CN106194822B - Closed impeller of centrifugal pump and design method thereof - Google Patents
Closed impeller of centrifugal pump and design method thereof Download PDFInfo
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- CN106194822B CN106194822B CN201610824236.6A CN201610824236A CN106194822B CN 106194822 B CN106194822 B CN 106194822B CN 201610824236 A CN201610824236 A CN 201610824236A CN 106194822 B CN106194822 B CN 106194822B
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- 238000000034 method Methods 0.000 title claims abstract description 28
- 230000001133 acceleration Effects 0.000 claims description 6
- 230000000694 effects Effects 0.000 abstract description 6
- 230000003068 static effect Effects 0.000 description 16
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Classifications
-
- 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
- F04D29/22—Rotors specially for centrifugal pumps
-
- 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
- F04D29/04—Shafts or bearings, or assemblies thereof
- F04D29/041—Axial thrust balancing
-
- 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
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
-
- 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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/669—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for liquid pumps
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- General Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Computational Mathematics (AREA)
- Mathematical Analysis (AREA)
- Mathematical Optimization (AREA)
- Pure & Applied Mathematics (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a design method of a closed impeller of a centrifugal pump, which comprises a front cover plate, a rear cover plate, blades positioned between the front cover plate and the rear cover plate, and shaft holes, wherein flow passages are arranged between two adjacent blades, balance holes are formed in the blades, and the aperture of each balance hole is D; the balance hole comprises an inlet and an outlet, wherein the inlet is positioned at the rear cover plate and far away from the hub, and the outlet is positioned at the front cover plate and near the hub; the included angle between the central line of the balance hole and the axis of the shaft hole is theta, and the distance between the inlet and the axis of the shaft hole is r 2 The distance between the outlet and the axis of the shaft hole is r 1 The method comprises the steps of carrying out a first treatment on the surface of the The balance hole is arranged in the blade and is not intersected with the runner. Through the design, the balance hole structure has no influence on the medium flow in the closed impeller of the centrifugal pump, can not interfere with the flow state in the impeller, can not generate volume loss, and improves the working efficiency of the centrifugal pump and the balance effect of the axial force of the impeller. The invention also discloses a closed impeller of the centrifugal pump.
Description
Technical Field
The invention relates to an impeller, in particular to a closed impeller of a centrifugal pump. The invention relates to a design method of a closed impeller of a centrifugal pump, in particular to a design method of an impeller.
Background
In the centrifugal pump, due to the fact that the front cover plate and the rear cover plate of the impeller are asymmetric, fluid acting forces are different, and a part of axial force is remained after the fluid acting forces are offset, and the acting direction of the axial force faces the direction of the suction inlet of the impeller. During centrifugal pump design, it is necessary to manage to balance or eliminate the axial forces on the impeller, which would otherwise cause rotor play and even rotor contact with stationary parts, resulting in part damage. According to actual production statistics, the faults caused by axial force account for more than 40% of pump faults, the maintenance workload of the pump is also quite large, the working cost is increased intangibly, and the utilization rate is reduced.
In order to balance the axial force on the impeller, the proposal adopted at present is to arrange balance holes to balance the axial force, the proposal is to arrange two sealing rings with the same diameter on the front cover plate and the back cover plate of the impeller, and uniformly arrange a plurality of balance holes below the mouth ring of the back cover plate of the impeller, so that the balance chamber of the back cover plate is communicated with the suction inlet of the impeller, thereby achieving the purpose of balancing the axial force. However, this solution has the following drawbacks: (1) the leakage flow of the balance hole seriously damages the flow state of the inlet of the impeller, so that the cavitation resistance of the pump is reduced; (2) the liquid flow leaks from the balance hole to cause larger volume loss, so that the efficiency of the centrifugal pump is reduced; (3) the position and the size of the balance hole are empirically valued, so that the effect of balancing the axial force is not ideal; (4) the axial forces cannot be balanced completely and there is still residual axial force.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention provides a closed impeller design method of a centrifugal pump, which can effectively balance axial force on an impeller.
