CN103452912A - Multi-working-condition design method for guide vanes of axial flow pumps - Google Patents
Multi-working-condition design method for guide vanes of axial flow pumps Download PDFInfo
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- CN103452912A CN103452912A CN 201310425580 CN201310425580A CN103452912A CN 103452912 A CN103452912 A CN 103452912A CN 201310425580 CN201310425580 CN 201310425580 CN 201310425580 A CN201310425580 A CN 201310425580A CN 103452912 A CN103452912 A CN 103452912A
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Abstract
The invention provides a design method, meeting requirements on multiple working condition points, for guide vanes of axial flow pumps. The design method is characterized in that during designing of the guide vanes of the axial flow pumps, geometrical parameters of the guide vanes and performance parameters of different working condition points are linked together, and actual operation performance curves of the axial flow pumps are enabled to be identical to required performance curves, so that effect that design performance curves of the pumps are coincident with the required performance curves is achieved. The geometrical parameters of the guide vanes designed by the method can be adjusted to achieve the objective that performance of the axial flow pumps can meet the requirements on the multiple working condition points. Consistency of the actual operation performance curves of the axial flow pumps and the required performance curves can be guaranteed, and the design method is especially suitable for designing of the guide vanes, with strict requirements on the multiple working condition points, of the axial flow pumps.
Description
Technical field
The present invention relates to a kind of axial-flow pump stator multi-operating mode design method, both can axial-flow pump than low-specific-speed operating condition design stator the time use, also can when the higher specific speed operating condition design stator of axial-flow pump, use, be particularly useful for the situation strict to axial-flow pump multi-operating mode point performance parameter and use.
Background technique
Axial-flow pump belongs to low lift, high-capacity pump, and performance range roughly is, lift 1 ~ 12m, flow 0.3-65m
3/ s, specific speed 500-1600.The design method of stator can be used the lift method, integration method and streamline method, but generally all adopt the streamline method.Past axial-flow pump design mainly is confined to single operating point, and still, along with the needs of production development, occasion need to be at axial-flow pump in different operating point work sometimes, and different flow points needs the lift of appointment.Therefore, the multi-operating mode design method becomes the inevitable choice of axial-flow pump stator design.
Summary of the invention
In order to overcome the deficiency of existing axial-flow pump stator design method, the invention provides a kind of multi-operating mode design method of new axial-flow pump stator, the quantity of multi-operating mode point can be between 2 ~ 6.Adopt the stator of the present invention's design to be regulated the geometric parameter of stator, reach the predicted performance curves and the effect that the performance curve of requirement overlaps of axial-flow pump, meet the purpose of a plurality of operating point requirements.Patent of the present invention can guarantee the actual motion performance curve and the conformity that requires performance curve of axial-flow pump, is specially adapted to the design of the strict axial flow stator of a plurality of operating point performance requirements.Utilize following relation to determine the main geometric parameters of stator, mainly comprise: optimum efficiency operating point flow
q bEP , optimum efficiency operating point lift
h bEP , optimum efficiency operating point specific speed
n sBEP , the
ithe flow of operating point
q i , of traditional design method
ithe lift of operating point
h i ', wheel speed
n, the
ithe difference that requires lift and traditional design lift of operating point
h i , the impeller hub diameter
d h0 , the stator hub diameter
d h , the vane inlet diameter
d 3, the stator angle of flare
θ, guide vane height
h, each stream interface vane inlet laying angle
α 3
k .
Realize that the design method that above-mentioned purpose adopts is:
（2）
（6）
（8）
In formula:
q bEP ---optimum efficiency operating point flow, cube meter per second;
h bEP ---optimum efficiency operating point lift, rice;
n sBEP ---optimum efficiency operating point specific speed;
q i ---the
ithe flow of operating point, cube meter per second;
h i '---of traditional design method
ithe lift of operating point, rice;
h i ---the
ithe difference that requires lift and traditional design lift of operating point, rice;
n---wheel speed, rev/min;
d h0 ---impeller hub diameter, rice;
d h ---stator hub diameter, rice;
d 3---vane inlet diameter, rice;
θ---stator angle of flare, degree;
h---guide vane height, rice;
α 3
k ---each stream interface vane inlet laying angle (
k=1 ..., 5), degree.
