WO2019200624A1 - 一种泵流动诱导振动性能综合评价方法 - Google Patents

一种泵流动诱导振动性能综合评价方法 Download PDF

Info

Publication number
WO2019200624A1
WO2019200624A1 PCT/CN2018/085521 CN2018085521W WO2019200624A1 WO 2019200624 A1 WO2019200624 A1 WO 2019200624A1 CN 2018085521 W CN2018085521 W CN 2018085521W WO 2019200624 A1 WO2019200624 A1 WO 2019200624A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
pump flow
frequency
amplitude
induced vibration
Prior art date
Application number
PCT/CN2018/085521
Other languages
English (en)
French (fr)
Inventor
谈明高
廉益超
吴贤芳
刘厚林
王凯
王勇
董亮
Original Assignee
江苏大学
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 江苏大学 filed Critical 江苏大学
Priority to GB2016276.4A priority Critical patent/GB2586756B/en
Publication of WO2019200624A1 publication Critical patent/WO2019200624A1/zh

Links

Images

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
    • F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
    • F04D15/0088—Testing machines
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • 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
    • G—PHYSICS
    • 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
    • G—PHYSICS
    • 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
    • G06F17/16—Matrix or vector computation, e.g. matrix-matrix or matrix-vector multiplication, matrix factorization
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • 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
    • 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
    • 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
    • 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

