CN204532956U - Centrifugal impeller, centrifugal fan assembly and air conditioning unit - Google Patents
Centrifugal impeller, centrifugal fan assembly and air conditioning unit Download PDFInfo
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- CN204532956U CN204532956U CN201520032153.4U CN201520032153U CN204532956U CN 204532956 U CN204532956 U CN 204532956U CN 201520032153 U CN201520032153 U CN 201520032153U CN 204532956 U CN204532956 U CN 204532956U
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- 238000004378 air conditioning Methods 0.000 title abstract 2
- 238000009434 installation Methods 0.000 claims abstract description 29
- 241000237858 Gastropoda Species 0.000 claims description 15
- 230000000712 assembly Effects 0.000 claims 6
- 238000000429 assembly Methods 0.000 claims 6
- 230000009286 beneficial effect Effects 0.000 description 9
- 239000012530 fluid Substances 0.000 description 9
- 230000009467 reduction Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 2
- 230000008901 benefit Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000008676 import Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
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Abstract
The utility model discloses a centrifugal impeller, centrifugal fan subassembly and air conditioning unit. The centrifugal impeller comprises a wheel disc (21) and blades (23) arranged on the wheel disc (21), wherein the inlet installation angle of each blade (23) ranges from 90 degrees to 120 degrees, and the outlet installation angle of each blade (23) ranges from 25 degrees to 40 degrees. Because the inlet mounting angle and the outlet mounting angle of the blade are in a reasonable range and reasonably matched with each other, the air flow velocity distribution at the outlet of the volute is more uniform, and the flow noise of the centrifugal fan assembly can be reduced.
Description
Technical field
The utility model relates to compressed machinery field, particularly a kind of centrifugal impeller, centrifugal blower assembly and air-conditioner set.
Background technique
As the important component part of air-conditioner set, centrifugal blower assembly generally comprises spiral case and centrifugal impeller, and the air circulation being responsible for air-conditioner set provides power.Its running principle is: by driven by motor centrifugal impeller in spiral case inner rotation, centrifugal impeller is inner to air work at spiral case, and change gas flow direction by spiral case and increase gas pressure, make to form pressure reduction between spiral case intake grill and exhaust outlet, ensure the circulation of gas.
In prior art, the operation noise of centrifugal blower assembly is one of dominant noise source of air-conditioner set.Such as, water-cooling case-type air-conditioner peculiar to vessel is installed on the region higher to the requirement of noise such as Ship dining rooms, crewman foyer, recreation room in a large number, therefore needs strictly to control the operation noise of centrifugal blower assembly.
Model utility content
The purpose of this utility model is to provide a kind of centrifugal impeller, centrifugal blower assembly and the air-conditioner set that can reduce flow noise.
The utility model first aspect provides a kind of centrifugal impeller, and comprise wheel disc and be arranged at the blade on described wheel disc, the stagger angle of described blade is 90 ° ~ 120 °, and the exit installation angle of described blade is 25 ° ~ 40 °.
Further, the stagger angle of described blade is 90 ° ~ 105 °, and the exit installation angle of described blade is 32 ° ~ 38 °.
Further, described blade is reduced to blade tip thickness gradually by root of blade.
Further, the ratio of the thickness F of the blade tip of described blade and the thickness E of root of blade is 0.35 ~ 0.7.
Further, the stagger angle d of the root of blade of described blade is greater than the stagger angle f of the blade tip of described blade, and the exit installation angle c of the root of blade of described blade is greater than the exit installation angle e of the blade tip of described blade.
Further, the difference of the stagger angle f of the stagger angle d of the root of blade of described blade and the blade tip of described blade is-5 ° ~ 5 °, and the difference of the exit installation angle e of the exit installation angle c of the root of blade of described blade and the blade tip of described blade is-5 ° ~ 5 °.
