CN115076156B - Full-flow high-efficiency high-speed centrifugal pump - Google Patents
Full-flow high-efficiency high-speed centrifugal pump Download PDFInfo
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- CN115076156B CN115076156B CN202210906619.3A CN202210906619A CN115076156B CN 115076156 B CN115076156 B CN 115076156B CN 202210906619 A CN202210906619 A CN 202210906619A CN 115076156 B CN115076156 B CN 115076156B
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- centrifugal pump
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- 238000013461 design Methods 0.000 claims abstract description 12
- 238000009792 diffusion process Methods 0.000 claims description 3
- 239000012530 fluid Substances 0.000 abstract description 4
- 238000012938 design process Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000004458 analytical method Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 1
- 238000010612 desalination reaction Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000011160 research Methods 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- 239000010865 sewage Substances 0.000 description 1
- 238000012795 verification Methods 0.000 description 1
Classifications
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- 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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for liquid pumps
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- 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
- F04D29/2205—Conventional flow pattern
- F04D29/2222—Construction and assembly
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- 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
- F04D29/242—Geometry, shape
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention relates to a centrifugal pump, belongs to the field of fluid machinery, and in particular relates to a full-flow high-efficiency high-speed centrifugal pump. The invention starts from ensuring the full flow high efficiency of the high-speed centrifugal pump, designs through the impeller and the volute, and explores the matching relation between different parameters of the volute and the impeller, so that the energy loss is minimum when the fluid flows from the impeller to the volute, and the purpose of high full flow high efficiency of the high-speed centrifugal pump is achieved.
Description
Technical Field
The invention relates to a centrifugal pump, belongs to the field of fluid machinery, and in particular relates to a full-flow high-efficiency high-speed centrifugal pump.
Background
Centrifugal pumps, which are a general-purpose machine in production and life, play an important role in various fields of national economy, and more fields require more specialized pump equipment, and efficient, safe and stable operation thereof is a final goal of centrifugal pump design pursuit.
The efficiency of the pump is mainly considered in the design process of the conventional centrifugal pump so as to achieve the aim of saving energy consumption, and the centrifugal pump can achieve the highest working efficiency through the design of geometric parameters of an impeller and a volute. In an industrial system, a multistage centrifugal pump is adopted to pressurize a medium to finish pretreatment of a process, but the multistage centrifugal pump has the advantages of large volume, long spindle, complex shape, multiple easily damaged parts, difficult maintenance and difficult axial force balance; the method is generally applied to occasions with good working conditions and no limitation on equipment places. The high-speed centrifugal pump can achieve the purposes of high lift and high pressure by increasing the rotating speed of a centrifugal rotor and increasing the circumferential size of an impeller, can achieve the efficiency of a multistage pump under the same performance, has the characteristics of compact structure, convenient maintenance and low cost, and is widely applied to the fields of petrochemical industry, sewage treatment, seawater desalination, aerospace and the like at present.
Under the urgent need of the development of the new generation of aviation technology, the requirements of aviation propulsion technology are towards high safety, high reliability, high performance, low pollution and economic affordability, wherein the design and performance analysis of a high-speed and high-pressure centrifugal pump play an important role. In the accessory of the aeroengine, the high-speed centrifugal pump can be used for conveying aerofuel, pressurizing the aerofuel and supplying the aeroengine with the fuel, so that the high-speed centrifugal pump has practical application value in analysis of the high-speed centrifugal pump.
The high-speed centrifugal pump increases the single-stage lift by increasing the rotation speed of the pump shaft to achieve the same multi-stage lift design and further reduces the size of the impeller, so that the volume of the centrifugal pump is reduced under the same flow and lift. In the aspect of high performance of a centrifugal pump in the design process, the current research is mainly focused on optimizing geometric parameters of an impeller, including the number of blades, the placement angle of a blade inlet and a blade outlet, the wrap angle, the blade molded line and the like, but only focusing on partial impeller design parameters, the aim of full-flow high efficiency cannot be completely achieved, particularly in the working condition of extremely small flow, great difficulty exists in efficiency improvement, and the high-speed centrifugal pump can have full-flow high efficiency characteristics only through matching among different parameters and joint design of the impeller and a volute.
Disclosure of Invention
In order to improve the efficiency of the high-speed centrifugal pump, the high-speed centrifugal pump still can keep high efficiency under the working condition of extremely small flow, the impeller and the volute are originally researched and developed, and the influence of main geometric parameters of the impeller and the volute on the performance of the pump is analyzed, so that the full-flow high-efficiency high-speed centrifugal pump is obtained. The invention can effectively solve the problem that the high-speed centrifugal pump keeps high efficiency under the condition of ultra-large flow span and ultra-multiple working conditions, thereby achieving the purpose of high efficiency of full flow.
