WO2020125128A1 - Axial flow fan blade, ventilation device and air conditioner - Google Patents

Axial flow fan blade, ventilation device and air conditioner Download PDF

Info

Publication number
WO2020125128A1
WO2020125128A1 PCT/CN2019/109186 CN2019109186W WO2020125128A1 WO 2020125128 A1 WO2020125128 A1 WO 2020125128A1 CN 2019109186 W CN2019109186 W CN 2019109186W WO 2020125128 A1 WO2020125128 A1 WO 2020125128A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
axial
flow
tip
blade tip
Prior art date
Application number
PCT/CN2019/109186
Other languages
French (fr)
Chinese (zh)
Inventor
刘中杰
曹锋
和浩浩
邹建煌
Original Assignee
珠海格力电器股份有限公司
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Publication of WO2020125128A1 publication Critical patent/WO2020125128A1/en

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/26Rotors specially for elastic fluids
    • F04D29/32Rotors specially for elastic fluids for axial flow pumps
    • F04D29/38Blades
    • F04D29/388Blades characterised by construction
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/66Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/666Combating 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/66Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667Combating 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 present application relates to the technical field of impeller machinery, in particular to an axial fan, a ventilator, and an air conditioner.
  • the basic structure of the general fan blade includes a hub as a rotating shaft and a plurality of blades arranged radially on the outer periphery of the center. The leading edge of the blade flows in and blows out from the trailing edge portion of the blade after the blade is boosted, thereby forming a pressure surface and a suction surface.
  • a low-pressure region that is, a vortex
  • This vortex is mainly caused by the flow of air flowing through the high-pressure region of the pressure surface of the blade to the low-pressure region of the suction surface.
  • this phenomenon is called "leakage”.
  • the suction of the blades will cause boundary layer separation near the front edge, resulting in eddy currents.
  • the above two conditions will cause the vortex noise of the fan blade, which in turn causes the total value of the fan noise to increase, which affects the overall performance of the air conditioner.
  • the axial flow blade tip is designed to be bent or folded in the direction of the pressure surface toward the suction surface, as shown in FIGS. 1 to 6, and the detailed bending diagram is shown in FIGS. 7 to Figure 8, detailed diagram of hemming is shown in Figure 9 to Figure 10.
  • the design intent is to control the diffusion of the blade tip vortex by reducing the pressure difference between the suction surface and the pressure surface at the blade tip to avoid secondary flow losses.
  • it while reducing the pressure difference on the suction pressure surface, it also caused a decrease in the fan blade's functional capacity, resulting in a decrease in the amount of wind generated by the fan blade.
  • the hemming structure shown in FIGS. 1 to 10 is adopted, which is “L” type (L lower end is the blade tip), or the bending structure is “J” type (The lower end of J is the blade tip) It is used to alleviate the pressure difference between the pressure surface and the suction surface, so as to avoid the leakage of the airflow and the influence of the leakage airflow on the mainstream flow.
  • the key parameters of the hemming structure include the angle a1 or a2 of the hemming edge, the position of the hemming edge D2, and the range of the hemming edge at the tip of the blade.
  • the key parameters of the hemming structure include the bending radius R1 or R2, and the bending position D2. Bending is within the range of the blade tip. Obviously, after adopting such a structure that the pressure faces the suction surface with a single hem or a bend, the working force of the blade 4 near the blade tip will be reduced, that is, the pressure on the pressure surface near the blade tip will decrease and the pressure on the suction surface will increase, resulting in the blade 4 The functional capacity here is reduced, and the air volume generated by the axial flow blades is reduced. In particular, the axial fan blades for air conditioning, the main work area of the blade 4 lies in the trailing edge of the blade tip.
  • the main purpose of the present application is to provide an axial fan blade, a ventilator, and an air conditioner, so as to effectively control the diffusion of the blade tip vortex.
  • a further object of the present application is to provide an axial fan blade with two bending or flanging structures at the same time, which can control the degree of turbulence of the leakage airflow at the tip of the blade and reduce the turbulence generated by the axial fan blade here noise.
  • At least one embodiment of the present application provides an axial-flow blade, including a hub and a plurality of blades, and the two surfaces of each blade are a pressure surface on the air outlet side and a suction surface on the air inlet side, respectively.
  • the radially outward edge portion is the blade tip, and the blade tip of each blade is provided with a first edge and a second edge, the first edge is bent and extends toward the suction surface, and the second edge is oriented The pressure surface is bent and extended.
  • the first side and the second side are a bent structure or a folded structure relative to the blade body.
  • the maximum outer diameter of the first side is equal to the maximum outer diameter of the second side.
  • the maximum outer diameter of the first side is smaller than the maximum outer diameter of the second side.
  • the first side and the second side are disposed within the entire length of the blade tip.
  • the first side and the second side are disposed in a partial range of the blade tip.
  • the maximum outer diameter of the first side is greater than the maximum outer diameter of the second side.
  • the first side is an arc bend with a first radius
  • the second side is an arc bend with a second radius
  • the first radius is smaller than the second radius
  • the first side is a flange having a first angle with the blade body
  • the second side is a flange with a second angle with the blade body, the first An angle is smaller than the second angle.
  • the first side is an arc-shaped bend
  • the second side is a folded edge having a second angle with the blade body
  • the setting range of the first side and the second side accounts for 0.4-0.6 of the total length of the blade tip.
  • a ventilation device which includes an axial fan blade, and the axial fan blade is the aforementioned axial fan blade.
  • an air conditioner which includes an axial fan blade, and the axial fan blade is the aforementioned axial fan blade.
  • the beneficial effect obtained by adopting the above optional technical solution is that the structure of the blade tip is changed from the original two-dimensional edge structure to a three-dimensional space interval.
  • This structure can play the role of buffering pressure, alleviating airflow leakage, and controlling the flow, so as to improve the working capacity of the axial fan blade, increase the air volume, and reduce the noise by controlling the blade tip leakage vortex.
  • the fan blades of the present application enhance the function of the blades, realize the control of the blade tip leakage vortex, and reduce the blade noise.
  • Figure 1 Schematic diagram of the front view of the existing folding axial flow fan blade
  • Figure 2 Schematic diagram of the current side of the folded flange axial flow fan blade
  • Figure 3 Schematic diagram of the top view of the existing folding axial flow fan blades
  • Figure 4 Schematic diagram of the front view of the existing bending axial fan
  • Figure 5 Schematic diagram of the side view of the existing bending axial fan blade
  • Figure 6 Schematic diagram of the top structure of the existing bending axial fan
  • Figure 7 The detailed structure diagram of the existing folded edge axial flow fan blade 2
  • Figure 8 The detailed structural schematic diagram of the existing folding edge axial flow fan blade 3;
  • Figure 9 Existing bending axial flow vane Figure 5 Detailed structural diagram of the bending structure
  • Figure 10 The detailed schematic diagram of the bending structure of the existing bending axial flow blade 6;
  • Figure 11 A schematic diagram of the front view of the first embodiment of the present application.
  • Figure 12 Schematic diagram of a side view of an embodiment of the present application.
  • Figure 13 Schematic diagram of the top view of the first embodiment of the present application.
  • Figure 14 A detailed schematic diagram of the tip bending of an embodiment of the present application.
  • Figure 15 A schematic diagram of the front view of the second embodiment of the present application.
  • Figure 16 Schematic diagram of a side view of an embodiment of the present application.
  • Figure 17 Schematic diagram of the top view of the second embodiment of the present application.
  • Figure 18 Detailed structural diagram of the bending structure of the second embodiment of the present application.
  • FIG. 19 Schematic diagram of the structure of the two-blade crimping or bending area according to the embodiment of the present application.
  • Figure 20 Detailed schematic diagram of the hemming structure of the third embodiment of the present application.
  • Figure 21 Comparison of relative velocity distribution at the downstream of the blade near the tip of the blade
  • Figure 22 Comparison of the velocity distribution of the wind blade near the blade tip.
  • An embodiment of the present application provides an axial fan blade, which mainly includes a hub 5 and a plurality of blades 4, and the two surfaces of each blade 4 are a pressure surface 3 on the outlet side and a suction surface 1 on the inlet side, respectively.
  • the radially outward edge portion of the blade 4 is a blade tip 2.
