CN118153140A - High-efficiency high-reliability multistage pump design method based on time sequence effect analysis - Google Patents
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Abstract
The invention discloses a high-efficiency high-reliability multistage centrifugal pump hydraulic design method, which comprises the steps of firstly, designing a preliminary hydraulic component of a multistage pump by a traditional multistage centrifugal pump design method; secondly, selecting key design parameters of the impeller, optimizing parameters of the impeller of the multistage pump based on a curved surface response method, calculating a flow field of the multistage pump by adopting a computational fluid dynamics method, predicting the key parameter values of an optimal scheme by fitting a regression equation, and obtaining a reliable and efficient multistage pump hydraulic model through true experiment verification; and then, optimizing the multistage pump based on a time sequence effect, only adjusting the relative positions of impellers of each stage, monitoring the efficiency and pressure pulsation of the multistage pump through unsteady numerical simulation, defining the flow density of the pressure pulsation to measure the stability of the multistage pump, and forming a final efficient and highly reliable multistage pump design scheme. The invention simplifies the optimization variable of the multistage pump, saves the development cost, simultaneously can effectively improve the performance of the multistage pump, and realizes the optimization of the multistage centrifugal pump with short period and low cost.
Description
Technical Field
The invention relates to a multistage centrifugal pump design method in hydraulic machinery design, which is suitable for multistage centrifugal pump design with higher requirements on operation efficiency and operation stability.
Background
Centrifugal pumps are used as an important fluid conveying device and are widely applied to industries such as liquid conveying, water supply, water discharge, petroleum, chemical industry, energy sources and the like. With the continuous development of social economy, the requirements for multistage centrifugal pumps are also increasing. However, the conventional multistage centrifugal pump still has some non-negligible problems in use, which limit further application and development thereof, and mainly comprises the following three aspects: (1) low efficiency: the existing multistage centrifugal pump has lower efficiency under the working conditions of high lift and large flow, so that the energy waste and the running cost are increased; (2) operational stability: part of the existing multistage centrifugal pumps are easy to generate vibration and noise in the running process, and the stability and the service life of equipment are affected; (3) maintenance cost: some traditional multistage centrifugal pumps have complex structures, are difficult to maintain, require frequent overhauling and maintenance, and increase the economic burden of enterprises and users.
The existing hydraulic design method of the multistage pump usually designs and optimizes a single-stage hydraulic model, and then realizes hydraulic design of the multistage pump by connecting the same hydraulic model in series. However, the internal flow of the multistage pump is complex, different parameters are mutually influenced, and the design defects in the three aspects are difficult to be considered. The prior patent number CN115681165A, named as an optimal design method of the segmental multistage pump, proposes an energy-saving multistage pump design method with the lowest cost of the life cycle of the pump, the method takes manufacturing cost, maintenance cost and energy cost as economic measurement indexes, and the multistage pump stage number is determined by taking the pump efficiency as an optimization target after the structure, the shaft sealing form and the bearing form of the segmental multistage pump are determined. The method comprehensively considers the life cycle cost and the operation efficiency of the multistage pump, effectively reduces the maintenance cost, is limited by the determination of the pump structure, and cannot effectively consider the maximization of the pump efficiency and the design of the operation stability of the pump.
The prior patent number CN105604953B, named as a multistage pump impeller dislocation arrangement method based on vibration optimization, proposes a multistage pump design method which can greatly reduce the vibration of a multistage pump during operation and improve the operation stability of the pump on the premise of not changing the hydraulic design and the structural design of the pump and ensuring that the pump efficiency and the pump lift change are very small, and the method can effectively improve the operation efficiency and the operation stability of the pump under the condition of limiting the pump structure, but needs a large number of true experiments, and a large amount of time and experiment cost are consumed for searching an impeller dislocation arrangement scheme with optimal stability through experimental data analysis.
Aiming at the defects, the inventor finds out a high-efficiency and high-reliability multistage pump design method based on time sequence effect analysis, performs response surface method optimization design on multistage pump impellers on the basis of not changing pump structure design, performs comparison verification by combining an external characteristic test, performs time sequence position design on each stage of impellers of the multistage pump after obtaining a high-efficiency multistage pump impeller hydraulic model, performs unsteady calculation, sets impeller runner pressure pulsation monitoring points, defines pressure pulsation energy flow density to accurately measure multistage pump operation stability, optimizes a high-efficiency and high-reliability impeller arrangement scheme according to efficiency and pressure pulsation of each time sequence scheme, and finally obtains the high-efficiency and high-reliability multistage pump design scheme.
