CN105179303A - Axial flow pump impeller all-operating-condition design method - Google Patents
Axial flow pump impeller all-operating-condition design method Download PDFInfo
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Abstract
An axial flow pump impeller all-operating-condition design method comprises the following steps that 1, parametric modeling of an axial flow pump impeller is performed, namely 2k design parameters including k wing section cascade solidities and wing placement angle values of the axial flow pump impeller are selected; 2, all-operating-condition optimal design is performed: firstly, conventional design parameters of the impeller are dertemined, then numerical calculation is conducted on the design conditions of the axial flow pump impeller and various losses in a pump are comprehensively analyzed to preliminarily design the axial flow pump impeller having better hydraulic performance under the design conditions in a total-loss minimization mode; secondly, guide blades, a water guide cone and water inlet and outlet flowing channels of the impeller are designed; thirdly, the optimal all-operating-condition weighted average effciency of the pump device is regarded as a target, a lift is regarded as a constraint condition, and a seqential quadratic programming method of a gradient optimum algorithm is adopted to constantly change the design parameters of the axial flow pump impeller and perform iterative numerical calculation of the pump device. The axial flow pump impeller all-operating-condition design method adopts CFD numerical calculation, the design accuray is high, and optimization results are reliable.
Description
Technical field
The present invention relates to a kind of axial-flow pump impeller full working scope design method, belong to water conservancy and power engineering technology field.
Background technique
Traditional axial-flow pump design method is only by single design method of design conditions, namely according to use occasion, a certain group of design discharge and rated lift value are proposed, carry out the design of whole pump, and so-called design conditions are in fact a bit on lift-flow (H-Q) performance curve.With the design that traditional design conditions method is carried out, under ideal fluid and Utopian flox condition, just ensure the performance of design point, as the performance under off-design behaviour, cannot ensure in the design, or can only draw from test.And in most cases, application axial-flow pump scene, its usage requirement can not be fixed on design conditions, the most of the time be in off-design behaviour under run.The designing requirement of axial-flow pump should be: as far as possible high efficiency, suitable performance curve and good Cavitation Characteristics.And efficiency requirements higher under the unilateral pursuit design conditions of traditional axial-flow pump design method, have ignored other hydraulic performance requirement.Therefore, traditional this design conditions design method more and more will can not meet day by day complicated Production requirement, and the defect of the design conditions design method that this axial-flow pump impeller is traditional mainly contains the following aspects:
1. the theory of method is Euler's equation, and Euler's equation just establishes the relation between external characteristics parameter and axial-flow pump impeller import and export speed, impeller internal velocity field and pressure field are not analyzed, although some design considers fluid viscosity impact, carry out the correction of empirical correlation, but still too coarse.
2. design process is for axial-flow pump impeller itself, does not consider the impact of the flow passage components such as stator, inlet and outlet channel on Internal Flow in Axial Pump and axial-flow pump performance.Particularly design conditions, can only say the requirement substantially meeting design conditions.
3. design process oversimplification, personal factor is comparatively large, and error is large.
4. under off-design behaviour, axial flow pump performance cannot be taken into account, and the efficiency under design conditions also can only reach the level of institute's statistics, is difficult to improve further.
5. design is carried out successively, does not consider influencing each other between upstream and downstream and between various loss.
But along with the development of numerical simulation technology and numerical optimization technique, and for the innovation of axial-flow pump impeller design concept, patent of the present invention proposes a kind of axial-flow pump full working scope design method.
Summary of the invention
The object of this invention is to provide a kind of axial-flow pump impeller full working scope design method, use indirect problem design method, consider that the multiple target of multiple operating point carries out full working scope optimal design to axial-flow pump.When optimal design, overall calculation is carried out to the hydraulic performance of pump-unit, determines the design proposal of axial-flow pump impeller according to pump-unit result of calculation.When calculating, carry out numerical simulation by CFX flow simulations software, calculation accuracy is high, and optimum results is reliable.Example optimal design shows: design point efficiency increases, but increasing degree is not obvious, but large discharge operating point efficiency and low flow rate condition efficiency improve comparatively obvious, wherein large discharge operating point efficiency improves about 7.4%, low flow rate condition point efficiency improves about 2.6%, efficient district scope obviously broadens, optimal design successful.
