CN116717503A - Design method of second impeller molded line of water lifting pump for multistage well - Google Patents
Design method of second impeller molded line of water lifting pump for multistage well Download PDFInfo
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- CN116717503A CN116717503A CN202310688146.9A CN202310688146A CN116717503A CN 116717503 A CN116717503 A CN 116717503A CN 202310688146 A CN202310688146 A CN 202310688146A CN 116717503 A CN116717503 A CN 116717503A
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- 238000000034 method Methods 0.000 title claims abstract description 33
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 24
- 230000004044 response Effects 0.000 claims abstract description 38
- 238000005457 optimization Methods 0.000 claims abstract description 16
- 235000020681 well water Nutrition 0.000 claims abstract description 13
- 239000002349 well water Substances 0.000 claims abstract description 13
- 238000004422 calculation algorithm Methods 0.000 claims abstract description 7
- 238000004088 simulation Methods 0.000 claims abstract description 6
- 238000005070 sampling Methods 0.000 claims description 6
- 230000002068 genetic effect Effects 0.000 claims description 5
- 238000005211 surface analysis Methods 0.000 claims description 5
- 239000004743 Polypropylene Substances 0.000 claims description 2
- 229910000746 Structural steel Inorganic materials 0.000 claims description 2
- 229920006351 engineering plastic Polymers 0.000 claims description 2
- 239000000463 material Substances 0.000 claims description 2
- -1 polypropylene Polymers 0.000 claims description 2
- 229920001155 polypropylene Polymers 0.000 claims description 2
- 239000012530 fluid Substances 0.000 abstract description 3
- 238000010586 diagram Methods 0.000 description 8
- 230000006872 improvement Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005764 inhibitory process Effects 0.000 description 1
- 230000002262 irrigation Effects 0.000 description 1
- 238000003973 irrigation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Abstract
The invention discloses a design method of a second impeller molded line of a water lifting pump for a multistage well, which can optimize design parameters of a blade structure as much as possible while reducing axial force of a rotor so as to maintain higher efficiency of a system and weaken negative influence caused by pre-rotation of incoming flow at an inlet of the second impeller. On the basis of calculating and obtaining the inlet diameter, the outlet diameter and the outlet width of an impeller according to a speed coefficient method, a regression model equation is established by using Design Expert 10 software, a blade wrap angle, an inlet placement angle and an outlet placement angle are used as variables, three different values are selected for each variable, 17 groups of impeller molded line samples are designed, hydraulic efficiency and rotor axial force of the multistage well water lifting pump with different blade molded lines are obtained through fluid numerical simulation, then a multi-objective optimization is carried out by using NSGA-II algorithm to obtain a hydraulic efficiency and rotor axial force statistical formula, and optimal values of the blade wrap angle, the inlet placement angle and the outlet placement angle of the impeller are reversely deduced based on response relations.
Description
Technical Field
The invention relates to the technical field of design of lifting pump impellers for wells, in particular to a design method of a second impeller molded line of a lifting pump for multistage wells.
Background
As core equipment for pumping underground water, the multistage well water lifting pump has the advantages of small volume, high lift, light weight, reasonable price and the like, and is widely used in the fields of geothermal energy, agricultural irrigation and the like.
The multistage well water lifting pump generally comprises a first impeller and at least one second impeller, wherein the first impeller is arranged at a water inlet, the inlet of the first impeller is not pre-rotated, the inlet of the second impeller is pre-rotated, in order to weaken the influence caused by the pre-rotation, the inlet setting angle of the second impeller is generally increased in design and manufacture, fluid flows according to a designed streamline to ensure the high efficiency and stability of the flow as much as possible, and because the increase of the inlet setting angle of the second impeller has too much uncertainty, the hydraulic efficiency and the axial force of a rotor are greatly influenced, and the optimal design method is needed to be changed.
Disclosure of Invention
In order to solve the technical problems, the invention provides a design method of a molded line of a second impeller of a water lifting pump for a multi-stage well, which is characterized in that through improving the inlet and outlet placement angles and the blade wrap angles of the blades of the second impeller, the second impeller is better adapted to the operation requirement, the problems of balanced axial force and low efficiency of a rotor of the multi-stage pump are solved, and an excellent molded line of the second impeller of the water lifting pump for the multi-stage well is designed, so that the performance level of the whole machine is improved.
The present invention achieves the above technical object by the following technical means.
