CN105756975B - The axial flow blower that a kind of blade inlet edge is blown with groove structure and blade root - Google Patents
The axial flow blower that a kind of blade inlet edge is blown with groove structure and blade root Download PDFInfo
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- CN105756975B CN105756975B CN201610263059.9A CN201610263059A CN105756975B CN 105756975 B CN105756975 B CN 105756975B CN 201610263059 A CN201610263059 A CN 201610263059A CN 105756975 B CN105756975 B CN 105756975B
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- 229910052742 iron Inorganic materials 0.000 claims abstract description 4
- 238000009954 braiding Methods 0.000 claims abstract description 3
- UJCHIZDEQZMODR-BYPYZUCNSA-N (2r)-2-acetamido-3-sulfanylpropanamide Chemical compound CC(=O)N[C@@H](CS)C(N)=O UJCHIZDEQZMODR-BYPYZUCNSA-N 0.000 claims description 5
- 241001669680 Dormitator maculatus Species 0.000 claims description 5
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- 238000000926 separation method Methods 0.000 abstract description 10
- 230000006872 improvement Effects 0.000 abstract description 4
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- 230000002829 reductive effect Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
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- 239000003245 coal Substances 0.000 description 3
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- 238000005119 centrifugation Methods 0.000 description 1
- 235000013339 cereals Nutrition 0.000 description 1
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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
- F04D29/384—Blades characterised by form
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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
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
-
- 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
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
- F04D29/329—Details of the hub
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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
-
- 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
-
- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/541—Specially adapted for elastic fluid pumps
-
- 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
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
-
- 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
- F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
- F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
- F04D29/703—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps specially for fans, e.g. fan guards
Abstract
The invention discloses the axial flow blower that a kind of blade inlet edge is blown with groove structure and blade root, including guard, impeller, stator, inner cylinder, outer barrel, motor；The guard is that have iron wire braiding to form, and is fixed on outer barrel；The impeller includes wheel hub and blade, the fluted structure of blade inlet edge, and vane tip trailing edge has bulge-structure, there is blowing groove on impeller hub；The blade is the airfoil fan for the design of circular rector Isolated Airfoil method such as passing through, and blade tip trailing edge adds bulge-structure and stator suction surface to add deflector, can reduce leaf root part boundary layer thickness；Suppress blade inlet edge point boundary layer separation；Control the size of tip clearance vortex and the shedding frequence in whirlpool；Reduce the flowing of stator radial second；Suppress stator wake's flow field noise.Make that the profile shaft flow fan is more efficient, and noise is lower, more energy-conserving and environment-protective by the improvement to axial flow blower diverse location.
Description
Technical field
The invention belongs to blower fan technical field, axle stream of more particularly to a kind of blade inlet edge with groove structure and blade root air blowing
Blower fan.
Background technology
Axial flow blower is by the mechanical energy of input, improves gas pressure and supplies gas side by side the machinery of body.It is widely used in work
Factory, ventilation, dust discharge and the cooling of mine, tunnel, cooling tower, vehicle, ship and building；The ventilation of boiler and industrial furnace and
Air inducing；Cooling and ventilation in the apparatus of air conditioning and domestic electric appliance；The drying of cereal and select and recommend；Wind-tunnel wind regime and air cushion
Propulsion of the inflation of ship etc., there is very important application in national economy every profession and trade.According to statistics, blower fan electricity consumption accounts for national hair
The 10% of electricity, coal master will lead to 16% that machine average current drain accounts for mine power consumption；The blower fan power consumption of metal mine accounts for mining and used
The 30% of electricity；The blower fan power consumption of steel and iron industry accounts for the 20% of its productive power；The blower fan power consumption of coal industry accounts for coal industry
The 17% of electricity consumption.As can be seen here, status and effect of the Fan Energy-saving in each department of national economy are very important.Due to axle
The specific speed of flow fan is higher, and so it has the characteristics of flow is big, total head is low, all occupies in these industries irreplaceable
Status.