  • Each blade tip 2 of the blade 4 is provided with a first side 21 and a second side 22. The first side 21 faces the suction surface 1 Bending and extending, the second side 22 is bent and extending toward the pressure surface 3.
  • the air flow here is relatively turbulent. It is the main area of secondary flow, leakage, and return flow, and the main source of noise. Therefore, the design of the structure here has a significant impact on the performance of the fan blades.
  • Existing design of the blade tip of the axial flow blade whether it is a "L" shape with a folded structure or a "J" shape with a curved structure, the outermost blade tip is a single two Dimensional curve, the airflow is easy to produce secondary flow, leakage, backflow and other turbulent flow through the gap formed with the surrounding static components.
  • the axial fan blade structure provided by the embodiment of the present application has bends at the blade tip of the blade 4 toward the pressure surface 3 and the suction surface 1, respectively, so that it can be formed Type, or the folded-edge structure "Y" type, the structure of the blade tip and the surrounding static parts form an area with a substantially triangular cross-section, and the gap is changed from the original two-dimensional edge structure to a three-dimensional space interval.
  • the shape of the three-dimensional space can be changed, which can play a role in buffering pressure, alleviating airflow leakage, and controlling the flow, which can improve the working capacity and increase of the axial fan blade. Air volume and reduce noise by controlling blade tip leakage vortex.
  • Definition a1 In Figure 7, the fold line is tangent to both sides along the polyline, and the angle between the two tangents is a1; Similarly, definition a2: In Figure 8, the fold line is made tangent to the sides along the polyline, and the two tangents The included angle is a2; Definition a3: In Figure 20, the three crimped surfaces along the fold line to the fold line are tangent, the angle between the tangent of the blade near the inner side and the tangent to the first crimped surface is a1, and the blade is near the inner side The angle between the tangent and the tangent of the second hemming surface is a3.
  • R1, R2, R3 are similar to a1, a2, a3, here is different from fold line as tangent, but tangent circle at the fold line, the definition of tangent radius is named R1, R2, R3.
  • D1 is the center of the rotation axis, the axis of rotation is normal, and the maximum diameter is tangent to the outer diameter of the fan blade, that is, the maximum outer diameter of the suction surface bending or hemming structure
  • D2 is the center of rotation through the rotation axis
  • the rotation axis is a normal line to draw a circle.
  • the line diameter is D2 when the line is suddenly changed by the hemming structure fold line or the bending structure curvature
  • D3 is the circle drawn by the rotation axis as the center and the rotation axis as the normal line.
  • the pressure surface is bent or The outer diameter of the hemming structure.
  • b1 the outermost circle point of the leading edge of the blade, the starting point of the bend or edge along the direction of airflow, the angle between the two points and the center of the circle
  • b2 the outermost circle point of the trailing edge of the blade, bend or The starting point of the folding edge along the direction of airflow, the angle between the two points and the center of the circle.
  • FIG. 11 is a schematic view of a front view of an embodiment of the present application
  • FIG. 12 is a schematic view of a side view of an embodiment of the present application
  • FIG. 13 is a schematic structural view of a top view of an embodiment of the present application
  • FIG. 14 is a bent top of an embodiment of the present application Detailed structural diagram.
  • the entire range of the blade tip 2 of the blade 4 is set (the entire length of the blade tip refers to the entire length of the entire blade tip from the leading edge of the intake to the trailing edge of the outlet).
  • the first side 21 and the second side 22 the blade tip 2 as a whole type( The upper end is the blade tip 2), or the structure of the hemming is in the shape of "Y" (the upper end of Y is the blade tip 2).
  • the first side 21 is bent toward the suction surface 1 to one side to produce a structure with a bending radius of R1, thereby ensuring that the positive pressure area of the pressure surface is not affected, that is, the function of the wind blade is ensured.
  • the second side 22 also bends toward the pressure surface 3 to produce a structure with a bending radius of R3, thereby ensuring the pressure increase of the pressure surface 3 near the blade tip and reducing the pressure between the pressure surface 3 and the suction surface 1 If the difference is too large, it may cause air leakage.
  • the structure of the blade tip 2 is changed from the original two-dimensional edge structure to a three-dimensional space interval. This structure can play the role of buffering pressure, alleviating airflow leakage, and controlling the flow, so as to improve the working capacity of the axial flow blade, increase the air volume, and reduce the noise by controlling the blade tip leakage vortex.
  • the first side 21 is an arc bend with a first radius R1
  • the second side 22 is an arc bend with a second radius R3
  • the first radius R1 is greater than the second Radius R3.
  • FIG. 15 is a schematic view of the front view of the second embodiment of the present application
  • FIG. 16 is a schematic view of the side view of the second embodiment of the present application
  • FIG. 17 is a schematic top view of the second embodiment of the present application
  • FIG. 18 is a detailed view of the bending structure of the second embodiment of the present application
  • a structural schematic diagram, and FIG. 19 is a schematic structural diagram of a two-blade crimping or bending region according to an embodiment of the present application.
  • the partial range of the blade tip (with respect to the "full length range of the blade tip", only one end of the blade tip There is a first side and a second side), that is, from b1 to the outermost circle point of the leading edge of the blade 4 in FIG. 19, the starting point of the bend or edge along the direction of airflow, the angle between the two points and the center of the circle; b2——The starting point of the outermost circle point, bend or edge of the trailing edge of the blade 4 along the direction of airflow, and the angle between the two points and the center of the circle.
  • the blade is divided into multiple blade segments radially from inside to outside.
  • the tip of the blade is the blade segment near the outermost edge and the tip of the blade, and the full length of the blade tip is the entire part of the blade tip from the leading edge side of the intake to the trailing edge side of the outlet length.
  • This application adopts the structure of bending or flanging on both sides, which may be the same outer diameter on both sides, or may be unequal outer diameter. That is, D1 in FIG. 18 is the outermost diameter of the fan blade, that is, the outermost diameter of the bending or flanging structure of the pressure surface 3, and D3 is the outermost diameter of the bending or flanging structure of the suction surface 1, where D1 is selected to be greater than Or equal to D3.
  • D1 is selected to be greater than Or equal to D3.
  • the first side 21 and the second side 22, and the blade tip 2 as a whole type(
  • the upper end is the blade tip 2), or the structure of the hemming is in the shape of "Y" (the upper end of Y is the blade tip 2).
  • the first side 21 is bent toward the suction surface 1 to one side to produce a structure with a bending radius of R1, thereby ensuring that the positive pressure area of the pressure surface is not affected, that is, the function of the wind blade is ensured.
  • the second side 22 also bends toward the pressure surface 3 to produce a structure with a bending radius of R3, thereby ensuring the pressure increase of the pressure surface 3 near the blade tip and reducing the pressure between the pressure surface 3 and the suction surface 1 If the difference is too large, it may cause air leakage.
  • the first side 21 is an arc bend with a first radius R1
  • the second side 22 is an arc bend with a second radius R3
  • the first radius R1 is smaller than the second Radius R3.
  • the structure of the blade tip 2 is changed from the original two-dimensional edge structure to a three-dimensional space interval.
  • This structure can play the role of buffering pressure, alleviating airflow leakage, and controlling the flow, so as to improve the working capacity of the axial fan blade, increase the air volume, and reduce the noise by controlling the blade tip leakage vortex.
  • FIG. 20 is a detailed schematic diagram of the hemming structure of Embodiment 3 of the present application.
  • the first side 21 and the second side 22 are folded edges, wherein the angle between the first side 21 and the blade 4 is a1, and the angle between the second side 22 and the blade 4 is a3, the relationship between the two A1 ⁇ a3, or R1 ⁇ R3.
  • the relative velocity distribution at the position downstream of the blade near the blade tip is shown. Small fluctuations in the relative speed represent relatively low noise. Therefore, the structure of the first embodiment of the present application is similar to the existing blade structure. Has an advantage.
  • Figure 22 shows the velocity distribution of the wind blade near the blade tip.
  • Figure A shows the performance of the existing blade structure. There are two large vortices in the upstream and downstream of the blade tip.
  • Figure B shows the performance of the blade of the structure of the embodiment of this application. The vortexes on the upstream and downstream of the blade tip have been suppressed to some extent, and part of the turbulent flow is controlled in the space formed by the stationary area around the blade tip and the wind blade.

