WO2019006972A1

WO2019006972A1 - Impeller, fan and motor

Info

Publication number: WO2019006972A1
Application number: PCT/CN2017/113991
Authority: WO
Inventors: 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
Priority date: 2017-07-03
Filing date: 2017-11-30
Publication date: 2019-01-10

Abstract

An impeller (100), fan and motor, the impeller (100) comprising an approximately conical hub (11) and a plurality of blades (12), provided at intervals along a circumferential direction on a peripheral surface of the hub (11). The blades comprise a front edge surface at an inlet end and a rear edge surface at an outlet end. The blades (12) are flat plates that have been twisted. Front edge sections and rear edge sections of the blades (12) are respectively twisted in opposite circumferential directions and form slopes. By adopting an impeller having this structure, fluid loss at the inlet and outlet ends can be effectively reduced, expanding the effective working area of the impeller, markedly improving the operating performance of the impeller, thereby improving the overall performance of a fan and motor employing the impeller having this structure.

Description

Impeller, fan and motor

Technical field

The invention belongs to the field of impellers, and more particularly to an impeller and a fan and an electric machine therewith.

Background technique

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. Among them, the impeller is a key component of the vacuum cleaner, and its performance directly determines the overall working efficiency of the fan system.

However, 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.

Summary of the invention

In view of the above-mentioned drawbacks or deficiencies of the prior art, the present invention provides an impeller capable of optimizing work performance.

To achieve the above object, 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.

Preferably, 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.

Preferably, the inclination angle δ of the trailing edge section of the blade toward the upstream side is inclined to satisfy: 10°≤δ≤45°.

Preferably, 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. %.

Preferably, 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

In the shape of the blade, 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.

Preferably, 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° ≤ γ ≤ 90°.

Preferably, 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.

Preferably, 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.

Preferably, the root mounting angle of the blade root is β1, the outlet mounting angle is β2, and satisfies: 25°≤β1≤75°, 40°≤β2≤80°, and 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.

Preferably, the inlet top angle of the blade tip of the blade is β3, the outlet mounting angle is β4, and satisfies: 25°≤β3≤75°, 35°≤β4≤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.

Preferably, 5 to 12 of the blades are distributed on the outer circumferential surface of the hub at equal intervals in the circumferential direction.

Further, the present invention accordingly provides a fan and an electric motor each including the above-described impeller.

Through the above technical solution, 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.

Other features and advantages of the invention will be described in detail in the detailed description which follows.

DRAWINGS

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.

Reference mark:

100: Impeller

11: wheel hub; 12: blade;

121: leading edge surface; 122: trailing edge surface;

123: leaf top; 124: leaf root;

125 convex surface; 126 concave surface;

21 upstream; 22 downstream;

δ: tilt angle

γ: angle

B1: the height of the leading edge

B2: height of the trailing edge

W: direction of rotation

11: inlet mounting angle of the root of the blade

22: outlet installation angle of the root of the blade

33: inlet mounting angle at the top of the leaf

44: outlet installation angle at the top of the leaf

Detailed ways

The specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. It is to be understood that the specific embodiments described herein are merely illustrative and not restrictive.

It should be noted that the embodiments in the present invention and the features in the embodiments may be combined with each other without conflict.

In the present invention, the 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. In the above, the components are described in terms of their positional relationship.

The invention will be described in detail below with reference to the drawings in conjunction with the embodiments.

As shown in FIGS. 1 to 3, 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.

Preferably, 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. It should be noted that 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.

Since the leading edge section of the blade 12 is twisted toward the downstream side 22, the trailing edge section is twisted toward the upstream side 21, which facilitates the fitting of the fluid drainage, and in particular, the twisted convex surface 125 and the concave surface 126 are streamlined and the like. In summary, by twisting the leading edge and the trailing edge of the flat blade in opposite directions, 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.

Specifically, the inclination angle δ of the trailing edge section of the blade 12 toward the upstream side 21 is preferably 10° ≤ δ ≤ 45°, see FIG. 1 . For example, δ may be 15°, 25°, 40°, etc., and may be specifically set according to actual conditions.

Referring to Figure 1, 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. Wherein the rotation of the leaf tip of the leading edge section of the blade 12 The ratio of the twist length to the total length of the blade 12 is preferably 10% to 50%.

Referring to Figure 1, 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. Wherein, 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%.

Visibly, 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.

Specifically, 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 γ and satisfies: 30° ≤ γ ≤ 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. Specifically, 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. Among them, it preferably satisfies: 5 mm ≤ b1 ≤ 15 mm, and 2 mm ≤ b2 ≤ 7 mm, respectively. In other words, 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. By designing and limiting the blade height, it is possible to reduce the volume of the blade 12 while ensuring the structural strength and workability of the blade 12, thereby reducing the weight of the entire fan.

To achieve a streamlined design, 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.