The invention discloses a design method of a second impeller molded line of a lifting pump for a multi-stage well, which comprises a group of first impellers and at least one group of second impellers, wherein the first impellers are close to a water inlet of the lifting pump for the multi-stage well; the second impellers are sequentially arranged between the first impellers and the water outlets of the multistage well water lifting pump; the design method of the second impeller molded line of the water lifting pump for the multistage well comprises the following steps:
s1: design flow Qm based on multistage well water lifting pump 3 S, single-stage lift Hm, rotating speed nr/min, calculating the obtained specific rotating speedDeriving blade inlet angle beta 1 Blade outlet angle beta 2 The blade wrap angle phi relates to the specific rotational speed n s Is the control equation of (1): />
S2: sampling the blade inlet setting angle, the blade outlet setting angle and the blade wrap angle by taking the control equation obtained in the step S1 as a basis;
s3: obtaining the axial force and the efficiency corresponding to the sample acquired in the step S2 under the rated flow working condition through hydrodynamic numerical simulation;
s4: obtaining the response relation among the axial force, the efficiency, the blade inlet setting angle, the blade outlet setting angle and the blade wrap angle obtained in the step S3 by adopting a BBD design method and a response surface analysis method;
s5: optimizing the axial force and the efficiency by adopting an NSGA-II genetic algorithm to obtain the optimal value of the axial force and the efficiency, and reversely deducing an inlet setting angle beta based on the response relation obtained in the step S4 1 Outlet setting angle beta 2 And the optimum design value of the impeller blade wrap angle phi.
Further, in the step S2, the specific operation steps are as follows:
three blade inlet mounting angles were designed: 0.5 beta 1 、β 1 、1.5β 1 Three blade outlet mounting angles: 0.75 beta 2 、β 2 、1.25β 2 Three blade wrap angles: 0.9Φ, Φ, 1.1Φ; according to the BBD box line-type test design method, a central point is added, data sampling of design variables is obtained through fewer working condition numbers on the basis of avoiding low-efficiency sampling points, and particularly 17 groups of impeller line samples of the water lifting pump for the multistage well are obtained through the design method.
Further, in the step S4, the specific operation steps are as follows:
obtaining the response relations among the blade inlet setting angle, the blade outlet setting angle and the blade wrap angle by adopting a BBD design method and a response surface analysis method,
Efficiency＝A 1 Φ+A 2 β 1 -A 3 β 2 +B 1 Φβ 1 -B 2 Φβ 2 +B 3 β 1 β 2 -C 1 Φ 2 -C 2 β 1 2 +C 3 β 2 2 +D 1 ；
Force＝-A 4 Φ-A 5 β 1 +A 6 β 2 -B 4 Φβ 1 -B 5 Φβ 2 -B 6 β 1 β 2 +C 4 Φ 2 +C 5 β 1 2 -C 6 β 2 2 +D 2 ；
wherein Efficiency in the response relation is Efficiency; force is axial Force; a is that 1 、A 2 、A 3 、A 4 、A 5 、A 6 、B 1 、B 2 、B 3 、B 4 、B 5 、B 6 、C 1 、C 2 、C 3 、C 4 、C 5 、C 6 、D 1 、D 2 Are all constant.
Further, in the step S5, the specific operation steps are as follows:
performing three-parameter two-objective optimization on the response relationship obtained in the step S4 by using a second generation genetic algorithm NSGA-II, wherein three parameters are beta respectively 1 、β 2 And phi, the optimization targets are respectively that the axial force is minimum and the efficiency is maximum, and the optimal value relationship between the efficiency and the axial force under the rated flow working condition is obtained through optimization; based on response relation, reversely pushing out inlet placement angle beta 1 Outlet setting angle beta 2 And the optimum design value of the impeller blade wrap angle phi.
Furthermore, the second impeller of the multistage well water lifting pump can be made of polypropylene PPO engineering plastics or structural steel materials.
The invention provides a design method of a second impeller molded line of a lifting pump for a multistage well, which is characterized in that a preferable scheme of the molded line of a blade is obtained through the influence rule of an inlet setting angle, an outlet setting angle and a blade wrap angle of a sample on efficiency and axial force, and an excellent hydraulic design scheme of the lifting pump for the multistage well can be obtained.