Abstract

Provided are an axial flow fan blade, a ventilation device and an air conditioner. The axial flow fan blade comprises a hub (5) and a plurality of blades (4), two surfaces of each blade (4) are respectively a pressure surface (3) on the air outlet side and a suction surface (1) on the air inlet side, the radial outward edge portion of each blade (4) is a blade tip, the blade tip of each blade is provided with a first edge (21) and a second edge (22), wherein the first edge (21) is bent and extends towards the suction surface, and the second edge (22) is bent and extends towards the pressure surface. The axial flow fan blade can improve working capability of the blades (4), control the blade tip leakage vortex of the blades (4), and reduce the noise of the fan blade.

Description

轴流风叶、换气装置以及空调器Axial fan, ventilation device and air conditioner
本申请要求于2018年12月19日提交至中国国家知识产权局、申请号为201811556731.9、发明名称为“轴流风叶、换气装置以及空调器”的专利申请的优先权。This application requires the priority of the patent application filed with the State Intellectual Property Office of China on December 19, 2018, with the application number 201811556731.9 and the invention titled "Axial Fan, Ventilation Device, and Air Conditioner".
技术领域Technical field
本申请涉及叶轮机械技术领域,尤其涉及一种轴流风叶、换气装置以及空调器。The present application relates to the technical field of impeller machinery, in particular to an axial fan, a ventilator, and an air conditioner.
背景技术Background technique
换气装置中为实现空气循环流动而通常采用各种风叶,一般风叶的基本结构包括作为旋转轴的轮毂和在这个中枢外周呈放射状排列的多个叶片组成,通过动力驱动旋转,空气从叶片的前缘流入,在叶片被升压后从叶片的后缘部吹出,从而形成了压力面和吸力面。In order to realize the air circulation flow, various fan blades are usually used in the ventilation device. The basic structure of the general fan blade includes a hub as a rotating shaft and a plurality of blades arranged radially on the outer periphery of the center. The leading edge of the blade flows in and blows out from the trailing edge portion of the blade after the blade is boosted, thereby forming a pressure surface and a suction surface.
现有的轴流风叶在运转过程中,经常会在吸力面的叶顶中间部分区域产生低压区,即涡流,该涡流主要是由气流经风叶的压力面高压区流向吸力面的低压区导致,这种现象被称为“泄露”。除此之外,叶片的吸力面前缘附近,会发生边界层分离,导致涡流产生。总之,上述两种情况皆会导致风叶的涡流噪声,进而导致风机噪音总值升高,影响了空调整机的总体性能。During the operation of the existing axial fan blades, a low-pressure region, that is, a vortex, is often generated in the middle part of the blade tip of the suction surface. This vortex is mainly caused by the flow of air flowing through the high-pressure region of the pressure surface of the blade to the low-pressure region of the suction surface. As a result, this phenomenon is called "leakage". In addition, the suction of the blades will cause boundary layer separation near the front edge, resulting in eddy currents. In short, the above two conditions will cause the vortex noise of the fan blade, which in turn causes the total value of the fan noise to increase, which affects the overall performance of the air conditioner.
为了减少叶顶涡,现有技术中会将轴流风叶叶顶设计成压力面向吸力面方向折弯或者折边形式,见图1至图6所示意,其中折弯详细图见图7至图8,折边详细图见图9至图10。其设计意图是通过降低吸力面、压力面在叶顶处的压力差,从而控制叶顶涡的扩散,避免引起二次流损失。但是这在降低吸压力面的压力差的同时,也引起了风叶做功能力的降低,导致风叶产生风量的降低。In order to reduce the blade tip vortex, in the prior art, the axial flow blade tip is designed to be bent or folded in the direction of the pressure surface toward the suction surface, as shown in FIGS. 1 to 6, and the detailed bending diagram is shown in FIGS. 7 to Figure 8, detailed diagram of hemming is shown in Figure 9 to Figure 10. The design intent is to control the diffusion of the blade tip vortex by reducing the pressure difference between the suction surface and the pressure surface at the blade tip to avoid secondary flow losses. However, while reducing the pressure difference on the suction pressure surface, it also caused a decrease in the fan blade's functional capacity, resulting in a decrease in the amount of wind generated by the fan blade.
现有设计轴流风叶在风叶旋转工作时,在轮毂5的外周向上会均布或者不均匀布置2至10个风叶叶片4对空气进行做功,产生风量。 此时,每个风叶叶片4的吸力面1是迎风面,因此吸力面1表面的压力分布为负值;而对应风叶叶片4反面压力面3则是在背风面,其表面压力分布为正值。因此在两者的交界的一个位置叶顶2处则存在着明显的压力差,从而导致气流会自然从压力面3通过叶顶2向吸力面1泄漏。压力差值越大则泄漏气流的动力越大。In the existing design, when the axial flow vane rotates, 2 to 10 wind vane blades 4 are uniformly distributed or unevenly arranged on the outer periphery of the hub 5 to perform work on the air to generate air volume. At this time, the suction surface 1 of each vane blade 4 is the windward surface, so the pressure distribution on the surface of the suction surface 1 is negative; and the pressure surface 3 corresponding to the reverse side of the blade 4 is on the leeward surface, and its surface pressure distribution is Positive value. Therefore, there is a significant pressure difference at the tip 2 of the blade at a position at the boundary between the two, causing the airflow to naturally leak from the pressure surface 3 through the blade tip 2 to the suction surface 1. The greater the pressure difference, the greater the power of the leaking airflow.
现有设计轴流风叶的叶顶2时,采用了图1至图10所示的折边结构,呈“L”型(L下端为叶顶),或者折弯结构,呈“J”型(J下端为叶顶),用来缓解压力面和吸力面的压力差,从而避免气流泄露量,以及泄漏气流对主流流动的影响。其折边结构的关键参数包括折边的夹角a1或者a2、折边的位置D2、折边在叶顶的范围,折弯结构的关键参数包括折弯的半径R1或者R2、折弯的位置D2、折弯在叶顶的范围。很明显,采用这种压力面向吸力面单折边或者折弯的结构后,会降低叶顶附近叶片4的做功能力,即叶顶附近压力面压力降低、吸力面压力升高,从而导致叶片4在此处的做功能力降低,轴流风叶产生的风量下降。特别是空调用轴流风叶,其叶片4主要做功区域在于叶顶尾缘处。When designing the blade tip 2 of the axial flow blade in the prior art, the hemming structure shown in FIGS. 1 to 10 is adopted, which is “L” type (L lower end is the blade tip), or the bending structure is “J” type (The lower end of J is the blade tip) It is used to alleviate the pressure difference between the pressure surface and the suction surface, so as to avoid the leakage of the airflow and the influence of the leakage airflow on the mainstream flow. The key parameters of the hemming structure include the angle a1 or a2 of the hemming edge, the position of the hemming edge D2, and the range of the hemming edge at the tip of the blade. The key parameters of the hemming structure include the bending radius R1 or R2, and the bending position D2. Bending is within the range of the blade tip. Obviously, after adopting such a structure that the pressure faces the suction surface with a single hem or a bend, the working force of the blade 4 near the blade tip will be reduced, that is, the pressure on the pressure surface near the blade tip will decrease and the pressure on the suction surface will increase, resulting in the blade 4 The functional capacity here is reduced, and the air volume generated by the axial flow blades is reduced. In particular, the axial fan blades for air conditioning, the main work area of the blade 4 lies in the trailing edge of the blade tip.
发明内容Summary of the invention
为了解决现有技术存在的问题,本申请的主要目的在于,提供一种轴流风叶、换气装置以及空调器,以便于有效控制叶顶涡的扩散。In order to solve the problems in the prior art, the main purpose of the present application is to provide an axial fan blade, a ventilator, and an air conditioner, so as to effectively control the diffusion of the blade tip vortex.
本申请的再一目的在于,提供一种轴流风叶,同时存在的两个折弯或者折边结构,可以控制叶顶泄漏气流的紊乱程度,降低轴流风叶在此处产生的紊流噪声。A further object of the present application is to provide an axial fan blade with two bending or flanging structures at the same time, which can control the degree of turbulence of the leakage airflow at the tip of the blade and reduce the turbulence generated by the axial fan blade here noise.
本申请的至少一个实施例提供了一种轴流风叶,包括轮毂和多个叶片,各所述叶片的两面分别为出风侧的压力面和进风侧的吸力面,各所述叶片的径向向外的边缘部位为叶顶,各所述叶片的叶顶处设置 有第一边与第二边,所述第一边向所述吸力面弯折延伸,所述第二边向所述压力面弯折延伸。At least one embodiment of the present application provides an axial-flow blade, including a hub and a plurality of blades, and the two surfaces of each blade are a pressure surface on the air outlet side and a suction surface on the air inlet side, respectively. The radially outward edge portion is the blade tip, and the blade tip of each blade is provided with a first edge and a second edge, the first edge is bent and extends toward the suction surface, and the second edge is oriented The pressure surface is bent and extended.
根据本申请的一实施例,所述第一边以及第二边为相对于叶片主体的折弯结构或者折边结构。According to an embodiment of the present application, the first side and the second side are a bent structure or a folded structure relative to the blade body.
