CN105736426A - Axial flow fan comprising blade pressure surfaces with winglets and blade tops with blowing structures - Google Patents
Axial flow fan comprising blade pressure surfaces with winglets and blade tops with blowing structures Download PDFInfo
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- CN105736426A CN105736426A CN201610263041.9A CN201610263041A CN105736426A CN 105736426 A CN105736426 A CN 105736426A CN 201610263041 A CN201610263041 A CN 201610263041A CN 105736426 A CN105736426 A CN 105736426A
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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
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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
- 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
- F04D29/26—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
- F04D29/40—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
- F04D29/542—Bladed diffusers
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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
- F04D29/40—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
- F04D29/542—Bladed diffusers
- F04D29/544—Blade shapes
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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
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/68—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
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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
- F04D29/68—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
- F04D29/682—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid extraction
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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
- F04D29/68—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
- F04D29/684—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses an axial flow fan comprising blade pressure surfaces with winglets and blade tops with blowing structures. The axial flow fan comprises a mesh enclosure, an impeller, guide blades, an inner cylinder, an outer cylinder and a motor, wherein the mesh enclosure formed by weaving of iron wires is fixed on the outer cylinder, and the impeller comprises a hub and blades. The blade top blowing structures are added on the blade tops, winglet structures are added at the tails of blade force suction surfaces, and the inner cylinder at the guide-blade-grade outer end is provided with rectangular holes, so that blade top flowing conditions can be improved, blade top leakage and vortex loss are reduced, noise generated in gaps is reduced, radially moving secondary flow is controlled, boundary layer thickness of blade surfaces is controlled, vortex noise caused by blade wakes is inhibited, vortex guide blade-grade vortex shedding frequency is decreased and outlet noise is reduced. Based on improvements on different positions of an existing axial flow fan, the axial flow fan is higher in efficiency, lower in noise and more energy saving and environment friendly.
Description
Technical field
The invention belongs to blower fan technical field, wear winglet particularly to a kind of blade pressure and Ye Ding has the axial flow blower of blowing structure.
Background technology
Axial flow blower is dependent on the mechanical energy of input, improves gas pressure and supplies gas side by side the machinery of body.It is widely used in the ventilation of factory, mine, tunnel, cooling tower, vehicle, boats and ships and building, dust discharge and cooling；The ventilation of boiler and industrial furnace and air inducing；Cooling in the apparatus of air conditioning and domestic electric appliance and ventilation；The drying of corn and selecting and recommending；The propelling etc. of the inflation of wind-tunnel wind regime and aircushion vehicle, all has very important application in national economy every profession and trade.According to statistics, blower fan electricity consumption accounts for the 10% of national generating capacity, and coal master to be led to machine average current drain and be accounted for the 16% of mine power consumption；The blower fan power consumption of metal mine accounts for the 30% of mining electricity consumption；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 the 17% of coal industry electricity consumption.As can be seen here, Fan Energy-saving status in each department of national economy and effect are very important.Due to, the specific speed of axial flow blower is higher, and so it has the advantages that flow is big, total head is low, all occupies irreplaceable status in these industries.
Therefore the axial fan that design optimization goes out efficiency height, performance is good, noise is low, energy-conservation is critically important.But axial flow blower flows extremely complex property, is mainly reflected in: 1) flow three-dimensionality；2) viscosity of fluid；3) non-stationarity flowed.Traditional fan design is difficult to consider 3 point above, even if modern Design having been used CFD do Aided Design, but three factors impact on fan performance above cannot be controlled completely, wherein the factor of most critical is the viscosity of fluid, and it is meet the blade wake passing vortex that Kutta-Joukowsky condition is formed that viscosity not only has influence on exit edge of blade.Owing to viscosity, blade surface and ring wall channel surface all can exist viscous boundary layer, between them and and main flow between have strong interaction, produce so-called " Secondary Flow " phenomenon.Secondary flow is the main contributor that axial flow blower loss rises, efficiency declines.Simultaneously as the impact of viscosity, making to exist in axial flow blower aerodynamic noise, the aerodynamic noise of axial flow blower is mainly made up of two parts: rotational noise and eddy current crack.If fan outlet is directly discharged into air, also has exhaust noise.
