CN111577661A - High-specific-speed double-outlet volute pump - Google Patents
High-specific-speed double-outlet volute pump Download PDFInfo
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- CN111577661A CN111577661A CN202010394833.6A CN202010394833A CN111577661A CN 111577661 A CN111577661 A CN 111577661A CN 202010394833 A CN202010394833 A CN 202010394833A CN 111577661 A CN111577661 A CN 111577661A
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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
-
- 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)
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- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a high specific speed double-outlet volute pump, wherein a circle of guide plate is arranged in an annular opening on the inner side of a double-outlet volute, an impeller is sleeved at the annular opening on the inner side of the double-outlet volute, and the bottom of the impeller is connected with one end of a water suction pipeline; the blades in the impeller are of a backward bending structure, the water inlet edges of the blades extend to the opening at the bottom of the impeller, two water flow outlets are formed in the double-outlet volute in the circumferential direction, and the two water flow outlets are arranged in a centrosymmetric manner; the front surface and the back surface of the blade are smoothly connected by curved surfaces with different curvatures from top to bottom. According to the high-specific-speed double-outlet volute pump provided by the invention, bidirectional water outlet is realized through the two water outlets, the outflow efficiency of the 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 pump is improved, the hydraulic loss is reduced, and the high-specific-speed volute pump has good hydraulic performance and operation efficiency.
Description
Technical Field
The invention relates to a high-specific-speed double-outlet volute pump, and belongs to the technical field of volute pumps.
Background
A pump is a machine that delivers or pressurizes a fluid, and transfers mechanical energy of a prime mover or other external energy to the fluid, causing the fluid to be energized. The main flow-through components of a volute pump are the impeller and the volute. The hydraulic structure of the volute has a crucial influence on the efficiency of the 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 a volute casing pump, and the number of outlets of the volute casing 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 in the field of volute pump technology.
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 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 dual outlet volute pump comprising: the double-outlet volute is internally provided with a circle of guide plates in an inner annular opening, an impeller is sleeved at the inner annular opening of the double-outlet volute, and the bottom of the impeller is connected with one end of a water suction pipeline; the blades in the impeller are of a backward bending structure, the water inlet edges of the blades extend to the opening at the bottom of the impeller, two water flow outlets are formed in the double-outlet volute in the circumferential direction, and the two water flow outlets are arranged in a centrosymmetric manner; the front and the reverse side of the blade 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 and the reverse side from top to bottom are arranged as follows:
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 15mm away from the top of the impeller is as follows:
y＝2.61555×10-8x4-8.51259×10-6x3+0.00577x2-0.71953x-75.07373
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝-4.57625×10-7x3+0.00467x2-0.6473x-81.43915
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 30mm away from the top of the impeller is as follows:
y＝1.09978×10-7x4-4.16007×10-5x3+0.01003x2-0.87744x-78.82072
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝1.40553×10-7x4-5.06813×10-5x3+0.01049x2-0.84968x-84.77746
at a position 45mm away from the top of the impeller, the section airfoil curve formula of the curved surface of the front surface of the blade is as follows:
y＝2.08824×10-7x4-7.39163×10-5x3+0.01304x2-0.88989x-87.03325
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝2.49715×10-7x4-8.36911×10-5x3+0.01322x2-0.8378x-92.95376
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 60mm away from the top of the impeller is as follows:
y＝2.30725×10-7x4-7.73996×10-5x3+0.01261x2-0.76462x-96.62722
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝2.23657×10-7x4-7.23222×10-5x3+0.01152x2-0.70003x-101.44047
the section airfoil curve formula of the curved surface of the front surface of the blade at a position 75mm away from the top of the impeller is as follows:
y＝5.32771×10-7x4-1.06481×10-4x3+0.01064x2-0.53256x-106.23393
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝5.66414×10-7x4-9.96469×10-5x3+0.00936x2-0.49696x-110.24512
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 90mm away from the top of the impeller is as follows:
y＝8.68176×10-7x4-8.57193×10-5x3+0.0069x2-0.41865x-115.50897
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝1.42812×10-6x4-7.15625×10-5x3+0.00488x2-0.41897x-119.36017
the section airfoil curve formula of the curved surface of the front surface of the blade at a position 105mm away from the top of the impeller is as follows:
y＝4.24072×10-6x4+2.75651×10-4x3+0.01273x2-0.39778x-128.87463
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝4.18704×10-6x4+2.86796×10-6x3+0.01379x2-0.33735x-133.4376。
preferably, the number of the blades of the impeller is 4-8.
Preferably, the backward bending angle theta of the blade is set to be 35-45 degrees.
Preferably, the blade backward bending angle θ is set to 40 °.
As the preferred scheme, 6-8 guide plates are uniformly distributed in the inner side annular opening of the double-outlet type volute.
As a preferred scheme, 8 guide plates are uniformly distributed in an inner side annular opening of the double-outlet type volute.
