CN216742162U - Centrifugal impeller, compressor and refrigeration equipment - Google Patents

Abstract

The application relates to a centrifugal impeller, a compressor and refrigeration equipment. The centrifugal impeller includes: a hub; the wheel cover is arranged at intervals with the hub along the axial direction of the centrifugal impeller; the main blades are clamped between the hub and the wheel cover and are arranged in pairs along the rotating direction of the centrifugal impeller, and each pair of main blades, the wheel cover and the hub define an air channel together; and each shunting fan blade is arranged in one air channel and divides the air channel into two sub air channels which are sequentially distributed along the rotating direction of the centrifugal impeller, and each shunting fan blade is provided with a shunting channel communicated between the two sub air channels. The centrifugal impeller, the compressor and the refrigeration equipment provided by the application have high energy transfer efficiency.

Description

Centrifugal impeller, compressor and refrigeration equipment

Technical Field

The application relates to the technical field of power, in particular to a centrifugal impeller, a compressor and refrigeration equipment.

Background

The centrifugal impeller is used as the heart of the centrifugal compressor, and is used for converting self mechanical energy into pressure energy and kinetic energy of airflow and providing power for the compressor. In a traditional centrifugal impeller, an airflow field formed inside the centrifugal impeller is very complex and is often accompanied by a plurality of phenomena such as boundary layer separation, vortex, jet flow and the like, so that the wind loss of the centrifugal impeller is serious, and the energy transfer efficiency is weakened.

SUMMERY OF THE UTILITY MODEL

In view of the above, it is necessary to provide a centrifugal impeller, a compressor, and a refrigeration apparatus having high energy transfer efficiency, in order to solve the problem of the reduction in energy transfer efficiency.

A centrifugal impeller, comprising:

a hub;

the wheel cover is arranged at intervals with the hub along the axial direction of the centrifugal impeller;

the main blades are clamped between the hub and the wheel cover and are arranged in pairs along the rotation direction of the centrifugal impeller, and each pair of main blades, the wheel cover and the hub define an air channel; and

each shunting fan blade is arranged in one air channel and divides the air channel into two sub air channels which are sequentially distributed along the rotation direction of the centrifugal impeller, and each shunting fan blade is provided with a shunting channel communicated between the two sub air channels.

In one embodiment, the number of the flow-dividing fan blades is multiple, all the air channels correspond to all the flow-dividing fan blades one to one, and each flow-dividing fan blade is arranged in one corresponding air channel.

In one embodiment, each of the flow dividing fan blades includes a first portion and a second portion, and in an airflow outflow direction in the air duct where each of the flow dividing fan blades is located, the first portion and the second portion of each of the flow dividing fan blades are arranged at an interval and define one of the flow dividing channels.

In one embodiment, each pair of main blades comprises a downstream main blade located downstream in the rotation direction of the centrifugal impeller;

each first part is provided with an injection channel, an air inlet of each injection channel is communicated with the corresponding air channel, and an air outlet of each injection channel faces to the suction surface of the corresponding downstream main fan blade.

In one embodiment, an air inlet aperture of each of the injection channels is larger than an air outlet aperture thereof.

In one embodiment, a plurality of flow guide channels are formed in the wheel cover, and all the flow guide channels correspond to all the flow dividing fan blades one to one;

each first portion comprises a first tail edge, and each flow guide channel is used for guiding the airflow at the position of the corresponding first tail edge to the air inlet of the corresponding spraying channel.

In one embodiment, each of the second portions includes an arcuate body segment defining the flow diversion channel with the corresponding first portion, the arcuate body segment having an arc greater than the arc of the first portion.

In one embodiment, each of the second portions further includes a trailing edge section sequentially disposed and connected to the arc-shaped main body section along an airflow outflow direction of the air duct in which the trailing edge section is disposed, and the trailing edge section extends in a radial direction of the centrifugal impeller.

In one embodiment, the wheel cover is provided with an air inlet communicated with each air duct, and the projection of each flow dividing fan blade in the plane where the air inlet is located is positioned outside the air inlet.

A compressor comprising a centrifugal impeller as claimed in any one of the preceding claims.

A refrigeration plant includes the above-mentioned compressor.

