CN111396356A - Impeller assembly and air conditioner - Google Patents
Impeller assembly and air conditioner Download PDFInfo
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- CN111396356A CN111396356A CN202010312568.2A CN202010312568A CN111396356A CN 111396356 A CN111396356 A CN 111396356A CN 202010312568 A CN202010312568 A CN 202010312568A CN 111396356 A CN111396356 A CN 111396356A
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- 230000007423 decrease Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000000737 periodic effect Effects 0.000 description 2
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/30—Vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/422—Discharge tongues
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- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The embodiment of the invention provides an impeller assembly and an air conditioner, and relates to the technical field of air conditioners. The impeller assembly comprises a plurality of through-flow blades and a wheel disc, wherein the number of the through-flow blades is multiple, the through-flow blades are arranged along the circumferential direction of the wheel disc, the through-flow blades have an outer diameter and an inner diameter relative to the rotating axis of the impeller assembly, and at least one of the outer diameter and the inner diameter changes linearly along the extending direction of the rotating axis. The impeller assembly and the air conditioner have low noise, and the rotating noise of the indoor unit of the air conditioner can be effectively reduced.
Description
Technical Field
The invention relates to the technical field, in particular to an impeller assembly and an air conditioner.
Background
The outlet airflow of the cross-flow impeller blade of the air conditioner impacts the volute tongue at a higher speed, and is separated at the volute tongue to generate larger momentum and energy change. At the same time, a large rotational noise is also caused.
Disclosure of Invention
The invention solves the problem that the blade of the through-flow impeller can generate larger rotation noise.
In order to solve the problems, the invention provides an impeller assembly and an air conditioner.
In a first aspect, an embodiment provides an impeller assembly, including a plurality of through-flow blades and a disk, the through-flow blades being arranged in a circumferential direction of the disk, the through-flow blades having an outer diameter and an inner diameter with respect to a rotation axis of the impeller assembly, and at least one of the outer diameter and the inner diameter varying in an extending direction of the rotation axis.
The impeller subassembly that the embodiment of the invention provides: at least one of the inner diameter and the outer diameter of the through-flow blade varies in the direction of extension of the rotation axis, i.e. at least one of the inner diameter and the outer diameter is not constant, and the distance between one of the inner side surface and the outer side surface of the through-flow blade and the volute tongue is not constant, so that the aerodynamic performance of the through-flow blade at different positions is not uniform, thereby destroying the axial periodicity effect of the impeller assembly and the volute tongue and reducing the above-mentioned rotational noise.
In an alternative embodiment, at least one of the outer diameter and the inner diameter varies linearly along the extension of the rotation axis.
In an optional embodiment, the outer diameter changes linearly along the extension direction of the rotation axis, and an included angle between a connecting line of the outer diameter and the rotation axis ranges from 0 degree to 5 degrees; and/or the inner diameter linearly changes along the extending direction of the rotating axis, and the included angle between the connecting line of the inner diameter and the rotating axis ranges from-5 degrees to 5 degrees.
In an alternative embodiment, the cross-flow blade has a pressure side and a suction side, the pressure side being opposite the suction side, and the pressure side and the suction side both being curved.
In an alternative embodiment, at least one of the linearity of the pressure surface and the suction surface is a most deceleration line.
In an alternative embodiment, at least one of the pressure side and the suction side satisfies the following linear curve equation:
x＝k*c/(2*π)*(θ-sinθ)；
y＝k*c/(2*π)*(1-cosθ)；
and k is a coefficient, the value range is 0.1-10, c is the chord length of the through-flow blade, and theta is the included angle between the connecting line of the end point and the midpoint of the mean camber line of the through-flow blade and the x direction.
In an optional embodiment, the impeller assembly further includes at least one middle segment disc, and the two adjacent middle segment discs and the fan blade located between the two adjacent middle segment discs form a fan blade small segment, or the adjacent middle segment discs, the adjacent wheel disc, and the fan blade located between the adjacent middle segment discs and the adjacent wheel disc form the fan blade small segment; the impeller assembly is provided with at least two fan blade small sections, and blades in at least one fan blade small section are the cross-flow blades.
