 4、R 5、R 6分别为253mm、222mm、195mm、172mm、151mm、126mm。与轮毂1的轮廓圆11同心、半径分别为R 1、R 2、R 3、R 4、R 5、R 6的定位圆在前缘轮廓线211和圆弧构造线3之间形成的圆弧的长度L 1、L 2、L 3、L 4、L 5、L 6分别为447mm、389mm、341mm、299mm、261mm、218mm，与轮毂1的轮廓圆11同心、半径分别为R 1、R 2、R 3、R 4、R 5、R 6的定位圆在前缘轮廓线211和曲线2312之间形成的圆弧的长度l 1、l 2、l 3、l 4、l 5、l 6分别为447mm、343mm、302mm、274mm、246mm、218mm。分别借 助驱动电机对本发明上述形状尺寸的轴流叶轮以及与该轴流扇叶区别仅在于后缘设置正弦形锯齿结构的现有轴流叶轮进行对比测试，测试后得到二者的参数如下表1和表2所示：
表1
转速rpm 现有叶轮噪音dB(A) 本发明叶轮噪音dB(A)
850 62.3 60.5
800 60.1 58.8
750 58.3 56.8
700 56.4 54.7
650 54.1 52.6
600 52 50.7
表2
Figure PCTCN2021108152-appb-000001
如表1和图4所示，在相同的转速下，本发明的轴流叶轮的噪音比现有轴流叶轮的噪音降低了1.3-1.8dB，明显降低了叶轮的噪音。
如表2和如图5所示，本发明叶轮与现有叶轮相比，在出风量相同的情况下，驱动本发明叶轮的电机所消耗的功率比驱动现有叶轮的电机所消耗的功率减小了6-22w，功耗降低了6-12％。从表2可以看出，在转速相同的情况下，风量基本向保持不变。也就是说，本发明的轴流叶轮与现有轴流叶轮相比，被驱动电机以相同转速驱动时，不仅降低了噪音，满足了更高的降噪需求，同时保证了出风量，并在此基础上降低了驱动电机的功耗。
通过上述的实验数据对比，可以看出，本发明的轴流叶轮与现有的轴流叶轮相比，具有更低的噪音，能够满足更高的降噪要求，并且在满足相同出风量所消耗的功率更低，具有更好的节能减排优势。
另一方面，本发明还提供了一种轴流风机，该轴流风机包括上述实施例中任一项的轴流叶轮。
此外，本发明还提供了一种空调器，该空调器包括上述实施例中任一项的轴流叶轮。空调器可以是窗式空调器，壁挂式空调器、立柜式空调器、吊顶式空调器等。
通过以上描述可以看出，在本发明的技术方案中，轴流叶轮包括轮毂和分布在轮毂周向的多个叶片，在沿轮毂轴向的投影中，叶片的轮廓包括前缘轮廓线、后缘轮廓线和侧缘轮廓线，后缘轮廓线包括依次连接的第一圆弧线、曲线以及第二圆弧线，第一圆弧线和第二圆弧线位于同一圆弧构造线上，曲线的两端点之间的点均位于圆弧构造线靠近前缘轮廓线的一侧。通过将叶片后缘设置成包括位于同一圆弧构造线上的第一圆弧线和第二圆弧线以及位于第一圆弧线和第二圆弧线之间的向前缘凹陷的曲线，即在后缘中部区域形成内凹缺口，内凹缺口的两端区域形成外凸的弧状部分，内凹缺口和外凸的弧状部分配合，改变了叶片的压力分布状态，减少了附面层分离，从而减少了后缘部位产生的涡流，降低了气流产生的噪音。在相同转速的条件下，风量基本保持不变，降低了噪音的大小，并且减小了轴流叶轮的重量，降低了电机的功率。同时，外凸的弧状部分保证了叶片的连接强度，避免了叶片由于强度不够导致转动时振动产生噪音。
本领域的技术人员能够理解，尽管在此所述的一些实施例包括其它实施例中所包括的某些特征而不是其它特征，但是不同实施例的特征的组合意味着处于本发明的范围之内并且形成不同的实施例。例如，在本发明的权利要求书中，所要求保护的实施例的任意之一都可以以任意的组合方式来使用。
至此，已经结合附图所示的优选实施方式描述了本发明的技术方案，但是，本领域技术人员容易理解的是，本发明的保护范围显然不局限于这些具体实施方式。在不偏离本发明的原理的前提下，本领域技术人员可以对相关技术特征作出等同的更改或替换，这些更改或替换之后的技术方案都将落入本发明的保护范围之内。

Claims (10)

  1. 一种轴流叶轮，其特征在于，包括轮毂和分布在所述轮毂周向的多个叶片，在沿所述轮毂轴向的投影中，所述叶片的轮廓包括前缘轮廓线、后缘轮廓线和侧缘轮廓线，所述后缘轮廓线包括依次连接的第一圆弧线、曲线以及第二圆弧线，所述第一圆弧线和所述第二圆弧线位于同一圆弧构造线上，所述曲线的两端点之间的点均位于所述圆弧构造线靠近所述前缘轮廓线的一侧。
  2. 根据权利要求1所述的轴流叶轮，其特征在于，所述曲线为由N个控制点K i限定形成的样条曲线，其中所述控制点K i通过如下方式确定：
    与所述轮毂的轮廓圆同心且半径为R i的多个定位圆在所述前缘轮廓线与所述圆弧构造线之间形成的圆弧的长度分别为L i，每个所述控制点K i分别位于一个所述长度为L i的圆弧上并将对应的圆弧分为两段，在所述前缘轮廓线与所述控制点K i之间形成的圆弧段的长度为l i，所述侧缘轮廓线的半径为R，并且R i/R和l i/L i满足预设条件，其中，i＝1-N。
  3. 根据权利要求2所述的轴流叶轮，其特征在于，N＝6，R 1、R 2、R 3、R 4、R 5以及R 6依次减小，(L 1-l 1)、(L 3-l 3)、(L 4-l 4)、(L 5-l 5)以及(L 6-l 6)均小于(L 2-l 2)。
  4. 根据权利要求3所述的轴流叶轮，其特征在于，R 2/R＝0.78～0.84，l 2/L 2＝0.881。
  5. 根据权利要求4所述的轴流叶轮，其特征在于，R 1/R＝0.9～0.96，l 1/L 1＝1，R 3/R＝0.69～0.74，l 3/L 3＝0.886，R 4/R＝0.6～0.67，l 4/L 4＝0.916，R 5/R＝0.52～0.58，l 5/L 5＝0.943，R 6/R＝0.43～0.49，l 6/L 6＝1。
  6. 根据权利要求5所述的轴流叶轮，其特征在于，所述R i/R满足以下条件的至少一个：
    R 1/R＝0.93；R 2/R＝0.81；R 3/R＝0.71；R 4/R＝0.63；R 5/R＝0.55；R 6/R＝0.46。
  7. 根据权利要求1至6中任一项所述的轴流叶轮，其特征在于，所述前缘轮廓线的半径与侧缘轮廓线的半径的比值为0.585，并且/或者所述圆弧构造线的半径与侧缘轮廓线的半径的比值为0.68。
  8. 根据权利要求7所述的轴流叶轮，其特征在于，所述叶片的数量为三个。
  9. 一种轴流风机，其特征在于，所述风机包括权利要求1至8中任一项所述的轴流叶轮。
  10. 一种空调器，其特征在于，所述空调器包括权利要求1至8中任一项所述的轴流叶轮。
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