CN108757520A - The axial flow blower of novel impeller blade - Google Patents
The axial flow blower of novel impeller blade Download PDFInfo
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- CN108757520A CN108757520A CN201810622515.3A CN201810622515A CN108757520A CN 108757520 A CN108757520 A CN 108757520A CN 201810622515 A CN201810622515 A CN 201810622515A CN 108757520 A CN108757520 A CN 108757520A
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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
- 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
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
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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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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
Abstract
The invention discloses the axial flow blowers of novel impeller blade.Existing axial flow blower is difficult that further structure optimization carrys out improving performance.The blade wheel structure of the present invention is that the section established angle in six sections on the blade of SDF-11.2 model draught fan impellers is respectively designed to βA‑A、βA‑B、βA‑C、βA‑D、βA‑E、βAStructure after-F, βA- A=49.37 °, βA- B=47.05 °, βA- C=41.15 °, βA- D=38.57 °, βA- E=44.66 °, βA- F=42.65 °；Section A be blade and wheel hub intersection, section F be leaf top section, section B, C, D, E be respectively at the leaf position of section A distance 20%, 40%, 60%, 80%.The present invention greatly improves impeller aeroperformance by 6 section established angles of change SDF-11.2 model wind turbines.
Description
Technical field
The invention belongs to axial flow blower technical fields, and in particular to a kind of axial flow blower of novel impeller blade.
Background technology
Axial flow blower is to improve gas pressure by the mechanical energy of input and supply gas side by side the machinery of body.Axial flow blower has
The characteristics of low-head, big flow, because axial flow blower has relative to centrifugal blower small, installation is simple, is widely used in state
Each field of people's economy, such as electric tool, engineering machinery, air-conditioning, electric power, metallurgy, the energy, medical and health field have very big
Application value and vast market prospect.Energy-saving and emission-reduction, sustainable development overall background under, as the rich and influential family of energy consumption, wind
Machine energy expenditure occupies national machinery industry 12%, and a large amount of market demand puies forward the efficiency and operation stability of axial flow blower
Higher requirement is gone out, has reduced noise of axial flow fan, it is axial flow blower design to increase axial flow blower flow, improve axis stream efficiency
Important technology index.Currently, being concentrated mainly on the selection of flow pattern coefficient to the research of axial ventilator and using Isolated Airfoil
Or the selection of Design of Cascade method is above, and specific speed, blade peace are primarily upon in the design of majority research axial ventilator
Fill the influences of the critical design elements to fan performance such as angle, impeller inlet and outlet flow angle.But turbomachine internal flow is complicated,
There are the diversified forms such as boundary layer separation, tail and vortex movement, have the characteristics that stickiness, compressibility and non-stationarity, because
It is very difficult that pneumatic design is unfolded to it in this.The traditional design of axial flow blower is using accurate three-dimensional design method and engineering test
Method after mutually saving, has the design experiences of designer very high requirement, but also to carry out a large amount of verification experimental verification, further according to
Test result is improved design to structure, finally finds out feasible program.Therefore on the basis of traditional design, to axial flow blower
It optimizes, further increases its efficiency as that need solve the problems, such as at present.
Invention content
The purpose of the present invention is for pressure existing for existing axial flow blower is low, efficiency is low, blade tip clearance amount of leakage is big
Phenomenon provides the axial flow blower of novel impeller blade.
The present invention includes impeller, guide vane, outer barrel, inner cylinder, motor, axle sleeve and guard；Outer barrel, guide vane and the inner cylinder is logical
Welding is crossed to be fixed together；The pedestal of motor is fixed on inner cylinder, and impeller is fixed on by axle sleeve on the output shaft of motor；Guard
It is fixed on outer barrel；Blade wheel structure is by the section established angle difference in six sections on the blade of SDF-11.2 model draught fan impellers
It is designed to βA-A、βA-B、βA-C、βA-D、βA-E、βAStructure after-F, wherein βA-A、βA-B、βA-C、βA-D、βA-E、βA- F points
Do not represent section A, B, C, D, E, F section established angle, βA- A=49.37 °, βA- B=47.05 °, βA- C=41.15 °, βA-D
=38.57 °, βA- E=44.66 °, βA- F=42.65 °.In six sections, section A is the intersection of blade and wheel hub, section F
For leaf top section, section B, C, D, E be respectively at the leaf position of section A distance 20%, 40%, 60%, 80%.
