CN103362858B - Axial flow fan - Google Patents
Axial flow fan Download PDFInfo
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- CN103362858B CN103362858B CN201310105962.9A CN201310105962A CN103362858B CN 103362858 B CN103362858 B CN 103362858B CN 201310105962 A CN201310105962 A CN 201310105962A CN 103362858 B CN103362858 B CN 103362858B
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- fin
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- impeller
- inner circumferential
- string
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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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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention provides the axial flow fan of low noise, comprise the impeller (1) of multiple fins (3) with the wheel hub (2) rotated around axle center and the peripheral part being disposed in wheel hub, fin has the bending area (36) that the upstream side to primary fluid flow bends sleekly near peripheral end, in the plane outspread drawing of the cylinder section centered by the running shaft of impeller, link the front acies (31) of fin and be H in the sense of rotation front of this fin with the length of the straight line of the rear acies (32) of its adjacent fin, the diameter of impeller is D, in plane outspread drawing, linking the front acies (31) of fin and the straight line of the rear acies (32) of this fin and the ratio (l/t) of the length (l) of fin string (37) and the interval of adjacent fin and fin pitch (t) is chord-pitch ratio σ, when the running shaft of impeller and the formed angle of fin string (37) are oblique angle γ, in bending area (36), be configured to satisfied 0 < H/D < 0.35, 0.72 < σ < 0.91, and 60 ° of < γ < 66 °.
Description
Technical field
The present invention relates to the axial flow fan of such as air-conditioning, air regenerating device etc.
Background technique
Up to the present, as the technology of the noise of reduction axial flow fan, there are known to following such technology.Namely, by arranging the little fin tilted to primary fluid flow direction in the edge, periphery of blade, suitably form the shape of the edge, periphery of blade, suppress the generation of end of blade eddy current, reduce the noise (for example, referring to patent documentation 1) produced because of the interference with horn mouth or blade.
Patent documentation 1: Japanese Unexamined Patent Publication 6-173895 publication (the 5th page, Fig. 1)
In the technology that above-mentioned patent documentation 1 is recorded, by arranging the little fin tilted to primary fluid flow direction at the peripheral end of fin (blade), suitably form the shape of the peripheral end of fin, suppress the generation of fin end eddy current.But cannot guarantee the effective flow path width between the fin that can reduce due to fin end eddy current fully, the resistance of flowing increases, and the disorder of flowing increases, so there is noise to increase such problem points.
Summary of the invention
The present invention proposes to solve the above problems, and its object is to, and provides a kind of axial flow fan of low noise.
Axial flow fan of the present invention possesses impeller, this impeller has the wheel hub rotated around axle center, with the multiple fins of peripheral part being disposed in above-mentioned wheel hub, above-mentioned fin has the bending area that the upstream side to primary fluid flow bends sleekly near peripheral end, 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 in the sense of rotation front of this fin with the straight line of the rear acies of its adjacent above-mentioned fin is H, the diameter of above-mentioned impeller is D, in above-mentioned plane outspread drawing, linking the front acies of above-mentioned fin and the straight line of the rear acies of this fin and the interval of the length l of fin string and adjacent above-mentioned fin and the ratio (l/t) of fin pitch t is chord-pitch ratio σ, when formed by the running shaft of above-mentioned impeller and above-mentioned fin string, angle is oblique angle γ, at above-mentioned bending area, be configured to satisfied 0 < H/D < 0.35, 0.72 < σ < 0.91, and 60 ° of < γ < 66 °.
The present invention is configured to meet 0 < H/D < 0.35,0.72 < σ < 0.91 and 60 ° of < γ < 66 ° at bending area by making fin, fully can guarantee finned length and not reduce effective work done, fully can guarantee the effective flow path width between fin, the resistance of flowing can be reduced, suppress the disorder of flowing, can noise be reduced.
Accompanying drawing explanation
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 in Fig. 2 of the axial flow fan of embodiments of the present invention 1.
Fig. 4 is the plotted curve of the relation representing chord-pitch ratio and noise reducing amount.
Fig. 5 is the plotted curve of the relation representing oblique angle and noise reducing amount.
Fig. 6 is that II-II cross section in Fig. 2 of the axial flow fan of embodiments of the present invention 2 is to the projection drawing in the plane comprising running shaft.
Fig. 7 is the plotted curve of the relation representing top rake and noise reducing amount.
Fig. 8 is that II-II cross section in Fig. 2 of the axial flow fan of embodiments of the present invention 3 is to the projection drawing in the plane comprising running shaft.
