CN107762966A - A kind of design method of high-efficiency helical sweepback axial wheel hydraulic model - Google Patents

A kind of design method of high-efficiency helical sweepback axial wheel hydraulic model Download PDF

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Publication number
CN107762966A
CN107762966A CN201710948115.7A CN201710948115A CN107762966A CN 107762966 A CN107762966 A CN 107762966A CN 201710948115 A CN201710948115 A CN 201710948115A CN 107762966 A CN107762966 A CN 107762966A
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blade
unit
rice
impeller
axial
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CN107762966B (en
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王俊华
白茂宁
尤保健
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HEFEI KAIQUAN MOTOR PUMP CO Ltd
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HEFEI KAIQUAN MOTOR PUMP CO Ltd
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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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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The invention discloses a kind of design method of high-efficiency helical sweepback axial wheel hydraulic model, belong to hydrodynamic force engineering design technology field, including wheel hub, the blade being uniformly arranged in circumference of hub, design feature and actual operating mode for submersible axial flow pump propose rational hub ratio, nD values, the geometric parameters such as consistency, blade is designed using rational circular rector and axis plane velocity changing rule, aerofoil profile stacking form is by the leading edge stacking for waiting variable angle spiral change, blade shape uses swept-back, addition blade is antecurvature and applies the corresponding optimal kyphotic angle of optimization means optimization.The axial-flow pump impeller that the present invention designs, the media such as particle suspensions, fiber or biological floc can preferably be transported, it is outstanding without blocking and antiwind ability, good effect is achieved in actual sewage processing, suitable curved plunder can also improve " hump zone " easily occurred in axial-flow pump, make the interior flowing of pump more steady, improve the runnability of axial-flow pump.

Description

A kind of design method of high-efficiency helical sweepback axial wheel hydraulic model
Technical field：
The present invention relates to hydrodynamic force engineering design technology field, and in particular to a kind of high-efficiency helical sweepback axial wheel waterpower The design method of model.
Background technology：
With the continuous development of economic society, submersible axial flow pump has larger demand in market of sewage treatment, in agriculture The fields such as field irrigation, municipal plumbing, water diversion project, electric power plant circulating water are widely used.
At present, the submersible axial flow pump of domestic production, hydraulic model used are commonly domestic and develop more ripe dry type axle stream The outstanding hydraulic model of pump, it integrates hydraulic performance and can compared favourably with external product, and some indexs have been even more than external similar production Product.But these hydraulic models are applied in submersible axial flow pump, its hydraulic performance significantly declines, efficiency reduction by 10%~ 20%, the significant wastage of electric power energy is caused, adds the operating cost of pump, is not saved also uneconomical.On the other hand, dry type axle Stream pump pumped (conveying) medium be clear water, does not consider the abrasion of wheel member in actual condition, foreign matter winding and blocking etc. during work.
Submerged axial-flow pump configuration is that motor combines as a whole with water pump, and motor flows through electronic in the top of water pump, medium The annular channel of machine outer wall.Because the outer wall dimension of motor is determined by power and rotating speed, which limits diffuser Outlet size, also just define stator angle of flare.Because the lower flange size of motor is larger, hub size is smaller, stator diffusion Angle normal conditions are bigger than normal a lot, and this results in divergence loss very big in diffuser, reduce the efficiency of water pump.
To sum up state, the design method of dry type axial-flow pump impeller, can not be applied in the design of efficient submerged axial-flow impeller of pump, Therefore, it is necessary to consider the structure and actual operating mode of submersible axial flow pump；Therefore, contrast diving and two kinds of submersible axial flow pumps of dry type Structure type, adapt to the medium requirements of actual operating mode, explore and be applied to the energy-efficient hydraulic model of submersible axial flow pump Design method is extremely urgent.
The content of the invention：
In order to make up the deficiency of prior art problem, it is an object of the invention to provide a kind of high-efficiency helical sweepback axial wheel The design method of hydraulic model, there is the premium properties such as energy-efficient, anti-cavitation performance is good, anti-blocking resistant wear and antiwind property are good.
