CN109763995A - A kind of axial-flow pump impeller design method based on wheelbase - Google Patents

A kind of axial-flow pump impeller design method based on wheelbase Download PDF

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CN109763995A
CN109763995A CN201910113073.4A CN201910113073A CN109763995A CN 109763995 A CN109763995 A CN 109763995A CN 201910113073 A CN201910113073 A CN 201910113073A CN 109763995 A CN109763995 A CN 109763995A
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section
impeller
correction factor
axial
specific speed
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CN109763995B (en
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吴贤芳
田骁
谈明高
刘厚林
王凯
王勇
董亮
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Jiangsu University
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Jiangsu University
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Priority to PCT/CN2019/077064 priority patent/WO2020164168A1/en
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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
    • F04D29/18—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F04D3/005—Axial-flow pumps with a conventional single stage rotor
    • 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
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially adapted for liquid 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
    • F04D29/18—Rotors
    • F04D29/181—Axial flow rotors
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • F05D2240/30—Characteristics of rotor blades, i.e. of any element transforming dynamic fluid energy to or from rotational energy and being attached to a rotor
    • F05D2240/301—Cross-sectional characteristics
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2113/00—Details relating to the application field
    • G06F2113/08—Fluids

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • General Physics & Mathematics (AREA)
  • Theoretical Computer Science (AREA)
  • Pure & Applied Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
  • Mathematical Optimization (AREA)
  • Mathematical Analysis (AREA)
  • Computational Mathematics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention belongs to fluid machinery design fields, disclose a kind of axial-flow pump impeller design method based on wheelbase；The following steps are included: (1) is with axial-flow pump impeller axial length L design function L=l × sin βLBased on, according to given axial-flow pump design discharge Q, lift H, revolving speed n, specific speed nsDesign parameter equidistantly divides section from impeller hub to impeller outer edge, passes through specific speed nsDetermine section number and the number of blade；Then the aerofoil profile chord length l and blade angle β of axial-flow pump impeller are determinedL；(2) with aerofoil profile chord length l and blade angle βLFor benchmark coefficient, impeller diameter D, hub diameter d are determinedh, pitch t；(3) 791 profile thickness changing rules of selection carry out thickening vanes.

Description

A kind of axial-flow pump impeller design method based on wheelbase
Technical field
The invention belongs to fluid machinery design field, refer in particular to be related to a kind of axial-flow pump impeller design method based on wheelbase.
Background technique
Pumping plant and sluice are the important components of the engineerings such as water conservancy, environmental protection, city water supply and sewage and enterprise waterworks, wherein pumping It is drainage and irrigation equipment, lock is the low water head hydraulic structure for adjusting water level, controlling flow.The construction of conventional pump lock generallys use axial-flow type The mode that water pump and sluice combine, i.e., along river cross-section, in one fan brake door of intermediate arrangement, gate both sides respectively arrange one The form of platform water pump.The pump of this pump lock, lock separate design cause conventional pump lock displacement far below actual needs, and flood season is often It cannot timely and effectively carry out dredging flood, carry out river and change the efficiency of water pollution treatment also well below ideal value, while this arrangement side Formula also limits the cross-section of river in river, slows down river-flow, unfavorable to the water quality exchanges and water circulation in inland river, Bu Nengman The requirement of sufficient inland river water ecological environment, weakens the self-purification capacity in river.
Novel all-in-one pump lock, pump group is directly arranged on gate, gate be both water-retaining structure again water pump support Basis is combined into one sluice and pumping plant.Compared with conventional pump lock, integration pump lock has the advantages that (1) pumps right angle setting In on gate, not needing additional pump chamber, the area of passage in river can be made to increase 1 times or more when rising lock, pump can be obvious when falling lock Improve drainage speed；(2) switchgear house, water pump, gate and flap valve are only needed, main building is not built, does not assist Oil, Water, Gas system, Occupied area is small, easy for construction, quick, to reduce the civil engineering and electromechanical equipment investment of pumping plant；(3) pass through installation liquid level control The auxiliary equipment such as system processed and air lock automatic control system, can make whole system linkage control, really realize it is unattended, from Dynamic control significantly reduces pump lock later period personnel's maintenance cost.
