CN106930977A - A kind of direct-cooled noise reduction axial flow blower - Google Patents
A kind of direct-cooled noise reduction axial flow blower Download PDFInfo
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- CN106930977A CN106930977A CN201710159965.9A CN201710159965A CN106930977A CN 106930977 A CN106930977 A CN 106930977A CN 201710159965 A CN201710159965 A CN 201710159965A CN 106930977 A CN106930977 A CN 106930977A
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- 210000000474 Heel Anatomy 0.000 claims abstract 2
- 238000001816 cooling Methods 0.000 abstract description 14
- 230000003313 weakening Effects 0.000 abstract description 2
- 230000000052 comparative effect Effects 0.000 description 13
- 230000000694 effects Effects 0.000 description 3
- 230000035515 penetration Effects 0.000 description 3
- 230000001629 suppression Effects 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000003247 decreasing Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000000149 penetrating Effects 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 230000008929 regeneration Effects 0.000 description 1
- 238000011069 regeneration method Methods 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/388—Blades characterised by construction
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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
- F04D29/386—Skewed blades
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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
- F04D29/663—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
- F04D29/667—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
Abstract
The invention discloses a kind of direct-cooled noise reduction axial flow blower in power station, including wheel hub and some around the equally distributed blade of wheel hub, it is characterized in that, some exhausting holes are installed with the blade, it is linearly evenly distributed along length of blade direction per exhausting hole, first exhausting hole before burble point near blade side position, heel row through hole be in after move after Disengagement zone and near blade another side, the centre position between the first exhausting hole and rear exhausting hole is without through hole.The present invention can ensure blower fan lift, while weakening influence of the perforate to fan performance, it is effectively improved the gas flow condition on non-working surface surface, increase blade surface gas flow rates, reduce the generation that vortex departs from, so as to reduce the noise of blower fan, the noise level of whole Air-Cooling Island also will be improved, so that direct-cooled power station meets increasingly strict environmental requirement.
Description
Technical field
The invention belongs to power station cooling device field, more particularly to a kind of direct-cooled noise reduction axial flow blower.
Background technology
In northern China water-deficient area, power station air cooling technology is widely applied.Wherein direct air cooling system is to use
Force ventilation forced convection mode is cooled down to the steam discharge of steam turbine, and a usual Direct Air-cooled Unit needs tens of of configuration
Axial flow blower, therefore direct air cooling system can operationally produce sizable noise, be the Main Noise Sources of power plant.Therefore drop
Low noise of axial flow fan has very important effect to the noise level for reducing whole power plant.
The noise of blower fan is broadly divided into mechanical noise and the major class of air power noise two.Air power noise is again main
It is divided into discrete noise (rotational noise) and the class of broadband noise (eddy current crack) two.The rotation of discrete noise (rotational noise) and impeller
It is relevant.Especially in the case of high speed, underload, this noise is especially prominent.Discrete noise is due to asymmetrical junction around blade
The noise that structure rotates formed circumferential asymmetry uniform flow field interactions and produces with blade.When eddy current crack is by air current flow
Various separation eddies produce, in practice it has proved that, the air power noise that fan blade is produced is far longer than the machinery of blower fan
Noise and electromagnetic noise, if blower fan radiation can significantly be reduced by improving blower fan inlet and outlet and blade construction
Noise, and noise reduction of being tried every possible means in terms of blade has very big research and application prospect.
The content of the invention
The present invention be directed to the current with serious pollution problem of direct air cooling system fan noise, it is proposed that a kind of direct-cooled noise reduction
Axial flow blower, by way of the perforate on blade, the vortex for reducing blade is separated, and then noise is decreased, and is played and is changed
The effect of the noise of kind Air-Cooling Island, improves the Environmental Protection Level of whole power plant.