Drawings
In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a cross-sectional view of a conventional multi-stage well pump;
FIG. 2 is a schematic diagram of a second impeller of the multi-stage well pump;
FIG. 3 (a) is a response curve for axial force between the blade inlet placement angle β1 and the wrap angle Φ;
FIG. 3 (b) is a response curve for axial force between the blade exit placement angle β2 and the wrap angle Φ;
FIG. 3 (c) is a response curve for axial force between the vane inlet and outlet mounting angles β1 and β2;
FIG. 4 (a) is a response curve for efficiency between the blade inlet placement angle β1 and the wrap angle Φ;
FIG. 4 (b) is a response curve for efficiency between the blade exit placement angle β2 and the wrap angle Φ;
FIG. 4 (c) is a response curve for efficiency between the vane inlet placement angle β1 and outlet placement angle β2;
fig. 5 is a main technical route diagram of the present invention.
The following supplementary explanation is given to the accompanying drawings:
in fig. 1, a motor drive coupling; 2. a hexagonal spindle; 3. a water inlet chamber; 4. a first support plate; 5. a first impeller; 6. a first guide vane; 7. a second support plate; 8. a second impeller; 9. an upper sliding bearing; 10. a water outlet chamber; 11. a second guide vane;
in fig. 2, β1 is the blade inlet setting angle, β2 is the blade outlet setting angle, and Φ is the blade wrap angle;
FIG. 3 (a) contains three sets of coordinates, the x-axis being the blade wrap angle Φ; the y axis is the blade inlet mounting angle beta 1; the z-axis is the rotor axial force;
FIG. 3 (b) contains three sets of coordinates, the x-axis being the blade wrap angle Φ; the y axis is the blade outlet mounting angle beta 2; the z-axis is the rotor axial force;
FIG. 3 (c) contains three sets of coordinates, the x-axis being the blade inlet mounting angle β1; the y axis is the blade outlet mounting angle beta 2; the z-axis is the rotor axial force;
FIG. 4 (a) contains three sets of coordinates, the x-axis being the blade wrap angle Φ; the y axis is the blade inlet mounting angle beta 1; the z-axis is efficiency;
FIG. 4 (b) contains three sets of coordinates, the x-axis being the blade wrap angle Φ; the y axis is the blade outlet mounting angle beta 2; the z-axis is efficiency;
FIG. 4 (c) contains three sets of coordinates, the x-axis being the blade exit placement angle β2; the y axis is the blade inlet mounting angle beta 1; the z-axis is efficiency.
Detailed Description
The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings. It is apparent that the described embodiments are only some embodiments of the present invention, but not all embodiments, and the embodiments described below by referring to the drawings are exemplary for explaining the present invention and are not to be construed as limiting the present invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Reference herein to "one embodiment" or "an embodiment" means that a particular feature, structure, or characteristic may be included in at least one implementation of the invention.
1. Structural arrangement
As shown in fig. 1, fig. 1 is a schematic structural diagram of a multi-stage well water lifting pump, which comprises a pump shell, wherein a hexagonal main shaft 2 is arranged along the length direction of the pump shell, the hexagonal main shaft 2 is provided with a first end and a second end, and a motor drive coupler 1 is sleeved on the first end; a first support plate 4, a first guide vane 5, a first guide vane 6, a second support plate 7, a second impeller 8, a second guide vane 11 and an upper sliding bearing 9 are sequentially connected to the hexagonal spindle 2 along the first end towards the second end; in the pump shell, a water inlet chamber 3 is arranged near the first section of the hexagonal main shaft 2, and the water inlet chamber 3 is used for providing a water inlet for the first guide vane 5; a water outlet chamber 10 is arranged near the second end of the hexagonal spindle 2;
in practical applications, the operation stability of the multistage well pump is affected by the action of liquid impact and axial force.
As shown in FIG. 2, FIG. 2 is a schematic view of a second impeller type line of the multi-stage well pump according to the present invention, wherein the blade inlet mounting angle is beta 1 The blade outlet setting angle is beta 2 The blade wrap angle is phi.
2. Dimensional parameter design and optimization
According to the structural setting and parameters, the second impeller molded line parameter expansion design and optimization are implemented as follows:
in the known flow Q of water lifting pump for multi-stage well, unit m 3 And/s, and a single-stage lift H, under the premise of unit m, through a calculation formulaObtaining the specific rotation speed n s According to the experimental data result fitting curve of the excellent hydraulic model to obtain the blade inlet angle beta 1 Blade outlet angle beta 2 The blade wrap angle phi relates to the specific rotational speed n s Is the control equation of (1):thereby controlling the second impeller beta 1 、β 2 Phi designing method, beta 1 、β 2 The phi is respectively set as three levels: 0.5 beta 1 、β 1 、1.5β 1 ；0.75β 2 、β 2 、1.25β 2 And 0.9Φ, Φ, 1.1Φ; test device through BBD box line typeThe metering method obtains 17 groups of second impeller molded line samples, beta 1 、β 2 The set level of Φ is shown in table 1 below, and 17 sets of samples selected based on the above levels are shown in table 2. Beta in tables 1 and 2 1 、β 2 Both phi and phi are the results after dimensionless treatment.
