CN105626574B - A kind of high-lift axial-flow pump impeller Hydraulic Design Method - Google Patents
A kind of high-lift axial-flow pump impeller Hydraulic Design Method Download PDFInfo
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- CN105626574B CN105626574B CN201511004087.0A CN201511004087A CN105626574B CN 105626574 B CN105626574 B CN 105626574B CN 201511004087 A CN201511004087 A CN 201511004087A CN 105626574 B CN105626574 B CN 105626574B
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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
- F04D29/181—Axial flow rotors
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Abstract
The present invention relates to a kind of high-lift axial-flow pump impeller Hydraulic Design Method, there is provided the main geometric parameters of impeller, including axial flow pump blade inner maximum gauge δmax, molded line radius R, impeller blade number z, impeller hub side cascade solidity Sh, wheel rim side cascade solidity S0, vane inlet laying angle β1, blade exit laying angle β2, vane inlet axis plane velocity vm1, blade exit axis plane velocity vm2, peripheral compoent of velocity v at blade exitu2, impeller diameter D, hub ratio Rd, impeller head coefficient Ψ, hub diameter d at impeller inlet2, impeller hub angle of flare α, impeller round nut height hb, blade exit laying angle COEFFICIENT Kβ2, vane inlet laying angle COEFFICIENT Kβ1, blade different cross section the selection of aerofoil profile etc..The impeller of the axial-flow pump designed using the present invention not only increases the lift of impeller, while also improves the anti-cavitation performance of axial-flow pump.And contribute to computer programming, it can largely substitute the original similar-design method of axial-flow pump and velocity-coefficient method.
Description
Technical field
The present invention relates to a kind of design method of the major part of axial-flow pump, more particularly to a kind of high-lift axial-flow pump impeller
Hydraulic Design Method.The lift of the axial-flow pump is higher and anti-cavitation performance is good, suitable for agricultural irrigation, municipal plumbing, thermoelectricity,
Petrochemical enterprise is used for the fields, especially nuclear power field such as periodical feeding, process feedwater and regional water transfer.
Background technology
Axial-flow pump is one kind of vane pump, has and accounts for the spies such as simple in construction, floor space is small, flow is big and efficiency is high
Property, the specific revolution of axial-flow pump also begin to gradually open up to the field of other pump class products in 500~1600, at present its application
Exhibition.
Axial-flow pump is primarily adapted for use in agricultural drainage and irrigation, municipal plumbing, thermoelectricity, nuclear power, petrochemical enterprise etc. and is used to circulate
The fields such as water supply, process feedwater and regional water transfer.And the flow of axial-flow pump is high at present, but lift is relatively low.With new
The development of the energy, nuclear power is using more and more extensive, but also by as the mainstay of China's energy cause.But it is presently considered
During to big flow, lift does not reach requirement but；When lift reaches requirement, flow is really comparatively smaller.Thus big flow is high
The pump of lift is that nuclear power industry is badly in need of.
The Hydraulic Design Method of the axial-flow pump impeller of prior art does not provide the design method of system, and designs
Impeller lift it is relatively low, and be largely still to depend on empirical equation, operability is not strong, undue to rely on engineering skill
The experience of art personnel.It is difficult to meet the high-lift and good requirement of anti-cavitation performance, and be difficult accomplish computer programming apply and
CAD.Nowadays axial-flow pump is a popular domain in nuclear power industry, relies solely on transformation impeller shape sometimes
It can not meet to improve its lift and anti-cavitation performance, it is necessary to do the Hydraulic Design Method of axial-flow pump impeller further perfect.
A kind of " axial flow pump impeller vane ", the invention are disclosed in the Chinese invention patent that Application No. 02133456.0
It is related to a kind of axial-flow pump impeller blade, this design method only gives the specific implementation method of the parameter of impeller blade,
Other specification still relies on the experience of engineers and technicians, does not provide system, accurate design method, and is difficult to accomplish
Computer programming is applied and CAD.The Chinese invention patent that Application No. 201410481735.0 discloses one
The multi-state design method of kind multi-phase mixed delivering axial-flow pump impeller, the present invention relates to a kind of multi-state of multi-phase mixed delivering axial-flow pump impeller
Design method, the performance requirement of what all parameter and multiple operating modes of the axial-flow pump of the axial wheel is linked together.