Definitions

  • the invention relates to the field of fluid mechanical design, in particular to a comprehensive evaluation method for pump flow induced vibration performance.
  • the pump acts as a general-purpose machine and plays an irreplaceable role in many industrial fields. With the development of society, new requirements are placed on the stability of the pump during operation. The lower vibration level not only saves energy and improves performance, but also is critical to ensuring the life of the pump.
  • vibrations of the pump There are two kinds of vibrations of the pump: one is the vibration of the system caused by mechanical vibration, and the other is the vibration caused by the flow induction.
  • the former is mainly affected by design and manufacturing, and has been solved by active control technology, etc., while the latter is mainly caused by unsteady flow inside the pump, and its mechanism of action is still being studied.
  • the pressure pulse action is a specific manifestation of the unsteady flow characteristics in the pump, and is also the main factor that induces the pump flow induced vibration.
  • most of the current analysis methods for pressure pulsation only focus on the amplitude analysis of the main frequency (the frequency corresponding to the maximum amplitude).
  • the secondary main frequency usually the leaf frequency, it may also be the axial frequency, the dynamic and static interference frequency, etc.
  • the amplitude is considered less.
  • these methods can reflect the vibration level of the pump to a certain extent, when the amplitude of the secondary frequency is large, the analysis method is not comprehensive enough. Therefore, there is an urgent need to propose a method that can comprehensively evaluate the pump flow induced vibration performance.
  • no relevant reports on the comprehensive evaluation method of pump flow induced vibration have been reported.
  • the present invention provides a comprehensive evaluation method for pump flow induced vibration performance, which comprehensively reflects the vibration performance of the pump.
  • the present invention achieves the above technical objects by the following technical means.
  • a comprehensive evaluation method for pump flow induced vibration performance comprising the following steps:
  • Step 1 Select the impeller outlet as the monitoring point, use the test test or numerical calculation to obtain the pressure pulsation data of the monitoring point, and calculate the time-domain change function of the dimensionless pressure pulsation coefficient;
  • Step 2 Perform fast Fourier transform on the time-domain variation function of the pressure pulsation coefficient to obtain a frequency domain variation function, perform a full frequency domain search, and select the first three frequencies as the calculation frequency points according to the amplitude from large to small;
  • Step 3 The analytic hierarchy process is used to determine the weighting factor of the amplitude of the calculated frequency point in the overall evaluation of the pump flow induced vibration.
  • the third-order comprehensive vibration of the pump is obtained by calculating the amplitude of each calculated frequency point and the corresponding weighting factor.
  • Pressure, according to the pump third-order comprehensive vibration pressure to evaluate the pump flow induced vibration performance the greater the third-order comprehensive vibration pressure of the pump, the worse the pump flow induced vibration performance, the smaller the third-order comprehensive vibration pressure of the pump, the pump flow The better the induced vibration performance.
  • the outlet of the impeller is selected as the monitoring point, and the data sampling is performed after the pump is stably operated, the sampling frequency f s is selected as 1000f 1 , and f 1 is the axis of the pump.
  • the invalid data in the pressure pulsation data is removed and matched with the time information, and the pressure pulsation time domain variation function F p (t) is obtained, and data processing such as EXCEL or ORIGIN is adopted.
  • the software changes the pressure pulsation time domain variation function F p (t) to the time domain variation function F C (t) of the pressure pulsation coefficient C P to realize the dimensionlessization of the selected variable, wherein p is the static pressure at the monitoring point at the impeller exit; The average static pressure of the monitoring point at the impeller exit during one rotation cycle; ⁇ is the fluid density; u is the circumferential velocity of the monitoring point at the impeller exit.
  • the step two is specifically as follows:
  • step (2) Using MATLAB or EXCEL or ORIGIN data analysis software to globally search the frequency domain variation function obtained in step (1), and arrange the data of each frequency point in order of magnitude from large to small, and select the amplitude row.
  • the frequency points of the first three digits are used as the calculation frequency points.
  • the step three is specifically as follows:
  • the intermediate judgment layer matrix A is constructed according to the relationship between each calculated frequency point and its amplitude, as follows:
  • the data of the three calculated frequency points are arranged in order of magnitude (f 1 , A 1 ), (f 2 , A 2 ), (f 3 , A 3 ), and the elements a ij (i ⁇ The value of j, i and j, 1, 2 or 3) is a positive integer closest to b ij . and
  • the intermediate judgment layer matrix A is normalized to obtain a matrix. among them Each row element of the B matrix is summed and normalized to obtain a feature vector among them
  • the elements in the W matrix are the weighting factors of the amplitude of each calculated frequency point to the pump flow induced vibration;
  • the data analysis software is MATLAB software or ORIGIN software.
  • the intermediate process uses the pressure pulsation coefficient as a dimensionless variable, which is suitable for the vibration performance evaluation of different types of pumps under different working conditions, and has wide application prospects.
  • the evaluation method involves three frequency points with the largest amplitude in the frequency domain.
  • the calculated third-order comprehensive vibration pressure of the pump can reflect the pump flow-induced vibration performance comprehensively and succinctly.
  • FIG. 1 is a flow chart of a comprehensive evaluation method for pump flow induced vibration performance according to the present invention.
  • Figure 2 is a time-domain diagram of the pressure pulsation coefficient at the pump outlet in the embodiment.
  • Figure 3 is a graph showing the frequency domain variation of the pressure pulsation coefficient at the pump outlet in the embodiment.
  • a comprehensive evaluation method for pump flow induced vibration performance includes the following steps:
  • Step 1 Select the impeller outlet as the monitoring point, use the test test or numerical calculation to obtain the pressure pulsation data of the monitoring point, and calculate the time-domain change function of the dimensionless pressure pulsation coefficient, as follows:
  • Step 2 Perform a fast Fourier change on the time-domain variation function of the pressure pulsation coefficient to obtain a frequency domain variation function. As shown in FIG. 3, perform a full frequency domain search, and select the first three frequencies according to the amplitude from large to small. The frequency point is as follows:
  • step (2) Using ORIGIN software to globally search the frequency domain variation function obtained in step (1), and arrange the data of each frequency point in order of magnitude from large to small, and select the frequency points whose amplitude is ranked in the first three digits. As a calculation frequency point.
  • Step 3 Determine the weighting factor of the amplitude of the calculated frequency point in the comprehensive evaluation method by using the analytic hierarchy process, and calculate the third-order comprehensive vibration pressure of the pump by calculating the amplitude of each calculated frequency point and its corresponding weighting factor.
  • the pump-induced vibration performance is evaluated. The greater the third-order comprehensive vibration pressure of the pump, the worse the pump flow-induced vibration performance is as follows:
  • the intermediate judgment layer matrix A is constructed according to the relationship between each calculated frequency point and its amplitude, as follows:
  • the data of the three calculated frequency points are arranged in order of magnitude (f 1 , A 1 ), (f 2 , A 2 ), (f 3 , A 3 ), (f 1 , A 1 ) according to the amplitude.
  • specific values are (386.667, 0.0246), (48.333, 0.0041), (870, 0.0024).
  • the intermediate judgment layer matrix A is normalized to obtain a matrix. which is among them
  • Each row element of the B matrix is summed and normalized to obtain a feature vector which is among them
  • the elements in the W matrix are the weighting factors of the amplitude of each calculated frequency point to the pump flow induced vibration.
  • a pump with a small L value has a flow-induced vibration performance superior to a pump with a large L value.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Theoretical Computer Science (AREA)
  • Geometry (AREA)
  • Mathematical Physics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mathematical Optimization (AREA)
  • Pure & Applied Mathematics (AREA)
  • Mathematical Analysis (AREA)
  • Computational Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
  • Data Mining & Analysis (AREA)
  • Mechanical Engineering (AREA)
  • Algebra (AREA)
  • Databases & Information Systems (AREA)
  • Software Systems (AREA)
  • Computing Systems (AREA)
  • Discrete Mathematics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)

