CN218266484U - Impeller and centrifugal fan with same - Google Patents
Impeller and centrifugal fan with same Download PDFInfo
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- CN218266484U CN218266484U CN202222248212.4U CN202222248212U CN218266484U CN 218266484 U CN218266484 U CN 218266484U CN 202222248212 U CN202222248212 U CN 202222248212U CN 218266484 U CN218266484 U CN 218266484U
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Abstract
The utility model provides an impeller and have its centrifugal fan, belong to centrifugal fan technical field, the impeller includes front bezel, middle disc, back plate, a plurality of blades and wheel hub, wherein, the middle disc is located between front bezel and the back plate, the blade passes the middle disc, one end of blade is connected to the front bezel and the other end is connected between the back plate, the wheel hub is installed in the inner periphery of middle disc, and a plurality of blades are evenly distributed along the periphery of wheel hub, have the runner that is used for the fluid to flow through between two adjacent blades; the blade comprises a suction surface and a pressure surface which are opposite, the suction surface comprises a bulge, the pressure surface comprises a groove, the height of the bulge and the groove depth of the groove are 0-0.4 times of the width of the corresponding flow channel, and the depth of the groove is smaller than the thickness of the blade. The utility model discloses can improve the fluid flow homogeneity, reduce aerodynamic noise.
Description
Technical Field
The utility model relates to a centrifugal fan technical field, in particular to impeller and have its centrifugal fan.
Background
With the popularization of the range hood, consumers can accept the range hood with large air volume and operation noise more easily. For the internal noise of the range hood, the internal noise can be generally divided into two categories of shell structure vibration noise and aerodynamic noise. The centrifugal fan is an important component of the range hood, particularly the surface of the traditional fan blade is smooth, and a large amount of vortex is generated inside the impeller flow passage. The generation and collapse of vortices in the impeller flow channel is one of the main sources of aerodynamic noise.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide an impeller, through set up on the blade protruding with the recess can improve the fluid flow homogeneity, reduces pneumatic noise.
The utility model aims at providing a centrifugal fan.
For realizing the purpose of the utility model, the utility model adopts the following technical scheme:
according to an aspect of the utility model, an impeller is provided for centrifugal fan. The impeller includes:
the central disc is positioned between the front disc and the rear disc;
the blades penetrate through the middle disc, one end of each blade is connected to the front disc, the other end of each blade is connected between the rear discs, and a flow passage for fluid to flow through is formed between every two adjacent blades;
the hub is arranged on the inner periphery of the middle disc, and the blades are uniformly distributed along the outer periphery of the hub;
the blade comprises a suction surface and a pressure surface which are opposite, the suction surface comprises a bulge for improving the uniformity of fluid flow, the pressure surface comprises a groove for improving the uniformity of fluid flow, the height of the bulge and the groove depth of the groove are 0-0.4 times of the width of a corresponding flow channel, and the depth of the groove is smaller than the thickness of the blade.
According to an embodiment of the present invention, the number of the protrusions is a plurality, wherein the plurality of protrusions are distributed in an array to form a protrusion array for mixing the flow of the fluid on the boundary layer of the suction surface to reduce the broadband noise;
the pressure surface is provided with a plurality of grooves, wherein the grooves are distributed in an array manner to form a groove array, and the grooves are used for forming vortex, so that the boundary layer of the pressure surface is transited in advance, and the flow uniformity is improved.
According to an embodiment of the present invention, the longitudinal section of the protrusion and the longitudinal section of the groove are respectively one of an arc shape, a V shape, an inverted U shape, and a quadratic curve;
the protrusion array comprises protrusions with one or more of arc-shaped, V-shaped, inverted U-shaped and quadratic curves in longitudinal section, and the groove array comprises grooves with one or more of arc-shaped, V-shaped, inverted U-shaped and quadratic curves in longitudinal section.
According to an embodiment of the present invention, wherein the number of the blades is Z, wherein Z is greater than or equal to 30 and less than or equal to 100.
