GB2586756A - Comprehensive evaluation method for pump flow induced vibration performance - Google Patents
Comprehensive evaluation method for pump flow induced vibration performance Download PDFInfo
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Classifications
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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
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0088—Testing machines
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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
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0077—Safety measures
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- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F17/00—Digital computing or data processing equipment or methods, specially adapted for specific functions
- G06F17/10—Complex mathematical operations
- G06F17/14—Fourier, Walsh or analogous domain transformations, e.g. Laplace, Hilbert, Karhunen-Loeve, transforms
- G06F17/141—Discrete Fourier transforms
- G06F17/142—Fast Fourier transforms, e.g. using a Cooley-Tukey type algorithm
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- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F17/00—Digital computing or data processing equipment or methods, specially adapted for specific functions
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- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/52—Outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/301—Pressure
- F05D2270/3013—Outlet pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/334—Vibration measurements
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/10—Noise analysis or noise optimisation
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
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Abstract
A comprehensive evaluation method for pump flow induced vibration performance: first, utilizing an experimental test or value to produce by calculation pressure pulsation data at a pump impeller outlet and to calculate a dimensionless pressure pulsation coefficient time-domain transformation function; then, performing a fast Fourier transformation with respect to the time-domain transformation function to acquire a frequency-domain transformation function, then performing a full frequency domain search, arranging in a descending order according to amplitude and selecting the first three frequency points to serve as calculation frequency points; then, employing a analytic hierarchy process to determine weight factors of the amplitudes of the calculation frequency points in a pump flow inducted vibration overall evaluation, and finally, by means of a calculation with respect to the amplitudes of the calculation frequency points and the corresponding weight factors, acquiring a third-order comprehensive vibration pressure of a pump to evaluate the overall vibration level of the pump. The method takes into comprehensive consideration the amplitudes of a pump impeller outlet pressure pulsation transformation function on multiple frequency points, overcomes the lopsidedness in the past where only the vibration amplitude at a main frequency is taken into consideration in evaluating pump vibration performance, and has broad engineering application values.
Description
COMPREHENSIVE EVALUATION METHOD FOR FLOW-INDUCED
VIBRATION PERFORMANCE OF PUMP
Technical Field
The present invention relates to the field of fluid mechanical design, and in part cular to a comprehensive evaluation method for flow-induced vibration performance of a pump.
Background
As a kind of general machinery, pumps play an irreplaceable and important role in many industrial fields. With the development of society, new requirements have been put forward for the stability of pump operation. A lower vibration level of a pump can not only save energy and improve performances, but also is vital to improve the working life of the pump.
The vibration of a pump can be divided into two types: system vibration caused by mechanical vibration, and flow-induced vibration. The former is mainly influenced by design and manufacturing, and has been solved well by active control technology and the like, while the latter is mainly caused by the unsteady flow inside the pump, and its mechanism is still under constant study. Pressure pulsation is a specific manifestation of unsteady flow characteristics in the pump, and it is also the main factor causing flow-induced vibration of the pump. However, at present, most of the methods for analyzing the pressure pulsation only focus on analyzing the amplitude at a main frequency (the frequency corresponding to the maximum amplitude), and pay less attention to the amplitude at a secondary main frequency (usually blade passing frequency, but also shaft frequency, dynamic and static interference frequency, etc.). Although these methods can reflect the vibration level of the pump to a certain extent, when the amplitude at the secondary main frequency and other frequencies becomes larger, this analysis method is not comprehensive enough. Therefore, it is urgent to propose a comprehensive evaluation method for flow-induced vibration performance of a pump. However, up to now, no comprehensive evaluation method for flow-induced vibration of a pump has been reported.
Summary
In order to overcome the shortcomings in the prior art, the present invention provides a comprehensive evaluation method for flow-induced vibration performance of a pump, which can reflect the vibration performance of the pump more comprehensively.
The present invention achieves the above technical objectives through the following technical solutions.
The present invention provides a comprehensive evaluation method for flow-induced vibration performance of a pump, including the following steps: Step 1: selecting an outlet of an impeller as a monitoring point, and by an experimental test or numerical calculation, obtaining pressure pulsation data at the monitoring point, and calculating a time-domain transformation function of a dimensionless pressure pulsation coefficient; Step 2: applying Fast Fourier transform to transform the time-domain transformation function of the pressure pulsation coefficient to a frequency-domain transformation function, which then is subjected to a global frequency domain search to rank frequency points in a descending order according to their amplitudes and select the top three frequency points as calculation frequency points; Step 3: using Analytic Hierarchy Process (AT1P) to determine weight factors of the amplitudes of the three calculation frequency points in overall evaluation for the flow-induced vibration of the pump, and by calculating the amplitude of each of the calculation frequency points and the corresponding weight factor, obtaining a third-order comprehensive vibration pressure of the pump to evaluate the flow-induced vibration performance of the pump based thereon, wherein the higher the third-order comprehensive vibration pressure of the pump is, the worse the flow-induced vibration performance of the pump is, and the lower the third-order comprehensive vibration pressure of the pump is, the better the flow-induced vibration performance of the pump is.