The object of the invention is to be achieved through the following technical solutions, a kind of axial-flow pump impeller full working scope design method, comprises the following steps:
(1) axial-flow pump impeller parametric modeling:
Select k aerofoil profile section cascade solidity of axial-flow pump impeller and aerofoil profile to lay angle value and amount to 2k design parameter;
(2) full working scope optimal design:
The first, first determine this impeller conventional design parameters, design discharge Q, rated lift H, rotating speed n, monolateral gap, leaf top, unit is mm; Impeller blade number, axial-flow pump impeller hub ratio dd; Then numerical calculation is carried out to axial-flow pump impeller design conditions, comprehensive analyze every loss in pump, go out hydraulic performance preferably one pair of axial-flow pump impeller under design conditions with the minimum proposal plan of total losses;
The second, then the design carrying out stator, water guide cone and inlet and outlet channel for this impeller, determine the size of diffuser diffusion angle, the stator number of blade, water guide cone and inlet and outlet channel;
3rd, finally by Isight numerical optimization platform intergration CFX numerical optimization software, impeller, stator, water guide cone and inlet and outlet channel are integrated into pump-unit, optimum for target with the weighted average efficiency of pump-unit full working scope, lift is constraint conditio, selects the Sequential Quadratic Programming method of gradient optimal method, continuous change axial-flow pump impeller design parameter, iterations and numerical simulation is carried out to pump-unit, by iteration, finally finds the design proposal making axial-flow pump impeller that pump-unit overall efficiency is the highest.
Preferably, the computational methods of cascade solidity in described parametric modeling: by changing blade tip cascade solidity value a
1with blade root cascade solidity multiple a
2, change each section cascade solidity value, the formula of cascade solidity l/t (i) is:
l/t(i)＝n+m/r(i)
m＝(a
2-1)*a
1/(1/dd-1)
n＝a
1-m
Wherein, a
1for blade tip cascade solidity value; a
2for blade root cascade solidity multiple; Dd is hub ratio; N, m are intermediate computations amount; I=1-k, k are aerofoil profile section sum; R (i) is the relative radius value of i-th section, i.e. the ratio of each cross sectional radii and impeller radius; L/t (i) is the cascade solidity value of i-th section.
Preferably, in described parametric modeling, the computational methods of aerofoil profile laying angle are: the aerofoil profile according to an impeller k section of initial designs operating mode lays angle value, by carrying out matching by quadratic polynomial to these ten aerofoil profile laying angles, matching obtains the relation between aerofoil profile laying angle β and relative radius value r:
β＝a
3-a
4*r+a
5*r
2
Defining this quadratic polynomial three coefficients is a
3, a
4, a
5for the design variable of optimal design, by controlling this three coefficient a
3, a
4, a
5the change of value controls the change of each section wing laying angle, realizes the parametric modeling of impeller blade.
Preferably, described full working scope optimal design, when operating mode is selected, chooses three flow rate working conditions points, selects design discharge operating point, low flow rate condition point and large discharge operating point respectively: design discharge operating point is Q
0, then low flow rate condition point Q
little=(0.7-0.9) * Q
0, large discharge operating point Q
greatly=(1.1-1.3) * Q
0;
Under three flow rate working conditions, lift change among a small circle, constantly changes the value of axial flow pump blade inner design variable, makes the efficiency of three flow rate working conditions point pump-units all reach optimum value, to widen the efficient district scope of axial-flow pump device, and then determine the design proposal of axial-flow pump impeller;
Optimized model is as follows:
Objective function: max η (x)=w
1η
1(x)+w
2η
2(x)+w
3η
3(x) (1)
Design variable: x=[a
l, a
2, a
3, a
4, a
5]
t
Wherein η
1, η
2and η
3the efficiency of low flow rate condition, design conditions and large discharge operating mode respectively; w
1, w
2and w
3be respectively corresponding weighted value, weighted value is determined according to the actual run time of pumping plant low flow rate condition, design conditions and large discharge operating mode; H
1, H
2and H
3be respectively the lift of low flow rate condition, design conditions and large discharge operating mode, unit m; Impeller for design conditions design is initial scheme, and the initial designs variate-value of corresponding impeller is A
1, A
2, A
3, A
4, A
5.