Design about integration pump lock at present focuses mostly on the pond flow regime before and after optimization gate structure and with improvement Research；Axial-flow pump is typically all the direct type selecting from existing product as the crucial power-equipment of integration pump lock.In fact, Due to the limitation of gate thickness, integration pump lock requires the axial length of axial-flow pump short as far as possible.Axial-flow pump axial length Excessive, gate is thicker, causes design, manufacture, operation and the maintenance cost of integration pump lock that can all be substantially improved, while gate Response speed can also decline to a great extent.This allow for existing axial-flow pump product be not well positioned to meet integration pump lock structure and Performance requirement.Therefore, there is an urgent need to develop a kind of simple and practical axial-flow pump impeller design method based on wheelbase, so that it was both It can guarantee axial-flow pump hydraulic performance, and can effectively control the axial length of axial-flow pump impeller according to actual needs.
For this purpose, proposing a kind of axial-flow pump impeller design method based on wheelbase, this method is with L=l × sin βLBased on, By flow Q, lift H and revolving speed n and based on actual needs, axial-flow pump impeller aerofoil profile chord length l and blade angle β are determinedL's Value；And with impeller aerofoil profile chord length l and blade angle βLBased on, determine impeller remaining design parameter impeller diameter D, wheel hub Diameter dhWith pitch t.Finally, 791 profile thickness changing rules of selection carry out thickening vanes.
So far, there is not yet a kind of axial-flow pump impeller design method based on axial length discloses report, the present invention is mentioned A kind of axial-flow pump impeller design method based on wheelbase is supplied.
Summary of the invention
The axial-flow pump impeller design method based on wheelbase that the object of the present invention is to provide a kind of, includes the following steps:
S1: with axial-flow pump axial distance L=l × sin βLBased on, according to given axial-flow pump design discharge Q, lift H, Revolving speed n, specific speed nsDesign parameter equidistantly divides section from impeller hub to impeller outer edge, passes through specific speed nsDetermine section The several and number of blade；Then the aerofoil profile chord length l and blade angle β of axial-flow pump impeller axial length L are determinedL；
S2: work as L1/Lw=0.95~1；Wherein, L1For design requirement axial length；LwThe axial length of outermost side section； Choose axial-flow pump impeller parameter aerofoil profile chord length l, chord of foil laying angle βLFor benchmark parameter, impeller diameter D, hub diameter d are determinedh, section Away from t；
S3: on the basis of aerofoil profile chord length l, 791 profile thickness changing rules is selected to carry out thickening vanes.
