WO2016066111A1

WO2016066111A1 - Backward centrifugal impeller and centrifugal blower

Info

Publication number: WO2016066111A1
Application number: PCT/CN2015/093124
Authority: WO
Inventors: 刘池; 熊军; 廖俊杰; 彭勃
Original assignee: 珠海格力电器股份有限公司
Priority date: 2014-10-29
Filing date: 2015-10-28
Publication date: 2016-05-06
Also published as: CN104314865A

Abstract

Disclosed are a backward centrifugal impeller and a centrifugal blower, comprising: a chassis (10); a plurality of air guide blades (20), wherein the plurality of air guide blades (20) are arranged in a circumferential direction of the chassis (10), and the air guide blades (20) extend from the centre of the chassis (10) to an outer edge of the chassis (10), and a diversion channel (40) is formed between each two adjacent air guide blades (20); and a splitter-blade (30), provided in the diversion channel (40) so as to reduce the speed variation of gas in the diversion channel (40). The backward centrifugal impeller and the centrifugal blower are able to reduce the gas flow variation in the diversion channel such that the gas flow speed in the diversion channel is even, which prevents the generation of turbulence noise and improves the performance of the backward centrifugal impeller.

Description

Backward centrifugal impeller and centrifugal fan

Technical field

The invention relates to the technical field of wind turbines, in particular to a backward centrifugal impeller and a centrifugal fan.

Background technique

The centrifugal impeller is named as the forward, radial and backward impeller according to the angle between the exit side and the opposite direction of the peripheral speed. The forward impeller exit angle is greater than 90°, the radial impeller exit angle is equal to 90°, and the backward impeller exit The angle is less than 90°. In the same outer diameter and speed of the impeller, under the same air volume, the full pressure of the outlet of the forward impeller is greater than that of the radial impeller. The total aerodynamic noise of the impeller is proportional to the flow rate and total pressure. Therefore, the use of a backward impeller can achieve better noise performance without requiring a higher total pressure condition. However, the degree of rearward expansion of the long blade flow channel is severe, resulting in uneven airflow velocity in the flow channel, causing turbulence and turbulence noise.

Summary of the invention

The main object of the present invention is to provide a backward centrifugal impeller and a centrifugal fan to solve the problem of turbulent noise which is easy to generate in the backward centrifugal impeller in the prior art.

In order to achieve the above object, according to an aspect of the invention, a rearward centrifugal impeller is provided, comprising: a chassis; a plurality of air guiding blades, a plurality of air guiding blades are arranged along a circumference of the chassis, and each of the air guiding blades is from the chassis The central portion extends toward the outer edge of the chassis, and a flow guiding channel is formed between two adjacent air guiding vanes; the backward centrifugal impeller further includes: a splitter vane disposed in the diversion channel to reduce gas in the diversion channel Speed changes.

Further, the extending direction of the splitter blade is consistent with the extending direction of the wind guide vane, and the distance from the center of the splitter blade near the center of the chassis to the center of the chassis is greater than the distance from the center of the guide vane near the center of the chassis to the center of the chassis.

Further, the splitter vanes are disposed on the chassis and are located in a downstream section of the flow guide channel adjacent the outer edge of the chassis.

Further, the length of the splitter blade is 1/3 to 2/3 of the length of the wind guide blade.

Further, the distance from the splitter blade to the suction face side of the wind guide blade is smaller than the distance from the splitter blade to the pressure face side of the wind guide blade.

Further, a splitter blade is disposed between the adjacent two wind guide vanes, and the distance from the splitter vane to the suction side of the wind guide vane is 1/3 of the width of the guide passage at the position where the splitter vane is located.

Further, the distance from the splitter blade to the suction face side of the wind guide blade is greater than the distance from the splitter blade to the pressure face side of the wind guide blade.

Further, a splitter vane is disposed between the adjacent two guide vanes, and the distance from the splitter vane to the pressure side of the wind guide vane is 1/3 of the width of the diversion passage at the position where the splitter vane is located.

Further, a splitter vane is disposed between the adjacent two air guiding vanes, and the splitter vane is located at the center of the diversion channel.

Further, the width of the wind guide vanes is consistent with the width of the splitter vanes.

Further, the backward centrifugal impeller further includes a fixed ring, and the outer ends of the air guiding blade and the splitter blade are fixedly connected to the fixed ring.

According to another aspect of the present invention, a centrifugal fan is provided, including a backward centrifugal impeller, and the backward centrifugal impeller is the above-described backward centrifugal impeller.