Wherein, the process of optimization of impeller blade is specific as follows：
Step 1: introducing six influence factors, i.e. six sections, six sectional uniforms are distributed in protophyll on piece, wherein
Section A is the intersection of original blade and wheel hub, and section F is leaf top section, and section B, C, D, E are respectively and section A distance
20%, at 40%, 60%, 80% leaf position；Section A, B, C, D, E, F section established angle be respectively defined as βA-A、βA-
B、βA-C、βA-D、βA-E、βA-F.Each factor takes five levels, respectively on the basis of original blade variation -10%, -5%,
0% ,+5% ,+10%, table 1 is specific factor level table, and level 1 indicates blade profile established angle on the basis of original blade
Upper to reduce 10%, level 2 indicates that section established angle reduces 5%, and level 3 indicates that section established angle is consistent with original blade, level 4
Indicate that section established angle increases 5%, level 5 indicates that section established angle increases 10%.Due to being the horizontal orthogonal test of 6 factor 5,
So choosing L25(56) orthogonal arrage carry out orthogonal optimization, do 25 groups of experiments, optimization aim is total head and efficiency.Specific test group
Testing program and numerical simulation result during conjunction is shown in Table 2.
1 factor level of table
2 testing program of table and numerical simulation result
Step 2: total head range analysis is carried out, it is specific as follows：As shown in table 3, setting mean value 1,2,3,4 and 5 indicates respectively
Each factor includes the average value of the sum of five groups of experiment total heads of level 1, level 2, level 3, level 4 and level 5, under certain factor
The bigger expression of mean value of the sum of certain horizontal total head is more conducive to improve total head.It is very poor to indicate that each factor is maximum in each horizontal mean value
Value subtracts the difference of minimum value.R is found out from very poorE>RF>RB>RA>RD>RC, RE、RF、RB、RA、RD、RCRespectively represent βA-E、βA-
F、βA-B、βA-A、βA-D、βA- C is corresponding very poor, RmaxRepresent RE、RF、RB、RA、RD、RCIn maximum value, by each section of blade
Established angle according to the primary and secondary sequence for influencing total head arrange：βA-E、βA-F、βA-B、βA-A、βA-D、βA- C, to obtain
The combination that total head can most be improved is A1、B2、C3、D5、E5、F5。A1Section A is represented in the section established angle of level 1, B2Represent section B
In section established angle, the C of level 23Represent section C level 3 section established angle, D5Section D is represented in the section of level 5 to pacify
Fill angle, E5Represent section E level 5 section established angle, F5Represent section F level 5 section established angle.
3 total head range analysis of table
Step 3: into line efficiency range analysis, it is specific as follows：As shown in table 4, setting mean value 1 ', 2 ', 3 ', 4 ' and 5 ' point
Do not indicate that each factor includes the average value of the sum of five groups of test efficiencies of level 1, level 2, level 3, level 4 and level 5, from
R is found out in very poorB>RA>RC>RD>RF>RE, each section established angle of blade is arranged according to the primary and secondary sequence influenced on efficiency
?：βA-B、βA-A、βA-C、βA-D、βA-F、βA- E, to show that it is A that can most propose efficient combination1、B2、C1、D1、E2、F2。C1
Represent section C level 1 section established angle, D1Represent section D level 1 section established angle, E2Section E is represented in level 2
Section established angle, F2Represent section F level 2 section established angle.
