WO2019006972A1 - 叶轮、风机和电机 - Google Patents

叶轮、风机和电机 Download PDF

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Publication number
WO2019006972A1
WO2019006972A1 PCT/CN2017/113991 CN2017113991W WO2019006972A1 WO 2019006972 A1 WO2019006972 A1 WO 2019006972A1 CN 2017113991 W CN2017113991 W CN 2017113991W WO 2019006972 A1 WO2019006972 A1 WO 2019006972A1
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WO
WIPO (PCT)
Prior art keywords
blade
leading edge
impeller
trailing edge
impeller according
Prior art date
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PCT/CN2017/113991
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English (en)
French (fr)
Inventor
蒋婷婷
冯国平
Original Assignee
广东威灵电机制造有限公司
美的威灵电机技术（上海）有限公司
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Publication date
Priority claimed from CN201720799246.9U external-priority patent/CN206874554U/zh
Priority claimed from CN201710531106.8A external-priority patent/CN107143522A/zh
Application filed by 广东威灵电机制造有限公司, 美的威灵电机技术（上海）有限公司 filed Critical 广东威灵电机制造有限公司
Publication of WO2019006972A1 publication Critical patent/WO2019006972A1/zh

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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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/24—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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

Definitions

  • the invention belongs to the field of impellers, and more particularly to an impeller and a fan and an electric machine therewith.
  • the impeller In the vacuum cleaner, the impeller is driven to rotate at a high speed by a motor to form a negative pressure environment in the sealed casing, so that dust and the like are sucked into the dust collecting device, thereby achieving a cleaning effect.
  • the impeller is a key component of the vacuum cleaner, and its performance directly determines the overall working efficiency of the fan system.
  • the vacuum cleaners in the prior art generally have the disadvantages of large volume and low performance of the fan, and it is necessary to continuously optimize the design of the impeller structure to further improve the working performance of the vacuum cleaner.
  • the present invention provides an impeller capable of optimizing work performance.
  • the present invention provides an impeller including a substantially conical hub and a plurality of blades circumferentially spaced apart on an outer peripheral surface of the hub, the blades including a leading edge at an inlet end
  • the face and the trailing edge face at the outlet end are the flat plate twisting blades, and the blade leading edge section and the trailing edge section of the blade are respectively twisted in opposite directions in the circumferential direction.
  • the blade leading edge section of the blade is inclined toward the downstream side with respect to the rotation direction of the impeller, and the blade trailing edge section of the blade is inclined toward the upstream side with respect to the rotation direction.
  • the inclination angle ⁇ of the trailing edge section of the blade toward the upstream side is inclined to satisfy: 10° ⁇ 45°.
  • the upstream side surface of the leading edge section of the blade is formed as a convex surface and the downstream side surface is formed as a concave surface, and the length of the twist of the tip of the blade leading edge section is 10% to 50% of the total length of the blade. %.
  • the upstream side surface of the trailing edge section of the blade is formed as a concave surface and the downstream side surface is formed as a convex surface
  • the length of the tip of the blade at the trailing edge of the blade is 5% to 30% of the total length of the blade.
  • the leading edge face is an inclined plane with respect to a central axis of the hub, and the angle of the inclined plane with respect to the central axis is 30° ⁇ ⁇ ⁇ 90°.
  • the blade includes a blade root connected to an outer peripheral surface of the hub and extending from the leading edge face to the trailing edge face and extending from a tip end of the leading edge face to the trailing edge face
  • the top surface of the tip of the blade gradually decreases in height from the leading edge toward the trailing edge surface with respect to the height of the blade root.
  • the height b1 of the leading edge face and the height b2 of the trailing edge face respectively satisfy: 5 mm ⁇ b1 ⁇ 15 mm, and 2 mm ⁇ b2 ⁇ 7 mm.
  • the root mounting angle of the blade root is ⁇ 1
  • the outlet mounting angle is ⁇ 2
  • the root edge line of the blade root is from The bottom end of the leading edge face extends to a smooth curve of the bottom end of the trailing edge face.
