CN106640752B

CN106640752B - Kitchen ventilator impeller

Info

Publication number: CN106640752B
Application number: CN201611178716.6A
Authority: CN
Inventors: 何立博; 茅忠群; 诸永定; 申志贤
Original assignee: Ningbo Fotile Kitchen Ware Co Ltd
Current assignee: Ningbo Fotile Kitchen Ware Co Ltd
Priority date: 2016-12-19
Filing date: 2016-12-19
Publication date: 2023-08-18
Anticipated expiration: 2036-12-19
Also published as: CN106640752A

Abstract

The invention discloses a kitchen ventilator impeller, which comprises a front disc, a rear disc and blades fixed between the front disc and the rear disc, and is characterized in that: the outer side edge of each blade is provided with straight line segments distributed at intervals and concave segments positioned between adjacent straight line segments, each concave segment is respectively corresponding to a corresponding R angle, and the R angles gradually increase from the middle of the blade or the position close to the middle of the blade to the two ends of the blade. Compared with the prior art, the invention has the advantages that: because the outer side of the vane of the impeller is provided with the straight line sections and the concave sections positioned between the adjacent straight line sections at intervals, each concave section is respectively corresponding to a corresponding R angle, and the R angles gradually increase from the middle of the vane or the position close to the middle of the vane to the two ends of the vane, namely, the effective acting area in the middle of the impeller is noise-reduced by adopting small waves, and the positions close to the two end discs of the impeller are noise-reduced by adopting large waves, thereby effectively improving the maximum static pressure and the static pressure of the effective air volume section while reducing the noise.

Description

Kitchen ventilator impeller

Technical Field

The invention relates to a range hood impeller.

Background

The existing multi-wing blade noise reduction mode mainly adopts a uniform wave saw tooth structure at the outer side edge of the blade, namely at the tail edge of the blade, and after the blade adopts the wave saw tooth structure, the noise can be reduced, but the actual acting area of the blade is greatly reduced, and the static pressure of a fan and the static pressure of an effective air volume section are reduced. The impeller of the centrifugal fan disclosed in the application number 201310639469.5 (application publication number CN 103696985A) comprises a front ring and a rear ring, a plurality of blades are fixed between the front ring and the rear ring, and the outlet ends of the blades are formed into wavy saw-tooth shapes by a plurality of saw teeth, so that the falling positions of wake vortices at the tail edges of the blades are changed, the distance between vortex cores is increased, disturbance of falling vortices on wake flow is restrained, and then pneumatic noise caused by unsteady pressure pulsation and wake vortices on the surfaces of the blades is reduced. As disclosed in the chinese patent application with application number 20110432234. X (application publication number CN 102536892U), the blade air inlet edge of the centrifugal fan is concave, convex, concave-convex, or oblique, the blade air outlet edge is formed by a straight line, a curved line, a broken line, or a combination of a curved line and a straight line, and after adopting the structure, the blade has a certain effect of noise reduction. Although the impeller of the conventional centrifugal fan can reduce fan noise to a certain extent by changing the shape of the outlet end of the blade, the impeller greatly reduces the actual acting area of the blade and the static pressure of the fan while reducing noise.

Disclosure of Invention

The invention aims to solve the technical problem of providing the extractor hood impeller which has good noise reduction effect and can simultaneously promote the maximum static pressure and the static pressure of an effective air volume section.

The technical scheme adopted for solving the technical problems is as follows: the impeller of the range hood comprises a front disc, a rear disc and blades fixed between the front disc and the rear disc, and is characterized in that: the outer side edge of each blade is provided with straight line segments distributed at intervals and concave segments positioned between adjacent straight line segments, each concave segment is respectively corresponding to a corresponding R angle, and the R angles gradually increase from the middle of the blade or the position close to the middle of the blade to the two ends of the blade.

Preferably, the blade further comprises a middle disc, the R angle corresponding to the concave section nearest to the middle disc is the smallest, and the R angle between the middle disc and the front disc on the blade and the R angle between the middle disc and the rear disc on the blade are distributed in an arithmetic progression.

Further preferably, the concave depth b of each concave section is equal, and the interval h between two adjacent concave sections is equal.

In order to make the size of the R angle and the distance between the adjacent R angles more reasonable, the R angles R corresponding to the two adjacent concave sections _n 、R _n+1 Meeting the distance hAnd θ is 1 degree or more and 10 degrees or less.

Further preferably, R angle R corresponding to the concave section of the blade nearest to the front disk ₁ The ratio of the spacing h to the spacing h is 0.01-R ₁ And/h is less than or equal to 0.2. After the numerical range is adopted, the concave section is cut off from the tail edge of the blade, so that noise can be reduced, and meanwhile, a high static pressure head can be reserved, and the resistance capacity of the air outlet can be improved.

It is further preferred that the distance between the middle of the concave section closest to the blade end and the corresponding end of the blade is a, and the ratio of the distance a to the concave depth b satisfies 3.ltoreq.a/b.ltoreq.20.

Further preferably, the ratio of the concave depth b to the spacing h satisfies 3.ltoreq.h/b.ltoreq.20.

As another preferable scheme, the R angle corresponding to the concave section in the middle of the blade is minimum, the R angles corresponding to the concave section nearest to the front disc and the concave section nearest to the rear disc on the blade are maximum and equal, and the R angles between the middle of the blade and the front disc and the R angles between the middle of the blade and the rear disc are distributed in an arithmetic progression.

Compared with the prior art, the invention has the advantages that: because the outer side of the vane of the impeller is provided with the straight line sections and the concave sections positioned between the adjacent straight line sections at intervals, each concave section is respectively corresponding to a corresponding R angle, and the R angles gradually increase from the middle or the position close to the middle of the vane to the two ends of the vane, namely, the effective acting area in the middle of the impeller is noise-reduced by adopting small waves, and the positions close to the two end discs of the impeller are noise-reduced by adopting large waves, thereby effectively improving the maximum static pressure and the static pressure of the effective air volume section while reducing the noise.