Fig. 9 is that II-II cross section in Fig. 2 of the axial flow fan of embodiments of the present invention 4 is to the projection drawing in the plane comprising running shaft.
Figure 10 represents that the bending length that starts is than the plotted curve with the relation of noise reducing amount.
Figure 11 is the plotted curve of the relation representing δ zw × α and noise reducing amount.
The explanation of reference character
Before 1 impeller, 2 wheel hubs, 3 fins, 3a benchmark fin, 3b front fin, 4 fin end eddy current, 31, after acies, 32, acies, 33 inner circumferential ends, 34 outer circumference end, 35 bend initial positions, 36 bending areas, 37 fin strings, 38 fin string central points, 39 fin mid-chord lines.
Embodiment
Hereinafter, with reference to the accompanying drawings of for implementing mode of the present invention.In addition, for the reference character in Fig. 1 ~ Figure 11, the component marking identical reference character is identical or suitable with this component component, and this is general in the full text of specification.In addition, for multiple fin, only reference character has been marked to representational 1 fin.In addition, in order to implement in mode of the present invention, the number illustrating fin as an example is the situation of 5, but for the number of the fin beyond 5, also can obtain effect of the present invention.
Mode of execution 1
Fig. 1 ~ Fig. 3 is the figure of the axial flow fan in order to embodiments of the present invention 1 are described.Specifically, 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 in Fig. 2 of the 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 up of with multiple fins 3 of the peripheral part being disposed in above-mentioned wheel hub 2 wheel hub 2 rotated around axle center.Fin 3 by front acies 31, rear acies 32, inner circumferential end 33, outer circumference end 34 around.Fin 3, near the peripheral end of the outer circumferential side of bending initial position 35, has the bending area 36 that the upstream side to primary fluid flow (air-flow) bends sleekly.
Then, be described with Fig. 3.In figure 3, in order to the context of clearly multiple fin 3, when making arbitrary fin 3 for benchmark fin 3a, the fin 3 be adjacent in sense of rotation front from it is marked as front fin 3b.As shown in Figure 3, in the plane outspread drawing of the cylinder section centered by the running shaft of impeller 1, before making link benchmark fin 3a, the length of the straight line of the rear acies 32 of acies 31 and front fin 3b is H, when making the diameter of impeller 1 be D, at bending area 36, be configured to 0 < H/D < 0.35.And, in this plane outspread drawing, before making link fin 3, the ratio l/t of the length l of the fin string 37 of acies 31 and rear acies 32 and the interval of adjacent fin 3 and fin pitch t is chord-pitch ratio σ, when making that formed by the axial line of the running shaft of impeller 1 and fin string 37, angle is oblique angle γ, at bending area 36, be configured to satisfied 0.72 < σ < 0.91, and 60 ° of < γ < 66 °.
Then, illustrate by as described above form obtained effect.Upstream bent sleekly side at bending area 36 by fin 3, the size of the eddy current of fin end eddy current 4 is suppressed, but fin end eddy current 4 entirety upstream moves side, stenosis is little in fact at the interval (effective flow path width) of adjacent fin 3 and fin end eddy current 4.By being configured to satisfied 0.72 < σ < 0.91 at bending area 36, and 60 ° of < γ < 66 °, can fully guarantee the length of fin 3 and not reduce effective work done, expand the interval of adjacent fin 3 and fin end eddy current 4 and fully guarantee effective flow path width, the resistance of flowing can be reduced, suppress the disorder of flowing, thus can noise be reduced.
Then, the relation of chord-pitch ratio σ and oblique angle γ and noise reducing amount is described with Fig. 4 and Fig. 5.Fig. 4 is the plotted curve of the relation representing chord-pitch ratio and noise reducing amount, and Fig. 5 is the plotted curve of the relation representing oblique angle and noise reducing amount.Here, noise reducing amount represent when make axial flow fan in the past (such as the technology of patent documentation 1) for when 0dB, the reducing amount of the relative noise of the axial flow fan of embodiments of the present invention 1.In the diagram, as an example, represent that oblique angle γ is 63.5 °, top rake δ z described later is 9 °, bending beginning length described later than α be 0.7, the value of δ zw × α described later be 2.3 time plotted curve.In addition, plotted curve relative to graphical pointv with roughly 2 curve approximations, but in the relation of chord-pitch ratio and noise reducing amount, approximate harmless appropriate property in this wise.As can be seen from Figure 4, in the scope of 0.72 < σ < 0.91, the noise reducing amount of more than 1dB degree can be obtained, there is significant noise reducing effect.Particularly when σ=0.83, the noise reducing amount of 2.2dB can be obtained.In Figure 5, as an example, represent that chord-pitch ratio σ is 0.83, top rake δ z described later is 9 °, bending beginning length described later than α be 0.7, the value of δ zw × α described later be 2.3 time plotted curve.In addition, plotted curve relative to graphical pointv with roughly 2 curve approximations, but in the relation of oblique angle and noise reducing amount, approximate harmless appropriate property in this wise.As can be seen from Figure 5, in the scope of 60 ° of < γ < 66 °, the noise reducing amount of more than 1dB can be obtained, there is obvious noise reducing effect.From Fig. 4 and Fig. 5, chord-pitch ratio σ be 0.83, oblique angle γ be 63.5 ° time noise reducing effect the highest, noise reducing amount becomes 5dB.Particularly when γ=63.5 °, the noise reducing amount of 3dB can be obtained.