4 efficiency range analysis of table
Step 4: being obtained by step 3, can most improve total head is combined as A1、B2、C3、D5、E5、F5, can most carry efficient
It is combined as A1、B2、C1、D1、E2、F2, the optimum combination that comprehensive analysis obtained while improving total head and efficiency is carried out to two combinations,
Comprehensive analysis process is specific as follows：
Introduce relative quantity R/Rmax, which is meant that the ratio between the very poor value of certain factor and maximum very poor value.Due to two
A combination selects A1、B2, then optimal selection is exactly A1、B2；For section C, influence of the sections the C established angle to total head comes the 6th
Position, and R/RmaxOnly 0.1, but influence of the established angle in the sections C to efficiency comes the 3rd, and R/RmaxHave 0.78, institute
Optimal selection with the sections C is C1；For the sections D, influence of the sections the D established angle to total head comes the 5th, R/RmaxOnly
Influence of 0.27, the D section to efficiency comes the 4th, but R/RmaxReach the sections 0.66, D established angle influences bigger to efficiency,
And the influence to total head is little, so optimal selection is D1；For the sections E, influence of the sections the E established angle to total head comes the 1st
Position, R/RmaxIt is 1, and influence of the sections E to efficiency comes the 6th, R/RmaxShadow of only 0.25, the E section established angles to total head
Bigger is rung, and the influence to fan efficiency is small, so the optimal selection in the sections E is E5；For the sections F, the sections F established angle is to complete
The influence of pressure comes the 2nd, R/RmaxInfluence for the sections 0.5, F established angle to efficiency comes the 5th, R/RmaxIt is 0.31, institute
Total head is influenced greatly with the sections F established angle, it is small on efficiency influence, so the optimal selection in the sections F is F5.Therefore, total head is improved
Optimum combination with efficiency is A1、B2、C1、D1、E5、F5。
Step 5: to optimum combination A1、B2、C1、D1、E5、F5Numerical simulation is carried out, and in SDF-11.2 model draught fan impellers
Declared working condition under with SDF-11.2 model draught fan impellers carry out static pressure, total head and efficiency comparison, verify the optimum combination
To the promotion effect of blower press and efficiency.
The rated speed of the motor is 720r/min, rated power 4KW.
The wheel hub lateral surface of the impeller is 10mm with the radial clearance of inner cylinder medial surface diameter.
The quantity of the impeller blade is 6, and blade blade tip clearance is the 2% of blade height.
The quantity of the guide vane is 7~17, and the thickness of guide vane is 2~4mm.
Beneficial effects of the present invention：
1, the present invention is to carry out just blade as Optimal Parameters from blade root to the established angle in the 6 equally distributed sections in leaf top
Optimization is handed over, substantially increases impeller aeroperformance so that in entire flow rate zone, static pressure, total head, efficiency have substantially to be carried impeller
Height, specially：Impeller reduces the total head of blade middle and lower part, increases the total head of part at the top of leaf, while the entire leaf Gao Jing of impeller
Pressure is obtained for raising, makes impeller middle and lower part flow to have obtained very big improvement, has reached while having improved impeller total head and effect
The purpose of rate；
2, the size in whirlpool has obtained apparent inhibition at blade root of the invention, and the speed of whirlpool position obviously increases
Greatly, it loses and reduces caused by vortex；
3, present invention decreases the amount of leakage of blade tip clearance, and main leak area is made also to be reduced.
4, the present invention provides new approaches to the optimization design of axial flow blower, is also applied for the excellent of other model axial flow blowers
Change.
Description of the drawings
Fig. 1 is the wind turbine sectional view after present invention optimization；
Fig. 2 is the original impeller blade schematic diagram of SDF-11.2 model wind turbines；
Fig. 3 is the location map that impeller blade respectively optimizes section；
Fig. 4 is the impeller blade schematic diagram after present invention optimization.
Specific implementation mode
As shown in Figure 1, the axial flow blower of novel impeller blade, including impeller 1, guide vane 2, outer barrel 3, inner cylinder 4, motor 5, axis
Set 6 and guard 7；Outer barrel 3, guide vane 2 and inner cylinder 4 are fixed together by welding, and the pedestal of motor 5 is fixed on the web of inner cylinder 4
On, wherein the rated speed of motor 5 is 720r/min, rated power 4KW；Impeller 1 is fixed on the defeated of motor 5 by axle sleeve 6
On shaft；The wheel hub lateral surface of impeller 1 is 10mm with the radial clearance of 4 medial surface diameter of inner cylinder；Guard 7 is fixed on outer barrel 3,
There is rectification and prevents foreign matter from entering.