According to the technical solution of the present invention, the plurality of air guiding blades are evenly arranged along the circumferential direction of the chassis, and each of the air guiding blades extends from the center of the chassis to the outer edge of the chassis, and a guiding channel is formed between the adjacent two guiding blades. The flow guiding channel formed at this time is widened from the center of the chassis to the outer edge of the chassis, and when the gas flows out from the flow guiding channel, the velocity of the gas decreases with the widening of the guiding channel; the splitter blade It is disposed in the flow guiding channel, can occupy the space of the guiding channel, reduce the volume change of the guiding channel, and further reduce the velocity change of the gas in the guiding channel. The invention provides a shunt blade in the flow guiding channel capable of reducing the velocity change of the gas in the flow guiding channel, so that the gas flow velocity in the guiding channel is changed little, the gas flow velocity in the guiding channel is uniform, and the disorder is not easy to occur. In addition, the generation of turbulent noise can be avoided, and the performance of the backward centrifugal impeller can be improved.

DRAWINGS

The accompanying drawings, which are incorporated in the claims of the claims In the drawing:

Figure 1 is a schematic perspective view showing a first embodiment of a backward centrifugal impeller of the present invention;

Figure 2 is a schematic plan view showing a first embodiment of the backward centrifugal impeller of the present invention;

Figure 3 is a schematic perspective view showing a second embodiment of the backward centrifugal impeller of the present invention;

Figure 4 is a schematic plan view showing a second embodiment of the backward centrifugal impeller of the present invention;

Figure 5 is a schematic perspective view showing a third embodiment of the backward centrifugal impeller of the present invention;

Figure 6 is a schematic plan view showing a third embodiment of the backward centrifugal impeller of the present invention;

Figure 7 is a view schematically showing a distribution diagram of a gas flow velocity and an axial vortex of a gas in a flow guiding passage of a backward centrifugal impeller in the prior art;

Fig. 8 is a view schematically showing the distribution of the gas flow velocity and the axial vortex of the gas in the flow guiding passage of the backward centrifugal impeller of the present invention.

Wherein, the above figures include the following reference numerals:

10, the chassis; 20, the wind guide blade; 30, the splitter blade; 40, the flow guiding channel; 50, the hub; 60, the fixed ring.

detailed description

It should be noted that the embodiments in the present application and the features in the embodiments may be combined with each other without conflict. The invention will be described in detail below with reference to the drawings in conjunction with the embodiments.

Referring to Figures 1 and 2, in accordance with a first embodiment of the present invention, a rearward centrifugal impeller is provided. The rearward centrifugal impeller includes a chassis 10, a plurality of air guiding blades 20, and a splitter blade 30. The plurality of air guiding blades 20 are evenly arranged along the circumferential direction of the chassis 10, and each of the air guiding blades 20 extends from the center of the chassis 10 toward the outer edge of the chassis 10, and a flow guiding channel 40 is formed between the two adjacent air guiding blades 20, The flow guiding passage 40 formed at this time is sequentially widened from the center of the chassis 10 toward the outer edge of the chassis 10, and when the gas flows out into the flow guiding passage 40, the velocity of the gas becomes wider as the flow guiding passage 40 becomes wider. In order to prevent the attenuation of the gas velocity, the splitter blade 30 of the present embodiment is disposed in the flow guiding channel 40, can occupy the space of the flow guiding channel 40, reduce the volume change of the guiding channel 40, and thereby reduce the flow guiding channel. The velocity of the gas within 40 changes. The present invention provides a shunting vane 30 capable of reducing the velocity change of the gas in the flow guiding passage 40 in the flow guiding passage 40, so that the gas flow velocity in the guiding passage 40 is small, and the disorder is not likely to occur, and the guiding passage 40 is not easily generated. The gas flow rate inside is uniform, which can avoid the generation of turbulent noise and improve the performance of the backward centrifugal impeller.

According to the structure of the backward centrifugal impeller according to the present embodiment, at the outer edge of the chassis 10, the volume of the flow guiding passage 40 is the largest, the speed of the gas changes the fastest, and the speed is the smallest, in order to effectively prevent the gas velocity from changing too fast, The extending direction of the splitter blade 30 in this embodiment coincides with the extending direction of the wind guide vane 20, and the distance from the center of the splitter blade 30 near the center of the chassis 10 to the center of the chassis 10 is greater than the center of the wind guide blade 20 near the chassis 10. The distance from one end of the chassis 10 to the center of the disk 10 facilitates a reduction in the change in gas velocity at the wider position of the flow channel 40.