Abstract

一种泵流动诱导振动性能综合评价方法，首先利用试验测试或数值计算得到泵叶轮出口处的压力脉动数据并计算出无量纲压力脉动系数时域变化函数；然后对上述时域变化函数进行快速傅里叶变化获得频域变化函数，之后进行全频域搜索，按幅值从大到小排列并选取前三个频率点作为计算频率点；接着采用层次分析法确定各计算频率点的幅值在泵流动诱导振动整体评价中的权重因子，最终通过对各个计算频率点的幅值和与之对应的权重因子的计算获得泵三阶综合振动压强来评价泵整体振动水平。该方法综合考虑泵叶轮出口压力脉动变化函数在频域上多个频率点的幅值，克服了以往只考虑主频处振动幅值来衡量泵振动性能的片面性，具有广泛的工程应用价值。

Description

一种泵流动诱导振动性能综合评价方法 技术领域
本发明涉及流体机械设计领域，特指涉及一种泵流动诱导振动性能综合评价方法。
背景技术
泵作用一种通用机械，在众多工业领域中发挥着不可取代的重要作用。随着社会的发展，对泵运行时的稳定性提出了新的要求，较低的振动水平不但可以节省能量提高性能，而且对保证泵的寿命也至关重要。
泵的振动有两种：一是机械振动引起的系统振动，二是流动诱导引起的振动。前者主要是受设计和制造影响，现已通过主动控制技术等得到了较好的解决，而后者主要是由于泵内部的非定常流动所引起的，其作用机理还在不断的研究中。压力脉动作为泵内非定常流动特征的具体表现形式，同时也是引发泵流动诱导振动的主要因素。但是目前对于压力脉动的分析方法大多只关注主频处(最大幅值对应的频率)的幅值分析，对于次主频处(通常是叶频，也可能是轴频、动静干涉频率等)的幅值考虑的较少。虽然这些方法能够在一定程度上反应泵的振动水平，但当次主频等频率处的幅值较大时，这种分析方法就显得不够全面。因此，急需提出一种能够综合评价泵流动诱导振动性能的方法。但是迄今为止，尚未见泵流动诱导振动综合评价方法的相关报道。
发明内容
针对现有技术中存在不足，本发明提供了一种泵流动诱导振动性能综合评价方法，较为全面地反映泵的振动性能。
本发明是通过以下技术手段实现上述技术目的的。
一种泵流动诱导振动性能综合评价方法，包含以下步骤：
步骤一：选取叶轮出口处作为监测点，采用试验测试或数值计算得到监测点的压力脉动数据，并计算出无量纲化的压力脉动系数时域变化函数；
步骤二：对压力脉动系数时域变化函数进行快速傅里叶变化以获得频域变化函数，进行全频域搜索，按幅值从大到小选取前三个频率为计算频率点；
步骤三：采用层次分析法确定计算频率点的幅值在泵流动诱导振动整体评价中的权重因子，通过对各个计算频率点的幅值和与之对应的权重因子的计算获得泵三阶综合振动压强，根据所述泵三阶综合振动压强评判泵流动诱导振动性能，所述泵三阶综合振动压强越大，则泵流动诱导振动性能越差，泵三阶综合振动压强越小，则泵流动诱导振动性能越好。
优选地，所述步骤一中，利用试验测试获取数据时，选取叶轮出口处作为监测点，当泵稳定运行后方可进行数据采样，采样频率f s选定为1000f 1，f 1为泵的轴频，持续时间t＝2T，T为待测泵的旋转周期；
利用数值计算获取压力脉动数据时，将正确的定常计算结果设置为非定常计算的初始条件，并设置非定常计算时间步长
Figure PCTCN2018085521-appb-000001
计算总时间为7T，选取最后两个周期内的数据作为压力脉动数据。
优选地，所述步骤一中，获取压力脉动数据后，除去压力脉动数据中的无效数据并与时间信息相匹配，获得压力脉动时域变化函数F p(t)，采用EXCEL或ORIGIN等数据处理软件将得到的压力脉动时域变化函数F p(t)变化为压力脉动系数C P的时域变化函数F C(t)，实现所选变量的无量纲化，其中
Figure PCTCN2018085521-appb-000002
p为叶轮出口处监测点的静压；
Figure PCTCN2018085521-appb-000003
为1个旋转周期内叶轮出口处监测点的平均静压；ρ为流体密度；u为叶轮出口处监测点的圆周速度。
优选地，所述步骤二具体如下：
(1)通过ORIGIN或MATLAB等数据分析软件对得到的压力脉动系数时域变化函数F C(t)进行快速傅里叶变化以获取相应的频域变化函数；
