CN104533829A - Diagonal flow pump impeller hydraulic design method - Google Patents

Diagonal flow pump impeller hydraulic design method Download PDF

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Publication number
CN104533829A
CN104533829A CN201410711980.6A CN201410711980A CN104533829A CN 104533829 A CN104533829 A CN 104533829A CN 201410711980 A CN201410711980 A CN 201410711980A CN 104533829 A CN104533829 A CN 104533829A
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impeller
inlet
blade
formula
shroud
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CN104533829B (en
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付强
张本营
朱荣生
王秀礼
王学吉
刘永
张帆
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Jiangsu University
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Jiangsu University
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/18Rotors

Abstract

The invention relates to a diagonal flow pump impeller hydraulic design method. A design formula about main geometric parameters of the impeller is given, and includes an included angle Alpha between the outlet of the diagonal flow pump impeller and the horizontal line, the actual thickness Delta of each point of each vane, vane wrap angle Phi, the inlet fillet radius RTS of the rear cover plate of the impeller, the number z of impeller vanes, the diameter D2 of the impeller outlet, the width b2 of the vane outlet, the equivalent diameter D0 of the impeller inlet, a distance ZE between the vane inlet of the front cover plate and the outlet of the front cover plate of the impeller, a distance g1 from the inlet edge to the initial end of the curve of the front cover plate, the inlet fillet radius RDB of the front cover plate of the impeller, round nut radius Ra of the impeller, round nut height Rb of the impeller, the placing angle of the vane Beta, the placing angles Beta1 of inlet of the vane, the placing angles Beta2 of inlet of the vane, the slipping coefficient Rho and the hydraulic efficiency Etah. According to the impeller of the diagonal flow pump designed by the invention, the hydraulic efficiency of the impeller and the stability performance of the diagonal flow pump are improved, and computer programming is facilitated, and thereby the original similar design method and the velocity coefficient method of the diagonal flow pump can be replaced to a great extent.

Description

A kind of diagonal pumps impeller Hydraulic Design Method
Technical field
The present invention relates to a kind of design method of major part of diagonal pumps, particularly a kind of diagonal pumps impeller Hydraulic Design Method.This diagonal pumps impeller is applicable to hydraulic efficiency is high and stability is good agricultural drainage and irrigation, municipal plumbing, thermoelectricity, nuclear power, petrochemical enterprise etc. for fields such as periodical feeding, process feedwater and regional water transfer.
Background technique
Diagonal pumps are called guide vane mixed flow pump again, have that floor space is few, external diameter is little, easy startup and a characteristic such as efficiency is high, and be a kind of performance and the water pump of structure between centrifugal pump and axial-flow pump, the shortcoming that compensate for both has both advantages simultaneously.The specific speed of diagonal pumps is 290 ~ 590, and its application area also starts to expand to the field of other pump series products gradually at present.
Diagonal pumps are mainly applicable to agricultural drainage and irrigation, municipal plumbing, thermoelectricity, nuclear power, petrochemical enterprise etc. for fields such as periodical feeding, process feedwater and regional water transfer, and therefore, the Hydraulic Design of diagonal pumps impeller is just related to oblique flow pump performance.Diagonal pumps are primarily of parts compositions such as pump case, impeller, stator, motors, and the impeller hydraulic part that to be diagonal pumps most crucial, also be unique dynamic element, the geometric parameter of impeller is very large to diagonal pumps performance impact, and therefore impeller has material impact to the hydraulic efficiency of diagonal pumps and hydraulic performance.
The Hydraulic Design Method of the diagonal pumps impeller of prior art does not provide the design method of system, still depends on empirical correlation to a great extent, and operability is not strong, still too relies on the experience of engineers and technicians in actual design.Be difficult to the requirement that hydraulic efficiency is high and stability is good meeting diagonal pumps, and be difficult to accomplish computer programming application and computer-aided design.Nowadays diagonal pumps are popular domains in fluid machinery, only rely on transformation impeller shape sometimes can not meet the requirement improving its stability and hydraulic efficiency, need to do the Hydraulic Design Method of diagonal pumps impeller perfect further.