To achieve these goals, the present invention uses following technical scheme：
A kind of direct-cooled noise reduction axial flow blower, including wheel hub and some around the equally distributed blade of wheel hub, wherein, every institute
State and be installed with blade some exhausting holes, linearly evenly distributed along length of blade direction per exhausting hole, the first exhausting hole is being separated
Near the position of blade side before point, after rear exhausting hole (other through holes i.e. in addition to the first exhausting hole) is moved after being in
Disengagement zone and another side of close blade, the centre position between the first exhausting hole and rear exhausting hole is without through hole.
Further, the blade is forward swept twisted blade, using advanced aerofoil profile.
Further, the number of the blade be 6~8, diameter 9144mm~10363mm (common axial flow blower
Diameter has tri- kinds of 9144mm, 9754mm and 10363mm, and the number of blade of every kind of blower fan can be 6/7/8).
Further, the through hole is round through hole, and the diameter of the through hole is identical.
Further, the diameter of the through hole is between 2mm~5mm.
Further, the spacing between the rear exhausting hole is respectively arranged is identical.
Further, the summation of the spacing between the rear exhausting hole is respectively arranged is the 1/2 of leaf chord length.
Further, it is 5~8 rows that the row of the through hole has altogether.
Further, the perforation deflection angle (angle between blade profile chord length where axially bored line and the hole) of the through hole
It is taken as 40 °~45 °.
Further, the perforation coefficient of the blade is 0.08~0.1.
The beneficial effects of the invention are as follows：
Compared with other blade perforate modes, before the present invention is arranged in burble point using the first exhausting hole, other rows are logical
Hole is arranged in the Disengagement zone after being moved after being in, and does not dispose the perforate mode of through hole between the two, can ensure blower fan lift
(lift coefficient declines no more than 4%), while weakening influence of the perforate to fan performance, is effectively improved the air of non-working surface
Flow condition, reduces the intensity and scope of vortex, so as to effectively reduce the noise (noise reduction value is 3~5dB) of blower fan, whole air cooling
The noise level on island also will be improved, so that direct-cooled power station meets increasingly strict environmental requirement.
Brief description of the drawings
Fig. 1 is existing direct air cooling system φ 9.144m type axial flow blower side views.
Fig. 2 is existing direct air cooling system φ 9.144m type axial flow blower top views.
Fig. 3 is the direct-cooled noise reduction axial flow blower side view of the embodiment of the present invention 1.
Fig. 4 is the direct-cooled noise reduction axial flow blower top view of the embodiment of the present invention 1.
Fig. 5 is the direct-cooled noise reduction axial-flow fan blade perforated sections figure of the embodiment of the present invention 1.
Specific embodiment
The present invention proposes a kind of direct-cooled noise reduction axial flow blower for direct air cooling system, is said below in conjunction with the accompanying drawings
It is bright.
The fan blade for below using is sweepforward type twisted blade, advanced aerofoil profile.
Existing direct air cooling system φ 9.144m types axial flow blower as depicted in figs. 1 and 2, including wheel hub 1-1 and some
The forward swept twisted blade 1-2 around wheel hub 1-1 is evenly arranged in, cooling air is blown into condenser unit finned tube by axial flow blower
Shu Jinhang is exchanged heat, and the air after heat exchange is entered in air.Blower fan is in design conditions with optimal aerodynamic characteristic, whirlpool and whirlpool
Stream departs from not serious, with highest efficiency and minimum noise.But when blower fan off-design operating mode, aeroperformance meeting
Deteriorate, be easily caused vortex and depart from, so that noise figure also will increase.And blower fan usually can off-design work in actual motion
Condition.
In order to reduce blower fan eddy current crack, runner vane perforation method can be used.Because often occurring at blade exit
Vortex is separated, and using blade method for punching fraction can be made to flow to blade low pressure surface from blade high-pressure side, can be promoted
Blade burble point is mobile to flowing lower section, and its mechanism is equal to boundary-layer blowing.Which decrease the separation in blade exit section
Area, Disengagement zone strength of vortex and size are reduced, and noise is also reduced therewith.Penetrating parameter includes perforation row, perforation field, perforation
Coefficient, penetration hole diameter and perforation deflection angle.