Technical scheme is as follows：
The design method of high-efficiency helical sweepback axial wheel hydraulic model, it is characterised in that comprise the following steps,
1), impeller shape uses the structure type of swept-back, and blade sweepback angle is in 15 °~30 ° ranges, aerofoil profile heap Folded to be stacked using leading edge, blade inlet edge, which is pressed, waits the change of variable angle spiral rule, and blade designs by swirl distribution rule is become；
R=r1·eθtanβ；In formula：
- angle of sweep, degree；
r1- import and wheel hub cross streams radius surface, unit：Rice；
r2- import and wheel rim cross streams radius surface, unit：Rice；
β-isogonism angle changing, unit：Degree；
R-stream interface radius, unit：Rice；
The cornerite of θ-stream interface and inlet side intersection point, unit：Degree；
2) impeller outer diameter, is corrected：Boss shape is designed as taper, outline is adapted with stator, is ensureing cavitation Under the premise of impeller outer diameter is modified, using increase hub ratio dh/ D modes, to meet submersible axial flow pump actual motion neutrality Energy parameter, i.e., according to hub ratio d corresponding to specific speed nsh/ D values, and ensure that nD values scope is corresponding with specific speed ns value ranges：
In formula：
D-impeller outer diameter, rice；
dh/ D-hub ratio；
Q-flow, cubic meter is per hour；
N-rotating speed, rpm；
2), impeller hydraulic model chooses the number of blade：On the premise of efficiency and cavitation is taken into account, select rational leaf grating dense Degree, increase root aerofoil profile length, reduce wheel rim aerofoil profile length, the energy conversion of balanced each stream interface, ensure number of blade z according to than turning Fast ns is chosen；
In formula：
L/t-cascade solidity；
R-stream interface radius, unit：Rice；
H-lift, unit：Rice；
N-rotating speed, unit：Rev/min；
R-impeller radius, unit：Rice；
K-correction factor；
3), blade designs by swirl distribution rule is become：The total circular rector of blade is evenly distributed on each blade, then by change ring Amount the regularity of distribution circular rector is assigned on each stream interface, each stream interface circular rector is radially changed according to certain rules, make root and Blade load is small at outer rim, and middle stream interface blade load is big；
Kj=0.768g4.618 (r/R) -2.848 (r/R)2, in formula：
Kj- swirl distribution coefficient；
R-stream interface radius, unit：Rice；
R-impeller radius, unit：Rice；
4) lift-drag ratio, is designed using lift force method, and thickeied from the aerofoil profile to match with required lift coefficient, is selected NACA series aerofoil sections sheet simultaneously carries out antecurvature optimization to impeller axis projection, and antecurvature angle is generally 8 °~14 °, found out optimal Angle.
It is an advantage of the invention that：
The axial-flow pump impeller that the present invention designs, it can preferably transport Jie such as particle suspensions, fiber or biological floc Matter, no blocking and antiwind ability are outstanding, achieve good effect in actual sewage processing, suitable curved plunder can also improve " hump zone " easily occurred in axial-flow pump, make the interior flowing of pump more steady, improve the runnability of axial-flow pump.
Brief description of the drawings：
Fig. 1 is submerged axial-flow pump impeller shaft face perspective view of the present invention；
Fig. 2 is the plane figure of the axial-flow pump impeller of the present invention.
Fig. 3 is the hub ratio value table under different specific speed ns of the present invention.
Fig. 4 is different specific speed ns values of the present invention and different nD values corresponding tables.
Fig. 5 is different specific speed ns of the present invention and different leaves number z, adjusted coefficient K corresponding table.
Reference：1st, impeller blade；2nd, impeller hub, 3, entrance edge of blade, 4, exit edge of blade, 5, impeller hub it is straight Footpath dh, 6, impeller outer diameter D, 7-stream interface radius r, 8, angle of sweep9th, import and wheel rim cross streams radius surface r2,10, stream interface with The wrap angle of inlet side intersection point, 11, stream interface radius r, 12, import and wheel hub cross streams radius surface r1.