According to an embodiment of the present invention, the cross section of the blade is circular arc;
the inner diameter of the impeller is R 1 The outer diameter of the impeller is R 2 Wherein R is not less than 0.7 1 /R 2 ≤0.9。
According to the utility model discloses an embodiment, wherein, follow the import of blade is to the export direction, will the N that the runner is evenly divided into is regional, wherein, the entrance point of blade the width of runner is W 1 The width of the flow passage at the outlet end of the blade is W N The width of the flow channel corresponding to the bulge is W i The thickness of the blade is delta, and the height of the bulge is h 1 The depth of the groove is h 2 Wherein h is 1 ∈[0～0.4W i )，h 2 ∈[0～0.4W i ) And h is 2 <δ, formula i =1,2, \8230;, N.
According to an embodiment of the present invention, wherein 0.3 delta < d i ＜0.2W i Wherein W is i >1.5δ。
According to an embodiment of the present invention, wherein d i ＝(N+1-i)*(W 1 –W N ) N, and d i ＝min[(N+1-i)*(W 1 –W N )/N，0.4W i ]In the formula: d i Is the height of the protrusion (411) of the i-th area or the groove depth of the groove (421).
According to the utility model discloses an embodiment, wherein, there is the biggest runner district in the middle part of runner (40), the import of runner (40) arrives regional first runner district that is between the biggest runner district, the export in the biggest runner district arrives regional second runner district that is between runner (40), the width in the biggest runner district is W max The height of the protrusion (411) or the groove depth of the groove (421) at the maximum flow passage area is d max The height of the protrusion (411) or the groove depth of the groove (421) in the first flow channel area is d p The height of the protrusion (411) or the groove depth of the groove (421) in the second flow channel region is d q Wherein, in the step (A),
W max >W 1 ，W max >W N ；
d max ＝min[|(W 2 -W 1 )|，0.4W max ]；
d p ＝(M+1-p)*|(W N -W 1 ) I/M, and d p ＝min[(M+1-i)*|(W N -W 1 )|/M，0.4W i ]；
d q ＝(M+1-p)*|(W N -W 1 ) I/F, and d q ＝min[(F+1-q)*|(W N -W 1 )|/F，0.4W i ]；
In the formula, M is the number of areas which averagely divide the first runner area along the direction from the inlet of the runner (40) to the maximum runner area;
f is the number of areas into which the second flow channel area is divided equally in the direction from the maximum flow channel area to the outlet of the flow channel (40);
p =1,2, \ 8230, M is more than or equal to 1;
q =1,2, \8230:, F, and F is more than or equal to 1.
According to the utility model discloses a centrifugal fan is provided in another aspect, this centrifugal fan includes foretell impeller, spiral case, motor, wherein, the motor the impeller all set up in the spiral case, impeller connect in the output of motor, be used for the drive the rotation of impeller.
The utility model provides an embodiment has following advantage or beneficial effect:
the utility model discloses an impeller and have its centrifugal fan, through set up on the blade protruding with the recess to improve the fluid flow homogeneity, reduce aerodynamic noise.
Through setting up bellied height with the groove depth of recess to improve fan flow state, reduce wide band noise, improve centrifugal fan's performance.
Drawings
The above and other features and advantages of the present invention will become more apparent by describing in detail exemplary embodiments thereof with reference to the attached drawings.
FIG. 1 is a schematic view of an impeller shown according to an exemplary embodiment.
Fig. 2 is an exploded view of an impeller shown according to an exemplary embodiment.
FIG. 3 is a schematic illustration of the attachment of a suction surface shown in accordance with an exemplary embodiment.
FIG. 4 is a schematic diagram of a pressure surface shown in accordance with an exemplary embodiment.
FIG. 5 is a cross-sectional view of an impeller shown according to an exemplary embodiment.
Fig. 6 is an enlarged view at E in fig. 5.
FIG. 7 is a schematic view of adjacent blades shown according to an exemplary embodiment.
Wherein the reference numerals are as follows:
1. a front plate; 2. a middle disc; 3. a rear disc; 4. a blade; 40 flow passages; 41. a suction surface; 411. a protrusion; 42. a pressure surface; 421. a groove; 5. a hub; 6. and (4) an aluminum piece.
Detailed Description
Example embodiments will now be described more fully with reference to the accompanying drawings. Example embodiments may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of example embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and thus their detailed description will be omitted.
