CN109209990A - Cross-flow fan blade, cross-flow fan and air conditioner - Google Patents
Cross-flow fan blade, cross-flow fan and air conditioner Download PDFInfo
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- CN109209990A CN109209990A CN201811259976.5A CN201811259976A CN109209990A CN 109209990 A CN109209990 A CN 109209990A CN 201811259976 A CN201811259976 A CN 201811259976A CN 109209990 A CN109209990 A CN 109209990A
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- 238000010586 diagram Methods 0.000 description 10
- 238000013461 design Methods 0.000 description 5
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- 238000012360 testing method Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 235000013399 edible fruits Nutrition 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
Classifications
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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
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
-
- 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
-
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/663—Sound attenuation
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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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention provides a cross-flow fan blade, a cross-flow fan and an air conditioner. The cross-flow fan blade comprises a wheel disc and a plurality of blades distributed on the wheel disc, wherein each blade is provided with a far-end point and a near-end point, the far-end points of the blades are all positioned on a first circle with the rotation axis O of the cross-flow fan blade as the circle center, and the minimum distance between the near-end point of each blade and the rotation axis O is different. According to the cross-flow fan blade, the cross-flow fan and the air conditioner, noise generated when the cross-flow fan blade rotates can be obviously reduced.
Description
Technical field
The invention belongs to air-conditioning technique fields, and in particular to a kind of through-flow fan blade, cross flow fan, air conditioner.
Background technique
Existing through-flow fan blade includes the multiple blades being circumferentially arranged, and air-flow flows through direction such as Fig. 1 institute in the running
Show, air-flow flows through the inside air duct of through-flow fan blade along the dotted line in A in Fig. 1 to B point direction, that is, first air-flow by air duct into
Mouth side enters through-flow fan blade (air-flow passes through impeller clearance from periphery and enters inside through-flow fan blade (a1-a2)), and later, air-flow is again
By blade close to through-flow fan blade axis side far from flow out the through-flow fan blade towards ducting outlet side, (namely air-flow is by passing through
Impeller clearance, which is passed through, inside stream fan blade flow to peripheral (a3-a4)), it is seen then that the both ends of blade (namely blade is close to and far from through-flow
The both ends of fan blade axis are respectively defined as proximal points, remote point) not only it has been inlet end but also has been outlet side.It is again as shown in Fig. 2, existing
Through-flow fan blade on each blade arranged on the circumference in the axle center of opposite through-flow fan blade, and the proximal points of each blade and distal end
Point is all on the identical circle of a radius, as R1 is the inner circle radius of median segment of cross-flow fan blade end cap, the inner area of R < R1 in Fig. 2
Domain is the circulation part of through-flow fan blade；R2 is through-flow blade inscribed radius (i.e. proximal points radius), and R3 is through-flow blade circumscribed half
Diameter (i.e. remote point radius), R4 are circumcircle in the outer diameter of through-flow fan blade end cap namely each blade of existing through-flow fan blade
On same circle namely each blade of through-flow fan blade rotates in a circumferential direction arrangement around fan blade rotating shaft center point, and form parameter is consistent,
With same position point on blade and rotating shaft center's point line, the angle of two neighboring line is blade pitgh angle β.
The angle value distribution situation of the blade pitgh angle β in through-flow fan blade between each blade in the prior art of table 1
| Blade serial number | 1 | 2 | 3 | 4 | 5 | 6 | 7 |
| β/° | 10.63 | 12.35 | 8.3 | 12.44 | 9.71 | 9 | 11.5 |
| Blade serial number | 8 | 9 | 10 | 11 | 12 | 13 | 14 |
| β/° | 9.86 | 10.33 | 9.63 | 9.25 | 11.22 | 12.6 | 10.48 |
| Blade serial number | 15 | 16 | 17 | 18 | 19 | 20 | 21 |
| β/° | 10.17 | 10.86 | 10 | 10.54 | 11.19 | 10.34 | 9.17 |
| Blade serial number | 22 | 23 | 24 | 25 | 26 | 27 | 28 |
| β/° | 9.66 | 9.02 | 10.52 | 9.67 | 9.88 | 10.64 | 10.12 |
| Blade serial number | 29 | 30 | 31 | 32 | 33 | 34 | 35 |
| β/° | 8.78 | 11.33 | 11.06 | 10.65 | 11.19 | 9.3 | 8.65 |
Existing through-flow fan blade design generates the rotation under blade passing frequency from noise point, when fan blade being avoided to rotate
Noise peak, therefore the blade pitgh angle β for using unequal spacing is designed namely β is the underrange (angle that such as table 1 provides
Value), but to result in the acting of each different leaves runner (being formed between adjacent blades) inconsistent for this processing mode, leads to through-flow
The outlet air of fan blade is uneven, and pressure oscillation is larger in flow field, and broadband noise is larger.
