CN103362858A - Axial flow blower - Google Patents
Axial flow blower Download PDFInfo
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- CN103362858A CN103362858A CN2013101059629A CN201310105962A CN103362858A CN 103362858 A CN103362858 A CN 103362858A CN 2013101059629 A CN2013101059629 A CN 2013101059629A CN 201310105962 A CN201310105962 A CN 201310105962A CN 103362858 A CN103362858 A CN 103362858A
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- impeller
- axial flow
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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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
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Abstract
The invention provides an axial flow blower which generates low noise. The axial flow blower has a hub (2) which rotates around the axis and an impeller (1) which is disposed on multiple fins (3) on the periphery of the hub. Every fin has a bending area (36) which smoothly bends towards an upstream side of the main stream of the fluid near a peripheral end portion. In a plane expanded view of a cylindrical cross section which takes a rotation shaft of the impeller as the center, the length of a straight line that a front rim end (31) and a rear rim end (32) of an adjacent fin ahead in the rotation direction of the fin is determined as H; the diameter of the impeller is determined as D; the ratio (1/t) of the length (1) of a fin string (37) which is the straight line linking the front rim end (31) of the fin and the rear rim end (32) of the fin to the fin pitch distance (t) which is the distance between two adjacent fins is determined as chord-pitch ratio [sigma]; an angle formed by the rotation shaft of the impeller and the fin string (37) is an oblique angle [gamma], and the bending area (36) satisfies 0<H/D<0.35, 0.72<[sigma]<0.91, and 60 DEG<[gamma]<66 DEG.
Description
Technical field
The present invention relates to the axial flow fan of usefulness such as air-conditioning, air regenerating device.
Background technique
Up to the present, as the technology of the noise that reduces axial flow fan, known have following such technology.Namely, arrange to the little fin of fluid main flow direction inclination by the periphery edge at blade, suitably form the shape of the periphery edge of blade, suppress the generation of end of blade eddy current, reduce the noise (for example, with reference to patent documentation 1) that produces because of the interference with horn mouth or blade.
Patent documentation 1: Japanese kokai publication hei 6-173895 communique (the 5th page, Fig. 1)
In the technology of above-mentioned patent documentation 1 record, arrange to the little fin of fluid main flow direction inclination by the peripheral end at fin (blade), suitably form the shape of the peripheral end of fin, suppress the generation of fin end eddy current.But, the effective flow path width between the fin that can't guarantee fully can reduce owing to fin end eddy current, mobile resistance increment, mobile disorder increases, so exist noise to increase such problem points.
Summary of the invention
The present invention proposes in order to solve the above problems a little, and its purpose is, a kind of axial flow fan of low noise is provided.
Axial flow fan of the present invention possesses impeller, this impeller has the wheel hub that rotates around the axle center, a plurality of fins with the peripheral part that is equipped on above-mentioned wheel hub, above-mentioned fin has near peripheral end to the upstream side of fluid main flow crooked bending area sleekly, in the plane outspread drawing of the cylinder section centered by the running shaft of above-mentioned impeller, link the front acies of above-mentioned fin and the length with the straight line of the rear acies of its adjacent above-mentioned fin is H in sense of rotation the place ahead of this fin, the diameter of above-mentioned impeller is D, in the above-mentioned plane outspread drawing, the straight line that links the rear acies of the front acies of above-mentioned fin and this fin is that the interval of length l and the adjacent above-mentioned fin of fin string is that the ratio (l/t) of fin pitch t is chord-pitch ratio σ, when the angle that the running shaft of above-mentioned impeller becomes with above-mentioned fin string is oblique angle γ, at above-mentioned bending area, constitute and satisfy 0＜H/D＜0.35,0.72＜σ＜0.91, and 60 °＜γ＜66 °.
The present invention satisfies 0＜H/D＜0.35,0.72＜σ＜0.91 and 60 °＜γ＜66 ° by fin is constituted at bending area, can fully guarantee finned length and not reduce effective work done, can fully guarantee the effective flow path width between fin, can reduce mobile resistance, suppress mobile disorder, can reduce noise.
Description of drawings
Fig. 1 is the stereogram of the axial flow fan of embodiments of the present invention 1.
Fig. 2 is the plan view of the axial flow fan of embodiments of the present invention 1.