Disclosure of Invention
The invention aims to provide a high-efficiency high-reliability multistage pump design method based on time sequence effect analysis for the design of a multistage centrifugal pump, which can enable the multistage centrifugal pump to have higher efficiency and better operation stability without changing the structural parameters of the multistage pump, and reduce a large amount of experimental test cost.
The invention aims at the optimal design of the performance and the operation stability of the multistage pump, and is realized by the following steps: (1) Determining the main structural size of each flow-through part of the multistage centrifugal pump by adopting a traditional centrifugal pump design method, and aiming at the multistage pump with low specific speed, designing an impeller by adopting a design method for increasing the flow, and correcting related design coefficients to ensure that the design point efficiency of the impeller designed by increasing the flow is higher than that of the impeller designed by adopting a conventional unitary theory; (2) And selecting a streamline inlet setting angle A of a rear cover plate of an impeller blade, a streamline inlet setting angle B of a middle streamline inlet, a streamline inlet setting angle C of a front cover plate and a streamline outlet setting angle D of the blade as parameter variables to carry out response surface method optimization design on the multistage pump impeller, carrying out calculation domain three-dimensional modeling on each scheme of a response surface, carrying out calculation analysis on an internal flow field of the multistage pump by adopting a Computational Fluid Dynamics (CFD) method, and predicting the performance of the multistage pump of each scheme. (3) And predicting theoretical values of all parameters of the impeller with the lowest theoretical efficiency by fitting regression equations of performance parameters of all schemes, performing numerical simulation prediction verification, and obtaining the efficient multistage pump hydraulic model if the determined efficiency is the highest in all schemes and the response surface method is effective in optimization prediction. Otherwise, the calculation of the new scheme needs to be carried out again. (4) The maximum stagger angle between two adjacent blades of the impeller is used as the variable range of the circumferential position of the impeller, the design of the impeller time sequence position scheme is carried out according to the rule of an orthogonal method, then the steady calculation result of the hydraulic model of the efficient impeller multistage pump is used as the initial field to carry out unsteady calculation on the time sequence scheme, the efficiency of each time sequence scheme and the pressure pulsation data of the monitoring point of the impeller runner are obtained, the pressure pulsation energy flow density is defined to reflect the operation stability of the multistage pump, the time sequence scheme with the optimal efficiency and the optimal operation stability is screened, and the production and the manufacture can be started.
The multi-stage pump performance prediction method adopted in the invention is a computational fluid dynamics method (CFD), and the whole numerical simulation process comprises the following steps: selecting a control equation, three-dimensional modeling of a calculation domain, grid division of the calculation domain, setting of boundary conditions and steady calculation of a solver, wherein the turbulence model can adopt a k-omega (SST) turbulence model with a wider application range, taking a steady calculation result as an initial value to perform unsteady calculation, collecting pressure pulsation data of monitoring points arranged in a flow channel, and preparing for judging the running stability of a subsequent pressure multistage pump.
The invention has the beneficial effects that: adopting a mathematical statistics method to carry out multi-objective optimization on the impeller, identifying key influence factors and finding out the optimal combination, adopting a numerical simulation method to predict the hydraulic model optimization effect, reducing the experiment test times, saving the development cost and shortening the development period; after the design parameters of all parts of the multistage pump are determined, based on time sequence effect analysis, only the relative installation positions of the impellers are changed, so that the performance of the multistage pump is further improved.
Drawings
In order to more clearly illustrate the technical scheme of the invention, the following drawings are used for assisting the description.
FIG. 1 is a flow chart of a hydraulic design of a conventional multistage centrifugal pump;
FIG. 2 is a flow chart of a method for designing a high-efficiency and high-reliability multistage pump based on time sequence effect analysis;
FIG. 3 is a flow chart of an impeller optimization design based on a curved surface response method;
FIG. 4 is a flow chart of calculating a pump flow field by calculating a hydrodynamic value in accordance with the present invention;
FIG. 5 is a schematic diagram of a timing scheme design rotation of an impeller of the present invention;
FIG. 6 is a schematic diagram of the arrangement of pressure pulsation monitoring points in the flow channels of each stage of the multistage pump of the present invention.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application.