The patent No. is disclose one " mixed-flow double-suction pump impeller Hydraulic Design Method " in the Chinese invention patent of No. 201410091278.4, and this design method only gives impeller inlet diameter D j, impeller outlet diameter D 2, blade exit width b 2the concrete implementing method of three parameters, other parameters still rely on the experience of engineers and technicians, do not provide system, accurate design method, and are difficult to accomplish computer programming application and computer-aided design.The patent No. is that the Chinese invention patent of No. 200910072255.8 discloses one " mixed-flow pump impeller ", in this patent of invention, inventor gives the construction design method of mixed-flow pump impeller, this design method not only increases stiffness and the reliability of mixed-flow pump impeller, also ensures the operation of set steady safety.But this patent does not relate to the Hydraulic Design of mixed-flow pump impeller, more do not provide the design of design parameter.The patent No. is that the Chinese invention patent of No. 201110266687.X discloses one " a kind of design method for cutting performance of inclined flow pump impeller ", inventor adopt blade to cut sth. askew in that patent or with outlet parallel cutting mode, establish the relation of impeller outlet diameter, impeller specific speed and pump performance.This design method not only makes the standardization of diagonal pumps impeller and systematize, also meets water conservancy and municipal engineering to the requirement of diagonal pumps multi-parameter operating mode.But inventor does not provide the system of the basic parameter of diagonal pumps impeller, accurate design method in that patent yet, still relies on original similar-design method and velocity-coefficient method to a great extent.
For the defect of above-mentioned existence, the present inventor has invented " a kind of diagonal pumps impeller Hydraulic Design Method ", do not only give diagonal pumps impeller parameters system, accurate design method, also solve the problem of diagonal pumps performance unstability, enhance the reliability of diagonal pumps, improve the hydraulic efficiency of diagonal pumps, extend working life and the service cycle of pump, the most important thing is to contribute to computer programming application and computer-aided design, the original similar-design method of diagonal pumps and velocity-coefficient method can be replaced to a great extent.
Goal of the invention
Along with the fast development of China's economy and the minimizing day by day of global energy, how energy saving has become the problem that people more and more pay close attention to.Domestic being in great demand for pump series products at present, 20% ~ 25% of every annual electricity generating capacity all can consume on pump series products.How to realize diagonal pumps while guarantee water conservancy efficiency is high, widen efficient district further, and energy stable operation, become the pressing problem of current diagonal pumps development.Existing design method, Theoretical Design and realistic model quite different, be difficult to reach desired effect.The object of the invention is to avoid diagonal pumps performance unstability, strengthen the reliability of diagonal pumps, improve diagonal pumps hydraulic efficiency, increase life-span and the service cycle of pump, to reduce the workload of maintainer.Also contribute to computer programming application and computer-aided design, the original similar-design method of diagonal pumps and velocity-coefficient method can be replaced to a great extent, and calculate more accurate, Theoretical Design and realistic model are more met.
Summary of the invention
In order to solve the problem, the invention provides a kind of diagonal pumps impeller Hydraulic Design Method.By improving the design method of several important parameters of impeller, improving mobility status, improving diagonal pumps hydraulic efficiency and stability.