The centrifugal impeller, the compressor and the refrigeration equipment comprise an upstream main blade located in the rotation direction of the centrifugal impeller and a downstream main blade located in the rotation direction of the centrifugal impeller in each pair of main blades. When the centrifugal impeller works, the pressure surface of the upstream main fan blade and the suction surface of the downstream main fan blade are both arranged towards the air channel, and the air pressure of the pressure surface of the upstream main fan blade is greater than that of the suction surface of the downstream main fan blade. Because the flow dividing channels are formed in the flow dividing fan blades, on the basis of the air pressure balance principle, air flow on the pressure surface of the upstream main fan blade blows to the suction surface of the downstream main fan blade through the flow dividing channels, so that the loss of the boundary layer on the suction surface of the downstream main fan blade is caused, further, the wind loss of the boundary layer can be reduced, and the high energy transfer efficiency is achieved.

Drawings

Fig. 1 is a schematic overall structure diagram of a centrifugal impeller according to an embodiment of the present application;

FIG. 2 is a schematic view of the centrifugal impeller shown in FIG. 1 with the shroud removed;

FIG. 3 is a bottom perspective view of the centrifugal impeller shown in FIG. 2;

fig. 4 is a schematic structural view of each pair of main blades and one splitter blade in the centrifugal impeller shown in fig. 3;

fig. 5 is a cross-sectional view of the centrifugal impeller shown in fig. 1, with the main blade and the shunting blade removed, taken along a cross-section parallel to a shunting pressure surface of the shunting blade;

fig. 6 is a schematic structural view of a first portion of a flow dividing blade in the centrifugal impeller shown in fig. 1.

Reference numerals:

100. a centrifugal impeller; 10. a hub; 12. an inner bottom surface; 20. a wheel cover; 22. an inner top surface; 24. a drainage channel; 241. a drainage section; 243. a gas collection section; 26. an air inlet; 30. a main fan blade; 31. an upstream main fan blade; 312. an upstream suction surface; 314. an upstream pressure face; 33. a downstream main fan blade; 332. a downstream suction surface; 334. a downstream pressure surface; 40. shunting fan blades; 41. a diversion suction surface; 42. shunting a pressure surface; 43. a first part; 432. an injection channel; 4321. an air inlet section; 4323. an air outlet section; 434. a first leading edge; 436. a first trailing edge; 437. a first end face; 438. a second end face; 44. a second section; 441. an arc-shaped main body section; 443. a trailing edge segment; 45. a flow distribution channel; 50. an air duct; 52. an upstream sub-duct; 54. a downstream sub-duct; 60. and (4) a nozzle.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present application more comprehensible, embodiments accompanying the present application are described in detail below with reference to the accompanying drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. This application is capable of embodiments in many different forms than those described herein and that modifications may be made by one skilled in the art without departing from the spirit and scope of the application and it is therefore not intended to be limited to the specific embodiments disclosed below.

In the description of the present application, it is to be understood that the terms "central," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present application and to simplify the description, but are not intended to indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, and are not to be construed as limiting the present application.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present application, "plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In this application, unless expressly stated or limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can include, for example, fixed connections, removable connections, or integral parts; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as the case may be.

In this application, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through intervening media. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like as used herein are for illustrative purposes only and do not denote a unique embodiment.

Referring to fig. 1, the present application provides a compressor, which includes a motor and a centrifugal impeller 100, wherein the motor is in transmission connection with the centrifugal impeller 100, and the motor is used to drive the centrifugal impeller 100 to rotate, so that the centrifugal impeller 100 can convert its mechanical energy into pressure energy and kinetic energy of an air flow and provide power for the compressor.

Referring to fig. 2, fig. 3 and fig. 4, the centrifugal impeller 100 includes a hub 10, a shroud 20, a plurality of main blades 30 and at least one splitter blade 40, the hub 10 and the shroud 20 are used to support all the main blades 30 and all the splitter blades 40 together, and all the main blades 30 and all the splitter blades 40 are used to guide the airflow and compress the airflow. Specifically, the wheel cap 20 and the wheel hub 10 are disposed at intervals along the axial direction of the centrifugal impeller 100, and all the main blades 30 and all the split blades 40 are clamped between the wheel hub 10 and the wheel cap 20. All the main blades 30 are arranged in pairs along the rotation direction of the centrifugal impeller 100 (as indicated by the arc-shaped arrow a in fig. 2), and each pair of main blades 30, the shroud 20 and the hub 10 define a wind channel 50. Each of the flow dividing fan blades 40 is disposed in one of the air ducts 50, and divides the air duct 50 into two sub-air ducts sequentially arranged along the rotation direction of the centrifugal impeller 100, and each of the flow dividing fan blades 40 is provided with a flow dividing passage 45 communicated between the two sub-air ducts.