The terms "a," "an," "the," "said" are used to indicate the presence of one or more elements/components/etc.; the terms "comprising" and "having" are intended to be inclusive and mean that there may be additional elements/components/etc. other than the listed elements/components/etc.
As shown in fig. 1 to 7, fig. 1 shows a schematic view of an impeller provided by the present invention. Fig. 2 shows an exploded view of the impeller provided by the present invention. Fig. 3 shows a schematic connection diagram of the suction surface 41 provided by the present invention. Fig. 4 shows a schematic view of a pressure surface 42 provided by the present invention. Fig. 5 shows a cross-sectional view of an impeller provided by the present invention. Fig. 6 is an enlarged view at E in fig. 5. Fig. 7 shows a schematic view of an adjacent blade 4 provided by the present invention.
The utility model discloses an impeller for centrifugal fan, this impeller includes:
the device comprises a front disc 1, a middle disc 2 and a rear disc 3, wherein the middle disc 2 is positioned between the front disc 1 and the rear disc 3;
a plurality of blades 4 penetrating the middle disc 2, one end of each blade being connected to the front disc 1 and the other end of each blade being connected between the rear discs 3, wherein a flow passage 40 for fluid to flow through is formed between two adjacent blades 4;
the hub 5 is arranged on the inner periphery of the middle disc, and the blades 4 are uniformly distributed along the outer periphery of the hub 5;
the blade 4 comprises a suction surface 41 and a pressure surface 42 which are opposite, the suction surface 41 comprises a protrusion 411 for improving the uniformity of fluid flow, the pressure surface 42 comprises a groove 421 for improving the uniformity of fluid flow, the height of the protrusion 411 and the depth of the groove 421 are both 0-0.4 times of the width of the corresponding flow channel, and the depth of the groove 421 is smaller than the thickness of the blade 4.
Wherein, the front bezel 1, well dish 2 and back plate 3 are parallel to each other, the both ends of blade 4 are provided with respectively and set up the turn-ups, in order to connect front bezel 1 and back plate 3, and a plurality of blades 4 are along wheel hub 5's periphery evenly distributed, wheel hub 5 is installed in the interior week of well dish 2, wheel hub 5 and well dish 2 can adopt integrated into one piece's manufacturing, furthermore, the impeller still includes aluminium spare 6, aluminium spare 6 passes through the rivet and is connected with wheel hub 5, the through-hole has been seted up at the center of aluminium spare 6, an output for connecting the motor, the motor can drive wheel hub 5 and wheel hub 5's periphery blade 4 rotate and then drive the rotation of air current like this, realize discharging fume. In this embodiment, the front disc 1, the middle disc 2, the rear disc 3, the hub 5, and the aluminum member 6 are all the prior art, and the structure and the connection mode thereof are not described in detail herein.
The suction surface 41 of the blade 4 is provided with the protrusion 411, the pressure surface 42 of the blade 4 is provided with the groove 421, the fluid is used for correspondingly mixing the fluid in the boundary layer in a flowing manner, large-scale vortex generated when the fluid passes through an irregular flow channel is damaged, the flowing uniformity of the fluid is improved, particularly, when the height of the protrusion 411 and the groove depth of the groove 421 are 0-0.4 times of the width of the corresponding flow channel, and the depth of the groove 421 is smaller than the thickness of the blade 4, the fluid can be reduced, and the pneumatic noise can be effectively improved. In this embodiment, the height of the protrusion 411 is the height from the highest point of the protrusion 411 to the suction surface 41.
In a preferred embodiment of the present invention, the protrusion 411 is plural, wherein the plural protrusions 411 are distributed in an array to form a protrusion array for mixing the flow of the fluid on the boundary layer of the suction surface 11 to reduce the broadband noise;
the grooves 421 are multiple, wherein the grooves 421 are distributed in an array to form a groove array, and the grooves 421 are used for forming a vortex, so that a boundary layer of the pressure surface 12 is transited in advance, and the flow uniformity is improved.
In a preferred embodiment of the present invention, the longitudinal section of the protrusion 411 and the longitudinal section of the groove 421 are respectively one of an arc shape, a V shape, an inverted U shape, and a quadratic curve;
the protrusion array comprises protrusions 411 with one or more of arc-shaped, V-shaped, inverted U-shaped and conic sections in longitudinal section, and the groove array comprises grooves 421 with one or more of arc-shaped, V-shaped, inverted U-shaped and conic sections in longitudinal section.