The technical scheme adopted for solving the technical problems is as follows: the utility model provides a design method of centrifugal pump closed impeller, closed impeller includes preceding apron, back shroud, is located a plurality of blades between preceding apron and the back shroud, and link up the shaft hole of preceding apron and back shroud in proper order, is equipped with runner, its characterized in that between two adjacent blades: the blades are provided with balance holes, and the aperture of each balance hole is D; the balance hole comprises an inlet and an outlet, wherein the inlet of the balance hole is positioned at the rear cover plate and far away from the hub, and the outlet is positioned at the front cover plate and near the hub; the connecting line between the balance hole inlet and the balance hole outlet is a balance hole center line, the included angle between the balance hole center line and the shaft hole axis is theta, and the distance between the balance hole inlet and the shaft hole axis is r 2 The distance between the outlet of the balance hole and the axis of the shaft hole is r 1 The method comprises the steps of carrying out a first treatment on the surface of the The balance hole is arranged in the blade and is not intersected with the runner; wherein,
tanθ＝(r 2 -r 1 )/b 2 ；
D＝(0.4：0.7)b 1 ；
in the method, in the process of the invention,
R m -ororing radius, m;
R h -hub radius, m;
z-number of blades;
omega-speed, rad/s;
H p -impeller outlet potential lift, m;
R 2 -impeller radius, m;
b 2 blade width, m;
b 1 blade thickness, m;
g-gravitational acceleration.
The beneficial effects of the invention are as follows: through the design, the balance hole structure has no influence on the medium flow in the closed impeller of the centrifugal pump, can not interfere with the flow state in the impeller, can not generate volume loss, and improves the working efficiency of the centrifugal pump and the balance effect of the axial force of the impeller.
Further preferably, the method comprises the following steps: the included angle theta is in the range of 0-60 degrees.
The blade setting scheme is that the number of balance holes on each blade is more than 1 or 2, and the number of the balance holes on each blade is consistent, so that the stress balance of the front cover plate and the rear cover plate of the closed impeller is ensured.
The other blade setting scheme is that the number of the blades is even, and the number of the blades is more than or equal to 4, and then the blades provided with the balance holes are evenly distributed at intervals around the shaft hole. That is, not every blade is provided with a balancing hole, but more than 1 blade or 2 blades without balancing holes exist between any two blades with balancing holes, and the blades with balancing holes are uniformly distributed on the closed impeller. The uniformity refers to that on the same closed impeller, blades without balance holes between any two blades with balance holes are kept consistent.
In order to overcome the defects of the prior art, the invention provides a closed impeller of a centrifugal pump, which can effectively balance the axial force on the impeller.
The technical scheme adopted for solving the technical problems is as follows: a centrifugal pump closed impeller comprises a front cover plate, a rear cover plate, a plurality of blades positioned between the front cover plate and the rear cover plate, and shaft holes sequentially penetrating through the front cover plate and the rear cover plate, wherein a flow passage is arranged between two adjacent blades, balance holes are formed in the blades, and the aperture of each balance hole is D; the balance hole comprises an inlet and an outlet, wherein the inlet of the balance hole is positioned at the rear cover plate and far away from the hub, and the outlet is positioned at the front cover plate and near the hub; the connecting line between the balance hole inlet and the balance hole outlet is a balance hole center line, the included angle between the balance hole center line and the shaft hole axis is theta, and the distance between the balance hole inlet and the shaft hole axis is r 2 The distance between the outlet of the balance hole and the axis of the shaft hole is r 1 The method comprises the steps of carrying out a first treatment on the surface of the The balance hole is arranged in the blade and is not intersected with the runner; wherein,
tanθ＝(r 2 -r 1 )/b 2 ；
D＝(0.4：0.7)b 1 ；
in the method, in the process of the invention,
R m -ororing radius, m;
R h -hub radius, m;
z-number of blades;
omega-speed, rad/s;
H p -impeller outlet potential lift, m;
R 2 -impeller radius, m;
b 2 blade width, m;
b 1 blade thickness, m;
g-gravitational acceleration.
