CN116066400A - Impeller with maximum lift and maximum diameter and multistage pump - Google Patents
Impeller with maximum lift and maximum diameter and multistage pump Download PDFInfo
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- CN116066400A CN116066400A CN202211464681.8A CN202211464681A CN116066400A CN 116066400 A CN116066400 A CN 116066400A CN 202211464681 A CN202211464681 A CN 202211464681A CN 116066400 A CN116066400 A CN 116066400A
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- 238000000034 method Methods 0.000 claims abstract description 7
- 238000010586 diagram Methods 0.000 claims description 4
- 238000000605 extraction Methods 0.000 abstract description 2
- 239000012530 fluid Substances 0.000 abstract description 2
- 238000005065 mining Methods 0.000 abstract 1
- 238000010992 reflux Methods 0.000 abstract 1
- 238000010008 shearing Methods 0.000 abstract 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract 1
- 238000004088 simulation Methods 0.000 description 6
- 239000003054 catalyst Substances 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 3
- 238000005259 measurement Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000004364 calculation method Methods 0.000 description 2
- 238000011056 performance test Methods 0.000 description 2
- 238000004422 calculation algorithm Methods 0.000 description 1
- 238000013135 deep learning Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000013505 freshwater Substances 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 230000002068 genetic effect Effects 0.000 description 1
- 239000003673 groundwater Substances 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
- 238000007789 sealing Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000012795 verification Methods 0.000 description 1
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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
- F04D29/24—Vanes
- F04D29/242—Geometry, shape
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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
- F04D1/06—Multi-stage pumps
Abstract
The invention belongs to the field of fluid machinery, and discloses an impeller with a maximum lift and a maximum diameter and a multistage pump. Due to deep well oil extraction the working environments such as mining, water lifting and the like severely limit the maximum diameter of the multistage pump, the single-stage lift is lower, so that the pump stage number is increased, and the operation stability and the application cost are seriously affected. The invention extends the outlets of the blades of the common impeller and uses two sections of straight line sections to perform rotary shearing, increases the working process of the blades of the impeller on the medium, improves the pressure difference between an inlet and an outlet, guides the medium to flow to the next stage of guide vane, further improves the medium flow state of the outlet of the impeller, reduces secondary reflux, and effectively solves the problems of excessive number of stages of the multistage pump and even poor stability of a long axis system caused by the limitation of the well diameter.
Description
Technical Field
The invention belongs to in the field of fluid machines, in particular to an impeller with maximum lift and maximum diameter and a multistage pump with the impeller.
Background
The lack of fresh water resources and the utilization of groundwater resources are greatly concerned by society; expanding deep layer the oil gas resource is used for the oil gas, has important practical and strategic significance for building the resource foundation of energy safety in China. The multistage pump is used as the core power source equipment for resource exploitation, the working environment is generally a deep well buried underground, and the well diameter is not suitable to be excavated too much in order to save cost because the well cost is in direct proportion to the well diameter (well diameter for short). The impeller exit diameter is a critical factor affecting the pump head, and under limited well diameter conditions, the maximum impeller exit diameter is tightly defined. In addition to the impeller outlet diameter affecting the pump head of the multistage pump, the impeller blade number, the blade outlet width, the blade shape, etc. are also key factors affecting the pump head. At present, many optimization design methods aiming at the multistage pump and aiming at improving the lift are adopted, such as genetic algorithm, deep learning and the like, to find the optimal matching of key parameters so as to obtain an optimal model. Therefore, on the basis of the optimal model, under the condition that each parameter of the impeller is determined, how to further improve the pump lift of the multistage pump and reduce the engineering cost are of great significance.
Disclosure of Invention
The invention aims at the defects and the problems and provides an impeller with a maximum lift and a maximum diameter and a multistage pump with the impeller. The impeller further improves the lift of the multistage pump and effectively reduces the application cost on the basis of adopting the maximum outlet diameter and ensuring that the efficiency is not obviously changed.