In an optional embodiment, if the number of the middle discs is odd, the impeller assembly is symmetrical with respect to the middle disc located at the middle position; if the number of the middle section discs is even, the inner diameter and the outer diameter of the blades positioned on the middle section are constant values.
In a second aspect, an embodiment provides an impeller assembly for being matched with a volute tongue of an air conditioner, the impeller assembly including a plurality of through-flow blades and a wheel disc, the plurality of through-flow blades being arranged along a circumferential direction of the wheel disc and having a rotation axis, the through-flow blades having opposite first and second sides, the first side being disposed on an outer side of the impeller assembly, and the second side being disposed on an inner side of the impeller assembly; in the extending direction of the rotating axis, the distance between the first side edge and the volute tongue changes linearly, and/or the distance between the second side edge and the volute tongue changes linearly.
The impeller subassembly that the embodiment of the invention provides: the distance between at least one of the first side edge and the second side edge of the through-flow blade and the volute tongue is not constant, so that the aerodynamic performance of different positions of the through-flow blade is inconsistent, the axial periodic action of the impeller assembly and the volute tongue is damaged, and the rotating noise is reduced.
In an optional embodiment, the cross-flow blade has a pressure surface and a suction surface, the pressure surface is opposite to the suction surface, the first side is connected to one end of the pressure surface and one end of the suction surface, the second side is connected to the other end of the pressure surface and the other end of the suction surface, and both the pressure surface and the suction surface are arc surfaces.
In a third aspect, embodiments provide an air conditioner comprising an impeller assembly as described in any of the preceding embodiments.
The air conditioner has the advantages that the air conditioner is similar to the impeller assembly, noise can be reduced, and user experience is improved.
Drawings
FIG. 1 is a schematic structural diagram of an impeller assembly provided in an embodiment of the present invention;
FIG. 2 is a schematic view of the impeller assembly of FIG. 1 from another perspective;
FIG. 3 is a schematic view of the impeller assembly and volute tongue of FIG. 1;
FIG. 4 is a schematic structural view of the flow vane of FIG. 1;
FIG. 5 is an enlarged view of the structure at A in FIG. 4;
FIG. 6 is a schematic structural view of the flow-through vane of FIG. 4 from another perspective;
FIG. 7 is a schematic diagram of the line of the mean camber line in FIG. 6 in a rectangular coordinate system;
FIG. 8 is a schematic structural diagram of the middle segment disk of FIG. 1 with an odd number;
fig. 9 is a schematic structural diagram of fig. 1 when the number of the middle disks is even.
Icon: 100-an impeller assembly; 101-axis of rotation; 11-cross flow vanes; 11 a-outer diameter; 11 b-inner diameter; 11 c-pressure side; 11 d-suction side; 11 e-mean camber line; 11 f-end point; 11 g-midpoint; 11 h-first side; 11 i-a second side; 11 j-the direction of the axis of rotation; 12-a wheel disc; 13-middle section disc; 200-volute tongue.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.
Referring to fig. 1, a structure of an impeller assembly 100 according to an embodiment of the present invention is shown, where the impeller assembly 100 can be used in an air conditioner, for example, an indoor unit of the air conditioner. This impeller subassembly 100 has lower rotational noise, can reduce the rotational noise of air conditioner or air conditioner indoor set, is favorable to promoting user's use and experiences.
In the embodiment of the present invention, the impeller assembly 100 includes a plurality of through-flow blades 11 and a disk 12, the number of the through-flow blades 11 is plural, and the plurality of through-flow blades 11 are arranged in the circumferential direction of the disk 12 (as shown in fig. 2), the through-flow blades 11 have an outer diameter 11a and an inner diameter 11b with respect to a rotation axis 101 of the impeller assembly 100, and at least one of the outer diameter 11a and the inner diameter 11b varies along the extending direction of the rotation axis 101.
It should be noted that the above-mentioned "at least one of the outer diameter 11a and the inner diameter 11b varies along the extending direction of the rotation axis 101" means that at least one of the outer diameter 11a and the inner diameter 11b varies, that is, at least one of the outer diameter 11a and the inner diameter 11b is not a constant value, that is, at least one of the outer diameter 11a and the inner diameter 11b has two or more values. The outer diameter 11a of the flow-through vane 11 refers to the distance between the outside of the flow-through vane 11 and the rotation axis 101, and the inner diameter 11b of the flow-through vane 11 refers to the distance between the inside of the flow-through vane 11 and the rotation axis 101.