Summary of the invention
It therefore, can the technical problem to be solved in the present invention is that providing a kind of through-flow fan blade, cross flow fan, air conditioner
It is substantially reduced noise when through-flow fan blade rotation.
To solve the above-mentioned problems, the present invention provides a kind of through-flow fan blade, including wheel disc and is distributed on the wheel disc
Multiple blades, the blade have remote point and proximal points, and on the axis projection of the through-flow fan blade, multiple blades respectively have
Some remote points are all in using the axis of rotation O of the through-flow fan blade as on first circle in the center of circle, and the multiple blade is respectively
The minimum spacing of the proximal points and the axis of rotation O that have differs.
Preferably, first radius of circle is R3, the proximal points of any one blade in the multiple blade with it is described
Minimum spacing between axis of rotation O is Rx, Rx=0.8 × m × R3, wherein 0.8≤m≤1.2.
Preferably, the wheel disc has a first end face being oppositely arranged, second end face in the axial direction, the first end face and
Or second end face is equipped with mass balance block, so that the through-flow fan blade is when rotated at the mass balance point of the through-flow fan blade
In in the rotary shaft of the through-flow fan blade.
Preferably, the line of any one blade has in the multiple blade proximal points and O point is First Line, with institute
The line for stating proximal points that the adjacent blade of any one blade has and O point is the second line, the First Line and second linear
At blade pitgh angle β, the β in the multiple blade between two blades of arbitrary neighborhood is equal.
Preferably, the line of the remote point of any one blade and O point forms third line, the First Line with it is described
Cornerite γ is formed between third line, the γ is definite value.
Preferably, the straightway between the remote point and the proximal points forms the chord length Lx, Lx=of the blade
0.24 × n × R3, wherein 0.8≤n≤1.2.
Preferably, the wheel disc has internal flow bore, and the radius of the internal flow bore is R1, COS (λ)=(R12+
Rx2-Lx2)/(2×R1×Rx)。
The present invention also provides a kind of cross flow fans, including above-mentioned through-flow fan blade.
The present invention also provides a kind of air conditioners, including above-mentioned cross flow fan.
A kind of through-flow fan blade provided by the invention, cross flow fan, air conditioner, due to the multiple blade respectively have it is close
The proximal points that the minimum spacing of endpoint and the axis of rotation O differ namely the multiple blade respectively has are not at institute
It states on any one circumference that axis of rotation O is the center of circle, that is, having the through-flow fan blade does not wait blades inscribed circle radius
Design structure, this can make air-flow flow through formed between two blades of arbitrary neighborhood it is inconsistent by frequency, thus
Prevent the generation of rotational noise phenomenon caused by through-flow fan blade passes through frequency unanimously due to air-flow in the prior art.
Detailed description of the invention
Fig. 1 is the airflow schematic diagram of through-flow fan blade in the prior art；
Fig. 2 is the axis projection schematic diagram of through-flow fan blade in the prior art；
Fig. 3 is the axis projection schematic diagram (embodying unequal inscribed circle radius) of the through-flow fan blade of the embodiment of the present invention；
Fig. 4 is the axis projection schematic diagram (embodying blade pitgh angle) of the through-flow fan blade of the embodiment of the present invention；
Fig. 5 is the axis projection schematic diagram (embodying subtended angle of blade) of the through-flow fan blade of the embodiment of the present invention；
Fig. 6 is the flow field monitoring point arrangement schematic diagram carried out using through-flow fan blade of the invention；
Fig. 7 is relative velocity comparison diagram on foreign aid's week of the through-flow fan blade of the embodiment of the present invention；
Fig. 8 is the pressure fluctuation comparison diagram of P1 point in Fig. 6；
Fig. 9 is the pressure fluctuation comparison diagram of P2 point in Fig. 6；
Figure 10 is the pressure fluctuation comparison diagram of P3 point in Fig. 6.