Therefore the axial fan that design optimization goes out that efficiency high, performance are good, noise is low, save is critically important.But
Extremely complex property is flowed in axial flow blower, is mainly reflected in：1）What is flowed is three-dimensionality；2）The viscosity of fluid；3）What is flowed is non-fixed
Perseverance.It is difficult in view of 3 points above in traditional fan design, is set even if doing auxiliary with CFD in modern Design
Meter, but influence of three factors to fan performance above can not be controlled completely, the factor of wherein most critical is the viscosity of fluid,
Viscosity not only has influence on exit edge of blade to meet blade wake passing vortex that Kutta-Joukowsky condition is formed.Due to
Viscosity, blade surface and ring wall passage surface can have viscous boundary layer, have between them and between main flow strong
Interaction, produce so-called " Secondary Flow " phenomenon.Secondary flow is that axial flow blower loses rising, main that efficiency declines
Source.Simultaneously as the influence of viscosity, makes aerodynamic noise in axial flow blower be present, the aerodynamic noise master of axial flow blower
To be made up of two parts：Rotational noise and eddy current crack.If fan outlet is directly discharged into air, also exhaust noise.
In summary, want design optimization and go out the axial fan that efficiency high, performance are good, noise is low, save, seek to
Control and reduce secondary flow, control and reduce boundary layer thickness, prevent vortex shedding or control whirlpool formation.
The content of the invention
The purpose of the present invention is can not to be controlled well in axial flow blower by traditional design in view of the shortcomings of the prior art
Boundary layer thickness, Secondary Flow and eddy current crack, there is provided the axle stream wind that a kind of blade inlet edge is blown with groove structure and blade root
Machine, in front of the blade edge process groove structure, close to blade suction surface wheel hub on open blowing groove, blade tip trailing edge adds convex
Play structure and stator suction surface adds deflector, leaf root part boundary layer thickness can be reduced；Suppress blade inlet edge point boundary layer minute
From；Control the size of tip clearance vortex and the shedding frequence in whirlpool；Reduce the flowing of stator radial second；Suppress stator wake's flow field to make an uproar
Sound.Make that the profile shaft flow fan is more efficient, and noise is lower, more energy-conserving and environment-protective by the improvement to axial flow blower diverse location.
The technical solution adopted by the present invention is such：The axle stream wind that a kind of blade inlet edge is blown with groove structure and blade root
Machine, including guard, impeller, stator, inner cylinder, outer barrel, motor；The guard is formed by iron wire braiding, is fixed on outer barrel；Its
It is characterised by：The impeller includes wheel hub and blade, the fluted structure of blade inlet edge, and vane tip trailing edge has bulge-structure,
There is blowing groove on impeller hub；The blade is the airfoil fan for the design of circular rector Isolated Airfoil method such as passing through, and turns round speed with radius
Increase and reduce, pressure is radially constant, vane thickness be distributed, aerofoil profile phase identical with NACA 4-digit number profile thickness distributions
It is 10%-15% to thickness, blade quantity is 5-9, and blade blade tip clearance is 1%-the 2% of blade height；The blade inlet edge
Groove structure, center falls on the shape line of aerofoil cross section, and is uniformly distributed, and channel section is shaped as circular arc, and groove runs through
Whole blade inlet edge, groove extend since leading edge point to the equidistant side in both sides, and groove diameter is the same, and the quantity of groove is 4-10
It is individual, 1%-the 3% of a diameter of chord length, the distance between groove is 3%-the 8% of chord length；The vane tip trailing edge bulge-structure
Cuboid is shaped as, bulge-structure is perpendicular to blade suction surface, and raised width is high 3% -6% of leaf, and length is width
2-4 times, thickness is that width is 1/4-1/2；The air blowing slot structure, on wheel hub, close to the suction surface side of blade, blow
The contour line of air drain is to offset to obtain by blade and wheel hub suction surface intersection, and the length of blowing groove is blade root section chord length
20%-30%, the width of blowing groove is 5-10mm, blowing groove completely through wheel hub wall, air blowing slot tail and blade root trailing edge away from
From 20% -40% for blade root chord length；The stator is fixed on above inner cylinder and outer barrel, and stator blade is circular arc plate blade, edge
And be radially provided with torsion stator, quantity is 7-17, and the size of the axial gap of stator impeller and impeller is 5-10mm, stator
The thickness of blade is 2-4mm, and stator has deflector close to the suction surface of trailing edge；The deflector is evenly distributed on suction surface tail
Edge point, equal in magnitude perpendicular to stator surface, with stator trailing edge apart from identical, the position with respect to guide vane height exists respectively
20%th, 40%, 60% and 80%, deflector length is 20%-the 30% of vane root chord length, the height of deflector for length 1/3-
1/2, the thickness of deflector is identical with stator, and the distance of deflector and blade trailing edge is 3%-the 5% of vane root chord length；It is described
Motor is threephase asynchronous machine, and motor is fixed on the web of inner cylinder, and impeller is connected by axle sleeve with motor shaft.