(2)采用MATLAB或EXCEL或ORIGIN等数据分析软件对步骤(1)获取的频域变化函数进行全局搜索，将各频率点的数据按照幅值由大到小的顺序依次排列，选取幅值排在前三位的频率点作为计算频率点。
优选地，所述步骤三具体如下：
S1：根据各计算频率点及其幅值的相互关系构建中间判断层矩阵A，具体如下：
三个所述计算频率点的数据按照幅值由大到小依次排列为(f 1,A 1)、(f 2,A 2)、(f 3,A 3)，定义元素a ij(i<j，i和j的取值为1、2或3)的取值为最接近b ij的一个正整数，
Figure PCTCN2018085521-appb-000004
并且
Figure PCTCN2018085521-appb-000005
a ij的含义为：关于计算频率点幅值对于泵流动诱导振动的重要性，第i个计算频率点幅值为第j个计算频率点幅值的a ij倍，例如：a 12＝3，其含义为：第一个计算频率幅值对泵整体振动的重要性为第二个计算频率的3倍。以a ij构建中间判断层矩阵
Figure PCTCN2018085521-appb-000006
通过这种方式，层次分析法将定性方法与定量方法有机地结合起来，保证了得出的权重因子是合适且正确的。
S2：使用规范列平均法对中间判断层A进行计算，获得各个计算频率点幅值的权重因子；
首先对中间判断层矩阵A进行归一化处理，得到矩阵
Figure PCTCN2018085521-appb-000007
其中
Figure PCTCN2018085521-appb-000008
对B矩阵的每一行元素求和并进行归一化处理得到特征向量
Figure PCTCN2018085521-appb-000009
其中
Figure PCTCN2018085521-appb-000010
W矩阵中的元素即为各计算频率点的幅值对泵流动诱导振动的权重因子；
S3：计算得出泵三阶综合振动压强
Figure PCTCN2018085521-appb-000011
其中ρ为流体密度；u为叶轮出口处监测点的圆周速度，L值越小代表泵流动诱导振动性能越好，L值越大代表泵流动诱导振动性能越差。
优选地，所述数据分析软件为MATLAB软件或ORIGIN软件。
本发明的有益效果：
1)中间过程采用压力脉动系数作为无量纲变量，适用于不同种类泵在不同工况下的振动性能评估，具有广泛的使用前景。
2)利用层次分析法计算出不同频率点幅值的权重因子，能较为全面地表达出各频率点幅值对泵流动诱导振动性能的重要程度。
3)该评价方法涉及了频域上幅值最大的三个频率点，计算出的泵三阶综合振动压强可较全面地、简洁地反映泵流动诱导振动性能。
附图说明
图1为本发明所述一种泵流动诱导振动性能综合评价方法的流程图。
图2为实施例中泵出口处的压力脉动系数时域变化图。
图3为实施例中泵出口处的压力脉动系数频域变化图。
具体实施方式
下面结合附图以及具体实施例对本发明作进一步的说明，但本发明的保护范围并不限于此。
本实施例采用比转数为27的五级离心泵，其设计流量Q＝5m 3/h，扬程H＝36m，转速n＝2900r/min，叶轮叶片数z＝8，导叶数为6。
如图1所示，一种泵流动诱导振动性能综合评价方法，包含以下步骤：
步骤一：选取叶轮出口处作为监测点，采用试验测试或数值计算得到监测点的压力脉动数据，并计算出无量纲化压力脉动系数时域变化函数，具体如下：
1)选取叶轮出口处作为监测点，采用试验测试或数值计算得到监测点的压力脉动数据，本实施例利用数值计算获取压力脉动数据，将正确的定常计算结果设置为非定常计算的初始条件，并设置非定常计算时间步长
Figure PCTCN2018085521-appb-000012
计算总时间为7T＝0.14483s，选取最后两个周期内的数据作为压力脉动数据；
2)除去压力脉动数据中的无效数据并与时间信息相匹配，获得压力脉动时域变化函数F p(t)，采用EXCEL软件软件将得到的压力脉动时域变化函数F p(t)变化为压力脉动系数C P的时域变化函数F C(t)，如图2所示，实现无量纲化，其中
Figure PCTCN2018085521-appb-000013
p为叶轮出口处监测点的静压；