In sum, the axial fan that design optimization goes out efficiency height, performance is good, noise is low, energy-conservation is wanted, it is simply that will control and reduce secondary flow, control and reduction boundary layer thickness, prevent vortex shedding or control the formation in whirlpool.
Summary of the invention
It is an object of the invention to cannot pass through traditional design for the deficiencies in the prior art and well control the boundary layer thickness in axial flow blower, Secondary Flow and eddy current crack, there is provided a kind of blade pressure to wear winglet and Ye Ding has the axial flow blower of blowing structure, leaf top blowing structure is added on blade and blade top, blade suction surface afterbody adds little wing structure, with processing rectangular opening on the inner core of the stator level port of export, it is possible to improve the mobility status on leaf top；Reduce leaf top leakage loss, eddy current loss；Reduce the noise that gap produces；Control the Secondary Flow of radial motion；Control blade surface boundary layer thickness；Inhibit the eddy current crack that blade wake passing causes；Reduce whirlpool stator level vortex shedding frequency, reduce outlet noise.By the improvement of axial flow blower diverse location makes this profile shaft flow fan in hgher efficiency, noise is lower, more energy-conserving and environment-protective.
The technical solution used in the present invention is: a kind of blade pressure wears winglet and Ye Ding has the axial flow blower of blowing structure, including guard, impeller, stator, inner core, urceolus, motor；Described guard is to have iron wire braiding to form, and is fixed on urceolus；It is characterized in that: described impeller includes wheel hub and blade, and blade suction surface afterbody has little wing structure, and blade tip has gas hole structure；Described blade is the airfoil fan design of circular rector Isolated Airfoil method such as passing through, turn round speed to reduce along with the increase of reducing, pressure is radially constant, vane thickness distribution is identical with NACA 4-digit number profile thickness distribution, relative thickness of airfoil is 10%-15%, blade quantity is 5-9, and blade blade tip clearance is the 1%-2% of blade height；Described blade suction surface winglet is evenly distributed on blade, the position high relative to leaf is respectively 20%, 40%, 60% and 80% 4 position, the tail end of winglet is perpendicular to blade surface, leading edge and blade surface have 30-60 °, and middle excessive by SPL, the chord length of each cross section winglet is equal, account for mean radius and go out about the 1/4-1/3 of chord length, winglet thickness is 4-8mm, and winglet height is the 30%-60% of its chord length, and the trailing edge distance blade trailing edge of winglet has the blade mean chord of 5%-10%；Described leaf top blowing structure, it is from vane tip pressure face perforate, high pressure gas physical ability is made to flow through blade tip clearance, gas hole is evenly distributed on the mean camber line of leaf top aerofoil section, the diameter in hole is the 5-10% of chord length, distance between aperture is the 10%-20% of chord length, and pressure face aperture is mainly evenly distributed in the region of the high 85%-90% of leaf；Described stator is fixed on above inner core and urceolus, and stator blade is circular arc plate blade, and along radially not reversing, stator quantity is 7-17, the axial gap of stator impeller and impeller be sized to 5-10mm, the thickness of stator blade is 2-4mm；Described inner core, at place's gas segment trailer, has rectangular opening；Described rectangular opening even structure be distributed on the whole circumference of inner core, the length of rectangular opening is the 3%-5% of inner core circumferential length, and the length-width ratio of rectangular saw-tooth is 2-4, and the quantity of rectangular opening is between 10-30；Described motor is threephase asynchronous machine, and motor is fixed on the web of inner core, and impeller is connected with motor shaft by axle sleeve.