Appended drawing reference indicates are as follows:
1, wheel disc；11, internal flow bore；2, blade；21, remote point；22, proximal points；3, the first circle.
Specific embodiment
In conjunction with referring to shown in Fig. 1 to Figure 10, according to an embodiment of the invention, provide a kind of through-flow fan blade, including wheel disc 1 and
The multiple blades 2 being distributed on the wheel disc 1, the blade 2 has remote point 21 and proximal points 22, in the through-flow fan blade
On axis projection, the remote point 21 that multiple blades 2 respectively have is all in using the axis of rotation O of the through-flow fan blade as the center of circle
On first circle 3, and the minimum spacing of the proximal points 22 and axis of rotation O that respectively has of the multiple blade 2 is (namely existing
Inscribed circle radius in technology) it differs, it is to be understood that remote point 21 above-mentioned refers to rotation described in distance on the blade 2
Shaft heart O farthest point, and the proximal points 22 then mutually should be the point that axis of rotation O described in distance is nearest on the blade 2.
In the technical solution, the minimum spacing of the proximal points 22 and the axis of rotation O that respectively have due to the multiple blade 2 is not
Deng namely the proximal points 22 that respectively have of the multiple blade 2 be not at any one circle using the axis of rotation O as the center of circle
Zhou Shang, that is, the through-flow fan blade is made to have the design structure for not waiting blades inscribed circle radius, this can be such that air-flow flows through arbitrarily
Formed between the blade 2 of adjacent two it is inconsistent by frequency, thus prevent in the prior art through-flow fan blade due to gas
The generation of rotational noise phenomenon caused by overfrequency circulate unanimously.
A kind of optimization range as spacing between the proximal points 22 and the axis of rotation O, it is preferable that described first
3 radiuses of circle are R3, the minimum between the proximal points 22 and the axis of rotation O of any one blade 2 in the multiple blade 2
Spacing is Rx, Rx=0.8 × m × R3, wherein 0.8≤m≤1.2, at this point, the Rx is limited in relatively reasonable range,
Not only improving prevents air-flow by the consistent of frequency, and can preferably be guided air-flow.
It is understood that since the remote point 21 of the blade 2 is consistent with the spacing of axis of rotation O, and proximal points 22
There is also variations with the spacing of axis of rotation O, this will likely have an adverse effect to the dynamic balancing of the through-flow fan blade of rotation, because
This, it is preferable that the wheel disc 1 has the first end face, the second end face that are oppositely arranged in the axial direction, the first end face and/or
Second end face is equipped with mass balance block, so that the mass balance point of the through-flow fan blade through-flow fan blade when rotated is in
In the rotary shaft of the through-flow fan blade, that is, ensure that the dynamic balancing of the through-flow fan blade when rotated, prevent due to dynamic balancing
Bad bring noise and to through-flow fan blade structural damage itself.
Further, the line of any one blade 2 has in the multiple blade 2 proximal points 22 and O point is the
The line of one line, proximal points 22 that the blade 2 adjacent with any one blade 2 has and O point is the second line, described first
Line and the second line form blade pitgh angle β, and the β in the multiple blade 2 between two blades 2 of arbitrary neighborhood is equal,
That is, the multiple blade 2 blade pitgh angle having the same, this can reduce through-flow fan blade outlet since pressure fluctuation is big and
The broadband noise of generation, more specifically, etc. blade pitghs angle design can reduce cross flow fan outlet pressure fluctuation,
To which the broadband noise of through-flow fan blade or cross flow fan be effectively reduced, and the outlet air of the through-flow fan blade can be made more equal
It is even.
