CN104912851A - Channel type guide valve designing method - Google Patents
Channel type guide valve designing method Download PDFInfo
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- CN104912851A CN104912851A CN201510382897.3A CN201510382897A CN104912851A CN 104912851 A CN104912851 A CN 104912851A CN 201510382897 A CN201510382897 A CN 201510382897A CN 104912851 A CN104912851 A CN 104912851A
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- formula
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- width
- stator
- impeller
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Abstract
The invention discloses a channel type guide valve designing method and is mainly applied to solving the problem of low working efficiency of a pump, caused by ignorance of importance of mismatch between a conventional channel type guide valve and an impeller when the conventional channel type guide valve is designed. For the purpose of eliminating the defect, the method, based on the design of the conventional channel type guide valve, determines an inlet width b3 of the guide valve, a throat width a3 of the guide valve and a guide valve number z by use of Anderson' area ratio principle. According to the invention, on the basis of the design of the conventional channel type guide valve, by use of the Anderson' area ratio principle, the inlet width b3 of the guide valve, the throat width a3 of the guide valve and the guide valve number z are determined, and the match between the impeller and the guide valve is taken into consideration, such that the waterpower loss is reduced, the efficiency of the pump is improved, and the purposes of energy conservation and consumption reduction are realized.
Description
Technical field
The present invention relates to multistage centrifugal pump field, particularly a kind of flow channel type guide blade design method.
Background technique
Along with the development at a high speed of China's economy and the minimizing day by day of global energy, save energy and reduce the cost and become global common focus problem.Pump series products is in the one of fluid machinery series products, and domestic is in great demand, and every annual electricity generating capacity 20%--25% is wasted on pump series products.And multistage centrifugal pump is as common a kind of product.Be widely used in the fields such as industrial production, mine, urban water supply and sewerage, stator is the important component part in each element of multistage pump, is the keypoint part of loss in efficiency in pump flow passage components.The radial stator of many application and flow channel type guide blade in multistage pump, radial stator is simple because of its structure, casts, processing technology is convenient and be widely used.Flow channel type guide blade is made up of several independently closed flow, has good hydraulic characteristic, but its casting, processing technology is more loaded down with trivial details is not widely used.But along with the development of current manufacturing technology and 3-D technology, flow channel type guide blade is applied in some important multistage pumps gradually.
Design method and the radial stator of flow channel type guide blade are similar.Traditional design method first determines stator axial plane entrance width, stator throat width is estimated by stator axial plane entrance width, the number of blade is obtained again by stator throat width calculation, result of calculation is rounded up and obtains gate vane channel number, this forward design method considers that the matching of impeller and stator is less, and gate vane channel number major parameter value degrees of freedom is comparatively large, be limited to statistics and personal factor, designing quality can not ensure.Which results in the changeover portion loss of fluid between impeller and flow channel type guide blade comparatively large, the efficiency of pump is declined to some extent, does not meet the requirement that pump is energy-conservation.
Summary of the invention
For the deficiencies in the prior art, object of the present invention is intended to provide a kind of flow channel type guide blade design method, causes to reduce because impeller and stator do not mate the problem that pump energy consumption increases, and improves the efficiency of pump, meets the requirement that pump is energy-conservation.
For achieving the above object, the present invention adopts following technological scheme:
A kind of flow channel type guide blade design method, comprises the following steps:
Step one, try to achieve vane inlet width b by formula (1)
3,
b
3=b
2+(2~5)mm (1)
In formula, b
3for vane inlet width, b
2for impeller outlet width;
Step 2, try to achieve vane inlet laying angle α by formula (2)
3,
tgα
3=(1.1~1.3)tgα
2(2)
In formula, α
3for vane inlet laying angle, α
2for the absolute flow angle of impeller outlet;
Step 3, try to achieve stator base circle diameter (BCD) D by formula (3)
3,
D
3=(1.02~1.05)D
2(3)
In formula, D
2for impeller diameter, D
3for stator base circle diameter (BCD);
Step 4, blade inlet thickness δ
3value is 3 ~ 7mm;
Step 5, by vane inlet laying angle α
3, blade inlet thickness δ
3with stator Base radius R
3bring formula (4) into, obtain number of blade z and throat width a
3relation,
In formula, z is the number of blade, α
3for vane inlet laying angle, a
3for stator throat width, δ
3for blade inlet thickness, R
3for stator Base radius;
Step 6, according to Anderson area ratio principle, the area ratio formula of flow channel type guide blade multistage pump is:
Y=F
2/F
d(5)
In formula, Y is area ratio coefficient, F
2for the discharge area between impeller blade, F
dfor stator throat opening area;
Discharge area F between step 7, impeller blade
2can be calculated by formula (6)
F
2=πD
2b
2tgβ
2(6)
In formula, D
2for impeller diameter, b
2for impeller outlet width, β
2for blade exit laying angle;
Step 8, determine area ratio coefficient Y by formula (7),
Y=1/(0.036849+0.002310n
s) (7)
In formula, n
sfor the specific speed of pump;
Step 9, because of the known F of flow channel type guide blade throat opening area formula
dwith a
3with the relation of z,
F
d=za
3b
3(8)
In formula, z is the number of blade, a
3for stator throat width, b
3for vane inlet width;
Step 10, the F that formula (6) is determined
2and the area ratio coefficient Y that formula (7) is determined substitutes in formula (5), thus try to achieve F
d, then the F that will try to achieve
dsubstitute into formula (8), obtain a
3with the relation of z, owing to also obtaining number of blade z and throat width a in formula (4)
3relation, obtain two unknown numbers according to formula (4) and formula (9) two solution of equations and draw stator throat width a
3with number of blade z, after trying to achieve number of blade z, be taken as integer, then substitute in formula (4) and determine a
3numerical value, finally obtain b
3, z and a
3parameters combination.