Specifically, the rotational direction of the centrifugal impeller 100 coincides with the circumferential direction of the centrifugal impeller 100. Any two adjacent main blades 30 arranged in the rotation direction of the centrifugal impeller 100 form a pair of main blades 30. Taking three main blades 30 as an example, which are respectively a first main blade, a second main blade and a third main blade, the first main blade, the second main blade and the third main blade are sequentially arranged along the rotation direction, the first main blade 30 and the second main blade 30 are arranged at intervals to form a pair of main blades 30, the second main blade 30 and the third main blade 30 are arranged at intervals to form a pair of main blades 30, and the third main blade 30 and the first main blade 30 are arranged at intervals to form a pair of main blades 30.

Referring to fig. 4, each pair of main blades 30 further includes an upstream main blade 31 and a downstream main blade 33, which are sequentially disposed at intervals along the rotation direction of the centrifugal impeller 100. The upstream main blade 31 and the downstream main blade 33 both extend to the outer peripheral surfaces of the shroud 20 and the hub 10 in the radial direction of the centrifugal impeller 100. The upstream main blade 31 and the downstream main blade 33 each have a suction surface and a pressure surface which are arranged to face each other in the rotation direction of the centrifugal impeller 100.

In each pair of main blades 30, the upstream main blade 31 of the pair is also the downstream main blade 33 of the previous pair of main blades 30, and the downstream main blade 33 of the pair is also the upstream main blade 31 of the next pair of main blades 30. The suction surface of the upstream main blade 31 is defined as an upstream suction surface 312, the pressure surface of the upstream main blade 31 is defined as an upstream pressure surface 314, the suction surface of the downstream main blade 33 is defined as a downstream suction surface 332, and the pressure surface of the downstream main blade 33 is defined as a downstream pressure surface 334. In each pair of main blades 30, the upstream suction surface 312 of the upstream main blade 31 is also a downstream suction surface 332 of the downstream main blade 33 in the previous pair of main blades 30, and the upstream pressure surface 314 of the upstream main blade 31 is also a downstream pressure surface 334 of the downstream main blade 33 in the previous pair of main blades 30. In each pair of main blades 30, the downstream suction surface 332 of the downstream main blade 33 is also the upstream suction surface 312 of the upstream main blade 31 in the next pair of main blades 30, and the downstream pressure surface 334 of the downstream main blade 33 is also the upstream pressure surface 314 of the upstream main blade 31 in the next pair of main blades 30.

Referring also to FIG. 5, the wheel cover 20 and the wheel hub 10 have an inner top surface 22 and an inner bottom surface 12, respectively, disposed opposite and facing each other. An air duct 50 is formed by the upstream pressure surface 314 and the downstream suction surface 332 of each pair of main blades 30, the inner top surface 22 and the inner bottom surface 12, the end surface of the upstream main blade 31 far away from the central axis of the centrifugal impeller 100, the end surface of the downstream main blade 33 far away from the central axis of the centrifugal impeller 100, the outer peripheral surface of the hub 10 and the outer peripheral surface of the wheel cover 20 together define an air outlet of the air duct 50. The wheel cover 20 is further provided with an air inlet 26 communicated with an air inlet of each air duct 50. When the centrifugal impeller 100 is in operation, external air flows into each air duct 50 through the air inlet 26, and flows out of the air outlet of each air duct 50 to the outside (as indicated by arrows e-f-g-h in fig. 5 or as indicated by arrows j-k-m in fig. 5) after passing through each air duct 50 in the radial direction of the centrifugal impeller 100.