Further, the vane type line of described blade by smooth connection the first blade spline curve and lay respectively at the second blade spline curve of described first blade spline curve both sides and Three-blade spline curve forms, described first blade spline curve is positioned at the inlet of described blade, described second blade spline curve is positioned at the front of described blade, and described Three-blade spline curve is positioned at the back side of described blade.
Further, described centrifugal impeller is double-impeller, and two groups of blades are arranged at the both sides of described wheel disc respectively, and described two groups of blades dislocation is arranged, the lobe numbers often organizing blade is 41 ~ 61.
Further, the ratio of the width L of described blade and the air intake outline diameter Φ 2 of described centrifugal impeller is 5% ~ 15%.
The utility model second aspect provides a kind of centrifugal blower assembly, and comprise spiral case and be arranged at the centrifugal impeller in described spiral case, wherein, described centrifugal impeller is the centrifugal impeller according to any one of the utility model first aspect.
Further, the matching gap A between the intake grill of described spiral case and the end face of described centrifugal impeller is 3mm ~ 15mm.
Further, described spiral case has snail tongue, and the snail tongue radius R 1 of described snail tongue is 3mm ~ 15mm.
Further, described intake grill is convergent mouth, and the convergent curve of described convergent mouth is quarter circular arc, and the radius R 2 of described quarter circular arc is 10mm ~ 20mm.
Further, the exhaust outlet angle g of described spiral case is 15 ° ~ 30 °.
Further, the throat diameter Φ 1 of described intake grill is more than or equal to the air intake outline diameter Φ 2 of described centrifugal impeller, and described throat diameter Φ 1 is 1.0 ~ 1.2 with the ratio of described air intake outline diameter Φ 2.
Further, the ratio of the width C of described spiral case and the width H of described centrifugal impeller is 1.1 ~ 1.4.
The utility model third aspect provides a kind of air-conditioner set, comprises centrifugal blower assembly, and wherein, described centrifugal blower assembly is the centrifugal blower assembly according to any one of the utility model second aspect.
Based on centrifugal impeller, centrifugal blower assembly and air-conditioner set that the utility model provides, wherein centrifugal impeller comprises wheel disc and is arranged at the blade on wheel disc, it is characterized in that, the stagger angle of blade is 90 ° ~ 120 °, and the exit installation angle of blade is 25 ° ~ 40 °.Because the stagger angle of blade and exit installation angle are in rational scope and the two reasonable coordination, the Velocity Profiles at volute outlet place is more even, thus can lower the flow noise of centrifugal blower assembly.
By referring to the detailed description of accompanying drawing to exemplary embodiment of the present utility model, further feature of the present utility model and advantage thereof will become clear.
Accompanying drawing explanation
Accompanying drawing described herein is used to provide further understanding of the present utility model, and form a application's part, schematic description and description of the present utility model, for explaining the utility model, is not formed improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 is the perspective view of the centrifugal blower assembly of the utility model preferred embodiment.
Fig. 2 is the side-looking structural representation of centrifugal blower assembly embodiment illustrated in fig. 1.
Fig. 3 is the sectional structure schematic diagram of centrifugal blower assembly embodiment illustrated in fig. 1.
Fig. 4 is the perspective view of centrifugal impeller in centrifugal blower assembly embodiment illustrated in fig. 1.
Fig. 5 is the side-looking structural representation of centrifugal impeller in centrifugal blower assembly embodiment illustrated in fig. 1.
Fig. 6 is the sectional structure schematic diagram of centrifugal impeller in centrifugal blower assembly embodiment illustrated in fig. 1.
Fig. 7 is I structure for amplifying schematic diagram of Fig. 6.