Fig. 3 is the plane outspread drawing in the I-I cross section among Fig. 2 of axial flow fan of embodiments of the present invention 1.
Fig. 4 is the plotted curve of expression chord-pitch ratio and reducing noise the relationship between quantities.
Fig. 5 is the plotted curve of expression oblique angle and reducing noise the relationship between quantities.
Fig. 6 is the projection drawing of II-II cross section on the plane that comprises running shaft among Fig. 2 of axial flow fan of embodiments of the present invention 2.
Fig. 7 is the plotted curve of expression top rake and reducing noise the relationship between quantities.
Fig. 8 is the projection drawing of II-II cross section on the plane that comprises running shaft among Fig. 2 of axial flow fan of embodiments of the present invention 3.
Fig. 9 is the projection drawing of II-II cross section on the plane that comprises running shaft among Fig. 2 of axial flow fan of embodiments of the present invention 4.
Figure 10 is the plotted curve of expression crooked beginning Length Ratio and reducing noise the relationship between quantities.
Figure 11 is the plotted curve of expression δ zw * α and reducing noise the relationship between quantities.
The explanation of reference character
1 impeller, 2 wheel hubs, 3 fins, 3a benchmark fin, 3b the place ahead fin, 4 fin end eddy current, 31 front acies, 32 rear acies, 33 interior Zhou Duan, 34 outer circumference end, 35 crooked initial positions, 36 bending areas, 37 fin strings, 38 fin string central points, 39 fin mid-chord lines.
Embodiment
Below, be used for implementing mode of the present invention with reference to description of drawings.In addition, for the reference character in Fig. 1～Figure 11, the member that has marked identical reference character is identical or suitable with this member member, and this is general in the full text of specification.In addition, for a plurality of fins, only representational 1 fin has been marked reference character.In addition, in order to implement in the mode of the present invention, the number that illustrates fin as an example is 5 situation, but for the number of the fins beyond 5, also can obtain effect of the present invention.
Mode of execution 1
Fig. 1～Fig. 3 is the figure for the axial flow fan that embodiments of the present invention 1 are described.Particularly, Fig. 1 is the stereogram of the axial flow fan of embodiments of the present invention 1, Fig. 2 is the plan view of the axial flow fan of embodiments of the present invention 1, and Fig. 3 is the plane outspread drawing in the I-I cross section among Fig. 2 of axial flow fan of embodiments of the present invention 1.
As depicted in figs. 1 and 2, the axial flow fan of embodiments of the present invention 1 has impeller 1, and this impeller 1 is made of the wheel hub 2 that rotates around the axle center and a plurality of fins 3 that are equipped on the peripheral part of above-mentioned wheel hub 2.Fin 3 is centered on by front acies 31, rear acies 32, interior all ends 33, outer circumference end 34.Fin 3 has to the upstream side of fluid main flow (air-flow) crooked bending area 36 sleekly near the peripheral end of the outer circumferential side of crooked initial position 35.
Then, describe with Fig. 3.In Fig. 3, for the context of clear and definite a plurality of fins 3, when making arbitrarily fin 3 for benchmark fin 3a, fin 3 souvenirs that will be adjacent in sense of rotation the place ahead from it are the place ahead fin 3b.As shown in Figure 3, in the plane outspread drawing of the cylinder section centered by the running shaft of impeller 1, be H in the length of the straight line of the rear acies 32 that makes the front acies 31 that links benchmark fin 3a and the place ahead fin 3b, when making the diameter of impeller 1 be D, at bending area 36, constitute 0＜H/D＜0.35.And, in this plane outspread drawing, the ratio l/t that at the interval of the length l of the fin string 37 that makes the front acies 31 that links fin 3 and rear acies 32 and adjacent fin 3 is fin pitch t is chord-pitch ratio σ, when making the axial line of the running shaft of impeller 1 be oblique angle γ with the angle of 37 one-tenth on fin string, at bending area 36, constitute and satisfy 0.72＜σ＜0.91, and 60 °＜γ＜66 °.
Then, the effect that obtains that consists of by as described above is described.Upstream side is crooked sleekly at bending area 36 by fin 3, the eddy current of fin end eddy current 4 big or small suppressed, but fin end eddy current 4 integral body are side shifting upstream, and stenosis is little in fact with the interval of fin end eddy current 4 (effectively flow path width) for adjacent fin 3.Satisfy 0.72＜σ＜0.91 by constituting at bending area 36, and 60 °＜γ＜66 °, can fully guarantee the length of fin 3 and not reduce effective work done, enlarge adjacent fin 3 and fully guarantee effective flow path width with the interval of fin end eddy current 4, can reduce mobile resistance, suppress mobile disorder, thereby can reduce noise.