The beneficial effects of the invention are as follows: the closed impeller structure is improved, the balance hole structure can not influence the medium flow in the closed impeller of the centrifugal pump, the flow state in the impeller can not be disturbed, the volume loss can not be generated, the working efficiency of the centrifugal pump is improved, and the balance effect of the axial force of the impeller is improved.
Drawings
Fig. 1 is a schematic structural view of an impeller according to an embodiment.
Fig. 2 is an axial cross-sectional view of an impeller according to one embodiment.
Fig. 3 is a front view of an impeller according to an embodiment, with the front cover plate removed.
Fig. 4 is an axial force analysis diagram of an impeller according to an embodiment.
Detailed Description
The invention is further described below with reference to the accompanying drawings:
embodiment one: as shown in fig. 1, 2, 3 and 4, the design method of the embodiment is as follows, the closed impeller comprises a front cover plate 11, a rear cover plate 12, a plurality of blades 2 positioned between the front cover plate 11 and the rear cover plate 12, and shaft holes 13 penetrating through the front cover plate 11 and the rear cover plate 12 in sequence, and a flow passage 4 is arranged between two adjacent blades 2. Each blade 2 is provided with 1 balance hole 3, and the aperture of the balance hole 3 is D; the balance hole 3 comprises an inlet 32 and an outlet 31, the inlet 32 of the balance hole 3 is positioned at the rear cover plate 12 and far away from the hub 14, the outlet 31 is positioned at the front cover plate 11 and near the hub 14, and the static pressure of the inlet 32 of the balance hole 3 is higher than that of the outlet 31. The connecting line between the inlet 32 and the outlet 31 of the balance hole 3 is the center line of the balance hole 3, the included angle between the center line of the balance hole 3 and the axis of the shaft hole 13 is theta, and the value range of theta is 0-60 degrees; the distance between the inlet 32 of the balance hole 3 and the axis of the shaft hole 13 is r 2 The distance between the outlet of the balance hole 3 and the axis of the shaft hole 13 is r 1 . The balance hole 3 is arranged inside the blade 2 and does not intersect with the flow passage 4, i.e. the balance hole 3 is only arranged inIn the blades 2 and do not pass through the flow channels 4 in the shrouded impeller.
The amount of balancing axial force of the balancing holes 3 depends on the hole diameter of the balancing holes 3, the positions of the inlet 32 and the outlet 31 and the number of the balancing holes 3, and the specific calculation method is as follows:
at any radius R of the impeller back cover plate 12, the differential pressure h is applied,
r is the distance from any point on the blade to the axis of the shaft hole, m;
H p -impeller outlet potential lift, m;
h' -the head at any radius R, m;
R 2 -impeller radius, m;
omega-speed, rad/s;
multiplying the two sides by the liquid density ρ and the gravitational acceleration g and integrating the diameter of the hub 14 to the diameter of the seal ring to obtain the cover plate axial force T 1 Is that
I.e.
Omega-speed, rad/s;
R m -ororing radius, m;
R h -hub radius, m;
g-gravitational acceleration.