Referring to fig. 1, the hydraulic design flow of the conventional multistage pump mainly depends on engineering experience of a designer and test data of a true machine test, the true machine external characteristic test is performed after the primary design is completed, the design target is not met, the test needs to be repeatedly modified, and finally, the standard model is manufactured.
In combination with fig. 2, the multistage pump impeller is selected for parameter optimization, the multistage pump impeller is more comprehensively optimized based on a response surface method, the flow chart is shown in fig. 3, the efficiency and the operation stability of the multistage pump are improved by considering the time sequence effect of the impeller, and the short-period low-cost optimization of the multistage centrifugal pump is realized.
Taking a model pump design as an example, the design parameters of the multistage pump are as follows: flow q=36 m/H, head h=331.3m, rotational speed n=3800 r/min.
Step one: preliminary hydraulic design of multistage pump impeller:
Single-stage specific rotation speed ；
Equivalent diameter of impeller；
Hub diameter；
Diameter of inletTaking 96mm;
Impeller outlet diameter ；
Impeller outlet widthTaking 6.5mm;
Number of blades z=5;
Blade outlet setting angle ；
Wrap angle；
Step two: (1) On the basis of the preliminary impeller design parameters, the following four factors are selected to set a four-factor two-level full-factor test: impeller blade back shroud streamline inlet mounting angle a (36 °,52 °), intermediate streamline inlet mounting angle B (23 °,35 °), front shroud streamline inlet mounting angle C (13 °,22 °) and blade outlet mounting angle D (22 °,34 °). The test protocol is shown in table 1.
Table 1 full factor test protocol
| A | B | C | D |
| 36 | 35 | 13 | 34 |
| 52 | 23 | 13 | 34 |
| 52 | 23 | 22 | 22 |
| 52 | 23 | 22 | 34 |
| 52 | 35 | 22 | 22 |
| 44 | 29 | 17.5 | 28 |
| 36 | 35 | 22 | 22 |
| 36 | 23 | 13 | 22 |
| 52 | 35 | 13 | 22 |
| 52 | 35 | 13 | 34 |
| 44 | 29 | 17.5 | 28 |
| 36 | 23 | 13 | 34 |
| 52 | 23 | 13 | 22 |
| 36 | 23 | 22 | 34 |
| 36 | 35 | 22 | 34 |
| 36 | 23 | 22 | 22 |
| 36 | 35 | 13 | 22 |
| 44 | 29 | 17.5 | 28 |
| 52 | 35 | 22 | 34 |
12 Test points are added on the basis of the full factor test, a response surface test is carried out, and a response surface scheme is shown in table 2.
TABLE 2 response surface scheme
| Run sequence | Point type | Granule group | A | B | C | D |
| 1 | 1 | 1 | 36 | 35 | 13 | 34 |
| 2 | 1 | 1 | 52 | 35 | 22 | 34 |
| 3 | 1 | 1 | 36 | 23 | 13 | 22 |
| 4 | -1 | 1 | 44 | 29 | 17.5 | 16 |
| 5 | -1 | 1 | 44 | 29 | 8.5 | 28 |
| 6 | 0 | 1 | 44 | 29 | 17.5 | 28 |
| 7 | 0 | 1 | 44 | 29 | 17.5 | 28 |
| 8 | -1 | 1 | 44 | 17 | 17.5 | 28 |
| 9 | -1 | 1 | 44 | 29 | 26.5 | 28 |
| 10 | 1 | 1 | 36 | 35 | 22 | 22 |
| 11 | 1 | 1 | 36 | 35 | 13 | 22 |
| 12 | 0 | 1 | 44 | 29 | 17.5 | 28 |
| 13 | -1 | 1 | 44 | 29 | 17.5 | 40 |
| 14 | 1 | 1 | 52 | 23 | 22 | 34 |
| 15 | 1 | 1 | 36 | 23 | 22 | 22 |
| 16 | 1 | 1 | 52 | 35 | 22 | 22 |
| 17 | 1 | 1 | 36 | 23 | 22 | 34 |
| 18 | 0 | 1 | 44 | 29 | 17.5 | 28 |
| 19 | 0 | 1 | 44 | 29 | 17.5 | 28 |
| 20 | -1 | 1 | 60 | 29 | 17.5 | 28 |
| 21 | -1 | 1 | 28 | 29 | 17.5 | 28 |
| 22 | 0 | 1 | 44 | 29 | 17.5 | 28 |
| 23 | 1 | 1 | 36 | 35 | 22 | 34 |
| 24 | 1 | 1 | 52 | 23 | 13 | 34 |
| 25 | 1 | 1 | 52 | 23 | 13 | 22 |
| 26 | 0 | 1 | 44 | 29 | 17.5 | 28 |
| 27 | 1 | 1 | 36 | 23 | 13 | 34 |
| 28 | 1 | 1 | 52 | 35 | 13 | 22 |