Preferably, described H
2excursion value 0-0.2m; H
1, H
3excursion value 0-1m.
Compared with prior art, the present invention has following beneficial effect:
The first, adopt CFD numerical calculation, design accuracy is high, and optimum results is reliable.By calculating the final design scheme of pump-unit hydraulic performance determination axial-flow pump impeller, take into full account influencing each other of each passage component of pump-unit and various hydraulic loss, improve the efficiency of each operating point of pump-unit, the pump assembly efficiency curve that the efficient district obtained is wider, obtains more suitable characteristic curve of pump.
Second, along with the construction of Inter-Basin Water Transfer Project, the enforcement of the large-scale and small and medium-sized pumping station technical innovation of country, amount to thousands of seat pumping plant to need carry out newly-built and renovate, and require more and more higher to pump performance, therefore the application of this patent and enforcement, will obtain larger economic benefit and social benefit.
Accompanying drawing explanation
Fig. 1 is axial-flow pump device optimal design flow chart.
Fig. 2 is pump-unit mathematical calculation model.
Fig. 3 is for optimizing front and back pump-unit performance curve.
Wherein 1. intake pipe 2. impeller 3. diffuser 4. outlet pipes in Fig. 2.
Embodiment
Below in conjunction with accompanying drawing, this aial flow impeller is described further.
1, the technical problem to be solved in the present invention
1) adopt CFD numerical calculation as subject analysis mode, design accuracy is high, avoids artificial design by rule of thumb.
2) optimal design adopts full working scope Optimization Design, takes into account the hydraulic performance under off-design behaviour, widens efficient district scope as far as possible, obtain more suitable performance curve.
3) optimal design adopts multi-objective optimization design of power method, improves the efficiency of each flow rate working conditions point as much as possible, also should have good cavitation performance.
4) optimal design determines the final design scheme of axial-flow pump impeller according to the hydraulic performance optimum of the pump-unit of numerical calculation, designs different successively, take into full account influencing each other between each passage component of pump-unit and various loss from tradition.
2, technological scheme of the present invention
1) axial-flow pump impeller parametric modeling
During the design of general axial-flow pump impeller, axial flow pump blade inner is divided into 11 two-dimentional aerofoil profile sections and designs.Axial-flow pump impeller is combined into again by smooth for each section wing designed.Axial flow pump blade inner design parameter is a lot, can be changed the shape of axial flow pump blade inner by the change each section cascade solidity of axial-flow pump and aerofoil profile laying angle very easily.
In patent of the present invention, cascade solidity (l/t) is an important parameter of axial flow pump blade inner design, l: refer to aerofoil profile section chord length; T=2 π r/z, wherein z is the number of blade, and r is the radius value at this aerofoil profile section place.Blade tip cascade solidity refers to the cascade solidity value of the aerofoil profile section of blade outer most edge, and blade root cascade solidity is exactly the cascade solidity value of the aerofoil profile section of wheel hub.Blade root cascade solidity multiple refers to the ratio of blade root cascade solidity and blade tip cascade solidity, such as: blade tip cascade solidity is 0.82, blade root cascade solidity multiple is 1.4, then blade root cascade solidity=blade tip cascade solidity 0.82* blade root cascade solidity multiple 1.4=1.148.Middle each section cascade solidity linearly changes from blade tip to blade root.Angle between the chord length at aerofoil profile laying angle and each section wing place and horizontal line.