Referring to fig. 3, it should also be noted that the impeller assembly 100 is matched with a volute tongue 200 of an air conditioner, and the impeller assembly 100 is spaced from the volute tongue 200. When at least one of the outer diameter 11a and the inner diameter 11b changes in the extending direction of the rotation axis 101, the distance between the corresponding one of the inner side surface and the outer side surface of the flow-through vane 11 and the volute tongue 200 also changes. That is, if the outer diameter 11a changes in the extending direction of the rotation axis 101, the distance between the outer side of the cross flow blade 11 and the volute tongue 200 also changes; when the inner diameter 11b changes in the extending direction of the rotation axis 101, the distance between the inner side of the flow-through vane 11 and the volute tongue 200 also changes. That is, the distance of at least one of the outer and inner sides of the blade from the volute tongue 200 on the rotation axis 101 is not constant.
Also, it should be understood that the distance between the volute tongue 200 and the rotation axis 101 is constant, and when at least one of the outer diameter 11a and the inner diameter 11b changes in the extending direction of the rotation axis 101 when the cross flow blade 11 is located between the volute tongue 200 and the rotation axis 101, the corresponding one of the inner side surface and the outer side surface of the cross flow blade 11 also changes with the volute tongue 200, and the change is opposite to the trend of the inner diameter 11b and the outer diameter 11 a. For example, if the outer diameter 11a increases in the extension direction of the rotation axis 101, the distance between the outer side of the through-flow blade 11 and the volute tongue 200 decreases; if the outer diameter 11a decreases in the direction of extension of the axis of rotation 101, the distance between the outer side of the through-flow blade 11 and the volute tongue 200 decreases and increases.
In the prior art, the blades of the impeller are uniformly distributed around the circumference of the disk 12, and strong periodic action is generated between the blades and the volute tongue 200, so that high rotating noise is caused. In the embodiment of the present invention, at least one of the inner diameter 11b and the outer diameter 11a of the through-flow blade 11 varies in the extending direction of the rotation axis 101, that is, at least one of the inner diameter 11b and the outer diameter 11a is not constant, and the distance between one of the inner side surface and the outer side surface of the through-flow blade 11 and the volute tongue 200 is not constant, so that the aerodynamic performance of different positions of the through-flow blade 11 is not uniform, thereby destroying the axial periodicity of the impeller assembly 100 and the volute tongue 200, and reducing the above-mentioned rotational noise.
Referring to fig. 4, in an alternative embodiment, at least one of the outer diameter 11a and the inner diameter 11b varies linearly along the extension direction of the rotation axis 101. That is, at least one of the outer diameter 11a and the inner diameter 11b linearly increases or linearly decreases in the extending direction of the rotation axis 101.
It should be understood that the linear increase or decrease of at least one of the outer diameter 11a and the inner diameter 11b along the extension direction of the rotation axis 101 can facilitate the manufacture of the through-flow blade 11 on the one hand, and the linear change of at least one of the outer diameter 11a and the inner diameter 11b can reduce the influence of the wind on the through-flow blade 11 while destroying the periodicity between the through-flow blade 11 and the volute tongue 200, i.e. the service performance and service life of the through-flow blade 11 are ensured, and the service reliability of the through-flow blade 11 is improved.
Referring to fig. 5, further, the outer diameter 11a varies linearly along the extending direction of the rotation axis 101, and the included angle between the connection line of the outer diameter 11a and the rotation axis 101 is 0 to 5 degrees, i.e. a in fig. 51The angle range of (A) is 0 to 5 degrees.
It should be noted that, here, the "connection line of the outer diameter 11 a" refers to that the outer diameter 11a changes linearly on the flow-through vane 11, and the size of the outer diameter 11a is a plurality of sets of values that change continuously from large to small, and the connection line of the outer diameter 11a can be understood as a straight line on which the outer side surface of the flow-through vane 11 is located.