Preferably, in the Step 1, if the data are obtained by the experimental test, the outlet of the impeller is selected as the monitoring point and is subjected to data sampling after the pump runs steadily, at a sampling frequency f selected as 1000 fi for a duration 1=2T, wherein fi is a shaft frequency of the pump, and T is a rotation period of the pump to be tested; if the pressure pulsation data are obtained by the numerical calculation, correct steady-state calculation results are set as initial conditions of an unsteady-state calculation, and an unsteady-state calculation time step at is set as 0t=3613 T,a total calculation time is set as 7T, (-) and the data in the last two rotation periods are selected as the pressure pulsation data.
Preferably, in the Step 1, after obtaining the pressure pulsation data, invalid data are removed from the pressure pulsation data, and the resulting pressure pulsation data are matched with time information to obtain a time-domain transformation function Fp (t) of pressure pulsation, and then, a data processing software such as EXCEL or ORIGIN is used to transform the obtained time-domain transformation function Fp (t) of the pressure pulsation to the time-domain transformation function Fc (t) of the pressure pulsation coefficient Cr, achieving dimensionlessness of the selected variable, wherein Cp = pP, p is a static pressure at the -2pu monitoring point at the outlet of the impeller, 77 s an average static pressure at the monitoring point at the outlet of the impeller in 1 rotation period, p is a fluid density, and u is a circumferential velocity at the monitoring point at the outlet of the impeller.
Preferably, in the Step 2, specifically, (1) Fast Fourier transform is applied to transform the obtained time-domain transformation function Fc (0 of the pressure pulsation coefficient to the corresponding frequency-domain transformation function by a data analysis software such as ORIGIN or MATLAB; (2) a data analysis software such as MATLAB, EXCEL or ORIGIN is used to perform the global search on the frequency-domain transformation function obtained in the Step (I) to rank the data of the frequency points in the descending order according to their amplitudes and select the three frequency points with amplitudes ranked top three as the calculation frequency points. Preferably, in the Step 3, specifically, S1: a matrix A of intermediate judgment layers is constructed according to the relationship between the three calculation frequency points and their amplitudes, specifically, the data of the three calculation frequency points are ranked in the descending order according to their amplitudes as (fi,A1), (12,A2), (,A;), and a value of an element al (i<j, i and j are selected Ai from 1, 2, or 3) is defined as a positive integer closest to bti, wherein bii= aii-, and ali=1; a,j aii means that regarding the importance of the amplitude of the calculation frequency point to the flow-induced vibration of the pump, the importance of the amplitude of the ith calculation frequency point is times greater than that of the amplitude of the jth calculation frequency point, for example, a12=3 means that the importance of the amplitude of the first calculation frequency point to the overall vibration of the pump is 3 times greater than that of the amplitude of the second calculation frequency point. The matrix A of the intermediate judgment layers is constructed as A = all a21 a12 a13.\ using aii in such a manner that the Analytic Hierarchy Process organically asl a92 a3, a39 33 combines qualitative and quantitative methods to ensure that the weight factors obtained are appropriate and correct; S2: the matrix A of the intermediate judgment layers is subjected to calculation by a normalized column averaging method to obtain the weight factors of the amplitudes of the calculation frequency points: B = the matrix b," A of the intermediate judgment layers is normalized to a matrix b", b29 b23, wherein b.. a..
baI /332 b33 i.; ai, and then, elements in each row of the matrix B are summed and normalized to obtain a characteristic vector d if = d2 d3 \ wherein by dz 3 -1 3 3 a -' -1 the elements in the matrix W each are the weight factor of the amplitude of each of the calculation frequency points to the flow-induced vibration of the pump; S3: the third-order comprehensive vibration pressure L of the pump is calculated as L=12(di Ai+ dz Az+ d3 A3)pu2, wherein p is a fluid density, and u is a circumferential velocity at the monitoring point at the outlet of the impeller, and the smaller the value of L is, the better the flow-induced vibration performance of the pump is, and the larger the value of L is, the worse the flow-induced vibration performance of the pump is.
Preferably, the data analysis software is MATLAB software or ORIGIN software.