In Fig. 1 to Fig. 7, each reference character represents respectively:
10, spiral case
11, spiral case body
12, intake grill
13, exhaust outlet
14, mounting flange
15, snail tongue
20, centrifugal impeller
21, wheel disc
22, live axle assembly department
23, blade
231, root of blade
232, blade tip
24, blade ring
Embodiment
Below in conjunction with the accompanying drawing in the utility model embodiment, be clearly and completely described the technological scheme in the utility model embodiment, obviously, described embodiment is only the utility model part embodiment, instead of whole embodiments.Illustrative to the description only actually of at least one exemplary embodiment below, never as any restriction to the utility model and application or use.Based on the embodiment in the utility model, those of ordinary skill in the art are not making the every other embodiment obtained under creative work prerequisite, all belong to the scope of the utility model protection.
Unless specifically stated otherwise, otherwise positioned opposite, the numerical expression of the parts of setting forth in these embodiments and step and numerical value do not limit scope of the present utility model.Meanwhile, it should be understood that for convenience of description, the size of the various piece shown in accompanying drawing is not draw according to the proportionate relationship of reality.May not discuss in detail for the known technology of person of ordinary skill in the relevant, method and apparatus, but in the appropriate case, described technology, method and apparatus should be regarded as a part of authorizing specification.In all examples with discussing shown here, any occurrence should be construed as merely exemplary, instead of as restriction.Therefore, other example of exemplary embodiment can have different values.It should be noted that: represent similar terms in similar label and letter accompanying drawing below, therefore, once be defined in an a certain Xiang Yi accompanying drawing, then do not need to be further discussed it in accompanying drawing subsequently.
Realizing model utility people discovery in process of the present utility model, the flow noise of centrifugal blower assembly mainly affects by following factor: it is unreasonable that blade imports and exports established angle design, causes volute outlet place Velocity Profiles uneven; The design of the molded line of spiral case, the molded line of blade and the matching gap between centrifugal impeller and spiral case is unreasonable, makes spiral case inner flow velocity gradient larger; It is less than normal that the size etc. of lobe numbers, snail tongue radius, centrifugal impeller and spiral case designs unreasonable do work scarce capacity, the air quantity of centrifugal centrifugal impeller that make, and also causes flow noise bigger than normal.
For the reason of the flow noise of the above centrifugal blower assembly of above impact, the utility model embodiment provides a kind of centrifugal impeller, centrifugal blower assembly and the air-conditioner set that can reduce flow noise.
As shown in Figures 1 to 7, the centrifugal blower assembly of the utility model embodiment comprises spiral case 10 and centrifugal impeller 20.Spiral case 10 comprises spiral case body 11, intake grill 12, exhaust outlet 13, outlet(discharge) flange 14 and snail tongue 15.Centrifugal impeller 20 is Multivane impeller.Centrifugal impeller 20 comprises wheel disc 21, live axle assembly department 22, blade 23 and blade ring 24.The root of blade 231 of each blade 23 is connected with wheel disc 21, and blade tip 232 is connected with blade ring 24.
During centrifugal blower component operation, by driven by motor centrifugal impeller 20 in spiral case 10 inner rotation, centrifugal impeller 20 in spiral case 10 inside to air work, and change gas flow direction by spiral case 10 and increase gas pressure, make to form pressure reduction between the intake grill 12 of spiral case 10 and exhaust outlet 13, ensure the circulation of gas.
Wherein, the stagger angle of blade 23 is 90 ° ~ 120 °, and the exit installation angle of blade 23 is 25 ° ~ 40 °.Preferably, the stagger angle of blade 23 is 90 ° ~ 105 °, and the exit installation angle of blade 23 is 32 ° ~ 38 °.Because the stagger angle of blade 23 and exit installation angle to be in rational scope and the two reasonable coordination, the flowing of fluid between blade 23 to be stablized, makes the Velocity Profiles in spiral case 10 outlet port more even further, thus can flow noise be lowered.
Blade 23 is reduced to blade tip 232 thickness gradually by root of blade 231.Preferably, the ratio of the thickness F of blade 23 blade tip 232 and the thickness E of root of blade 231 is 0.35 ~ 0.7.In the present embodiment, the thickness E of root of blade 231 is 3.6mm, and the thickness F of blade tip 232 is 1.6mm.The thickness rationally arranging blade 23 and the thickness reasonable change making blade 23 can make fluid flowing between the blades stablize, and are beneficial to reduction flow noise.