Referring to fig. 3 and 4 again, each of the split-flow blades 40 is disposed in one air duct 50, and divides the air duct 50 into two sub-air ducts, which are sequentially disposed along the rotation direction of the centrifugal impeller 100 and respectively form an upstream sub-air duct 52 and a downstream sub-air duct 54. Specifically, each of the flow-dividing fan blades 40 also has a suction surface and a pressure surface which are sequentially arranged in the rotation direction of the centrifugal impeller 100. The suction surface of each shunting fan blade 40 is defined as a shunting suction surface 41, the pressure surface of each shunting fan blade 40 is defined as a shunting pressure surface 42, an upstream pressure surface 314, the shunting suction surface 41, the inner top surface 22 and the inner bottom surface 12 are defined to enclose an upstream sub-air channel 52, and the shunting pressure surface 42, the downstream suction surface 332, the inner top surface 22 and the inner bottom surface 12 are defined to enclose a downstream sub-air channel 54. The branch passage 45 communicates between the upstream sub-duct 52 and the downstream sub-duct 54. In addition, each of the flow dividing fan blades 40 further has a first end surface 437 and a second end surface 438 which are oppositely arranged along the axial direction of the centrifugal impeller 100, and the first end surface 437 and the second end surface 438 are respectively arranged adjacent to the upstream pressure surface 314 and the flow dividing suction surface 41. When each of the fan blades 40 is disposed in one of the wind channels 50, the first end surface 437 is attached to the inner top surface 22 of the wheel cover, and the second end surface 438 is attached to the inner bottom surface 12 of the wheel hub 10.

In operation of centrifugal impeller 100, upstream pressure surface 314, diverging pressure surface 42, and downstream pressure surface 334 are used to compress air. Thus, the pressure at the upstream pressure surface 314 is greater than the pressure at the upstream suction surface 312, the pressure at the divergent pressure surface 42 is greater than the pressure at the divergent suction surface 41, and the pressure at the downstream pressure surface 334 is greater than the pressure at the downstream suction surface 332.

In the conventional centrifugal impeller 100, wind loss is large due to the presence of the boundary layer. The boundary layer refers to a thin airflow layer closely attached to an object plane (for example, the surface of the main blade 30, the surface of the shunting blade 40, the surface of the hub 10, the surface of the shroud 20, and the like). In the boundary layer, due to the action of molecular attraction, the airflow is completely adhered to the object surface, and the relative flow velocity with the object is zero. Therefore, the air flow at the boundary layer cannot be effectively output by the centrifugal impeller 100, and the air flow velocity at the boundary layer is smaller than the air flow velocity at other positions inside the centrifugal impeller 100, so that the wind loss is increased, and the energy transfer efficiency is reduced. In addition, the larger the surface area of the blades in the centrifugal impeller 100, the larger the area of the boundary layer formed. Based on the positive correlation between the area of the boundary layer and the surface area of the blades, if the total area of the blades is reduced by directly reducing the number of the blades, although the formation of the boundary layer can be reduced, the space defined by the hub 10 and the shroud 20 of the centrifugal impeller 100 is relatively hollow. Thus, the air flow between the hub 10 and the shroud 20 is liable to form vortex and swirl between the hub 10 and the shroud 20, which also results in increased wind loss. Therefore, how to reduce the boundary layer without reducing the number of the blades becomes a problem to be solved urgently.

Returning to the present application, all the main blades 30 and all the splitter blades 40 are combined to form blades of the entire centrifugal impeller 100, and the number of the blades in the present application is substantially the same as or equal to that of the blades in the prior art, so as to prevent the space between the hub 10 and the shroud 20 from being too hollow to form vortex and convolution. When the centrifugal impeller 100 works, based on the principle of air pressure balance, in the pair of main blades 30 provided with the split blades 40, the air flow on the upstream pressure surface 314 flows to the split suction surface 41 at a high speed through the upstream sub-air ducts 52, and impacts the boundary layer at the split suction surface 41, resulting in loss of the boundary layer at the split suction surface 41. Further, due to the arrangement of the diversion channel 45, the air flow flowing into the diversion suction surface 41 can also flow into the downstream sub-air ducts 54 through the diversion channel 45 (as indicated by the straight arrow d in fig. 4) and impact the boundary layer at the diversion pressure surface 42, and the air flow can also flow to the downstream suction surface 332 through the downstream sub-air ducts 54 to impact the boundary layer at the downstream suction surface 332. Thus, in summary, losses occur in the boundary layer at the split suction surface 41, the boundary layer at the split pressure surface 42, and the boundary layer at the downstream suction surface 332. The more the boundary layer is lost, the less the wind loss of the boundary layer is in the entire centrifugal impeller 100, and the air flow of the lost boundary layer can be output and work is done, thereby contributing to the improvement of the energy transfer efficiency of the centrifugal impeller 100.