Drawings

FIG. 1 is a schematic diagram of an embodiment of the present invention;

FIG. 2 is a schematic view of a blade structure according to an embodiment of the present invention;

FIG. 3 is an enlarged schematic view of portion A of FIG. 2;

fig. 4 is a schematic diagram showing a relationship between R angles of two adjacent concave segments according to an embodiment of the present invention.

Detailed Description

The invention is described in further detail below with reference to the embodiments of the drawings.

As shown in fig. 1, the impeller of the range hood in this embodiment includes a vane 1, a front plate 2, a rear plate 3 and a middle plate 4, the vane passes through the middle plate 4, two ends of the vane 1 are respectively fixed on the front plate 2 and the rear plate 3, and the mounting structure of the vane 1 is the same as that of the existing impeller, and is not described here.

As shown in fig. 2 to 4, the outer side edge of the blade 1, i.e. the blade trailing edge, is provided with straight line segments 11 which are distributed at intervals and concave segments 12 which are positioned between adjacent straight line segments, i.e. the wave saw tooth structure is formed at the blade trailing edge. In particular, each concave section 12 corresponds to a respective R angle, and the R angle gradually increases from the middle of the blade 1 to both ends of the blade. In this embodiment, the R angle corresponding to the concave section 12 of the blade 1 nearest to the middle disc 4 is the smallest, and the R angles on the blade 1 between the middle disc 4 and the front disc 2 and the R angles on the blade 1 between the middle disc 4 and the rear disc 3 are all distributed in an arithmetic progression.

In this embodiment, the concave depth b of each concave section 12 is equal, and the concave depth b is the distance between the trough and the trailing edge of the blade. The distance h between two adjacent concave sections 12 is equal, and the distance h is the distance between two adjacent wave troughs. And, R angles R corresponding to two adjacent concave sections 12 _n 、R _n+1 With a spacing h ofWherein θ is used to control the variation of the R angle at the trailing edge of the blade along the length of the blade, and is generally controlled at 1.ltoreq.θ.ltoreq.10 depending on the impeller size and height. With the direction indicated by arrow B in FIG. 2 as the forward direction, the R angle R corresponding to the concave section 12 of the blade 1 nearest the front plate 2 ₁ The ratio of the pitch h to the spacing h is 0.01-R ₁ /h≤0.2。

In addition, the distance between the middle of the concave section 12 closest to the end and the corresponding end of the blade is a, and the ratio of the distance a to the concave depth b is 3-20. The ratio of the concave depth b to the interval h is more than or equal to 3 and less than or equal to 20.

Because the middle part of the impeller is an effective acting area, the impeller blades of the embodiment reduce noise by adopting small waves in the effective acting area of the middle part of the impeller, and the positions close to the front disc and the rear disc of the impeller adopt large waves for reducing noise.

While the foregoing is directed to the preferred embodiments of the present invention, it will be appreciated by those skilled in the art that various modifications and improvements may be made to the present invention without departing from the principles of the present invention, for example, the impeller without a center plate may be designed such that the R angle in the middle of the vane is the smallest, the R angles on the vane nearest the front and rear plates are the largest and equal, and the R angles between the middle of the vane and the front plate and the R angles between the middle of the vane 1 and the rear plate are all equally spaced, which are considered to be within the scope of the present invention.

Claims

1. A range hood impeller is a centrifugal impeller and comprises a front disc (2), a rear disc (3) and blades (1) fixed between the front disc and the rear disc, and is characterized in that: the outer side of the blade (1) is provided with straight line sections (11) distributed at intervals and concave sections (12) positioned between adjacent straight line sections, each concave section (12) corresponds to a corresponding R angle, and the R angles gradually increase from the middle of the blade (1) or a position close to the middle of the blade to the two ends of the blade.

2. The range hood impeller of claim 1, wherein: the novel solar energy turbine blade is characterized by further comprising a middle disc (4), wherein the R angle corresponding to the concave section (12) nearest to the middle disc (4) of the blade (1) is minimum, and the R angle between the middle disc (4) and the front disc (2) on the blade (1) and the R angle between the middle disc (4) and the rear disc (3) on the blade (1) are distributed in an arithmetic progression mode.

3. The range hood impeller of claim 1, wherein: the concave depth b of each concave section (12) is equal, and the interval h between two adjacent concave sections (12) is equal.

4. A range hood impeller according to claim 3, wherein: r angle R corresponding to two adjacent concave sections (12) _n 、R _n+1 Meeting the distance hAnd θ is 1 degree or more and 10 degrees or less.

5. The range hood impeller of claim 4, wherein: r angle R corresponding to the concave section (12) nearest to the front disc (2) on the blade (1) ₁ The ratio of the spacing h to the spacing h is 0.01-R ₁ /h≤0.2。

6. A range hood impeller according to claim 3, wherein: the distance between the middle of the concave section (12) closest to the blade end and the corresponding end of the blade is a, and the ratio of the distance a to the concave depth b is 3-20.

7. A range hood impeller according to claim 3, wherein: the ratio of the concave depth b to the interval h is more than or equal to 3 and less than or equal to 20.

8. The range hood impeller of claim 1, wherein: the R angle corresponding to the middle concave section (12) of the blade (1) is minimum, the R angles corresponding to the concave section (12) nearest to the front disc (2) and the concave section (12) nearest to the rear disc (3) on the blade (1) are maximum and equal, and the R angles between the middle of the blade (1) and the front disc (2) and the R angles between the middle of the blade (1) and the rear disc (3) are distributed in an arithmetic progression mode.