As shown in Figure 1, impeller 1 is driven dynamic pressure and the static pressure for improving gas to air work, the leaf on impeller 1 by motor 5
Piece is the original blade optimization of impeller according to the wind turbine of SDF-11.2 models, and blade quantity is 6, and blade blade tip clearance is
The 2% of blade height.
The process of optimization of impeller blade is specific as follows：
The definition of blade profile established angle is as shown in Fig. 2, blade profile established angle is the folder of blade profile string and front
Angle betaA.Accurately to be optimized to each section established angle of blade, six influence factors, i.e. six sections are firstly introduced into,
As shown in figure 3, six sectional uniforms are distributed on blade, wherein section A is the intersection of blade and wheel hub, and section F is leaf top
Section, section B, C, D, E be respectively at the leaf position of section A distance 20%, 40%, 60%, 80%；Section A, B, C, D,
E, the section established angle of F is respectively defined as βA-A、βA-B、βA-C、βA-D、βA-E、βA-F.In view of design error and blade plus
Work difficulty, it is -10%~+10% to take the section established angle variation range of each sectional position, to keep test sample sufficiently large, energy
Accurate response goes out true situation, and each factor takes five levels, respectively on the basis of original blade variation -10%, -5%,
0% ,+5% ,+10%, table 1 is specific factor level table, and level 1 indicates blade profile established angle on the basis of master mould
Reducing 10%, level 2 indicates that section established angle reduces 5%, and level 3 indicates that section established angle is consistent with master mould, remains unchanged,
Level 4 indicates that section established angle increases 5%, and level 5 indicates that section established angle increases 10%.Due to being the orthogonal of 6 factor, 5 level
Experiment, so having chosen L25(56) orthogonal arrage carry out orthogonal optimization, need to do 25 groups of experiments, specific test combinations are shown in Table in 2
Testing program and numerical simulation result.
1 factor level of table
2 testing program of table and numerical simulation result
Due to it is a principal object of the present invention to improve total head and efficiency as possible, so only being listed in the test result of table 2
Total head and efficiency two indices.The highest total head known to the test data in table 2 has reached 244.08pa, than original wind turbine
226.07pa has been higher by 18.01pa, opposite to improve 8%；Peak efficiency has reached 54.3%, is carried than original wind turbine 51.59%
It is high by 2.71%, it is opposite to improve 5.25.It can also be seen that test group 13,22,23 all improves the complete of wind turbine simultaneously from table 2
Pressure and efficiency, this explanation are effective come the method for improving aerodynamic performance by the established angle in each section of optimization.
3 total head range analysis of table
Then, as shown in table 3, total head range analysis is carried out, mean value 1 indicates in table 3, and each factor includes five groups of level 1
Test the average value of the sum of total head, and so on mean value 2,3,4 and 5 indicate respectively each factor include level 2, it is level 3, horizontal
4 and level 5 the sum of five groups of experiment total heads average value, and under certain factor the sum of certain horizontal total head the bigger expression of mean value more
Conducive to raising total head.It is very poor to indicate that maximum value subtracts the difference of minimum value in each horizontal mean value in each factor.It is very poor to see
It is strong and weak to go out influence of certain factor to index, can also represent susceptibility, it is very poor it is bigger illustrate to influence it is bigger.It can from very poor
Go out RE>RF>RB>RA>RD>RC, RE、RF、RB、RA、RD、RCRespectively represent βA-E、βA-F、βA-B、βA-A、βA-D、βAThe corresponding poles-C
Difference, RmaxRepresent RE、RF、RB、RA、RD、RCIn maximum value, this illustrates that the primary and secondary that each section established angle of blade influences total head is suitable
Sequence is：βA-E、βA-F、βA-B、βA-A、βA-D、βA-C.From primary and secondary sequence it is found that close to leaf top part blade profile established angle
Total head is influenced maximum；Take second place on total head influence close to leaf root part blade profile established angle；Middle part of blade section established angle pair
Total head influences very little.Compared by mean value it is found that the combination that can most improve total head is A1、B2、C3、D5、E5、F5。A1Section A is represented to exist
The section established angle of level 1, B2Represent section B level 2 section established angle, C3Section C is represented to install in the section of level 3
Angle, D5Represent section D level 5 section established angle, E5Represent section E level 5 section established angle, F5Section F is represented to exist
The section established angle of level 5.