(1) determination of row of perforating
Blade perforation row increases, and noise decrease value increases, but blast can also decline, therefore row should not be too many.If each
Round is all distributed in after vortex burble point, and noise reduction can not possibly be optimal, because it can not effectively suppress the product that vortex departs from
It is raw, therefore the first round so must just can guarantee that the generation for effectively suppressing vortex disengaging, after making burble point before burble point
Move, through hole below moved after being then in after Disengagement zone in, effectively prevent the generation and expansion of Disengagement zone.It is unsuitable in the middle of blade
Perforation is arranged, because it provides most lift, so can guarantee that lift coefficient declines smaller.
(2) determination of perforation coefficient
The increase of blade perforation coefficient, noise reduction value increases, resistance coefficient reduction, but lift coefficient is also subject to shadow
Ring.With the increase of perforation coefficient, the rear shifting of one side burble point increased fluid deflection increases lift coefficient, the opposing party
Air-flow flows to non-working surface from working face after the blade perforation of face reduces fluid deflection, and perforation coefficient 0.1 is lift coefficient pole
Value point, perforation coefficient can both obtain larger noise reduction at 0.08~0.1, lift coefficient will not again decline too many.
(3) determination of penetration hole diameter
Blade penetration hole diameter is too big, and the air-flow through through hole will produce influence to the air-flow from blade relatively large distance, be not
Profit；Kong Tai little, the air-flow for passing through will be unable to the generation for suppressing to flow backwards, in addition it is also contemplated that perforation causes high frequency regeneration noise
Problem, therefore consider lower aperture and be selected in 2~5mm.After aperture, hole row, perforation coefficient determine, pitch-row also mutually should determine that
.
(4) determination of perforation field
After aperture, hole row, perforation coefficient determine, pitch-row is also accordingly determined.Spacing between exhausting hole is respectively arranged afterwards
Equal, spacing summation is the 1/2 of chord length, and their particular location will determine according to the gas flow condition of different blade profiles.Example
The direct-cooled blower fan of φ 9.144m is such as selected, then the original position of rear exhausting hole is at the position of chord length 40%.
(5) determination of deflection angle of perforating
Perforation deflection angle a increases, and noise reduction value can reduce, and lift coefficient decline, resistance coefficient can be caused to rise, so a
Should be as small as possible, and a<Influence at 60 ° to lift coefficient is not notable.Consider more than influence and technological problemses, a select 40 °~
45 ° are advisable.
Embodiment 1
As shown in Figures 3 and 4, the direct-cooled noise reduction axial flow blower includes wheel hub 2-1 and some is evenly arranged in around wheel hub 2-1
Forward swept twisted blade 2-2, the number of blade be 6.But it is different from existing direct air cooling system φ 9.144m type axial flow blowers, should
Embodiment is equipped with 5 row's manholes on every blade of the direct-cooled blower fan of φ 9.144m, per exhausting hole (when other specification determines
When, through hole number is determined that) it is linearly evenly distributed along length of blade direction, aperture is identical, is 2mm.Due to each round
All can not effectively suppress vortex after burble point is vortexed to depart from, therefore the first exhausting hole 2-3 on blade is before burble point
The position of close blade side, another side of Disengagement zone and close blade after being moved after four exhausting hole 2-4 are in afterwards, so that
The generation and expansion of Disengagement zone can effectively be suppressed.Blade centre position is without through hole, because it is to provide the main portion of blower fan lift
Point, can so ensure that lift coefficient declines smaller.After aperture, hole row, perforation coefficient determine, pitch-row also mutually should determine that
.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2 of chord length, and the original position of rear exhausting hole is in chord length
At 40% position.