But this patent pertains only to several parameters of axial-flow pump impeller, the design side of the parameter of complete axial-flow pump impeller is not provided
Method.The Chinese invention patent that Application No. 201310744652.1 discloses a kind of Double-way axial flow impeller of pump optimization design side
Method, the present invention disclose a kind of Double-way axial flow impeller of pump Optimization Design, on the basis of conventional flow collimation method design axial-flow pump impeller
On, reversible axial flow pump impeller performance is improved by the optimization to aerofoil profile and paddle wheel plane figure, reaches while improves Double-way axial flow
The purpose of impeller of pump efficiency and anti-cavitation performance.This design method not only makes the standardization of oblique flow impeller of pump and systematization, also full
The requirement of sufficient water conservancy and municipal works to diagonal pumps multi-parameter operating mode.But inventor does not also give shaft stream in that patent
System, the accurate design method of the basic parameter of impeller of pump, largely still rely on original similar-design method and
Velocity-coefficient method.
For above-mentioned defect, the present inventor has invented a kind of high-lift axial-flow pump impeller Hydraulic Design Method, no
Axial-flow pump impeller parameter system, accurate design method are only gived, the problem of also solving axial-flow pump low lift and cavitation,
The lift and cavitation performance of axial-flow pump are improved, extends the service life and maintenance cycle of pump, it is most important that contribute to computer
Program Appliance and CAD, it can largely substitute axial-flow pump original similar-design method and velocity-coefficient method.
Goal of the invention
With the fast development of China's economy and the increasingly reduction of global energy, it is more next as people how to save the energy
The problem of more paying close attention to.The country's being in great demand for pump class product at present, 20%~25% per annual electricity generating capacity can all consume
On pump class product.How to realize that axial-flow pump while big flow is ensured, further widens high efficient district, and lift can be improved,
Have become the pressing problem of current axial-flow pump development.Existing design method, Theoretical Design is quite different with realistic model, it is difficult to
Reach desired effect.It is an object of the invention to improve axial-flow pump lift, strengthen axial-flow pump anti-cavitation performance, increase the life-span of pump
And maintenance cycle, to reduce the workload of maintainer.Computer programming application and CAD are additionally aided, can be very
Substitute the original similar-design method of axial-flow pump and velocity-coefficient method in big degree, and calculating is more accurate, makes Theoretical Design and reality
Model more meets.
The content of the invention
In order to solve the above problems, the invention provides a kind of axial-flow pump impeller Hydraulic Design Method.By improving impeller
Several important parameters design method, improve mobility status, improve the lift and cavitation performance of axial-flow pump.
Technical scheme is used by realizing above-mentioned purpose：
(1) impeller head coefficient ψ
In formula：
ψ-impeller head coefficient；
ns- specific revolution；
(2) hub ratio Rd
In formula：
Rd- hub ratio；
dh- impeller hub diameter, rice；
D- impeller diameters, rice；
ψ-impeller head coefficient；
(3) impeller diameter D
In formula：
D- impeller diameters, rice；
ns- specific revolution；
Rd- hub ratio；
Q- design conditions flows, rice3/ the second；
N- design conditions rotating speeds, rev/min；
(4) vane inlet axis plane velocity v is not correctedm’
In formula：
vm1'-does not correct vane inlet axis plane velocity, meter per second；
vm2'-does not correct blade exit axis plane velocity, meter per second；
ns- specific revolution；
Q- design conditions flows, rice3/ the second；
D- impeller diameters, rice；
Rd- hub ratio；
(5) vane inlet axis plane velocity vm1, blade exit axis plane velocity vm2
In formula：
vm1- vane inlet axis plane velocity, meter per second；
vm2- blade exit axis plane velocity, meter per second；
ns- specific revolution；
(6) peripheral compoent of velocity v at blade exitu2
In formula：
vu2The peripheral compoent of velocity at-blade exit, meter per second；
ns- specific revolution；
D- impeller diameters, rice；
N- design conditions rotating speeds, rev/min；
(7) impeller hub side cascade solidity Sh
In formula：
Sh- impeller hub side cascade solidity；
L- aerofoil profile chord lengths, rice；
th- impeller hub side pitch, rice；
ns- specific revolution；
(8) wheel rim side cascade solidity S0
In formula：
S0- wheel rim side cascade solidity；
L- aerofoil profile chord lengths, rice；
t0- wheel rim side pitch, rice；
ns- specific revolution；
(9) vane inlet laying angle COEFFICIENT Kβ1
In formula：
Kβ1- vane inlet lays ascent；
ns- specific revolution；
(10) blade exit laying angle COEFFICIENT Kβ2
In formula：
Kβ2- blade exit lays ascent；
ns- specific revolution；
(11) vane inlet laying angle β1
In formula：
β1- vane inlet laying angle, degree；