The distance between the center of the inlet 32 of the balance hole 3 and the axis of the shaft hole 13 is r 2 The distance between the center of the outlet 31 of the balance hole 3 and the axis of the shaft hole 13 is r 1 Included angle tanθ= (r) between center line of balance hole 3 and axis of shaft hole 13 2 -r 1 )/b 2 。
Static head at the inlet 32 of balance hole 3
Static pressure head at outlet 31 of balance hole 3
Since the diameter of the balance hole 3 is smaller, the static pressure at the center of the balance hole 3 can be approximated to the average static pressure of the balance hole, and the static pressures are respectively:
T 20 -balancing the average static pressure at the inlet of the holes, N;
T 10 -balancing the average static pressure at the orifice outlet, N;
the axial force that can be balanced by one balance hole 3 is deltat 0 ：
In this embodiment, taking only 1 balance hole 3 of one blade 2 as an example, the total axial force balanced by all balance holes 3 is Δt:
z-number of blades;
let Δt=t 1 The method can obtain:
to ensure the effect of balancing the axial force, the static pressure at the inlet 32 of the balancing hole 3 is at least 2 times greater than the static pressure at the mouth ring, so that the static pressure difference between the inlet 32 and the outlet of the balancing hole 3 is greater than the static pressure at the mouth ring. (the mouth ring, also called sealing ring, or wear ring) thus,
since the balance hole 3 is formed on the blade 2, the aperture range is
D＝(0.4：0.7)b 1 ；
b 2 Blade width, m;
b 1 blade thickness, m;
the comprehensive preparation method comprises the following steps:
tanθ＝(r 2 -r 1 )/b 2 ；
D＝(0.4：0.7)b 1 ；
in the embodiment, the following steps are described:
r is the distance from any point on the blade to the axis of the shaft hole, m;
h' -the head at any radius R, m;
H p -impeller outlet potential lift, m;
R 2 -impeller radius, m;
omega-speed, rad/s;
T 1 -cover plate axial force, N;
R m -ororing radius, m;
R h -hub radius, m;
h 2 -balancing the static head at the entrance of the hole, m;
h 1 -a static head at the exit of the balancing hole, m;
T 20 -balancing the average static pressure at the inlet of the holes, N;
T 10 -balancing the average static pressure at the orifice outlet, N;
ΔT 0 -an axial force balanced by the balancing hole, N;
Δt—the total axial force balanced by the balance holes, N;
z-number of blades;
b 2 blade width, m;
b 1 blade thickness, m;
g-gravitational acceleration.
The relation between the position of the balance hole 3 and the inclination angle of the balance hole 3 can be obtained by the equation set, and then the proper specific size of the balance hole 3 is determined through optimization calculation according to the related parameters of the closed impeller.
Compared with the prior art, the axial force balancing method for the closed impeller of the centrifugal pump changes the position and the mode of the balancing hole 3, retains the advantage of simple and easy operation of the structure, does not interfere the internal flow state of the closed impeller of the centrifugal pump, does not generate volume loss, and improves the efficiency and the axial force balancing effect of the centrifugal pump, so the axial force balancing method for the closed impeller of the centrifugal pump has strong advantages compared with the traditional balancing hole method.
The examples are preferred embodiments of the present invention, but the present invention is not limited to the above-described embodiments, and any obvious modifications, substitutions or variations that can be made by one skilled in the art without departing from the spirit of the present invention are within the scope of the present invention.
Embodiment two: the difference from the first embodiment is that the number of the blades 2 is an even number and the number of the blades 2 is 4 or more, and the blades 2 provided with the balance holes 3 are uniformly distributed at intervals around the shaft hole 13. Wherein, the blades without balance holes are called primary blades, and 1 or more primary blades can be arranged between the blades 2 with the adjacent two balance holes 3, and the number of the primary blades between the blades 2 with the adjacent two balance holes 3 is kept consistent on the same closed impeller.
In a third embodiment, the present embodiment is a closed impeller of a centrifugal pump, and the closed impeller of the centrifugal pump is designed by adopting the design method disclosed in the first embodiment or the second embodiment.
Claims (4)
1. The utility model provides a design method of centrifugal pump closed impeller, closed impeller includes preceding apron, back shroud, is located a plurality of blades between preceding apron and the back shroud, and link up the shaft hole of preceding apron and back shroud in proper order, is equipped with runner, its characterized in that between two adjacent blades: the blades are provided with balance holes, and the aperture of each balance hole is D; the balance hole comprises an inlet and an outlet, wherein the inlet of the balance hole is positioned at the rear cover plate and far away from the hub, and the outlet is positioned at the front cover plate and near the hub; the connecting line between the balance hole inlet and the balance hole outlet is a balance hole center line, the included angle between the balance hole center line and the shaft hole axis is theta, and the distance between the balance hole inlet and the shaft hole axis is r 2 The distance between the outlet of the balance hole and the axis of the shaft hole is r 1 The method comprises the steps of carrying out a first treatment on the surface of the The balance hole is arranged in the blade and is not intersected with the runner; wherein,
tanθ＝(r 2 -r 1 )/b 2 ；
D＝(0.4：0.7)b 1 ；
in the method, in the process of the invention,
R m -ororing radius, m;
R h -hub radius, m;
z-number of blades;
omega-speed, rad/s;
H p -impeller outlet potential lift, m;
R 2 -impeller radius, m;
b 2 blade width, m;
b 1 blade thickness, m;
g-gravitational acceleration.