  • the inlet top angle of the blade tip of the blade is ⁇ 3, the outlet mounting angle is ⁇ 4, and satisfies: 25° ⁇ 3 ⁇ 75°, 35° ⁇ 4 ⁇ 80°, the top surface of the blade is from the The top end of the leading edge face extends to a smooth curved surface at the top end of the trailing edge face.
  • 5 to 12 of the blades are distributed on the outer circumferential surface of the hub at equal intervals in the circumferential direction.
  • the present invention accordingly provides a fan and an electric motor each including the above-described impeller.
  • the shape of the blade is optimized in the impeller of the invention, especially in the leading edge section and the trailing edge section, and the leading edge section of the flat twisted blade is inclined toward the downstream side with respect to the rotation direction of the impeller.
  • the angle is such that the upstream side surface of the leading edge section of the blade is formed as a convex surface, and the trailing edge section is inclined at an angle with respect to the rotation direction of the impeller toward the upstream side, so that the upstream side surface of the trailing edge section of the blade is formed into a concave surface,
  • the impeller of the structure, the fluid loss at the inlet end and the outlet end is effectively reduced, the effective working area of the impeller is enlarged, and the working performance of the impeller is remarkably improved.
  • Figure 1 is a perspective view of an impeller in accordance with a preferred embodiment of the present invention.
  • Figure 2 is a front elevational view of the impeller of Figure 1;
  • Figure 3 is a plan view of the impeller of Figure 1.
  • orientation words such as “up, down, top, and bottom” are generally used for the directions shown in the drawings or for vertical, vertical or gravity directions, unless otherwise stated.
  • the components are described in terms of their positional relationship.
  • the present invention provides an impeller 100 including a substantially conical hub 11 and a plurality of blades 12 circumferentially spaced apart on the outer peripheral surface of the hub 11, each blade 12 being located
  • the leading edge surface 121 of the inlet end and the trailing edge surface 122 at the outlet end, the blade 12 is a flat plate twisting blade, and the blade leading edge section and the trailing edge section of the blade 12 are respectively twisted in opposite directions in the circumferential direction.
  • the leading edge section of the blade 12 is inclined with respect to the direction of rotation w of the impeller 12 toward the downstream side 22, the trailing edge section of the blade 12 facing the upstream side 21 with respect to the direction of rotation w
  • the twist is tilted.
  • the leading edge portion of the blade is not limited to being twisted to the downstream side 22, and the trailing edge portion of the blade is not limited to being twisted to the upstream side 21, and the same impeller 100 may be rotated in the opposite direction of rotation w as illustrated, but The efficiency is relatively poor.
  • the impeller 100 of the present invention can effectively reduce the fluid loss at the inlet end and the outlet end of the blade 12, and expand the operation of the impeller 100 under a small flow rate.
  • the area, that is, the effective working range is increased, and the working performance of the impeller 100 is greatly improved.
  • the inclination angle ⁇ of the trailing edge section of the blade 12 toward the upstream side 21 is preferably 10° ⁇ ⁇ ⁇ 45°, see FIG. 1 .
  • ⁇ may be 15°, 25°, 40°, etc., and may be specifically set according to actual conditions.
  • the leading edge section of the blade 12 is twisted toward the downstream side 22 such that the upstream side of the leading edge section of the blade 12 is formed as a convex surface 125 and the downstream side is formed as a concave surface 126.
  • the ratio of the twist length to the total length of the blade 12 is preferably 10% to 50%.
  • the trailing edge section of the blade 12 is twisted toward the upstream side 21 such that the upstream side of the trailing edge section of the blade 12 is formed as a concave surface 126 and the downstream side is formed as a convex surface 125.
  • the ratio of the length of the twist of the tip of the blade of the trailing edge section of the blade 12 to the total length of the blade 12 is preferably 5% to 30%.
  • the streamlined design of the blade 12 facilitates reducing fluid loss within the blade passage, improving fluid flow characteristics, and thereby improving the performance of the impeller 100.