11 aerofoil profile sections just have 22 design parameters, the efficiency of blade optimization greatly can be reduced when optimizing, and found by matching, axial-flow pump each section cascade solidity is linear, therefore only needs namely can change 11 section cascade solidity values by change blade tip cascade solidity and blade root cascade solidity multiple; And 11 section wing laying angles become quadratic relation.That is: β=a
1-a
2* r+a
3* r
2, the aerofoil profile only needing three coefficients changing quadratic relation can change 11 sections lays angle value.Hub ratio and the number of blade are chosen according to relevant references recommendation.When being optimized design, the value that only need change above 5 variablees can change the distorted shape of axial flow pump blade inner, and then changes the hydraulic performance of axial-flow pump device, improves the efficiency optimized, and shortens the cycle of design.The program of being write by fortran can realize changing the value of these 5 variablees and then changing the shape of axial flow pump blade inner.
2) full working scope optimal design
The basic ideas of Patent design axial-flow pump impeller of the present invention: first according to ideal flow situation, real liguid, numerical calculation is carried out according to design conditions to axial-flow pump impeller, every loss in comprehensive analysis pump, go out one pair of axial-flow pump impeller of hydraulic performance optimum under design conditions with the minimum proposal plan of total losses, determine the geometrical shape of this impeller and each design parameter.Carry out the design of stator, water guide cone and inlet and outlet channel again for this impeller, parametric modeling is carried out to this impeller simultaneously, can change the geometrical shape of axial-flow pump impeller easily by changing design parameter.Finally by iSIGHT numerical optimization platform intergration CFX numerical optimization software, each passage component is integrated into pump-unit, optimum for target with the weighted average efficiency of pump-unit full working scope, lift is constraint conditio, continuous change axial-flow pump impeller design parameter, iterative computation is carried out to pump-unit, by iteration, finally finds the design proposal making axial-flow pump impeller that pump-unit overall efficiency is the highest.
Optimal design operating mode is determined:
Full working scope optimal design, when operating mode is selected, mainly chooses three flow rate working conditions points, selects design discharge operating point, low flow rate condition point and large discharge operating point respectively.As: design discharge operating point is Q
0, then low flow rate condition point Q
little=0.8*Q
0, large discharge operating point Q
greatly=1.2*Q
0.
The target of optimal design:
During multi-objective optimization design of power, during main consideration full working scope optimal design, the efficiency of each flow rate working conditions point is higher, to widen the efficient district scope of performance curve.Each operating point efficiency adopts normalized when optimizing, i.e. max η (x)=w
1η
1(x)+w
2η
2(x)+w
3η
3(x), wherein η
1, η
2and η
3the efficiency of low flow rate condition, design conditions and large discharge operating mode respectively.W
1, w
2and w
3be respectively corresponding weighted value.Weighted value is determined according to pumping plant each flow rate working conditions point actual run time.
The constraint conditio of optimal design:
Constraint conditio is mainly the lift of each operating point, and the cavitation performance requirement of design point.In order to ensure the service condition that can meet same seat pumping plant after axial-flow pump impeller before optimization, its nominal specific speed is consistent, operating point for design lift excursion should be little as far as possible, excursion suggestion value 0 ~ 0.2m, other operating point for design lift excursions suggestion value 0 ~ 1m.Depending on pumping plant concrete condition.
Because cavitation performance is when off-design behaviour, numerical simulation calculation error is comparatively large, and therefore when full working scope optimal design, singly can consider the necessary NPSH requirement of design conditions, necessary NPSH is the smaller the better.Different impeller necessary NPSH value changes greatly, for ensureing that impeller has good cavitation performance, and the binding occurrence of visual concrete impeller determination necessary NPSH.
The selection of optimized algorithm:
Axial-flow pump full working scope multi-objective optimization design of power is constrained, non-linear, multiple target and the not unique optimization design problem of solution, selects the Sequential Quadratic Programming method (SequentialQuadraticProgramming, SQP) of gradient optimal method.The method can directly process equation and inequality constraints, is one of outstanding nonlinear thermal gradient algorithm of generally acknowledging at present.Have good global convergence and local and superlinear convergence characteristic, iterations is few, fast convergence rate, has very strong border and receives Suo Nengli, few for this paper design variable, and the few optimization design problem of constraint conditio is especially applicable.