The technical scheme adopted by the invention is as follows:
an impeller with maximum lift and maximum diameter comprises a front cover plate, a rear cover plate, blades, a balance disc, a hub, balance holes and a mouth ring seal, wherein the specific rotation speed range of the impeller is 80<n s <800，
The front cover plate is divided into a front cover plate inner wall surface and a front cover plate outer wall surface, and the included angle between the front cover plate inner wall surface and the rotating shaft of the impeller is theta 1 The value range is 60 DEG<θ 1 <90°。
The thickness of the front cover plate is t 1 The value range is not less than 2mm and not more than t 1 ≤5mm。
The back cover plate is divided into an inner wall surface of the back cover plate and an outer wall surface of the back cover plate, and an included angle between the inner wall surface of the back cover plate and a rotating shaft of the impeller is theta 2 The value range is 60 DEG<θ 2 <90°。
The thickness of the rear cover plate is t 2 The value range is not less than 2mm and not more than t 2 ≤5mm。
The included angle between the inner wall surface of the front cover plate and the inner wall surface of the rear cover plate is theta 3 The value range is-2 degrees less than or equal to theta 3 ≤2°。
The maximum diameter of the front cover plate is D q The maximum diameter of the rear cover plate is D h Both of the sizes are D q <D h . The connecting line of the maximum diameter positions of the front cover plate and the rear cover plate is the projection line of the common impeller blade outlet on the axial plane projection graph, wherein the included angle between the projection line of the common impeller blade outlet on the axial plane projection graph and the straight line parallel to the impeller rotation shaft is alpha 1 The value range is 0 DEG<α 1 Less than or equal to 40 degrees; the included angle between the projection line of the blade outlet of the common impeller on the axial plane projection diagram and the straight line perpendicular to the rotation axis of the impeller is beta 1 The value range is 50 degrees less than or equal to beta 1 <90°。
The blades are cylindrical blades or twisted blades, the number of the blades is Z, and the value range of the blades is more than or equal to 5 and less than or equal to 9.
Wherein, cylinder blade and distortion blade all contain blade inlet limit and blade outlet limit.
The axial plane projection of the inlet edge of the blade is a single spline curve or a straight line.
The axial projection of the blade outlet edge is composed of two straight line segments, wherein the included angle between the front straight line segment and the straight line parallel to the impeller rotation axis is alpha 2 The value range is 1/3 alpha 1 ≤α 2 ≤2/3α 1 The method comprises the steps of carrying out a first treatment on the surface of the The included angle between the rear straight line segment and the straight line perpendicular to the rotation axis of the impeller is beta 2 The value range is 1/3 beta 1 ≤β 2 ≤2/3β 1 。
The circumference of the balance hole is uniformly distributed near the inlet edge of the blade, the cross section is circular, the number of the balance holes is K, the value of the balance holes is K=Z, and the diameter of the circular cross section is D k The value range is not less than 1mm and not more than D k ≤5mm。
The balance disc is in a circular ring shape, the ring width is w, and the value range of the balance disc is more than or equal to 3mm and less than or equal to 5mm. The balance disc is arranged on the outer wall surface of the rear cover plate and integrally processed with the rear cover plate.
The mouth ring is arranged on the outer wall surface of the front cover plate in a sealing way and integrally processed with the front cover plate.
The invention relates to a multistage pump, which is provided with impellers with maximum lift and maximum diameter, wherein the impellers and guide vanes are alternately matched end to form the multistage pump with the impellers with the maximum lift and the maximum diameter.
Compared with the prior art, the invention has the beneficial effects that:
compared with a common impeller, the vane length of the invention is increased, the work applied to media in the multistage pump is increased, and the inlet-outlet pressure difference of the multistage pump is effectively improved. The increased length of the blades not only effectively improves the lift, but also is beneficial to guiding the medium to flow to the next stage guide vane, has a certain improvement effect on the medium flow state at the outlet of the impeller, and reduces secondary backflow. Therefore, the invention can not only improve the lift of the multistage pump, but also improve the flow state of the impeller outlet.
Drawings
Fig. 1 is a two-dimensional schematic view of an axial section of an embodiment of an impeller with a maximum head diameter according to the present invention.
Figure 2 is a three-dimensional cross-sectional view of an embodiment of an impeller of the present invention having a maximum head maximum diameter.
Fig. 3 is a top view of an embodiment of an impeller with a maximum head diameter according to the present invention.
FIG. 4 multistage pump performance test bench.
Fig. 5 is a graph comparing numerical simulation and experimental data.
Fig. 6 head versus curve.
FIG. 7 illustrates a mid-section velocity, streamline profile for an impeller and vane, a-invention, b-invention.
Reference numerals illustrate:
1-front cover plate, 2-mouth ring seal, 3-blade, 4-hub, 5-blade outlet edge, 6-balance disc, 7-back cover plate, 8-front straight line segment, 9-back straight line segment, 10-projection line of general impeller blade outlet on axial plane projection drawing, 11-straight line parallel to impeller rotation axis, 12-straight line perpendicular to impeller rotation axis, 13-balance hole, 111-front cover plate inner wall surface, 112-front cover plate outer wall surface, 711-back cover plate inner wall surface, 712-back cover plate outer wall surface, 31-blade inlet edge.