It should be noted that, in the present application, the splitter blade 40 not only serves to guide the airflow from the upstream pressure surface 314 to the downstream sub-air duct 54 through the upstream sub-air duct 52, but also has the same function of compressing the airflow and applying work to the airflow as the main blade 30.

Preferably, there are a plurality of flow dividing fan blades 40, all the air ducts 50 correspond to all the flow dividing fan blades 40 one by one, and each flow dividing fan blade 40 is disposed in one air duct 50 corresponding to the flow dividing fan blade. That is, a split-flow fan blade 40 is disposed between each pair of main fan blades 30. Therefore, the boundary layers from the flow-dividing suction surface 41 of each flow-dividing fan blade 40, the flow-dividing pressure surface 42 of each flow-dividing fan blade 40, and the downstream suction surface 332 of each pair of main fan blades 30 can be lost in the process of operating the centrifugal impeller 100, thereby contributing to further improving the energy transfer efficiency of the centrifugal impeller 100. It should be noted that, the more the number of the shunting blades 40 is, the more the number of the main blades 30 should be adaptively reduced, so that the sum of the numbers of the main blades 30 and the shunting blades 40 is kept unchanged.

Of course, in some other embodiments, due to the arrangement of the flow dividing channel 45 on the flow dividing fan blade 40, the centrifugal impeller 100 has higher energy transfer efficiency, and therefore, the sum of the main fan blade 30 and the flow dividing fan blade 40 can also be increased adaptively.

Further, each of the flow dividing fan blades 40 includes a first portion 43 and a second portion 44, and in an airflow outflow direction (as indicated by an arrow b or an arrow c in fig. 4) in the air duct 50 where each of the flow dividing fan blades 40 is located, the first portion 43 and the second portion 44 of each of the flow dividing fan blades 40 are disposed at an interval and define a flow dividing channel 45. That is, in each flow dividing fan blade 40, the first portion 43 is located upstream of the second portion 44, and the first portion 43 and the second portion 44 define a flow dividing channel 45. Compared with a mode of directly forming the flow dividing channel 45 on each flow dividing fan blade 40, the method for forming the flow dividing channel 45 by dividing the flow dividing fan blade 40 into the two disconnected first parts 43 and second parts 44 can reduce the difficulty in forming the flow dividing channel 45. In addition, in this arrangement, the flow dividing channel 45 can extend to both ends of the flow dividing fan blade 40 along the height direction of the flow dividing fan blade 40 (i.e., the axial direction of the centrifugal impeller 100). Therefore, the size of the flow dividing channel 45 is larger, so that the resistance to the air flow is smaller, and the energy transfer efficiency of the centrifugal impeller 100 can be further improved.

Referring to fig. 6, further, each first portion 43 is provided with a spraying channel 432, an air inlet of the spraying channel 432 is communicated with the corresponding air duct 50, and an air outlet of the spraying channel 432 faces the suction surface of the downstream main blade 33 corresponding thereto. Specifically, the air inlet of the injection channel 432 may be communicated with the upstream sub-air channel 52 or the downstream sub-air channel 54 in the air channel 50 where the injection channel 432 is located, and it is only required to ensure that the air flow in the air channel 50 where the injection channel 432 is located can flow in from the air inlet of the injection channel 432 and is ejected to the suction surface of the downstream main blade 33 through the air outlet of the injection channel 432. As can be understood, by arranging the air outlet of the injection channel 432 facing the corresponding suction surface of the downstream main blade 33, it can be ensured that a boundary layer loss can occur at the suction surface of the downstream main blade 33, and the loss degree is greater, thereby contributing to further improving the energy transfer efficiency of the centrifugal impeller 100.