The technical solution of the present invention is as follows:
In step S1, aerofoil profile chord length l and blade angle β are determined by flow Q, lift H, revolving speed nL, calculation method is such as Under:
(1) Impeller Design section quantity and the number of blade are determined
Axial-flow pump impeller is divided into 4~6 sections, equidistantly divides section from impeller hub to impeller outer edge；Section number Pass through specific speed n with the number of bladesIt determines；
Specific speed ns ns≤450 450≤ns≤800 800≤ns
Impeller section number 4 5 6
Specific speed ns ns≤600 600≤ns≤850 850≤ns≤1500
The number of blade 5 4 3
(2) aerofoil profile chord length l is calculated according to lift method
Aerofoil profile chord length lcPass through outermost section wing chord length lwIt determines；
When impeller section number is 6, outermost side section is section 6；When impeller section number is 5, outermost side section is For section 5；When impeller section number is 4, outermost side section is section 4；
Wherein, a is correction factor, and obtaining value method is as follows；
Aerofoil profile section wing chord length lcIt is determined by following general formula:
lc=a1×lw
Wherein, a1For proportionality coefficient, specific value is as shown in the table:
(3) blade angle β is calculated according to lift methodL
Aerofoil profile section blade angle βLcPass through outermost blade angle βLwIt determines；
Outermost side section blade angle βLwCalculation method it is as follows:
Wherein, Vm1Import axis plane velocity；Vm2Export axis plane velocity；U peripheral speed；Vu2Rotate component velocity；β1Vane inlet Angle；Outlet blade angle；B is correction factor, is determined by specific speed；
Specific speed ns 0~380 380~610 610~930 930~1500
Correction factor b (6 sections) 0.21~0.28 0.16~0.21 0.12~0.16 0.05~0.12
Correction factor b (5 sections) 0.19~0.24 0.13~0.19 0.08~0.13 0.03~0.08
Correction factor b (4 sections) 0.16~0.22 0.13~0.16 0.07~0.13 0.03~0.07
Aerofoil profile section blade angle βLcIt is determined by following general formula:
βLc=b1×βLw
Wherein, b1For proportionality coefficient, specific value is as shown in the table:
(4) axial length L
Pass through L=l × sin βLDetermine the axial length of axial-flow pump impeller；L1For design requirement axial length；LwOutermost The axial length of section；Design error allowed band is 5%, i.e. L1/ L=0.95~1；
If L1> L and error are greater than 5%, then return step (2) increases the value or return step (3) of correction factor a Increase the value of correction factor b；
If L1< L and error are greater than 5%, then return step (2) reduces the value or return step (3) of correction factor a Reduce the value of correction factor b.
In step S2, pass through aerofoil profile chord length l and blade angle βLDetermine impeller diameter D, hub diameter dh, pitch t；
(1) impeller diameter D
The impeller diameter D of each sectioncIt is determined by following general formula；
Impeller maximum dimension DwIt is determined by following general formula
Wherein, c is proportionality coefficient, and K is correction factor, and specific value is as shown in the table；
(2) impeller hub diameter dh
Wherein, DwFor impeller maximum gauge, wheel hub ratioPass through specific speed ns+3.87×sinβLIt determines；
Work as ns+3.87×sinβL≤ 470,
As 470≤ns+3.87×sinβL≤ 720,
As 720≤ns+3.87×sinβL≤ 940,
As 940≤ns+3.87×sinβL≤ 1200,
As 1200≤ns+3.87×sinβL≤ 1500,
(3) pitch t
Each section pitch tcIt is determined by following general formula；
In step S3,791 profile thickness changing rules is selected to carry out thickening vanes；
(1) aerofoil profile maximum gauge δmax
(2) it on the basis of aerofoil profile chord length l, is thickeied using 791 profile thickness changing rules；The variation of 791 profile thickness It is regular as shown in the table；X is the distance away from aerofoil profile left side edge, and δ is profile thickness；
(3) it when thickening, is rearwardly thickeied using molded line as working face.
The invention has the benefit that
(1) it uses based on wheelbase axial-flow pump impeller design method, it can be achieved that with the integrated pump lock compared with short axial length Perfect cooperation；
(2) compared to the traditional design method to be converted by scale model, not only low efficiency but also bad adaptability, this method It is adaptable good given the quick formula for determining axial-flow pump impeller size, calculate fast, high-efficient advantage；
(3) existing axial-flow pump Hydraulic Design Method is mostly to guarantee based on flow lift, and causes axial-flow pump axially long Length is spent, the design method can pump axial length by control shaft stream while guaranteeing flow lift；
(4) that establishes has the advantages that construction period is short, construction cost is low based on wheelbase axial-flow pump impeller design method；
(5) that establishes can be provided based on wheelbase axial-flow pump impeller design method to solve the development bottleneck of integration pump lock Road；
(6) with the construction of national hydraulic engineering, the large-scale update with small and medium-sized pumping station of country is each for axial-flow pump The requirement of parameter will be higher and higher, therefore the present invention will obtain higher economic benefit and social benefit.