  • the leading edge surface 121 of the blade 12 is an inclined plane with respect to a central axis of the substantially conical shape of the hub 11, the angle of the inclined plane with respect to the central axis is ⁇ and satisfies: 30° ⁇ ⁇ ⁇ 90°, that is, when the fluid flows in from the leading edge surface 121 of each blade 12, it flows in an oblique direction, effectively controlling the wind pressure at the inlet end of the blade 12, and reducing the loss of the fluid at the inlet end.
  • the blade 12 includes a blade root portion 124 coupled to an outer peripheral surface of the hub 11 and extending from the leading edge surface 121 to the trailing edge surface 122 and extending from a tip end of the leading edge surface 121 to the trailing edge surface
  • the tip top surface 123 of the tip end 122 of the 122 gradually decreases in height from the leading edge surface 121 toward the trailing edge surface 122 with respect to the blade root portion 124.
  • the height b1 from the front edge surface 121 of the blade 12 to the height b2 of the trailing edge surface 122 is gradually decreased.
  • it preferably satisfies: 5 mm ⁇ b1 ⁇ 15 mm, and 2 mm ⁇ b2 ⁇ 7 mm, respectively.
  • the height value b1 of the tip surface 123 of the leading edge surface 121 of each blade 12 with respect to the blade root 124 is the largest, and the blade top surface 123 of the trailing edge surface 121 of each blade 12 is opposite to the blade root 124.
  • the height value b2 is the smallest, and the height between the maximum height b1 and the minimum height b2 of the blade 12 is gradually decreasing.
  • the root edge line of the blade root 124 is preferably a smooth curve extending from the bottom end of the leading edge face 121 to the bottom end of the trailing edge face 122.
  • the inlet angle of the blade root portion 124 of the blade 12 is ⁇ 1, the outlet mounting angle is ⁇ 2, and it satisfies: 25° ⁇ ⁇ 1 ⁇ 75°, 40° ⁇ ⁇ 2 ⁇ 80°.
  • the blade root edge line of the blade root portion 124 of the blade 12 is the intersection line of the side surface of the blade 12 and the outer circumferential surface of the hub 11 , that is, the intersection curve between the face and the face, whereby the blade 12
  • the inlet mounting angle of the blade root 124 is the angle between the first tangent at the leading edge point of the blade root line and the second tangent.
  • the first tangent is a tangent to a leading edge point of the blade root edge line with respect to the blade root edge line
  • the second tangent is the distance from the foremost edge point to the central axis of the hub 11 with the leading edge point being The tangent of the circle of the radius.
  • the exit mounting angle is the tangent angle at the last edge of the blade root edge line, ie the tangent to the last edge point relative to the blade root edge line and the last edge point relative to the center of the last edge point and hub 11
  • the axis is at an angle ⁇ 2 between the tangent to the circle of the radius.
  • the tip surface of the leaf tip 123 is preferably from the leading edge surface 121 The top end extends to a smooth curved surface at the top end of the trailing edge surface 122.
  • the inlet tip angle of the blade tip portion 123 of the blade 12 is ⁇ 3, the outlet mounting angle is ⁇ 4, and it satisfies: 25° ⁇ ⁇ 3 ⁇ 75°, 35° ⁇ ⁇ 4 ⁇ 80°.
  • the tip edge line of the blade top surface is the intersection line of the blade top surface and the side surface of the blade 12, and the inlet mounting angle of the blade top portion 123 of the blade 12 is the forefront of the blade top edge line. The angle between the first tangent at the point and the second tangent.
  • the first tangent is a tangent to a leading edge point of the tip edge line with respect to the tip edge line
  • the second tangent is the distance from the leading edge point to the central axis of the hub 11 with the leading edge point being The tangent of the circle of the radius.
  • the exit mounting angle is the tangent angle at the last edge of the tip line of the tip, that is, the tangent to the last edge relative to the tip edge line and the last edge relative to the center of the last edge and hub 11.
  • the axis is at an angle ⁇ 4 between the tangent lines of the circle of radius.