A full-flow high-efficiency high-speed centrifugal pump comprises a volute and an impeller, and is characterized in that the volute and the impeller are concentrically arranged, and the diameter D of the inlet edge of the volute 2 Diameter D greater than the impeller outlet edge 1 The ratio of the two has obvious influence on the performance of the centrifugal pump, and the value range is D 2 /D 1 =1.15 to 1.25:1. suitable impeller outlet width B 1 And volute inlet width B 2 The ratio can reduce the energy loss of the centrifugal pump, and the value range is B 2 /B 1 =3 to 5:1. In the design process, the number of blades of the impeller is an important aspect of the performance improvement of the high-speed centrifugal pump. The impeller adopts a multi-blade and long-middle-short blade staggered mode, the blade number has a large influence on the lift and the working condition efficiency of small flow, and the long-middle blade number is 4-6, and the short blade number is 1-2 times of the long-middle blade number for achieving the purpose of high efficiency. The arrangement of the blades has two modes: firstly, arranging the long, middle and short three-stage staggered sequences in sequence, and calculating from a blade working surface, wherein the middle blade is arranged at 0.2S-0.4S of a long blade runner, the short blade is arranged at 0.6S-0.8S, and S is the arc length of the outlet edge of a single runner impeller of the long blade; secondly, arranging the blades according to the staggered sequence of the length, the middle and the short, and calculating from the working surface of the blade, wherein the middle blade is arranged at 0.4S-0.6S, the short blade is arranged at 0.1S-0.3S and 0.7S-0.9S, and S is the arc length of the outlet edge of the single-flow-channel impeller of the long blade. The length of the middle blade is 0.6L-0.8L of the long blade, the length of the short blade is 0.2L-0.5L of the long blade, and L is the arc length of the working surface of the long blade. The value of the blade wrap angle phi directly influences the diffusivity of the blade channel, the length and the surface area of the blade, so that the size of the flow channel diffusion loss and the blade surface friction loss is determined, and the value range is 120-160 degrees. After the area of the throat part of the volute (the IX cross section in figure 1) is enlarged, the matching performance with the impeller is improved, and as the ratio of the outlet area A1 of the impeller to the area A2 of the throat part of the volute is increased, the lift and the efficiency of the pump are both improved, and the value range of the pump is A1/A2=5.0-10.0.
The invention has the advantages that: the high-speed centrifugal pump with the structure is a full-flow high-efficiency high-speed centrifugal pump, and the design is carried out through the impeller and the volute, and the matching relation between different parameters of the volute and the impeller is explored, so that the energy loss is minimum when fluid flows from the impeller to the volute, and the purpose of high efficiency of the full-flow high-speed centrifugal pump is achieved.
Drawings
The invention is further described below with reference to the accompanying drawings.
Fig. 1 is a plan projection view of a high-speed centrifugal pump of the present invention having full-flow, high-efficiency characteristics.
FIG. 2 is a graph comparing the efficiency of a high-speed centrifugal pump with full-flow high-efficiency characteristics of the present invention.
In the figure, 1 is an impeller, 2 is a volute, 3 is a volute inlet side, 4 is an impeller outlet side, 5 is a long blade, 6 is a middle blade, and 7 is a short blade.
Detailed Description
Fig. 1 shows a plane projection view of a high-speed centrifugal pump with full-flow high-efficiency characteristic according to the invention, and as can be seen from fig. 1: the volute 2 and the impeller 1 are concentrically arranged, and the diameter D of the inlet edge 3 of the volute 2 Diameter D greater than the impeller outlet edge 4 1 The value range is D 2 /D 1 =1.22. Width B of volute inlet edge 3 2 And the width B of the impeller outlet edge 4 1 Ratio B 2 /B 1 =3.33. The blade wrap angle phi determines the magnitude of the flow path diffusion loss and the blade surface friction loss, and takes a value of 140 degrees. The ratio A1/a2=8.0 of the impeller exit area A1 to the volute throat (section IX) area A2. The number of long blades 5 and medium blades 6 is 5, and the number of short blades 7 is 10. The second type of blade stagger is: long, short (0.25 s,0.5 l), medium (0.5 s,0.7 l), short (0.75 s,0.5 l) blades are staggered. In this example, the standard working point of the centrifugal pump is q=50m 3 And/h, the rotating speed n=23000r/min, the design lift is 1425m, n s ＝42.6。
The invention starts from the original design of the impeller and the volute, and achieves the purpose of high efficiency of full flow by improving the matching characteristic of the impeller and the volute. After verification by numerical Calculation (CFD), it was found that: compared with the high-speed centrifugal pump with conventional design, the high-speed centrifugal pump with the method can effectively improve the efficiency of full flow, and as can be seen from fig. 2, the efficiency of the low-flow working condition is improved by 13%, and the efficiency of the standard working condition is improved by 10%. Therefore, the high-speed centrifugal pump with the structure provided by the invention has the characteristic of full-flow high efficiency.