Embodiment：
Referring to accompanying drawing：
The present invention uses blade swept-back, and aerofoil profile, by waiting variable angle spiral rule to change, uses along leading edge between each stream interface Become circular rector, become the lift method design of axis plane velocity, be below operating principle：
1st, the shapes and sizes of wheel hub affect the fluidised form before fluid contact blade, also just influence the efficiency of impeller indirectly, Boss shape of the present invention uses cone hub, and contour line coordinates gate vane channel shape, makes flowing much smoother.Due to submersible axial flow pump Lower flange is larger, and stator angle of flare is too big, and efficiency, hub ratio d are improved to reduce divergence lossh/ D is suitably increased, and is not turned on year-on-year basis Hub ratio value under fast ns can be found in accompanying drawing 3：
2nd, impeller outer diameter D and rotating speed n is axial-flow pump important geometric parameter, and submersible axial flow pump performance parameter is equal in actual motion There is different degrees of decline, original impeller outer diameter calculation formula need to be modified, calculation formula is as follows, but nD values analyze water pump The contact of energy and cavitation characteristics, it is necessary to assure pump nD values are no more than a zone of reasonableness, the specific value of different specific speed referring to Accompanying drawing 4.
In formula：
D-impeller outer diameter, unit：Rice；
dh/ D-hub ratio；
Q-flow, unit：Cubic meter/per hour；
N-rotating speed, unit：Rev/min；
3rd, number of blade z is chosen by specific speed ns, and with reference to foreign outstanding water model, value is with reference to following table.Cascade solidity l/t It is the important parameter for influenceing the efficiency of pump and cavitation performance, consistency crosses ambassador's friction loss increase, and efficiency reduces, and consistency is too small Then need accordingly to increase camber and blade angle, increase cavitation is dangerous, suitably increases leaf in the case where taking into account efficiency and cavitation The cascade solidity of root, ensure the energy conversion with outer rim aerofoil profile same degree as far as possible, balanced blade exit lift, reduce radially Flowing, efficiency is improved, specific value refers to following formula, and wherein K is correction factor, and value is referring to accompanying drawing 5.
In formula：
L/t-cascade solidity；
R-stream interface radius, unit：Rice；
H-lift, unit：Rice；
N-rotating speed, unit：Rev/min；
R-impeller radius, unit：Rice；
K-correction factor；
4th, it is non-interference based on blade infinite span and each stream interface layer during blade design it is assumed that using more meeting diving axle The change circular rector of the actual fluidised form of mixed-flow pump becomes axis plane velocity design method, selects rational blade ring quantitative change law, makes each stream Face ring amount radially changes according to certain rules, makes blade load at root and outer rim smaller, and middle stream interface blade load is larger, Swirl distribution COEFFICIENT KjRecommend to be calculated with following following formula：
Kj=0.7684.618 (r/R) -2.848 (r/R)2, in formula：
Kj- swirl distribution coefficient；
R-stream interface radius, rice；
R-impeller radius, rice；
5th, blade sweepback angleBigger, solid volume fraction is smaller on blade pressure surface, and solid phase Radial Flow is brighter It is aobvious, the abrasion of blade pressure surface is greatly reduced, improves service life of the aial flow impeller in sewage disposal and reliable Property, but blade angle of sweepBigger, lift and efficiency are lower, therefore blade sweepback angleIn 15 °~30 ° ranges, occurrence It can be calculated according to following formula：
In formula：
- angle of sweep, unit：Degree；
r1- import and wheel hub cross streams radius surface, unit：Rice；
r2- import and wheel rim cross streams radius surface, unit：Rice；
β-isogonism angle changing, unit：Degree；
6th, NACA series aerofoil sections are chosen in the recommendation of sweepback impeller aerofoil profile, in the case where cavitation performance is up to standard using larger Lift-drag ratio, and from and required lift coefficient CyThe aerofoil profile of matching is thickeied, lift coefficient CyIt is calculated as follows.Actually set Aerofoil profile recommends NACA16, its lift coefficient C in meteryIt is worth for 0.4~0.6, is closer to axial-flow pump actual condition.
7th, aerofoil profile stacks is stacked using leading edge, is changed by equiangular helical spiral rule, Controlling outline curve such as following formula, blade axial plane figure Antecurvature design is carried out using simple Bezier, antecurvature angle is generally 8 °~14 °, can find optimal angle by optimization：
R=r1·eθtanβ, in formula：
r1- import and wheel hub cross streams radius surface, unit：Rice；
β-isogonism angle changing, unit：Degree；
R-stream interface radius, unit：Rice；
The cornerite of θ-stream interface and inlet side intersection point, unit：Degree；
The specific implementation process of the inventive method is provided below, design is applied to the submerged axial-flow impeller of pump of conveying sewage Step is as follows：
1st, impeller outer diameter D and rotating speed n is axial-flow pump important geometric parameter, and nD values analyze pump Energy and cavitation characteristics Contact, it is necessary to assure pump nD values are no more than a zone of reasonableness.