The present invention has the following beneficial effects.
(1) The analysis process of the pressure pulsation is based on the pressure pulsation coefficient as a dimensionless variable, which means that the present invention can be used to evaluate the vibration performance of different types of pumps under different working conditions, and has a broad application prospect.
(2) Analytic Hierarchy Process (AHP) is used to obtain weight factors of amplitudes of different frequency points, which can more comprehensively express the importance of the amplitude of each frequency point to the flow-induced vibration performance of the pump.
(3) The evaluation method according to the present invention involves the three frequency points with the top three amplitudes in the frequency domain, and therefore, the calculated third-order comprehensive vibration pressure of the pump can reflect the flow-induced vibration performance of the pump more comprehensively and concisely.
Brief Description of the Drawings
FIG. I is a flowchart of a comprehensive evaluation method for flow-induced vibration performance of a pump according to the present invention.
FIG. 2 is a graph showing time-domain transformation of a pressure pulsation coefficient at an outlet of a pump in an embodiment FIG. 3 is a graph showing frequency-domain transformation of a pressure pulsation coefficient at an outlet of a pump in an embodiment.
Detailed Description of the Embodiments
The present invention will be further described below in conjunction with the drawings and specific embodiments, but the protection scope of the present invention is not limited thereto.
In this embodiment, a five-stage centrifugal pump with a specific speed of 27 is chosen for illustration. The five-stage centrifugal pump has a design flow 0,=5 m3/h, a head H=36 m, and a rotational speed n=2900 emin. Moreover, the five-stage centrifugal pump has an impeller in which the number z of blades is z=8, and a diffuser with 6 blades.
As shown in FIG. 1, a comprehensive evaluation method for flow-induced vibration performance of a pump includes the following steps: Step 1: An outlet of the impeller is selected as a monitoring point, and then, pressure pulsation data at the monitoring point are obtained by an experimental test or numerical calculation, and a time-domain transformation function of a dimensionless pressure pulsation coefficient is calculated, specifically, (1) the outlet of the impeller is selected as the monitoring point, and then, the pressure pulsation data at the monitoring point are obtained by the experimental test or numerical calculation. In this embodiment, the pressure pulsation data are obtained by the numerical calculation, correct steady-state calculation results are set as initial conditions of an unsteady-state calculation, and an unsteady-state calculation time step At s set as At= (-360) T = 5.7471e -6.
The total calculation time is set as 7T=0.14483 s. The data in the last two rotation periods are selected as the pressure pulsation data; (2) invalid data are removed from the pressure pulsation data, and the resulting pressure pulsation data are matched with time information to obtain a time-domain transformation function Fp (t) of pressure pulsation, and then, EXCEL software is used to transform the obtained time-domain transformation function Fp (t) of the pressure pulsation to the time-domain transformation function F (t) of the pressure pulsation coefficient Cp, as shown in FIG. 2, achieving the dimensionlessness, where Cp = p is a static pressure at the monitoring point at the outlet of the impeller, T9 is an average static pressure at the monitoring point at the outlet of the impeller in 1 rotation period, p is a fluid density, and u is a circumferential velocity at the monitoring point at the outlet of the impeller.
Step 2: Fast Fourier transform is applied to transform the time-domain transformation function of the pressure pulsation coefficient to a frequency-domain transformation function, as shown in FIG. 3, which then is subjected to a global frequency domain search to rank frequency points in a descending order according to their amplitudes and select the top three frequency points as calculation frequency points, specifically, (1) Fast Fourier transform is applied to transform the obtained time-domain transformation function Fc (t) of the pressure pulsation coefficient to the corresponding frequency-domain transformation function by MATLAB software; (2) ORIGIN software is used to perform the global search on the frequency-domain transformation function obtained in the Step (1) to rank the data of the frequency points in the descending order according to their amplitudes and select the three frequency points with amplitudes ranked top three as the calculation frequency points.
Step 3: Analytic Hierarchy Process (AHP) is used to determine weight factors of the amplitudes of the three calculation frequency points in the comprehensive evaluation method, and by calculating the amplitude of each of the calculation frequency points and the corresponding weight factor, a third-order comprehensive vibration pressure of the pump is obtained to evaluate the flow-induced vibration performance of the pump based thereon, and the higher the third-order comprehensive vibration pressure of the pump is, the worse the flow-induced vibration performance of the pump is, specifically, S 1: a matrix A of intermediate judgment layers is constructed according to the relationship between the three calculation frequency points and their amplitudes, specifically; the data of the three calculation frequency points are ranked in the descending order according to their amplitudes as (fi,Ai), (n,A2), (h,A3), and the specific values of (fi,AI), (f,A2), and (f3,A3) are (386.667,0.0246), (48.333,0.0041), and (870,0.0024), respectively.