As described above in present embodiment 1, by at bending area 36, fin 3 is made to be configured to satisfied 0 < H/D < 0.35,0.72 < σ < 0.91 and 60 ° of < γ < 66 °, fully can guarantee finned length and not reduce effective work done, expand the interval of fin 3 and fin end eddy current 4 and fully guarantee effective flow path width, the resistance of flowing can be reduced, suppress the disorder of flowing, thus can noise be reduced.
Mode of execution 2
Reduce to realize further noise, preferably formation as described below.Fig. 6 is that II-II cross section in Fig. 2 of the axial flow fan of embodiments of the present invention 2 is to the projection drawing in the plane comprising running shaft.The II-II cross section of Fig. 2 is for fin string central point 38(is with reference to Fig. 3 with the center of fin string 37), that comprise all each fin string central points 38 from the inner circumferential end 33 of fin 3 to outer circumference end 34, parallel with running shaft cross section.In figure 6, make each fin string central point 38 of link from the inner circumferential end 33 of fin 3 to outer circumference end 34, and the straight line projected in the plane of the running shaft comprising impeller 1 or curve are fin mid-chord line 39.As shown in Figure 6, by fin mid-chord line 39 and angle formed by the plane with the rotational axis vertical of impeller 1, to be just relative to this plane towards the direction of upstream side, be defined as top rake δ z.Now, in the inner circumferential side of bending area 36, top rake δ z is configured to satisfied 5 ° of < δ z < 40 °.
Then, illustrate by the effect forming acquisition as described above.When top rake δ z is excessively large, the flowing towards the outer circumferential side in the downstream side of fin 3 is promoted terrifically, and increase at outer circumference end 34 air-flow that upstream side is rolled from fin downstream side, the generation scale of fin end eddy current 4 increases.On the other hand, when top rake δ z is excessively little, the flowing towards the outer circumferential side in the downstream side of fin 3 is stagnated terrifically, and the upstream side of outer circumference end 34 and the pressure difference in downstream side increase, due to the pressure difference that this is excessive, the generation scale of fin end eddy current 4 increases.Satisfied 5 ° of < δ z < 40 ° are configured to by top rake δ z, owing to can suppress most effectively towards the flowing of the outer circumferential side in the downstream side of fin 3, the generation scale of fin end eddy current can be suppressed, so more noise can be reduced.
Then, the relation of top rake δ z and noise reducing amount is described with Fig. 7.Fig. 7 is the graph of relation representing top rake and noise reducing amount.In the figure 7, as an example, represent that chord-pitch ratio σ is 0.83, oblique angle γ is 63.5 °, bending beginning length described later than α be 0.7, the value of δ zw × α described later be 2.3 time plotted curve.In addition, plotted curve relative to graphical pointv with roughly 2 curve approximations, but in the relation of top rake and noise reducing amount, approximate harmless appropriate property in this wise.As can be seen from Figure 7, in the scope of 5 ° of < δ z < 40 °, the noise reducing amount of more than 5dB can be obtained, there is obvious noise reducing effect.When δ z=9 °, the noise reducing effect of 5.1dB can be obtained, when δ z=30 °, the noise reducing effect of 6.6dB can be obtained.
As described above in present embodiment 2, by the inner circumferential side at bending area 36, fin 3 is made to be configured to satisfied 5 ° of < δ z < 40 °, owing to can effectively suppress towards the flowing of the outer circumferential side in the downstream side of fin 3, the generation scale of fin end eddy current 4 can be suppressed, so more noise can be reduced.