Beneficial effect of the present invention is:
Compared to prior art, the present invention is on the basis that conventional flow field formula stator designs, and the area ratio principle of application Anderson, to determine vane inlet width b
3, stator throat width a
3with stator number z, consider the matching of impeller and stator, which reduce hydraulic loss, improve the efficiency of pump, reach energy-saving and cost-reducing object.
Accompanying drawing explanation
Fig. 1 is the structural representation of stator of the present invention;
Fig. 2 is the schematic side view of Fig. 1;
Fig. 3 is the specific speed n of area ratio coefficient Y and pump
sloose point and line graph.
Embodiment
Below, by reference to the accompanying drawings and embodiment, the present invention is described further:
As shown in Figure 1 to Figure 3, flow channel type guide blade design method of the present invention is mainly used in and ignores when solving the design of existing flow channel type guide blade and the unmatched significance of impeller and cause the problem that pump work efficiency is not high.For this reason, on the basis of conventional flow field formula stator design, the area ratio principle of application Anderson, to determine vane inlet width b
3, stator throat width a
3with stator number z.Anderson area ratio principle thinks that impeller outlet area of passage and pump throat area ratio are the main determining factors of the performance parameters such as centrifugal pump lift, flow, air horsepower.The present invention design stator according to the known parameters for the pump housing and blade wheel structure.
This flow channel type guide blade design method comprises the following steps:
Step one, consider vane inlet width b
3with impeller outlet width b
2mate, so b
3span very little, try to achieve vane inlet width b by formula (1)
3,
b
3=b
2+(2~5)mm (1)
In formula, b
3for vane inlet width, b
2impeller outlet width (b
2being the parameter of impeller, is given value);
Step 2, try to achieve vane inlet laying angle α by formula (2)
3,
tgα
3=(1.1~1.3)tgα
2(2)
In formula, α
3for vane inlet laying angle, α
2for the absolute flow angle (α of impeller outlet
2being the parameter of impeller, is given value);
Step 3, try to achieve stator base circle diameter (BCD) D by formula (3)
3,
D
3=(1.02~1.05)D
2(3)
In formula, D
2for impeller diameter (D
2being the parameter of impeller, is given value), D
3for stator base circle diameter (BCD);
Step 4, blade inlet thickness δ
3value is 3 ~ 7mm;
Step 5, by vane inlet laying angle α
3, blade inlet thickness δ
3with stator Base radius R
3bring formula (4) into, obtain number of blade z and throat width a
3relation,
In formula, z is the number of blade, α
3for vane inlet laying angle, a
3for stator throat width, δ
3for blade inlet thickness, R
3for stator Base radius is (due to D
3tried to achieve by formula (2), R
3=D
3/ 2 is also given value);
Step 6, according to Anderson area ratio principle, the area ratio formula of flow channel type guide blade multistage pump is:
Y=F
2/ F
d=(discharge area between impeller blade)/(stator throat opening area) (5)
In formula, Y is area ratio coefficient, F
2for the discharge area between impeller blade, F
dfor stator throat opening area;
Particularly, when Anderson area ratio principle is applied to Ordinary Centrifugal Pumps, formula Y=F can be obtained
2/ F
1, in formula, Y is area ratio coefficient, F
2for the discharge area between impeller blade, F
1for pump throat area; When Anderson area ratio principle is applied to flow channel type guide blade multistage pump, formula Y=F can be obtained
2/ F
d.