As shown in Figure 7, the stagger angle d of the root of blade 231 of blade 23 is greater than the stagger angle f of the blade tip 232 of blade 23, and the exit installation angle c of the root of blade 231 of blade 23 is greater than the exit installation angle e of the blade tip 232 of blade 23.Preferably, the difference of the stagger angle f of the stagger angle d of the root of blade 231 of blade 23 and the blade tip 232 of blade 23 is-5 ° ~ 5 °, and the difference of the exit installation angle e of the exit installation angle c of the root of blade 231 of blade 23 and the blade tip 232 of blade 23 is-5 ° ~ 5 °.Stagger angle d, the exit installation angle c of above root of blade 231 and the relation between stagger angle f, exit installation angle e of blade tip 232 make the flowing of fluid between blade 23 more stable, can reduce flow noise further.
As shown in Figure 7, in the present embodiment, the stagger angle d of root of blade 231 is 94.8 °; Exit installation angle c is 36.5 °.The stagger angle f of blade tip 232 is 94.5 °; Blade tip 232 exit installation angle is 33.9 °.
In addition as shown in Figure 7, the vane type line of blade 23 is made up of the first blade spline curve M1 of smooth connection and the second blade spline curve M2 and Three-blade spline curve M3 of laying respectively at the first blade spline curve M1 both sides, first blade spline curve M1 is positioned at the inlet of blade 23, second blade spline curve M2 is positioned at the front of blade 23, and Three-blade spline curve M3 is positioned at the back side of blade 23.The vane type line rationally arranging blade 23 is also conducive to fluid steady flow between blade, thus is beneficial to minimizing noise.
As shown in Figures 4 to 6, centrifugal impeller 20 is double-impeller, and two groups of blades 23 are arranged at the both sides of wheel disc 21 respectively, and two groups of blades 23 misplace and arrange.This is arranged so that the air flow energy flowing through blade 23 is not flowing out blade 23 in the same time, effectively can reduce the rotational noise of blade 23.The lobe numbers often organizing blade is 41 ~ 61.In the present embodiment, the lobe numbers often organizing blade 23 is 54.This is arranged so that centrifugal impeller 20 effectively can control air current flow, avoids blade 23 too much cause leaf road area to reduce and increase flow losses simultaneously.
The ratio of the width L of blade 23 and the air intake outline diameter Φ 2 of centrifugal impeller 20 is 5% ~ 15%.In the present embodiment, the air intake outline diameter Φ 2 of centrifugal impeller 20 is 191mm.Width of blade L is 17mm.This is arranged so that blade 23 effectively can control air current flow, avoid flow boundary layer be separated and air intake outline diameter Φ 2 too little.
As shown in Figure 3, centrifugal impeller 20 is the matching gap A between the intake grill 12 of spiral case 10 and the end face of centrifugal impeller 20 is 3mm ~ 15mm.More preferably, the matching gap A between the intake grill 12 of spiral case 10 and the end face of centrifugal impeller 20 is 6mm ~ 8mm.Spiral case 10 and centrifugal impeller 20 coaxial cooperation in the present embodiment, and the axial both sides end face of centrifugal impeller 20 is identical with the matching gap A of spiral case 10 axial both sides intake grill 12, matching gap A is 6.5mm.Matching gap between the intake grill 12 rationally arranging centrifugal impeller 20 and spiral case 10 can reduce the flowing velocity gradient of spiral case 10 internal flow, is beneficial to reduction noise.
The snail tongue radius R 1 of snail tongue 15 is 3mm ~ 15mm.More preferably, the snail tongue radius R 1 of snail tongue 15 is 10mm ~ 13mm.In the present embodiment, snail tongue radius R 1 is 10mm.Rationally arranging snail tongue radius R 1 makes the fluid in spiral case 10 be flowed out spiral case 10 smoothly, reduces eddy current, thus is beneficial to noise-decreasing.