Then, as shown in table 4, into line efficiency range analysis, setting mean value 1 ', 2 ', 3 ', 4 ' and 5 ' indicate respectively it is each because
The average value of the sum of the five groups of test efficiencies of element comprising level 1, level 2, level 3, level 4 and level 5, similarly it is found that due to
Very poor middle RB>RA>RC>RD>RF>RE, this illustrates that each section established angle of blade is on the primary and secondary sequence that efficiency influences：βA-B、βA-A、
βA-C、βA-D、βA-F、βA-E.It is found that being influenced on efficiency close to leaf root part blade profile established angle maximum from primary and secondary sequence；
Middle part of blade blade profile established angle takes second place on efficiency influence；Close to top, top part blade profile established angle does not have efficiency substantially
It influences.Compared by mean value it is found that it is A that can most propose efficient combination1、B2、C1、D1、E2、F2。
4 efficiency range analysis of table
In summary, can most improve total head is combined as A1、B2、C3、D5、E5、F5, can most carry and efficient be combined as A1、
B2、C1、D1、E2、F2.Since two kinds of optimum combinations are different, while in order to improve total head as far as possible, effect is improved as far as possible
Rate, finally, it is necessary to compromise consideration be carried out to combination in two, carry out the optimal set that comprehensive analysis obtained while improving total head and efficiency
It closes.Optimum combination is obtained to carry out synthetical comparison and assessment, and invention introduces relative quantity R/RmaxIt is analyzed, the meaning of the relative quantity
It is the ratio between the very poor value of certain factor and maximum very poor value, can indicates the relative intensity that the factor influences wind turbine index of correlation,
To the contribution degree of fan performance, the bigger contribution degree to performance in terms of wind turbine of numerical value is bigger, and 0 indicates not appoint correlated performance
What is contributed, and 1 indicates there is maximum contribution to correlated performance.For section A and B, it is easy to determine that optimal selection is exactly A1、
B2；For the C of section, influence of the sections the C established angle to total head comes the 6th, and R/RmaxOnly 0.1, but the sections C
Influence of the established angle to efficiency come the 3rd, and R/RmaxHave 0.78, so the optimal selection in the sections C is C1；D is cut
For face, influence of the sections the D established angle to total head comes the 5th, R/RmaxInfluence of the sections only 0.27, D to efficiency comes
4, but R/RmaxReach 0.66, it is therefore evident that the sections D established angle influences bigger to efficiency, and the influence to total head is little, institute
It is D with optimal selection1；For the sections E, influence of the sections the E established angle to total head comes the 1st, R/RmaxIt is 1, and E is cut
Influence in face of efficiency comes the 6th, R/RmaxOnly 0.25, this illustrates influence bigger of the sections the E established angle to total head, and right
The influence of fan efficiency is very weak, so the optimal selection in the sections E is E5；For the sections F, the sections F established angle is to total head
Influence comes the 2nd, R/RmaxInfluence for the sections 0.5, F established angle to efficiency comes the 5th, R/RmaxIt is 0.31, compares it
Under, the sections F established angle is major influence factors for total head, and for efficiency, only minor effect factor, so F is cut
The optimal selection in face is F5.It is combined as A by improve blower press and efficiency known to analysis above to greatest extent1、B2、
C1、D1、E5、F5.Since the combination does not appear in table 3 and table 4, so numerical simulation must be carried out to the combination, with true
Whether the fixed combination has achieved the purpose that while having improved blower press and efficiency to greatest extent.