Subject is analyzed:
Subject analysis adopts CFD numerical computation method, traditional optimization is carried out successively, hydraulic performance only for axial-flow pump impeller under design conditions (single pump) is optimized design, then carry out the design of stator and runner according to the impeller optimized, have ignored influencing each other between the passage component such as impeller, stator.The another large innovative point of patent of the present invention is, CFD numerical calculation is adopted during optimization, calculate the hydraulic performance of multiple flow rate working conditions point pump-unit (comprising impeller, stator, water guide cone and water-in and water-out runner), fully take into account influencing each other between each passage component of axial-flow pump device and various hydraulic loss.
Know-why:
Axial-flow pump device under design conditions in each passage component the flowing of liquid can think best flowing state, be similar to ideal flow.But when actual operating mode off-design operating mode, due to the impact of the factor such as viscosity of water, will produce the bad fluidised forms such as whirlpool, backflow, stall and the separation of flow in axial-flow pump inside and each passage component, these bad fluidised forms will be aggravated gradually along with the degree of off-design operating mode.Therefore, when designing axial-flow pump, only can not be conceived to the hydraulic performance requirement of design conditions, consider and paying attention to the hydraulic performance requirement of off-design behaviour point.Patent exploitation indirect problem design method of the present invention, considers that the multiple optimization aim of multiple operating point is optimized design to axial-flow pump.When optimal design, overall calculation is carried out to the hydraulic performance of pump-unit, determines the design proposal of axial-flow pump impeller according to pump-unit result of calculation.When calculating, carry out numerical simulation by CFX flow simulations software, calculation accuracy is high.Change axial-flow pump impeller design parameter, improve or postpone the bad fluidised form of axial-flow pump device inside, to reach the object improving each flow rate working conditions point efficiency.
3, beneficial effect
Adopt CFD numerical calculation, design accuracy is high, and optimum results is reliable.By calculating the final design scheme of pump-unit hydraulic performance determination axial-flow pump impeller, take into full account influencing each other of each passage component of pump-unit and various hydraulic loss, improve the efficiency of each operating point of pump-unit, the pump assembly efficiency curve that the efficient district obtained is wider, obtains more suitable characteristic curve of pump.
Embodiment 1
Use patent Optimization Design of the present invention, the axial-flow pump impeller being 800 for a certain nominal specific speed carries out full working scope multi-objective optimization design of power.Design parameter: design discharge Q=360L/s, rated lift H=6.0m, rotating speed n=1450r/min, monolateral gap, leaf top is 0.2mm.Exit guide vane body is design conditions for this impeller and for design, the angle of flare of diffuser is 6 °, the stator number of blade 7, impeller blade number 4, and axial-flow pump impeller hub ratio is 0.4333.Water inlet straight length and Discharging bent-tube section adopt Proe modeling, and impeller and diffuser, according to its three-dimensional coordinate data point, adopt Turbo-Grid modeling.Axial-flow pump device computation model as shown in Figure 2.
1. numerical simulation
Stress and strain model: water inlet straight length and Discharging bent-tube section adopt ICEM software to carry out structured grid division, and mesh quality is more than 0.4; Axial-flow pump impeller and diffuser carry out structured grid division in Turbo-Grid, and mesh quality is better, can meet calculation requirement.Axial-flow pump impeller grid number is 330928, and diffuser grid number is 365274, and whole computational fields grid number is 1215277.When calculating iteration, impeller grid number keeps quite, and miscellaneous part grid number remains unchanged.
Boundary conditions is arranged: the import of pump-unit computational fields is the import of intake pipe, and import border condition setting is stagnation pressure condition, and namely inlet's stagnation pressure is set to a standard atmospheric pressure.The outlet of pump-unit computational fields is the outlet of Discharging bent-tube section, and outlet border is set to mass flow rate and exports, and impeller is set to and rotates territory, and all the other computational fields are static territory.The stage model that sound interface adopts speed average, interface adopts None interface model silently.