Beneficial effects of the present invention：
The present invention can reduce and suppress the thickness in boundary layer by being provided with blowing groove on impeller hub, control
The separation in boundary layer, reduces eddy region, slow down the shedding frequence of vortex, reduces energy loss and eddy current crack；Together
When blade leading edge added with cylinder shape groove structure, the separation in leading edge point boundary layer can be suppressed, make in runner air-flow more
Steadily, efficiency is improved, reduces overall noise grade；At leaf top, trailing edge adds the bulge-structure perpendicular to blade surface, can be with
Effective control leaf top regional edge interlayer separation and the shedding frequence in whirlpool, reduce blower fan Trailing Edge Loss and eddy current crack；Leading
Leaf suction surface adds rear portion split flow plate, can be very good control due to radial flow caused by the pressure and centrifugal force imbalance of fluid
It is dynamic, while the size in a pair of channels whirlpool in blade passage can also be controlled, and blade surface boundary-layer creep flowing, also just control
The Secondary Flow of radial motion has been lived, has reduced the uneven of speed, has reduced jet Trailing Edge Loss, boundary layer thickness has been controlled, makes stator
Suction surface boundary layer separation point moves backward, reduces energy loss, control vortex shedding, it is suppressed that the whirlpool caused by stator tail
Flow noise.Make that the profile shaft flow fan is more efficient, and noise is lower, more energy-saving ring by the improvement to axial flow blower diverse location
Protect.
Brief description of the drawings
Fig. 1 is the axial flow blower graphics of the present invention.
Fig. 2 is the blade wheel structure figure of the present invention.
Fig. 3 is the wheel hub blowing structure schematic diagram of the present invention.
Fig. 4 is the impeller leading edge groove structure schematic diagram of the present invention.
Fig. 5 is the leading edge groove location schematic diagram of the present invention.
Fig. 6 is the blade tip trailing edge bulge-structure figure of the present invention.
Fig. 7 is the stator level graphics of the present invention.
Fig. 8 is the deflector position view of the present invention.
Fig. 9 is the vane airfoil profile Cross section Design schematic diagram of the present invention.
Embodiment
Below in conjunction with the accompanying drawings and embodiment the invention will be further described.
As shown in figure 1, the axial fan is made up of 6 parts, including it is 1, impeller 2, stator 3, inner cylinder 4, motor 5, outer
Cylinder 6, guard；Outer barrel 5, stator 2 and inner cylinder 3 are fixed together by welding, and motor 4 is fixed on the web of inner cylinder 3, wherein electricity
The running parameter of machine 4 is 720r/min, power 4KW;Impeller 1 is fixed on the axle of motor 4 by axle sleeve, the wheel hub of impeller 1 with
The gap of inner cylinder 3 is 10mm；Guard 6 is arranged on outer barrel 5, is played the role of rectification and is prevented foreign matter from entering.
As shown in Figure 1,2,3, 4, impeller 1 has motor 4 to drive to air work, improves dynamic pressure and the static pressure of gas, impeller 1
On blade 1-1 be the airfoil fan for the design of circular rector Isolated Airfoil method such as passing through, turn round speed and reduce with the increase of radius, pressure
Radially constant, blade relative thickness is 10%, and blade quantity is 6, and blade blade tip clearance is the 2% of blade height.
Impeller blade design specific method is as follows：
The simple radial equilibrium equation of axial fan internal flow：
Wherein P represents the pressure that fluid micellar is subject to, and Cu is the speed that fluid micellar is pivoted, and r is fluid micellar
Radius of turn.Formula represents to assume no Radial Flow inside axial flow blower, then optional position fluid micellar diametrically by
Pressure P and fluid micellar rotary motion caused by centrifugation dynamic balance.