Beneficial effects of the present invention:
The present invention by having added leaf top blowing structure on the top of impeller blade, the high energy gas of pressure face can be blown into the boundary layer region of blade tip clearance, boundary layer thickness can well be controlled, prevent the formation of gas backstreaming and tip vortex and come off, such that it is able to effectively improve the leakage flow at leaf top place, reduce flow losses, improve the low energy fluid caused due to leakage flow at leaf top place and assemble, block the problem of runner, thus reducing noise.This axial fan has added four winglets uniformly on the suction surface afterbody of impeller blade simultaneously, winglet can guide air-flow to move along tangential, the Radial Flow owing to pressure and the centrifugal force imbalance of fluid cause can well be controlled, the size in pair of channels whirlpool in blade passage can also be controlled simultaneously, flow with blade surface boundary-layer creep, also the Secondary Flow of radial motion has just been controlled, reduce the uneven of speed, reduce jet Trailing Edge Loss, control boundary layer thickness, make blade suction surface boundary layer separation point rearward movement, reduce energy loss, control vortex shedding, inhibit the eddy current crack owing to blade wake passing causes.The inner core rear portion of stator level is also designed to the shape of rectangular opening, can effectively control the shedding frequence in boundary layer thickness and whirlpool, big Passage Vortex can be cut, be carded to countless little eddy current by this structure simultaneously, and the viscosity air-flow of fan blade root is effectively separated, leads, cause and become desired airflow, reduce blower fan Trailing Edge Loss and eddy current crack.By the improvement of axial flow blower diverse location makes this profile shaft flow fan in hgher efficiency, noise is lower, more energy-conserving and environment-protective.
Accompanying drawing explanation
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 impeller blade pressure face schematic diagram of the present invention.
Fig. 4 is the impeller blade suction surface schematic diagram of the present invention.
Fig. 5 is the winglet sectional view of the present invention.
Fig. 6 is the stator level blade wheel structure figure of the present invention.
Fig. 7 is the vane airfoil profile Cross section Design schematic diagram of the present invention.
Detailed description of the invention
Below in conjunction with drawings and Examples, the invention will be further described.
As it is shown in figure 1, this axial fan is made up of 6 parts, including 1, impeller 2, inner core 3, motor 4, stator 5, urceolus 6, guard；Urceolus 5, stator 4 and inner core 2 are fixed together by welding, and motor 3 is fixed on the web of inner core 2, and wherein the running parameter of motor 3 is 720r/min, and power is 4KW；Impeller 1 is fixed on motor 3 axle by axle sleeve, and the gap of the wheel hub of impeller 1 and inner core 3 is 10mm；Guard 6 is arranged on urceolus 5, has rectification and the effect preventing foreign body from entering.
As shown in Fig. 1,2,3,5, impeller 1 has motor 3 to drive to air work, improve dynamic pressure and the static pressure of gas, blade 1-1 on impeller 1 is the airfoil fan design of circular rector Isolated Airfoil method such as passing through, turning round speed to reduce along with the increase of reducing, pressure is radially constant, and blade relative thickness is 10%, blade quantity is 6, and blade blade tip clearance is the 2% of blade height.Impeller blade design concrete grammar is as follows:
The simple radial equilibrium equation of axial fan internal flow:
Wherein P represents fluid micellar pressure experienced, and Cu is the speed that fluid micellar pivots, and r is the radius of turn of fluid micellar.Formula represents that axial flow blower is internal and assumes do not have Radial Flow, then the centrifugal force balance that optional position fluid micellar pressure experienced P diametrically and fluid micellar rotary motion produce.
In formula (2)-(3), Pt is the stagnation pressure of gas, and ρ is the density of gas, C is the sum velocity of gas, the circumferential speed of Cu, Ca, Cr respectively gas, circumferential speed, radial velocity, but there is known Cr=0 assumed above, and the stagnation pressure of gas adds static pressure equal to dynamic pressure.
The differential relationship such as formula (4) of Pt, P, Cu, Ca can be obtained by formula (2)-(3). formula (4) back substitution is entered formula (1) can be obtained by another kind of more general simple radial equilibrium equation (5).
Assuming that stagnation pressure Pt is radially constant etc. circular rector method for designing, axial velocity Ca is also radially constant, substitutes in formula (5) known:
By formula above it can be seen that etc. circular rector method for designing assume blower interior Cr=0 exactly, and stagnation pressure Pt is radially constant, and axial velocity Ca is also radially constant, and circumferential speed reduces along with the increase of radius.
Formula (7) is derived by Theories of Cascades, and one about solidity of blades, blade turns round speed, leaf grating lift coefficient, and average relative in leaf gratingBetween relation.
Isolated Airfoil method for designing just assumes that the lift coefficient of leaf gratingNot by the interference of blade, the namely lift coefficient of leaf grating between leaf gratingThe lift coefficient of Isolated AirfoilIdentical.