Then, with Fig. 4 and Fig. 5 chord-pitch ratio σ and oblique angle γ and reducing noise the relationship between quantities are described.Fig. 4 is the plotted curve of expression chord-pitch ratio and reducing noise the relationship between quantities, and Fig. 5 is the plotted curve of expression oblique angle and reducing noise the relationship between quantities.Here, the reducing noise scale is shown in the axial flow fan (for example technology of patent documentation 1) that makes in the past and is the reduction amount of the relative noise of axial flow fans in the situation of 0dB, embodiments of the present invention 1.In Fig. 4, as an example, expression oblique angle γ is that 63.5 °, top rake δ z described later are that 9 °, crooked beginning Length Ratio α described later are 0.7, the value of δ zw * α described later is 2.3 o'clock plotted curve.In addition, plotted curve with respect to graphical pointv with 2 curve approximations roughly, but in chord-pitch ratio and reducing noise the relationship between quantities, approximately in this wise can't harm appropriate property.As can be seen from Figure 4, in the scope of 0.72＜σ＜0.91, can obtain the above reducing noise amount of 1dB degree, have significant reducing noise effect.Particularly in σ=0.83 o'clock, can obtain the reducing noise amount of 2.2dB.In Fig. 5, as an example, expression chord-pitch ratio σ is 0.83, top rake δ z described later is that 9 °, crooked beginning Length Ratio α described later are 0.7, the value of δ zw * α described later is 2.3 o'clock plotted curve.In addition, plotted curve with respect to graphical pointv with 2 curve approximations roughly, but in oblique angle and reducing noise the relationship between quantities, approximately in this wise can't harm appropriate property.As can be seen from Figure 5, in the scope of 60 °＜γ＜66 °, can obtain the above reducing noise amount of 1dB, have obvious reducing noise effect.From Fig. 4 and Fig. 5 as can be known, at chord-pitch ratio σ be 0.83, the reducing noise effect was the highest when oblique angle γ was 63.5 °, and the reducing noise amount becomes 5dB.During particularly in γ=63.5 °, can obtain the reducing noise amount of 3dB.
As described above in present embodiment 1, by at bending area 36, fin 3 is constituted satisfy 0＜H/D＜0.35,0.72＜σ＜0.91 and 60 °＜γ＜66 °, can fully guarantee finned length and not reduce effective work done, enlarge fin 3 and fully guarantee effective flow path width with the interval of fin end eddy current 4, can reduce mobile resistance, suppress mobile disorder, thereby can reduce noise.
Mode of execution 2
In order to realize further reducing noise, preferred formation as described below.Fig. 6 is the projection drawing of II-II cross section on the plane that comprises running shaft among Fig. 2 of axial flow fan of embodiments of the present invention 2.The II-II cross section of Fig. 2 be take the center of fin string 37 as fin string central point 38(with reference to Fig. 3), comprise all end 33 cross sections each fin string central point 38, parallel with running shaft to outer circumference end 34 of interior week from fin 3.In Fig. 6, make interior week end 33 each the fin string central point 38 to outer circumference end 34 that link from fin 3, and the straight line or the curve that project on the plane of the running shaft that comprises impeller 1 are fin mid-chord line 39.As shown in Figure 6, with fin mid-chord line 39 and the angle that becomes with the vertical plane of the running shaft of impeller 1, with respect to this plane towards the direction of upstream side for just, be defined as top rake δ z.At this moment, in interior all sides of bending area 36, top rake δ z constitutes and satisfies 5 °＜δ z＜40 °.
Then, the effect that consists of acquisition by as described above is described.In the excessively large situation of top rake δ z, the flowing of outer circumferential side towards the downstream side of fin 3 promoted terrifically, outer circumference end 34 from the fin downstream side upstream the air-flow rolled of side increase, the generation scale of fin end eddy current 4 increases.On the other hand, in the excessively little situation of top rake δ z, to stagnate terrifically towards the flowing of outer circumferential side in the downstream side of fin 3, the upstream side of outer circumference end 34 and the pressure difference in downstream side increase, because this excessive pressure difference, the generation scale of fin end eddy current 4 increases.Constitute by top rake δ z and to satisfy 5 °＜δ z＜40 °, owing to can suppress most effectively can suppress the generation scale of fin end eddy current, so can more reduce noise towards the flowing of the outer circumferential side in the downstream side of fin 3.