2nd, the shapes and sizes of wheel hub affect the fluidised form before fluid contact blade, also just influence the efficiency of impeller indirectly, Boss shape of the present invention uses cone hub, and contour line coordinates gate vane channel shape, makes flowing much smoother；Due to submersible axial flow pump Lower flange is larger, and stator angle of flare is too big, and efficiency, wheel hub d are improved to reduce divergence losshIt is appropriate to take greatly, can be in dry type axle Increase 5% on the basis of stream pump impeller hub；
3rd, the number of blade refers to foreign outstanding water model, and 1000 specific speeds once take 4, more than 1000 specific speeds take 3.Leaf Piece design when it is non-interference based on blade infinite span and each stream interface layer it is assumed that using more meet diving the actual stream of axle mixed-flow pump The change circular rector of state becomes axis plane velocity design method, selects rational blade ring quantitative change law, makes each stream interface circular rector by certain Rule radially change, make blade load at root and outer rim smaller, middle stream interface blade load is larger；
4th, cascade solidity is larger to submersible axial flow pump performance impact, and consistency crosses ambassador's friction loss increase, efficiency drop Low, consistency is too small, needs accordingly to increase camber and blade angle, and increase cavitation is dangerous.Taking into account the situation of efficiency and cavitation The cascade solidity of lower appropriate increase blade root, ensures the energy conversion with outer rim aerofoil profile same degree, balanced blade exit as far as possible Lift, reduce Radial Flow, improve efficiency；
5th, blade sweepback angle is bigger, and solid volume fraction is smaller on blade pressure surface, and solid phase Radial Flow is more obvious, The abrasion of blade pressure surface is greatly reduced, improves service life and operational reliability of the aial flow impeller in sewage disposal, But blade angle of sweep is bigger, lift and efficiency are lower, therefore blade sweepback angle is selected according to actual condition；
6th, aerofoil profile stacks is stacked using leading edge, by change of variable angle spiral rule is waited, using larger lift-drag ratio, and is selected The aerofoil profile matched with required lift coefficient is thickeied, and blade axial plane figure carries out antecurvature design using Bezier, can pass through Optimum point is found in optimization.
The present invention is designed using the above method, and the impeller pattern drawn can well adapt to the structure of submersible axial flow pump And application scenario, make submersible axial flow pump more efficient, anti-clogging and antiwind ability are stronger, reduce the operating cost of pump, reduce Fault rate, enables the submersible axial flow pump long-term safety reliably operate.

Claims (1)

  1. A kind of 1. design method of high-efficiency helical sweepback axial wheel hydraulic model, it is characterised in that comprise the following steps,
    1), impeller shape uses the structure type of swept-back, and blade sweepback angle is stacked and adopted in 15 °~30 ° ranges, aerofoil profile Stacked with leading edge, blade inlet edge is by change of variable angle spiral rule is waited, and blade is by the rule design of change swirl distribution；
    R=r1geθtanβ；In formula：
    - angle of sweep, degree；
    r1- import and wheel hub cross streams radius surface, unit：Rice；
    r2- import and wheel rim cross streams radius surface, unit：Rice；
    β-isogonism angle changing, unit：Degree；
    R-stream interface radius, unit：Rice；
    The cornerite of θ-stream interface and inlet side intersection point, unit：Degree；
    2) impeller outer diameter, is corrected：Boss shape is designed as taper, outline is adapted with stator, is ensureing the premise of cavitation Under impeller outer diameter is modified, using increase hub ratio dh/ D modes, to meet that performance is joined in submersible axial flow pump actual motion Number, i.e., according to hub ratio d corresponding to specific speed nsh/ D values, and ensure that nD values scope is corresponding with specific speed ns value ranges：
    In formula：
    D-impeller outer diameter, rice；
    dh/ D-hub ratio；
    Q-flow, cubic meter is per hour；
    N-rotating speed, rpm；
    2), impeller hydraulic model chooses the number of blade：On the premise of efficiency and cavitation is taken into account, rational cascade solidity is selected, Increase root aerofoil profile length, reduce wheel rim aerofoil profile length, the energy conversion of balanced each stream interface, ensure number of blade z according to specific speed Ns is chosen；
    In formula：
    L/t-cascade solidity；
    R-stream interface radius, unit：Rice；
    H-lift, unit：Rice；
    N-rotating speed, unit：Rev/min；
    R-impeller radius, unit：Rice；
    K-correction factor；
    3), blade designs by swirl distribution rule is become：The total circular rector of blade is evenly distributed on each blade, then is divided by circular rector is become Circular rector is assigned on each stream interface by cloth rule, each stream interface circular rector is radially changed according to certain rules, is made root and outer rim Place's blade load is small, and middle stream interface blade load is big；
    Kj=0.768g4.618 (r/R) -2.848 (r/R)2, in formula：
    Kj- swirl distribution coefficient；
    R-stream interface radius, unit：Rice；
    R-impeller radius, unit：Rice；
    4) lift-drag ratio, is designed using lift force method, and thickeied from the aerofoil profile to match with required lift coefficient, from NACA systems Row aerofoil profile sheet simultaneously carries out antecurvature optimization to impeller axis projection, and antecurvature angle is generally 8 °~14 °, finds out optimal corner.