Realizing the technological scheme that above-mentioned purpose adopts is:
(1) impeller outlet diameter D 2
D 2 = D 20 + D 2 h 2 = M D 2 · [ - 0.72 Q 0.075 + 0.082 n 0.095 + ( Q / n ) 0.122 ] - - - ( 1 )
In formula:
The flow of Q-design conditions, rice 3/ second;
D 2-impeller outlet diameter, rice;
D 20the minimum outlet diameter of-impeller, rice;
D 2hthe maximum outlet diameter of-impeller, rice;
The rotating speed of n-design conditions, rev/min;
M d2-impeller outlet diametral quotient;
(2) blade exit width b 2
b 2=M b2.[0.0984Q 0.3345-0.9473n 0.00904+1.01] (2)
In formula:
The flow of Q-design conditions, rice 3/ second;
B 2-blade exit width, rice;
The rotating speed of n-design conditions, rev/min;
M b2-blade exit spread factor;
(3) impeller inlet equivalent diameter D 0
D 0 = M D 0 · [ 0.06687 Q 1.052 - 0.1671 n - 0.3423 + ( Q / n ) 0.3579 ] - - - ( 3 )
In formula:
The flow of Q-design conditions, rice 3/ second;
The rotating speed of n-design conditions, rev/min;
M d0-impeller inlet equivalent diameter coefficient;
(4) impeller outlet diametral quotient M d2
M D 2 = 0.8799 e [ - ( ( n s - 1643 ) / 971.1 ) 2 ] + 1.366 e [ - ( ( n s - 1977 ) / 3483 ) 2 ] - - - ( 4 )
In formula:
N s-specific speed;
(5) blade exit width diameter coefficient M b2
M b 2 = [ - 0.27 ln ( n s ) + 2.07 ] ( n s / 100 ) 5 6 - - - ( 5 )
In formula:
N s-specific speed;
(6) impeller inlet equivalent diameter coefficient M d0
M D 0 = 1.25 arctan ( sin ( Q 0.6 · n ) / H 4 ) - - - ( 6 )
In formula:
N s-specific speed;
The flow of Q-design conditions, rice 3/ second;
H-design conditions lift, rice;
(7) diagonal pumps impeller outlet and horizontal sextant angle α
α = arcsin [ ( ( 70.9539 · e [ - ( ( n s - 1461 ) / 1401 ) 2 · gH / n ) - D 2 ) / b 2 ] - - - ( 7 )
In formula:
α-diagonal pumps impeller outlet and horizontal sextant angle, degree;
D 2-impeller outlet diameter, rice;
B 2-blade exit width, rice;
The rotating speed of n-design conditions, rev/min;
N s-specific speed;
H-design conditions lift, rice;
G-gravity accleration, meter per second 2;
(8) front shroud of impeller import fillet radius coefficient M rDB
M RDB=0.0905ln(n s)-0.1836 (8)
In formula:
M rDB-front shroud of impeller import fillet radius coefficient;
N s-specific speed;
(9) front shroud of impeller import fillet radius RDB
R DB=M RDB·(0.3853Q 0.3335-2.9056n 0.01142+3.1508) (9)
In formula:
R dB-front shroud of impeller import fillet radius, rice;
The flow of Q-design conditions, rice 3/ second;
M rDB-front shroud of impeller import fillet radius coefficient;
(10) impeller round nut radius R a, impeller round nut height R b
R a=16.5311n(D 0)-65.11 (10)
R b=1.51R a(11)
In formula:
R a-impeller round nut radius, rice;
D 0the import equivalent diameter of-impeller, rice;
R b-impeller round nut height, rice;
(11) back shroud of impeller import fillet radius coefficient M rTS
M RTS = 0.6136 e ( 0.0007 n s ) - - - ( 12 )
In formula:
M rTS-back shroud of impeller import fillet radius coefficient;
N a-specific speed;
(12) back shroud of impeller import fillet radius R tS
R TS = R DB + M DTS [ ( D 0 2 - R a + b 2 ) / 2 ] - - - ( 13 )
In formula:
R tS-back shroud of impeller import fillet radius, rice;
R dB-front shroud of impeller import fillet radius, rice;
D 0-impeller inlet equivalent diameter, rice;
B 2-blade exit width, rice;
M rTS-front shroud of impeller import fillet radius coefficient;
R a-impeller round nut radius, rice;
(13) the distance Z that exports of front shroud of impeller vane inlet place and front shroud e
Z E = 0.4738 e [ - ( ( n s - 1461 ) / 1401 ) 2 ] · ( gHn s / n ) - - - ( 14 )
In formula:
Z ethe distance that-front shroud of impeller vane inlet place and front shroud export, rice;