Meanwhile, it should be understood that the range of the included angle between the connecting line of the outer diameter 11a and the rotation axis 101 is 0-5 degrees, so that the distance between the air outlet of the through-flow blade 11 and the volute tongue 200 is ensured to be proper, and the change of the outer diameter 11a is in a reasonable range, thereby ensuring the air volume.
Further, in the embodiment of the present invention, the inner diameter 11b varies linearly along the extending direction of the rotation axis 101, and the included angle between the connection line of the inner diameter 11b and the rotation axis 101 is in the range of-5 to 5 degrees, i.e. a in fig. 52The angle range of the angle is-5 to 5 degrees.
It should be noted that the included angle between the connection line of the inner diameter 11b and the rotation axis 101 is in the range of-5 to 5 degrees, wherein when the connection line of the inner diameter 11b is above the rotation axis direction 11j, the included angle between the connection line of the inner diameter 11b and the rotation axis 101 takes a negative value; when the line of the inner diameter 11b is below the rotation axis direction 11j, the angle between the line of the inner diameter 11b and the rotation axis 101 takes a positive value. The rotation axis direction 11j extends from one end to the other end of the flow-through vane 11, and the rotation axis direction 11j is parallel to, but not collinear with, the rotation axis 101.
Meanwhile, it should be understood that the included angle between the connection line of the inner diameter 11b and the rotation axis 101 is in the range of-5 to 5 degrees, so that the size of the cross flow blade 11 can be ensured, and the efficiency and the air volume of the impeller assembly 100 can be considered.
Referring to fig. 6, in the embodiment of the present invention, the cross flow blade 11 has a pressure surface 11c and a suction surface 11d, the pressure surface 11c is opposite to the suction surface 11d, and both the pressure surface 11c and the suction surface 11d are arc surfaces.
At the same time, the through-flow blades 11 also have a mean camber line 11e, optionally the pressure surface 11c, the suction surface 11d and the mean camber line 11e are of the same line type.
Furthermore, at least one of the linearity of the pressure surface 11c and the linearity of the suction surface 11d is a slowest speed line, so that the air flow flows out of the flow passage in the shortest time, the residence time of the air flow in the flow passage is reduced, and the air flow blockage of the flow passage is reduced. In the present embodiment, the pressure surface 11c, the suction surface 11d, and the camber line 11e are all the lines of the most decelerated line.
Referring to FIG. 7, in an alternative embodiment, at least one of the pressure side 11c and the suction side 11d satisfies the following linear curve equation:
x＝k*c/(2*π)*(θ-sinθ)；
y＝k*c/(2*π)*(1-cosθ)；
wherein k is a coefficient, the value range is 0.1-10, c is the chord length of the through-flow blade 11, i.e. the linear distance between two end points 11f of the mean camber line 11e, θ is the included angle between the connecting line of the end point 11f and the midpoint 11g of the mean camber line 11e of the through-flow blade 11 and the x direction, and the x direction is the x direction of the rectangular coordinate system as shown in the figure.
The rectangular coordinate system is established with one of the end points of the line shapes of the pressure surface 11c, the suction surface 11d, and the camber line 11e as the origin, with the chord length direction as the x-axis, and with the perpendicular chord length direction as the y-axis.
In the embodiment of the present invention, the pressure surface 11c, the suction surface 11d, and the camber line 11e all satisfy the above-described linear curve equation.
In an alternative embodiment, the impeller assembly 100 includes at least one middle segment disc 13, where two adjacent middle segment discs 13 and the fan blade located between the two adjacent middle segment discs 13 form a fan blade small segment, or the adjacent middle segment discs 13, the wheel disc 12 and the fan blade located between the adjacent middle segment discs 13 and the wheel disc 12 form a fan blade small segment; the impeller assembly 100 has at least two fan blade segments, and the blades in at least one fan blade segment are cross-flow blades 11 to reduce the noise generated by the fan blade segment.
It should be noted that, in the embodiment of the present invention, the blades located on the same blade segment are blades with substantially the same structure.