Detailed description of the invention
Fig. 1 is 1 impeller axial sectional view of embodiment.
Fig. 2 blade view.
Fig. 3 aerofoil profile thickeies schematic diagram.
Fig. 4 is flow chart of the invention.
In figure, l is aerofoil profile chord length, βLIt is impeller diameter, d for blade angle, DhIt is pitch for hub diameter, t, 1 is disconnected It is section 3,4 be section 4,5 is section 5 that face 1,2, which is section 2,3, and x is the distance away from aerofoil profile left side edge, and δ is profile thickness, δmaxFor aerofoil profile maximum gauge.
Specific embodiment
Embodiment:
Axial-flow pump design discharge Q=0.35m3/ s, lift H=6.72m, revolving speed n=1450r/min design axial length L1 =26mm.The present invention is described further below:
1. determining aerofoil profile chord length l and blade angle β by flow Q, lift H, revolving speed nL, calculation method is as follows:
(1) Impeller Design section quantity and the number of blade are determined
According to following table, taking impeller section number is 5
Specific speed ns ns≤450 450≤ns≤800 800≤ns
Impeller section number 4 5 6
According to following table, z=4 is taken；
Specific speed ns 0~600 600~850 850~1500
Number of blade z 3 4 5
(2) aerofoil profile chord length l
The aerofoil profile chord length l of section 55
According to following table, a=6 is taken；
Number of blade z 3 4 5
Correction factor a 3.4~5.8 5.8~7.6 7.6~9.4
So
The aerofoil profile chord length l of section 44
According to l4=a1×l5=(0.931~0.963) × l5, take l4=0.951 × l5=0.951 × 79.2=75.3mm
The aerofoil profile chord length l of section 33
According to l3=a1×l5=(0.826~0.894) × l5, take l3=0.842 × l5=0.842 × 79.2=66.7mm
The aerofoil profile chord length l of section 22
According to l2=a1×l5=(0.712~0.787) × l5, take l2=0.762 × l5=0.762 × 79.2=60.4mm
The aerofoil profile chord length l of section 11
According to l1=a1×l5=(0.623~0.685) × l5, take l1=0.651 × l5=0.651 × 79.2=51.6mm
(3) blade angle βL
The blade angle β of section 5L5
Because of ns=750, according to following table, take b=0.1；
Specific speed ns 0~380 380~610 610~930 930~1500
Correction factor b 0.19~0.24 0.13~0.19 0.08~0.13 0.03~0.08
The blade angle β of section 4L4
According to βL4=b1×βLw=(1.06~1.15) × βL5, take βL4=1.12 × βL5=1.12 × 19.29= 21.60°；
The blade angle β of section 3L3
According to βL3=b1×βLw=(1.22~1.34) × βL5, take βL3=1.31 × βL5=1.31 × 19.29= 25.27°；
The blade angle β of section 2L2
According to βL2=b1×βLw=(1.43~1.68) × βL5, take βL2=1.53 × βL5=1.53 × 19.29= 29.51°；
The blade angle β of section 1L2
According to βL1=b1×βLw=(1.84~2.18) × βL5, take βL1=2.02 × βL5=2.02 × 19.29= 38.97°；
(4) axial length L
Lw=l × sin βLw=79.2 × sin19.29 °=26.16mm
Error range meets design requirement less than 5%；
2. passing through aerofoil profile chord length l and blade angle βLDetermine impeller diameter D, hub diameter dhWith pitch t, calculation method It is as follows:
(1) impeller diameter D
The impeller diameter D of section 55
The impeller diameter D of section 44
The impeller diameter D of section 33
The impeller diameter D of section 22
The impeller diameter D of section 11
(2) impeller hub diameter dh
Because of ns+3.87×sinβL=750+3.87 × sin38.58 °=752, according to following table, take
(3) pitch t
The pitch t of section 55
The pitch t of section 44
The pitch t of section 33
The pitch t of section 22
The pitch t of section 11
3. being thickeied on the basis of aerofoil profile chord length l using 791 profile thickness changing rules；
(1) profile thickness of section 5
A. aerofoil profile maximum gauge δmax
According toIt takes
B. it on the basis of aerofoil profile chord length l, is thickeied using 791 profile thickness changing rules；
