CN1265099C - Method for designing low-rate revolution centrifugal pump impeller - Google Patents
Method for designing low-rate revolution centrifugal pump impeller Download PDFInfo
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- CN1265099C CN1265099C CN 200410014937 CN200410014937A CN1265099C CN 1265099 C CN1265099 C CN 1265099C CN 200410014937 CN200410014937 CN 200410014937 CN 200410014937 A CN200410014937 A CN 200410014937A CN 1265099 C CN1265099 C CN 1265099C
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- 238000000034 method Methods 0.000 title claims abstract description 19
- 241000209094 Oryza Species 0.000 claims description 18
- 235000007164 Oryza sativa Nutrition 0.000 claims description 18
- 235000009566 rice Nutrition 0.000 claims description 18
- 230000008676 import Effects 0.000 claims description 16
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 9
- 238000005266 casting Methods 0.000 abstract description 6
- 230000000694 effects Effects 0.000 abstract description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000004576 sand Substances 0.000 description 1
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Abstract
The present invention relates to a method for designing an impeller of a low-rate revolution centrifugal pump which can be mainly used in an operating mode of low-rate revolution, namely the operating mode with high lifting height and small flow rate, and can be used in the operating mode of high-rate revolution, namely the operating mode with low lifting height and great flow rate. The present invention is characterized in that when the impeller of the centrifugal pump is designed, a geometric parameter of the impeller establishes contact with a performance parameter of a designed operating mode point of the pump by a plurality of new relations, so the design effect that the designed operating mode of the pump, namely the usage operating modes of the flow rate and the lifting height coincide with the operating mode of a maximum efficiency point and the operating mode of a maximum power point is reached. The geometric parameter of the impeller designed by the present invention not only can satisfy requirement of the lifting height of the designed operating mode of the water pump and the requirements to increase efficiency and to suit for casting, but also can satisfy the requirement that the designed operating mode point is the operating mode point of the maximum power. Therefore, the low-rate revolution centrifugal pump designed by the present invention not only can be used in the operating mode with high lifting height and small flow rate efficiently and reliably, but also can be used in the operating mode with low lifting height and great flow rate safely without overload.
Description
Affiliated technical field
The present invention relates to a kind of design method of non-varactor pump major part, especially mainly being to use under the high-lift low flow rate condition in the low specific speed operating mode, will be the impeller design method of the low specific speed centrifugal pump that uses under the low lift and large flow rate operating mode in high specific speed operating mode also.
Background technique
At present, the impeller design method of known low specific speed centrifugal pump, all reduce impeller diameter as far as possible under the requirement of water pump design conditions lift and improve pump efficiency satisfying, thereby bigger impeller outlet width and blade outlet angle arranged, can only guarantee that centrifugal pump is that high-efficiency reliable is used under the high-lift low flow rate condition in the low specific speed operating mode, if in high specific speed operating mode is to use under the low lift and large flow rate operating mode, will power overload and burn out motor.But a lot of low specific speed centrifugal pumps, especially small-sized submersible pump and household centrifugal pump generally all can mobile places to use, and use today under the low specific speed operating mode, and may use under high specific speed operating mode tomorrow.The low specific speed centrifugal pump that this just requires us to design, can use in high-efficiency reliable under the high-lift low flow rate condition again can the overload free use of safety under the low lift and large flow rate operating mode.
For this reason, No. 89212885.2 patents of the patented technology that has earlier " the involute impeller that is used for rotary type fluid machine " and No. 90214606.8 patents " a kind of nothing overload low specific speed centrifugal pump impeller ", some new design method have been proposed, it mainly is the method that reduces impeller outlet angle and discharge area, but still there are following three problems in these two patented technologies: 1. there is bigger distance the position of peak output operating point and design conditions point position, also might overload at applying working condition; 2. subtended angle of blade is too big or the runner gap is too little, has increased difficulty to casting technique; 3. do not change the design method of blade import, often will add the import angle of attack, the peak efficiency operating mode that makes water pump is partial to big flow and design power efficiency is on the low side.
Summary of the invention
In order to overcome the deficiency of existing low specific speed centrifugal pump impeller design method, the invention provides a kind of new low specific speed centrifugal pump impeller design method, the lift that not only satisfies the water pump design conditions with the impeller geometric parameter of the present invention design requires and raises the efficiency the requirement with suitable for casting, also satisfies the requirement that design conditions point also is the peak output operating point.Thereby the low specific speed centrifugal pump that designs with the present invention not only can high-efficiency reliable use under high-lift low flow rate condition, can also guarantee the overload free use of safety under the low lift and large flow rate operating mode of this pump.
Technological scheme of the present invention is:
1. when design low specific speed centrifugal pump impeller, be the design conditions of pump that the applying working condition and the best efficiency point operating mode of flow lift is designed to overlap with power maximum point operating mode.