CN201710948115.7A 2017-10-12 2017-10-12 A kind of design method of high-efficiency helical sweepback axial wheel hydraulic model Active CN107762966B (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108302062A (en) * 2018-03-15 2018-07-20 中交疏浚技术装备国家工程研究中心有限公司 Dredging pump impeller structure and its design method suitable for different soil properties
CN111677689A (en) * 2020-06-23 2020-09-18 东方电气集团东方电机有限公司 Design method of vibration and noise reduction mixed flow pump or axial flow pump
CN116428197A (en) * 2023-05-17 2023-07-14 江苏大学 Design method of emergency flood control water pump and high-speed cavitation-resistant impeller

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US4063849A (en) * 1975-02-12 1977-12-20 Modianos Doan D Non-clogging, centrifugal, coaxial discharge pump
US20050281683A1 (en) * 2004-06-22 2005-12-22 Baker Hughes Incorporated Gas separator fluid crossover for well pump
CN101245711A (en) * 2007-02-16 2008-08-20 任明琪 Axial flow impeller machine design method and blade
CN102400946A (en) * 2011-11-18 2012-04-04 江苏国泉泵业制造有限公司 Method for designing single-screw axial-flow pump impeller
CN202431593U (en) * 2011-11-03 2012-09-12 江苏国泉泵业制造有限公司 Axial-flow pump impeller adopting spiral blades
CN104389810A (en) * 2014-09-19 2015-03-04 江苏大学 Multi-condition design method for multi-phase mixed transportation axial flow pump impeller
CN105673516A (en) * 2016-03-21 2016-06-15 上海奥一泵业制造有限公司 Portable hydraulically-driven submersible axial-flow pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4063849A (en) * 1975-02-12 1977-12-20 Modianos Doan D Non-clogging, centrifugal, coaxial discharge pump
US20050281683A1 (en) * 2004-06-22 2005-12-22 Baker Hughes Incorporated Gas separator fluid crossover for well pump
CN101245711A (en) * 2007-02-16 2008-08-20 任明琪 Axial flow impeller machine design method and blade
CN202431593U (en) * 2011-11-03 2012-09-12 江苏国泉泵业制造有限公司 Axial-flow pump impeller adopting spiral blades
CN102400946A (en) * 2011-11-18 2012-04-04 江苏国泉泵业制造有限公司 Method for designing single-screw axial-flow pump impeller
CN104389810A (en) * 2014-09-19 2015-03-04 江苏大学 Multi-condition design method for multi-phase mixed transportation axial flow pump impeller
CN105673516A (en) * 2016-03-21 2016-06-15 上海奥一泵业制造有限公司 Portable hydraulically-driven submersible axial-flow pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108302062A (en) * 2018-03-15 2018-07-20 中交疏浚技术装备国家工程研究中心有限公司 Dredging pump impeller structure and its design method suitable for different soil properties
CN111677689A (en) * 2020-06-23 2020-09-18 东方电气集团东方电机有限公司 Design method of vibration and noise reduction mixed flow pump or axial flow pump
CN116428197A (en) * 2023-05-17 2023-07-14 江苏大学 Design method of emergency flood control water pump and high-speed cavitation-resistant impeller
CN116428197B (en) * 2023-05-17 2024-06-07 江苏大学 Design method of emergency flood control water pump and high-speed cavitation-resistant impeller

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