Figure PCTCN2018085521-appb-000014
为1个旋转周期内叶轮出口处监测点的平均静压；ρ为流体密度；u为叶轮出口处监测点的圆周速度。
步骤二：对压力脉动系数时域变化函数进行快速傅里叶变化以获得频域变化函数，如图3所示，进行全频域搜索，按幅值从大到小选取前三个频率为计算频率点，具体如下：
(1)通过MATLAB软件对得到的压力脉动系数时域变化函数F C(t)进行快速傅里叶变化以获取相应的频域变化函数；
(2)采用ORIGIN软件对步骤(1)获取的频域变化函数进行全局搜索，将各频率点的数据按照幅值由大到小的顺序依次排列，选取幅值排在前三位的频率点作为计算频率点。
步骤三：采用层次分析法确定计算频率点的幅值在所述综合评价方法中的权重因子，通过对各个计算频率点的幅值和其对应的权重因子进行计算获得泵三阶综合振动压强，根据所述泵三阶综合振动压强评判泵流动诱导振动性能，所述泵三阶综合振动压强越大，泵流动诱导振动性能越差，具体如下：
S1：根据各计算频率点及其幅值的相互关系构建中间判断层矩阵A，具体如下：
三个所述计算频率点的数据按照幅值由大到小依次排列为(f 1,A 1)、(f 2,A 2)、(f 3,A 3)，(f 1,A 1)、(f 2,A 2)、(f 3,A 3)，具体数值为(386.667,0.0246)、(48.333,0.0041)、(870,0.0024)。
定义元素a ij(i<j，i和j的取值为1、2或3)的取值为最接近b ij的一个正整数，
Figure PCTCN2018085521-appb-000015
并且
Figure PCTCN2018085521-appb-000016
a ii＝1，a ij的含义为：关于计算频率点幅值对于泵流动诱导振动的重要性，第i个计算频率点幅值为第j个计算频率点幅值的a ij倍，利用公式
Figure PCTCN2018085521-appb-000017
确定b 12＝6,b 13＝10.25,b 23＝1.7083，取这些数值最接近的正整数，并定义为a 12、a 13、a 23、其具体数值分别为6、10、2。则具体的中间判断层各元素取值如下：a 11＝1、a 12＝6、a 13＝10、a 21＝1/6、 a 22＝1、a 23＝2、a 31＝1/10、a 32＝1/2、a 33＝1。以此构建中间判断层矩阵
Figure PCTCN2018085521-appb-000018
S2：使用规范列平均法对中间判断层A进行计算，获得各个计算频率点幅值的权重因子；
首先对中间判断层矩阵A进行归一化处理，得到矩阵
Figure PCTCN2018085521-appb-000019
即
Figure PCTCN2018085521-appb-000020
其中
Figure PCTCN2018085521-appb-000021
对B矩阵的每一行元素求和并进行归一化处理得到特征向量
Figure PCTCN2018085521-appb-000022
即
Figure PCTCN2018085521-appb-000023
其中
Figure PCTCN2018085521-appb-000024
W矩阵中的元素即为各计算频率点的幅值对泵流动诱导振动的权重因子，则各个计算频率点对泵的整体振动性能的权重因子d分别为d 1＝0.7862，d 2＝0.1396，d 3＝0.0742。
S3：计算得出泵三阶综合振动压强
Figure PCTCN2018085521-appb-000025
其中ρ为流体密度；u为叶轮出口处监测点的圆周速度，L值越小代表泵流动诱导振动性能越好，L值越大代表泵流动诱导振动性能越差。本实施例中
L＝(0.7862*0.0246+0.1396*0.0041+0.0742*0.0024)*93200＝1872.4775，根据此数值可以进行被选泵和其他泵之间的流动诱导振动性能综合评估与比较。L数值小的泵，其流动诱导振动性能优于L数值大的泵。
所述实施例为本发明的优选的实施方式，但本发明并不限于上述实施方式，在不背离本发明的实质内容的情况下，本领域技术人员能够做出的任何显而易见的改进、替换或变型均属于本发明的保护范围。