2. The method for designing a closed impeller of a centrifugal pump according to claim 1, wherein: the included angle theta is in the range of 0-60 degrees.
3. The method for designing a closed impeller of a centrifugal pump according to claim 1, wherein: the number of the balance holes on each blade is 1 or more than 2, and the number of the balance holes on each blade is consistent.
4. The method for designing a closed impeller of a centrifugal pump according to claim 1, wherein: the number of the blades is even, and the number of the blades is more than or equal to 4, and the blades provided with the balance holes are evenly distributed at intervals around the shaft hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610824236.6A CN106194822B (en) | 2016-09-15 | 2016-09-15 | Closed impeller of centrifugal pump and design method thereof |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610824236.6A CN106194822B (en) | 2016-09-15 | 2016-09-15 | Closed impeller of centrifugal pump and design method thereof |
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| Publication Number | Publication Date |
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| CN106194822A CN106194822A (en) | 2016-12-07 |
| CN106194822B true CN106194822B (en) | 2024-03-08 |
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| CN112555200A (en) * | 2020-11-20 | 2021-03-26 | 西安理工大学 | Multistage gas-liquid mixed transportation pump suitable for high gas content |
| CN114198318A (en) * | 2021-11-02 | 2022-03-18 | 北京慨尔康科技发展有限公司 | High-performance electronic circulating water pump for vehicle-mounted hydrogen fuel cell |
| CN114607639B (en) * | 2022-02-28 | 2024-02-20 | 江西南方锅炉股份有限公司 | Conveying device for steam boiler equipment |
| CN115324928A (en) * | 2022-08-08 | 2022-11-11 | 扬州大学 | Centrifugal pump capable of reducing axial thrust of impeller and design method thereof |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102322443A (en) * | 2011-09-08 | 2012-01-18 | 浙江工业大学 | Single-stage centrifugal pump with balanced axial force |
| CN202545343U (en) * | 2012-05-05 | 2012-11-21 | 贾志敏 | Centrifugal pump |
| CN203516115U (en) * | 2013-09-02 | 2014-04-02 | 轻工业杭州机电设计研究院 | Pulp-air secondary separation structure of medium consistency pulp pump |
| CN205036629U (en) * | 2015-09-25 | 2016-02-17 | 讯凯国际股份有限公司 | Impeller, fluid pump and liquid cooling device |
| CN206290481U (en) * | 2016-09-15 | 2017-06-30 | 浙江理工大学 | A kind of centrifugal pump closed type impeller |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FI20050450A (en) * | 2005-04-29 | 2006-10-30 | Sulzer Pumpen Ag | Centrifugal pump and impeller |
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Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102322443A (en) * | 2011-09-08 | 2012-01-18 | 浙江工业大学 | Single-stage centrifugal pump with balanced axial force |
| CN202545343U (en) * | 2012-05-05 | 2012-11-21 | 贾志敏 | Centrifugal pump |
| CN203516115U (en) * | 2013-09-02 | 2014-04-02 | 轻工业杭州机电设计研究院 | Pulp-air secondary separation structure of medium consistency pulp pump |
| CN205036629U (en) * | 2015-09-25 | 2016-02-17 | 讯凯国际股份有限公司 | Impeller, fluid pump and liquid cooling device |
| CN206290481U (en) * | 2016-09-15 | 2017-06-30 | 浙江理工大学 | A kind of centrifugal pump closed type impeller |
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