2. axial-flow pump impeller parametric modeling
Patent of the present invention selects change axial-flow pump impeller 11 aerofoil profile section cascade solidities and aerofoil profile to lay angle value totally 22 design parameters when parametric modeling, can change axial flow pump blade inner shape very easily.
Cascade solidity: by changing blade tip cascade solidity value (a
1) and blade root cascade solidity multiple (a
2), 11 section cascade solidity values can be changed very easily.Program is as follows:
a
1；
a
2；
dd＝0.4333
m＝(a
2-1)*a
1/(1/dd-1)
n＝a
1-m
doi＝1,k
l/t(i)＝n+m/r(i)
enddo
Wherein, a
1for blade tip cascade solidity value; a
2for blade root cascade solidity multiple; Dd is hub ratio; N, m are intermediate computations amount; K is aerofoil profile section number, totally 11 sections in this example; R (i) is the relative radius value of i-th section, i.e. the ratio of each cross sectional radii and impeller radius, is respectively: 1.000000 in this example from wheel rim to wheel hub; 0.9370334; 0.8740667; 0.8111000; 0.7481333; 0.6851667; 0.6222000; 0.5592333; 0.4962667; 0.4333000; 0.36667; L/t (i) is the cascade solidity value of i-th section.
This example hub ratio is fixed value, therefore only need provide the cascade solidity value that blade tip cascade solidity value and blade root cascade solidity can obtain each section, thus control axial flow pump blade inner geometrical shape easily.
Aerofoil profile laying angle: this example lays angle value according to the aerofoil profile of initial designs impeller 11 sections, by carrying out matching by quadratic polynomial to these ten aerofoil profile laying angles, matching obtains the relation between aerofoil profile laying angle and relative radius value:
β
m＝90.504-129.96.4r+57.26r
2
Defining this quadratic polynomial three coefficients is a
1, a
2, a
3the design variable of optimal design, is controlled the change of each section wing laying angle, and then realizes the parametric modeling of impeller blade by the change controlling these three coefficient values.
3. optimal design
By CFX numerical analysis software and Isight numerical optimization software, full working scope multi-objective optimization design of power is carried out to axial-flow pump.The final design scheme of the impeller of axial-flow pump is determined by the hydraulic performance calculating axial-flow pump device.
1) operating mode is determined:
Study full working scope optimal design herein, in order to obtain better performance curve, choosing large discharge, small flow and design discharge three operating points and being optimized design.According to design conditions Q=360L/s, about 0.8 times of selected design discharge and about 1.2 times as low flow rate condition and large discharge operating mode, the present invention for research convenient, round numbers, namely low flow rate condition gets Q=300L/s, and large discharge operating mode gets Q=420L/s.
2) optimized algorithm:
For constrained, non-linear, multiple target and the not unique axial-flow pump device multi-operating mode hydraulic performance optimization design problem of solution, select the Sequential Quadratic Programming method (SequentialQuadraticProgramming, SQP) of gradient optimal method.
3) Optimized model is set up:
The object optimized is in the optimization range of axial-flow pump impeller design variable, under constraint conditio, finds the optimum value of design parameter, makes the efficiency optimization of axial-flow pump device three operating points.To axial-flow pump full working scope multi-objective optimization design of power problem definition be: under three flow rate working conditions, lift change among a small circle, the value of continuous change axial flow pump blade inner design variable, the efficiency of three flow rate working conditions point pump-units is made all to reach optimum value, to widen the efficient district scope of axial-flow pump device, and then determine the design proposal of axial-flow pump impeller.This example is with the impeller designed for design conditions for initial scheme, and the initial designs variable of corresponding impeller is: a
1=0.9885, a
2=1.2897, a
3=90.504, a
4=-129.96, a
5=57.26.