  • ⁇ 1, ⁇ 2, ⁇ 3, ⁇ 4 are limited to 30° ⁇ ⁇ 1 ⁇ 80°, 40° ⁇ ⁇ 2 ⁇ 80°, 25° ⁇ ⁇ 3 ⁇ 75°, 35° ⁇ ⁇ 4 ⁇ 80°, which can be further reduced Fluid loss at the inlet and outlet ends.
  • all of the impellers 100 mentioned in the embodiment are distributed with 5 to 12 of the blades 12 at equal intervals in the circumferential direction on the outer circumferential surface of the hub 11.
  • the present invention also provides a fan including the above-described impeller 100.
  • the impeller 100 By using the impeller 100, the overall performance of the fan can be improved.
  • the present invention also provides an electric machine comprising the above-described impeller 100, by which the overall performance of the electric machine can also be improved.
  • the vacuum cleaner is tested below.
  • the fan in the vacuum cleaner uses different impellers.
  • Table 1 below shows performance test data for the examples of the impellers of the present invention and the comparative examples of the impellers of the prior art, respectively.
  • the US-based S3-L041C vacuum cleaner is commonly used.
  • the vacuum cleaner in the embodiment of the present invention adopts the impeller structure shown in FIG. 1 to FIG. 3, specifically, the blade is a flat plate twisted blade and the leading edge portion of the blade is inclined with respect to the rotating direction w toward the downstream side 22, and the trailing edge of the blade The segments are tilted toward the upstream side 21 with respect to the rotational direction w.
  • the tilt angles ⁇ in the first embodiment and the second embodiment are 25° and 35°, respectively, and the twist length of the leaf tip 123 of the leading edge portion of the blade is the total length of the blade.
  • the twisting length of the blade top 123 of the trailing edge section of the blade is 20% of the total length of the blade