It is shown in following table that it, which corresponds to profile thickness:
(2) profile thickness of section 4
A. aerofoil profile maximum gauge δmax
According toIt takes
B. it on the basis of aerofoil profile chord length l, is thickeied using 791 profile thickness changing rules；791 profile thickness variation rule Rule is as shown in the table；
(3) profile thickness of section 3
A. aerofoil profile maximum gauge δmax
According toIt takes
B. it on the basis of aerofoil profile chord length l, is thickeied using 791 profile thickness changing rules；791 profile thickness variation rule Rule is as shown in the table；
(4) profile thickness of section 2
A. aerofoil profile maximum gauge δmax
According toIt takes
B. it on the basis of aerofoil profile chord length l, is thickeied using 791 profile thickness changing rules；791 profile thickness variation rule Rule is as shown in the table；
(5) profile thickness of section 1
A. aerofoil profile maximum gauge δmax
According toIt takes
B. it on the basis of aerofoil profile chord length l, is thickeied using 791 profile thickness changing rules；791 profile thickness variation rule Rule is as shown in the table；
(6) it when thickening, is rearwardly thickeied using molded line as working face.

Claims (4)

1. a kind of axial-flow pump impeller design method based on wheelbase, which is characterized in that include step in detail below:
(S1) with axial-flow pump impeller axial length L design function L=l × sin βLFor design basis, set according to given axial-flow pump Count flow Q, lift H, revolving speed n, specific speed nsDesign parameter equidistantly divides section from impeller hub to impeller outer edge, passes through Specific speed nsDetermine section number and the number of blade；Then the aerofoil profile chord length l and blade angle of axial-flow pump impeller axial length L are determined βL；
(S2) work as L1/Lw=0.95~1；Wherein, L1For design requirement axial length；LwThe axial length of outermost side section；
Choose axial-flow pump impeller parameter aerofoil profile chord length l, blade angle βLFor benchmark parameter, impeller diameter D, hub diameter are determined dh, pitch t；
(S3) on the basis of aerofoil profile chord length l, 791 profile thickness changing rules is selected to be thickeied.
2. a kind of axial-flow pump impeller design method based on wheelbase according to claim 1, it is characterised in that: step S1 In, aerofoil profile chord length l and blade angle β are determined by flow Q, lift H, revolving speed nL, calculation method is as follows:
(1) according to specific speed nsDetermine Impeller Design section quantity and the number of blade:
Axial-flow pump impeller is divided into 4~6 sections, equidistantly divides section from impeller hub to impeller outer edge；Section number and leaf The piece number passes through specific speed nsIt determines；
As specific speed nsWhen≤450, impeller section number is 4；
As 450≤n of specific speedsWhen≤800, impeller section number is 5；
As 800≤n of specific speedsWhen, impeller section number is 6；
As specific speed nsWhen≤600, the number of blade 5；
As 600≤n of specific speedsWhen≤850, the number of blade 4；
As 850≤n of specific speedsWhen≤1500, the number of blade 3；
(2) aerofoil profile chord length l is calculated according to lift method,
Aerofoil profile section wing chord length lcPass through outermost section wing chord length lwIt determines；
When impeller section number is 6, outermost side section is section 6；When impeller section number is 5, outermost side section is disconnected Face 5；When impeller section number is 4, outermost side section is section 4；
Wherein, a is correction factor, and obtaining value method is as follows；