In formula（2）-（3）In, Pt be gas stagnation pressure, ρ be gas density, C be gas sum velocity, Cu, Ca,
Cr is respectively the circumferential speed, circumferential speed, radial velocity of gas, but have it is assumed above understand Cr=0, the stagnation pressure of gas etc.
In dynamic pressure plus static pressure.
By formula（2）-（3）Pt, P, Cu, Ca differential relationship such as formula can be obtained（4）Formula（4）Back substitution enters
Formula（1）In can be obtained by another more general simple radial equilibrium equation（5）.
Assume that stagnation pressure Pt is radially constant etc. circular rector design method, axial velocity Ca is also radially constant, substitutes into formula
（5）In understand：
It is exactly to assume blower interior Cr=0 etc. circular rector design method from formula above, and stagnation pressure Pt is radially not
Become, axial velocity Ca is also radially constant, and circumferential speed reduces with the increase of radius.
Formula（7）Derived by Theories of Cascades, one on solidity of blades, blade is turned round fast, leaf grating liter
Force coefficient, and average relative in leaf gratingBetween relation.
Isolated Airfoil design method just assumes that the lift coefficient of leaf gratingBlade is not interfered between by leaf grating, also
It is the lift coefficient of leaf gratingThe lift coefficient of Isolated AirfoilIt is identical.
It is exactly etc. circular rector Isolated Airfoil design method as described above, calculating each of blade by above method can
The chord length and established angle in section, vane inlet airflow machine and blade exit airflow machine, it is public plus some experiences by parameter above
Formula can calculates the shape of mean camber line, and it is 10% to take relative thickness of airfoil, and then, the mean camber line in each section is superimposed NACA
4-digit number profile thickness is distributed, and obtains each aerofoil section.NACA aerofoil profiles are the American National aviation information committees（National
Advisory Committee for Aeronautics）The profile set delivered, 4-digit number aerofoil profile are its conventional aerofoil profiles
Series, design method are as follows：
NACA 4-digit number profile thickness distribution function equations are：
Wherein：T represents relative thickness,, b is chord length, and using the profound line of aerofoil profile as X-axis, the origin of coordinates is placed on aerofoil profile leaf
In piece leading edge point,。
Method is as follows, and first, it is 10% to take relative thickness, obtains N number of discrete point of blade different cross section thickness distribution function, then, while each section mean camber line is also carried out decile and obtains N number of discrete point, and pass through
Calculus of finite differences asks for the slope of each point normal, then obtains inclination angle, so can be obtained by aerofoil profile upper and lower surface after converting
Coordinate points
Then aerofoil profile needed for a section is can be obtained by with connecting for line smoothing, as shown in figure 9, a1 is thickness profile function,
A4 is blade mean camber line, a2 and normal and tangent line that a3 is mean camber line any point.
As shown in Fig. 2,3,4,5, the fluted structure 1-5 of blade 1-1 leading edges, blade 1-1 leading edge groove structure 1-5 centers fall
On the shape line of aerofoil cross section, and it is uniformly distributed, groove 1-5 cross sectional shapes are circular arc, before groove runs through whole blade 1-1
Edge, groove equidistantly extend since leading edge point A1, to both sides, and leading edge point is the intersection point of vane type line and string of a musical instrument A2, groove diameter
Equally, the quantity of groove is 5, and suction surface has 3, and pressure face has 1, and leading edge point has 1, and diameter d1 is leaf top chord length
The distance between 1.5%, size 3mm, groove d2 is the 4% of leaf top chord length, size 8mm.
As shown in Figure 2,3, 4, there is air blowing slot structure 1-3 on the wheel hub 1-2 of impeller 1, air blowing slot structure 1-3 is in blade
Suction surface side, blowing groove 1-3 are to offset to obtain by blade and wheel hub suction surface intersection, and the length of blowing groove is blade root section string
Long 25%, length 70mm, blowing groove 1-3 width are 7mm, and blowing groove 1-3 is completely through wheel hub wall, blowing groove 1-3 afterbodys
Distance with blade root trailing edge is the 30% of blade root chord length.