The rotating speed of n-design conditions, rev/min;
N s-specific speed;
H-design conditions lift, rice;
G-gravity accleration, meter per second 2;
(14) inlet side is apart from front shroud curve starting end distance g 1
g 1 = R DB 7.5 · M RDB - - - ( 15 )
In formula:
G 1-inlet side distance front shroud curve starting end distance, rice;
R dB-front shroud of impeller import fillet radius, rice;
M rDB-front shroud of impeller import fillet radius coefficient;
(15) vane inlet axis plane velocity v m1
v m 1 = [ 0.3173 e ( 0.000971 n s ) - 1.0824 e ( - 0.0118 n s ) ] · gH - - - ( 16 )
In formula:
N s-specific speed;
H-design conditions lift, rice;
G-gravity accleration, meter per second 2;
(16) blade exit axis plane velocity v m2
v m 2 = { 17.2251 e [ - ( ( n s - 1358 ) / 705.7 ) 2 ] + 3.18198 e [ - ( ( n s - 526.2 ) / 415 ) 2 ] } · gH - - - ( 17 )
In formula:
N s-specific speed;
H-design conditions lift, rice;
(17) blade exit peripheral velocity u 2
u 2 = { 0.07382 e [ - ( ( n s - 1133 ) / 129.7 ) 2 ] + 3.3361 e [ - ( ( n s - 2210 ) / 2308 ) 2 ] } · gH / 10 - - - ( 18 )
In formula:
N s-specific speed;
H-design conditions lift, rice;
G-gravity accleration, meter per second 2;
(18) hydraulic efficiency η h
η h=1+0.0835lg(0.09633Q 0.3335-0.7264n 0.01142+0.7877) (19)
In formula:
The flow of Q-design conditions, rice 3/ second;
The rotating speed of n-design conditions, rev/min;
(19) slip coefficient ρ
ρ = 2.5287 v m 2 + 10.2157 · H u 2 · η h - - - ( 20 )
In formula:
H-design conditions lift, rice;
V m2-blade exit axis plane velocity, meter per second;
U 2-blade exit peripheral velocity, meter per second;
η h-hydraulic efficiency;
(20) vane inlet laying angle β 1
β 1 = arctan [ 19.099 v m 1 n · sin [ ( - 0.02 n s + 59.1 ) · D j ] ] - - - ( 21 )
In formula:
N s-specific speed;
D j-impeller inlet diameter, rice;
V m1-vane inlet axis plane velocity, meter per second;
The rotating speed of n-design conditions, rev/min;
(21) blade exit laying angle β 2
β 2 = arctan 0.001056 n s 1.608 · gH ρ v m 2 - ( gH v m 2 η h · u 2 ) - - - ( 22 )
In formula:
N s-specific speed;
V m2-blade exit axis plane velocity, meter per second;
ρ-slip coefficient;
U 2-blade exit peripheral velocity, meter per second;
η h-hydraulic efficiency;
G-gravity accleration, meter per second 2;
(22) blade angle β
β = [ 1 + 11.136 n s ( - 0.2238 ) - 1 1 + 3.33709 n s ( - 0.1129 ) ] ( β 1 + β 2 ) - - - ( 23 )
In formula:
β-blade angle, degree;
β 1-vane inlet laying angle, degree;
β 2-blade exit laying angle, degree;
N s-specific speed;
(23) impeller blade number z
z = 6.5 · [ D 2 + sin ( - 0.02 n s + 59.1 ) D j D 2 - sin ( - 0.02 n s + 59.1 ) D j ] · sin β 1 + β 2 2 - - - ( 24 )
In formula:
D 2-impeller outlet diameter, rice;
Z-impeller blade number;
β 1-vane inlet laying angle, degree;
β 2-blade exit laying angle, degree;
D j-impeller inlet diameter, wherein d hfor hub diameter; Work as d hwhen=0;
(24) subtended angle of blade
In formula:
N s-specific speed;
Z-impeller blade number;
(25) nominal airfoil thickness correction values δ k
δ k = [ 4.556 · e ( 0.002923 n s ) - 2.197 · e ( - 0.007274 n s ) ] · D 2 · ( H / z ) 1 2 - - - ( 26 )
In formula:
N s-specific speed;
H-design conditions lift, rice;
D 2-impeller outlet diameter, rice;
Z-impeller blade number;
(26) blade often puts actual thickness δ
δ=M δ·δ k(27)
M δ=0.7368e (0.0031L)(28)
In formula:
δ-blade often puts actual thickness, rice;
M δ-vane thickness coefficient;
δ k-nominal airfoil thickness correction values, rice;
L-length of blade, rice;
According to above-mentioned steps, can obtain a kind of relative system, the design method of accurate impeller major parameter.