Then, with Fig. 7 top rake δ z and reducing noise the relationship between quantities are described.Fig. 7 is expression top rake and reducing noise the relationship between quantities plotted curve.In Fig. 7, as an example, expression chord-pitch ratio σ is 0.83, oblique angle γ is that 63.5 °, crooked beginning Length Ratio α described later are 0.7, the value of δ zw * α described later is 2.3 o'clock plotted curve.In addition, plotted curve with respect to graphical pointv with 2 curve approximations roughly, but in top rake and reducing noise the relationship between quantities, approximately in this wise can't harm appropriate property.As can be seen from Figure 7, in the scope of 5 °＜δ z＜40 °, can obtain the above reducing noise amount of 5dB, have obvious reducing noise effect.In the time of δ z=9 °, can obtain the reducing noise effect of 5.1dB, in the time of δ z=30 °, can obtain the reducing noise effect of 6.6dB.
As described above in present embodiment 2, by the interior all sides at bending area 36, fin 3 is constituted satisfy 5 °＜δ z＜40 °, owing to can effectively suppress flowing towards the outer circumferential side in the downstream side of fin 3, the generation scale that can suppress fin end eddy current 4 is so can more reduce noise.
Mode of execution 3
As the other mode of execution of be used for realizing with the equal reducing noise of the axial flow fan of above-mentioned mode of execution 2, just like the axial flow fan of following such formation.Fig. 8 is the projection drawing of II-II cross section on the plane that comprises running shaft among Fig. 2 of axial flow fan of embodiments of the present invention 3.The II-II cross section of Fig. 2 be take the center of fin string 37 as fin string central point 38(with reference to Fig. 3), comprise all end 33 cross sections each fin string central point 38, parallel with running shaft to outer circumference end 34 of interior week from fin 3.In Fig. 8, make interior week end 33 each the fin string central point 38 to outer circumference end 34 that link from fin 3, and the straight line or the curve that project on the plane of the running shaft that comprises impeller 1 are fin mid-chord line 39.As shown in Figure 8, in present embodiment 3, with tangent line and the angle that becomes with the vertical plane of the running shaft of impeller 1 of fin mid-chord line 39, with respect to this plane towards the direction of upstream side for just, be defined as top rake δ z.At this moment, in interior all sides of bending area 36, top rake δ z constitutes and satisfies 5 °＜δ z＜40 °.Identical with mode of execution 2 by as described above the effect that consists of acquisition.
Mode of execution 4
In order to realize further reducing noise, preferred formation as described below.Fig. 9 is the projection drawing of II-II cross section on the plane that comprises running shaft among Fig. 2 of axial flow fan of embodiments of the present invention 4.In Fig. 9, take the fin 3 of the radial direction of impeller 1 from interior week end 33 to the length of span of outer circumference end 34 as L, take the length of the crooked initial position 35 from interior week end 33 to bending area 36 beginnings of fin 3 as Lw, ratio between two L/Lw is defined as crooked beginning Length Ratio α.In addition, in Fig. 9, make interior week end 33 each the fin string central point 38 to outer circumference end 34 that link from fin 3, and the straight line or the curve that project on the plane of the running shaft that comprises impeller 1 are fin mid-chord line 39.And, the difference of the top rake of the top rake of the outer circumference end 34 of fin 3 and crooked initial position 35 is defined as δ zw.That is, with the angle that the straight line of the initial position of the straight line that links the outer circumference end of fin mid-chord line 39 and interior Zhou Duan and the bending area 36 of binding fin mid-chord line 39 and interior Zhou Duan becomes, be defined as the difference δ zw of top rake.At this moment, constitute and satisfy 0.6＜α＜0.95, and 1/ α＜δ zw＜6/ α.
Then, the effect that consists of acquisition by as described above is described.Because the round and smooth curved shape of the upstream side of the bending area 36 of fin 3 is fit to the shape of fin end eddy current 4, can make the stabilization of fin end eddy current 4, so can effectively suppress the eddy current change, can reduce noise.