| 29 | -1 | 1 | 44 | 41 | 17.5 | 28 |
| 30 | 1 | 1 | 52 | 35 | 13 | 34 |
| 31 | 1 | 1 | 52 | 23 | 22 | 22 |
(2) According to the numerical simulation method shown in fig. 4, performance prediction is carried out on 31 design schemes in total by the response surface method, a control equation is established, three-dimensional modeling of calculation domains of each scheme is completed, grid division of the calculation domains is carried out, a k-omega (SST) turbulence model is selected, initial conditions and boundary conditions of the calculation domains are given, a solver is set for steady calculation, external characteristic data of each scheme is counted for fitting of a regression equation, so that impeller parameter values under the optimal theoretical efficiency scheme are predicted, steady calculation is carried out on the optimal theoretical efficiency scheme, comparison with external characteristic experiments is carried out for verifying whether the optimal theoretical efficiency scheme is reasonable or not, if the variable value range of the experiment is not reasonable to be checked, scheme prediction is carried out again, and if the verification is reasonable, the local hydraulic optimization result of the impeller of the response surface method is obtained. Through the maximum value prediction of theoretical efficiency of the response surface, each dependent variable predicted value is impeller blade back cover plate streamline inlet setting angle A (43.5152 degrees), middle streamline inlet setting angle B (30.8182 degrees), front cover plate streamline inlet setting angle C (21.7727 degrees) and blade outlet setting angle D (30.9394 degrees).
(3) On the basis of an impeller optimization hydraulic model, a time sequence position scheme is designed for the multistage pump impeller, the maximum staggering angle between two adjacent blades of the impeller is used as an impeller circumferential position variable range, the impeller time sequence position scheme is designed according to an orthogonal method, an impeller rotation schematic diagram is shown in fig. 5, a design scheme table 3 shows that a steady calculation result of the efficient multistage pump hydraulic model is used as a primary field, a steady calculation is carried out for the time sequence scheme, efficiency of each time sequence scheme and pressure pulsation data of a flow channel monitoring point are obtained, and the monitoring point is arranged as shown in fig. 6.
(4) The operation stability of the multistage pump is reflected by defining the pressure pulsation energy flow density, and a time sequence scheme with optimal efficiency and operation stability is screened out. And the 2 nd-stage impeller of the final three-stage pump model rotates 17 degrees, the 3 rd-stage impeller has the best stability when unchanged, and the efficiency is improved by 5.2% under the design working condition when Q=36 m/H and H=331.3m.
The fluence density is defined as follows:
Assuming that the pressure pulsation signal is a cosine simple harmonic, the pressure pulsation coefficient from the pulsation source a and the rate of change thereof are as follows:
；
；
the analog wave intensity is defined where the pressure pulse energy density ε is:
Wherein A is amplitude; omega is the angular frequency, rad/s; a is the distance from the pulsation source, m; u is the propagation speed of pressure pulsation, and 1000 m/s is taken; ρ is the medium density, kg/m 3.