TABLE 1 blade profile design parameters and levels
Table 2 blade profile samples
Acquisition of beta by numerical simulation of flow fields 1 、β 2 Different samples of phi correspond to different Efficiency and rotor axial Force under the rated flow working condition.
Designing and analyzing the second impeller molded line parameters through BBD design and RSM response surface analysis method to obtain Efficiency, rotor axial Force and blade inlet mounting angle beta 1 Blade outlet setting angle beta 2 And the response relation between the blade wrap angles phi.
Efficiency＝A 1 Φ+A 2 β 1 -A 3 β 2 +B 1 Φβ 1 -B 2 Φβ 2 +B 3 β 1 β 2 -C 1 Φ 2 -C 2 β 1 2 +C 3 β 2 2 +D 1
Force＝-A 4 Φ-A 5 β 1 +A 6 β 2 -B 4 Φβ 1 -B 5 Φβ 2 -B 6 β 1 β 2 +C 4 Φ 2 +C 5 β 1 2 -C 6 β 2 2 +D 2
A in response relation 1 、A 2 、A 3 、A 4 、A 5 、A 6 、B 1 、B 2 、B 3 、B 4 、B 5 、B 6 、C 1 、C 2 、C 3 、C 4 、C 5 、C 6 、D 1 、D 2 Are all constant.
FIGS. 3 and 4 show exemplary response curves obtained by BBD design and RSM analysis, where FIG. 3 (a) is beta 1 A response surface diagram between phi and phi for axial Force; FIG. 3 (b) is beta 2 A response surface diagram between phi and phi for axial Force; FIG. 3 (c) is beta 1 And beta 2 A response surface diagram of the axial Force; FIG. 4 (a) is beta 1 A response surface graph for Efficiency between phi and phi; FIG. 4 (b) is beta 2 A response surface graph for Efficiency between phi and phi; FIG. 4 (c) is beta 1 And beta 2 A response surface diagram for Efficiency. The above-described response formulas and the response curve diagrams thereof are merely exemplary in nature, and there is necessarily a slight difference in the response obtained based on different test or test data. In summary, according to the above work, the efficiency can be improved by 2.7% at maximum and the axial force can be reduced by 15.6% at maximum.
Performing three-parameter two-objective optimization on the response relationship by using a second generation genetic algorithm NSGA-II, wherein the three parameters are beta respectively 1 、β 2 And phi, wherein the optimization targets are respectively the minimum Force and the maximum Efficiency, and the optimal value relationship between Efficiency and Force under the working condition of rated flow is obtained through optimization. Based on response relation, reversely pushing out inlet placement angle beta 1 Outlet setting angle beta 2 And the optimum design value of the impeller blade wrap angle phi.
Table 3 shows comparative test data tables of second impeller molded lines of the lift pump for multi-stage well before and after design optimization, wherein NSGA-II is selected from Force and Efficiency values according to NSGA-II algorithm optimization result, and CFD simulation is selected from phi and beta by using CFD computational fluid dynamics simulation software 1 And beta 2 Force and Efficiency data obtained by simulation are actually measured in the value range. "before optimizationThe dimension parameters in the row are randomly selected, and the dimension parameters in the optimized row are selected based on the optimization result. All relevant parameters beta 1 、β 2 、Φ、F 1 、E 1 、F 2 、E 2 、F 3 、E 3 All are the results after dimensionless treatment.
Table 3 data comparison test
According to the comparison test, the design method and the optimization parameters of the second impeller molded line can achieve better rotor axial force inhibition and multistage pump efficiency improvement effects compared with randomly selected impeller molded line parameters, and the method can effectively optimize balance between reducing axial force and improving pump efficiency, so that the operation reliability of the multistage well water lifting pump is improved.
In the description of the present invention, the positional or positional relationship indicated by the terms such as "upper", "lower", "front", "rear", etc. are based on the positional or positional relationship shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present invention.
