CN111536077A - High-specific-speed double-outlet volute centrifugal pump - Google Patents
High-specific-speed double-outlet volute centrifugal pump Download PDFInfo
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- CN111536077A CN111536077A CN202010395156.XA CN202010395156A CN111536077A CN 111536077 A CN111536077 A CN 111536077A CN 202010395156 A CN202010395156 A CN 202010395156A CN 111536077 A CN111536077 A CN 111536077A
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- outlet
- impeller
- blade
- volute
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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
- F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
-
- 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
- F04D29/4293—Details of fluid inlet or outlet
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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 discloses a high-specific-speed double-outlet volute centrifugal pump, wherein an impeller is arranged at an annular opening at the inner side of a double-outlet volute, the bottom of the impeller is connected with a water suction pipeline, and two water outlets of the double-outlet volute are both connected with water outlet pipelines; the blades of the impeller adopt a similar cylindrical twisted structure, and the front surface and the back surface of each blade are smoothly connected by curved surfaces with different curvatures from top to bottom; the centers of the water suction pipeline, the impeller and the double-outlet volute are on the same axis. According to the invention, bidirectional water outlet is realized through the two water outlets, so that the outflow efficiency of the centrifugal pump is improved, the velocity component of water flow in the circumferential direction of the volute is enhanced, the water flow condition at the outlet of the volute is improved, the hydraulic loss is reduced, and the centrifugal pump has good hydraulic performance and operation efficiency.
Description
Technical Field
The invention relates to a high-specific-speed double-outlet volute centrifugal pump, and belongs to the technical field of centrifugal pumps.
Background
The main flow passage components of the centrifugal pump are an impeller and a water pumping chamber, and the water pumping chamber is gradually diffused due to the appearance of the water pumping chamber and is also called a volute. The volute is a necessary place for discharging fluid and pressurizing the fluid of the centrifugal pump, so that the hydraulic structure of the volute has a crucial influence on the efficiency of the centrifugal pump.
At present, people mainly focus on the aspects of the area and the shape of a cross section, the throat area, the mounting angle of a baffle tongue and the like in the research on the volute of the centrifugal pump, and the number of outlets of the volute is not changed and optimized according to the design so as to improve the pump efficiency.
Therefore, how to overcome the deficiencies of the prior art has become one of the key problems to be solved urgently in the technical field of centrifugal pumps of the present day.
Disclosure of Invention
The purpose is as follows: in order to overcome the defects in the prior art, the invention provides a high-specific-speed double-outlet volute centrifugal pump.
The technical scheme is as follows: in order to solve the technical problems, the technical scheme adopted by the invention is as follows:
a high-specific-speed double-outlet volute centrifugal pump comprises a double-outlet volute, wherein an impeller is arranged at an annular opening at the inner side of the double-outlet volute, the bottom of the impeller is connected with a water suction pipeline, and two water outlets of the double-outlet volute are both connected with water outlet pipelines; the blades of the impeller adopt a similar cylindrical twisted structure, and the front surface and the back surface of each blade are smoothly connected by curved surfaces with different curvatures from top to bottom; the centers of the water suction pipeline, the impeller and the double-outlet volute are on the same axis; the front surface and the back surface of the blade are arranged as follows from top to bottom according to the section airfoil curve of the curved surface:
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 50mm away from the top of the impeller is as follows:
y＝-0.72425x2+17.24068x+23.91072
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝0.00683x3-0.95369x2+18.94882x+19.35635
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 150mm away from the top of the impeller is as follows:
y＝-1.33765×10-7x4+4.63929×10-5x3-0.00788x2+0.55646x+112.20597
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝-1.36421×10-7x4+4.8806×10-5x3-0.00847x2+0.60056x+106.91616
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 250mm away from the top of the impeller is as follows:
y＝-1.3079×10-7x4+4.53574×10-5x3-0.00779x2+0.5519x+112.99371
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝-1.3285×10-7x4+4.75536×10-5x3-0.00835x2+0.59518x+107.68838
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 350mm away from the top of the impeller is as follows:
y＝-2.00056×10-6x4+5.66272×10-5x3-0.003x2+0.51281x+107.29902
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝-2.78571×10-6x4-1.36515×10-5x3-0.00192x2+0.54119x+112.37151
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 450mm away from the top of the impeller is as follows:
y＝0.14938x3+26.43681x2+1561.70207x+30844.31736
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝0.00199x3+0.23735x2+10.55235x+244.36147。
preferably, the water inlet edge of the blade extends to the inlet of the bottom of the impeller.