Mode of execution 3
As for realizing the other mode of execution that the noise equal with the axial flow fan of above-mentioned mode of execution 2 reduces, there is the axial flow fan of formation as described below.Fig. 8 is that II-II cross section in Fig. 2 of the axial flow fan of embodiments of the present invention 3 is to the projection drawing in the plane comprising running shaft.The II-II cross section of Fig. 2 is for fin string central point 38(is with reference to Fig. 3 with the center of fin string 37), that comprise all each fin string central points 38 from the inner circumferential end 33 of fin 3 to outer circumference end 34, parallel with running shaft cross section.In fig. 8, make each fin string central point 38 of link from the inner circumferential end 33 of fin 3 to outer circumference end 34, and the straight line projected in the plane of the running shaft comprising impeller 1 or curve are fin mid-chord line 39.As shown in Figure 8, in present embodiment 3, by the tangent line of fin mid-chord line 39 and angle formed by the plane with the rotational axis vertical of impeller 1, to be just relative to this plane towards the direction of upstream side, be defined as top rake δ z.Now, in the inner circumferential side of bending area 36, top rake δ z is configured to satisfied 5 ° of < δ z < 40 °.Identical with mode of execution 2 by the effect forming acquisition as described above.
Mode of execution 4
Reduce to realize further noise, preferably formation as described below.Fig. 9 is that II-II cross section in Fig. 2 of the axial flow fan of embodiments of the present invention 4 is to the projection drawing in the plane comprising running shaft.In fig .9, with the fin 3 of the radial direction of impeller 1 from inner circumferential end 33 to the length of span of outer circumference end 34 for L, with fin 3 from inner circumferential end 33 to bending area 36 the length of bending initial position 35 for Lw, ratio between two L/Lw is defined as the bending length that starts and compares α.In addition, in fig .9, make each fin string central point 38 of link from the inner circumferential end 33 of fin 3 to outer circumference end 34, and the straight line projected in the plane of the running shaft comprising impeller 1 or curve are fin mid-chord line 39.And, the difference of the top rake of the outer circumference end 34 of fin 3 and the top rake of bending initial position 35 is defined as δ zw.That is, by the straight line of the outer circumference end and inner circumferential end that link fin mid-chord line 39 with link angle formed by the initial position of bending area 36 of fin mid-chord line 39 and the straight line of inner circumferential end, be defined as the difference δ zw of top rake.Now, be configured to satisfied 0.6 < α < 0.95, and 1/ α < δ zw < 6/ α.
Then, illustrate by the effect forming acquisition as described above.Round and smooth curved shape due to the upstream side of the bending area 36 of fin 3 is applicable to the shape of fin end eddy current 4, can make the most stabilization of fin end eddy current 4, so can effectively suppress eddy current to change, can reduce noise.
Then, illustrate that the bending length that starts is than α and the difference δ zw of top rake and the relation of noise reducing amount with Figure 10 and Figure 11.Figure 10 represents that the bending length that starts is than the graph of relation with noise reducing amount, and Figure 11 is the plotted curve of the relation representing δ zw × α and noise reducing amount.In Fig. 10, as an example, represent plotted curve when chord-pitch ratio σ is 0.83, oblique angle γ is 63.5 °, top rake δ z is 9 °, the value of δ zw × α is 2.3.In addition, plotted curve relative to graphical pointv with roughly 2 curve approximations, but in the relation of bending length than α and noise reducing amount, approximate harmless appropriate property in this wise.As can be seen from Figure 10, in the scope of 0.6 < α < 0.95, the noise reducing amount of more than 5dB can be obtained, there is obvious noise reducing effect.When α=0.7, the noise reducing effect of 5.1dB can be obtained, when α=0.91, the noise reducing effect of 5.2dB can be obtained.In fig. 11, as an example, represent plotted curve when chord-pitch ratio σ is 0.83, oblique angle γ is 63.5 °, top rake δ z is 9 °, bending beginning length is 0.7 than α.In addition, plotted curve relative to graphical pointv with roughly 2 curve approximations, but in the relation of δ zw × α and noise reducing amount, approximate harmless appropriate property in this wise.As can be seen from Figure 11, at 1 < δ zw × α < 6, in the scope of i.e. 1/ α < δ zw < 6/ α, the noise reducing amount of more than 5dB can be obtained, there is obvious noise reducing effect.When δ zw × α=2.3, the noise reducing effect of 5.2dB can be obtained, when δ zw × α=7.3, the noise reducing effect of 4.9dB can be obtained.
As described above in present embodiment 4, satisfied 0.6 < α < 0.95 is configured to by making fin 3, and 1/ α < δ zw < 6/ α, round and smooth curved shape due to the upstream side of the bending area 36 of fin 3 is applicable to the shape of fin end eddy current 4, the most stabilization of fin end eddy current 4 can be made, so can effectively suppress to change eddy current, more noise can be reduced.