It should be understood that when the number of the fan blade segments is one, the fan blade segments are formed by disks at both ends and blades located between the disks, which are the aforementioned cross-flow blades 11. When the number of the fan blade sections is two or more, the impeller assembly 100 further comprises at least one middle section disc 13, the two adjacent middle section discs 13 and the fan blade positioned between the two adjacent middle section discs 13 form the fan blade sections, or the adjacent middle section discs 13 and the wheel disc 12 form the fan blade sections by the fan blade between the adjacent middle section discs 13 and the wheel disc 12; the through-flow blades 11 are arranged at least circumferentially along one of the at least one medium disk 13. That is, in each of the fan blade sections, at least one of the fan blade sections is the cross-flow blade 11.
If the number of the middle discs 13 is odd, the impeller assembly 100 is symmetrical relative to the middle disc 13 in the middle position; if the number of the middle segment discs 13 is even, the inner diameter 11b and the outer diameter 11a of the blade of the middle blade segment are constant.
Alternatively, the impeller assemblies 100 are symmetrically disposed. Referring to fig. 8, if the number of the middle segment discs 13 is odd, that is, the number of the fan blade segments of the impeller assembly 100 is even, the impeller assembly 100 is symmetrical to the middle segment disc 13; referring to fig. 9, if the number of the middle segment discs 13 is even, that is, the number of the blade segments of the impeller assembly 100 is odd, the inner diameter 11b and the outer diameter 11a of the blade located in the middle segment are fixed. The above arrangement can ensure stable stress of the whole impeller assembly 100, thereby ensuring the service life of the impeller assembly 100 and reducing the failure probability.
Referring to fig. 4 and 6, the cross flow blade 11 has a first side 11h and a second side 11i opposite to each other, the first side 11h is disposed outside the impeller assembly 100, and the second side 11i is disposed inside the impeller assembly 100; in the extending direction of the rotation axis 101, the distance between the first side 11h and the volute tongue 200 varies linearly, and/or the distance between the second side 11i and the volute tongue 200 varies linearly.
Further, the cross flow blade 11 has a pressure surface 11c and a suction surface 11d, the pressure surface 11c is opposite to the suction surface 11d, the first side 11h is connected to one end of the pressure surface 11c and one end of the suction surface 11d, the second side 11i is connected to the other end of the pressure surface 11c and the other end of the suction surface 11d, and both the pressure surface 11c and the suction surface 11d are arc surfaces.
An embodiment of the present invention further provides an air conditioner, including an impeller assembly 100 according to any one of the foregoing embodiments. The impeller assembly 100 can be installed in an indoor unit of an air conditioner to reduce noise of the indoor unit and improve user experience.
Referring to fig. 1 to 9, an impeller assembly 100 and an air conditioner according to an embodiment of the present invention are shown: at least one of the inner diameter 11b and the outer diameter 11a of the through-flow blade 11 varies in the extending direction of the rotation axis 101, i.e., at least one of the inner diameter 11b and the outer diameter 11a is not constant, the distance between one of the inner side surface and the outer side surface of the through-flow blade 11 and the volute tongue 200 is not constant, or the distance between at least one of the first side edge 11h and the second side edge 11i of the through-flow blade 11 and the volute tongue 200 is not constant, so that the aerodynamic performance of different positions of the through-flow blade 11 is not uniform, thereby destroying the axial periodicity of the impeller assembly 100 and the volute tongue 200 and reducing the above-mentioned rotational noise.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (11)
1. Impeller assembly comprising a through-flow blade (11) and a wheel disc (12), said through-flow blade (11) being in a plurality in number and said through-flow blades (11) being arranged in a circumferential direction of said wheel disc (12), characterized in that said through-flow blade (11) has an outer diameter (11a) and an inner diameter (11b) with respect to a rotation axis (101) of said impeller assembly (100), and at least one of said outer diameter (11a) and said inner diameter (11b) varies along the extension direction of said rotation axis (101).
2. The impeller assembly according to claim 1, characterized in that at least one of the outer diameter (11a) and the inner diameter (11b) varies linearly along the extension of the rotation axis (101).
3. The impeller assembly according to claim 1 or 2, characterized in that the outer diameter (11a) varies linearly along the extension of the rotation axis (101), and the line of the outer diameter (11a) forms an angle with the rotation axis (101) in the range of 0 to 5 degrees; and/or the inner diameter (11b) is linearly changed along the extension direction of the rotating axis (101), and the included angle between the connecting line of the inner diameter (11b) and the rotating axis (101) ranges from-5 degrees to 5 degrees.