As a preferred scheme, the double-outlet volute casing has two water outlets in the circumferential direction, and the two water outlets are arranged in an axial symmetry manner.
Preferably, the impeller is formed in one step by adopting a casting process.
Preferably, the number of the blades is 5-8.
Preferably, the number of the blades is 6.
Preferably, the cross section of the water outlet of the double-outlet volute is a circular cross section.
Has the advantages that: according to the high-specific-speed double-outlet volute centrifugal pump provided by the invention, the centrifugal pump is provided with the double-outlet volute, bidirectional water outlet is realized through the two water outlets, the outflow efficiency of the centrifugal pump is improved, the velocity component of water flow in the circumferential direction of the volute is enhanced, the water flow condition at the outlet of the volute is improved, the hydraulic loss is reduced, and the centrifugal pump has good hydraulic performance and operation efficiency.
Drawings
Fig. 1 is a schematic structural diagram of a high specific speed dual-outlet volute centrifugal pump provided by the invention.
Fig. 2 is a front three-axis view of a single blade as proposed by the present invention.
Fig. 3 is a top view of a single blade according to the present invention.
Fig. 4 is a schematic view of airfoil curves on the proposed blade at different axial distances from the impeller tip.
Fig. 5 is a front view of the impeller proposed by the present invention.
Fig. 6 is a schematic structural diagram of a plurality of blades in the impeller provided by the invention.
Detailed Description
The present invention will be further described with reference to the accompanying drawings.
As shown in fig. 1, the high specific speed double-outlet volute centrifugal pump sequentially comprises a water suction pipeline 1, an impeller 2, a double-outlet volute 3 and a water outlet pipeline 4 according to the water flow direction, wherein the impeller 2 is arranged at an annular opening at the inner side of the double-outlet volute 3, the bottom of the impeller 2 is connected with the water suction pipeline 1, and two water outlets of the double-outlet volute 3 are connected with the water outlet pipeline 4.
As shown in fig. 2-4, the blades of the impeller 2 adopt a cylindrical-like twisted structure, the front surface and the back surface of the blade 201 are smoothly connected by curved surfaces with different curvatures from top to bottom, and the section airfoil curves of the curved surfaces of the front surface and the back surface of the blade 201 from top to bottom are set as follows:
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at a distance of 50mm from the top of the impeller 2 are shown in table 1.
TABLE 1
The two curves fitted are respectively represented as:
the front side of the blade is as follows:
y＝-0.72425x2+17.24068x+23.91072
the reverse side of the blade:
y＝0.00683x3-0.95369x2+18.94882x+19.35635
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at a distance of 150mm from the top of the impeller 2 are shown in table 2.
TABLE 2
The two curves fitted are respectively represented as:
the front side of the blade is as follows:
y＝-1.33765×10-7x4+4.63929×10-5x3-0.00788x2+0.55646x+112.20597
the reverse side of the blade:
y＝-1.36421×10-7x4+4.8806×10-5x3-0.00847x2+0.60056x+106.91616
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 250mm from the top of the impeller 2 are shown in table 3.
TABLE 3
The two curves fitted can be represented as:
the front side of the blade is as follows:
y＝-1.3079×10-7x4+4.53574×10-5x3-0.00779x2+0.5519x+112.99371
the reverse side of the blade:
y＝-1.3285×10-7x4+4.75536×10-5x3-0.00835x2+0.59518x+107.68838
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 350mm from the top of the impeller 2 are shown in table 4.
TABLE 4
The two curves fitted are respectively represented as:
the front side of the blade is as follows:
y＝-2.00056×10-6x4+5.66272×10-5x3-0.003x2+0.51281x+107.29902
the reverse side of the blade:
y＝-2.78571×10-6x4-1.36515×10-5x3-0.00192x2+0.54119x+112.37151
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 450mm from the top of the impeller 2 are shown in table 5.