Preferably, the splitter vane 30 of the present embodiment is disposed on the chassis 10 and located at a downstream portion of the flow guiding passage 40 near the outer edge of the chassis 10, capable of diverting gas at the widest position of the flow guiding passage 40, After the splitter vanes 30 are increased, the degree of expansion of the flow guiding passages 40 is significantly reduced, and the relative velocity of the airflow changes more uniformly.

Preferably, the length of the splitter blade 30 is 1/3 to 2/3 of the length of the wind guide vane 20, for example, 1/2, which can effectively prevent the flow velocity of the gas from changing too fast at a wide position of the flow guide passage 40 to generate The emergence of a disordered phenomenon.

The splitter blade 30 of the present embodiment is disposed close to the wind guide vane 20, which can reduce the influence of the axial eddy current on the main flow, reduce the eddy current drop of the blade suction surface, reduce the eddy current noise, and improve the sound quality.

Referring again to FIGS. 1 and 2, in a preferred embodiment of the present invention, the distance from the side of the suction vane 30 to the suction side of the air guide vane 20 is smaller than the side of the pressure side of the splitter vane 30 to the air guide vane 20. distance. More preferably, a diverting blade 30 is disposed between the adjacent two air guiding blades 20, and the distance from the side of the suction surface of the diverting blade 30 to the suction surface of the suction vane 20 is the diversion channel 40 at the position where the diverting blade 30 is located. 1/3 of the width.

Referring to FIG. 7 and FIG. 8 , as can be seen from FIG. 7 , the expansion of the flow guiding channel 40 is serious, and the air flow speed is from the inlet of the impeller to the outlet of the impeller, and the relative speed changes greatly, and a uniform transition cannot be formed, resulting in the guiding channel 40 . The internal gas velocity distribution is uneven, causing flow disturbance. In Fig. 8, after the splitter blade 30 is added, the degree of expansion of the flow guiding channel 40 is significantly reduced, and the relative velocity of the airflow is uniformly changed. At this time, the axial eddy current between the splitter blade 30 and the pressure surface of the wind deflecting blade 20 is more obvious. . In Fig. 7, the velocity of the airflow on the suction surface, that is, the suction surface of the air guiding blade 20 is high, and it is easy to form the suction surface layer. Shedding phenomenon. Providing the diverting blade 30 near the suction surface of the wind guide vane 20 can effectively reduce the influence of the axial vortex, and reduce the speed difference between the suction surface and the pressure surface, that is, the pressure surface of the wind guide vane 20, thereby improving the suction surface layer. The eddy current shedding phenomenon reduces the influence of the axial eddy current on the main stream, reduces the eddy current shedding of the blade suction surface, reduces the eddy current noise, and improves the sound quality.

Preferably, the splitter blade 30 of the present invention in the present embodiment is identical to the guide vane 20 except for the length of the wind guide vane 20, specifically, the width of the wind guide vane 20 and the splitter vane The width of 30 is consistent, the shunting effect is good, the structure is simple, and it is easy to implement.

Preferably, the hub 50 is disposed at the center of the chassis 10 in this embodiment. During use, the arrangement of the hub 50 can provide the necessary structural foundation for the installation of the motor, and has a simple structure and convenient assembly and disassembly.

In order to improve the structural strength of the entire backward centrifugal impeller, the backward centrifugal impeller of the present embodiment further includes a fixing ring 60, and the outer ends of the air guiding blade 20 and the diverting blade 30 are fixed on the fixing ring 60, which is convenient for improving the present invention. Air intake and stability to the centrifugal impeller.

Referring to FIG. 3 and FIG. 4, according to a second embodiment of the present invention, a backward centrifugal impeller is provided. The structure of the backward centrifugal impeller of the present embodiment is substantially the same as that of the first embodiment, and is different. The splitter blade 30 of the present embodiment is located at the center of the flow guiding channel 40, which can improve the airflow performance in the flow guiding channel 40, reduce the uneven flow of the airflow in the guiding channel 40, reduce the eddy current noise, and improve the sound quality.

