CN107491567B - Design method of impeller of wide-efficiency energy-saving centrifugal pump - Google Patents
Design method of impeller of wide-efficiency energy-saving centrifugal pump Download PDFInfo
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Abstract
The invention discloses a design method of a wide-efficiency energy-saving centrifugal pump impeller, wherein a new relational expression is applied between geometric parameters of the impeller and performance parameters of a pump design working condition point, and the centrifugal pump impeller determined through the relation can achieve the purpose of wide-efficiency energy saving of a centrifugal pump in practical application.
Description
Technical Field
The invention relates to a design method of an impeller, in particular to a design method of a wide-efficiency energy-saving centrifugal pump impeller.
Background
Centrifugal pumps are both important devices in fluid delivery systems and consumers of electricity. The efficiency condition of the centrifugal pump in practical application in China is serious and low-efficiency, and energy waste is huge, which is completely inconsistent with the current global energy conservation and emission reduction trend. The reason is that: firstly), the design technology of the centrifugal pump is lagged behind, secondly) the production process and quality control are not in place, and thirdly) the efficiency of a design point is pursued too much and the cavitation problem is ignored; fourthly) the pump and the pipeline system have poor matching performance and large system loss.
With the increasing requirements of the country on environmental protection and energy conservation and emission reduction, the policy of energy conservation and subsidy implementation of the pump is even proposed, and in addition, in recent years, the global economic situation tends to be cold, the domestic serious excess of capacity and the serious loss of steel enterprises with large energy consumption are caused, and large-area production reduction, even production halt and production break occur. Therefore, the energy-saving improvement of the pump is urgent, and the development of an energy-saving type 'wide-efficiency' centrifugal pump is imperative. The most central component in the centrifugal pump is the impeller, and the efficiency of the impeller is often determined by the overall efficiency of the centrifugal pump. In the traditional centrifugal pump impeller design, only the efficiency of the working condition of a single design point is usually concerned, and in the actual use, the operating condition of the pump is changed, so that the high-efficiency area of the pump is required to be wide, and the comprehensive efficiency in the whole operating condition is highest.
The height of the efficiency of the centrifugal pump impeller and the width of the high-efficiency area are mainly determined by the outlet width b of the impeller 2 Impeller outer diameter D 2 Impeller inlet equivalent inner diameter D 0 Wrap angle phi of blade and outlet setting angle beta of blade 2 And the like. The values of the key parameters of the centrifugal pump impeller in the traditional design method are as follows:
1) Width b of impeller outlet 2 ：
b 2 = 0.64（ns/100） 5/6 (Q/n) 1/3 （m）
2) Impeller outer diameter D 2 ：
D 2 = (9.35~9.6)（ns/100） -1/2 （Q/n） 1/3 （m）
3) Equivalent inner diameter D of impeller inlet 0 ：
D 0 = K 0 （Q/n） 1/3 （m）
| ns | Efficiency is mainly considered | Compromise between efficiency and cavitation | Mainly considering cavitation |
| K 0 | 3.5~4.0 | 4.0~4.5 | 4.5~5.5 |
4) Blade wrap angle phi and blade outlet setting angle beta 2
In general, the blade wrap angle φ decreases with increasing specific speed ns, and the blade exit lay angle β 2 Increases with increasing specific speed ns. For low specific speed pumps, the blade exit setting angle beta is reduced due to reduced disc friction losses 2 And increasing the wrap angle phi of the blade.
The impeller designed by the traditional design method is narrow in high-efficiency area and poor in adaptability.
Disclosure of Invention
The invention aims to solve the technical problem of providing a design method of a wide-efficiency energy-saving centrifugal pump impeller, which adopts the technical scheme that: a design method for an impeller of a wide-efficiency energy-saving centrifugal pump is disclosed, wherein the following relation is suitable between geometric parameters of the impeller and performance parameters of a pump design working condition point:
1) Width b of impeller outlet 2 ：
b 2 = 2.56（ns/100） 0.99 （2gH） 0.5 /n （m） ns<80
b 2 = 0.7（ns/100） 0.7 (Q/n) 1/3 （m） 80 <ns<180
b 2 = 1.6（ns/100） 0.99 （2gH） 0.5 /n + 0.4（ns/100） 0.7 (Q/n) 1/3 （m）ns>180
2) Impeller outer diameter D 2 ：
D 2 = 8.8（ns/100） -1/2 （Q/n） 1/3 （m） ns<80
D 2 = 9.2（ns/100） -1/2 （Q/n） 1/3 （m） 80<ns<180
D 2 = 9.7（ns/100） -1/2 （Q/n） 1/3 （m） ns>180
3) Equivalent inner diameter D of impeller inlet 0 ：
D 0 = K 0 （Q/n） 1/3 （m）
| ns | 23~80 | 80~180 | 180~300 |
| K 0 | 5.5~5.0 | 5.0~4.6 | 4.6~4.4 |
4) Wrap angle phi of blade and bladeChip outlet setting angle beta 2
| ns | 23~60 | 60~120 | 120~210 | 210~300 |
| φ | 220°~160° | 160°~120° | 120°~105° | 105°~95° |
| β 2 | 16°~20° | 20°~23° | 23°~25° | 25°~26° |
In the formula:
q-design operating Point flow, cubic meters per second (m) 3 /s）；
H-design operating point lift, meter (m);
n-impeller speed, revolutions per minute (r/min);
ns-specific number of revolutions;
g-acceleration of gravity, m/s 2 （m/s 2 ）
D 2 -impeller outer diameter, meter (m);
D 0 -impeller-inlet equivalent internal diameter, meters (m);
b 2 -impeller exit width, meters (m);
phi-wrap angle of blade, degree (degree)
β 2 -vane outlet setting angle, degrees (°);
K 0 -a coefficient.