TABLE 5
The two curves fitted are respectively represented as:
the front side of the blade is as follows:
y＝0.14938x3+26.43681x2+1561.70207x+30844.31736
the reverse side of the blade:
y＝0.00199x3+0.23735x2+10.55235x+244.36147
as shown in fig. 5-6, the impeller 2 has 5-8 blades, and the water inlet edge of the blade extends to the inlet at the bottom of the impeller 2 to improve cavitation performance.
The centers of the water suction pipeline 1, the impeller 2 and the double-outlet volute 3 are on the same axis.
The double-outlet volute 3 is provided with two water outlets in the circumferential direction, the two water outlets are arranged in an axial symmetry mode, and the impeller is formed in one step through a casting process.
Example 1:
the centrifugal pump is optimally designed, the rated flow of the pump is 367m3/h, the lift is 25m, and the specific speed is 208.
The optimized parameters of the invention are as follows: the diameter of the inlet at the bottom of the impeller is 1700mm, the diameter of the outlet at the top of the impeller is 4100mm, and the outer diameter of the double-outlet volute is 4160 mm. The cross section of the water outlet of the double-outlet volute is a circular cross section with the diameter of 1700mm and is directly communicated with a water outlet pipeline. The number of the blades of the impeller is 6, and the blades adopt a cylindrical-like equal-thickness twisted structure.
Example 2:
the optimized parameters of the invention are as follows: the diameter of the inlet at the bottom of the impeller is 1700mm, the diameter of the outlet at the top of the impeller is 4100mm, and the outer diameter of the double-outlet volute is 4160 mm. The cross section of the water outlet of the double-outlet volute is a circular cross section with the diameter of 1700mm and is directly communicated with a water outlet pipeline. The number of the blades of the impeller is 8, and the blades adopt a cylindrical-like equal-thickness twisted structure.
Example 3:
the specific application process of the invention is as follows: the pump body of the centrifugal pump and the water suction pipeline 1 are filled with water, the motor drives the impeller 2 to rotate, water among blades in the impeller starts to rotate, and the water is thrown to the outer edge of the impeller from the center of the impeller 2 and is discharged from the two water outlets at higher pressure. Meanwhile, due to the action of pressure difference, the impeller 2 rotates continuously, and liquid continuously enters from the water suction pipeline 1 and flows out from the water outlet pipeline 4 through the double-outlet volute 3.
Descriptions not related to the embodiments of the present invention are well known in the art, and may be implemented by referring to the well-known techniques.
The above description is only of the preferred embodiments of the present invention, and it should be noted that: it will be apparent to those skilled in the art that various modifications and adaptations can be made without departing from the principles of the invention and these are intended to be within the scope of the invention.
Claims (7)
1. The utility model provides a high specific speed double outlet formula spiral case centrifugal pump which characterized in that: the water-saving device comprises a double-outlet volute, wherein an impeller is arranged at an annular opening at the inner side of the double-outlet volute, the bottom of the impeller is connected with a water suction pipeline, and two water outlets of the double-outlet volute are both connected with a water outlet pipeline; the blades of the impeller adopt a similar cylindrical twisted structure, and the front surface and the back surface of each blade are smoothly connected by curved surfaces with different curvatures from top to bottom; the centers of the water suction pipeline, the impeller and the double-outlet volute are on the same axis; the front surface and the back surface of the blade are arranged as follows from top to bottom according to the section airfoil curve of the curved surface:
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 50mm away from the top of the impeller is as follows:
y＝-0.72425x2+17.24068x+23.91072
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝0.00683x3-0.95369x2+18.94882x+19.35635
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 150mm away from the top of the impeller is as follows:
y＝-1.33765×10-7x4+4.63929×10-5x3-0.00788x2+0.55646x+112.20597
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝-1.36421×10-7x4+4.8806×10-5x3-0.00847x2+0.60056x+106.91616
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 250mm away from the top of the impeller is as follows:
y＝-1.3079×10-7x4+4.53574×10-5x3-0.00779x2+0.5519x+112.99371
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝-1.3285×10-7x4+4.75536×10-5x3-0.00835x2+0.59518x+107.68838
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 350mm away from the top of the impeller is as follows:
y＝-2.00056×10-6x4+5.66272×10-5x3-0.003x2+0.51281x+107.29902
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝-2.78571×10-6x4-1.36515×10-5x3-0.00192x2+0.54119x+112.37151
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 450mm away from the top of the impeller is as follows:
y＝0.14938x3+26.43681x2+1561.70207x+30844.31736
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝0.00199x3+0.23735x2+10.55235x+244.36147。
2. a high specific speed, dual outlet, volute centrifugal pump as claimed in claim 1, wherein: the water inlet edge of the blade extends to the inlet of the bottom of the impeller.