根据本申请的一实施例,所述第一边的最大外径与所述第二边最大外径相等。According to an embodiment of the present application, the maximum outer diameter of the first side is equal to the maximum outer diameter of the second side.
根据本申请的一实施例,所述第一边的最大外径小于所述第二边的最大外径。According to an embodiment of the present application, the maximum outer diameter of the first side is smaller than the maximum outer diameter of the second side.
根据本申请的一实施例,所述第一边以及第二边设置于所述叶顶全长范围。According to an embodiment of the present application, the first side and the second side are disposed within the entire length of the blade tip.
根据本申请的一实施例,所述第一边以及第二边设置于所述叶顶局部范围。According to an embodiment of the present application, the first side and the second side are disposed in a partial range of the blade tip.
根据本申请的一实施例,所述第一边的最大外径大于所述第二边的最大外径。According to an embodiment of the present application, the maximum outer diameter of the first side is greater than the maximum outer diameter of the second side.
根据本申请的一实施例,所述第一边为具有第一半径的弧形折弯,所述第二边为具有第二半径的弧形折弯,所述第一半径小于所述第二半径。According to an embodiment of the present application, the first side is an arc bend with a first radius, the second side is an arc bend with a second radius, the first radius is smaller than the second radius.
根据本申请的一实施例,所述第一边是所述叶片主体具有第一夹角的折边,所述第二边是与所述叶片主体具有第二夹角的折边,所述第一夹角小于所述第二夹角。According to an embodiment of the present application, the first side is a flange having a first angle with the blade body, and the second side is a flange with a second angle with the blade body, the first An angle is smaller than the second angle.
根据本申请的一实施例,所述第一边为弧形折弯,所述第二边是与所述叶片主体具有第二夹角的折边。According to an embodiment of the present application, the first side is an arc-shaped bend, and the second side is a folded edge having a second angle with the blade body.
根据本申请的一实施例,所述第一边以及第二边设置范围占所述叶顶全长的0.4~0.6。According to an embodiment of the present application, the setting range of the first side and the second side accounts for 0.4-0.6 of the total length of the blade tip.
根据本申请的一实施例,还可以认为是提供了一种换气装置,包括轴流风叶,所述轴流风叶为如前所述的轴流风叶。According to an embodiment of the present application, it can also be considered that a ventilation device is provided, which includes an axial fan blade, and the axial fan blade is the aforementioned axial fan blade.
根据本申请的一实施例,还可以认为是提供了一种空调器,包括轴流风叶,所述轴流风叶为前面所述的轴流风叶。According to an embodiment of the present application, it can also be considered that an air conditioner is provided, which includes an axial fan blade, and the axial fan blade is the aforementioned axial fan blade.
采用上述可选的技术方案所得到的有益效果是:叶顶的结构由原来的二维边线结构变成了一个三维空间区间。此结构可以起到缓冲压力,缓解气流泄露,控制流动的作用,从而能够提升轴流风叶的工作能力,增大风量,并通过控制叶顶泄漏涡,降低噪声。The beneficial effect obtained by adopting the above optional technical solution is that the structure of the blade tip is changed from the original two-dimensional edge structure to a three-dimensional space interval. This structure can play the role of buffering pressure, alleviating airflow leakage, and controlling the flow, so as to improve the working capacity of the axial fan blade, increase the air volume, and reduce the noise by controlling the blade tip leakage vortex.
相比现有风叶,本申请风叶提升叶片做功能力,实现对叶片叶顶泄露涡的控制,降低风叶噪声。Compared with the existing fan blades, the fan blades of the present application enhance the function of the blades, realize the control of the blade tip leakage vortex, and reduce the blade noise.
附图说明BRIEF DESCRIPTION
图1:现有折边轴流风叶正视结构示意图;Figure 1: Schematic diagram of the front view of the existing folding axial flow fan blade;
图2:现有折边轴流风叶侧结构示意图;Figure 2: Schematic diagram of the current side of the folded flange axial flow fan blade;
图3:现有折边轴流风叶俯视结构示意图;Figure 3: Schematic diagram of the top view of the existing folding axial flow fan blades;
图4:现有折弯轴流风叶正视结构示意图;Figure 4: Schematic diagram of the front view of the existing bending axial fan;
图5:现有折弯轴流风叶侧视结构示意图;Figure 5: Schematic diagram of the side view of the existing bending axial fan blade;
图6:现有折弯轴流风叶俯视结构示意图;Figure 6: Schematic diagram of the top structure of the existing bending axial fan;
图7:现有折边轴流风叶图2折边结构的详细结构示意图;Figure 7: The detailed structure diagram of the existing folded edge axial flow fan blade 2
图8:现有折边轴流风叶图3折边结构的详细结构示意图;Figure 8: The detailed structural schematic diagram of the existing folding edge axial flow fan blade 3;
图9:现有折弯轴流风叶图5折弯结构的详细结构示意图;Figure 9: Existing bending axial flow vane Figure 5 Detailed structural diagram of the bending structure;
图10:现有折弯轴流风叶图6折弯结构的详细结构示意图;Figure 10: The detailed schematic diagram of the bending structure of the existing bending axial flow blade 6;
图11:本申请实施例一正视结构示意图;Figure 11: A schematic diagram of the front view of the first embodiment of the present application;
图12:本申请实施例一侧视结构示意图;Figure 12: Schematic diagram of a side view of an embodiment of the present application;
图13:本申请实施例一俯视结构示意图;Figure 13: Schematic diagram of the top view of the first embodiment of the present application;
图14:本申请实施例一叶顶折弯的详细结构示意图;Figure 14: A detailed schematic diagram of the tip bending of an embodiment of the present application;
图15:本申请实施例二正视结构示意图;Figure 15: A schematic diagram of the front view of the second embodiment of the present application;
图16:本申请实施例二侧视结构示意图;Figure 16: Schematic diagram of a side view of an embodiment of the present application;
图17:本申请实施例二俯视结构示意图;Figure 17: Schematic diagram of the top view of the second embodiment of the present application;
图18:本申请实施例二折弯结构的详细结构示意图;Figure 18: Detailed structural diagram of the bending structure of the second embodiment of the present application;
图19:本申请实施例二叶顶折边或者折弯区域结构示意图;FIG. 19: Schematic diagram of the structure of the two-blade crimping or bending area according to the embodiment of the present application;
图20:本申请实施例三的折边结构详细示意图;Figure 20: Detailed schematic diagram of the hemming structure of the third embodiment of the present application;
图21:风叶下游靠近叶顶一周位置处相对速度分布对比图;Figure 21: Comparison of relative velocity distribution at the downstream of the blade near the tip of the blade;
图22:风叶靠近叶顶附近处速度分布对比图。Figure 22: Comparison of the velocity distribution of the wind blade near the blade tip.
1、吸力面;2、叶顶;3、压力面;4、叶片;5、轮毂;1. Suction surface; 2. Blade tip; 3. Pressure surface; 4. Blade; 5. Wheel hub;
a1、a2、a3——折边夹角;a1, a2, a3-angle of folding edge;
R1、R2、R3——不同处的折弯半径;R1, R2, R3——Bending radius in different places;
D1、D2、D3——不同处的直径;D1, D2, D3-the diameter of different places;
b1、b2——不同的圆心夹角。b1, b2-different angles of the center of the circle.
具体实施方式detailed description
为使本申请实施例的目的、技术方案和优点更加清楚,下面将结合本申请实施例中的附图,对本申请实施例中的技术方案进行清楚、完整地描述,显然,所描述的实施例是本申请的一部分实施例,而不是全部的实施例。基于本申请中的实施例,本领域普通技术人员在没有做出创造性劳动的前提下所获得的所有其他实施例,都属于本申请保护的范围。To make the objectives, technical solutions, and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be described clearly and completely in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments It is a part of the embodiments of this application, but not all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by a person of ordinary skill in the art without making creative efforts fall within the protection scope of the present application.
本申请实施例提供了一种轴流风叶,主要包括轮毂5和多个叶片4,各所述叶片4的两面分别为出风侧的压力面3和进风侧的吸力面1,各所述叶片4的径向向外的边缘部位为叶顶2,各所述叶片4的叶顶2处设置有第一边21与第二边22,所述第一边21向所述吸力面1弯折延伸,所述第二边22向所述压力面3弯折延伸。An embodiment of the present application provides an axial fan blade, which mainly includes a hub 5 and a plurality of blades 4, and the two surfaces of each blade 4 are a pressure surface 3 on the outlet side and a suction surface 1 on the inlet side, respectively. The radially outward edge portion of the blade 4 is a blade tip 2. Each blade tip 2 of the blade 4 is provided with a first side 21 and a second side 22. The first side 21 faces the suction surface 1 Bending and extending, the second side 22 is bent and extending toward the pressure surface 3.
现有风叶的叶顶与其周围静止部件配合存在一定间隙,气流在此 处流动相对比较紊乱,是二次流、泄漏、回流的主要区域,是产生噪声的主要噪声源。因此,此处结构的设计对风叶性能影响显著。现有设计轴流风叶的叶顶无论是折边结构“L”型,还是折弯结构“J”型,与叶顶平缓无弯折结构的风叶,均最外叶顶为单一二维曲线,气流很容易通过与周围静止部件形成的夹缝产生二次流、泄漏、回流等乱流。There is a certain gap between the blade tip of the existing wind blade and the surrounding static components. The air flow here is relatively turbulent. It is the main area of secondary flow, leakage, and return flow, and the main source of noise. Therefore, the design of the structure here has a significant impact on the performance of the fan blades. Existing design of the blade tip of the axial flow blade, whether it is a "L" shape with a folded structure or a "J" shape with a curved structure, the outermost blade tip is a single two Dimensional curve, the airflow is easy to produce secondary flow, leakage, backflow and other turbulent flow through the gap formed with the surrounding static components.