Difference δ zw and the reducing noise the relationship between quantities of crooked beginning Length Ratio α and top rake then, are described with Figure 10 and Figure 11.Figure 10 is expression crooked beginning Length Ratio and reducing noise the relationship between quantities plotted curve, and Figure 11 is the plotted curve of expression δ zw * α and reducing noise the relationship between quantities.In Figure 10, as an example, expression chord-pitch ratio σ is 0.83, oblique angle γ is that 63.5 °, top rake δ z are that 9 °, the value of δ zw * α are 2.3 o'clock plotted curve.In addition, plotted curve with respect to graphical pointv with 2 curve approximations roughly, but bending length than α and reducing noise the relationship between quantities in, approximately in this wise can't harm appropriate property.As can be seen from Figure 10, in the scope of 0.6＜α＜0.95, can obtain the above reducing noise amount of 5dB, have obvious reducing noise effect.In α=0.7 o'clock, can obtain the reducing noise effect of 5.1dB, in α=0.91 o'clock, can obtain the reducing noise effect of 5.2dB.In Figure 11, as an example, expression chord-pitch ratio σ is 0.83, oblique angle γ is that 63.5 °, top rake δ z are that 9 °, crooked beginning Length Ratio α are 0.7 o'clock plotted curve.In addition, plotted curve with respect to graphical pointv with 2 curve approximations roughly, but in δ zw * α and reducing noise the relationship between quantities, approximately in this wise can't harm appropriate property.As can be seen from Figure 11, in 1＜δ zw * α＜6, namely in the scope of 1/ α＜δ zw＜6/ α, can obtain the above reducing noise amount of 5dB, have obvious reducing noise effect.In δ zw * α=2.3 o'clock, can obtain the reducing noise effect of 5.2dB, in δ zw * α=7.3 o'clock, can obtain the reducing noise effect of 4.9dB.
As described above in present embodiment 4, by being constituted, fin 3 satisfies 0.6＜α＜0.95, and 1/ α＜δ zw＜6/ α, because the round and smooth curved shape of the upstream side of the bending area 36 of fin 3 is fit to the shape of fin end eddy current 4, can make fin end eddy current 4 stabilizations, so can effectively suppress to change eddy current, can more reduce noise.
Claims (3)
1. an axial flow fan is characterized in that,
This axial flow fan possesses impeller, and this impeller has the wheel hub that rotates around the axle center and is equipped on a plurality of fins of the peripheral part of above-mentioned wheel hub,
Above-mentioned fin has near peripheral end to the upstream side of fluid main flow crooked bending area sleekly,
Front acies in the plane outspread drawing of the cylinder section centered by the running shaft of above-mentioned impeller, that link above-mentioned fin and in sense of rotation the place ahead of this fin the length with the straight line of the rear acies of its adjacent above-mentioned fin is H,
The diameter of above-mentioned impeller is D,
The straight line of the rear acies of front acies in the above-mentioned plane outspread drawing, that link above-mentioned fin and this fin is that the interval of length l and the adjacent above-mentioned fin of fin string is that the ratio (l/t) of fin pitch t is chord-pitch ratio σ, when the angle that the running shaft of above-mentioned impeller becomes with above-mentioned fin string is oblique angle γ
At above-mentioned bending area, constitute and satisfy 0＜H/D＜0.35,0.72＜σ＜0.91 and 60 °＜γ＜66 °.
2. axial flow fan according to claim 1 is characterized in that,
Be attached to the central point of above-mentioned fin string of the outer circumference end of above-mentioned fin at the central point from the above-mentioned fin string of the interior Zhou Duan of above-mentioned fin, and the straight line or the curve that project on the plane of the running shaft that comprises above-mentioned impeller be the fin mid-chord line,
When the tangent line of above-mentioned fin mid-chord line or above-mentioned fin mid-chord line is top rake δ z with the angle that becomes with the vertical plane of the running shaft of above-mentioned impeller,
In interior all sides of above-mentioned bending area, constitute and satisfy 5 °＜δ z＜40 °.