The invention has the beneficial effects that:
the invention provides a design value taking method of a wide-efficiency energy-saving centrifugal pump impeller, which solves the defects of narrow high-efficiency area, poor adaptability and the like of the impeller designed by the existing design method. By reasonably taking values of all parameters, the optimal matching performance is achieved, and finally, the optimization of improving the comprehensive efficiency is achieved. The invention realizes the principle that the flow loss of fluid in an impeller flow channel is minimized by means of enlarging the width of an impeller outlet, reducing the outer diameter of the impeller, reasonably taking the equivalent diameter of the impeller inlet, enlarging the wrap angle of a blade outlet, reducing the placement angle of the blade outlet and the like, and realizes the highest efficiency and wide efficient area by the optimal matching of main relevant hydraulic parameters of the impeller.
Description of the drawings:
FIG. 1 is a schematic illustration of the outer diameter of an impeller, the equivalent inner diameter of the impeller inlet, and the width of the impeller outlet in the present invention;
FIG. 2 is a schematic representation of the blade wrap angle, blade exit placement angle of the present invention.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
A design method of a wide-efficiency energy-saving centrifugal pump impeller is disclosed, wherein the outer diameter of the impeller, the equivalent inner diameter of an impeller inlet and the width of an impeller outlet are shown in figure 1, the wrap angle of blades and the placement angle of the blade outlet are shown in figure 2, and the geometric parameters and performance parameters of a pump design working condition point are in the following relations:
1) Width b of impeller outlet 2 Taking the wider impeller outlet width, often:
b 2 = 2.56（ns/100） 0.99 （2gH） 0.5 /n （m） ns<80
b 2 = 0.7（ns/100） 0.7 (Q/n) 1/3 （m） 80 <ns<180
b 2 = 1.6（ns/100） 0.99 （2gH） 0.5 /n + 0.4（ns/100） 0.7 (Q/n) 1/3 （m）ns>180
2) Impeller outer diameter D 2 For a low specific speed pump, a smaller impeller outer diameter is adopted; for the high specific speed pump, a slightly larger impeller outer diameter is usually selected as follows:
D 2 = 8.8（ns/100） -1/2 （Q/n） 1/3 （m） ns<80
D 2 = 9.2（ns/100） -1/2 （Q/n） 1/3 （m） 80<ns<180
D 2 = 9.7（ns/100） -1/2 （Q/n） 1/3 （m） ns>180
3) Equivalent inner diameter D of impeller inlet 0 The value of the equivalent inner diameter of the impeller inlet must be a large value as much as possible on the basis of ensuring the diffusivity of the flow channel between the blades, and the large value is usually taken as follows:
D 0 = K 0 （Q/n） 1/3 （m）
| ns | 23~80 | 80~180 | 180~300 |
| K 0 | 5.5~5.0 | 5.0~4.6 | 4.6~4.4 |
4) Blade wrap angle phi and blade outlet setting angle beta 2， On the basis of not causing blade displacement, runner jam, get great blade cornerite, get less blade export lay angle, and make blade cornerite and blade export lay angle reach an optimum match, often get:
| ns | 23~60 | 60~120 | 120~210 | 210~300 |
| φ | 220°~160° | 160°~120° | 120°~105° | 105°~95° |
| β 2 | 16°~20° | 20°~23° | 23°~25° | 25°~26° |
in the formula:
q-design operating Point flow, cubic meters per second (m) 3 /s）；
H-design operating point lift, meter (m);
n-impeller speed, revolutions per minute (r/min);
ns-specific number of revolutions;
g-acceleration of gravity, m/s 2 （m/s 2 ）
D 2 -impeller outer diameter, meter (m);
D 0 -impeller-inlet equivalent internal diameter, meters (m);
b 2 -impeller exit width, meters (m);
phi-leaf wrap angle, degree (°)
β 2 -vane outlet setting angle, degrees (°);
K 0 -a coefficient.