本申请实施例提供的轴流风叶结构,在叶片4叶顶存在分别向压力面3和吸力面1的折弯,从而可以形成
Figure PCTCN2019109186-appb-000001
型,或者折边的结构“Y”型,叶顶的结构与周围静止部件形成一个截面概呈三角形的区域,夹缝由原来的二维边线结构变成了一个三维空间区间。可通过调节a1/a3、R1/R3、b1/b2等参数,改变三维空间形状,可以起到缓冲压力,缓解气流泄露,控制流动的作用,从而能够提升轴流风叶的工作能力,增大风量,并通过控制叶顶泄漏涡,降低噪声。
The axial fan blade structure provided by the embodiment of the present application has bends at the blade tip of the blade 4 toward the pressure surface 3 and the suction surface 1, respectively, so that it can be formed
Figure PCTCN2019109186-appb-000001
Type, or the folded-edge structure "Y" type, the structure of the blade tip and the surrounding static parts form an area with a substantially triangular cross-section, and the gap is changed from the original two-dimensional edge structure to a three-dimensional space interval. By adjusting a1/a3, R1/R3, b1/b2 and other parameters, the shape of the three-dimensional space can be changed, which can play a role in buffering pressure, alleviating airflow leakage, and controlling the flow, which can improve the working capacity and increase of the axial fan blade. Air volume and reduce noise by controlling blade tip leakage vortex.
以下结合本申请具体实施例,示例性说明如下:In the following, in conjunction with specific embodiments of the present application, an exemplary description is as follows:
a1、a2、a3折边夹角;a1, a2, a3 folding angle;
R1、R2、R3不同处的折弯半径;Bending radius at different places of R1, R2, R3;
D1、D2、D3不同处的直径;D1, D2, D3 different diameters;
b1、b2不同的圆心夹角。b1, b2 different center angles.
定义a1:在图7中,沿折线向两侧折边面作切线,两切线的夹角为a1;同理定义a2:在图8中,沿折线向两侧折边面作切线,两切线的夹角为a2;定义a3:在图20中,沿折线向共折线的三个折边面作切线,叶片靠内侧面切线与第一折边面切线的夹角为a1,叶片靠内侧面切线与第二折边面切线的夹角为a3。Definition a1: In Figure 7, the fold line is tangent to both sides along the polyline, and the angle between the two tangents is a1; Similarly, definition a2: In Figure 8, the fold line is made tangent to the sides along the polyline, and the two tangents The included angle is a2; Definition a3: In Figure 20, the three crimped surfaces along the fold line to the fold line are tangent, the angle between the tangent of the blade near the inner side and the tangent to the first crimped surface is a1, and the blade is near the inner side The angle between the tangent and the tangent of the second hemming surface is a3.
定义R1、R2、R3类似a1、a2、a3,此处不同与折线作切线,而是折线处作切圆,切圆半径定义分别命名为R1、R2、R3。Definition R1, R2, R3 are similar to a1, a2, a3, here is different from fold line as tangent, but tangent circle at the fold line, the definition of tangent radius is named R1, R2, R3.
D1为通过旋转轴为圆心、旋转轴为法线画圆,与风叶外径相切的 最大直径,亦即为吸力面折弯或者折边结构的最外径,D2为通过旋转轴为圆心、旋转轴为法线画圆,通过折边结构折线或者折弯结构曲率突然改变线,得到圆直径即D2;D3为通过旋转轴为圆心、旋转轴为法线画圆,压力面折弯或者折边结构的最外径。D1 is the center of the rotation axis, the axis of rotation is normal, and the maximum diameter is tangent to the outer diameter of the fan blade, that is, the maximum outer diameter of the suction surface bending or hemming structure, D2 is the center of rotation through the rotation axis 、The rotation axis is a normal line to draw a circle. The line diameter is D2 when the line is suddenly changed by the hemming structure fold line or the bending structure curvature; D3 is the circle drawn by the rotation axis as the center and the rotation axis as the normal line. The pressure surface is bent or The outer diameter of the hemming structure.
b1——叶片前缘最外圆点、折弯或者折边沿气流来流方向的起始位置点,两点与圆心连线的夹角;b2——叶片后缘最外圆点、折弯或者折边沿气流来流方向的起始位置点,两点与圆心连线的夹角。b1——the outermost circle point of the leading edge of the blade, the starting point of the bend or edge along the direction of airflow, the angle between the two points and the center of the circle; b2——the outermost circle point of the trailing edge of the blade, bend or The starting point of the folding edge along the direction of airflow, the angle between the two points and the center of the circle.
实施例一Example one
图11为本申请实施例一正视结构示意图,图12为本申请实施例一侧视结构示意图,图13为本申请实施例一俯视结构示意图,图14为本申请实施例一叶顶折弯的详细结构示意图。11 is a schematic view of a front view of an embodiment of the present application, FIG. 12 is a schematic view of a side view of an embodiment of the present application, FIG. 13 is a schematic structural view of a top view of an embodiment of the present application, and FIG. 14 is a bent top of an embodiment of the present application Detailed structural diagram.
如图所示,在叶片4的叶顶2全范围设置(叶顶全长是指整个叶顶从进气前缘到出气后缘整段)有分别向压力面3和吸力面1的折弯,也就是第一边21与第二边22,叶顶2整体呈
Figure PCTCN2019109186-appb-000002
型(
Figure PCTCN2019109186-appb-000003
上端为叶顶2),或者折边的结构,呈“Y”型(Y上端为叶顶2)。其中第一边21向吸力面1向一侧折弯产生折弯半径为R1的结构,从而保证了压力面的正压区域范围不受影响,即保证了风叶的做功能力。第二边22亦向压力面3一侧折弯产生折弯半径为R3的结构,从而保证了压力面3在叶顶附近压力的提升,降低压力面3和吸力面1两者之间的压差过大而导致气流的泄漏。本实施例中叶顶2的结构由原来的二维边线结构变成了一个三维空间区间。此结构可以起到缓冲压力,缓解气流泄露,控制流动的作用,从而能够提升轴流风叶的工作能力,增大风量,并通过控制叶顶泄漏涡,降低噪声。
As shown in the figure, the entire range of the blade tip 2 of the blade 4 is set (the entire length of the blade tip refers to the entire length of the entire blade tip from the leading edge of the intake to the trailing edge of the outlet). , That is, the first side 21 and the second side 22, the blade tip 2 as a whole
Figure PCTCN2019109186-appb-000002
type(
Figure PCTCN2019109186-appb-000003
The upper end is the blade tip 2), or the structure of the hemming is in the shape of "Y" (the upper end of Y is the blade tip 2). The first side 21 is bent toward the suction surface 1 to one side to produce a structure with a bending radius of R1, thereby ensuring that the positive pressure area of the pressure surface is not affected, that is, the function of the wind blade is ensured. The second side 22 also bends toward the pressure surface 3 to produce a structure with a bending radius of R3, thereby ensuring the pressure increase of the pressure surface 3 near the blade tip and reducing the pressure between the pressure surface 3 and the suction surface 1 If the difference is too large, it may cause air leakage. In this embodiment, the structure of the blade tip 2 is changed from the original two-dimensional edge structure to a three-dimensional space interval. This structure can play the role of buffering pressure, alleviating airflow leakage, and controlling the flow, so as to improve the working capacity of the axial flow blade, increase the air volume, and reduce the noise by controlling the blade tip leakage vortex.
本领域技术人员应该理解的是,全范围设置双侧折弯的实施例更适用于低风速大叶面的风叶实施例中。It should be understood by those skilled in the art that the embodiment in which the double-sided bending is provided in a full range is more suitable for the embodiment of a fan blade with a low wind speed and a large blade surface.
本实施例中,第一边21为具有第一半径R1的弧形折弯,所述第 二边22为具有第二半径R3的弧形折弯,所述第一半径R1大于所述第二半径R3。In this embodiment, the first side 21 is an arc bend with a first radius R1, the second side 22 is an arc bend with a second radius R3, and the first radius R1 is greater than the second Radius R3.
实施例二Example 2
图15为本申请实施例二正视结构示意图,图16为本申请实施例二侧视结构示意图,图17为本申请实施例二俯视结构示意图,图18为本申请实施例二折弯结构的详细结构示意图,以及图19为本申请实施例二叶顶折边或者折弯区域结构示意图。15 is a schematic view of the front view of the second embodiment of the present application, FIG. 16 is a schematic view of the side view of the second embodiment of the present application, FIG. 17 is a schematic top view of the second embodiment of the present application, and FIG. 18 is a detailed view of the bending structure of the second embodiment of the present application A structural schematic diagram, and FIG. 19 is a schematic structural diagram of a two-blade crimping or bending region according to an embodiment of the present application.