Claims (3)
1. an axial flow fan,
This axial flow fan possesses impeller, and this impeller has multiple fins of the wheel hub rotated around axle center and the peripheral part being disposed in above-mentioned wheel hub,
Above-mentioned fin has the bending area that the upstream side to primary fluid flow bends sleekly near peripheral end,
It is characterized in that,
In the plane outspread drawing of the cylinder section centered by the running shaft of above-mentioned impeller, link above-mentioned fin before acies and the length in the sense of rotation front of this fin with the straight line of the rear acies of its adjacent above-mentioned fin be H,
The diameter of above-mentioned impeller is D,
The ratio (l/t) of the straight line of rear acies of front acies in above-mentioned plane outspread drawing, that link above-mentioned fin and this fin and the interval of the length l of fin string and adjacent above-mentioned fin and fin pitch t is chord-pitch ratio σ, when formed by the running shaft of above-mentioned impeller and above-mentioned fin string, angle is oblique angle γ
At above-mentioned bending area, be configured to satisfied 0 < H/D < 0.35,0.72 < σ < 0.91 and 60 ° of < γ < 66 °.
2. axial flow fan according to claim 1, is characterized in that,
Be attached to the central point of the above-mentioned fin string of the outer circumference end of above-mentioned fin at the central point of the above-mentioned fin string of the inner circumferential end from above-mentioned fin, and the straight line projected in the plane of the running shaft comprising above-mentioned impeller or curve are 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 angle formed by the plane with the rotational axis vertical of above-mentioned impeller,
In the inner circumferential side of above-mentioned bending area, be configured to satisfied 5 ° of < δ z < 40 °.
3. axial flow fan according to claim 1 and 2, is characterized in that,
The length of span L from inner circumferential end to outer circumference end of the above-mentioned fin of the radial direction of above-mentioned impeller is bending with the ratio (L/Lw) of the length Lw from the inner circumferential end of above-mentioned fin to the initial position of above-mentioned bending area, length is than α,
Be attached to the central point of the 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 inner circumferential end of above-mentioned fin, and the straight line projected in the plane of the running shaft comprising above-mentioned impeller or curve are fin mid-chord line,
When the straight line linking the outer circumference end of above-mentioned fin mid-chord line and inner circumferential end is the difference δ zw of top rake with angle formed by the initial position of above-mentioned bending area linking above-mentioned fin mid-chord line and the straight line of inner circumferential end,
Be configured to satisfied 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 CN103362858A (en) | 2013-10-23 |
| CN103362858B true CN103362858B (en) | 2015-11-18 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| 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 |
|---|---|---|---|---|
| CN108216617A (en) * | 2017-12-29 | 2018-06-29 | 厦门大学 | A kind of method for inhibiting helicopter paddle-vortex interaction noise |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106030117B (en) * | 2014-02-24 | 2018-06-22 | 三菱电机株式会社 | Axial flow fan |
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| 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 |
| CN1522343A (en) * | 2002-02-28 | 2004-08-18 | ͬ�Ϳ�ҵ��ʽ���� | Fan |
| CN101096965A (en) * | 2006-06-26 | 2008-01-02 | 三菱电机株式会社 | Axial flow forced draft fan |
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| 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 |
| JP3203994B2 (en) * | 1994-10-31 | 2001-09-04 | 三菱電機株式会社 | Axial blower |
| JPH11303794A (en) * | 1997-10-17 | 1999-11-02 | Mitsubishi Electric Corp | Axial flow impeller and refrigerator |
| JP3629702B2 (en) * | 2001-12-21 | 2005-03-16 | ダイキン工業株式会社 | Blower |
| JP2005016457A (en) * | 2003-06-27 | 2005-01-20 | Matsushita Electric Ind Co Ltd | Blower and heat exchange unit equipped with blower |
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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
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN1522343A (en) * | 2002-02-28 | 2004-08-18 | ͬ�Ϳ�ҵ��ʽ���� | Fan |
| 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 |
|---|---|---|---|---|
| CN108216617A (en) * | 2017-12-29 | 2018-06-29 | 厦门大学 | A kind of method for inhibiting helicopter paddle-vortex interaction noise |
| CN108216617B (en) * | 2017-12-29 | 2020-04-24 | 厦门大学 | Method for suppressing helicopter propeller-vortex interference noise |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103362858A (en) | 2013-10-23 |
| JP5649608B2 (en) | 2015-01-07 |
| JP2013209884A (en) | 2013-10-10 |
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