Detailed Description
The invention will be described in further detail with reference to the drawings and the detailed description, but the scope of the invention is not limited thereto.
The design parameters of the impeller of the specific embodiment are respectively as follows: flow q=40m 3 and/H, designing the rotating speed n=2917 r/min, and the lift H=11.7m. Thus, the specific rotation speed
As shown in figure 1 of the drawings, the impeller structure comprises a front cover plate 1, a rear cover plate 7, blades 3, a balance disc 6, a hub 4, balance holes 13 and a mouth ring seal 2.
The front cover plate 1 is divided into a front cover plate inner wall surface 111 and a front cover plate outer wall surface 112, and the included angle between the front cover plate inner wall surface 111 and the rotation axis of the impeller is theta 1 The value of the catalyst is theta 1 ＝64°。
The thickness of the front cover plate 1 is t 1 The value of it is t 1 ＝2mm。
The back cover plate 7 is divided into a back cover plate inner wall surface 711 and a back cover plate outer wall surface 712, and the included angle between the back cover plate inner wall surface 711 and the rotation axis of the impeller is theta 2 The value of the catalyst is theta 2 ＝62°。
The thickness of the rear cover plate is t 2 The value of it is t 2 ＝2mm。
The included angle between the inner wall surface 111 of the front cover plate and the inner wall surface 711 of the rear cover plate is theta 3 The value of the catalyst is theta 3 ＝2°。
As shown in FIG. 2, aMaximum diameter D of the front cover plate 1 q =109.5mm, maximum diameter D of back cover 7 h =92.5mm. The line of the maximum diameter positions of the front cover plate 1 and the rear cover plate 7, namely the projection line 10 of the common impeller blade outlet on the axial plane projection diagram, and the included angle between the projection line 10 of the common impeller blade outlet on the axial plane projection diagram and the straight line 11 parallel to the impeller rotation axis is alpha 1 The value alpha is 1 =32°; the angle between the projection line 10 of the blade outlet of the common impeller on the axial plane projection and the straight line 12 perpendicular to the rotation axis of the impeller is beta 1 Take on the value beta 1 ＝58°。
The blades 3 are twisted blades, the number of the blades is Z, and the value Z=8.
The twisted vane 3 comprises a vane inlet edge 31 and a vane outlet edge 5.
The blade inlet edge 31 is shown as a single straight line in axial projection.
The axial projection of the blade outlet edge 5 is composed of two straight line segments, wherein the included angle between the front straight line segment 8 and the straight line 11 parallel to the rotation axis of the impeller is alpha 2 The value alpha is 2 =15°; the included angle between the rear straight line section 9 and the straight line 12 perpendicular to the rotation axis of the impeller is beta 2 Take on the value beta 2 ＝31°。
As shown in fig. 3, the balancing holes 13 are uniformly distributed around the inlet edge 31 of the blade, the cross section is circular, the number is K, the value k=8, and the diameter of the circular cross section is D k The value D k ＝3mm。
The balance disc 6 is in a circular ring shape, the ring width is w, and the value w=4mm. The balance disc 6 is arranged on the outer wall surface 712 of the back cover plate and is integrally processed with the back cover plate 7.
The mouth ring seal 2 is arranged on the outer wall surface 112 of the front cover plate and is integrally processed with the front cover plate 1.
Further, the impeller is matched with a space guide vane matched with any size, and the impeller is assembled to form the multistage pump with the impeller with the maximum lift and the maximum diameter.
External characteristic experimental tests and numerical simulation verification are carried out on the implementation examples, and a multi-stage pump lift curve, the middle section speed of the impeller and the flow line distribution of the guide vanes are obtained.
Numerical simulation was completed in ANSYS-CFX 2019R3, and the convergence accuracy of the calculation was 10 -4 The wall adopts a sliding-free boundary, a standard wall function, and different subfields are connected through interfaces, wherein when No relative motion exists between adjacent subfields (No frame change), general connection is adopted: no frame change. When there is relative motion between adjacent subfields, general connection is employed: pitch change. The initial pressure is set to the standard atmospheric pressure using mass flow outlet to facilitate convergence in conjunction with open inlet (total pressure inlet) boundary conditions, and the turbulence model selects SST k-omega.