The remote point 21 of any one blade 2 and the line of O point form third line, the First Line and the third
Cornerite γ is formed between line, the γ is definite value, and the γ is the acting ability that definite value can guarantee the through-flow fan blade, simultaneously
It is also the key factor for guaranteeing the air quantity of cross flow fan.It is understood that when the cornerite γ is definite value, due to the leaf
The Rx of piece 2 is different, and chord length Lx, blade outer circle flow angle α 1, the blade inner circle flow angle α 2 of blade can carry out appropriate set
Meter, thus finally determine the blade profile of the blade 2, and the value of the chord length Lx of the final pump motor set as the blade 2
Design is then particularly important, and by the work such as largely testing, emulating, analyze, verify, is finally obtained between the Lx and R3
Relationship be Lx=0.24 × n × R3, wherein 0.8≤n≤1.2, it should be noted that the remote point 21 and the proximal end
Straightway between point 22 forms the chord length Lx of the blade 2.
Further, the wheel disc 1 has internal flow bore 11, and the radius of the internal flow bore 11 is R1, COS
(λ)=(R12+Rx2-Lx22 × R1 of)/(× Rx), under such interrelational form, the noise of the through-flow fan blade or even cross flow fan
It is horizontal lower.
In a specific embodiment, the value of the Rx is as shown in table 2, specifically, giving one in table 2 has 35
The through-flow fan blade of a blade 2.
The comparative example of the Rx in a specific embodiment of table 2
| Serial number | 1 | 2 | 3 | 4 | 5 | 6 | 7 |
| Inner diameter size (mm) | 32.31 | 32.99 | 32.05 | 32.32 | 32.31 | 32.94 | 32.58 |
| Serial number | 8 | 9 | 10 | 11 | 12 | 13 | 14 |
| Inner diameter size (mm) | 33.18 | 32.94 | 32.66 | 32.89 | 32.55 | 32.35 | 32.35 |
| Serial number | 15 | 16 | 17 | 18 | 19 | 20 | 21 |
| Inner diameter size (mm) | 33.26 | 32.94 | 32.58 | 32.35 | 32.38 | 32.49 | 32.05 |
| Serial number | 22 | 23 | 24 | 25 | 26 | 27 | 28 |
| Inner diameter size (mm) | 32.32 | 33.11 | 33.03 | 33.26 | 32.89 | 32.35 | 33.1 |
| Serial number | 29 | 30 | 31 | 32 | 33 | 34 | 35 |
| Inner diameter size (mm) | 32.38 | 32.99 | 33.36 | 32.4 | 32.79 | 33.14 | 32.49 |
Related analogue simulation and experiment test are carried out, obtains, uses the air quantity of through-flow fan blade of the invention for 420m3/h、
Noise level be 43.2dB (corresponding power 27.2W), and use the corresponding air quantity of through-flow fan blade in the prior art for
432m3/ h, noise level are 44.5dB (corresponding power 28.1W), can with it is clear that through-flow fan blade of the invention with it is existing
Through-flow fan blade in technology is suitable on air quantity, and noise level is then effectively reduced.Pass through analogue simulation fan blade outer circle phase
To velocity variations, Fig. 7 is obtained, it can be seen that its fluctuation slows down, and equally illustrates through-flow fan blade of the present invention compared to the prior art
Fan blade noise decrease that (solid line represents response curve in the prior art in Fig. 7, and dotted line represents corresponding song of the invention
Line).
In order to verify the equidistant leaf angle bring effect being designed as unequal spacing in the prior art in the present invention
Fruit, as shown in fig. 6, determining that three points (respectively P1, P2, P3) carry out emulation mould to the flow field exits side of the through-flow fan blade
It is quasi- to monitor its amplitude of pressure fluctuation and corresponding broadband noise ability, by Fig. 8-10 it can clearly be seen that in the position of P1, P2, P3
It sets, pressure fluctuation is effectively controlled namely pressure fluctuation is substantially reduced that (in Fig. 8~10, solid line represents in the prior art
Response curve, dotted line represent response curve of the invention), broadband noise energy is reduced.According to an embodiment of the invention, also
A kind of cross flow fan is provided, including above-mentioned through-flow fan blade, noise when through-flow fan blade rotation can be substantially reduced.
According to an embodiment of the invention, also providing a kind of air conditioner, including above-mentioned cross flow fan, it can be substantially reduced and pass through
Flow noise when fan blade rotation.
Those skilled in the art will readily recognize that above-mentioned each advantageous manner can be free under the premise of not conflicting
Ground combination, superposition.