It is exactly described above etc. circular rector Isolated Airfoil method for designing, chord length and the established angle in each cross section of blade just can be calculated by above method, vane inlet airflow machine and blade exit airflow machine, just can calculate the shape of mean camber line plus some empirical equations by parameter above, taking relative thickness of airfoil is 10%, then, the mean camber line superposition NACA 4-digit number profile thickness in each cross section is distributed, and obtains each aerofoil section.NACA aerofoil profile is the profile set that American National aviation information committee (NationalAdvisoryCommitteeforAeronautics) is delivered, and 4-digit number aerofoil profile is its conventional profile set, and method for designing is as follows:
NACA 4-digit number profile thickness distribution function equation is:
Wherein: t represents relative thickness,, b is chord length, and with the profound line of aerofoil profile for X-axis, zero is placed in airfoil fan leading edge point,。
Method is as follows, and first, taking relative thickness is 10%, obtains N number of discrete point of blade different cross section thickness profile function, then, each cross section mean camber line is also carried out decile obtains N number of discrete point simultaneously, and the slope of each point normal is asked for by calculus of finite differences, then obtain inclination angle, so can be obtained by the coordinate points of aerofoil profile upper and lower surface after convertingThen can be obtained by aerofoil profile needed for cross section with coupling together of line smoothing, as it is shown in fig. 7, a1 is thickness profile function, a4 is blade mean camber line, and a2 and a3 is normal and the tangent line of mean camber line any point.
As shown in Figure 2,3, the suction surface trailing edge of the blade 1-1 on impeller 1 is uniform-distribution with 4 winglet 1-2, B1, B2, B3, B4, Fig. 4 is the sectional view of B2 place airfoil fan 1-1 and winglet 1-2, the position high relative to leaf is respectively 20%, 40%, 60% and 80% 4 position, distance d4 between winglet 1-2 is 56mm, and the tail end of winglet 1-2 is perpendicular to the angle of blade 1-1 surface, leading edge and blade 1-1 surface normalIt it is 30 °, middle excessive by SPL, the chord length of each cross section winglet 1-2 is equal, account for blade 1-1 mean radius and go out about the 1/3 of chord length d6, winglet 1-1 thickness d 3 is 5mm, winglet 1-2 height d5 is the 40% of its chord length, and the trailing edge of winglet 1-2 is to the blade 1-1 mean chord that distance d7 is 5% of blade trailing edge.
As shown in Fig. 2,3,5, there is top blowing structure 1-3 on blade 1-1 top on impeller 1, described leaf top blowing structure 1-3, is from vane tip pressure face perforate, makes high pressure gas physical ability flow through blade tip clearance, gas hole is evenly distributed on the mean camber line A of leaf top aerofoil section, diameter d2 is chord length the 5% of hole, is sized to 8mm, and the distance d1 between aperture is the 15% of chord length, being sized to 30mm, pressure face aperture is mainly evenly distributed in the region of the high 85%-90% of leaf.
As a shown in Figure 6, stator 4 is fixed on above inner core 2 and urceolus 5, and stator 4 is circular arc plate blade, is 9 along radially not reversing stator quantity, the axial gap of stator 4 impeller and impeller 1 be sized to 10mm, the thickness of stator 4 blade is 4mm；Inner core 2, at outlet side afterbody, has rectangular opening 2-1；Described rectangular opening structure 2-1 is evenly distributed on the whole circumference of inner core, and the length of rectangular opening is the 3% of inner core circumferential length, is sized to 60mm, and the length-width ratio of rectangular saw-tooth is 2, and the quantity of rectangular opening is at 14.