3. A high specific speed, dual outlet, volute centrifugal pump as claimed in claim 1, wherein: the double-outlet volute casing is provided with two water outlets in the circumferential direction, and the two water outlets are arranged in an axial symmetry manner.
4. A high specific speed, dual outlet, volute centrifugal pump as claimed in claim 1, wherein: the impeller is formed in one step by adopting a casting process.
5. A high specific speed, dual outlet, volute centrifugal pump as claimed in claim 1, wherein: the number of the blades is 5-8.
6. A high specific speed, dual outlet, volute centrifugal pump as claimed in claim 5, wherein: the number of the blades is 6.
7. A high specific speed, dual outlet, volute centrifugal pump as claimed in claim 1, wherein: the cross section of the water outlet of the double-outlet volute is a circular cross section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010395156.XA CN111536077A (en) | 2020-05-11 | 2020-05-11 | High-specific-speed double-outlet volute centrifugal pump |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010395156.XA CN111536077A (en) | 2020-05-11 | 2020-05-11 | High-specific-speed double-outlet volute centrifugal pump |
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| CN111536077A true CN111536077A (en) | 2020-08-14 |
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| CN202010395156.XA Pending CN111536077A (en) | 2020-05-11 | 2020-05-11 | High-specific-speed double-outlet volute centrifugal pump |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6082000A (en) * | 1997-03-14 | 2000-07-04 | Dab Pumps S.P.A. | Method for producing an impeller for turbine pumps provided with vanes having an improved profile |
| CN101881282A (en) * | 2009-05-08 | 2010-11-10 | 通用汽车环球科技运作公司 | Centrifugal fluid pump |
| CN104776050A (en) * | 2015-03-25 | 2015-07-15 | 中国计量学院 | Impeller and volute chamber guide device in double-suction centrifugal pump |
| CN107503978A (en) * | 2017-09-19 | 2017-12-22 | 河海大学 | A kind of high-lift higher specific speed mixed-flow pump |
| CN108626130A (en) * | 2018-03-01 | 2018-10-09 | 江苏大学 | A kind of high-temperature melting salt pump of the double outlet double volute pump bodies of band |
| CN209959477U (en) * | 2019-04-23 | 2020-01-17 | 大连耐酸泵技术开发公司 | High-temperature-resistant double-outlet type single-stage submerged pump |
-
2020
- 2020-05-11 CN CN202010395156.XA patent/CN111536077A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6082000A (en) * | 1997-03-14 | 2000-07-04 | Dab Pumps S.P.A. | Method for producing an impeller for turbine pumps provided with vanes having an improved profile |
| CN101881282A (en) * | 2009-05-08 | 2010-11-10 | 通用汽车环球科技运作公司 | Centrifugal fluid pump |
| CN104776050A (en) * | 2015-03-25 | 2015-07-15 | 中国计量学院 | Impeller and volute chamber guide device in double-suction centrifugal pump |
| CN107503978A (en) * | 2017-09-19 | 2017-12-22 | 河海大学 | A kind of high-lift higher specific speed mixed-flow pump |
| CN108626130A (en) * | 2018-03-01 | 2018-10-09 | 江苏大学 | A kind of high-temperature melting salt pump of the double outlet double volute pump bodies of band |
| CN209959477U (en) * | 2019-04-23 | 2020-01-17 | 大连耐酸泵技术开发公司 | High-temperature-resistant double-outlet type single-stage submerged pump |
Non-Patent Citations (1)
| Title |
|---|
| 离心式与轴流式水泵编写组: "《离心式与轴流式水泵》", 30 September 1980 * |
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Application publication date: 20200814 |