3. axial flow fan according to claim 1 and 2 is characterized in that,
Be crooked beginning Length Ratio α at the length of span L from interior Zhou Duan to outer circumference end of the above-mentioned fin of the radial direction of above-mentioned impeller with ratio (L/Lw) from the interior Zhou Duan of above-mentioned fin to the length L w of the initial position of above-mentioned bending area,
Be attached to the central point of above-mentioned fin string of the outer circumference end of above-mentioned fin from the central point of the above-mentioned fin string of the interior Zhou Duan of above-mentioned fin, and the straight line or the curve that project on the plane of the running shaft that comprises above-mentioned impeller be the fin mid-chord line,
When the angle that the straight line that links the outer circumference end of above-mentioned fin mid-chord line and interior Zhou Duan becomes with the straight line of the initial position of the above-mentioned bending area that links above-mentioned fin mid-chord line and interior Zhou Duan is the difference δ zw of top rake,
Constitute and satisfy 0.6＜α＜0.95, and 1/ α＜δ zw＜6/ α.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012078595A JP5649608B2 (en) | 2012-03-30 | 2012-03-30 | Axial blower |
| JP2012-078595 | 2012-03-30 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103362858A true CN103362858A (en) | 2013-10-23 |
| CN103362858B CN103362858B (en) | 2015-11-18 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310105962.9A Active CN103362858B (en) | 2012-03-30 | 2013-03-29 | Axial flow fan |
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| Country | Link |
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| JP (1) | JP5649608B2 (en) |
| CN (1) | CN103362858B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106030117A (en) * | 2014-02-24 | 2016-10-12 | 三菱电机株式会社 | Axial flow fan |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108216617B (en) * | 2017-12-29 | 2020-04-24 | 厦门大学 | Method for suppressing helicopter propeller-vortex interference noise |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08121391A (en) * | 1994-10-31 | 1996-05-14 | Mitsubishi Electric Corp | Axial flow blower |
| JPH11303794A (en) * | 1997-10-17 | 1999-11-02 | Mitsubishi Electric Corp | Axial flow impeller and refrigerator |
| CN1421615A (en) * | 2001-11-27 | 2003-06-04 | 北京森博苑科技有限公司 | Axial flow fan vane wheel with forward bent and twisted contour |
| JP2003184792A (en) * | 2001-12-21 | 2003-07-03 | Daikin Ind Ltd | Blower |
| CN1522343A (en) * | 2002-02-28 | 2004-08-18 | ͬ�Ϳ�ҵ��ʽ���� | Fan |
| JP2005016457A (en) * | 2003-06-27 | 2005-01-20 | Matsushita Electric Ind Co Ltd | Blower and heat exchange unit equipped with blower |
| CN101096965A (en) * | 2006-06-26 | 2008-01-02 | 三菱电机株式会社 | Axial flow forced draft fan |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3467815B2 (en) * | 1993-12-17 | 2003-11-17 | 株式会社デンソー | Electric fan |
-
2012
- 2012-03-30 JP JP2012078595A patent/JP5649608B2/en active Active
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- 2013-03-29 CN CN201310105962.9A patent/CN103362858B/en active Active
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08121391A (en) * | 1994-10-31 | 1996-05-14 | Mitsubishi Electric Corp | Axial flow blower |
| JPH11303794A (en) * | 1997-10-17 | 1999-11-02 | Mitsubishi Electric Corp | Axial flow impeller and refrigerator |
| CN1421615A (en) * | 2001-11-27 | 2003-06-04 | 北京森博苑科技有限公司 | Axial flow fan vane wheel with forward bent and twisted contour |
| JP2003184792A (en) * | 2001-12-21 | 2003-07-03 | Daikin Ind Ltd | Blower |
| CN1522343A (en) * | 2002-02-28 | 2004-08-18 | ͬ�Ϳ�ҵ��ʽ���� | Fan |
| JP2005016457A (en) * | 2003-06-27 | 2005-01-20 | Matsushita Electric Ind Co Ltd | Blower and heat exchange unit equipped with blower |
| CN101096965A (en) * | 2006-06-26 | 2008-01-02 | 三菱电机株式会社 | Axial flow forced draft fan |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106030117A (en) * | 2014-02-24 | 2016-10-12 | 三菱电机株式会社 | Axial flow fan |
| CN106030117B (en) * | 2014-02-24 | 2018-06-22 | 三菱电机株式会社 | Axial flow fan |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103362858B (en) | 2015-11-18 |
| JP5649608B2 (en) | 2015-01-07 |
| JP2013209884A (en) | 2013-10-10 |
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