As shown in Fig. 2,3,4,6, blade 1-1 top trailing edge added with bulge-structure 1-4, bulge-structure 1-4 shape
For cuboid, for bulge-structure 1-4 perpendicular to blade suction surface, raised width d5 is high 4% of leaf, is 10mm, and height d4 is wide
2 times of degree, thickness d 3 is that width is 1/2.
As shown in Fig. 2,3,4,6, stator 2 is fixed on above inner cylinder 3 and outer barrel 5, and stator 2 is circular arc plate blade, along
It is 9 to be radially provided with and reverse stator quantity, and the size of the axial gap of the impeller of stator 2 and impeller is 10mm, the thickness of the blade of stator 2
Spend has deflector 2-1 for 4mm, stator 2 close to the suction surface of trailing edge；The deflector 2-1 is evenly distributed on suction surface trailing edge portion
Point, it is equal in magnitude perpendicular to stator surface, with stator trailing edge apart from identical, with respect to guide vane height position respectively 20%,
40%th, 60% and 80%, spacing a3 are 53mm, and deflector length a2 is 25%, length 80mm of vane root chord length, deflector
Height a4 is the 1/3 of length a2, and the thickness a5 of deflector is all mutually 4mm with stator, and the distance a1 of deflector and blade trailing edge is
The 3% of vane root chord length, size 10mm.
The present invention is provided with blowing groove 1-3 on the wheel hub 1-2 of impeller 1 first, and blowing groove 1-3 is located at blade 1-1 at blade root and inhaled
The side in power face, during being rotated due to impeller 1, blade 1-1 suction surface is set to produce negative pressure, such gas can passes through
The suction surface side that wheel hub 1-2 axial faces are blown at blade root.The reason for blade root fluting is blown is that the fluid of suction surface is at one
Flow in the environment of adverse pressure gradient, and constantly increase along tangential adverse pressure gradient, can so cause suction surface boundary layer than pressure
Power face border thickness much, and also has end wall bounda layer caused by the friction of fluid and wheel hub arc surface in leaf root part, two kinds
Boundary layer mixes in the suction surface of blade root, forms extremely complex flowing, and can cause side with the thickening in boundary layer
Interlayer separates, and turns to twist to form eddy flow area, causes impeller channel obstruction, energy loss and broadband sound source noise.Blade root pressure
Face is blown, and the gas of higher-energy is entered root boundary layer region, can be reduced and suppress the thickness in boundary layer, control
The separation in boundary layer, reduces eddy region, slow down the shedding frequence of vortex, reduces energy loss and eddy current crack.So
Afterwards blade 1-1 leading edge added with cylinder shape groove structure 1-5, since leading edge point A1, center falls in aerofoil cross section groove 1-5
Molded line on, extend to two back gauge sides, groove 1-5 diameters are the same.Leading edge adds groove structure 1-5 to be because air-flow enters Ye Dao great
Carry certain impact more, constantly increase in particular with the reduction air-flow angle of attack of flow, can so cause leading edge point A1 with before
Stationary point A3 is misaligned, and preceding stationary point A3, on pressure face, the radius very little of leading edge roundlet, the curvature of leading edge blade profile is very big, production
The very big acceleration Flow Around around leading edge roundlet of angular acceleration is given birth to, from preceding stationary point A3 around the angle streamed to the air-flow of suction surface
Degree is big, generates bigger acceleration, so easily causes gas to be separated in leading edge point, has a strong impact on bucket rear main flow
Flowing, results even in rotating stall and surge, causes very big noise and loss.Before leading edge adds groove structure 1-5 to suppress
The separation in edge point boundary layer, makes air-flow in runner more steady, improves efficiency, reduces overall noise grade.Again at leaf top
Trailing edge adds the bulge-structure 1-4 perpendicular to blade 1-1 surfaces, and reason is blade 1-1 tops while end wall annular edge interlayer be present
With wing surfaces around laminar boundary layer also have blade tip clearance flowing cause the flowing in Ye Ding regions very complicated, and due to
Axial flow blower middle period top rotary speed is maximum, is a region for adding work(amount maximum, it is necessary to control the energy loss of this part