Table 5 optimizes front and back fan performance comparison
Table 5 is the front and back fan performance contrast table of optimization, and the wind turbine after it can see optimization in table is than original wind turbine, performance
It is greatly improved, static pressure increases 12.52pa, and 20% is improved than in the past, and total head improves 16.1pa, compared to premise
High by 7%, efficiency increases 2.38%, relatively before improve 5%.It is seen in conjunction with table 4, highest total head is in table 4
244.08pa, and the blower press optimized has reached 242.17pa, reduces only 1.91pa, opposite reduction amount is less than 1%；Table 4
Middle peak efficiency is 54.3%, and the wind turbine after optimizing has reached 53.97%, reduces only 0.33%, and opposite reduction amount is not yet
Foot 1%.This illustrates to combine A1、B2、C1、D1、E5、F5It is reasonable, has achieved the purpose that as far as possible while improving total head and efficiency.
Wind turbine is optimized by orthogonal test and has reached the set goal.
Table 6 optimizes front and back section established angle comparison
Table 6 is the change situation of the front and back blade profile established angle of optimization, as seen from the table, the wind turbine after optimization, blade root
The section established angle of portion and middle part of blade is all reduced, and the section established angle of vane tip is all increased, such variation
It can effectively improve the aeroperformance of wind turbine.
Optimize rear fan blade shape as shown in figure 4, root of blade and the section established angle of middle part of blade are all reduced,
The section established angle of vane tip is all increased, and variation in this way can effectively improve the aeroperformance of wind turbine.Root of blade stream
Dynamic obviously to have obtained very big improvement, original blade root has a obviously whirlpool, the size in whirlpool close to leading edge vicinity
70% blade surface is occupied, the size for optimizing whirlpool at rear blade blade root has obtained apparent inhibition, the speed of whirlpool position
It significantly increases, illustrates to lose reduction caused by vortex；Blade after optimization becomes in the apparent curvature of pressure face streamline of middle part of blade
It is small, it flows in an axial direction more steady.
The present invention has been greatly improved in entire flow rate zone, static pressure, total head, efficiency, and in design discharge point, total head increases
16.1pa, relative increment 7%, static pressure increase 12.5pa, relative increment 20%, and efficiency improves 2.38%, relatively
Increment is 4.6%；Impeller reduces the total head of blade middle and lower part, increases the total head at leaf top part, while the entire leaf of impeller is high
Static pressure is obtained for raising, and impeller middle and lower part is made to flow to have obtained very big improvement, reached and meanwhile improve impeller total head and
The purpose of efficiency；The size in whirlpool has obtained apparent inhibition at blade root, and the speed of whirlpool position significantly increases, and vortex is made
At loss reduce；Blade improves the stability of air-flow at impeller outlet, reduces the leakage rate of air-flow, reduces volumetric loss, carries
High efficiency；Boundary layer separation is prevented, the frequency to fall off and reduce vortex shedding in whirlpool is inhibited, on the whole, reduces energy loss, suppression
The eddy current crack caused by guide vane tail has been made, has kept the profile shaft flow fan more efficient, noise is lower, is more energy-saving and environmentally friendly.