The effects which can be achieved by taking the values of the main relevant parameters of the centrifugal pump impeller by the design method are listed as follows:
firstly, the wide width of the outlet of the impeller means that the channels among the blades are wide and smooth, so that the flow effect of the fluid is better; the casting is easy, the surface smoothness of the flow channel is good, and the flow channel is not easy to block; the flow loss of the fluid in the flow channel is small, so that the efficiency of the impeller is improved to the maximum extent, the curve becomes flat, and the range of the high-efficiency area is widened.
Second, taking a smaller impeller outer diameter is beneficial to reducing the disc friction loss, while taking a slightly larger impeller outer diameter is beneficial to reducing the diffusion degree of the flow channel. The friction loss and the diffusion loss are reduced, the natural curve is flat, the high-efficiency area is widened, and therefore the efficiency of the impeller is high and the high-efficiency area is wide.
Thirdly, the size of the equivalent inner diameter of the impeller inlet dominates the cavitation performance of the impeller, the diffusion degree of the flow channel between the blades is also influenced to a certain extent, once the impeller is cavitated, the efficiency is naturally greatly reduced, and the value of the equivalent inner diameter of the impeller inlet needs to be a large value as far as possible on the basis of ensuring the diffusion degree of the flow channel between the blades, so that the cavitation performance of the impeller is improved, the efficiency of the impeller is comprehensively improved, and the range of a high-efficiency area is widened;
fourthly, the diffusion loss among the blades is the main component of the hydraulic loss of the impeller, the increase of the wrap angle of the blades is beneficial to reducing the diffusion loss among the blades, but the too large wrap angle can increase the on-the-way loss, and can also cause the displacement of the blades and the blockage of a flow channel. The blade wrap angle and the outlet installation angle complement each other, and the blade wrap angle and the outlet installation angle are optimally matched, so that the flow in the impeller is reasonable, the loss is minimum, and the efficiency is naturally highest.
Claims (1)
1. A design method of a wide-efficiency energy-saving centrifugal pump impeller is characterized by comprising the following steps: the following relationship is suitable between the geometric parameters of the impeller and the performance parameters of the pump design working condition points:
width b of impeller outlet 2 ：
b 2 = 2.56（ns/100） 0.99 （2gH） 0.5 /n （m） ns<80
b 2 = 0.7（ns/100） 0.7 (Q/n) 1/3 （m） 80 <ns<180
b 2 = 1.6（ns/100） 0.99 （2gH） 0.5 /n + 0.4（ns/100） 0.7 (Q/n) 1/3 （m）ns>180
2) Impeller outer diameter D 2 ：
D 2 = 8.8（ns/100） -1/2 （Q/n） 1/3 （m） ns<80
D 2 = 9.2（ns/100） -1/2 （Q/n） 1/3 （m） 80<ns<180
D 2 = 9.7（ns/100） -1/2 （Q/n） 1/3 （m） ns>180
3) Equivalent inner diameter D of impeller inlet 0 ：
D 0 = K 0 （Q/n） 1/3 （m）
4) Blade wrap angle phi and blade outlet setting angle beta 2
In the formula:
q-design operating Point flow, cubic meters per second (m) 3 /s）；
H-design operating point lift, meter (m);
n-impeller speed, revolutions per minute (r/min);
ns-specific number of revolutions;
g-acceleration of gravity, m/s 2 （m/s 2 ）
D 2 -impeller outer diameter, meter (m);
D 0 -impeller-inlet equivalent internal diameter, meters (m);
b 2 -impeller exit width, meter (m);
phi-wrap angle of blade, degree (degree)
β 2 -vane outlet setting angle, degrees (°);
K 0 -a coefficient.
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| CN201610406413.9A CN107491567B (en) | 2016-06-12 | 2016-06-12 | Design method of impeller of wide-efficiency energy-saving centrifugal pump |
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|---|---|---|---|
| CN201610406413.9A CN107491567B (en) | 2016-06-12 | 2016-06-12 | Design method of impeller of wide-efficiency energy-saving centrifugal pump |
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| CN107491567B true CN107491567B (en) | 2023-04-07 |
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| CN1265099C (en) * | 2004-05-19 | 2006-07-19 | 江苏大学 | Method for designing low-rate revolution centrifugal pump impeller |
| CN2784587Y (en) * | 2005-04-20 | 2006-05-31 | 张兴林 | Impeller of centrifugal, mixed-flow type pump and compressor |
| CN104819167A (en) * | 2015-04-24 | 2015-08-05 | 江苏大学 | Impeller of stainless steel punching-welding centrifugal pump and designing method thereof |
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Effective date of registration: 20220804 Address after: Room JT2077, Building 8, No. 3188, Jiaxing Road, Jiading District, Shanghai, 201816 Applicant after: Shanghai Yuke Environmental Engineering Co.,Ltd. Address before: Room 1076, Building 1, No. 1366, Chengnan Road, Huinan Town, Pudong New Area, Shanghai, 201300 Applicant before: SHANGHAI TONGYU ENVIRONMENTAL PROTECTION ENERGY SAVING TECHNOLOGY Co.,Ltd. |
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