Claims (1)
1. The full-flow high-efficiency high-speed centrifugal pump comprises a volute and an impeller, and is characterized in that the volute and the impeller are concentrically arranged, and the matching among different parameters of the impeller and the combined design of the impeller and the volute enable the high-speed centrifugal pump to have full-flow high-efficiency characteristics; the diameter D2 of the inlet side of the volute is larger than the diameter D1 of the outlet side of the impeller, the ratio of the diameter D2 and the diameter D1 has obvious influence on the performance of the centrifugal pump, and the value range is D 2 /D 1 =1.15 to 1.25:1, a step of; suitable impeller outlet width B 1 And volute inlet width B 2 The ratio can reduce the energy loss of the centrifugal pump, and the value range is B 2 /B 1 =3 to 5:1; the impeller adopts a multi-blade and long-middle-short blade staggered mode, the blade number has a large influence on the lift and the working condition efficiency of small flow, and the long-middle blade number is 4-6, and the short blade number is 1-2 times of the long-middle blade number for achieving the purpose of high efficiency; the arrangement of the blades has two modes: firstly, arranging the long, middle and short three-stage staggered sequences in sequence, and calculating from a blade working surface, wherein the middle blade is arranged at 0.2S-0.4S of a long blade runner, the short blade is arranged at 0.6S-0.8S, and S is the arc length of the outlet edge of a single runner impeller of the long blade; secondly, arranging the blades according to a staggered sequence of length, middle and short, and calculating from a blade working surface, wherein the middle blade is arranged at 0.4S-0.6S, the short blades are arranged at 0.1S-0.3S and 0.7S-0.9S, and S is the arc length of the outlet edge of the single-flow-channel impeller of the long blade; the length of the middle blade is 0.6L-0.8L of the long blade, the length of the short blade is 0.2L-0.5L of the long blade, and L is the arc length of the working surface of the long blade; the value of the blade wrap angle phi directly influences the diffusivity of the blade channel and the length and the surface area of the blade, so that the size of the flow channel diffusion loss and the blade surface friction loss is determined, and the value range is 120-160 degrees; after the throat area of the volute is enlarged, the matching performance with the impeller is improved, and the area A of the outlet of the impeller is increased 1 With the throat area A of the volute 2 The ratio is increased, the pump lift and efficiency are improved, and the value range is A 1 /A 2 ＝5.0～10.0。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210906619.3A CN115076156B (en) | 2022-07-29 | 2022-07-29 | Full-flow high-efficiency high-speed centrifugal pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210906619.3A CN115076156B (en) | 2022-07-29 | 2022-07-29 | Full-flow high-efficiency high-speed centrifugal pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115076156A CN115076156A (en) | 2022-09-20 |
| CN115076156B true CN115076156B (en) | 2024-03-05 |
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| CN202210906619.3A Active CN115076156B (en) | 2022-07-29 | 2022-07-29 | Full-flow high-efficiency high-speed centrifugal pump |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1528964A1 (en) * | 1988-04-05 | 1989-12-15 | А. Ю. Синенко и В. С. Смирнов | Impeller of centrifugal turbomachine |
| CN2072611U (en) * | 1990-07-20 | 1991-03-06 | 江苏工学院 | Low specific speed centrifugal pump impeller short blade offset |
| CN2265446Y (en) * | 1996-02-07 | 1997-10-22 | 浙江大学 | High-speed composite impeller centrifugal pump |
| CN2426027Y (en) * | 1999-03-13 | 2001-04-04 | 格伦德福什联合股份有限公司 | Radial structure type impeller for centrifugal pump |
| CN204419687U (en) * | 2015-01-06 | 2015-06-24 | 浙江理工大学 | A kind of centrifugal pump splitterr vanes impeller |
| CN108916109A (en) * | 2018-06-06 | 2018-11-30 | 江苏大学 | A kind of Semi-open centrifugal pump impeller and its optimum design method |
| CN111396351A (en) * | 2020-04-27 | 2020-07-10 | 西安航空学院 | Flaring-supercharging impeller of centrifugal pump with ultralow specific speed |
| CN112196832A (en) * | 2020-10-26 | 2021-01-08 | 江苏大学 | Guide vane body with flow distribution sheet |
-
2022
- 2022-07-29 CN CN202210906619.3A patent/CN115076156B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SU1528964A1 (en) * | 1988-04-05 | 1989-12-15 | А. Ю. Синенко и В. С. Смирнов | Impeller of centrifugal turbomachine |
| CN2072611U (en) * | 1990-07-20 | 1991-03-06 | 江苏工学院 | Low specific speed centrifugal pump impeller short blade offset |
| CN2265446Y (en) * | 1996-02-07 | 1997-10-22 | 浙江大学 | High-speed composite impeller centrifugal pump |
| CN2426027Y (en) * | 1999-03-13 | 2001-04-04 | 格伦德福什联合股份有限公司 | Radial structure type impeller for centrifugal pump |
| CN204419687U (en) * | 2015-01-06 | 2015-06-24 | 浙江理工大学 | A kind of centrifugal pump splitterr vanes impeller |
| CN108916109A (en) * | 2018-06-06 | 2018-11-30 | 江苏大学 | A kind of Semi-open centrifugal pump impeller and its optimum design method |
| CN111396351A (en) * | 2020-04-27 | 2020-07-10 | 西安航空学院 | Flaring-supercharging impeller of centrifugal pump with ultralow specific speed |
| CN112196832A (en) * | 2020-10-26 | 2021-01-08 | 江苏大学 | Guide vane body with flow distribution sheet |
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| CN115076156A (en) | 2022-09-20 |
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