The foregoing is only illustrative of the present invention and is not to be construed as limiting thereof, but rather as various modifications, equivalent arrangements, improvements, etc., within the spirit and principles of the present invention.
Claims (5)
1. The design method of the second impeller molded line of the multi-stage well water lifting pump is characterized in that the multi-stage well water lifting pump comprises a group of first impellers and at least one group of second impellers, wherein the first impellers are close to a water inlet of the multi-stage well water lifting pump; the second impellers are sequentially arranged between the first impellers and the water outlets of the multistage well water lifting pump; the design method of the second impeller molded line of the water lifting pump for the multistage well comprises the following steps:
s1: design flow Qm based on multistage well water lifting pump 3 S, single-stage lift Hm, and rotating speed nr/min, calculating to obtain specific rotating speedDeriving blade inlet angle beta 1 Blade outlet angle beta 2 The blade wrap angle phi relates to the specific rotational speed n s Is the control equation of (1): />
S2: sampling the blade inlet setting angle, the blade outlet setting angle and the blade wrap angle by taking the control equation obtained in the step S1 as a basis;
s3: obtaining the axial force and the efficiency corresponding to the sample acquired in the step S2 under the rated flow working condition through hydrodynamic numerical simulation;
s4: obtaining the response relation among the axial force, the efficiency, the blade inlet setting angle, the blade outlet setting angle and the blade wrap angle obtained in the step S3 by adopting a BBD design method and a response surface analysis method;
s5: optimizing the axial force and the efficiency by adopting an NSGA-II genetic algorithm to obtain the optimal value of the axial force and the efficiency, and reversely deducing an inlet setting angle beta based on the response relation obtained in the step S4 1 Outlet setting angle beta 2 And the optimum design value of the impeller blade wrap angle phi.
2. The method for designing a second impeller profile of a lift pump for a multi-stage well according to claim 1, wherein the specific operation steps in the step S2 are as follows:
three blade inlet mounting angles were designed: 0.5 beta 1 、β 1 、1.5β 1 Three blade outlet mounting angles: 0.75 beta 2 、β 2 、1.25β 2 Three blade wrap angles: 0.9Φ, Φ, 1.1Φ; according to the BBD box line-type test design method, a central point is added, data sampling of design variables is obtained through fewer working condition numbers on the basis of avoiding low-efficiency sampling points, and particularly 17 groups of impeller line samples of the water lifting pump for the multistage well are obtained through the design method.
3. The method for designing a second impeller profile of a multi-stage well pump according to claim 2, wherein the specific operation steps in step S4 are as follows:
obtaining the response relations among the blade inlet setting angle, the blade outlet setting angle and the blade wrap angle by adopting a BBD design method and a response surface analysis method,
Efficiency＝A 1 Φ+A 2 β 1 -A 3 β 2 +B 1 Φβ 1 -B 2 Φβ 2 +B 3 β 1 β 2 -C 1 Φ 2 -C 2 β 1 2 +C 3 β 2 2 +D 1 ；
Force＝-A 4 Φ-A 5 β 1 +A 6 β 2 -B 4 Φβ 1 -B 5 Φβ 2 -B 6 β 1 β 2 +C 4 Φ 2 +C 5 β 1 2 -C 6 β 2 2 +D 2 ；
wherein Efficiency in the response relation is Efficiency; force is axial Force; a is that 1 、A 2 、A 3 、A 4 、A 5 、A 6 、B 1 、B 2 、B 3 、B 4 、B 5 、B 6 、C 1 、C 2 、C 3 、C 4 、C 5 、C 6 、D 1 、D 2 Are all constant.
4. The method for designing a second impeller profile of a pump for multi-stage wells according to claim 3, wherein the specific operation steps in said step S5 are as follows:
performing three-parameter two-objective optimization on the response relationship obtained in the step S4 by using a second generation genetic algorithm NSGA-II, wherein three parameters are beta respectively 1 、β 2 And phi, the optimization targets are respectively that the axial force is minimum and the efficiency is maximum, and the optimal value relationship between the efficiency and the axial force under the rated flow working condition is obtained through optimization; based on response relation, reversely pushing out inlet placement angle beta 1 Outlet setting angle beta 2 And the optimum design value of the impeller blade wrap angle phi.
5. The method for designing a second impeller molded line of a water pump for a multi-stage well according to claim 4, wherein the second impeller of the water pump for a multi-stage well is made of polypropylene PPO engineering plastic or structural steel material.
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