By above-mentioned computational methods determination diagonal pumps impeller main geometric parameters, comprise impeller outlet diameter, impeller inlet equivalent diameter, blade exit width, diagonal pumps impeller outlet and horizontal line angle, front shroud of impeller import fillet radius, impeller round nut radius, impeller round nut height, back shroud of impeller import fillet radius, the distance that front shroud of impeller vane inlet place and front shroud export, inlet side is apart from front shroud curve starting end distance, vane inlet axis plane velocity, blade exit axis plane velocity, blade exit peripheral velocity, hydraulic efficiency, slip coefficient, vane inlet laying angle, blade exit laying angle, blade angle, impeller blade number, subtended angle of blade, blade often puts actual thickness, be different from traditional analogue method and velocity-coefficient method, more can guarantee the mutual coupling of hydraulic part size, calculate more accurate, Theoretical Design and realistic model are more met, and be more conducive to computer application and programming.
Accompanying drawing explanation
Below in conjunction with the drawings and specific embodiments, the present invention is further described.
Fig. 1 is the axial plane figure of diagonal pumps impeller.
Fig. 2 is the planimetric map of diagonal pumps impeller.
Fig. 3 is that diagonal pumps blade often puts actual thickness.
Embodiment
The present invention determines impeller outlet diameter D by following formula 2, impeller inlet equivalent diameter D 0, blade exit width b 2, impeller outlet diametral quotient M d2, impeller inlet equivalent diameter coefficient M d0, blade exit spread factor M b2, diagonal pumps impeller outlet and horizontal line angle α, front shroud of impeller import fillet radius R dB, impeller round nut radius R a, impeller round nut height R h, back shroud of impeller import fillet radius R tS, the distance Z that exports of front shroud of impeller vane inlet place and front shroud e, inlet side is apart from front shroud curve starting end distance g 1, vane inlet axis plane velocity v m1, blade exit axis plane velocity v m2, blade exit peripheral velocity u 2, hydraulic efficiency η h, slip coefficient ρ, vane inlet laying angle β 1, blade exit laying angle β 2, blade angle β, impeller blade number z, subtended angle of blade blade often puts several parameters of the impellers such as actual thickness δ.