As shown in fig. 3-4, a plurality of protrusions 411 can form a protrusion array with equal or unequal row spacing on the suction surface 41 of the blade 4, and a plurality of grooves 412 can form a groove array with equal or unequal row spacing on the pressure surface 42 of the blade 4, wherein the protrusions 411 and the grooves 412 on the same cross section of the blade 4 can be in one-to-one correspondence with each other up and down, or can be staggered, and when the thickness of the blade 4 is less than 1.5mm, the protrusions 411 and the grooves 412 can be in one-to-one correspondence, so as to facilitate the processing of the blade 4. In addition, the longitudinal section of protrusion 411 and the longitudinal section of recess 421 are arc, V type, type of falling U, quadratic curve, and wherein, this row of recess can make and form the vortex structure in the inslot when flowing through recess 411, is favorable to improving the turbulent kinetic energy level of boundary layer for the boundary layer takes place to transition in advance, is favorable to destroying the large scale swirl structure that the fan coming flow produced when irregular runner, improves the flow uniformity.
Meanwhile, the bulge array can generate the effect of a vortex generator, and after the flows in the boundary layer are mixed, the energy is transferred to the boundary layer fluid in the inverse pressure gradient, so that the boundary layer fluid can be continuously attached to the surface of the blade after obtaining additional energy without flow separation, thereby improving the flow state of the fan, reducing broadband noise and improving the performance of the centrifugal fan.
In a preferred embodiment of the present invention, the number of blades 4 is Z, wherein Z is greater than or equal to 30 and less than or equal to 100;
the cross section of the blade 4 is arc-shaped; the inner diameter of the impeller is R 1 The outer diameter of the impeller is R 2 Wherein R is more than or equal to 0.7 1 /R 2 ≤0.9。
As shown in FIGS. 1-6, the cross section of the blade 4 is circular arc, and may be a quadratic curve or other curves, in this embodiment, the cross section of the blade 4 is circular arc, and when the number of the blades 4 is 30-100, R is greater than or equal to 0.7 ≦ R 1 /R 2 Less than or equal to 0.9, can carry out certain disturbance to the air current on boundary layer, improve fluidic runner homogeneity, reduce the flow separation of air current, prevent to produce the vortex between adjacent blade to improve the air performance of impeller, reduce aerodynamic noise, thereby promote centrifugal fan's aerodynamic performance. The cross section in this embodiment refers to a section of the blade 4 parallel to the front disk 1.
In a preferred embodiment of the present invention, the flow channel 40 is divided into N regions in the direction from the inlet to the outlet of the vane 4, wherein the width of the flow channel 40 at the inlet end of the vane 4 is W 1 The width of the flow passage 40 at the outlet end of the vane 4 is W N The width of the flow channel 40 corresponding to the protrusion 411 is W i The thickness of the blade 1 is delta and the height of the protrusion 411 is h 1 The depth of the groove 421 is h 2 Wherein h is 1 ∈[0～0.4W i )，h 2 ∈[0～0.4W i ) And h is 2 <δ, wherein i =1,2, \8230, N.
As shown in fig. 1 to 7, the flow channel 40 is equally divided into N regions, and the width of the flow channel in the region corresponding to the protrusion 411 or the groove 421 is W i In order to avoid the protrusion 411 blocking the flow channel 40 or the groove 421 affecting the flow channel of the fluid, the present embodiment finds that the height of the protrusion 411 is h 1 The depth of the groove 421 is h 2 Wherein the height h of the protrusion 411 1 ∈[0～0.4W i )，h 2 ∈[0～0.4W i ) And h is 2 <δ, in the formula, i =1,2, \8230;, N.
In a preferred embodiment of the invention, according to an embodiment of the invention, wherein 0.3 δ < >d i ＜0.2W i Wherein W is i >1.5δ。
Wherein, d i ＝(N+1-i)*(W 1 –W N ) N, and d i ＝min[(N+1-i)*(W 1 –W N )/N，0.4W i ]In the formula: d i Is the height of the protrusion (411) of the i-th area or the groove depth of the groove (421).