When section number is 6, and number of blade z is 3, correction factor a=4.2~6.3,
When section number is 6, and number of blade z is 4, correction factor a=6.3~8.9,
When section number is 6, and number of blade z is 5, correction factor a=8.9~10.2,
When section number is 5, and number of blade z is 3, correction factor a=3.4~5.8,
When section number is 5, and number of blade z is 4, correction factor a=5.8~7.6,
When section number is 5, and number of blade z is 5, correction factor a=7.6~9.4,
When section number is 4, and number of blade z is 3, correction factor a=2.8~5.5,
When section number is 4, and number of blade z is 4, correction factor a=5.5~7.3,
When section number is 4, and number of blade z is 5, correction factor a=7.3~8.9,
Aerofoil profile section wing chord length lcIt is determined by following general formula:
lc=a1×lw
Wherein, a1For proportionality coefficient, specific value is as follows:
When section number is 4, a of section 11It is 0.651~0.728, a of section 21It is 0.793~0.873, a of section 31For 0.894~0.981, a of section 41It is 1,
When section number is 5, a of section 11It is 0.623~0.685, a of section 21It is 0.712~0.787, a of section 31For 0.826~0.894, a of section 41It is 0.931~0.963, a of section 51It is 1,
When section number is 6, a of section 11It is 0.489~0.553, a of section 21It is 0.586~0.653, a of section 31For 0.705~0.781, a of section 41It is 0.793~0.842, a of section 51It is 0.856~0.925, a of section 61It is 1；
(3) blade angle β is calculated according to lift methodL,
Aerofoil profile section blade angle βLcPass through outermost side section blade angle βLwIt determines；
Outermost side section blade angle βLwCalculation method it is as follows:
Wherein, Vm1Import axis plane velocity；Vm2Export axis plane velocity；U peripheral speed；Vu2Rotate component velocity；β1Inlet blade angle；Leaf The piece angle of outlet；B is correction factor, is determined by specific speed；
In the case where section number is 6, as specific speed nsWhen being 0~380, correction factor b is 0.21~0.28；
As specific speed nsWhen being 380~610, correction factor b is 0.16~0.21；
As specific speed nsWhen being 610~930, correction factor b is 0.12~0.16；
As specific speed nsWhen being 930~1500, correction factor b is 0.05~0.12；
In the case where section number is 5, as specific speed nsWhen being 0~380, correction factor b is 0.19~0.24；
As specific speed nsWhen being 380~610, correction factor b is 0.13~0.19；
As specific speed nsWhen being 610~930, correction factor b is 0.08~0.13；
As specific speed nsWhen being 930~1500, correction factor b is 0.03~0.08；
In the case where section number is 4, as specific speed nsWhen being 0~380, correction factor b is 0.16~0.22；
As specific speed nsWhen being 380~610, correction factor b is 0.13~0.16；
As specific speed nsWhen being 610~930, correction factor b is 0.07~0.13；
As specific speed nsWhen being 930~1500, correction factor b is 0.03~0.07；
Aerofoil profile section blade angle βLcIt is determined by following general formula:
βLc=b1×βLw
Wherein, b1For proportionality coefficient, specific value is as follows:
When section number is 4, the b of section 11It is 1.92~2.24, the b of section 21It is 1.52~1.73, the b of section 31It is 1.36 ~1.56, the b of section 41It is 1,
When section number is 5, the b of section 11It is 1.84~2.18, the b of section 21It is 1.43~1.68, the b of section 31It is 1.22 ~1.34, the b of section 41It is 1.06~1.15, the b of section 51It is 1,
When section number is 6, the b of section 11It is 1.72~2.06, the b of section 21It is 1.21~1.53, the b of section 31It is 1.17 ~1.42, the b of section 41It is 0.97~1.21, the b of section 51It is 0.83~0.92, the b of section 61It is 1.