FIG. 4 shows a performance test bench for an embodiment of the invention. Instrument model and precision used in experiments: the flowmeter is a KEFC-A2-M-K electromagnetic flowmeter, and the precision grade is 0.5%. The inlet and outlet pressures were collected by two WT3000 intelligent pressure transmitters with a maximum allowable error of ± 0.075%. theJN338M-Atypetorquercanmeasurerotatingspeedandtorque,andtheprecisiongradeis0.2%. The total system uncertainty of this experiment included measurement uncertainty and random uncertainty, which was 0.25%. Therefore, the measurement error of the whole experimental system can be considered smaller, and the measurement requirement can be met.
Fig. 5 shows a comparison of numerical simulations with experimental data for an embodiment of the invention. In general, the trend of the simulated curve and the experimental curve are very similar. Moreover, when the flow rate is the design flow rate, the head error of the simulation and experiment is 1.4%. Therefore, the calculation accuracy of the numerical simulation method can be considered to satisfy the requirement.
Fig. 6 shows a comparison of pump head curves for multiple pumps employing embodiments of the present invention with maximum diameter characteristics of no maximum head. The multistage pump with the maximum lift and maximum diameter characteristics has obviously higher single-stage lift. Although the single-stage lift increasing rate is not high, the invention can be applied to a multistage pump to be overlapped step by step to ensure that the total lift is increased to a greater extent. For example, in the deep sea oil extraction industry, the number of stages of the multi-stage submersible electric pump can reach more than 100 stages, and the use number of stages of the multi-stage pump can be reduced under the same exploitation depth by adopting the invention, so that the application cost is reduced.
FIG. 7 shows a comparison of mid-section velocity and streamline distribution for a multi-stage pump impeller and vane with maximum diameter of electrodeless large lift using an embodiment of the present invention. It can be clearly found that when an electrodeless large-lift maximum diameter multistage pump is adopted, the flow near the outlets of the impeller blades is relatively turbulent, and a local low-speed region exists. The impeller outlet flow pattern is significantly improved when the embodiments of the present invention are employed.
The examples are given as preferred embodiments of the present invention and are not intended to limit the invention in any way, and any obvious modifications, substitutions or variations may be made by one skilled in the art without departing from the spirit of the invention.
Claims (10)
1. An impeller with maximum lift and maximum diameter comprises a front cover plate (1), a rear cover plate (7), blades (3), a balance disc (6), a hub (4), balance holes (13) and a mouth ring seal (2), wherein the specific rotation speed range of the impeller is 80<n s <800; it is characterized in that the method comprises the steps of,
the front cover plate (1) is divided into a front cover plate inner wall surface (111) and a front cover plate outer wall surface (112), and an included angle between the front cover plate inner wall surface (111) and the rotating shaft of the impeller is theta 1 The value range is 60 DEG<θ 1 <90°；
The rear cover plate (7) is divided into a rear cover plate inner wall surface (711) and a rear cover plate outer wall surface (712), and the included angle between the rear cover plate inner wall surface (711) and the rotating shaft of the impeller is theta 2 The value range is 60 DEG<θ 2 <90°；
The included angle between the inner wall surface (111) of the front cover plate and the inner wall surface (711) of the rear cover plate is theta 3 The value range is-2 degrees less than or equal to theta 3 ≤2°；
The maximum diameter of the front cover plate (1) is D q The maximum diameter of the rear cover plate (7) is D h Both of the sizes are D q ＞D h The method comprises the steps of carrying out a first treatment on the surface of the The connecting line of the maximum diameter positions of the front cover plate (1) and the rear cover plate (7), namely the projection line (10) of the common impeller blade outlet on the axial plane projection view,
wherein the blade outlet of the common impeller is arranged on the axial surfaceThe angle between the projection line (10) and the straight line (11) parallel to the rotation axis of the impeller is alpha 1 The value range is 0 DEG<α 1 ≤40°；
The angle between the projection line (10) of the blade outlet of the common impeller on the axial plane projection diagram and the straight line (12) perpendicular to the rotation axis of the impeller is beta 1 The value range is 50 degrees less than or equal to beta 1 <90°。
2. Impeller of maximum lift maximum diameter according to claim 1, characterized in that the front cover plate (1) has a thickness t 1 The value range is not less than 2mm and not more than t 1 ≤5mm。
3. Impeller of maximum lift maximum diameter according to claim 1, characterized in that the back cover plate (7) has a thickness t 2 The value range is not less than 2mm and not more than t 2 ≤5mm。
4. The impeller with the maximum lift and maximum diameter according to claim 1, wherein the blades (3) are cylindrical blades or twisted blades, the number of which is Z, and the value range of which is more than or equal to 5 and less than or equal to 9.