Kβ1- vane inlet lays ascent；
ns- specific revolution；
Di- different cross section impeller diameter, rice；
Vm1- vane inlet axis plane velocity, meter per second；
N- design conditions rotating speeds, rev/min；
(12) blade exit laying angle β2
In formula：
β2- blade exit laying angle, degree；
Kβ1- vane inlet lays ascent；
vm2- blade exit axis plane velocity, meter per second；
ns- specific revolution；
Di- different cross section impeller diameter, rice；
N- design conditions rotating speeds, rev/min；
vu2The peripheral compoent of velocity at-blade exit, meter per second；
(13) impeller blade number z
Z=111-0.06514ns-190.1S0+1.18×10-5ns 2+0.05042ns·S0+89.05S0 2 (13)
In formula：
Z- impeller blade numbers；
ns- specific revolution；
S0- wheel rim side cascade solidity；
(14) maximum blade thickness δmax
In formula：
δmax- maximum blade thickness, rice；
H- design conditions lifts, rice；
D- impeller diameters, rice；
(15) molded line radius R
In formula：
R- molded line radiuses, rice；
D- impeller diameters, rice；
L- aerofoil profile chord lengths, rice；
β2- blade exit laying angle, degree；
β1- vane inlet laying angle, degree；
(16) hub diameter d at impeller inlet2
d2=[- 0.0281ln (n)+0.81704] dh(16) in formula：
d2Hub diameter at-impeller inlet, rice；
H- design conditions lifts, rice；
dh- impeller hub diameter, rice；
(17) impeller hub angle of flare α
In formula：
α-impeller hub angle of flare, degree；
d2Hub diameter at-impeller inlet, rice；
H- design conditions lifts, rice；
dh- impeller hub diameter, rice；
(18) impeller round nut height hb
hb=(0.000002H2-0.00002H+0.38014)·d2 (18)
In formula：
hb- impeller round nut height, rice；
d2Hub diameter at-impeller inlet, rice；
H- design conditions lifts, rice；
(19) airfoil cross sectional shape
X ＜ (D-dhDuring)/2, cross sectional shape is using the larger aerofoil profile of thickness；
X ＞ (D-dhDuring)/2, cross sectional shape is larger using lift coefficient, relatively partially thin aerofoil profile.
In formula：
X- blades are apart from wheel hub side length.
According to above-mentioned steps, a kind of relative system, accurate impeller major parameter design method can be obtained.
Axial-flow pump impeller main geometric parameters, including axial-flow pump impeller head coefficient, leaf are determined by above-mentioned computational methods
Take turns hub ratio, impeller diameter, vane inlet axis plane velocity, blade exit axis plane velocity, the peripheral compoent of velocity, impeller at blade exit
Hub side cascade solidity, wheel rim side cascade solidity, blade exit lay ascent, vane inlet lays ascent,
Vane inlet laying angle, blade exit laying angle, impeller blade number, maximum blade thickness, wheel hub at molded line radius impeller inlet
Diameter, impeller hub angle of flare, impeller round nut height and different section forms, different from traditional analogue method and speed system
Number method, being mutually matched for hydraulic part size more being can ensure that, calculating is more accurate, Theoretical Design is more met with realistic model, and
And it is more beneficial for computer application and programming.
Brief description of the drawings
The present invention is further described with reference to the accompanying drawings and detailed description.
Fig. 1 is axial-flow pump impeller axle axial plane figure.
Fig. 2 is axial-flow pump impeller plane cascade figure.
Embodiment
The present invention determines to include axial-flow pump impeller head coefficient ψ, hub ratio R by following formulad, impeller
Diameter D, vane inlet axis plane velocity vm1, blade exit axis plane velocity vm2, peripheral compoent of velocity v at blade exitu2, impeller hub
Side cascade solidity Sh, wheel rim side cascade solidity S0, blade exit laying angle COEFFICIENT Kβ2, vane inlet lay ascent
Kβ1, vane inlet laying angle β1, blade exit laying angle β2, impeller blade number z, maximum blade thickness δmax, molded line radius R, leaf
Take turns entrance hub diameter d2, impeller hub angle of flare α, impeller round nut height hbDeng impeller several parameters and blade not
Same section form.
This embodiment is in given design conditions flow Q, design conditions lift H, design conditions rotating speed n, calculates impeller water
Force parameter：
Z=111-0.06514ns-190.1S0+1.18×10-5ns 2+0.05042ns·S0+89.05S0 2 (13)
d2=[- 0.0281ln (H)+0.81704] dh (16)
hb=(0.000002H2-0.00002H+0.38014)·d2 (18)
Formal in blade profile, different sections use different air foil shapes, x ＜ (D-dhDuring)/2, cross sectional shape
Using the aerofoil profile that thickness is larger；X ＞ (D-dhDuring)/2, cross sectional shape is larger using lift coefficient, relatively partially thin aerofoil profile.
The present invention carries out the Hydraulic Design using exact formulas design method, and the lift and anti-cavitation for making pump are greatly improved,
With good economic benefit, the Program Appliance of computer is more beneficial for.Because the design method of the present invention is different from traditional phase
Like method and velocity-coefficient method, it more can ensure that the size of hydraulic part is mutually matched.And calculate it is more accurate, make Theoretical Design with
Realistic model more meets.