Claims (5)
1. the axial flow blower of novel impeller blade, including impeller, guide vane, outer barrel, inner cylinder, motor, axle sleeve and guard；Described is outer
Cylinder, guide vane and inner cylinder are fixed together by welding；The pedestal of motor is fixed on inner cylinder, and impeller is fixed on motor by axle sleeve
Output shaft on；Guard is fixed on outer barrel；It is characterized in that：Blade wheel structure is by the blade of SDF-11.2 model draught fan impellers
The section established angle in upper six sections is respectively designed to βA-A、βA-B、βA-C、βA-D、βA-E、βAStructure after-F, wherein βA-
A、βA-B、βA-C、βA-D、βA-E、βA- F respectively represent section A, B, C, D, E, F section established angle, βA- A=49.37 °, βA-B
=47.05 °, βA- C=41.15 °, βA- D=38.57 °, βA- E=44.66 °, βA- F=42.65 °；In six sections, section A
For the intersection of blade and wheel hub, section F is leaf top section, section B, C, D, E be respectively with section A distance 20%, 40%,
60%, at 80% leaf position；
Wherein, the process of optimization of impeller blade is specific as follows：
Step 1: introducing six influence factors, i.e. six sections, six sectional uniforms are distributed in protophyll on piece, wherein section
A be original blade and wheel hub intersection, section F be leaf top section, section B, C, D, E be respectively with section A distance 20%,
40%, at 60%, 80% leaf position；Section A, B, C, D, E, F section established angle be respectively defined as βA-A、βA-B、βA-
C、βA-D、βA-E、βA-F；Each factor takes five levels, respectively on the basis of original blade variation -10%, -5%, 0% ,+
5% ,+10%, table 1 is specific factor level table, and level 1 indicates that blade profile established angle reduces on the basis of original blade
10%, level 2 indicates that section established angle reduces 5%, and level 3 indicates that section established angle is consistent with original blade, and level 4 indicates to cut
Face established angle increases 5%, and level 5 indicates that section established angle increases 10%；Due to being the horizontal orthogonal test of 6 factor 5, so choosing
Take L25(56) orthogonal arrage carry out orthogonal optimization, do 25 groups of experiments, optimization aim is total head and efficiency；Specific test combinations are shown in Table
Testing program and numerical simulation result in 2；
1 factor level of table
2 testing program of table and numerical simulation result
Step 2: total head range analysis is carried out, it is specific as follows：As shown in table 3, setting mean value 1,2,3,4 and 5 indicates each respectively
Factor includes the average value of the sum of five groups of experiment total heads of level 1, level 2, level 3, level 4 and level 5, certain water under certain factor
The bigger expression of mean value of the sum of flat total head is more conducive to improve total head；It is very poor to indicate that each factor maximum value in each horizontal mean value subtracts
Go the difference of minimum value；R is found out from very poorE>RF>RB>RA>RD>RC, RE、RF、RB、RA、RD、RCRespectively represent βA-E、βA-F、
βA-B、βA-A、βA-D、βA- C is corresponding very poor, RmaxRepresent RE、RF、RB、RA、RD、RCIn maximum value, each section of blade is pacified
Dress angle according to the primary and secondary sequence for influencing total head arrange：βA-E、βA-F、βA-B、βA-A、βA-D、βA- C, to obtain most
The combination that total head can be improved is A1、B2、C3、D5、E5、F5；A1Section A is represented in the section established angle of level 1, B2Section B is represented to exist
Section established angle, the C of level 23Represent section C level 3 section established angle, D5Section D is represented to install in the section of level 5
Angle, E5Represent section E level 5 section established angle, F5Represent section F level 5 section established angle；
3 total head range analysis of table
Step 3: into line efficiency range analysis, it is specific as follows：As shown in table 4, setting mean value 1 ', 2 ', 3 ', 4 ' and 5 ' difference table
Show that each factor includes the average value of the sum of five groups of test efficiencies of level 1, level 2, level 3, level 4 and level 5, from very poor
In find out RB>RA>RC>RD>RF>RE, each section established angle of blade according to the primary and secondary sequence for influencing efficiency arrange：
βA-B、βA-A、βA-C、βA-D、βA-F、βA- E, to show that it is A that can most propose efficient combination1、B2、C1、D1、E2、F2；C1Generation
Section established angle, Ds of the table section C in level 11Represent section D level 1 section established angle, E2Section E is represented in level 2