Optimized model is as follows:
Objective function:
maxη(x)＝w
1η
1(x)+w
2η
2(x)+w
3η
3(x)(1)
Design variable: x=[a
l, a
2, a
3, a
4, a
5]
t
In formula, η
1, η
2and η
3the efficiency of low flow rate condition, design conditions and large discharge operating mode respectively.W
1, w
2and w
3be respectively corresponding weighted value.Weighted value should be determined according to each operating point pumping plant actual run time.This example weighted value gets w respectively
1=0.3, w
2=0.4 and w
3=0.3.H
1, H
2and H
3be respectively the lift of each operating point, unit m.In order to the design point of axial-flow pump impeller is constant after ensureing optimal design, specific speed is consistent, and therefore operating point for design lift excursion is little as far as possible, and other 2 operating point lift excursions can be slightly large.
4) optimum results:
The design variable of continuous change axial-flow pump impeller, in lift restriction range, makes the total efficiency of axial-flow pump device 3 operating points the highest.Through continuous iterative computation, obtain the final design scheme of axial-flow pump impeller.Optimum results and initial results contrast as shown in table 1.
Table 1 pump-unit numerical optimization result
According to table 1 result, blade tip cascade solidity reduces, and outer rim aerofoil profile length reduces, and blade root cascade solidity multiple increases, and reduce the length difference of inside and outside aerofoil profile, balanced blade exit lift, reduces Radial Flow, improves the hydraulic performance of impeller; Can find according to the change of aerofoil profile laying angle fitting coefficient simultaneously, wheel rim lateral wing type laying angle increases, and hub side aerofoil profile laying angle reduces to some extent, reduces the distortion of impeller blade shapes, improve the operating conditions of aerofoil profile, this is consistent with the thinking of axial-flow pump impeller optimal design.Optimum results shows, design point efficiency increases, but increasing degree is not obvious, but large discharge operating point efficiency and low flow rate condition efficiency improve comparatively obvious, wherein large discharge operating point efficiency improves 7.4%, and low flow rate condition point efficiency improves 2.6%, and effect of optimization is obvious.
All the other each operating point pump-unit hydraulic performances are passed through numerical simulation calculation and contrasts with the front axial-flow pump device hydraulic performance of optimization, as shown in Figure 3.
Optimize front and back pump-unit performance chart according to Fig. 3, optimize after axial-flow pump device low flow rate condition and design conditions lift in a slight decrease, but efficiency increases; Large discharge operating mode lift raises to some extent, and efficiency also increases.Optimize behind efficiency curve integral raising, efficient district scope broadens, and improves pumping station operation stability, reduces pumping station operation cost, and pump-unit effect of optimization is fairly obvious.
1) propose the method for the axial-flow pump device optimization design under multiple working conditions based on numerical analysis and numerical optimization technique of complete set, the method can reduce axial-flow pump optimal design cost greatly, shortens the optimal design cycle.
2) the subject analysis mode adopting CFD to calculate, the means of binding tests research replace artificial optimal way by rule of thumb, improve the confidence level of optimum results, also demonstrate that the reliability of axial-flow pump device optimization design under multiple working conditions, high efficiency simultaneously.
3) axial-flow pump device low flow rate condition point efficiency improves about 2.6%, and design point efficiency improves about 0.5%, and large discharge operating point efficiency improves at most, and about 7.4%.After optimizing, the efficient district of axial-flow pump device obviously broadens, and greatly reduce pumping station operation cost, effect of optimization is fairly obvious.