如图所示,在叶片4的叶顶2局部范围内设置有分别向压力面3和吸力面1的折弯,叶顶局部范围(相对于“叶顶全长范围”,仅仅叶顶的一端存在第一边和第二边),即图19中b1至叶片4前缘最外圆点、折弯或者折边沿气流来流方向的起始位置点,两点与圆心连线的夹角;b2——叶片4后缘最外圆点、折弯或者折边沿气流来流方向的起始位置点,两点与圆心连线的夹角。而叶顶全范围(即,叶顶全长范围)为折弯或者折边的结构,则b1=0;若是叶顶局部范围,则b1/(b1+b2)属于(0,1)。一个具体实施例中,选择为b1/(b1+b2)在(0.4~0.6)范围内,也就是说,此范围内与周围静止部件相匹配具有较佳的技术优势。本领域技术人员应该理解的是,局部范围设置双侧折弯的实施例更适用于较高风速小叶面的风叶实施例中。将叶片从内向外径向划分多个叶片段,叶顶为叶片靠近最外缘、顶端部分的叶片段,叶顶全长则为叶顶部分从进气前缘侧到出气后缘侧的全部长度。As shown in the figure, in the partial range of the blade tip 2 of the blade 4, bending to the pressure surface 3 and the suction surface 1, respectively, is provided. The partial range of the blade tip (with respect to the "full length range of the blade tip", only one end of the blade tip There is a first side and a second side), that is, from b1 to the outermost circle point of the leading edge of the blade 4 in FIG. 19, the starting point of the bend or edge along the direction of airflow, the angle between the two points and the center of the circle; b2——The starting point of the outermost circle point, bend or edge of the trailing edge of the blade 4 along the direction of airflow, and the angle between the two points and the center of the circle. The full range of the blade tip (that is, the full length of the blade tip) is a bent or folded structure, and b1=0; if it is a partial range of the blade tip, b1/(b1+b2) belongs to (0,1). In a specific embodiment, it is selected that b1/(b1+b2) is in the range of (0.4 to 0.6), that is, matching with surrounding stationary components within this range has better technical advantages. It should be understood by those skilled in the art that the embodiment in which the double-sided bending is provided in a local range is more suitable for the embodiment of a fan blade with a small leaf surface at a higher wind speed. The blade is divided into multiple blade segments radially from inside to outside. The tip of the blade is the blade segment near the outermost edge and the tip of the blade, and the full length of the blade tip is the entire part of the blade tip from the leading edge side of the intake to the trailing edge side of the outlet length.
本申请采用两侧折弯或者折边的结构可以是两边等外径,也可以是不等外径。即图18中D1为风叶最外径,亦即为压力面3折弯或者折边结构的最外径,D3为吸力面1折弯或者折边结构的最外径,其中D1选择为大于或等于D3。从而减少压力面3向吸力面1一侧的漏风量,也就是减少相反于气流方向的漏风。This application adopts the structure of bending or flanging on both sides, which may be the same outer diameter on both sides, or may be unequal outer diameter. That is, D1 in FIG. 18 is the outermost diameter of the fan blade, that is, the outermost diameter of the bending or flanging structure of the pressure surface 3, and D3 is the outermost diameter of the bending or flanging structure of the suction surface 1, where D1 is selected to be greater than Or equal to D3. Thereby, the amount of air leakage from the pressure surface 3 to the suction surface 1 side is reduced, that is, the air leakage in the direction opposite to the air flow is reduced.
也就是第一边21与第二边22,叶顶2整体呈
Figure PCTCN2019109186-appb-000004
型(
Figure PCTCN2019109186-appb-000005
上端为 叶顶2),或者折边的结构,呈“Y”型(Y上端为叶顶2)。其中第一边21向吸力面1向一侧折弯产生折弯半径为R1的结构,从而保证了压力面的正压区域范围不受影响,即保证了风叶的做功能力。第二边22亦向压力面3一侧折弯产生折弯半径为R3的结构,从而保证了压力面3在叶顶附近压力的提升,降低压力面3和吸力面1两者之间的压差过大而导致气流的泄漏。本实施例中,第一边21为具有第一半径R1的弧形折弯,所述第二边22为具有第二半径R3的弧形折弯,所述第一半径R1小于所述第二半径R3。
That is, the first side 21 and the second side 22, and the blade tip 2 as a whole
Figure PCTCN2019109186-appb-000004
type(
Figure PCTCN2019109186-appb-000005
The upper end is the blade tip 2), or the structure of the hemming is in the shape of "Y" (the upper end of Y is the blade tip 2). The first side 21 is bent toward the suction surface 1 to one side to produce a structure with a bending radius of R1, thereby ensuring that the positive pressure area of the pressure surface is not affected, that is, the function of the wind blade is ensured. The second side 22 also bends toward the pressure surface 3 to produce a structure with a bending radius of R3, thereby ensuring the pressure increase of the pressure surface 3 near the blade tip and reducing the pressure between the pressure surface 3 and the suction surface 1 If the difference is too large, it may cause air leakage. In this embodiment, the first side 21 is an arc bend with a first radius R1, the second side 22 is an arc bend with a second radius R3, and the first radius R1 is smaller than the second Radius R3.
本实施例中叶顶2的结构由原来的二维边线结构变成了一个三维空间区间。此结构可以起到缓冲压力,缓解气流泄露,控制流动的作用,从而能够提升轴流风叶的工作能力,增大风量,并通过控制叶顶泄漏涡,降低噪声。In this embodiment, the structure of the blade tip 2 is changed from the original two-dimensional edge structure to a three-dimensional space interval. This structure can play the role of buffering pressure, alleviating airflow leakage, and controlling the flow, so as to improve the working capacity of the axial fan blade, increase the air volume, and reduce the noise by controlling the blade tip leakage vortex.
实施例三Example Three
图20为本申请实施例三的折边结构详细示意图。如图所示,第一边21与第二边22分别为折边,其中第一边21与叶片4的夹角为a1、第二边22与叶片4的夹角为a3,两者的关系为a1≤a3,或者认为R1≤R3。其中向压力面的折弯或者折边结构甚至可以近似为一直板“y”型(y上端为叶顶),即R3为无穷大或者a3=180°。FIG. 20 is a detailed schematic diagram of the hemming structure of Embodiment 3 of the present application. As shown in the figure, the first side 21 and the second side 22 are folded edges, wherein the angle between the first side 21 and the blade 4 is a1, and the angle between the second side 22 and the blade 4 is a3, the relationship between the two A1≤a3, or R1≤R3. The bending or hemming structure toward the pressure surface can even be approximated as a straight plate "y" type (the upper end of y is the blade tip), that is, R3 is infinity or a3=180°.
第一组对比实验The first group of comparative experiments
另外,申请人采用图1至图10所示现有轴流风叶与本申请实施例一所示轴流风叶进行了对比测试,对比实验的结构如表一所示。In addition, the applicant conducted a comparative test using the existing axial fan shown in FIGS. 1 to 10 and the axial fan shown in Example 1 of the present application. The structure of the comparative experiment is shown in Table 1.
表一、对比仿真计算结果数据对比Table 1. Comparison of data from simulation calculation results
结构structure 仿真计算流量m 3/h Simulation calculation flow m 3 /h
现有轴流风叶Existing axial fan 0.67490.6749
实施例一Example one 0.68290.6829
再如图21所对比示意,表示出风叶下游靠近叶顶一周位置处相对速度分布,相对速度波动小的代表噪声相对较小,因此本申请实施例一结构风叶噪声相对现有风叶结构较有优势。As shown in the comparison diagram in FIG. 21, the relative velocity distribution at the position downstream of the blade near the blade tip is shown. Small fluctuations in the relative speed represent relatively low noise. Therefore, the structure of the first embodiment of the present application is similar to the existing blade structure. Has an advantage.
第一组对比实验The first group of comparative experiments
另一方面,申请人采用图1至图10所示现有轴流风叶与本申请实施例二所示轴流风叶进行了对比测试,对比实验的结构如表二所示。On the other hand, the applicant conducted a comparative test using the existing axial fan blades shown in FIGS. 1 to 10 and the axial fan blades shown in Example 2 of the present application. The structure of the comparative experiment is shown in Table 2.
有无专利结构仿真计算结果数据对比,带专利结构风叶产生流量略偏大。Comparing the data of simulation calculation results with or without patent structure, the flow generated by the fan blade with patent structure is slightly larger.
结构structure 仿真计算流量m 3/h Simulation calculation flow m 3 /h
无专利结构风叶Patent-free structure 0.72740.7274
带专利结构风叶Blade with patent structure 0.75150.7515
表二,有无专利结构的叶片仿真计算结果图对比表Table 2: Comparison table of blade simulation calculation results with or without patent structure
图22中表示风叶靠近叶顶附近处速度分布,A图为现有风叶结构表现,其叶顶上下游均存在两个大的旋涡,而B图为本申请实施例结构风叶表现,叶顶上下游的旋涡得到了一定抑制,将部分紊乱流动控制在叶顶与风叶周围静止区域形成的空间内。Figure 22 shows the velocity distribution of the wind blade near the blade tip. Figure A shows the performance of the existing blade structure. There are two large vortices in the upstream and downstream of the blade tip. Figure B shows the performance of the blade of the structure of the embodiment of this application. The vortexes on the upstream and downstream of the blade tip have been suppressed to some extent, and part of the turbulent flow is controlled in the space formed by the stationary area around the blade tip and the wind blade.
最后应说明的是:以上实施例仅用以说明本申请的技术方案,而非对其限制;尽管参照前述实施例对本申请进行了详细的说明,本领域的普通技术人员应当理解:其依然可以对前述各实施例所记载的技术方案进行修改,或者对其中部分技术特征进行等同替换;而这些修改或者替换,并不使相应技术方案的本质脱离本申请各实施例技术方案的精神和范围。Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, not to limit them; although the present application has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that they can still The technical solutions described in the foregoing embodiments are modified, or some of the technical features are equivalently replaced; and these modifications or replacements do not deviate from the spirit and scope of the technical solutions of the embodiments of the present application.