  • the angle ⁇ of the leading edge surface 121 with respect to the central axis is 60°
  • the height b1 of the leading edge surface is 8 mm
  • the trailing edge The height b2 of the surface is 4 mm
  • the inlet mounting angle ⁇ 1 of the blade root, the outlet mounting angle ⁇ 2 are both 60°
  • each blade is provided with 8 blades.
  • the impeller in the comparative example was identical to the basic structure and parameters of the impeller of the present invention, except that the impeller in the comparative example was a flat blade.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种叶轮、风机和电机，所述叶轮（100）包括大致锥形的轮毂（11）和沿周向间隔布置在所述轮毂（11）的外周面上的多个叶片（12），所述叶片包括位于进口端的前缘面和位于出口端的后缘面，所述叶片（12）为平板扭曲叶片，所述叶片（12）的叶片前缘段和后缘段在圆周方向上分别向相反方向旋扭倾斜。采用该结构的叶轮，进口端和出口端的流体损失得到有效减小，扩大叶轮的有效工作面积，使叶轮的工作性能显著提高，进而提高具有该结构叶轮的风机以及电机的整体性能。

Description

叶轮、风机和电机 技术领域
本发明属于叶轮领域，更具体地，涉及一种叶轮及具有其的风机、电机。
背景技术
吸尘器中是通过电动机驱动叶轮高速旋转，以在密封壳体内形成负压环境，使尘屑等被吸入集尘装置中，从而达到清洁效果。其中，动叶轮属于吸尘器的关键部件，其性能好坏直接决定风机***的整体工作效率的高低。
而现有技术中的吸尘器普遍存在风机体积大、性能低的缺点，需要不断优化设计叶轮结构，进一步提升吸尘器的工作性能。
发明内容
针对现有技术的上述缺陷或不足，本发明提供了一种叶轮，能够优化提高工作性能。
为实现上述目的，本发明提供了一种叶轮，所述叶轮包括大致锥形的轮毂和沿周向间隔布置在所述轮毂的外周面上的多个叶片，所述叶片包括位于进口端的前缘面和位于出口端的后缘面，所述叶片为平板扭曲叶片，所述叶片的叶片前缘段和后缘段在圆周方向上分别向相反方向旋扭倾斜。
优选地，所述叶片的叶片前缘段相对于所述叶轮的旋转方向朝向下游侧旋扭倾斜，所述叶片的叶片后缘段相对于所述旋转方向朝向上游侧旋扭倾斜。
优选地，所述叶片后缘段朝向上游侧旋扭倾斜的倾斜偏角δ满足：10°≤δ≤45°。
优选地，所述叶片前缘段的上游侧面形成为凸形面且下游侧面形成为凹形面，所述叶片前缘段的叶顶部的旋扭长度占所述叶片的总长的10％～50％。
优选地，所述叶片后缘段的上游侧面形成为凹形面且下游侧面形成为凸
形面，所述叶片后缘段的叶顶部的旋扭长度占所述叶片的总长的5％～30％。
优选地，所述前缘面为相对于所述轮毂的中心轴线的倾斜平面，该倾斜平面相对于所述中心轴线的夹角为30°≤γ≤90°。
优选地，所述叶片包括连接于所述轮毂的外周面上并从所述前缘面延伸至所述后缘面的叶根部以及从所述前缘面的顶端延伸至所述后缘面的顶端的叶顶面，从所述前缘面向所述后缘面的延伸方向上，所述叶顶面相对于所述叶根部的高度逐渐递减。
优选地，所述前缘面的高度b1和所述后缘面的高度b2分别满足：5mm≤b1≤15mm，2mm≤b2≤7mm。
优选地，所述叶根部的进口安装角为β1，出口安装角为β2，且满足：25°≤β1≤75°，40°≤β2≤80°，所述叶根部的叶根边缘线为从所述前缘面的底端延伸至所述后缘面的底端的平滑曲线。
优选地，所述叶片的叶顶部的进口安装角为β3，出口安装角为β4，且满足：25°≤β3≤75°，35°≤β4≤80°，所述叶顶面为从所述前缘面的顶端延伸至所述后缘面的顶端的平滑曲面。