Fig. 5 is fan blade perforated sections figure, and the upper surface 2-5 in figure is working face, and lower surface 2-6 is non-working surface,
Because the increase of perforation deflection angle a can rise lift coefficient reduction and resistance coefficient, therefore a can not be too big, all through holes
Perforation deflection angle it is identical, 45 ° are taken as in the embodiment；The perforation coefficient of blade is 0.08.Due to blade perforation coefficient very little,
Therefore to the performance impact very little of blower fan.
(detected on the blower fan axis of blower fan 1m, following examples and comparative example use same detection side after testing
Formula), the blade perforation axial flow blower for meeting above parameter can reduce noise figure 5dB, and lift coefficient declines 3%.
Embodiment 2
The embodiment is to be equipped with 5 row's manholes on the every blade (number of blade is 6) of the direct-cooled blower fans of φ 9.754m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 3mm, and the first exhausting hole on blade is dividing
Before point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole, and the spacing between rear exhausting hole is respectively arranged is equal, and spacing summation is the 1/2 of chord length, all through holes
Perforation deflection angle it is identical, be 45 °；The perforation coefficient of blade is 0.08.
After testing, the blade perforation axial flow blower for meeting above parameter can reduce noise figure 4.5dB, and lift coefficient declines
3.5%.
Embodiment 3
The embodiment is to be equipped with 5 rows circle on the every blade (number of blade is 6) of the direct-cooled blower fans of φ 10.363m to lead to
Hole, linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 5mm, and the first exhausting hole on blade exists
Before burble point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole.After aperture, hole row, perforation coefficient determine, pitch-row is also accordingly determined.Exhausting hole afterwards
Spacing between each row is equal, and spacing summation is the 1/2 of chord length, and the perforation deflection angle of all through holes is identical, is 45 °；Blade
Perforation coefficient be 0.08.
After testing, the blade perforation axial flow blower for meeting above parameter can reduce noise figure 4.5dB, and lift coefficient declines
4%.
Embodiment 4
The embodiment is equipped with 6 row's manholes on the every blade (number of blade is 7) of the direct-cooled blower fan of φ 9.144m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 2mm, and the first exhausting hole on blade is dividing
Before point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2 of chord length, rear exhausting hole
Original position at the position of chord length 40%, the perforation deflection angle of all through holes is identical, is 42 °；The perforation coefficient of blade
It is 0.09.
After testing, the blade perforation axial flow blower for meeting above parameter can reduce noise figure 4dB, and lift coefficient declines
3.5%.
Embodiment 5
The embodiment is equipped with 7 row's manholes on the every blade (number of blade is 6) of the direct-cooled blower fan of φ 9.144m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 2mm, and the first exhausting hole on blade is dividing
Before point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2 of chord length, rear exhausting hole
Original position at the position of chord length 40%, the perforation deflection angle of all through holes is identical, is 45 °；The perforation coefficient of blade
It is 0.1.
After testing, the blade perforation axial flow blower for meeting above parameter can reduce noise figure 3dB, and lift coefficient declines 4%.
Embodiment 6
It is circular logical that the embodiment is equipped with 8 rows on the every blade (number of blade is 8) of the direct-cooled blower fan of φ 10.363m
Hole, linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 2mm, and the first exhausting hole on blade exists
Before burble point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2 of chord length, rear exhausting hole
Original position at the position of chord length 40%, the perforation deflection angle of all through holes is identical, is 40 °；The perforation coefficient of blade
It is 0.08.
After testing, the blade perforation axial flow blower for meeting above parameter can reduce noise figure 4dB, and lift coefficient declines 3%.
Comparative example 1
The comparative example is equipped with 4 row's manholes on the every blade (number of blade is 6) of the direct-cooled blower fan of φ 9.144m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 5mm, and the first exhausting hole on blade is dividing
Before point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2 of chord length, rear exhausting hole
Original position at the position of chord length 40%, the perforation deflection angle of all through holes is identical, is 45 °；The perforation coefficient of blade
It is 0.08.