Intake grill 12 is convergent mouth, and the convergent curve of convergent mouth is quarter circular arc, and the radius R 2 of quarter circular arc is 10mm ~ 20mm.In the present embodiment, the radius R 2 of quarter circular arc is 14mm.The shape rationally arranging intake grill 12 can reduce the impact of air intake to intake grill 12, is beneficial to noise-decreasing.
As shown in Figure 2, the exhaust outlet angle g of spiral case 10 is 15 ° ~ 30 °.In the present embodiment, the front horizontal sextant angle a of the exhaust outlet 13 of spiral case 10 is 50 °; Rear horizontal sextant angle b is 77 °; Spiral case exhaust outlet angle g is 27 °.Spiral case exhaust outlet angle g arranges and makes the fluid in spiral case 10 flow out spiral case 10 smoothly, reduces eddy current, thus is beneficial to noise-decreasing.
As shown in Figure 2, the throat diameter Φ 1 of intake grill 12 is more than or equal to the air intake outline diameter Φ 2 of centrifugal impeller 20, and throat diameter Φ 1 is 1.0 ~ 1.2 with the ratio of air intake outline diameter Φ 2.In the present embodiment, the throat diameter Φ 1 of intake grill 12 is 194mm.The air intake outline diameter Φ 2 of centrifugal impeller 20 is 191mm.The relation rationally arranged between the throat diameter Φ 1 of the intake grill 12 and air intake outline diameter Φ 2 of centrifugal impeller 20 makes the fluid entering centrifugal impeller 20 from intake grill 12 can comparatively flow evenly through blade 23, thus is beneficial to reduction noise.
In addition preferably, the ratio of the width C of spiral case 10 and the width H of centrifugal impeller 20 is 1.1 ~ 1.4.In the present embodiment, the width H of centrifugal impeller 20 is 200mm.The width C of spiral case is 241mm.The relation rationally arranged between the width C of spiral case 10 and the width H of centrifugal impeller 20 makes the fluid flowed out from centrifugal impeller 20 enter to flow after in spiral case 10 comparatively stable, thus is beneficial to reduction noise.
In addition, in the present embodiment, the external diameter Φ 3 of the blade ring 24 of centrifugal impeller 20 is 233mm.The outlet air end outline diameter Φ 4 of the blade 23 of centrifugal impeller 20 is 225mm.Distance B between the axial both sides intake grill 12 of spiral case 10 is 213mm.The thickness D of wheel disc 21 is 3.5mm.Length of blade G is 93.75mm.
The molded line of the spiral case main body 11 of spiral case 10 is made up of the first spiral case spline curve 111 seamlessly transitted and the second spiral case spline curve 112.The molded line rationally arranging spiral case 10 can make spiral case 10 inner fluid streams Dynamic stability, thus is beneficial to reduction noise.
The utility model embodiment also provides a kind of air-conditioner set, comprises aforesaid centrifugal blower assembly.
The above embodiment of the utility model optimizes the parameters such as spiral case size, spiral case inlet pressure; Optimize the parameter such as blades installation angle, vane type line, the number of blade of centrifugal impeller 20; Also optimize spiral case 10 and the matching gap of centrifugal impeller 20 and the dimensional fits relation of spiral case and centrifugal impeller 20.Verify by experiment, under identical operating conditions, the former machine of water-cooling case-type air-conditioner noise ratio of the centrifugal blower assembly of the present embodiment is adopted to reduce 7dB (A), wherein the reduction contribution of change to noise of the blades installation angle of centrifugal impeller 20 is the most outstanding, is about 5dB (A).
Finally should be noted that: above embodiment is only in order to illustrate that the technical solution of the utility model is not intended to limit; Although be described in detail the utility model with reference to preferred embodiment, those of ordinary skill in the field have been to be understood that: still can modify to embodiment of the present utility model or carry out equivalent replacement to portion of techniques feature; And not departing from the spirit of technical solutions of the utility model, it all should be encompassed in the middle of the technological scheme scope of the utility model request protection.