Energy flow of wavesDefined as the energy per unit time through a certain cross section. The average fluence I represents the fluence average of the pressure pulsation over one cycle, since the pressure pulsation signal contains many different frequency signals, and finally the pressure pulsation signal strength is represented by the pressure pulsation total fluence:
；
；
Table 3 impeller timing position scheme
| Scheme number | 2 Nd stage impeller rotation angle θ/° | 3 Rd stage impeller rotation angle θ/° |
| L1 | 0 | 0 |
| L2 | 0 | 17 |
| L3 | 0 | 34 |
| L4 | 0 | 51 |
| L5 | 17 | 0 |
| L6 | 17 | 17 |
| L7 | 17 | 34 |
| L8 | 17 | 51 |
| L9 | 34 | 0 |
| L10 | 34 | 17 |
| L11 | 34 | 34 |
| L12 | 34 | 51 |
| L13 | 51 | 0 |
| L14 | 51 | 17 |
| L15 | 51 | 34 |
| L16 | 51 | 51 |
Claims (6)
1. The design method of the high-efficiency high-reliability multistage pump based on the time sequence effect analysis is characterized by comprising the following steps of:
Step one, adopting a traditional multistage centrifugal pump hydraulic design method to carry out integral design on a multistage pump;
Step two, on the basis of the preliminary design scheme, selecting a core overcurrent component impeller with the greatest influence on the performance of the multistage pump to perform parameter optimization, and adjusting the relative position of the impeller based on time sequence effect analysis, wherein the method comprises the following steps:
s1, selecting key parameters of an impeller as test factors, and optimally designing the impeller by a response surface method;
S2, performing constant value simulation on the multistage pump, and analyzing and predicting an optimal scheme parameter combination of efficiency through fitting a regression equation and a response surface;
S3, adjusting the relative position of the impeller, carrying out unsteady numerical simulation on the multistage pump without modifying the structural parameters of the multistage pump, and monitoring the pressure pulsation characteristic of the multistage pump;
And S4, defining the pressure pulsation energy flow density, measuring the running stability of the multistage pump, and assisting in judging the optimal scheme.
2. The design method of the efficient high-reliability multistage pump based on time sequence effect analysis according to claim 1 is characterized in that the preliminary hydraulic design of the multistage pump is carried out by adopting a flow increasing design method, the problems of narrow and long flow passage of an impeller of a low-specific-speed pump are solved, and the problem of low efficiency is solved by adopting a common unitary theoretical design method.
3. The method for designing the efficient and highly reliable multistage pump based on time sequence effect analysis according to claim 1, wherein the optimization design process in the second step is completed by adopting numerical simulation, the efficiency values of the multistage pump under each scheme are counted through steady calculation, regression equations are fitted through the counted efficiency values, the values of all key parameters under the theoretical optimal efficiency are predicted, the reliability of the theoretical optimal scheme is determined through the numerical simulation, the numerical simulation step of multistage pump efficiency prediction comprises the steps of establishing a control equation, calculating a three-dimensional modeling of a domain, meshing, setting boundary conditions and steady calculation of a solver, if the theoretical optimal scheme efficiency is highest, the optimal scheme predicted by a response curved surface method is proved to be reliable, the scheme is a high-efficiency multistage pump hydraulic model without considering time sequence effect, a true experiment is performed on the high-efficiency multistage pump hydraulic model, and the numerical prediction is designed to be feasible within the experimental error range; and if the numerical prediction and experimental errors are too large, redesigning the calculation.
4. The design method of the efficient and reliable multistage pump based on time sequence effect analysis is characterized in that a time sequence effect of an impeller is considered on the basis of an optimized efficient and multistage pump hydraulic model, an impeller time sequence position arrangement scheme is designed, unsteady calculation is carried out on each scheme, the unsteady calculation needs to take a steady calculation result as an initial value, the calculation is continued on the basis, a k-omega turbulence model is generally adopted, the efficiency of each scheme and the pressure pulsation characteristic of an impeller runner monitoring point are recorded, and the time sequence scheme with the best efficiency and the time sequence scheme with the best running stability are obtained.
5. The method for designing a high-efficiency and high-reliability multistage pump based on time series effect analysis according to claim 1, wherein the analog wave intensity defines the pressure pulsation energy flow density, so as to measure the operation stability of the multistage pump.
6. The method for designing a highly efficient and reliable multistage pump based on timing analysis according to claim 1, wherein the multistage pump structure parameters are limited to other factors and still apply when they are difficult to modify.
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