Preferably, the cross section of the water flow outlet of the double-outlet volute is a circular cross section.
Preferably, the centers of the water suction pipeline, the impeller, the guide plate and the double-outlet volute are on the same axis.
Has the advantages that: according to the high-specific-speed double-outlet volute pump provided by the invention, bidirectional water outlet is realized through the two water outlets, the outflow efficiency of the 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 pump is improved, the hydraulic loss is reduced, and the high-specific-speed volute pump has good hydraulic performance and operation efficiency.
Drawings
Fig. 1 is a schematic structural diagram of a high specific speed dual-outlet volute pump according to the present invention.
Fig. 2 is a plan view of a plurality of blades in the impeller according to the present invention.
Fig. 3 is a front view of a plurality of blades in the impeller according to the present invention.
Fig. 4 is a schematic cross-sectional view of a dual outlet volute according to the present invention.
Fig. 5 is a schematic structural diagram of a blade backward bending structure according to the present invention.
Fig. 6 is a schematic view of airfoil curves on the proposed blade at different distances from the top of the impeller.
Detailed Description
The present invention will be further described with reference to the accompanying drawings.
As shown in fig. 1-3, the high specific speed dual-outlet volute pump provided by the invention sequentially comprises a water suction pipeline 1, an impeller 2, a guide plate 3 and a dual-outlet volute 4 according to the water flow direction, wherein a circle of guide plate 3 is arranged in an annular opening at the inner side of the dual-outlet volute 4, the impeller 2 is sleeved at the annular opening at the inner side of the dual-outlet volute 4, and the bottom of the impeller 2 is connected with one end of the water suction pipeline 1; the blades 201 in the impeller 2 are of a backward bending structure, and the water inlet edges of the blades extend to the opening at the bottom of the impeller 2 to improve the cavitation performance.
As shown in fig. 4, the water flow outlet of the dual outlet volute 4 has a circular cross section.
6-8 guide plates are uniformly distributed in an inner annular opening of the double-outlet volute 4.
The centers of the water suction pipeline 1, the impeller 2, the guide plate 3 and the double-outlet type volute 4 are on the same axis, the double-outlet type volute 4 has two water outlets in the circumferential direction, and the two water outlets are arranged in a central symmetry manner.
As shown in fig. 5, the backward bending angle θ of the vane 201 is set to 35 ° to 45 °, which is used to effectively ensure the contact area of the vane with the liquid and improve the radial thrust.
As shown in fig. 6, the front surface and the back surface of the blade 201 are smoothly connected from top to bottom by curved surfaces with different curvatures, 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 15mm 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＝2.61555×10-8x4-8.51259×10-6x3+0.00577x2-0.71953x-75.07373
the reverse side of the blade:
y＝-4.57625×10-7x3+0.00467x2-0.6473x-81.43915
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 30mm 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＝1.09978×10-7x4-4.16007×10-5x3+0.01003x2-0.87744x-78.82072
the reverse side of the blade:
y＝1.40553×10-7x4-5.06813×10-5x3+0.01049x2-0.84968x-84.77746
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 45mm from the top of the impeller 2 are shown in table 3.
TABLE 3
The two curves fitted are respectively represented as:
the front side of the blade is as follows:
y＝2.08824×10-7x4-7.39163×10-5x3+0.01304x2-0.88989x-87.03325
the reverse side of the blade:
y＝2.49715×10-7x4-8.36911×10-5x3+0.01322x2-0.8378x-92.95376
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 60mm 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＝2.30725×10-7x4-7.73996×10-5x3+0.01261x2-0.76462x-96.62722
the reverse side of the blade:
y＝2.23657×10-7x4-7.23222×10-5x3+0.01152x2-0.70003x-101.44047
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 75mm 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＝5.32771×10-7x4-1.06481×10-4x3+0.01064x2-0.53256x-106.23393
the reverse side of the blade:
y＝5.66414×10-7x4-9.96469×10-5x3+0.00936x2-0.49696x-110.24512
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 90mm from the top of the impeller 2 are shown in table 6.
TABLE 6
The two curves fitted are respectively represented as:
the front side of the blade is as follows:
y＝8.68176×10-7x4-8.57193×10-5x3+0.0069x2-0.41865x-115.50897
the reverse side of the blade:
y＝1.42812×10-6x4-7.15625×10-5x3+0.00488x2-0.41897x-119.36017
the values of the point coordinates on the airfoil curves of the front and back sections of the blade 201 at 105mm from the top of the impeller 2 are shown in table 7.
TABLE 7
The two curves fitted are respectively represented as:
the front side of the blade is as follows:
y＝4.24072×10-6x4+2.75651×10-4x3+0.01273x2-0.39778x-128.87463
the reverse side of the blade:
y＝4.18704×10-6x4+2.86796×10-6x3+0.01379x2-0.33735x-133.4376
the number of the blades 201 of the impeller 2 is 4-8.