Further, the air inlet aperture of each injection channel 432 is larger than the air outlet aperture thereof. On the premise of constant flow, the smaller the aperture of the fluid, the larger the flow velocity. Since the aperture of the air inlet of the injection channel 432 is larger than the aperture of the air outlet thereof, the flow rate of the air flow flowing in from the air inlet of the injection channel 432 is smaller than the flow rate of the air flow flowing out from the air outlet of the injection channel 432. That is, the airflow can be accelerated by the air outlet of the injection channel 432 and then injected to the suction surface of the downstream main fan blade 33. As such, the impact of the air flow on the boundary layer is greater, thereby contributing to the increased loss of the boundary layer, resulting in a higher energy transfer efficiency of the centrifugal impeller 100.

Preferably, each injection channel 432 has an air inlet section 4321 and an air outlet section 4323, an air inlet of the air inlet section 4321 is communicated with the air duct 50, an air outlet of the air outlet section 4323 faces a suction surface of the downstream main fan blade 33, and a diameter of the air inlet section 4321 is greater than a diameter of the air outlet section 4323. Therefore, the airflow can be accelerated by the air outlet section 4323 and then sprayed to the suction surface of the downstream main fan blade 33. Generally, the air outlet section 4323 has a certain length, and the air flow accelerated by the air outlet section 4323 has a higher flow velocity. Thus, the impact of the air flow on the boundary layer can be further increased.

In some embodiments, the air outlet section 4323 may be a single section, and in other embodiments, the air outlet section 4323 may be multiple sections, and all the air outlet sections 4323 are communicated with the air inlet section 4321. Therefore, the air flow in the air inlet section 4321 is divided and flows out through each air outlet section 4323. Specifically, the air outlets of the different air outlet sections 4323 correspond to different positions on the suction surface of the downstream main blade 33. By arranging the multi-section air outlet section 4323, the injection channel 432 can blow air to different positions of the suction surface of the downstream main fan blade 33, so that the loss of the boundary layer at the suction surface of the downstream main fan blade 33 can be improved.

Preferably, in the same splitter blade, the number of the outlet segments 4323 of the injection channel 432 is between 4 and 8, and the strength of the first portion 43 is affected by the excessive number of the outlet segments 4323 of the injection channel 432.

In other embodiments, to ensure the spraying effect, a nozzle 60 may be further disposed at the air outlet of each air outlet section 4323. The number of the nozzles 60 is the same as that of the air outlet sections 4323, and the nozzles correspond to the air outlet sections one by one. To facilitate the provision of the injection channel 432 in the first portion 43, the thickness of the first portion 43 should be relatively thick.

Referring to fig. 4 and fig. 5 again, in some embodiments, the wheel cover 20 is provided with a plurality of flow guide channels 24, and all the flow guide channels 24 correspond to all the flow dividing fan blades 40 one to one. Each first portion 43 includes a first leading edge 434 and a first trailing edge 436 which are sequentially arranged and connected along the outflow direction of the air flow in the air duct 50, the first leading edge 434 is arranged close to the central axis of the centrifugal impeller 100, the first trailing edge 436 and the second portion 44 corresponding to the first trailing edge 436 define a diversion channel 45, and each diversion channel 24 is used for guiding the air flow at the position of the first trailing edge 436 corresponding to the diversion channel 24 to the air inlet of the injection channel 432 corresponding to the diversion channel.

It will be appreciated that within each air duct 50, the direction of flow of the air is substantially the same as the radial direction of the centrifugal impeller 100. And in the process of the air flow flowing out, the farther the distance from the central axis of the centrifugal impeller 100 is, the faster the flow velocity of the air flow is due to the centrifugal force. That is, the flow rate of the airflow at the location of the first leading edge 434 is less than the flow rate of the airflow at the location of the first trailing edge 436. Therefore, each flow guiding channel 24 guides the airflow at the position of the corresponding first trailing edge 436 into the corresponding spraying channel 432, so that the flow speed of the airflow sprayed out from the spraying channel 432 is higher, and the loss of the boundary layer on the downstream main fan blade 33 can be effectively increased.

Of course, in other embodiments, each diversion channel 24 can be disposed on the shroud 20 and configured to direct the airflow at the location of its corresponding first leading edge 434 to the inlet of its corresponding ejection channel 432. Alternatively, in some other embodiments, each flow guiding channel 24 may be directly disposed on the corresponding flow dividing fan blade 40, and guides the airflow at the position of the corresponding first leading edge 434 or first trailing edge 436 to the air inlet of the corresponding spraying channel 432.