Discharge area F between step 7, impeller blade
2can be calculated by formula (6)
F
2=πD
2b
2tgβ
2(6)
In formula, D
2for impeller diameter, b
2for impeller outlet width, β
2for blade exit laying angle, D
2, b
2, β
2are all parameters of impeller blade, are given value;
Step 8, determine area ratio coefficient Y by formula (7),
Y=1/(0.036849+0.002310n
s) (7)
In formula, n
sfor the specific speed (n of pump
sbeing the parameter of pump, is given value);
Step 9, because of the known F of flow channel type guide blade throat opening area formula
dwith a
3with the relation of z,
F
d=za
3b
3(8)
In formula, z is the number of blade, a
3for stator throat width, b
3for vane inlet width, (b
3tried to achieve by formula (1));
Step 10, the F that formula (6) is determined
2and the area ratio coefficient Y that formula (7) is determined substitutes in formula (5), thus try to achieve F
d, then the F that will try to achieve
dsubstitute into formula (8), obtain a
3with the relation of z, owing to also obtaining number of blade z and throat width a in formula (4)
3relation, obtain two unknown numbers according to formula (4) and formula (9) two solution of equations and draw stator throat width a
3with number of blade z, after trying to achieve number of blade z, be taken as integer, then substitute in formula (4) and determine a
3numerical value, so just obtain best parameter group (b
3, z, a
3).
The present invention is on the basis that conventional flow field formula stator designs, and the area ratio principle of application Anderson, to determine vane inlet width b
3, stator throat width a
3with stator number z, consider the matching of impeller and stator, which reduce hydraulic loss, improve the efficiency of pump, reach energy-saving and cost-reducing object.
Further, as shown in Figure 3, in step 9, by the specific speed n of the lower 3 kinds of pattern pumps of sorting-out in statistics different specific speed
swith loose some graph of a relation of the inverse (1/Y) of area ratio coefficient Y, then give n by linear regression and linear fit
swith the manual line of loose point of 1/Y and the regression equation of Y, the regression equation of Y is formula (8).
To one skilled in the art, according to technological scheme described above and design, other various corresponding change and deformation can be made, and all these change and deformation all should belong within the protection domain of the claims in the present invention.
Claims (1)
1. a flow channel type guide blade design method, is characterized in that, comprises the following steps:
Step one, try to achieve vane inlet width b by formula (1)
3,
b
3=b
2+(2~5)mm (1)
In formula, b
3for vane inlet width, b
2for impeller outlet width;
Step 2, try to achieve vane inlet laying angle α by formula (2)
3,
tgα
3=(1.1~1.3)tgα
2(2)
In formula, α
3for vane inlet laying angle, α
2for the absolute flow angle of impeller outlet;
Step 3, try to achieve stator base circle diameter (BCD) D by formula (3)
3,
D
3=(1.02~1.05)D
2(3)
In formula, D
2for impeller diameter, D
3for stator base circle diameter (BCD);
Step 4, blade inlet thickness δ
3value is 3 ~ 7mm;
Step 5, by vane inlet laying angle α
3, blade inlet thickness δ
3with stator Base radius R
3bring formula (4) into, obtain number of blade z and throat width a
3relation,
In formula, z is the number of blade, α
3for vane inlet laying angle, a
3for stator throat width, δ
3for blade inlet thickness, R
3for stator Base radius;
Step 6, according to Anderson area ratio principle, the area ratio formula of flow channel type guide blade multistage pump is:
Y=F
2/F
d(5)
In formula, Y is area ratio coefficient, F
2for the discharge area between impeller blade, F
dfor stator throat opening area;
Discharge area F between step 7, impeller blade
2can be calculated by formula (6)
F
2=πD
2b
2tgβ
2(6)
In formula, D
2for impeller diameter, b
2for impeller outlet width, β
2for blade exit laying angle;
Step 8, determine area ratio coefficient Y by formula (7),
Y=1/(0.036849+0.002310n
s) (7)
In formula, n
sfor the specific speed of pump;
Step 9, because of the known F of flow channel type guide blade throat opening area formula
dwith a
3with the relation of z,
F
d=za
3b
3(8)
In formula, z is the number of blade, a
3for stator throat width, b
3for vane inlet width;
Step 10, the F that formula (6) is determined
2and the area ratio coefficient Y that formula (7) is determined substitutes in formula (5), thus try to achieve F
d, then the F that will try to achieve
dsubstitute into formula (8), obtain a
3with the relation of z, owing to also obtaining number of blade z and throat width a in formula (4)
3relation, obtain two unknown numbers according to formula (4) and formula (9) two solution of equations and draw stator throat width a
3with number of blade z, after trying to achieve number of blade z, be taken as integer, then substitute in formula (4) and determine a
3numerical value, finally obtain b
3, z and a
3parameters combination.