5. A maximum lift maximum diameter impeller according to claim 4, wherein the cylindrical and twisted blades each comprise a blade inlet edge (31) and a blade outlet edge (5).
6. The maximum lift maximum diameter impeller of claim 5, wherein the axial projection of the blade inlet edge (31) is a single spline curve or straight line, and the axial projection of the blade outlet edge (5) is composed of two straight line segments, wherein the angle between the front straight line segment (8) and the straight line (11) parallel to the impeller rotation axis is α 2 The value range is 1/3 alpha 1 ≤α 2 ≤2/3α 1 The method comprises the steps of carrying out a first treatment on the surface of the The included angle between the rear straight line section (9) and the straight line (12) perpendicular to the rotation axis of the impeller is beta 2 The value range is 1/3 beta 1 ≤β 2 ≤2/3β 1 。
7. Impeller with maximum head maximum diameter according to claim 5, characterized in that the balancing holes (13) are circumferentially uniformly distributed in the vicinity of the blade inlet edge (31), with a circular cross section, number K, which has a value k=z, and the circular cross section diameter D k The value range is not less than 1mm and not more than D k ≤5mm。
8. The impeller with the maximum lift and maximum diameter according to claim 1, wherein the balance disc (6) is in a circular ring shape, the ring width is w, and the value range of w is more than or equal to 3mm and less than or equal to 5mm; the balance disc (6) is arranged on the outer wall surface (712) of the rear cover plate and integrally processed with the rear cover plate (7).
9. The impeller with the maximum lift and maximum diameter according to claim 1, wherein the mouth ring seal (2) is arranged on the outer wall surface (112) of the front cover plate and is integrally processed with the front cover plate (1).
10. A multistage pump characterized in that an impeller of maximum head maximum diameter according to any one of claims 1 to 9 is mounted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211464681.8A CN116066400A (en) | 2022-11-22 | 2022-11-22 | Impeller with maximum lift and maximum diameter and multistage pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202211464681.8A CN116066400A (en) | 2022-11-22 | 2022-11-22 | Impeller with maximum lift and maximum diameter and multistage pump |
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| Publication Number | Publication Date |
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| CN116066400A true CN116066400A (en) | 2023-05-05 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202211464681.8A Pending CN116066400A (en) | 2022-11-22 | 2022-11-22 | Impeller with maximum lift and maximum diameter and multistage pump |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2839005A (en) * | 1953-10-14 | 1958-06-17 | Herbert E Means | Turbine driven pump |
| US5628616A (en) * | 1994-12-19 | 1997-05-13 | Camco International Inc. | Downhole pumping system for recovering liquids and gas |
| US5961282A (en) * | 1996-05-07 | 1999-10-05 | Institut Francais Du Petrole | Axial-flow and centrifugal pumping system |
| US20030155128A1 (en) * | 2002-02-20 | 2003-08-21 | Gay Farral D. | Electric submersible pump with specialized geometry for pumping viscous crude oil |
| CN201650848U (en) * | 2010-04-22 | 2010-11-24 | 浙江东音泵业有限公司 | Impeller for submersible pump for well |
| CN208578766U (en) * | 2018-06-29 | 2019-03-05 | 浙江南元泵业有限公司 | Centrifugal pump impeller |
-
2022
- 2022-11-22 CN CN202211464681.8A patent/CN116066400A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2839005A (en) * | 1953-10-14 | 1958-06-17 | Herbert E Means | Turbine driven pump |
| US5628616A (en) * | 1994-12-19 | 1997-05-13 | Camco International Inc. | Downhole pumping system for recovering liquids and gas |
| US5961282A (en) * | 1996-05-07 | 1999-10-05 | Institut Francais Du Petrole | Axial-flow and centrifugal pumping system |
| US20030155128A1 (en) * | 2002-02-20 | 2003-08-21 | Gay Farral D. | Electric submersible pump with specialized geometry for pumping viscous crude oil |
| CN201650848U (en) * | 2010-04-22 | 2010-11-24 | 浙江东音泵业有限公司 | Impeller for submersible pump for well |
| CN208578766U (en) * | 2018-06-29 | 2019-03-05 | 浙江南元泵业有限公司 | Centrifugal pump impeller |
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