Referring to FIG. 5 and FIG. 6, according to a third embodiment of the present invention, a backward centrifugal impeller is provided. The structure of the backward centrifugal impeller of this embodiment is substantially the same as that of the first embodiment, and the difference is The distance from the side of the suction vane 30 of the present embodiment to the suction side of the wind guide vane 20 is greater than the distance from the side of the splitter vane 30 to the pressure side of the wind guide vane 20. More preferably, the distance from the branching vane 30 to the pressure surface side of the air guiding vane 20 is 1/3 of the width of the flow guiding passage 40 at the position where the diverting vane 30 is located, as in the first embodiment, the shunting of the present embodiment The arrangement of the blade 30 can effectively reduce the influence of the axial eddy current, reduce the speed difference before the suction surface and the pressure surface, thereby improving the eddy current falling off of the suction surface of the suction surface, thereby reducing the influence of the axial eddy current on the main stream and reducing the suction of the blade. The surface layer vortex shedding is removed to avoid the generation of turbulent noise and improve the performance of the backward centrifugal impeller.

According to a fourth embodiment of the present invention, there is provided a centrifugal fan comprising a backward centrifugal impeller, the backward centrifugal impeller being a backward centrifugal impeller in any of the above embodiments.

From the above description, it can be seen that the above-mentioned embodiments of the present invention achieve the following technical effects: improving the airflow performance in the flow channel, reducing the uneven flow of the airflow in the flow channel, reducing the influence of the axial vortex on the main flow, and reducing the suction of the blade. The surface layer vortex shedding, reducing eddy current noise and improving sound quality.

The above are only the preferred embodiments of the present invention, and are not intended to limit the present invention, and various modifications and changes can be made to the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and scope of the present invention are intended to be included within the scope of the present invention.

Claims

A backward centrifugal impeller comprising:

Chassis (10);

a plurality of air guiding blades (20) arranged along a circumference of the chassis (10), and each of the air guiding blades (20) is from a center of the chassis (10) Extending toward an outer edge of the chassis (10), forming a flow guiding channel (40) between two adjacent air guiding blades (20);

The method further comprises: the backward centrifugal impeller further comprising:

A splitter vane (30) is disposed within the flow guide passage (40) to reduce a change in velocity of the gas within the flow guide passage (40).
The backward centrifugal impeller according to claim 1, wherein a direction in which the splitter vane (30) extends coincides with an extending direction of the wind guide vane (20), and a close proximity of the splitter vane (30) a center of one end of the chassis (10) to a center of the chassis (10) is greater than a center of the wind guide vane (20) near a center of the chassis (10) to a center of the chassis (10) distance.
The backward centrifugal impeller according to claim 1, wherein said splitter vane (30) is disposed on said chassis (10) and located adjacent said chassis (10) of said flow guiding passage (40) The downstream section of the outer edge.
The backward centrifugal impeller according to claim 1, wherein the length of the splitter vane (30) is 1/3 to 2/3 of the length of the wind guide vane (20).
The backward centrifugal impeller according to any one of claims 1 to 4, characterized in that the distance from the branching vane (30) to the suction side of the wind guide vane (20) is smaller than that of the splitter vane ( 30) A distance to the pressure side of the wind guide vane (20).
The backward centrifugal impeller according to claim 5, characterized in that a splitter blade (30) is disposed between two adjacent air guiding blades (20), and the splitter blade (30) is The distance on the suction side of the wind guide vane (20) is 1/3 of the width of the flow guiding passage (40) at the position where the splitter vane (30) is located.
The backward centrifugal impeller according to any one of claims 1 to 4, characterized in that the distance from the branching vane (30) to the suction side of the wind guide vane (20) is larger than that of the splitter vane ( 30) A distance to the pressure side of the wind guide vane (20).
The backward centrifugal impeller according to claim 7, wherein a splitter blade (30) is disposed between two adjacent air guiding blades (20), and the splitter blade (30) is The distance on the pressure side of the wind guide vane (20) is 1/3 of the width of the flow guiding passage (40) at the position where the splitter vane (30) is located.
The backward centrifugal impeller according to any one of claims 1 to 4, characterized in that a splitter blade (30) is disposed between two adjacent air guiding blades (20), the splitter blade (30) is located in the center of the flow guiding channel (40).
The backward centrifugal impeller according to any one of claims 1 to 4, characterized in that the width of the wind guide vane (20) coincides with the width of the splitter vane (30).
The backward centrifugal impeller according to any one of claims 1 to 4, wherein the backward centrifugal impeller further comprises a fixed ring (60), the air guiding blade (20) and the splitter blade ( The outer ends of 30) are each fixedly attached to the fixed ring (60).
A centrifugal fan comprising a backward centrifugal impeller, characterized in that the backward centrifugal impeller is a backward centrifugal impeller according to any one of claims 1 to 11.