Claims (17)
1. a centrifugal impeller, comprise wheel disc (21) and be arranged at the blade (23) on described wheel disc (21), it is characterized in that, the stagger angle of described blade (23) is 90 ° ~ 120 °, and the exit installation angle of described blade (23) is 25 ° ~ 40 °.
2. centrifugal impeller according to claim 1, is characterized in that, the stagger angle of described blade (23) is 90 ° ~ 105 °, and the exit installation angle of described blade (23) is 32 ° ~ 38 °.
3. centrifugal impeller according to claim 1, is characterized in that, described blade (23) is reduced to blade tip (232) thickness gradually by root of blade (231).
4. centrifugal impeller according to claim 3, is characterized in that, the ratio of the thickness F of the blade tip (232) of described blade (23) and the thickness E of root of blade (231) is 0.35 ~ 0.7.
5. centrifugal impeller according to any one of claim 1 to 4, it is characterized in that, the stagger angle d of the root of blade (231) of described blade (23) is greater than the stagger angle f of the blade tip (232) of described blade (23), and the exit installation angle c of the root of blade (231) of described blade (23) is greater than the exit installation angle e of the blade tip (232) of described blade (23).
6. centrifugal impeller according to claim 5, it is characterized in that, the difference of the stagger angle f of the stagger angle d of the root of blade (231) of described blade (23) and the blade tip (232) of described blade (23) is-5 ° ~ 5 °, and the difference of the exit installation angle e of the exit installation angle c of the root of blade (231) of described blade (23) and the blade tip (232) of described blade (23) is-5 ° ~ 5 °.
7. centrifugal impeller according to any one of claim 1 to 4, it is characterized in that, the vane type line of described blade (23) by smooth connection the first blade spline curve (M1) and lay respectively at the second blade spline curve (M2) of described first blade spline curve (M1) both sides and Three-blade spline curve (M3) forms, described first blade spline curve (M1) is positioned at the inlet of described blade (23), described second blade spline curve (M2) is positioned at the front of described blade (23), described Three-blade spline curve (M3) is positioned at the back side of described blade (23).
8. centrifugal impeller according to any one of claim 1 to 4, it is characterized in that, described centrifugal impeller (20) is double-impeller, two groups of blades (23) are arranged at the both sides of described wheel disc (21) respectively, described two groups of blades (23) dislocation is arranged, the lobe numbers often organizing blade (23) is 41 ~ 61.
9. centrifugal impeller according to any one of claim 1 to 4, is characterized in that, the ratio of the width L of described blade (23) and the air intake outline diameter Φ 2 of described centrifugal impeller (20) is 5% ~ 15%.
10. a centrifugal blower assembly, comprise spiral case (10) and be arranged at the centrifugal impeller (20) in described spiral case (10), it is characterized in that, described centrifugal impeller (20) is centrifugal impeller according to any one of claim 1 to 9.
11. centrifugal blower assemblies according to claim 10, is characterized in that, the matching gap A between the intake grill (12) of described spiral case (10) and the end face of described centrifugal impeller (20) is 3mm ~ 15mm.
12. centrifugal blower assemblies according to claim 10, is characterized in that, described spiral case (10) has snail tongue (15), and the snail tongue radius R 1 of described snail tongue (15) is 3mm ~ 15mm.
13. centrifugal blower assemblies according to claim 10, it is characterized in that, the intake grill (12) of described spiral case (10) is convergent mouth, and the convergent curve of described convergent mouth is quarter circular arc, and the radius R 2 of described quarter circular arc is 10mm ~ 20mm.
14. centrifugal blower assemblies according to claim 10, is characterized in that, the exhaust outlet angle g of described spiral case (10) is 15 ° ~ 30 °.