Its method is: the relation that is fit to following equation between the design conditions point performance parameter of the geometric parameter of blade exit and pump:
Q
p＝0.086n?b
2D
2 2tgβ
2(1-3.1416sinβ
2/Z)[1-S
2Z/(3.1416D
2sinβ
2)]
H
p＝0.0037n?D
2{0.0524nD
2-Q
p/(2.83D
2b
2tgβ
2)/[1-S
2Z/(3.1416D
2sinβ
2)]}
P
max＝9806?Q
p?H
p/η
p
In the formula: Q
pThe flow of-design conditions, rice
3/ second;
H
pThe lift of-design conditions, rice;
P
MaxThe pump power of-design conditions also is a power maximum in all operating modes, watt;
η
pThe pump efficiency of-design conditions also is the peak efficiency in all operating modes, %;
The n-wheel speed, rev/min;
b
2-impeller blade exit width, rice;
D
2The outside diameter of-impeller blade, rice;
β
2The outlet laying angle of-impeller blade, degree;
The number of blade of Z-impeller, individual;
S
2The vane thickness in-impeller blade outlet port, rice.
Subtended angle of blade is not claimed in above relation, can arbitrarily control cornerite when therefore designing does not influence casting.The accurate calculating of pump efficiency also is unable to handle at present, but the pump efficiency η of design conditions
pThe peak efficiency that is designed in all operating modes is accomplished easily, and the measure that blade import laying angle is proposed in the 3rd below especially is highly effective.
2. from above-mentioned design method, can see the outlet laying angle β of impeller blade
2Important function, but β
2Be subjected to the outlet laying angle β of front side of vane
2' and the outlet laying angle β of vacuum side of blade
2" restriction.When design low specific speed centrifugal pump impeller, the outlet laying angle β of front side of vane
2' be designed to 0 degree, the outlet laying angle β of vacuum side of blade
2" be designed to 2 β
2Degree, the outlet laying angle β of impeller blade
2=(β
2'+β
2")/2 can obtain good design effect.
3. when design low specific speed centrifugal pump impeller, is the design conditions of pump the operating mode that the applying working condition of flow lift is designed to blade entrance loss minimum, its method is: the import laying angle of impeller blade working surface and the import laying angle of vacuum side of blade equate, all equal β
1And the relation of suitable equation:
β
1＝arctg{Q
p/(0.164D
1 2n?b
1)/[1-(S
1Z)/(3.1416D
1sinβ
1)]}
In the formula: Q
pThe flow of-design conditions, rice
3/ second;
The n-wheel speed, rev/min;
b
1-impeller blade entrance width, rice;
D
1The interior circular diameter of-impeller blade, rice;
β
1The import laying angle of-impeller blade, degree;
The number of blade of Z-impeller, individual;
S
1The vane thickness of-impeller blade inlet, rice.
She Ji essence is exactly that the import laying angle of impeller blade is designed to equate (anomaly adding the angle of attack) with the import flow angle of water pump design conditions like this, reaches water pump at design conditions pump efficiency supreme good.
The invention has the beneficial effects as follows that the lift that not only satisfies the water pump design conditions with the impeller geometric parameter of the present invention design requires and raise the efficiency the requirement with suitable for casting, also satisfies the requirement that design conditions point also is the peak output operating point.Thereby the low specific speed centrifugal pump that designs with the present invention not only can high-efficiency reliable use under high-lift low flow rate condition, can also guarantee the overload free use of safety under the low lift and large flow rate operating mode of this pump.
Description of drawings
The present invention is further described below in conjunction with drawings and Examples.
Fig. 1 is the impeller axial plane sectional view of one embodiment of the invention.
Fig. 2 is same embodiment's impeller blade figure (throwing off the paddle wheel plane sectional view of seeing from front shroud of impeller towards back shroud of impeller behind the front shroud of impeller).
Among the figure: 1. front shroud of impeller, 2. back shroud of impeller, 3. impeller blade entrance width b
1, 4. impeller blade exit width b
2, the 5. interior circular diameter D of impeller blade
1, the 6. outside diameter D of impeller blade
2, 7. blade, 8. front side of vane, 9. vacuum side of blade, the 10. import laying angle of front side of vane, the import laying angle of 11. vacuum side of blades, the vane thickness S of 12. impeller blade inlets
1, the outlet laying angle β of 13. front side of vanes
2', the outlet laying angle β of 14. vacuum side of blades
2", the outlet laying angle β of 15. impeller blades
2, the vane thickness S in 16. impeller blade outlet ports
2, 17. subtended angle of blades.
Embodiment
Fig. 1 and Fig. 2 have determined this embodiment's impeller shape jointly.It is the same with most of centrifugal pump impellers, has front shroud of impeller (1) and back shroud of impeller (2), is a kind of double shrouded wheel.If do not have front shroud of impeller and back shroud of impeller very little, promptly make semi-open type or unshrouded impeller, do not influence enforcement of the present invention, because the present invention's control is the parameter of blade (7) yet.In the drawings, the convex surface of blade is front side of vane (8) again, and the concave surface of blade is vacuum side of blade (9) again, and present embodiment is front side of vane outlet laying angle β
2' (13) are designed to 0 degree, and this can be from β
2' two arms of angle and the angle on the 3rd limit all be that 90 degree come the outlet laying angle β of vacuum side of blade as can be seen
2" (14) are designed to 2 β
2Degree, so the outlet laying angle β of impeller blade
2=(β
2'+β
2")/2.The present invention adjusts impeller blade exit width b by following relation
2(4), the outside diameter D of impeller blade
2(6), the outlet laying angle β of impeller blade
2(15), the vane thickness S in impeller blade outlet port
2(16) and the number of blade Z of impeller, make this embodiment's pump performance satisfy our flow Q to design conditions
p, design conditions lift H
pPump power P with design conditions
MaxDesigning requirement when wheel speed is n.