优选地，所述轮毂的外周面上沿周向等间隔分布有5～12个所述叶片。
此外，本发明还相应提供了分别包括上述叶轮的一种风机和一种电机。
通过上述技术方案，本发明的叶轮中对叶片的形状进行了优化设计，尤其是在前缘段和后缘段，对平板扭曲叶片的前缘段相对于叶轮旋转方向朝向下游侧旋扭倾斜一定角度，以使得叶片前缘段的上游侧面形成为凸形面，后缘段相对于叶轮旋转方向朝向上游侧旋扭倾斜一定角度，以使得叶片后缘段的上游侧面形成为凹形面，采用该结构的叶轮，进口端和出口端的流体损失得到有效减小，扩大叶轮的有效工作面积，叶轮的工作性能显著提高。
本发明的其它特征和优点将在随后的具体实施方式部分予以详细说明。
附图说明
图1是根据本发明的优选实施例的叶轮的立体图；
图2是图1中的叶轮的主视图；
图3是图1中的叶轮的俯视图。
附图标记：
100：叶轮
11：轮毂；12：叶片；
121：前缘面；122：后缘面；
123：叶顶；124：叶根；
125凸形面；126凹形面；
21上游；22下游；
δ：倾斜偏角
γ：夹角
b1：前缘面的高度
b2：后缘面的高度
W：旋转方向
β1：叶根部的进口安装角
β2：叶根部的出口安装角
β3：叶顶部的进口安装角
β4：叶顶部的出口安装角
具体实施方式
以下结合附图对本发明的具体实施方式进行详细说明。应当理解的是，此处所描述的具体实施方式仅用于说明和解释本发明，并不用于限制本发明。
需要说明的是，在不冲突的情况下，本发明中的实施例及实施例中的特征可以相互组合。
在本发明中，在未作相反说明的情况下，使用的方位词如“上、下、顶、底”通常是针对附图所示的方向而言的或者是针对竖直、垂直或重力方向上而言的各部件相互位置关系描述用词。
下面将参考附图并结合实施例来详细说明本发明。
如图1至图3所示，本发明提供了一种叶轮100，包括大致锥形的轮毂11和沿周向间隔布置在轮毂11的外周面上的多个叶片12，每个叶片12包括位于进口端的前缘面121和位于出口端的后缘面122，所述叶片12为平板扭曲叶片，所述叶片12的叶片前缘段和后缘段在圆周方向上分别向相反方向旋扭倾斜。
优选地，所述叶片12的叶片前缘段相对于所述叶轮12的旋转方向w朝向下游侧22旋扭倾斜，所述叶片12的叶片后缘段相对于所述旋转方向w朝向上游侧21旋扭倾斜。需要说明的是，叶片前缘段也不限于向下游侧22扭转，叶片后缘段也不限于向上游侧21扭转，对于同一叶轮100，也可反向于图示的旋转方向w旋转，但效率相对差。
由于叶片12的前缘段向下游侧22扭转，后缘段向上游侧21扭转，有利于贴合流体引流，尤其是扭转后的凸形面125和凹形面126呈流线型等。总之，通过对平板叶片的前缘和后缘分别向相反方向旋扭，本发明的叶轮100可以有效减小叶片12的进口端和出口端的流体损失，扩大叶轮100在小流量的情况下的工作面积，即增加了有效工作范围，大大提升叶轮100的工作性能。
具体地，所述叶片12后缘段朝向上游侧21旋扭倾斜的倾斜偏角δ优选满足：10°≤δ≤45°，参见图1。例如，δ可取15°、25°、40°等，具体可根据实际情况具体设定。
参见图1，叶片12的前缘段向下游侧22扭转后，使得叶片12前缘段的上游侧面形成为凸形面125且下游侧面形成为凹形面126。其中，所述叶片12前缘段的叶顶部的旋 扭长度占所述叶片12的总长的比例优选为10％～50％。
参见图1，叶片12的后缘段向上游侧21扭转后，使得叶片12后缘段的上游侧面形成为凹形面126且下游侧面形成为凸形面125。其中，所述叶片12后缘段的叶顶部的旋扭长度占所述叶片12的总长的比例优选为5％～30％。
可见地，叶片12的该流线型设计有利于降低流体在叶片通道内的损失，改善流体的流动特性，从而提高叶轮100的工作性能。
具体地，叶片12的前缘面121为相对于大致锥形状的所述轮毂11的中心轴线的倾斜平面，该倾斜平面相对于所述中心轴线的夹角为γ且满足：30°≤γ≤90°，即流体由每个叶片12的前缘面121流入时为倾斜方向流入，有效地控制叶片12进口端的风量风压，减小了进口端流体的损失。