15. centrifugal blower assemblies according to claim 10, it is characterized in that, the throat diameter Φ 1 of the intake grill (12) of described spiral case (10) is more than or equal to the air intake outline diameter Φ 2 of described centrifugal impeller (20), and described throat diameter Φ 1 is 1.0 ~ 1.2 with the ratio of described air intake outline diameter Φ 2.
16. centrifugal blower assemblies according to claim 10, is characterized in that, the ratio of the width C of described spiral case and the width H of described centrifugal impeller (20) is 1.1 ~ 1.4.
17. 1 kinds of air-conditioner set, comprise centrifugal blower assembly, it is characterized in that, described centrifugal blower assembly is for according to claim 10 to the centrifugal blower assembly according to any one of 16.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520032153.4U CN204532956U (en) | 2015-01-16 | 2015-01-16 | Centrifugal impeller, centrifugal fan assembly and air conditioning unit |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201520032153.4U CN204532956U (en) | 2015-01-16 | 2015-01-16 | Centrifugal impeller, centrifugal fan assembly and air conditioning unit |
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| CN204532956U true CN204532956U (en) | 2015-08-05 |
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| CN201520032153.4U Active CN204532956U (en) | 2015-01-16 | 2015-01-16 | Centrifugal impeller, centrifugal fan assembly and air conditioning unit |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104564803A (en) * | 2015-01-16 | 2015-04-29 | 珠海格力电器股份有限公司 | Centrifugal impeller, centrifugal fan assembly and air conditioning unit |
| CN105782076A (en) * | 2016-04-29 | 2016-07-20 | 浙江苏泊尔家电制造有限公司 | Centrifugal fan and kitchen ventilator |
| CN107288922A (en) * | 2017-07-13 | 2017-10-24 | 广东美的厨房电器制造有限公司 | Dislocation impeller and range hood used for range hood |
| CN110088482A (en) * | 2016-12-20 | 2019-08-02 | 三菱电机株式会社 | Multiple-wing fan |
| CN110566503A (en) * | 2019-10-10 | 2019-12-13 | 珠海格力电器股份有限公司 | centrifugal fan blade, centrifugal fan, air conditioner and transportation means |
| CN112377457A (en) * | 2020-10-13 | 2021-02-19 | 宁波方太厨具有限公司 | Impeller, centrifugal fan applying same and range hood |
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2015
- 2015-01-16 CN CN201520032153.4U patent/CN204532956U/en active Active
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104564803A (en) * | 2015-01-16 | 2015-04-29 | 珠海格力电器股份有限公司 | Centrifugal impeller, centrifugal fan assembly and air conditioning unit |
| CN105782076A (en) * | 2016-04-29 | 2016-07-20 | 浙江苏泊尔家电制造有限公司 | Centrifugal fan and kitchen ventilator |
| CN110088482A (en) * | 2016-12-20 | 2019-08-02 | 三菱电机株式会社 | Multiple-wing fan |
| US10907655B2 (en) | 2016-12-20 | 2021-02-02 | Mitsubishi Electric Corporation | Multiblade fan |
| CN107288922A (en) * | 2017-07-13 | 2017-10-24 | 广东美的厨房电器制造有限公司 | Dislocation impeller and range hood used for range hood |
| CN110566503A (en) * | 2019-10-10 | 2019-12-13 | 珠海格力电器股份有限公司 | centrifugal fan blade, centrifugal fan, air conditioner and transportation means |
| CN110566503B (en) * | 2019-10-10 | 2020-05-15 | 珠海格力电器股份有限公司 | Centrifugal fan blade, centrifugal fan, air conditioner and transportation means |
| CN112377457A (en) * | 2020-10-13 | 2021-02-19 | 宁波方太厨具有限公司 | Impeller, centrifugal fan applying same and range hood |
| CN112377457B (en) * | 2020-10-13 | 2021-12-17 | 宁波方太厨具有限公司 | Impeller, centrifugal fan applying same and range hood |
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