First the present invention has added leaf top blowing structure 1-2 at this axial flow blower on the top of impeller 1 blade 1-1, boundary layer thickness can well be controlled, prevent the formation of gas backstreaming and tip vortex and come off, such that it is able to effectively improve the leakage flow at leaf top place, reduce flow losses, improve the low energy fluid caused due to leakage flow at leaf top place and assemble, block the problem of runner, thus reducing noise.nullOn the suction surface afterbody of impeller 1 blade 1-1, four winglet 1-2 have been added uniformly at this axial fan simultaneously，Reason be border, specific pressure face, suction surface boundary region thickness many，Cause that suction surface flowing is considerably complicated，And along with in fluid process from leading edge to trailing edge，Suction surface adverse pressure gradient constantly increases，Cause that suction surface boundary region constantly thickeies，So the mobility status of controlled suction face latter half fluid，It is very crucial to improving fan performance，The effect of winglet 1-2 is to guide air-flow to move along tangential，The Radial Flow owing to pressure and the centrifugal force imbalance of fluid cause can well be controlled，The size in pair of channels whirlpool in blade 1-1 runner can also be controlled simultaneously，Flow with the boundary-layer creep of blade 1-1 surface，Also the Secondary Flow of radial motion has just been controlled，Reduce the uneven of speed，Reduce jet Trailing Edge Loss，Control boundary layer thickness，Make blade suction surface boundary layer separation point rearward movement，Reduce energy loss、Control vortex shedding，Inhibit the eddy current crack owing to blade 1-1 tail causes.The last shape 2-1 being also designed to rectangular opening at inner core 2 rear portion of stator 4 grades, through optimizing design, find that this structure can effectively reduce stator 4 tail noise, reason is that stator 4 is in the 4 grades of passages of stator made due to the superposition of blade 1-1 tail and stator 4 boundary region after movable vane to flow complexity very, and the flow boundary layer air near wheel hub and inner core 2 side can increase further, namely there is very big vortex in the close inner core 2 side outlet air-flow of stator 4 grades.Therefore go out rectangular opening 2-1 in the export processing of inner core 2, can effectively control the shedding frequence in boundary layer thickness and whirlpool, big Passage Vortex can be cut, be carded to countless little eddy current by this structure simultaneously, and the viscosity air-flow of fan blade root is effectively separated, leads, cause and become desired airflow, reduce blower fan Trailing Edge Loss and eddy current crack.By the improvement of axial flow blower diverse location makes this profile shaft flow fan in hgher efficiency, noise is lower, more energy-conserving and environment-protective.
Claims (1)
1. blade pressure wears winglet and Ye Ding has the axial flow blower of blowing structure, including guard, impeller, stator, inner core, urceolus, motor；Described guard is to have iron wire braiding to form, and is fixed on urceolus；It is characterized in that: described impeller includes wheel hub and blade, and blade suction surface afterbody has little wing structure, and blade tip has gas hole structure；Described blade is the airfoil fan design of circular rector Isolated Airfoil method such as passing through, turn round speed to reduce along with the increase of reducing, pressure is radially constant, vane thickness distribution is identical with NACA 4-digit number profile thickness distribution, relative thickness of airfoil is 10%-15%, blade quantity is 5-9, and blade blade tip clearance is the 1%-2% of blade height；Described blade suction surface winglet is evenly distributed on blade, the position high relative to leaf is respectively 20%, 40%, 60% and 80% 4 position, the tail end of winglet is perpendicular to blade surface, leading edge and blade surface have 30-60 °, and middle excessive by SPL, the chord length of each cross section winglet is equal, account for mean radius and go out about the 1/4-1/3 of chord length, winglet thickness is 4-8mm, and winglet height is the 30%-60% of its chord length, and the trailing edge distance blade trailing edge of winglet has the blade mean chord of 5%-10%；Described leaf top blowing structure, it is from vane tip pressure face perforate, high pressure gas physical ability is made to flow through blade tip clearance, gas hole is evenly distributed on the mean