The efficiency and pressure of blower fan could be improved.Bulge-structure 1-4 can be very good to reduce this partial loss, because Ye Ding regions are flowed
Complex boundary layer growth rate is fast, and boundary layer separation easily occurs, and forms vortex, particularly in suction surface side, passes through this
Individual bulge-structure 1-4 can effectively control the shedding frequence in the regional edge interlayer separation of leaf top and whirlpool, while the structure can be right
Big Gap cirele is cut, is combed into countless small vortex, reduces blower fan Trailing Edge Loss and eddy current crack.Finally in stator 2
Close to rectangular guiding plate 2-1 has partly been added afterwards behind the convex surface of level, because stator 2 is not only influenceed by oneself boundary layer, also
Influenceed by the interference of above impeller wakes, simultaneously because flowing of the gas in impeller 1 is extremely complex, cause the import of stator 2
Flow angle is radially very big with circumferential fluctuation, and fluid is very unstable in the runner of stator 2 and pressure face is compared in suction surface boundary layer
Border thickness much, cause suction surface flowing it is increasingly complex, and with fluid from the leading edge of stator 2 to trailing edge during, side
Interlayer constantly thickeies, so the mobility status of the control suction surface latter half fluid of stator 2, also very heavy to improving fan performance
Will, deflector 2-1 effect is that guiding air-flow moves along tangential, can be very good control due to the pressure and centrifugal force of fluid
Radial Flow caused by imbalance, while the size in a pair of channels whirlpool in blade passage can also be controlled, and the attached face of blade surface
Layer creep flowing, has also just controlled the Secondary Flow of radial motion, has reduced the uneven of speed, reduces jet Trailing Edge Loss, control
Boundary layer thickness processed, stator suction surface boundary layer separation point is moved backward, reduce energy loss, control vortex shedding, it is suppressed that
The eddy current crack caused by stator tail.The profile shaft flow fan efficiency is made more by the improvement to axial flow blower diverse location
Height, noise is lower, more energy-conserving and environment-protective.
Claims (1)
1. the axial flow blower that a kind of blade inlet edge is blown with groove structure and blade root, including it is guard, impeller, stator, inner cylinder, outer
Cylinder, motor；The guard is formed by iron wire braiding, is fixed on outer barrel；It is characterized in that：The impeller includes wheel hub and leaf
Piece, the fluted structure of blade inlet edge, vane tip trailing edge have bulge-structure, there is blowing groove on impeller hub；The blade is
The airfoil fan of circular rector Isolated Airfoil method design such as pass through, turn round speed and reduces with the increase of radius, pressure is radially constant, leaf
Piece thickness distribution is identical with NACA 4-digit number profile thickness distributions, relative thickness of airfoil be 10%-15%, blade quantity be 5-
9, blade blade tip clearance is 1%-the 2% of blade height；The blade inlet edge groove structure, center fall the type in aerofoil cross section
On line, and be uniformly distributed, channel section is shaped as circular arc, and groove runs through whole blade inlet edge, groove since leading edge point,
To the extension of the equidistant side in both sides, groove diameter is the same, and the quantity of groove is 4-10, and 1%-the 3% of a diameter of chord length, between groove
Distance be chord length 3% -8%；The vane tip trailing edge bulge-structure is shaped as cuboid, and bulge-structure is perpendicular to leaf
Piece suction surface, raised width are high 3%-6% of leaf, and length is 2-4 times of width, and thickness is that width is 1/4-1/2；Institute
Air blowing slot structure is stated, on wheel hub, close to the suction surface side of blade, the contour line of blowing groove is by blade and wheel hub suction
Face intersection offsets to obtain, and the length of blowing groove is 20%-the 30% of blade root section chord length, and the width of blowing groove is 5-10mm, is blown
For air drain completely through wheel hub wall, the distance of air blowing slot tail and blade root trailing edge is 20%-the 40% of blade root chord length；The stator is consolidated