The middle part of the runner (40) is provided with a maximum runner area, the area from the inlet of the runner (40) to the maximum runner area is a first runner area, the area from the outlet of the maximum runner area to the runner (40) is a second runner area, and the width of the maximum runner area is W max The height of the protrusion (411) or the groove depth of the groove (421) at the maximum flow passage area is d max The height of the protrusion (411) or the groove depth of the groove (421) in the first flow channel area is d p The height of the protrusion (411) or the groove depth of the groove (421) in the second flow channel region is d q Wherein, in the process,
W max >W 1 ，W max >W N ；
d max ＝min[|(W 2 -W 1 )|，0.4W max ]；
d p ＝(M+1-p)*|(W N -W 1 ) I/M, and d p ＝min[(M+1-i)*|(W N -W 1 )|/M，0.4W i ]；
d q ＝(M+1-p)*|(W N -W 1 ) I/F, and d q ＝min[(F+1-q)*|(W N -W 1 )|/F，0.4W i ]；
In the formula, M is the number of areas which averagely divide the first runner area along the direction from the inlet of the runner (40) to the maximum runner area;
f is the number of areas into which the second flow channel area is divided equally in the direction from the maximum flow channel area to the outlet of the flow channel (40);
p =1,2, \8230, M is more than or equal to 1;
q =1,2, \8230:, F, and F is more than or equal to 1.
As shown in FIGS. 5 to 6, for the inlet width of the flow path 40, when Z is 30. Ltoreq. Z.ltoreq.60 and R is 0.7. Ltoreq.R 1 /R 2 When the weight is less than or equal to 0.8, directly measuring W by a geometric drawing method 1 (ii) a When 60 is turned on<Z is less than or equal to 100 and is 0.8<R 1 /R 2 When the content is less than or equal to 0.9,
it uses the following approximate algorithm to assume the inlet points of adjacent blades 4 are A and B respectively, and the grid distance at the inlet of blade 4 is f 1 Wherein, in the process,
as the number of the vanes 4 increases, the angle between the width of the inlet runner and the pitch tends to 0, and the inlet width W of the runner 40 is calculated 1 。
The pitch at the outlet of the adjacent blades 4 is f for the outlet width of the flow channel 40 2 Wherein, in the step (A),
in the formula: r is b Radius of arc of cross-section of the blade, beta b2 Is the included angle between the radius of the circular arc where the exit point of the blade 4 is located and the connecting line from the exit point of the blade 4 to the center of the impeller. As shown in fig. 7, in the present embodiment, for the section of the blade 4 being an arc, the cross section in this embodiment is a section parallel to the front disk 1, and by establishing the above formula, and using the arc radius of the exit point on the cross section of the blade 4 and the included angle between the exit point and the center connecting line of the impeller, the width W of the exit end of the flow channel 40 can be quickly calculated through modeling or the above function N 。
For different areas W i The value of W can be directly measured by a geometric drawing method 1 It can also be determined by modelling or building a function of the section of the blade 4.
In this embodiment, for three different flow channels 40, the relationship between the height of the protrusion 411 or the groove depth of the groove 421 in different areas and the width of the flow channel is specified, so as to improve the flow uniformity of the fluid and reduce the aerodynamic noise.
1) For a uniform flow channel 40, W 1 ≈W N ≈W i ，d i ∈[0～0.4W i ) In the formula, d i The height of the protrusion 411 or the groove depth of the groove 421 in the i-th region;
2) For the accelerated flow path 40, W 1 ＞W i ＞W N ，d i ＝(N+1-i)*(W 1 –W N ) N, and d i ＝min[(N+1-i)*(W 1 –W N )/N，0.4W i ]In the formula: d is a radical of i The height of the protrusion 411 or the groove depth of the groove 421 in the ith area is preferably equal to or more than 3 and equal to or less than 6; when the developed width of the blade 4 is small, such as less than 25mm, then N =1;
3) For the middle of the deceleration-before-acceleration runner 40, there is a maximum runner region having a width W max Wherein W is max >W 1 ，W max >W N The height of the protrusion 411 or the depth of the groove 421 at the maximum flow path region is d max ，d max ＝min[|(W 2 -W 1 )|，0.4W max ]；
The area between the inlet of the flow channel 40 and the maximum flow channel area is a first flow channel area, the first flow channel area is equally divided into M areas along the direction from the inlet of the flow channel 40 to the maximum flow channel area, the height of the protrusion 411 or the depth of the groove 421 in the first flow channel area is d p Wherein d is p ＝(M+1-p)*|(W N -W 1 ) I/M, and d p ＝min[(M+1-i)*|(W N -W 1 )|/M，0.4W i ]In the formula: p =1,2, \ 8230, M is more than or equal to 1; preferably, M is more than or equal to 3 and less than or equal to 6, and when the unfolding width of the blade is smaller than 25mm, M =1 is selected.