The above is merely preferred embodiments of the present invention, be not intended to limit the invention, it is all in spirit of the invention and
Made any modifications, equivalent replacements, and improvements etc., should all be included in the protection scope of the present invention within principle.Above only
It is the preferred embodiment of the present invention, it is noted that for those skilled in the art, do not departing from this hair
Under the premise of bright technical principle, several improvements and modifications can also be made, these improvements and modifications also should be regarded as guarantor of the invention
Protect range.
Claims (9)
1. a kind of through-flow fan blade, which is characterized in that including wheel disc (1) and the multiple blades (2) being distributed on the wheel disc (1),
The blade (2) has remote point (21) and proximal points (22), on the axis projection of the through-flow fan blade, multiple blades (2)
The remote point (21) respectively having all is in be justified on (3) using the axis of rotation O of the through-flow fan blade as the first of the center of circle, and described
The minimum spacing of proximal points (22) and the axis of rotation O that multiple blades (2) respectively have differs.
2. through-flow fan blade according to claim 1, which is characterized in that the first circle (3) radius is R, the multiple leaf
Minimum spacing between the proximal points (22) and the axis of rotation O of any one blade (2) in piece (2) is Rx, Rx=0.8
× m × R3, wherein 0.8≤m≤1.2.
3. through-flow fan blade according to claim 1, which is characterized in that the wheel disc (1) has in the axial direction to be oppositely arranged
First end face, second end face, the first end face and/or second end face are equipped with mass balance block, so that the through-flow fan blade
The mass balance point of the through-flow fan blade is in the rotary shaft of the through-flow fan blade when rotated.
4. through-flow fan blade according to claim 1, which is characterized in that any one blade (2) in the multiple blade (2)
The line of the proximal points (22) and O point that have is First Line, and adjacent blade (2) has with any one blade (2)
The line of proximal points (22) and O point is the second line, and the First Line and the second line form blade pitgh angle β, the multiple leaf
β in piece (2) between two blades (2) of arbitrary neighborhood is equal.
5. through-flow fan blade according to claim 4, which is characterized in that the remote point (21) of any one blade (2)
Third line is formed with the line of O point, forms cornerite γ between the First Line and the third line, the γ is definite value.
6. through-flow fan blade according to claim 1, which is characterized in that the remote point (21) and the proximal points (22) it
Between straightway form chord length Lx, Lx=0.24 × n × R3 of the blade (2), wherein 0.8≤n≤1.2.
7. through-flow fan blade according to claim 5, which is characterized in that the wheel disc (1) has internal flow bore (11), institute
The radius for stating internal flow bore (11) is R1,
COS (λ)=(R12+Rx2-Lx2)/(2×R1×Rx)。
8. a kind of cross flow fan, including through-flow fan blade, which is characterized in that the through-flow fan blade is any one of claims 1 to 7
The through-flow fan blade.
9. a kind of air conditioner, including cross flow fan, which is characterized in that the cross flow fan is through-flow wind according to any one of claims 8
Machine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811259976.5A CN109209990B (en) | 2018-10-26 | 2018-10-26 | Cross-flow fan blade, cross-flow fan and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811259976.5A CN109209990B (en) | 2018-10-26 | 2018-10-26 | Cross-flow fan blade, cross-flow fan and air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN109209990A true CN109209990A (en) | 2019-01-15 |
| CN109209990B CN109209990B (en) | 2024-07-02 |
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ID=64997156
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811259976.5A Active CN109209990B (en) | 2018-10-26 | 2018-10-26 | Cross-flow fan blade, cross-flow fan and air conditioner |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111396356A (en) * | 2020-04-20 | 2020-07-10 | 宁波奥克斯电气股份有限公司 | Impeller assembly and air conditioner |
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| JP2012067768A (en) * | 2012-01-12 | 2012-04-05 | Mitsubishi Electric Corp | Cross-flow fan, blower, and air conditioner |
| CN206917925U (en) * | 2017-06-30 | 2018-01-23 | 广东美的环境电器制造有限公司 | Tubular wine wheel and warm-air drier |
| CN208935012U (en) * | 2018-10-26 | 2019-06-04 | 珠海格力电器股份有限公司 | Cross-flow fan blade, cross-flow fan and air conditioner |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111396356A (en) * | 2020-04-20 | 2020-07-10 | 宁波奥克斯电气股份有限公司 | Impeller assembly and air conditioner |
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