叶片12包括连接于所述轮毂11的外周面上并从所述前缘面121延伸至所述后缘面122的叶根部124以及从所述前缘面121的顶端延伸至所述后缘面122的顶端的叶顶面123，从所述前缘面121向所述后缘面122的延伸方向上，所述叶顶面123相对于所述叶根部124的高度逐渐递减。具体地，即从叶片12的前缘面121的高度b1到所述后缘面122的高度b2是逐渐递减的。其中，优选地分别满足：5mm≤b1≤15mm，2mm≤b2≤7mm。换言之，每个叶片12的前缘面121的叶顶面123相对于所述叶根部124的高度值b1最大，每个叶片12的后缘面121的叶顶面123相对于所述叶根部124的高度值b2最小，在叶片12的最大高度b1和最小高度b2之间的高度是逐渐递减的。通过该叶片高度的设计及限制，能够在保证叶片12的结构强度和工作性能的同时，减小叶片12的体积，从而降低整个风机的重量。
为实现流线型设计，所述叶根部124的叶根边缘线优选为从所述前缘面121的底端延伸至所述后缘面122的底端的平滑曲线。
另外如图3所示，叶片12的叶根部124的进口安装角为β1，出口安装角为β2，且满足：25°≤β1≤75°，40°≤β2≤80°。具体地，结合图1所示，叶片12的叶根部124的叶根边缘线是叶片12的侧面与轮毂11的外周面的相交线，即面与面之间的相交曲线，由此叶片12的叶根部124的进口安装角为叶根边缘线的最前缘点处的第一切线与第二切线之间的夹角。所述第一切线为叶根边缘线的最前缘点相对于该叶根边缘线的切线，所述第二切线为该最前缘点相对于以该最前缘点与轮毂11的中心轴线距离为半径的圆的切线。同样地，出口安装角为叶根边缘线的最后缘点处的切线夹角，即最后缘点相对于叶根边缘线的切线与该最后缘点相对于以该最后缘点与轮毂11的中心轴线距离为半径的圆的切线之间的夹角β2。
此外，为进一步实现流线型设计，所述叶顶部123的叶顶面优选为从所述前缘面121 的顶端延伸至所述后缘面122的顶端的平滑曲面。
另外如图3所示，叶片12的叶顶部123的进口安装角为β3，出口安装角为β4，且满足：25°≤β3≤75°，35°≤β4≤80°。具体地，结合图1所示，所述叶顶面的叶顶边缘线为叶片12的叶顶面与侧面的相交线，叶片12的叶顶部123的进口安装角为叶顶边缘线的最前缘点处的第一切线与第二切线之间的夹角。所述第一切线为叶顶边缘线的最前缘点相对于该叶顶边缘线的切线，所述第二切线为该最前缘点相对于以该最前缘点与轮毂11的中心轴线距离为半径的圆的切线。同样地，出口安装角为叶顶边缘线的最后缘点处的切线夹角，即最后缘点相对于叶顶边缘线的切线与该最后缘点相对于以该最后缘点与轮毂11的中心轴线距离为半径的圆的切线之间的夹角β4。
由此，将β1、β2、β3、β4、限制为30°≤β1≤80°，40°≤β2≤80°，25°≤β3≤75°，35°≤β4≤80°，可进一步减小了进口端及出口端的流体损失。
优选地，本实施例中提及的所有叶轮100，在其所述轮毂11的外周面上沿周向等间隔分布有5～12个所述叶片12。
在上述叶轮100的优化结构的基础上，本发明还提供了一种风机，其包括上述叶轮100。通过采用该叶轮100，可以提高风机的整体性能。同样的，本发明还提供了一种电机，包括上述的叶轮100，通过采用该叶轮100，也可以提高电机的整体性能。
以下对吸尘器进行试验。其中，吸尘器中的风机采用了不同的叶轮。具体地，下表1显示的是分别采用本发明的叶轮的实施例和采用现有技术的叶轮的对比例的性能试验数据。
其中，采用市面常见的美的S3-L041C吸尘器。本发明的实施例中的吸尘器采用了图1至图3所示的叶轮结构，具体地，叶片为平板扭曲叶片且叶片前缘段相对于旋转方向w朝向下游侧22旋扭倾斜，叶片后缘段相对于旋转方向w朝向上游侧21旋扭倾斜，实施例1、实施例2中的倾斜偏角δ分别为25°、35°，叶片前缘段的叶顶部123的旋扭长度占叶片总长的35％，叶片后缘段的叶顶部123的旋扭长度占叶片总长的20％，前缘面121相对于中心轴线的夹角γ为60°，前缘面的高度b1为8mm，后缘面的高度b2为4mm，叶根部的进口安装角β1、出口安装角β2均为60°，叶顶部的进口安装角β3、出口安装角β4均为50°，每个叶轮安装有8个叶片。对比例中的叶轮与本发明的叶轮的基本结构、参数相同，不同之处在于对比例中的叶轮为平板叶片。
表1：
Figure PCTCN2017113991-appb-000001
从表格中的数据对比可以看出，本发明的结构优化后的叶轮的风量、真空度和效率都显著高于现有技术的叶轮。
以上结合附图详细描述了本发明的优选实施方式，但是，本发明并不限于上述实施方式中的具体细节，在本发明的技术构思范围内，可以对本发明的技术方案进行多种简单变型，这些简单变型均属于本发明的保护范围。