Section established angle, F2Represent section F level 2 section established angle；
4 efficiency range analysis of table
Step 4: being obtained by step 3, can most improve total head is combined as A1、B2、C3、D5、E5、F5, can most propose efficient combination
For A1、B2、C1、D1、E2、F2, the optimum combination that comprehensive analysis obtained while improving total head and efficiency is carried out to two combinations, it is comprehensive
Analytic process is specific as follows：
Introduce relative quantity R/Rmax, which is meant that the ratio between the very poor value of certain factor and maximum very poor value；Due to two groups
Conjunction selects A1、B2, then optimal selection is exactly A1、B2；For section C, influence of the sections the C established angle to total head comes the 6th,
And R/RmaxOnly 0.1, but influence of the established angle in the sections C to efficiency comes the 3rd, and R/RmaxHave 0.78, so C
The optimal selection in section is C1；For the sections D, influence of the sections the D established angle to total head comes the 5th, R/RmaxOnly 0.27, D
Influence of the section to efficiency comes the 4th, but R/RmaxReach the sections 0.66, D established angle influences bigger to efficiency, and to complete
The influence of pressure is little, so optimal selection is D1；For the sections E, influence of the sections the E established angle to total head comes the 1st, R/
RmaxIt is 1, and influence of the sections E to efficiency comes the 6th, R/RmaxInfluence of only 0.25, the E section established angles to total head is more
Greatly, the influence and to fan efficiency is small, so the optimal selection in the sections E is E5；For the sections F, the sections F established angle is to total head
Influence comes the 2nd, R/RmaxInfluence for the sections 0.5, F established angle to efficiency comes the 5th, R/RmaxIt is 0.31, so F is cut
Face established angle influences greatly total head, small on efficiency influence, so the optimal selection in the sections F is F5；Therefore, total head and efficiency are improved
Optimum combination be A1、B2、C1、D1、E5、F5；
Step 5: to optimum combination A1、B2、C1、D1、E5、F5Numerical simulation is carried out, and in the volume of SDF-11.2 model draught fan impellers
Determine the comparison with SDF-11.2 model draught fan impellers progress static pressure, total head and efficiency under operating mode, verifies the optimum combination to wind
The promotion effect of machine total head and efficiency.
2. the axial flow blower of novel impeller blade according to claim 1, it is characterised in that：The rated speed of the motor
For 720r/min, rated power 4KW.
3. the axial flow blower of novel impeller blade according to claim 1, it is characterised in that：On the outside of the wheel hub of the impeller
The radial clearance of face and inner cylinder medial surface diameter is 10mm.
4. the axial flow blower of novel impeller blade according to claim 1, it is characterised in that：The quantity of the impeller blade
It it is 6, blade blade tip clearance is the 2% of blade height.
5. the axial flow blower of novel impeller blade according to claim 1, it is characterised in that：The quantity of the guide vane is 7
~17, the thickness of guide vane is 2~4mm.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001099093A (en) * | 1999-09-30 | 2001-04-10 | Mitsubishi Electric Corp | Blower and refrigerator using the same |
| CN202707609U (en) * | 2012-08-06 | 2013-01-30 | 株洲联诚集团有限责任公司 | Internal-circulation cooling axial-flow impeller for gas turbine generator |
| CN205638999U (en) * | 2016-04-26 | 2016-10-12 | 浙江理工大学 | Blade area wing section guide plate and stator have bionical tail edge's axial fan |
| CN107061329A (en) * | 2017-04-24 | 2017-08-18 | 浙江理工大学 | A kind of axial flow blower |
| CN206738198U (en) * | 2017-04-24 | 2017-12-12 | 浙江理工大学 | A kind of axial flow blower |
-
2018
- 2018-06-15 CN CN201810622515.3A patent/CN108757520B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001099093A (en) * | 1999-09-30 | 2001-04-10 | Mitsubishi Electric Corp | Blower and refrigerator using the same |
| CN202707609U (en) * | 2012-08-06 | 2013-01-30 | 株洲联诚集团有限责任公司 | Internal-circulation cooling axial-flow impeller for gas turbine generator |
| CN205638999U (en) * | 2016-04-26 | 2016-10-12 | 浙江理工大学 | Blade area wing section guide plate and stator have bionical tail edge's axial fan |
| CN107061329A (en) * | 2017-04-24 | 2017-08-18 | 浙江理工大学 | A kind of axial flow blower |
| CN206738198U (en) * | 2017-04-24 | 2017-12-12 | 浙江理工大学 | A kind of axial flow blower |
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