This embodiment is at given design conditions flow Q, design conditions lift H, design conditions rotating speed n, calculates impeller hydraulic parameters:
D 2 = D 20 + D 2 h 2 = M D 2 · [ - 0.72 Q 0.075 + 0.082 n 0.095 + ( Q / n ) 0.122 ] - - - ( 1 )
b 2 = M b 2 · [ 0.0984 Q 0.3345 - 0.9473 n 0.00904 + 1.01 ] - - - ( 2 )
D 0 = M D 0 · [ 0.06687 Q 1.052 - 0.1671 n - 0.3423 + ( Q / n ) 0.3579 ] - - - ( 3 )
M D 2 = 0.8799 e [ - ( ( n s - 1643 ) / 971.1 ) 2 ] + 1.366 e [ - ( ( n s - 1977 ) / 3483 ) 2 ] - - - ( 4 )
M b 2 = [ - 0.27 ln ( n s ) + 2.07 ] ( n s / 100 ) 5 6 - - - ( 5 )
M D 0 = 1.25 arctan ( sin ( Q 0.6 · n ) / H 4 ) - - - ( 6 )
α = arctan [ ( ( 70.9539 · e [ - ( ( n s - 1461 ) / 1401 ) 2 ] · gH / n ) - D 2 ) / b 2 ] - - - ( 7 )
M RDB=0.0905ln(n s)-0.1836 (8)
R DB=M RDB·(0.3853Q 0.3335-2.9056n 0.01142+3.1508) (9)
R a=16.5311n(D 0)-65.11 (10)
R b=1.51R a(11)
M RTS = 0.6136 e ( 0.0007 n s ) - - - ( 12 )
R TS = R DB + M RTS [ ( D 0 2 - R a + b 2 ) / 2 ] - - - ( 13 )
Z E = 0.4738 e [ - ( ( n s - 1461 ) / 1401 ) 2 ] · ( gH n s / n ) - - - ( 14 )
g 1 = R DB 7.5 · M RDB - - - ( 15 )
v m 1 = [ 0.3173 e ( 0.000971 n s ) - 1.0824 e ( - 0.0118 n s ) ] · gH - - - ( 16 )
v m 2 = { 17.2251 e [ - ( ( n s - 1358 ) / 705.7 ) 2 ] + 3.18198 e [ - ( ( n s - 526.2 ) / 415 ) 2 ] } · gH - - - ( 17 )
u 2 = { 0.07382 e [ - ( ( n s - 1133 ) / 129.7 ) 2 ] + 3.3361 e [ - ( ( n s - 2210 ) / 2308 ) 2 ] } · gH / 10 - - - ( 18 )
η h=1+0.0835lg(0.09633Q 0.3335-0.7264n 0.01142+0.7877) (19)
ρ = 2.5287 v m 2 + 10.2157 · H u 2 · η h - - - ( 20 )
β 1 = arctan [ 19.099 v m 1 n · sin [ ( - 0.02 n s + 59.1 ) · D j ] ] - - - ( 21 )
β 2 = arctan 0.001056 n s 1.608 · gH ρ v m 2 - ( gH v m 2 η h · u 2 ) - - - ( 22 )
β = [ 1 + 11.136 n s ( - 0.2238 ) - 1 1 + 3.33709 n s ( - 0.1129 ) ] ( β 1 + β 2 ) - - - ( 23 )
z = 6.5 · [ D 2 + sin ( - 0.02 n s + 59.1 ) D j D 2 - sin ( - 0.02 n s + 59.1 ) D j ] · sin β 1 + β 2 2 - - - ( 24 )
δ k = [ 4.556 · e ( 0.002923 n s ) - 2.197 · e ( - 0.007274 n s ) ] · D 2 · ( H / z ) 1 2 - - - ( 26 )
δ=M δ·δ k(27)
M δ=0.7368e (0.0031L)(28)
The present invention adopts exact formulas design method to carry out the Hydraulic Design, the hydraulic efficiency of pump and stability is greatly improved, has good economic benefit, be more conducive to the Program Appliance of computer.Because design method of the present invention is different from traditional analogue method and velocity-coefficient method, the mutual coupling of the size of hydraulic part more can be guaranteed.And calculate more accurate, Theoretical Design and realistic model are more met.
Above, that makes with reference to embodiment for patent of the present invention illustrates, but the present invention is not limited to above-described embodiment, also comprises other embodiments in concept of the present invention or variation.