另外需要说明的是，在上述具体实施方式中所描述的各个具体技术特征，在不矛盾的情况下，可以通过任何合适的方式进行组合，为了避免不必要的重复，本发明对各种可能的组合方式不再另行说明。
此外，本发明的各种不同的实施方式之间也可以进行任意组合，只要其不违背本发明的思想，其同样应当视为本发明所公开的内容。

Claims (13)

  1. 一种叶轮，所述叶轮(100)包括大致锥形的轮毂(11)和沿周向间隔布置在所述轮毂的外周面上的多个叶片(12)，所述叶片包括位于进口端的前缘面和位于出口端的后缘面，所述叶片为平板扭曲叶片，所述叶片的叶片前缘段和后缘段在圆周方向上分别向相反方向旋扭倾斜。
  2. 根据权利要求1所述的叶轮，其特征在于，所述叶片的叶片前缘段相对于所述叶轮的旋转方向(w)朝向下游侧旋扭倾斜，所述叶片的叶片后缘段相对于所述旋转方向(w)朝向上游侧旋扭倾斜。
  3. 根据权利要求1～2中任意一项所述的叶轮，其特征在于，所述叶片后缘段朝向上游侧旋扭倾斜的倾斜偏角δ满足：10°≤δ≤45°。
  4. 根据权利要求1～3中任意一项所述的叶轮，其特征在于，所述叶片前缘段的上游侧面形成为凸形面且下游侧面形成为凹形面，所述叶片前缘段的叶顶部的旋扭长度占所述叶片的总长的10％～50％。
  5. 根据权利要求1～4中任意一项所述的叶轮，其特征在于，所述叶片后缘段的上游侧面形成为凹形面且下游侧面形成为凸形面，所述叶片后缘段的叶顶部的旋扭长度占所述叶片的总长的5％～30％。
  6. 根据权利要求1～5中任意一项所述的叶轮，其特征在于，所述前缘面为相对于所述轮毂的中心轴线的倾斜平面，该倾斜平面相对于所述中心轴线的夹角为30°≤γ≤90°。
  7. 根据权利要求1～6中任意一项所述的叶轮，其特征在于，所述叶片包括连接于所述轮毂的外周面上并从所述前缘面延伸至所述后缘面的叶根部以及从所述前缘面的顶端延伸至所述后缘面的顶端的叶顶面，从所述前缘面向所述后缘面的延伸方向上，所述叶顶面相对于所述叶根部的高度逐渐递减。
  8. 根据权利要求7所述的叶轮，其特征在于，所述前缘面的高度b1和所述后缘面的高度b2分别满足：5mm≤b1≤15mm，2mm≤b2≤7mm。
  9. 根据权利要求7所述的叶轮，其特征在于，所述叶根部的进口安装角为β1，出口安装角为β2，且满足：25°≤β1≤75°，40°≤β2≤80°，所述叶根部的叶根边缘线为从所述前缘面的底端延伸至所述后缘面的底端的平滑曲线。
  10. 根据权利要求7所述的叶轮，其特征在于，所述叶片的叶顶部的进口安装角为β3，出口安装角为β4，且满足：25°≤β3≤75°，35°≤β4≤80°，所述叶顶面为从所述前缘 面的顶端延伸至所述后缘面的顶端的平滑曲面。
  11. 根据权利要求1～10中任意一项所述的叶轮，其特征在于，所述轮毂的外周面上沿周向等间隔分布有5～12个所述叶片。
  12. 一种风机，其特征在于，所述风机包括权利要求1～11中任意一项所述的叶轮。
  13. 一种电机，其特征在于，所述电机包括权利要求1～11中任意一项所述的叶轮。
PCT/CN2017/113991 2017-07-03 2017-11-30 叶轮、风机和电机 WO2019006972A1 (zh)

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CN107143522A (zh) * 2017-07-03 2017-09-08 广东威灵电机制造有限公司 叶轮、风机和电机
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EP2189663A2 (en) * 2008-11-21 2010-05-26 Hitachi Plant Technologies, Ltd. Centrifugal compressor
CN201606305U (zh) * 2009-12-15 2010-10-13 北京北机机电工业有限责任公司 新型风机叶轮
JP6034162B2 (ja) * 2012-11-30 2016-11-30 株式会社日立製作所 遠心式流体機械
CN103912519A (zh) * 2013-01-09 2014-07-09 发那科株式会社 形状由多条直线定义的叶轮的形成方法以及叶轮
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