A value of an element aij (i<j, i and j are selected from 1, 2, or 3) is defined as a positive Ai
-
integer closest to IN, where bij=, aji, and ad=1; aii means that regarding the importance of the Ai au amplitude of the calculation frequency point to the flow-induced vibration of the pump, the importance of the amplitude of the calculation frequency point is ay times greater than that of the Ai amplitude of the jth calculation frequency point. In this embodiment, using the formula bu-, it is A j determined that b12=6, '313=10.25, and b23=1.7083, and positive integers closest to these values are taken and defined as ail, an, and an whose specific values are 6, 10, and 2, respectively. Therefore, the specific values of the elements of the intermediate judgment layers are as follows: all=1, a12=6, a13=10, a2.1=1/6, a22=1, a23=2, a31=1/10, a32=1/2, and a33=1, which are used to construct the matrix A 1 6 10v of the intermediate judgment layers as A = 1 / 6 1 2; A /10 1/2 1 52: the matrix A of the intermediate judgment layers is subjected to calculation by a normalized column averaging method to obtain the weight factors of the amplitudes of the calculation frequency points: the matrix A of the intermediate judgment layers is normalized to a matrix B = 7b11 -h 19 b13 b93, that is B = (0.7895 0.8 0.7692, where bi; ai i, and then, -11 1129 1133 y 0.1316 0.1333 0.1538 1121 fis, 0.0789 0.0667 0.0769 1131 - ./ 1 8'11 j =1 elements in each row of the matrix B are summed and normalized to obtain a characteristic vector W = di\ d2, that is W = \ 0.7862 0.1396 0.0742y, where di h". , the elements in the matrix 1,1,1 each are \-d3 1-1 "ij 1-1 1-1 the weight factor of the amplitude of each of the calculation frequency points to the flow-induced vibration of the pump, and therefore, the weight factors d of the calculation frequency points to the overall vibration performance of the pump each are di=0.7862, d2=0.1396, and d3=0.0742; S3: the third-order comprehensive vibration pressure L of the pump is calculated as L= (d1 Al+ dz Az+ d3 A3)pu2, where p is the fluid density, and u is the circumferential velocity at the monitoring point at the outlet of the impeller, and the smaller the value of L is, the better the flow-induced vibration performance of the pump is, and the larger the value of L is, the worse the flow-induced vibration performance of the pump is. In this embodiment, 1_,-(0. 7862* O. 0246+0.1396* O. 0041+0 0742*0. 0024)* 93200=1872. 4775, which can be used for comprehensive evaluation and comparison of flow-induced vibration performance between the selected pump and other pumps. A pump with a smaller 11 value has better flow-induced vibration performance than a pump with a larger L value.
The embodiment is preferred implementation of the present invention, but the present invention is not limited to the above embodiment. Without departing from the essence of the present invention, those skilled in the art can make any obvious modifications, substitutions or variations, and these all fall within the protection scope of the present invention.
Claims (1)
- Claims What is claimed is: 1. A comprehensive evaluation method for flow-induced vibration performance of a pump, characterized by comprising the following steps: Step l: selecting an outlet of an impeller as a monitoring point, and by an experimental test or numerical calculation, obtaining pressure pulsation data at the monitoring point, and calculating a time-domain transformation function of a dimensionless pressure pulsation coefficient; Step 2: applying Fast Fourier transform to transform the time-domain transformation function of the pressure pulsation coefficient to a frequency-domain transformation function, which then is subjected to a global frequency domain search to rank frequency points in a descending order according to their amplitudes and select the top three frequency points as calculation frequency points; and Step 3: using Analytic Hierarchy Process (ARP) to determine weight factors of the amplitudes of the three calculation frequency points in comprehensive evaluation for the flow-induced vibration of the pump, and by calculating the amplitude of each of the calculation frequency points and the corresponding weight factor, obtaining a third-order comprehensive vibration pressure of the pump to evaluate the flow-induced vibration performance of the pump based thereon, wherein the higher the third-order comprehensive vibration pressure of the pump is, the worse the flow-induced vibration performance of the pump is, and the lower the third-order comprehensive vibration pressure of the pump is, the better the flow-induced vibration performance of the pump is 2. The comprehensive evaluation method for the flow-induced vibration performance of the pump according to claim 1, characterized in that in the Step 1, if the data are obtained by the experimental test, the outlet of the impeller is selected as the monitoring point and is subjected to data sampling after the pump runs steadily, at a sampling frequency L selected as 1000 fi for a duration t=2T, whereinfi is a shaft frequency of the pump, and T is a rotation period of the pump to be tested; and if the pressure pulsation data are