Q
p＝0.086n?b
2D
2 2tgβ
2(1-3.1416sin?β
2/Z)[1-S
2Z/(3.1416D
2sinβ
2)]
H
p＝0.0037n?D
2{0.0524nD
2-Q
p/(2.83D
2b
2tgβ
2)/[1-S
2Z/(3.1416D
2sinβ
2)]}
P
max＝9806Q
pH
p/η
p
This embodiment's water pump will be less than the power P of design conditions at the power of other applying working conditions
Max
In the drawings, the import laying angle (10) of front side of vane and the import laying angle (11) of vacuum side of blade equate, all equal β
1And with impeller blade entrance width b
1(3), the interior circular diameter D of impeller blade
1(5) and the vane thickness S of impeller blade inlet
1(12) be fit to the relation of equation jointly:
β
1＝arctg{Q
p/(0.164D
1 2n?b
1)/[1-(S
1Z)/(3.1415D
1sinβ
1)]}
Like this design just can guarantee this embodiment water pump in the import liquid stream of design conditions and the impact loss minimum of inlet side, be the applying working condition of flow lift and the purpose of best efficiency point operating mode coincidence thereby reach the design conditions of pump.
In this embodiment, subtended angle of blade (17) is designed to about 90 degree, and casting and sand removal are all than being easier to.
Claims (3)
1. low specific speed centrifugal pump impeller design method, it is according to the flow Q of pump to design conditions
p, design conditions lift H
pPump power P with design conditions
MaxDesigning requirement when wheel speed is n, come the geometric parameter of designing and calculating impeller blade, it is characterized in that: is design conditions that the applying working condition and the best efficiency point operating mode of flow lift is designed to overlap with power maximum point operating mode, promptly is fit to the relation of following equation between the design conditions point performance parameter of the geometric parameter of impeller outlet and pump:
Q
p＝0.086?n?b
2?D
2 2?tgβ
2(1-3.1416sinβ
2/Z)[1-S
2Z/(3.1416D
2sinβ
2)]
H
p＝0.0037n?D
2{0.0524nD
2-Q
p/(2.83D
2b
2tgβ
2)/[1-S
2Z/(3.1416D
2sinβ
2)]}
P
max＝9806Q
p?H
p/η
p
In the formula: Q
pThe flow of-design conditions, rice
3/ second;
H
pThe lift of-design conditions, rice;
P
MaxThe pump power of-design conditions also is a power maximum in all operating modes, watt;
η
pThe pump efficiency of-design conditions also is the peak efficiency in all operating modes, %;
The n-wheel speed, rev/min;
b
2-impeller blade exit width, rice;
D
2The outside diameter of-impeller blade, rice;
β
2The outlet laying angle of-impeller blade, degree;
The number of blade of Z-impeller, individual;
S
2The vane thickness in-impeller blade outlet port, rice.
2. a kind of low specific speed centrifugal pump impeller design method as claimed in claim 1 is characterized in that: the outlet laying angle β of the impeller vane of centrifugal pumps working surface of design
2' be 0 degree, the outlet laying angle β of vacuum side of blade
2" be 2 β
2Degree;
3. a kind of low specific speed centrifugal pump impeller design method as claimed in claim 1 is characterized in that: the import laying angle of the impeller vane of centrifugal pumps working surface of design and the import laying angle of vacuum side of blade equate, all equal β
1And the relation of suitable equation:
β
1＝arctg{Q
p/(0.164?D
1 2?n?b
1)/[1-(S
1Z)/(3.1416?D
1sinβ
1)]}
In the formula: Q
pThe flow of-design conditions, rice
3/ second;
The n-wheel speed, rev/min;
b
1-impeller blade entrance width, rice;
D
1The interior circular diameter of-impeller blade, rice;
β
1The import laying angle of-impeller blade, degree;
The number of blade of Z-impeller, individual;
S
1The vane thickness of-impeller blade inlet, rice.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200410014937 CN1265099C (en) | 2004-05-19 | 2004-05-19 | Method for designing low-rate revolution centrifugal pump impeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200410014937 CN1265099C (en) | 2004-05-19 | 2004-05-19 | Method for designing low-rate revolution centrifugal pump impeller |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1580577A CN1580577A (en) | 2005-02-16 |
| CN1265099C true CN1265099C (en) | 2006-07-19 |
Family
ID=34581723
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200410014937 Expired - Fee Related CN1265099C (en) | 2004-05-19 | 2004-05-19 | Method for designing low-rate revolution centrifugal pump impeller |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1265099C (en) |
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2004
- 2004-05-19 CN CN 200410014937 patent/CN1265099C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1580577A (en) | 2005-02-16 |
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