camber line of leaf top aerofoil section, the diameter in hole is the 5-10% of chord length, distance between aperture is the 10%-20% of chord length, and pressure face aperture is mainly evenly distributed in the region of the high 85%-90% of leaf；Described stator is fixed on above inner core and urceolus, and stator blade is circular arc plate blade, and along radially not reversing, stator quantity is 7-17, the axial gap of stator impeller and impeller be sized to 5-10mm, the thickness of stator blade is 2-4mm；Described inner core, at place's gas segment trailer, has rectangular opening；Described rectangular opening even structure be distributed on the whole circumference of inner core, the length of rectangular opening is the 3%-5% of inner core circumferential length, and the length-width ratio of rectangular saw-tooth is 2-4, and the quantity of rectangular opening is between 10-30；Described motor is threephase asynchronous machine, and motor is fixed on the web of inner core, and impeller is connected with motor shaft by axle sleeve.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201610263041.9A CN105736426A (en) | 2016-04-26 | 2016-04-26 | Axial flow fan comprising blade pressure surfaces with winglets and blade tops with blowing structures |
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| CN201610263041.9A CN105736426A (en) | 2016-04-26 | 2016-04-26 | Axial flow fan comprising blade pressure surfaces with winglets and blade tops with blowing structures |
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Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106704261A (en) * | 2016-12-07 | 2017-05-24 | 浙江理工大学 | Axial flow fan ternary impeller with vein-shaped structure and nonuniform empennage |
| CN106762825A (en) * | 2016-12-07 | 2017-05-31 | 浙江理工大学 | Axial flow blower 3 d impeller with leaf vein texture and circular arc post splitterr vanes |
| CN106762824A (en) * | 2016-12-07 | 2017-05-31 | 浙江理工大学 | Axial flow blower 3 d impeller with leaf vein texture and sea-gull type splitterr vanes |
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| CN114526249A (en) * | 2021-12-17 | 2022-05-24 | 可孚医疗科技股份有限公司 | Two-stage centrifugal impeller fan for air pressurization system of breathing machine |
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| CN106762824A (en) * | 2016-12-07 | 2017-05-31 | 浙江理工大学 | Axial flow blower 3 d impeller with leaf vein texture and sea-gull type splitterr vanes |
| CN106837867A (en) * | 2016-12-07 | 2017-06-13 | 浙江理工大学 | Axial flow blower 3 d impeller with leaf vein texture and splitterr vanes |
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| CN107061348A (en) * | 2017-02-24 | 2017-08-18 | 西华大学 | A kind of extremely low specific speed centrifugal pump impeller |
| CN107061329A (en) * | 2017-04-24 | 2017-08-18 | 浙江理工大学 | A kind of axial flow blower |
| CN107050542A (en) * | 2017-04-28 | 2017-08-18 | 浙江理工大学 | Minitype centrifugal blood pump and its circulation blood supply method that a kind of anti-haemocyte is damaged |
| 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 |
| CN107050543A (en) * | 2017-05-04 | 2017-08-18 | 浙江理工大学 | A kind of microminiature micro-centrifugal blood pump with self-regulation blade |
| CN107143527A (en) * | 2017-06-06 | 2017-09-08 | 浙江理工大学 | Mini-type spiral pump and its workflow that a kind of multistage is prewhirled |
| CN107143527B (en) * | 2017-06-06 | 2023-09-08 | 湖南司诺精密机械有限公司 | Multistage pre-rotation micro screw pump and working flow thereof |
| CN109707668A (en) * | 2019-01-30 | 2019-05-03 | 霍通恩 | A kind of low noise aial flow impeller structure with noise elimination cavity |
| CN111156201A (en) * | 2019-12-30 | 2020-05-15 | 江汉大学 | Axial flow fan and guide vane thereof |
| CN111396357A (en) * | 2020-03-10 | 2020-07-10 | 南京航空航天大学 | Micro-jet forming method for controlling leakage flow of blade tip of compressor rotor |
| TWI736181B (en) * | 2020-03-18 | 2021-08-11 | 奇鋐科技股份有限公司 | Jet structure of fan rotor |
| US11346370B2 (en) | 2020-04-07 | 2022-05-31 | Asia Vital Components Co., Ltd. | Jet structure of fan rotor |
| CN112032110A (en) * | 2020-09-25 | 2020-12-04 | 依必安派特风机(上海)有限公司 | Axial fan's wind-guiding circle and axial fan |
| CN113217462A (en) * | 2021-06-08 | 2021-08-06 | 西北工业大学 | Subsonic vortex blowing type compressor blade |
| CN114526249A (en) * | 2021-12-17 | 2022-05-24 | 可孚医疗科技股份有限公司 | Two-stage centrifugal impeller fan for air pressurization system of breathing machine |
| CN117948290A (en) * | 2024-03-22 | 2024-04-30 | 河北冀力重型机械设备有限公司 | High-air-volume high-pressure axial flow fan |
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