The area between the outlet of the maximum flow path area and the flow path 40 is a second flow path area which is equally divided into F areas along the direction from the maximum flow path area to the outlet of the flow path 40, and the second flow path areaThe height of the protrusion 411 or the depth of the groove 421 in the flow channel region is d q Wherein d is q ＝(M+1-p)*|(W N -W 1 ) I/F, and d q ＝min[(F+1-q)*|(W N -W 1 )|/F，0.4W i ]In the formula: q =1,2, \ 8230;, F, and F ≧ 1. Preferably, F is more than or equal to 3 and less than or equal to 6, and F =1 is taken when the unfolding width of the blade is smaller than 25 mm.
In the present embodiment, the height of the protrusion 411 or the depth of the groove 421 in different areas and the width of the corresponding flow channel 40 are defined for different types of flow channels 40. So that the bulge 411 or the groove 421 in the above range can disturb the boundary layer fluid, improve the uniformity of the fluid flow, reduce the aerodynamic noise, and improve the aerodynamic performance of the centrifugal fan.
The utility model discloses centrifugal fan includes: like above-mentioned impeller, spiral case, motor, wherein, motor, impeller all set up in the spiral case, and the impeller is connected in the output of motor for the rotation of drive impeller.
Wherein, the centrifugal fan can exhaust the waste gas of stove burning and the oil smoke that produces in the culinary art process fast and discharge outdoors. The centrifugal fan in the embodiment includes any one of the above-mentioned impellers, and since the above-mentioned impeller has the above-mentioned technical effects, the range hood having the above-mentioned impeller should also have the same technical effects.
In the embodiments of the present invention, the term "plurality" means two or more unless explicitly defined otherwise. The terms "mounted," "connected," "fixed," and the like are used broadly and should be construed to mean, for example, that "connected" may be a fixed connection, a removable connection, or an integral connection. The specific meaning of the above terms in the embodiments of the present invention can be understood by those skilled in the art according to specific situations.
In the description of the embodiments of the present invention, it should be understood that the terms "upper", "lower", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, which are only for convenience of description and simplification of the description of the embodiments of the present invention, and do not indicate or imply that the device or unit indicated by the terms must have a specific direction, be constructed and operated in a specific orientation, and therefore, should not be construed as limiting the embodiments of the present invention.
In the description herein, the description of the terms "one embodiment," "a preferred embodiment," etc. means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the embodiments of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes may be made to the embodiment of the present invention by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the embodiments of the present invention should be included in the protection scope of the embodiments of the present invention.
Claims (10)
1. An impeller for a centrifugal fan, comprising:
a front disc (1), a middle disc (2) and a rear disc (3), wherein the middle disc (2) is positioned between the front disc (1) and the rear disc (3);
a plurality of blades (4) which penetrate through the middle disc (2), one end of each blade is connected to the front disc (1) and the other end of each blade is connected between the rear discs (3), wherein a flow passage (40) for fluid to flow through is formed between every two adjacent blades (4);
the hub (5) is arranged on the inner periphery of the central disc, and the blades (4) are uniformly distributed along the outer periphery of the hub (5);
the blade (4) comprises a suction surface (41) and a pressure surface (42) which are opposite, the suction surface (41) comprises a protrusion (411) used for improving the uniformity of fluid flow, the pressure surface (42) comprises a groove (421) used for improving the uniformity of fluid flow, the height of the protrusion (411) and the groove depth of the groove (421) are 0-0.4 times of the width of a corresponding flow channel, and the depth of the groove (421) is smaller than the thickness of the blade (4).