Claims (15)

  1. 一种轴流风叶,包括轮毂(5)和多个叶片(4),各所述叶片(4)的两面分别为出风侧的压力面(3)和进风侧的吸力面(1),各所述叶片(4)的径向向外的边缘部位为叶顶,其特征在于:An axial-flow wind blade, including a hub (5) and a plurality of blades (4), two surfaces of each blade (4) are a pressure surface (3) on the air outlet side and a suction surface (1) on the air inlet side The radial outward edge of each blade (4) is the blade tip, which is characterized by:
    各所述叶片(4)的叶顶处设置有第一边(21)与第二边(22),所述第一边(21)向所述吸力面(1)弯折延伸,所述第二边(22)向所述压力面(3)弯折延伸。A first side (21) and a second side (22) are provided at the tip of each blade (4), the first side (21) is bent and extends toward the suction surface (1), and the first The two sides (22) bend and extend toward the pressure surface (3).
  2. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)以及第二边(22)为相对于叶片(4)主体的折弯结构或者折边结构。The axial-flow blade according to claim 1, wherein the first side (21) and the second side (22) are a bent structure or a folded structure relative to the main body of the blade (4).
  3. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)的最大外径与所述第二边(22)最大外径相等。The axial flow vane according to claim 1, characterized in that the maximum outer diameter of the first side (21) is equal to the maximum outer diameter of the second side (22).
  4. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)的最大外径大于所述第二边(22)的最大外径。The axial flow vane according to claim 1, wherein the maximum outer diameter of the first side (21) is greater than the maximum outer diameter of the second side (22).
  5. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)以及第二边(22)设置于所述叶顶全长范围。The axial-flow blade according to claim 1, characterized in that the first side (21) and the second side (22) are provided over the entire length of the blade tip.
  6. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)以及第二边(22)设置于所述叶顶局部范围。The axial-flow blade according to claim 1, characterized in that the first side (21) and the second side (22) are arranged in a partial range of the blade tip.
  7. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)以及第二边(22)设置范围占所述叶顶全长的0.4~0.6。The axial-flow blade according to claim 1, wherein the first side (21) and the second side (22) are arranged in a range of 0.4 to 0.6 of the total length of the blade tip.
  8. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)的最大外径小于所述第二边(22)的最大外径。The axial flow vane according to claim 1, wherein the maximum outer diameter of the first side (21) is smaller than the maximum outer diameter of the second side (22).
  9. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)为具有第一半径的弧形折弯,所述第二边(22)为具有第二半径的弧形折弯。The axial flow blade according to claim 1, characterized in that the first side (21) is an arc-shaped bend with a first radius, and the second side (22) is an arc with a second radius Shaped bend.
  10. 根据权利要求9所述的轴流风叶,其特征在于,所述第一半径小于所述第二半径。The axial flow vane according to claim 9, wherein the first radius is smaller than the second radius.
  11. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边 (21)是所述叶片(4)主体具有第一夹角的折边,所述第二边(22)是与所述叶片(4)主体具有第二夹角的折边。The axial-flow blade according to claim 1, characterized in that the first side (21) is a folded edge with a first included angle of the blade (4) body, and the second side (22) is A flange with a second angle to the main body of the blade (4).
  12. 根据权利要求11所述的轴流风叶,其特征在于,所述第一夹角小于所述第二夹角。The axial flow vane according to claim 11, wherein the first included angle is smaller than the second included angle.
  13. 根据权利要求1所述的轴流风叶,其特征在于,所述第一边(21)为弧形折弯,所述第二边(22)是与所述叶片(4)主体具有第二夹角的折边。The axial flow blade according to claim 1, characterized in that the first side (21) is curved and the second side (22) has a second position with the main body of the blade (4) Angled hem.
  14. 一种换气装置,包括轴流风叶,其特征在于,所述轴流风叶为权利要求1至13中任一项所述的轴流风叶。A ventilation device includes an axial fan blade, wherein the axial fan blade is the axial fan blade according to any one of claims 1 to 13.
  15. 一种空调器,包括轴流风叶,其特征在于,所述轴流风叶为权利要求1至13中任一项所述的轴流风叶。An air conditioner includes an axial fan blade, wherein the axial fan blade is the axial fan blade according to any one of claims 1 to 13.
PCT/CN2019/109186 2018-12-19 2019-09-29 Axial flow fan blade, ventilation device and air conditioner WO2020125128A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201811556731.9A CN109538532A (en) 2018-12-19 2018-12-19 Axial-flow leaf, air interchanger and air conditioner
CN201811556731.9 2018-12-19