Stator is divided into 5 stream interfaces when the Hydraulic Design, so the vane inlet laying angle
α 3
k 5 values are arranged.
In above relation, the parameters such as the number of blade and the outlet angle of attack are not claimed, therefore, as long as under the prerequisite that does not affect casting and processing technology, during design, can arbitrarily control as required these parameters.
The profile thickness Changing Pattern is according to the circular arc aerofoil profile, and this structure processing is simple, and facts have proved that efficiency is not defeated in other aerofoil profile.During thickening, the molded line of take is thickeied to the back side as working surface.
The invention has the beneficial effects as follows: stator meets the multi-operating mode service condition, has improved axial flow lift of pump and efficiency, has widened the scope in efficient district, and has improved the operational reliability of axial-flow pump.
The present invention is on probation through the user, and reaction effect is good, can effectively reduce investment outlay, energy saving.
The accompanying drawing explanation
Fig. 1 is the guide vane structure schematic diagram of one embodiment of the invention.
Fig. 2 is same embodiment's aerofoil profile unfolded drawing.
In figure: 1. stator hub diameter
d h , 2. vane inlet diameter
d 3, 3.1/2 stator angle of flare
θ/ 2,4. guide vane height
h, 5. each stream interface vane inlet laying angle
α 3
k .
Embodiment
Fig. 1 and Fig. 2 have determined this embodiment's stator shape jointly.The present invention adjusts the stator hub diameter by following relation
d h (1), vane inlet diameter
d 3(2), 1/2 stator angle of flare
θ/ 2(3), guide vane height
hand each stream interface vane inlet laying angle (4)
α 3
k (5), make this embodiment's axial-flow pump performance meet the flow of optimum efficiency operating mode
q bEP , the optimum efficiency operating mode lift
h bEP ,
ithe flow of operating point
q i ,
ithe lift of operating point
h i , wheel speed
nrequirement.
In formula:
q bEP ---optimum efficiency operating point flow, cube meter per second;
h bEP ---optimum efficiency operating point lift, rice;
n sBEP ---optimum efficiency operating point specific speed;
q i ---the
ithe flow of operating point, cube meter per second;
h i '---of traditional design method
ithe lift of operating point, rice;
h i ---the
ithe difference that requires lift and traditional design lift of operating point, rice;
n---wheel speed, rev/min;
d h0 ---impeller hub diameter, rice;
d h ---stator hub diameter, rice;
d 3---vane inlet diameter, rice;
θ---stator angle of flare, degree;
h---guide vane height, rice;
α 3
k ---each stream interface vane inlet laying angle (
k=1 ..., 5), degree.
Stator is divided into 5 stream interfaces when the Hydraulic Design, so the vane inlet laying angle
α 3
k 5 values are arranged.
To parameters such as the number of blade and the outlet angles of attack, as long as under the prerequisite that does not affect casting and processing technology, can calculate according to conventional method.
The profile thickness Changing Pattern is according to the circular arc aerofoil profile, and this structure processing is simple, and facts have proved that efficiency is not defeated in other aerofoil profile.During thickening, the molded line of take is thickeied to the back side as working surface.
In Fig. 2, the wheel hub rear extends naturally, makes flow field more stable, is convenient to processing and casting simultaneously.
Claims (5)
1. an axial-flow pump stator multi-operating mode design method, its is according to the flow to axial-flow pump optimum efficiency operating point
q bEP , the optimum efficiency operating point lift
h bEP , wheel speed
n, the optimum efficiency operating point specific speed
n sBEP ,
iindividual operating point flow
q i ,
iindividual operating point lift
h i 'requirement, design the geometric parameter of axial-flow pump stator, it is characterized in that: the geometric parameter of stator is linked together from the performance parameter of different operating points, make the actual motion performance curve of axial-flow pump consistent with required performance curve, between stator main geometric parameters and different operating point performance parameters, be applicable to the relation of following equation:
In formula:
q bEP ---optimum efficiency operating point flow, cube meter per second;
h bEP ---optimum efficiency operating point lift, rice;
n sBEP ---optimum efficiency operating point specific speed;
q i ---the
ithe flow of operating point, cube meter per second;
h i '---of traditional design method
ithe lift of operating point, rice;
h i ---the
ithe difference that requires lift and traditional design lift of operating point, rice;
n---wheel speed, rev/min;
d h0 ---impeller hub diameter, rice;
d h ---stator hub diameter, rice;
d 3---vane inlet diameter, rice;
θ---stator angle of flare, degree;
h---guide vane height, rice;
α 3
k ---each stream interface vane inlet laying angle (
k=1 ..., 5), degree.