Priority Applications (1)
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CN201510382897.3A CN104912851A (en) | 2015-06-29 | 2015-06-29 | Channel type guide valve designing method |
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---|---|---|---|
CN201510382897.3A CN104912851A (en) | 2015-06-29 | 2015-06-29 | Channel type guide valve designing method |
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Publication Number | Publication Date |
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CN104912851A true CN104912851A (en) | 2015-09-16 |
Family
ID=54082211
Family Applications (1)
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CN201510382897.3A Pending CN104912851A (en) | 2015-06-29 | 2015-06-29 | Channel type guide valve designing method |
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CN (1) | CN104912851A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105673554A (en) * | 2016-01-07 | 2016-06-15 | 江苏大学 | Reversed spiral line type guide vane of nuclear main pump and design method of reversed spiral line type guide vane |
CN107299915A (en) * | 2016-12-07 | 2017-10-27 | 江苏国泉泵业制造有限公司 | A kind of Hydraulic Design Method of mining centrifugal pump stator |
KR20220160847A (en) * | 2021-05-28 | 2022-12-06 | 두산에너빌리티 주식회사 | Design method for flowpath of axial compressor of gas turbine |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH08260561A (en) * | 1995-03-27 | 1996-10-08 | Kubota Corp | Suction water tank for pump |
JPH0921400A (en) * | 1995-07-05 | 1997-01-21 | Hitachi Ltd | Diffuser with vane |
EP1219838A2 (en) * | 2000-11-14 | 2002-07-03 | CALPEDA S.p.A. | Guide wheel for centrifugal pumps |
CN201133354Y (en) * | 2007-12-13 | 2008-10-15 | 姚庆余 | Underground bittern collecting and conveying dedicated pump |
CN203308695U (en) * | 2013-05-15 | 2013-11-27 | 江苏太阳宝新能源有限公司 | Fused salt submerged pump guide vane device |
CN104533838A (en) * | 2014-12-18 | 2015-04-22 | 珠海格力电器股份有限公司 | Adjustable diffuser |
-
2015
- 2015-06-29 CN CN201510382897.3A patent/CN104912851A/en active Pending
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH08260561A (en) * | 1995-03-27 | 1996-10-08 | Kubota Corp | Suction water tank for pump |
JPH0921400A (en) * | 1995-07-05 | 1997-01-21 | Hitachi Ltd | Diffuser with vane |
EP1219838A2 (en) * | 2000-11-14 | 2002-07-03 | CALPEDA S.p.A. | Guide wheel for centrifugal pumps |
CN201133354Y (en) * | 2007-12-13 | 2008-10-15 | 姚庆余 | Underground bittern collecting and conveying dedicated pump |
CN203308695U (en) * | 2013-05-15 | 2013-11-27 | 江苏太阳宝新能源有限公司 | Fused salt submerged pump guide vane device |
CN104533838A (en) * | 2014-12-18 | 2015-04-22 | 珠海格力电器股份有限公司 | Adjustable diffuser |
Non-Patent Citations (4)
Title |
---|
H.H.ANDERSON: "《泵的面积比规律》", 《流体工程》 * |
关醒凡: "《泵的理论与设计》", 28 February 1987, 机械工业出版社 * |
孔繁余等: "离心泵径向导叶正叶片参数的优化设计", 《农业工程学报》 * |
王广业: "《不锈钢冲压焊接多级离心泵叶轮优化设计及CFD分析》", 《工程科技Ⅰ辑》 * |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105673554A (en) * | 2016-01-07 | 2016-06-15 | 江苏大学 | Reversed spiral line type guide vane of nuclear main pump and design method of reversed spiral line type guide vane |
CN105673554B (en) * | 2016-01-07 | 2018-02-27 | 江苏大学 | The backpitch line stator and its design method of one seed nucleus main pump |
CN107299915A (en) * | 2016-12-07 | 2017-10-27 | 江苏国泉泵业制造有限公司 | A kind of Hydraulic Design Method of mining centrifugal pump stator |
KR20220160847A (en) * | 2021-05-28 | 2022-12-06 | 두산에너빌리티 주식회사 | Design method for flowpath of axial compressor of gas turbine |
KR102519091B1 (en) | 2021-05-28 | 2023-04-05 | 두산에너빌리티 주식회사 | Design method for flowpath of axial compressor of gas turbine |
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Application publication date: 20150916 |
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