Publications (1)

Publication Number Publication Date
WO2020125128A1 true WO2020125128A1 (en) 2020-06-25

Family

ID=65855737

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2019/109186 WO2020125128A1 (en) 2018-12-19 2019-09-29 Axial flow fan blade, ventilation device and air conditioner

Country Status (2)

Country Link
CN (1) CN109538532A (en)
WO (1) WO2020125128A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109538532A (en) * 2018-12-19 2019-03-29 珠海格力电器股份有限公司 Axial-flow leaf, air interchanger and air conditioner
CN111946667A (en) * 2020-07-28 2020-11-17 东风马勒热系统有限公司 Fan with bent blades

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4757587A (en) * 1986-03-28 1988-07-19 Gold Star Co., Ltd. Propeller construction of an electric fan
CN201574972U (en) * 2009-07-14 2010-09-08 广东顺威精密塑料股份有限公司 Axial flow wind wheel
CN103486081A (en) * 2012-06-11 2014-01-01 珠海格力电器股份有限公司 Axial-flow fan blade, fan and air-conditioner outdoor unit
US20140147282A1 (en) * 2012-11-23 2014-05-29 Cooler Master Co., Ltd. Fan structure
CN106593952A (en) * 2017-01-12 2017-04-26 珠海格力电器股份有限公司 Axial-flow fan blade, fan with same, and air conditioner outdoor unit
JP2017106409A (en) * 2015-12-11 2017-06-15 三菱日立パワーシステムズ株式会社 Rotor blade of rotary machine
CN109538532A (en) * 2018-12-19 2019-03-29 珠海格力电器股份有限公司 Axial-flow leaf, air interchanger and air conditioner
CN209743240U (en) * 2018-12-19 2019-12-06 珠海格力电器股份有限公司 Axial flow fan blade, air interchanger and air conditioner

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6626640B2 (en) * 2001-11-19 2003-09-30 Durmitor Inc. Fan with reduced noise
JP2011513618A (en) * 2008-02-21 2011-04-28 ボーグワーナー・インコーポレーテッド Partial ring cooling fan
US10422349B2 (en) * 2014-07-08 2019-09-24 Daikin Industries, Ltd. Propeller fan and blower unit

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4757587A (en) * 1986-03-28 1988-07-19 Gold Star Co., Ltd. Propeller construction of an electric fan
CN201574972U (en) * 2009-07-14 2010-09-08 广东顺威精密塑料股份有限公司 Axial flow wind wheel
CN103486081A (en) * 2012-06-11 2014-01-01 珠海格力电器股份有限公司 Axial-flow fan blade, fan and air-conditioner outdoor unit
US20140147282A1 (en) * 2012-11-23 2014-05-29 Cooler Master Co., Ltd. Fan structure
JP2017106409A (en) * 2015-12-11 2017-06-15 三菱日立パワーシステムズ株式会社 Rotor blade of rotary machine
CN106593952A (en) * 2017-01-12 2017-04-26 珠海格力电器股份有限公司 Axial-flow fan blade, fan with same, and air conditioner outdoor unit
CN109538532A (en) * 2018-12-19 2019-03-29 珠海格力电器股份有限公司 Axial-flow leaf, air interchanger and air conditioner
CN209743240U (en) * 2018-12-19 2019-12-06 珠海格力电器股份有限公司 Axial flow fan blade, air interchanger and air conditioner

Also Published As

Publication number Publication date
CN109538532A (en) 2019-03-29

Similar Documents

Publication Publication Date Title
US11506211B2 (en) Counter-rotating fan
JP6352936B2 (en) Centrifugal compressor with twisted return channel vanes
US11078921B2 (en) Blade, impeller and fan
CN104641121A (en) Propeller fan and air conditioner equipped with same
US10550855B2 (en) Axial flow fan
JP4888436B2 (en) Centrifugal compressor, its impeller and its operating method
WO2020125128A1 (en) Axial flow fan blade, ventilation device and air conditioner
WO2021147605A1 (en) Impeller, mixed flow blower, and air conditioner
CN104487712A (en) Propeller fan, and fan, air-conditioner and outdoor unit for hot-water supply provided with propeller fan
WO2021208496A1 (en) Mixed flow wind wheel, fan assembly, power system, and fan
JPWO2019150567A1 (en) Axial blower
JP2022515453A (en) Modeling method for aero engine fan assembly
CN104033422B (en) A kind of small axial flow fan of band splitterr vanes
CN108603513B (en) Compressor impeller and method for manufacturing same
CN209743240U (en) Axial flow fan blade, air interchanger and air conditioner
JPWO2017077564A1 (en) Axial flow fan and air conditioner having the axial flow fan
CN115544878A (en) Design method of blade profile, blade, wind wheel, fan and oil fume suction device
CN209724796U (en) A kind of return channel blade
CN204126958U (en) With the small axial flow fan of splitterr vanes
CN211259115U (en) Blade, multi-wing centrifugal fan blade and multi-wing centrifugal fan
CN109209989B (en) Centrifugal fan and range hood
CN113007135A (en) Axial flow blade and axial flow fan
CN202418036U (en) Axial flow fan and air conditioner with same
CN112228400A (en) Volute profile construction method, volute, air duct structure and range hood
JP2010275986A (en) Fan and axial flow blower

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19900778

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19900778

Country of ref document: EP

Kind code of ref document: A1