It is scheduled on above inner cylinder and outer barrel, stator blade is circular arc plate blade, and along torsion stator is radially provided with, quantity is 7-17,
The size of the axial gap of stator impeller and impeller is 5-10mm, and the thickness of stator blade is 2-4mm, and stator is close to trailing edge
Suction surface has deflector；The deflector is evenly distributed on suction surface trailing edge part, equal in magnitude perpendicular to stator surface, with
Stator trailing edge apart from identical, with respect to guide vane height position respectively 20%, 40%, 60% and 80%, deflector length is stator leaf
20%-the 30% of root chord length, the height of deflector are 1/3-the 1/2 of length, and the thickness of deflector is identical with stator, deflector and
The distance of blade trailing edge is 3%-the 5% of vane root chord length；The motor is threephase asynchronous machine, and motor is fixed on inner cylinder
On web, impeller is connected by axle sleeve with motor shaft.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610263059.9A CN105756975B (en) | 2016-04-26 | 2016-04-26 | The axial flow blower that a kind of blade inlet edge is blown with groove structure and blade root |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610263059.9A CN105756975B (en) | 2016-04-26 | 2016-04-26 | The axial flow blower that a kind of blade inlet edge is blown with groove structure and blade root |
Publications (2)
| Publication Number | Publication Date |
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| CN105756975A CN105756975A (en) | 2016-07-13 |
| CN105756975B true CN105756975B (en) | 2018-02-27 |
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| CN201610263059.9A Active CN105756975B (en) | 2016-04-26 | 2016-04-26 | The axial flow blower that a kind of blade inlet edge is blown with groove structure and blade root |
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Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| IT201700005808A1 (en) * | 2017-01-19 | 2018-07-19 | Ansaldo Energia Spa | SHOVEL FOR A COMPRESSOR AND COMPRESSOR INCLUDING THE SHOVEL |
| CN107050542B (en) * | 2017-04-28 | 2023-07-04 | 浙江理工大学 | Miniature centrifugal blood pump capable of preventing blood cells from being damaged and circulating blood supply method thereof |
| CN107366022B (en) * | 2017-08-04 | 2022-12-20 | 中国农业科学院麻类研究所 | Pneumatic fiber anti-winding mechanism |
| IT201800005779A1 (en) * | 2018-05-28 | 2019-11-28 | OPERATING MACHINE | |
| CN108426318A (en) * | 2018-06-19 | 2018-08-21 | 奥克斯空调股份有限公司 | air channel structure and air conditioner |
| CN110173451A (en) * | 2019-07-07 | 2019-08-27 | 代元军 | A kind of blade tip is in the mining partial axial ventilator of W type structure |
| CN113153803B (en) * | 2021-04-21 | 2022-05-27 | 江苏大学 | Mixed flow pump stall operating mode impeller wake vortex dissipation device |
| CN114282327B (en) * | 2022-03-08 | 2022-05-03 | 中国空气动力研究与发展中心计算空气动力研究所 | Vortex generator cavity design method for efficiently promoting transition and vortex generator |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4035237B2 (en) * | 1998-09-30 | 2008-01-16 | 東芝キヤリア株式会社 | Axial blower |
| GB0428368D0 (en) * | 2004-12-24 | 2005-02-02 | Rolls Royce Plc | A composite blade |
| JP5929522B2 (en) * | 2012-05-31 | 2016-06-08 | 株式会社デンソー | Axial blower |
| JP6303461B2 (en) * | 2013-12-06 | 2018-04-04 | 日本電産株式会社 | Impeller and blower |
| CN205639000U (en) * | 2016-04-26 | 2016-10-12 | 浙江理工大学 | Blade leading edge takes axial fan that groove structure and blade root blew |
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Inventor after: Dou Huashu Inventor after: Xu Wenqian Inventor after: Xu Jinqiu Inventor after: Jiang Chenfeng Inventor after: Jia Huixia Inventor after: Zhang Shuo Inventor after: Chen Xiaoping Inventor after: Wei Yikun Inventor after: Yang Hui Inventor before: Dou Huashu Inventor before: Xu Jinqiu Inventor before: Jiang Chenfeng Inventor before: Jia Huixia Inventor before: Xu Wenqian Inventor before: Zhang Shuo Inventor before: Chen Xiaoping Inventor before: Wei Yikun Inventor before: Yang Hui |
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Application publication date: 20160713 Assignee: ZHEJIANG SCI-TECH UNIVERSITY SHANGYU INDUSTRIAL TECHNOLOGY RESEARCH INSTITUTE Co.,Ltd. Assignor: ZHEJIANG SCI-TECH University Contract record no.: X2020330000077 Denomination of invention: An axial flow fan with groove structure on the leading edge of blade and air blowing at blade root Granted publication date: 20180227 License type: Common License Record date: 20201022 |
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