Preferably, each flow guiding channel 24 further includes a flow guiding section 241 and a gas collecting section 243, and the gas collecting section 243 of each flow guiding channel 24 is communicated between the flow guiding section 241 and the injection channel 432 corresponding thereto. Each flow guiding section 241 is used for guiding the airflow in the corresponding air duct 50 to the air collecting section 243 (as indicated by an arrow n in fig. 5), and the air collecting section 243 is used for collecting air, so that the airflow can be concentrated to have a larger pressure in the air collecting section 243 and then flows to the injection channel 432. When the air flow with a larger pressure flows out from the injection channel 432, the air pressure is also larger, and the impact effect on the downstream main fan blade 33 is stronger, so that the boundary layer is easier to be lost.

It is worth mentioning that, in order to ensure that there is only a small air flow inflow guiding section 241 in each air duct 50, the diameter of the guiding channel 24 can be set smaller (the air flow inflow can be reduced by increasing the resistance of the air flow inflow). To reduce the resistance of the air flow from the air collecting section 243 to the injection channel 432, the apertures of the air collecting section 243 and the air intake section 4321 may be set to be the same.

In some embodiments, each second portion 44 includes an arc-shaped main body section 441 and a trailing edge section 443, which are sequentially arranged and connected in the airflow outflow direction in the wind tunnel 50, the arc-shaped main body section 441 and the first portion 43 corresponding to the second portion 44 define the flow dividing channel 45, the arc degree of the arc-shaped main body section 441 is greater than that of the first portion 43, and the trailing edge section 443 extends in the radial direction of the centrifugal impeller 100. Specifically, the resistance suffered by the airflow is small in the process of flowing under the guidance of the fan blades with slightly large radian. Since the arc-shaped main body segment 441 is farther from the central axis of the centrifugal impeller 100 than the first portion 43, the flow velocity of the air flow at the position of the arc-shaped main body segment 441 is greater than the flow velocity of the air flow at the position of the first portion 43 by the centrifugal force. By providing the arc of the arc-shaped main body section 441 to be greater than the arc of the first portion 43, the air flow in the air duct 50 is facilitated to be discharged in the radial direction of the centrifugal impeller 100.

By providing the trailing edge section 443, and extending the trailing edge section 443 in the radial direction of the centrifugal impeller 100, the airflow can flow out in the radial direction of the centrifugal impeller 100 under the guidance of the trailing edge section 443 when flowing into the position where the airflow contacts the trailing edge section 443. According to the principle that the straight line between two points is shortest, since the trailing edge section 443 extends along the radial direction of the centrifugal impeller 100, the airflow has the shortest outflow path, so that the loss in the flowing process of the airflow is also the smallest, the stronger the work capacity of the airflow flowing out to the outside is, and the higher the energy transfer efficiency is.

Specifically, the second portion 44 mainly performs the function of performing work, and the trailing edge section 443 of the second portion 44 is too thick to easily generate the trailing loss, so that the thickness of the trailing edge section 443 is set to be as thin as possible, and is less than or equal to 3 mm.

In some embodiments, a projection of each of the flow dividing fan blades 40 in a plane in which the air inlet 26 is located outside the air inlet 26. Therefore, the area of the air inlet 26 shielded by the shunting fan blades 40 is also small, so as to prevent the air inlet 26 from being blocked, and enable external air flow to flow into each air duct 50 more smoothly.

Preferably, in the radial direction of the centrifugal impeller 100, the boundary line between each of the flow-dividing fan blades 40 and the air inlet 26 is arranged at an interval, and the interval between each of the flow-dividing fan blades 40 and the boundary line between each of the flow-dividing fan blades 26 is within a range of 20% to 30% of the total arc length of any one of the main fan blades 30.