(4) pass through L=l × sin βLDetermine the axial length of axial-flow pump impeller；L1For design requirement axial length；LwOutermost is disconnected The axial length in face；Design error allowed band is 5%, i.e. L1/Lw=0.95~1；
If L1> Lw and error are greater than 5%, then return step (2) increases the value of correction factor a or return step (3) increases The value of correction factor b；
If L1< Lw and error are greater than 5%, then return step (2) reduces the value of correction factor a or return step (3) reduces The value of correction factor b.
3. a kind of axial-flow pump impeller design method based on wheelbase according to claim 1 or 2, it is characterised in that: step In S2, pass through aerofoil profile chord length l and blade angle βLDetermine impeller diameter D, hub diameter dh, pitch t, calculation method is as follows:
(1) impeller diameter D
The impeller diameter D of each sectioncIt is determined by following general formula；
Impeller maximum dimension DwIt is determined by following general formula
Wherein, c is proportionality coefficient, and K is correction factor, and specific value is as follows；
When section number is 4, adjusted coefficient K is 19.3~22.45；The proportionality coefficient c of section 1 is 0.5, the ratio system of section 2 Number c is 0.64, and the proportionality coefficient c of section 3 is 0.76, and the proportionality coefficient c of section 4 is 0.98；
When section number is 5, adjusted coefficient K is 17.8~20.14；The proportionality coefficient c of section 1 is 0.5, the ratio system of section 2 Number c is 0.61, and the proportionality coefficient c of section 3 is 0.73, and the proportionality coefficient c of section 4 is 0.85, and the proportionality coefficient c of section 5 is 0.97；
When section number is 6, adjusted coefficient K is 15.8~19.6；The proportionality coefficient c of section 1 is 0.5, the proportionality coefficient of section 2 C is 0.53, and the proportionality coefficient c of section 3 is 0.57, and the proportionality coefficient c of section 4 is 0.69, and the proportionality coefficient c of section 5 is 0.82, The proportionality coefficient c of section 6 is 0.93；
(2) impeller hub diameter dh
Wherein, DwFor impeller maximum gauge, wheel hub ratioPass through specific speed ns+3.87×sinβLIt determines；
Work as ns+3.87×sinβL≤ 470,
As 470≤ns+3.87×sinβL≤ 720,
As 720≤ns+3.87×sinβL≤ 940,
As 940≤ns+3.87×sinβL≤ 1200,
As 1200≤ns+3.87×sinβL≤ 1500,
(3) pitch t
Each section pitch tcIt is determined by following general formula；
4. a kind of axial-flow pump impeller design method based on wheelbase according to claim 1, it is characterised in that: step S3 In, select 791 profile thickness changing rules to be thickeied；
(1) maximum profile thickness δmax
(2) it on the basis of aerofoil profile chord length l, is thickeied using 791 profile thickness changing rules；791 profile thickness changing rules As follows；X is the distance away from aerofoil profile left side edge, and δ is profile thickness；
When x/l is 0, δ/δmaxIt is 0；
When x/l is 0.05, δ/δmaxIt is 0.296；
When x/l is 0.075, δ/δmaxIt is 0.405；
When x/l is 0.1, δ/δmaxIt is 0.489；
When x/l is 0.2, δ/δmaxIt is 0.778；
When x/l is 0.3, δ/δmaxIt is 0.92；
When x/l is 0.4, δ/δmaxIt is 0.978；
When x/l is 0.5, δ/δmaxIt is 1.0；
When x/l is 0.6, δ/δmaxIt is 0.883；
When x/l is 0.7, δ/δmaxIt is 0.756；
When x/l is 0.8, δ/δmaxIt is 0.544；
When x/l is 0.9, δ/δmaxIt is 0.356；
When x/l is 0.95, δ/δmaxIt is 0.2；
When x/l is 1.0, δ/δmaxIt is 0；
(3) it when thickening, is rearwardly thickeied using molded line as working face.
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