Further, as shown in Fig. 3, the inlet angle of the blade root portion 124 of the blade 12 is β1, the outlet mounting angle is β2, and it satisfies: 25° ≤ β1 ≤ 75°, 40° ≤ β2 ≤ 80°. Specifically, as shown in FIG. 1 , 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, and 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. Similarly, 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 β2 between the tangent to the circle of the radius.

Furthermore, to further achieve a streamlined design, 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.

Further, as shown in Fig. 3, the inlet tip angle of the blade tip portion 123 of the blade 12 is β3, the outlet mounting angle is β4, and it satisfies: 25° ≤ β3 ≤ 75°, 35° ≤ β4 ≤ 80°. Specifically, in conjunction with FIG. 1, 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, and 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. Similarly, 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 β4 between the tangent lines of the circle of radius.

Thus, β1, β2, β3, β4 are limited to 30° ≤ β1 ≤ 80°, 40° ≤ β2 ≤ 80°, 25° ≤ β3 ≤ 75°, 35° ≤ β4 ≤ 80°, which can be further reduced Fluid loss at the inlet and outlet ends.

Preferably, 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.

Based on the optimized structure of the impeller 100 described above, the present invention also provides a fan including the above-described impeller 100. By using the impeller 100, the overall performance of the fan can be improved. Similarly, 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. Among them, the fan in the vacuum cleaner uses different impellers. Specifically, 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.

Among them, 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 δ 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. 35%, 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 γ of the leading edge surface 121 with respect to the central axis is 60°, and 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 β1 of the blade root, the outlet mounting angle β2 are both 60°, the inlet mounting angle β3 at the top of the blade, and the outlet mounting angle β4 are both 50°, and 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.

Table 1:

As can be seen from the comparison of the data in the table, the air volume, vacuum degree and efficiency of the optimized impeller of the present invention are significantly higher than those of the prior art impeller.

The preferred embodiments of the present invention have been described in detail above with reference to the accompanying drawings. However, the present invention is not limited to the specific details of the embodiments described above, and various modifications may be made to the technical solutions of the present invention within the scope of the technical idea of the present invention. These simple variations are within the scope of the invention.

It should be further noted that the specific technical features described in the above specific embodiments may be combined in any suitable manner without contradiction. To avoid unnecessary repetition, the present invention has various possibilities. The combination method will not be described separately.

In addition, any combination of various embodiments of the invention may be made as long as it does not deviate from the idea of the invention, and it should be regarded as the disclosure of the invention.

Claims

An impeller (100) comprising a substantially conical hub (11) and a plurality of blades (12) circumferentially spaced apart on an outer circumferential surface of the hub, the blades including a leading edge at the 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 impeller according to claim 1, wherein a blade leading edge section of said blade is inclined toward a downstream side with respect to a rotational direction (w) of said impeller, and said blade trailing edge section of said blade is opposite to said The direction of rotation (w) is inclined toward the upstream side.
The impeller according to any one of claims 1 to 2, characterized in that the inclination angle δ of the trailing edge section of the blade toward the upstream side is inclined to satisfy: 10 ° ≤ δ ≤ 45 °.
The impeller according to any one of claims 1 to 3, characterized in that 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, the leaf of the leading edge section of the blade The length of the top twist is 10% to 50% of the total length of the blade.
The impeller according to any one of claims 1 to 4, characterized in that 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 leaf of the trailing edge section of the blade The length of the top twist is 5% to 30% of the total length of the blade.
The impeller according to any one of claims 1 to 5, wherein the leading edge surface is an inclined plane with respect to a central axis of the hub, and an angle of the inclined plane with respect to the central axis is 30 ° ≤ γ ≤ 90 °.
The impeller according to any one of claims 1 to 6, wherein 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 a tip surface extending from a top end of the leading edge face to a tip end surface of the trailing edge face, a height of the tip top face relative to the blade root portion from a direction in which the leading edge faces the trailing edge face Gradually decreasing.
The impeller according to claim 7, wherein 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 impeller according to claim 7, wherein said blade root has an inlet mounting angle of β1 and an outlet mounting angle of β2, and satisfies: 25° ≤ β1 ≤ 75°, 40° ≤ β2 ≤ 80°, The blade root edge line of the blade root is a smooth curve extending from the bottom end of the leading edge face to the bottom end of the trailing edge face.
The impeller according to claim 7, wherein an inlet mounting angle of the blade tip of the blade is β3, an outlet mounting angle is β4, and satisfies: 25° ≤ β3 ≤ 75°, 35° ≤ β4 ≤ 80° The top surface of the leaf is from the leading edge The top end of the face extends to a smooth curved surface at the top end of the trailing edge face.
The impeller according to any one of claims 1 to 10, characterized in that 5 to 12 of the blades are distributed on the outer circumferential surface of the hub at equal intervals in the circumferential direction.
A fan characterized by comprising the impeller according to any one of claims 1 to 11.
An electric machine comprising the impeller according to any one of claims 1 to 11.