2. axial-flow pump stator according to claim 1 is divided into 5 stream interfaces when the Hydraulic Design, so the vane inlet laying angle
α 3
k 5 values are arranged.
3. the profile thickness Changing Pattern is according to the circular arc aerofoil profile.
4. when thickening, the molded line of take is thickeied to the back side as working surface.
5.., to parameters such as the number of blade and the outlet angles of attack, as long as under the prerequisite that does not affect casting and processing technology, can calculate according to conventional method.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201310425580 CN103452912A (en) | 2013-09-18 | 2013-09-18 | Multi-working-condition design method for guide vanes of axial flow pumps |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201310425580 CN103452912A (en) | 2013-09-18 | 2013-09-18 | Multi-working-condition design method for guide vanes of axial flow pumps |
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| Publication Number | Publication Date |
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| CN103452912A true CN103452912A (en) | 2013-12-18 |
Family
ID=49735641
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103883556A (en) * | 2014-04-04 | 2014-06-25 | 江苏国泉泵业制造有限公司 | Designing method of axial flow rotation wheel |
| CN103994095A (en) * | 2014-04-29 | 2014-08-20 | 江苏大学 | Designing method of multiphase mixed transportation axial flow pump impeller |
| CN105179303A (en) * | 2015-10-24 | 2015-12-23 | 扬州大学 | Axial flow pump impeller all-operating-condition design method |
| CN105485057A (en) * | 2015-12-25 | 2016-04-13 | 江苏大学 | Hydraulic design method of radial guide blade of diagonal flow pump |
| CN105626574A (en) * | 2015-12-25 | 2016-06-01 | 江苏大学 | Hydraulic design method of high-lift axial flow pump impeller |
| CN105927590A (en) * | 2016-07-01 | 2016-09-07 | 长安益阳发电有限公司 | Axial-flow type movable blade adjustable draught fan |
| CN112901502A (en) * | 2021-03-16 | 2021-06-04 | 兰州理工大学 | Method for setting mounting angle of inlet of spatial guide vane of axial flow pump |
-
2013
- 2013-09-18 CN CN 201310425580 patent/CN103452912A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103883556A (en) * | 2014-04-04 | 2014-06-25 | 江苏国泉泵业制造有限公司 | Designing method of axial flow rotation wheel |
| CN103883556B (en) * | 2014-04-04 | 2016-04-13 | 江苏国泉泵业制造有限公司 | A kind of design method of axial flow runner |
| CN103994095A (en) * | 2014-04-29 | 2014-08-20 | 江苏大学 | Designing method of multiphase mixed transportation axial flow pump impeller |
| CN105179303A (en) * | 2015-10-24 | 2015-12-23 | 扬州大学 | Axial flow pump impeller all-operating-condition design method |
| CN105485057A (en) * | 2015-12-25 | 2016-04-13 | 江苏大学 | Hydraulic design method of radial guide blade of diagonal flow pump |
| CN105626574A (en) * | 2015-12-25 | 2016-06-01 | 江苏大学 | Hydraulic design method of high-lift axial flow pump impeller |
| CN105626574B (en) * | 2015-12-25 | 2018-01-30 | 江苏大学 | A kind of high-lift axial-flow pump impeller Hydraulic Design Method |
| CN105485057B (en) * | 2015-12-25 | 2019-02-22 | 江苏源泉泵业股份有限公司 | A kind of Hydraulic Design Method of diagonal pumps radial vane |
| CN105927590A (en) * | 2016-07-01 | 2016-09-07 | 长安益阳发电有限公司 | Axial-flow type movable blade adjustable draught fan |
| CN112901502A (en) * | 2021-03-16 | 2021-06-04 | 兰州理工大学 | Method for setting mounting angle of inlet of spatial guide vane of axial flow pump |
| CN112901502B (en) * | 2021-03-16 | 2021-11-26 | 兰州理工大学 | Method for setting mounting angle of inlet of spatial guide vane of axial flow pump |
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Application publication date: 20131218 |
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| WD01 | Invention patent application deemed withdrawn after publication |