Example 1:
optimally designing a pump, wherein the design head of the pump is 32.2m, and the design flow is 398m3The specific speed is 179.5.
The optimized parameters of the invention are as follows: the diameter of the inlet at the bottom of the impeller is 250mm, the diameter of the outlet at the top of the impeller is 355mm, the number of blades of the impeller is 5, the blades of the impeller adopt a backward bending type non-uniform thickness twisting structure, and the backward bending angle is 45 degrees. 8 guide plates are arranged at the water inlet of the volute, and the cross section of the water flow outlet of the double-outlet volute is a circular cross section with the diameter of 350mm and is directly communicated with a water outlet pipeline.
Example 2:
the specific application process of the invention is as follows: the pump body 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 two water outlets through the volute 4.
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 (8)
1. A high specific speed double-outlet volute pump is characterized in that: the method comprises the following steps: the double-outlet volute is internally provided with a circle of guide plates in an inner annular opening, an impeller is sleeved at the inner annular opening of the double-outlet volute, and the bottom of the impeller is connected with one end of a water suction pipeline; the blades in the impeller are of a backward bending structure, the water inlet edges of the blades extend to the opening at the bottom of the impeller, two water flow outlets are formed in the double-outlet volute in the circumferential direction, and the two water flow outlets are arranged in a centrosymmetric manner; the front and the reverse side of the blade 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 and the reverse side from top to bottom are arranged as follows:
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 15mm away from the top of the impeller is as follows:
y＝2.61555×10-8x4-8.51259×10-6x3+0.00577x2-0.71953x-75.07373
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝-4.57625×10-7x3+0.00467x2-0.6473x-81.43915
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 30mm away from the top of the impeller is as follows:
y＝1.09978×10-7x4-4.16007×10-5x3+0.01003x2-0.87744x-78.82072
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝1.40553×10-7x4-5.06813×10-5x3+0.01049x2-0.84968x-84.77746
at a position 45mm away from the top of the impeller, the section airfoil curve formula of the curved surface of the front surface of the blade is as follows:
y＝2.08824×10-7x4-7.39163×10-5x3+0.01304x2-0.88989x-87.03325
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝2.49715×10-7x4-8.36911×10-5x3+0.01322x2-0.8378x-92.95376
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 60mm away from the top of the impeller is as follows:
y＝2.30725×10-7x4-7.73996×10-5x3+0.01261x2-0.76462x-96.62722
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝2.23657×10-7x4-7.23222×10-5x3+0.01152x2-0.70003x-101.44047
the section airfoil curve formula of the curved surface of the front surface of the blade at a position 75mm away from the top of the impeller is as follows:
y＝5.32771×10-7x4-1.06481×10-4x3+0.01064x2-0.53256x-106.23393
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝5.66414×10-7x4-9.96469×10-5x3+0.00936x2-0.49696x-110.24512
the section airfoil curve formula of the curved surface of the front surface of the blade at the position 90mm away from the top of the impeller is as follows:
y＝8.68176×10-7x4-8.57193×10-5x3+0.0069x2-0.41865x-115.50897
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝1.42812×10-6x4-7.15625×10-5x3+0.00488x2-0.41897x-119.36017
the section airfoil curve formula of the curved surface of the front surface of the blade at a position 105mm away from the top of the impeller is as follows:
y＝4.24072×10-6x4+2.75651×10-4x3+0.01273x2-0.39778x-128.87463
the section airfoil curve formula of the curved surface of the reverse surface of the blade is as follows:
y＝4.18704×10-6x4+2.86796×10-6x3+0.01379x2-0.33735x-133.4376。
2. a high specific speed dual outlet volute pump as defined in claim 1 wherein: the number of the blades of the impeller is 4-8.
3. A high specific speed dual outlet volute pump as defined in claim 1 wherein: the backward bending angle theta of the blade is set to be 35-45 degrees.
4. A high specific speed dual outlet volute pump as defined in claim 3 wherein: the blade back bend angle theta is set to 40 deg..
5. A high specific speed dual outlet volute pump as defined in claim 1 wherein: 6-8 guide plates are uniformly distributed in the annular opening at the inner side of the double-outlet volute.
6. The high specific speed dual outlet volute pump of claim 5, wherein: 8 guide plates are uniformly distributed in the inner side annular opening of the double-outlet volute.
7. A high specific speed dual outlet volute pump as defined in claim 1 wherein: the cross section of the water flow outlet of the double-outlet volute is a circular cross section.
8. A high specific speed dual outlet volute pump as defined in claim 1 wherein: the centers of the water suction pipeline, the impeller, the guide plate and the double-outlet volute are on the same axis.
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| CN202010394833.6A CN111577661A (en) | 2020-05-11 | 2020-05-11 | High-specific-speed double-outlet volute pump |
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Citations (6)
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|---|---|---|---|---|
| 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 CN202010394833.6A patent/CN111577661A/en active Pending
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| 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: 20200825 |