Claims (5)
1. an axial-flow pump impeller full working scope design method, is characterized in that, comprises the following steps:
(1) axial-flow pump impeller parametric modeling:
Select k aerofoil profile section cascade solidity of axial-flow pump impeller and aerofoil profile to lay angle value and amount to 2k design parameter;
(2) full working scope optimal design:
The first, first determine this impeller conventional design parameters, design discharge Q, rated lift H, rotating speed n, monolateral gap, leaf top, unit is mm; Impeller blade number, axial-flow pump impeller hub ratio dd; Then numerical calculation is carried out to axial-flow pump impeller design conditions, comprehensive analyze every loss in pump, go out hydraulic performance preferably one pair of axial-flow pump impeller under design conditions with the minimum proposal plan of total losses;
The second, then the design carrying out stator, water guide cone and inlet and outlet channel for this impeller, determine the size of diffuser diffusion angle, the stator number of blade, water guide cone and inlet and outlet channel;
3rd, finally by Isight numerical optimization platform intergration CFX numerical optimization software, impeller, stator, water guide cone and inlet and outlet channel are integrated into pump-unit, optimum for target with the weighted average efficiency of pump-unit full working scope, lift is constraint conditio, selects the Sequential Quadratic Programming method of gradient optimal method, continuous change axial-flow pump impeller design parameter, iterations and numerical simulation is carried out to pump-unit, by iteration, finally finds the design proposal making axial-flow pump impeller that pump-unit overall efficiency is the highest.
2. axial-flow pump impeller full working scope design method according to claim 1, is characterized in that, the computational methods of cascade solidity in described parametric modeling: by changing blade tip cascade solidity value a
1with blade root cascade solidity multiple a
2, change section cascade solidity value, the formula of cascade solidity l/t (i) is:
l/t(i)＝n+m/r(i)
m＝(a
2-1)*a
1/(1/dd-1)
n＝a
1-m
Wherein, a
1for blade tip cascade solidity value; a
2for blade root cascade solidity multiple; Dd is hub ratio; N, m are intermediate computations amount; I=1-k, k are aerofoil profile section sum; R (i) is the relative radius value of i-th section, i.e. the ratio of each cross sectional radii and impeller radius; L/t (i) is the cascade solidity value of i-th section.
3. axial-flow pump impeller full working scope design method according to claim 1, it is characterized in that, in described parametric modeling, the computational methods of aerofoil profile laying angle are: the aerofoil profile according to an impeller k section of initial designs operating mode lays angle value, by carrying out matching by quadratic polynomial to these ten aerofoil profile laying angles, matching obtains the relation between aerofoil profile laying angle β and relative radius value r:
β＝a
3-a
4*r+a
5*r
2
Defining this quadratic polynomial three coefficients is a
3, a
4, a
5for the design variable of optimal design, by controlling this three coefficient a
3, a
4, a
5the change of value controls the change of each section wing laying angle, realizes the parametric modeling of impeller blade.
4. axial-flow pump impeller full working scope design method according to claim 1, it is characterized in that, described full working scope optimal design, when operating mode is selected, chooses three flow rate working conditions points, selects design discharge operating point, low flow rate condition point and large discharge operating point respectively: design discharge operating point is Q
0, then low flow rate condition point Q
little=(0.7-0.9) * Q
0, large discharge operating point Q
greatly=(1.1-1.3) * Q
0;
Under three flow rate working conditions, lift change among a small circle, constantly changes the value of axial flow pump blade inner design variable, makes the efficiency of three flow rate working conditions point pump-units all reach optimum value, to widen the efficient district scope of axial-flow pump device, and then determine the design proposal of axial-flow pump impeller;
Optimized model is as follows:
Objective function: max η (x)=w
1η
1(x)+w
2η
2(x)+w
3η
3(x) (1)
Design variable scope
Constraint conditio
Design variable: x=[a
l, a
2, a
3, a
4, a
5]
t
Wherein η
1, η
2and η
3the efficiency of low flow rate condition, design conditions and large discharge operating mode respectively; w
1, w
2and w
3be respectively corresponding weighted value, weighted value is determined according to the actual run time of pumping plant low flow rate condition, design conditions and large discharge operating mode; H
1, H
2and H
3be respectively the lift of low flow rate condition, design conditions and large discharge operating mode, unit m; Impeller for design conditions design is initial scheme, and the initial designs variable of corresponding impeller is a
1, a
2, a
3, a
4, a
5.
5. axial-flow pump impeller full working scope design method according to claim 4, is characterized in that, described H
2excursion value 0-0.2m; H
1, H
3excursion value 0-1m.
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