4. The impeller assembly according to claim 1, characterized in that the through-flow blade (11) has a pressure surface (11c) and a suction surface (11d), the pressure surface (11c) being opposite to the suction surface (11d), the pressure surface (11c) and the suction surface (11d) being both arc-shaped surfaces.
5. The impeller assembly of claim 4, characterized in that at least one of the linearity of the pressure surface (11c) and the suction surface (11d) is a most decreasing line.
6. The impeller assembly of claim 4 or 5, characterized in that at least one of the pressure surface (11c) and the suction surface (11d) satisfies the following linear curve equation:
x＝k*c/(2*π)*(θ-sinθ)；
y＝k*c/(2*π)*(1-cosθ)；
the value range of k is 0.1-10, c is the chord length of the through-flow blade (11), theta is the included angle between the connecting line of the end point (11f) and the midpoint (11g) of the mean camber line (11e) of the through-flow blade (11) and the x direction, and the x direction is the direction of the x axis under a rectangular coordinate system.
7. The impeller assembly according to claim 1, characterized in that the impeller assembly (100) further comprises at least one middle segment disc (13), and the two adjacent middle segment discs (13) and the fan blade between the two adjacent middle segment discs (13) form a fan blade segment, or the adjacent middle segment discs (13), the wheel disc (12) and the fan blade between the adjacent middle segment discs (13) and the wheel disc (12) form the fan blade segment; the impeller assembly is provided with at least two fan blade small sections, and blades in at least one fan blade small section are the cross-flow blades (11).
8. The impeller assembly according to claim 7, characterized in that if the number of the middle discs (13) is odd, the impeller assembly (100) is symmetrical with respect to the middle disc (13) located at the middle position; if the number of the middle section discs (13) is even, the inner diameter (11b) and the outer diameter (11a) of the blades positioned at the middle section are constant.
9. An impeller assembly for cooperating with a volute tongue (200) of an air conditioner, the impeller assembly (100) comprising a plurality of through-flow blades (11) and a disk (12), the through-flow blades (11) being plural in number, and the plural through-flow blades (11) being arranged along a circumferential direction of the disk (12) and having a rotation axis (101), characterized in that the through-flow blades (11) have opposite first and second sides (11h, 11i), the first side (11h) being disposed outside the impeller assembly (100), the second side (11i) being disposed inside the impeller assembly (100); in the extending direction of the rotation axis (101), the distance between the first side edge (11h) and the volute tongue (200) changes linearly, and/or the distance between the second side edge (11i) and the volute tongue (200) changes linearly.
10. The impeller assembly according to claim 9, characterized in that the cross flow blade (11) has a pressure side (11c) and a suction side (11d), the pressure side (11c) being opposite to the suction side (11d), the first side (11h) being connected to one end of the pressure side (11c) and the suction side (11d), respectively, the second side (11i) being connected to the other end of the pressure side (11c) and the suction side (11d), respectively, the pressure side (11c) and the suction side (11d) being both arc-shaped.
11. An air conditioner, characterized in that it comprises an impeller assembly (100) according to any one of claims 1 to 10.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010312568.2A CN111396356A (en) | 2020-04-20 | 2020-04-20 | Impeller assembly and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010312568.2A CN111396356A (en) | 2020-04-20 | 2020-04-20 | Impeller assembly and air conditioner |
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| CN111396356A true CN111396356A (en) | 2020-07-10 |
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| CN202010312568.2A Pending CN111396356A (en) | 2020-04-20 | 2020-04-20 | Impeller assembly and air conditioner |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2022143328A1 (en) * | 2020-12-31 | 2022-07-07 | 广东美的厨房电器制造有限公司 | Centrifugal fan, household appliance, volute, and cooking utensil |
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| CN211924559U (en) * | 2020-04-20 | 2020-11-13 | 宁波奥克斯电气股份有限公司 | Impeller assembly and air conditioner |
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| WO2022143328A1 (en) * | 2020-12-31 | 2022-07-07 | 广东美的厨房电器制造有限公司 | Centrifugal fan, household appliance, volute, and cooking utensil |
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