Claims (10)

1. an impeller Hydraulic Design Method for diagonal pumps, provides the main geometric parameters of impeller, comprises diagonal pumps impeller outlet and horizontal sextant angle α, blade often put actual thickness δ, subtended angle of blade back shroud of impeller import fillet radius R tS, impeller blade number z, impeller outlet diameter D 2, blade exit width b 2, impeller inlet equivalent diameter D 0, impeller outlet diametral quotient M d2, blade exit spread factor M b2, impeller inlet equivalent diameter coefficient M d0, the distance Z that exports of front shroud of impeller vane inlet place and front shroud e, inlet side is apart from front shroud curve starting end distance g 1, front shroud of impeller import fillet radius R dB, impeller round nut radius R a, impeller round nut height R b, blade angle β, vane inlet laying angle β 1, blade exit laying angle β 2, slip coefficient ρ, vane inlet axis plane velocity v m1, blade exit axis plane velocity v m2, blade exit peripheral velocity u 2, hydraulic efficiency η hdeng, it is characterized in that: between impeller geometric parameter and pump operating point for design performance parameter, be applicable to following relation:
δ=M δ·δ k(3)
M δ=0.7368e (0.0031L)(5)
In formula:
α-diagonal pumps impeller outlet and horizontal sextant angle, degree;
D 2-impeller outlet diameter, rice;
B 2-blade exit width, rice;
The rotating speed of n-design conditions, rev/min;
N s-specific speed;
H-design conditions lift, rice;
G-gravity accleration, meter per second 2;
δ-blade often puts actual thickness, rice;
δ k-nominal airfoil thickness correction values, rice;
M δ-vane thickness coefficient;
L-length of blade, rice;
Z-impeller blade number;
subtended angle of blade, degree.
2. back shroud of impeller import fillet radius R tSdesign formula:
In formula:
R tS-back shroud of impeller import fillet radius, rice;
R dB-front shroud of impeller import fillet radius, rice;
D 0-impeller inlet equivalent diameter, rice;
M rTS-back shroud of impeller import fillet radius coefficient;
R a-impeller round nut radius, rice.
3. according to right (1) requirement, impeller blade number z design formula:
In formula:
β 1-vane inlet laying angle, degree;
β 2-blade exit laying angle, degree;
D j-impeller inlet diameter, wherein d hfor hub diameter; For single-stage diagonal pumps d h=0.
4. according to right (1) requirement, impeller outlet diameter D 2, blade exit width b 2, impeller outlet diametral quotient M d2, blade exit spread factor M b2design formula:
In formula:
D 20the minimum outlet diameter of-impeller, rice;
D 2hthe maximum outlet diameter of-impeller, rice;
M d2-impeller outlet diametral quotient;
M b2-blade exit spread factor.
5. the distance Z that exports of front shroud of impeller vane inlet place and front shroud e, inlet side is apart from front shroud curve starting end distance g 1design formula:
In formula:
Z ethe distance that-front shroud of impeller vane inlet place and front shroud export, rice;
G 1-inlet side distance front shroud curve starting end distance, rice;
M rDB-front shroud of impeller import fillet radius coefficient.
6. according to right (2) requirement, impeller inlet equivalent diameter D 0, impeller inlet equivalent diameter coefficient M d0, front shroud of impeller import fillet radius R dB, impeller round nut radius R a, impeller round nut height R bdesign formula:
M RDB=0.0905ln(n s)-0.1836 (18)
R a=16.531ln(D 0)-65.11 (19)
R b=1.51R a(20)
In formula:
M d0-impeller inlet equivalent diameter coefficient.
R b-impeller round nut height, rice.
7. the design formula of blade angle β:
In formula:
β-blade angle, degree;
β 1-vane inlet laying angle, degree;
β 2-blade exit laying angle, degree.
8. according to right (3) requirement, vane inlet laying angle β 1, blade exit laying angle β 2design formula:
In formula:
ρ-slip coefficient;
V m1-vane inlet axis plane velocity, meter per second;
V m2-blade exit axis plane velocity, meter per second;
U 2-impeller outlet peripheral velocity, meter per second;
η h-hydraulic efficiency.
9. according to right (8) requirement, slip coefficient ρ design formula:
10. according to right (8) requirement, vane inlet axis plane velocity v m1, blade exit axis plane velocity v m2, blade exit peripheral velocity u 2, hydraulic efficiency η hdesign formula:
η h=1+0.0835lg(0.09633Q 0.3335-0.7264n 0.01142+0.7877) (28)
CN201410711980.6A 2014-11-26 2014-11-26 A kind of oblique flow impeller of pump Hydraulic Design Method Active CN104533829B (en)

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