More than, illustrated for patent of the present invention with reference to what embodiment was made, but the present invention is not limited to above-mentioned implementation
Example, also comprising the other embodiment or variation in the range of present inventive concept.
Claims (9)
1. a kind of high-lift axial-flow pump impeller Hydraulic Design Method, there is provided the main geometric parameters of impeller, including axial flow pump blade inner
Maximum gauge δmax, molded line radius R, impeller blade number z, impeller hub side cascade solidity Sh, wheel rim side cascade solidity
S0, vane inlet laying angle β1, blade exit laying angle β2, vane inlet axis plane velocity vm1, blade exit axis plane velocity vm2, leaf
Piece exit peripheral compoent of velocity vu2, impeller diameter D, hub ratio Rd, impeller head coefficient ψ, hub diameter at impeller inlet
d2, impeller hub angle of flare α, impeller round nut height hb, blade exit laying angle COEFFICIENT Kβ2, vane inlet lay ascent
Kβ1, blade different cross section aerofoil profile selection, it is characterised in that：Between impeller geometric parameter and pump operating point for design performance parameter
It is adapted to following relation：
Z=111-0.06514ns-190.1S0+1.18×10-5ns 2+0.05042ns·S0+89.05S0 2
In formula：
R- molded line radiuses, rice；
D- impeller diameters, rice；
L- aerofoil profile chord lengths, rice；
β2- blade exit laying angle, degree；
β1- vane inlet laying angle, degree；
H- design conditions lifts, rice；
δmax- maximum blade thickness, rice；
nS- specific revolution；
Z- impeller blade numbers；
S0- wheel rim side cascade solidity.
2. high-lift axial-flow pump impeller Hydraulic Design Method according to claim 1, it is characterised in that：Vane inlet is laid
Angle beta1, blade exit laying angle β2Design formula：
In formula：
Kβ2- blade exit lays ascent；
vm2- blade exit axis plane velocity, meter per second；
Di- different cross section impeller diameter, rice；
N- design conditions rotating speeds, rev/min；
vu2The peripheral compoent of velocity at-blade exit, meter per second；
Kβ1- vane inlet lays ascent；
vm1- vane inlet axis plane velocity, meter per second.
3. high-lift axial-flow pump impeller Hydraulic Design Method according to claim 1, it is characterised in that：Impeller hub lateral lobe
Grid consistency Sh, wheel rim side cascade solidity S0Design formula：
-0.017cos(0.052ns)+0.08sin(0.052ns)
In formula：
Sh- impeller hub side cascade solidity；
L- aerofoil profile chord lengths, rice；
th- impeller hub side pitch, rice；
t0- wheel rim side pitch, rice.
4. high-lift axial-flow pump impeller Hydraulic Design Method according to claim 2, it is characterised in that：Vane inlet axial plane
Speed vm1, blade exit axis plane velocity vm2, the peripheral compoent of velocity at blade exitDesign formula：
In formula：
vm1'-does not correct vane inlet axis plane velocity, meter per second；
Q- design conditions flows, rice3/ the second.
5. high-lift axial-flow pump impeller Hydraulic Design Method according to claim 1, it is characterised in that：Impeller diameter D is set
Count formula：
In formula：
Rd- hub ratio.
6. high-lift axial-flow pump impeller Hydraulic Design Method according to claim 5, it is characterised in that：Hub ratio Rd、
Impeller head coefficient ψ design formulas：
In formula：
dh- impeller hub diameter, rice.
7. high-lift axial-flow pump impeller Hydraulic Design Method according to claim 1, it is characterised in that：Taken turns at impeller inlet
Hub diameter d2, impeller hub angle of flare α, impeller round nut height hbDesign formula：
d2=[- 0.0281ln (H)+0.81704] dh
hb=(0.000002H2-0.00002H+0.38014)·d2
In formula：
d2Hub diameter at-impeller inlet, rice；
α-impeller hub angle of flare, degree；
hb- impeller round nut height, rice.
8. high-lift axial-flow pump impeller Hydraulic Design Method according to claim 2, it is characterised in that：Blade exit is laid
Ascent Kβ2, vane inlet laying angle COEFFICIENT Kβ1Design formula：
9. high-lift axial-flow pump impeller Hydraulic Design Method according to claim 1, it is characterised in that：The section shape of blade
Shape uses different section forms：
X ＜ (D-dhDuring)/2, cross sectional shape is using the larger aerofoil profile of thickness；
X ＞ (D-dhDuring)/2, cross sectional shape is larger using lift coefficient, relatively partially thin aerofoil profile；
In formula：
X- blades are apart from wheel hub side length.
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Cited By (1)
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