After testing, the blade perforation axial flow blower for meeting above parameter is only capable of reducing noise figure 2dB, and lift coefficient declines
5%.
Comparative example 2
The comparative example is equipped with 5 row's manholes on the every blade (number of blade is 6) of the direct-cooled blower fan of φ 9.144m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 2mm, and each exhausting hole on blade is all distributed
Be vortexed burble point after and spacing is equal, spacing summation for chord length 1/2, the perforation deflection angle of all through holes is identical, is
45°；The perforation coefficient of blade is 0.08.
After testing, the blade perforation axial flow blower for meeting above parameter is only capable of reducing noise figure 1.5dB, and lift coefficient declines
3%.
Comparative example 3
The comparative example is equipped with 5 row's manholes on the every blade (number of blade is 6) of the direct-cooled blower fan of φ 9.144m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 2mm, and the first exhausting hole on blade is dividing
Before point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Also there is through hole in side, blade centre position.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2, Suo Youtong of chord length
The perforation deflection angle in hole is identical, is 45 °；The perforation coefficient of blade is 0.08.
After testing, although the blade perforation axial flow blower for meeting above parameter can reduce noise figure 4dB, under lift coefficient
Drop 8%.
Comparative example 4
The comparative example is equipped with 5 row's manholes on the blade (number of blade is 7) of the direct-cooled blower fan every of φ 9.144m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 2mm, and the first exhausting hole on blade is dividing
Before point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2 of chord length, all through holes
Perforation deflection angle it is identical, be 45 °；The perforation coefficient of blade is 0.2.
After testing, although the blade perforation axial flow blower for meeting above parameter can reduce noise figure 5dB, lift coefficient
Also have dropped 10%.
Comparative example 5
The comparative example is equipped with 5 row's manholes on the every blade (number of blade is 6) of the direct-cooled blower fan of φ 9.144m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 8mm, and the first exhausting hole on blade is dividing
Before point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2 of chord length, all through holes
Perforation deflection angle it is identical, be 45 °；The perforation coefficient of blade is 0.08.
After testing, the blade perforation axial flow blower for meeting above parameter is only capable of reducing noise figure 2dB, and lift coefficient declines
9%.
Comparative example 5
The comparative example is equipped with 5 row's manholes on the every blade (number of blade is 8) of the direct-cooled blower fan of φ 9.144m,
Linearly evenly distributed along length of blade direction per exhausting hole, aperture is identical, is 2mm, and the first exhausting hole on blade is dividing
Before point near blade side position, after four exhausting holes are in afterwards move after Disengagement zone and near the opposite side of blade
Side, blade centre position is without through hole.Spacing between exhausting hole is respectively arranged afterwards is equal, and spacing summation is the 1/2 of chord length, all through holes
Perforation deflection angle it is identical, be 65 °；The perforation coefficient of blade is 0.08.
After testing, although the blade perforation axial flow blower for meeting above parameter can reduce noise figure 3dB, under lift coefficient
Drop 11%.
Claims (10)
1. a kind of direct-cooled noise reduction axial flow blower, including wheel hub and some around the equally distributed blade of wheel hub, it is characterised in that every
Some exhausting holes are installed with blade described in piece, linearly evenly distributed along length of blade direction per exhausting hole, the first exhausting hole exists
Before burble point near blade side position, heel row through hole be in after move after Disengagement zone and near the opposite side of blade
Side, the centre position between the first exhausting hole and rear exhausting hole is without through hole.
2. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 1, it is characterised in that the blade is that forward swept turns round leaf
Piece, using advanced aerofoil profile.
3. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 1, it is characterised in that the number of the blade is 6~8
Piece, diameter is in 9144mm~10363mm.
4. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 1, it is characterised in that the through hole is round through hole, institute
The diameter for stating through hole is identical.
5. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 4, it is characterised in that the diameter of the through hole 2mm~
Between 5mm.
6. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 1, it is characterised in that the rear exhausting hole is respectively between row
Spacing is identical.
7. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 6, it is characterised in that the rear exhausting hole is respectively between row
The summation of spacing is the 1/2 of leaf chord length.
8. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 1, it is characterised in that it is 5 that the row of the through hole has altogether
~8 rows.
9. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 1, it is characterised in that the perforation deflection angle of the through hole takes
It is 40 °~45 °.
10. a kind of direct-cooled noise reduction axial flow blower as claimed in claim 1, it is characterised in that the perforation coefficient of the blade is
0.08~0.1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710159965.9A CN106930977A (en) | 2017-03-17 | 2017-03-17 | A kind of direct-cooled noise reduction axial flow blower |
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| CN201710159965.9A CN106930977A (en) | 2017-03-17 | 2017-03-17 | A kind of direct-cooled noise reduction axial flow blower |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110228586A (en) * | 2019-05-07 | 2019-09-13 | 刘羽双 | A kind of unmanned plane rotor eddy current crack reduction method based on blade perforation |
| US11280352B2 (en) * | 2019-02-28 | 2022-03-22 | Schneider Electric It Corporation | Fan cover |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005240749A (en) * | 2004-02-27 | 2005-09-08 | Mitsubishi Electric Corp | Blower |
| WO2010066140A1 (en) * | 2008-12-11 | 2010-06-17 | 中山大洋电机股份有限公司 | A fan blade of an axial fan or a centrifugal fan |
| US20120009065A1 (en) * | 2010-07-07 | 2012-01-12 | Rolls-Royce Plc | Rotor blade |
| CN104454641A (en) * | 2014-11-13 | 2015-03-25 | 中国北车集团大连机车研究所有限公司 | Low-noise axial flow fan impeller for high-speed electric multiple unit cooling system |
| CN204493262U (en) * | 2014-10-30 | 2015-07-22 | 湖北双剑鼓风机股份有限公司 | A kind of fan blade with noise reduction hole |
| CN204610370U (en) * | 2015-04-22 | 2015-09-02 | 浙江理工大学 | A kind of centrifugal impeller of blade trailing edge perforation |
| CN206845538U (en) * | 2017-03-17 | 2018-01-05 | 中国大唐集团科技工程有限公司 | A kind of direct-cooled noise reduction axial flow blower |
-
2017
- 2017-03-17 CN CN201710159965.9A patent/CN106930977A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005240749A (en) * | 2004-02-27 | 2005-09-08 | Mitsubishi Electric Corp | Blower |
| WO2010066140A1 (en) * | 2008-12-11 | 2010-06-17 | 中山大洋电机股份有限公司 | A fan blade of an axial fan or a centrifugal fan |
| US20120009065A1 (en) * | 2010-07-07 | 2012-01-12 | Rolls-Royce Plc | Rotor blade |
| CN204493262U (en) * | 2014-10-30 | 2015-07-22 | 湖北双剑鼓风机股份有限公司 | A kind of fan blade with noise reduction hole |
| CN104454641A (en) * | 2014-11-13 | 2015-03-25 | 中国北车集团大连机车研究所有限公司 | Low-noise axial flow fan impeller for high-speed electric multiple unit cooling system |
| CN204610370U (en) * | 2015-04-22 | 2015-09-02 | 浙江理工大学 | A kind of centrifugal impeller of blade trailing edge perforation |
| CN206845538U (en) * | 2017-03-17 | 2018-01-05 | 中国大唐集团科技工程有限公司 | A kind of direct-cooled noise reduction axial flow blower |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11280352B2 (en) * | 2019-02-28 | 2022-03-22 | Schneider Electric It Corporation | Fan cover |
| CN110228586A (en) * | 2019-05-07 | 2019-09-13 | 刘羽双 | A kind of unmanned plane rotor eddy current crack reduction method based on blade perforation |
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