The centrifugal impeller 100, the compressor and the refrigeration equipment include, in each pair of main blades 30, an upstream main blade 31 located in the rotation direction of the centrifugal impeller 100 and a downstream main blade 33 located in the rotation direction of the centrifugal impeller 100. When the centrifugal impeller 100 works, the pressure surface of the upstream main blade 31 and the suction surface of the downstream main blade 33 are both arranged towards the air duct 50, and the air pressure of the pressure surface of the upstream main blade 31 is greater than that of the suction surface of the downstream main blade 33. Because the flow dividing channel 45 is formed in the flow dividing fan blade 40, based on the air pressure balance principle, the air flow on the pressure surface of the upstream main fan blade 31 is blown to the suction surface of the downstream main fan blade 33 through the flow dividing channel 45, so that the loss of the boundary layer on the suction surface of the downstream main fan blade 33 is caused, and further, the wind loss of the boundary layer can be reduced, thereby having higher energy transfer efficiency.

The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.

The above-mentioned embodiments only express several embodiments of the present application, and the description thereof is more specific and detailed, but not construed as limiting the claims. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the concept of the present application, which falls within the scope of protection of the present application. Therefore, the protection scope of the present patent shall be subject to the appended claims.

Claims (11)

1. A centrifugal impeller (100), the centrifugal impeller (100) comprising:

a hub (10);

a shroud (20) spaced from the hub (10) in an axial direction of the centrifugal impeller (100);

the main blades (30) are clamped between the hub (10) and the wheel cover (20) and are arranged in pairs along the rotating direction of the centrifugal impeller (100), and each pair of main blades (30), the wheel cover (20) and the hub (10) define an air channel (50); and

each shunting fan blade (40) is arranged in one air duct (50) and divides the air duct (50) into two sub air ducts which are sequentially distributed along the rotation direction of the centrifugal impeller (100), and each shunting fan blade (40) is provided with a shunting channel (45) communicated between the two sub air ducts.

2. The centrifugal impeller (100) of claim 1, wherein the number of the flow-dividing fan blades (40) is multiple, all the air channels (50) correspond to all the flow-dividing fan blades (40) one by one, and each flow-dividing fan blade (40) is arranged in one of the air channels (50) corresponding to the flow-dividing fan blade.

3. The centrifugal impeller (100) according to claim 2, wherein each of the flow dividing blades (40) comprises a first portion (43) and a second portion (44), and in an airflow outflow direction in the air duct (50) in which each of the flow dividing blades (40) is located, the first portion (43) and the second portion (44) of each of the flow dividing blades (40) are spaced apart from each other and define one of the flow dividing channels (45).

4. The centrifugal impeller (100) according to claim 3, wherein each pair of main blades (30) comprises a downstream main blade (33) located downstream in the direction of rotation of the centrifugal impeller (100);

each first portion (43) is provided with a spraying channel (432), an air inlet of each spraying channel (432) is communicated with the corresponding air channel (50), and an air outlet of each spraying channel (432) faces to a suction surface of the corresponding downstream main fan blade (33).

5. The centrifugal impeller (100) of claim 4, wherein each injection channel (432) has an air inlet aperture that is larger than its air outlet aperture.

6. The centrifugal impeller (100) of claim 4, wherein a plurality of flow guide channels (24) are formed in the impeller cover (20), and all the flow guide channels (24) correspond to all the flow dividing fan blades (40) one by one;

each first portion (43) comprises a first trailing edge (436), and each flow-directing channel (24) is used for directing the air flow at the position of the first trailing edge (436) corresponding to the flow-directing channel to the air inlet of the spraying channel (432) corresponding to the flow-directing channel.

7. The centrifugal impeller (100) of claim 3, wherein each of the second portions (44) comprises an arcuate body section (441) defining the flow dividing channel (45) with the first portion (43) corresponding thereto, the arc of the arcuate body section (441) being greater than the arc of the first portion (43).

8. The centrifugal impeller (100) of claim 7, wherein each second portion (44) further comprises a trailing edge section (443) arranged and connected in series with the curved main body section (441) in the air flow outflow direction of the air channel (50) in which it is located, the trailing edge section (443) extending in the radial direction of the centrifugal impeller (100).

9. The centrifugal impeller (100) of claim 1, wherein the shroud (20) is provided with an air inlet (26) communicated with each air duct (50), and a projection of each flow dividing fan blade (40) in a plane where the air inlet (26) is located outside the air inlet (26).

10. A compressor, characterized by comprising a centrifugal impeller (100) according to any one of claims 1 to 9.

11. A refrigerating apparatus comprising a compressor as claimed in claim 10.

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