2. The impeller according to claim 1,
the number of the protrusions (411) is multiple, wherein the protrusions (411) are distributed in an array to form a protrusion array, and the protrusion array is used for flow mixing of fluid on a boundary layer of the suction surface (41) so as to reduce broadband noise;
the grooves (421) are distributed in an array manner to form a groove array, and the grooves (421) are used for forming vortex, so that transition of a boundary layer of the pressure surface (42) occurs in advance, and the flow uniformity is improved.
3. The impeller according to claim 2, characterized in that the longitudinal section of the protrusion (411) and the longitudinal section of the groove (421) are respectively one of a circular arc, a V-shape, an inverted U-shape, a quadratic curve;
the protrusion array comprises protrusions (411) with one or more of circular arc-shaped, V-shaped, inverted U-shaped and quadratic curves in longitudinal section, and the groove array comprises grooves (421) with one or more of circular arc-shaped, V-shaped, inverted U-shaped and quadratic curves in longitudinal section.
4. The impeller according to claim 1, characterised in that the number of blades (4) is Z, wherein 30. Ltoreq. Z.ltoreq.100.
5. The impeller according to claim 4, characterized in that the cross section of the blade (4) is circular arc;
the inner diameter of the impeller is R 1 The outer diameter of the impeller is R 2 Wherein R is more than or equal to 0.7 1 /R 2 ≤0.9。
6. The impeller according to claim 5, characterized in that the flow channel (40) is equally divided into N in the inlet-to-outlet direction of the blades (4)A region in which the width of the flow channel (40) at the inlet end of the blade (4) is W 1 The width of the flow channel (40) at the outlet end of the blade (4) is W N The width of the flow channel (40) corresponding to the bulge (411) is W i The thickness of the blade (4) is delta, and the height of the bulge (411) is h 1 The depth of the groove (421) is h 2 Wherein h is 1 ∈[0～0.4W i )，h 2 ∈[0～0.4W i ) And h is 2 <δ, in the formula, i =1,2, \8230;, N.
7. The impeller according to claim 6, characterized in that 0.3 δ < d i ＜0.2W i Wherein, W i >1.5δ。
8. The impeller of claim 6, wherein d is i ＝(N+1-i)*(W 1 –W N ) N, and d i ＝min[(N+1-i)*(W 1 –W N )/N，0.4W i ]In the formula: d i Is the height of the protrusion (411) of the i-th area or the groove depth of the groove (421).
9. The impeller of claim 6, wherein a maximum flow channel region is present in the middle of the flow channel (40), the area between the inlet of the flow channel (40) and the maximum flow channel region being a first flow channel region, the area between the outlet of the maximum flow channel region and the flow channel (40) being a second flow channel region, the maximum flow channel region having a width W max The height of the protrusion (411) or the groove depth of the groove (421) at the maximum flow passage area is d max The height of the protrusion (411) or the groove depth of the groove (421) in the first flow channel area is d p The height of the protrusion (411) or the groove depth of the groove (421) in the second flow channel region is d q Wherein, in the step (A),
W max >W 1 ，W max >W N ；
d max ＝min[|(W 2 -W 1 )|，0.4W max ]；
d p ＝(M+1-p)*|(W N -W 1 ) I/M, and d p ＝min[(M+1-i)*|(W N -W 1 )|/M，0.4W i ]；
d q ＝(M+1-p)*|(W N -W 1 ) I/F, and d q ＝min[(F+1-q)*|(W N -W 1 )|/F，0.4W i ]；
In the formula, M is the number of areas which divide the first flow channel area into the first flow channel area along the direction from the inlet of the flow channel (40) to the maximum flow channel area;
f is the number of areas into which the second flow channel area is divided equally in the direction from the largest flow channel area to the outlet of the flow channel (40);
p =1,2, \ 8230, M is more than or equal to 1;
q =1,2, \ 8230;, F, and F ≧ 1.
10. A centrifugal fan comprising an impeller according to any one of claims 1 to 9, a volute, and a motor, wherein the motor and the impeller are both disposed in the volute, and the impeller is connected to an output end of the motor for driving the impeller to rotate.
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