obtained by the numerical calculation, correct steady-state calculation results are set as initial conditions of an unsteady-state calculation, and an unsteady-state calculation time step At is set as At= (-360)T, a total calculation time is set as 7T, and the data in the last two rotation periods are selected as the pressure pulsation data.3. The comprehensive evaluation method for the flow-induced vibration performance of the pump according to claim 1, characterized in that in the Step 1, after obtaining the pressure pulsation data, invalid data are removed from the pressure pulsation data, and the resulting pressure pulsation data are matched with time information to obtain a time-domain transformation function Fp (t) of pressure pulsation, and then, a data processing software is used to transform the obtained time-domain transformation function Fp (t) of the pressure pulsation to the time-domain transformation function Fc(t) of the pressure_pulsation coefficient Cp, achieving dimens onlessness, wherein an -rPT,p isa static pressure at 7pu the monitoring point at the outlet of the impeller, T, is an average static pressure at the monitoring point at the outlet of the impeller in 1 rotation period, p is a fluid density, and u is a circumferential velocity at the monitoring point at the outlet of the impeller.4. The comprehensive evaluation method for the flow-induced vibration performance of the pump according to claim 1, characterized in that in the Step 2, specifically, (1) Fast Fourier transform is applied to transform the obtained time-domain transformation function Fc (0 of the pressure pulsation coefficient to the corresponding frequency-domain transformation function by a data analysis software; (2) a data analysis software is used to perform the global search on the frequency-domain transformation function obtained in the Step (1) to rank the data of the frequency points in the descending order according to their amplitudes and select the three frequency points with amplitudes ranked top three as the calculation frequency points.5. The comprehensive evaluation method for the flow-induced vibration performance of the pump according to claim I, characterized in that in the Step 3, specifically, S I: a matrix A of intermediate judgment layers is constructed according to relationship between the three calculation frequency points and their amplitudes, specifically, the data of the three calculation frequency points are ranked in the descending order according to their amplitudes as (fi,Ai), (fi,A2), (f3,A3), and a value of an element (i<j, i and j are selected Ai from 1, 2, or 3) is defined as a positive integer closest to bi.,, wherein b.;,=,aj and aii=1; a,j at, means that regarding importance of the amplitude of the calculation frequency point to the flow-induced vibration of the pump, the importance of the amplitude of the calculation frequency point is au times greater than that of the amplitude of the jth calculation frequency point, a 1 a 12 a 13 and the matrix A of the intermediate judgment layers is constructed as. A = a 21 12 a 23 using X22 \f3.111 832 an, aii; 52: the matrix A of the intermediate judgment layers is subjected to calculation by a normalized column averaging method to obtain the weight factors of the amplitudes of the calculation frequency points: the matrix A of the intermediate judgment layers is normalized to a matrix wherein all 1=1, and then, elements in each row of the matrix B are summed and (d1\ rf = d2 hi] i =I, the elements normalized to obtain a characteristic vector \i3 wherein di 3 3 in the matrix W each are the weight factor of the amplitude of each of the calculation frequency points to the flow-induced vibration of the pump; S3: the third-order comprehensive vibration pressure L of the pump is calculated as /,-(di A1+ d2 A2+ d3 A3)pu2, wherein p is a fluid density, and u is a circumferential velocity at the monitoring point at the outlet of the impeller, and the smaller the value of L is, the better the flow-induced vibration performance of the pump is, and the larger the value of L is, the worse the flow-induced vibration performance of the pump is.6. The comprehensive evaluation method for the flow-induced vibration performance of the pump according to claim 4, characterized in that the data analysis software is MATLAB software or ORIGIN software.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810361545.3A CN108664710A (en) | 2018-04-20 | 2018-04-20 | A kind of pump flow-induced vibration performance comprehensive evaluation method |
| PCT/CN2018/085521 WO2019200624A1 (en) | 2018-04-20 | 2018-05-04 | Comprehensive evaluation method for pump flow induced vibration performance |
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| GB202016276D0 GB202016276D0 (en) | 2020-11-25 |
| GB2586756A true GB2586756A (en) | 2021-03-03 |
| GB2586756B GB2586756B (en) | 2021-09-08 |
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| GB (1) | GB2586756B (en) |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2019200624A1 (en) | 2019-10-24 |
| CN108664710A (en) | 2018-10-16 |
| GB2586756B (en) | 2021-09-08 |
| GB202016276D0 (en) | 2020-11-25 |
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