Claims (6)

  1. 一种泵流动诱导振动性能综合评价方法，其特征在于，包含以下步骤：
    步骤一：选取叶轮出口处作为监测点，采用试验测试或数值计算得到监测点的压力脉动数据，并计算出无量纲化的压力脉动系数时域变化函数；
    步骤二：对压力脉动系数时域变化函数进行快速傅里叶变化以获得频域变化函数，进行全频域搜索，按幅值从大到小选取前三个频率点为计算频率点；
    步骤三：采用层次分析法确定计算频率点的幅值在泵流动诱导振动综合评价中的权重因子，通过对各个计算频率点的幅值和与之对应的权重因子进行计算获得泵三阶综合振动压强，根据所述泵三阶综合振动压强评判泵流动诱导振动性能，所述泵三阶综合振动压强越大，则泵流动诱导振动性能越差，泵三阶综合振动压强越小，则泵流动诱导振动性能越好。
  2. 根据权利要求1所述的泵流动诱导振动性能综合评价方法，其特征在于，
    所述步骤一中，利用试验测试获取数据时，选取叶轮出口处作为监测点，当泵稳定运行后方可进行数据采样，采样频率f s选定为1000f 1，f 1为泵的轴频，持续时间t＝2T，T为待测泵的旋转周期；
    利用数值计算获取压力脉动数据时，将正确的定常计算结果设置为非定常计算的初始条件，并设置非定常计算时间步长
    Figure PCTCN2018085521-appb-100001
    计算总时间为7T，选取最后两个周期内的数据作为压力脉动数据。
  3. 根据权利要求1所述的泵流动诱导振动性能综合评价方法，其特征在于，
    所述步骤一中，获取压力脉动数据后，除去压力脉动数据中的无效数据并与时间信息相匹配，获得压力脉动时域变化函数F p(t)，采用数据处理软件将得到的压力脉动时域变化函数F p(t)变化为压力脉动系数C P的时域变化函数F C(t)，实现无量纲化，其中
    Figure PCTCN2018085521-appb-100002
    p为叶轮出口处监测点的静压；
    Figure PCTCN2018085521-appb-100003
    为1个旋转周期内叶轮出口处监测点的平均静压；ρ为流体密度；u为叶轮出口处监测点的圆周速度。
  4. 根据权利要求1所述的泵流动诱导振动性能综合评价方法，其特征在于，所述步骤二具体如下：
    (1)通过数据分析软件对得到的压力脉动系数时域变化函数F C(t)进行快速傅里叶变化以获取相应的频域变化函数；
    (2)采用数据分析软件对步骤(1)获取的频域变化函数进行全局搜索，将各频率点的数据按照幅值由大到小的顺序依次排列，选取幅值排在前三位的频率点作为计算频率点。
  5. 根据权利要求1所述的泵流动诱导振动性能综合评价方法，其特征在于，所述步骤三具体如下：
    S1：根据各计算频率点及其幅值的相互关系构建中间判断层矩阵A，具体如下：
    三个所述计算频率点的数据按照幅值由大到小依次排列为(f 1，A 1)、(f 2，A 2)、(f 3，A 3)，定义元素a ij(i＜j，i和j的取值为1、2或3)的取值为最接近b ij的一个正整数，
    Figure PCTCN2018085521-appb-100004
    并且
    Figure PCTCN2018085521-appb-100005
    a ii＝1；
    a ij的含义为：关于计算频率点幅值对于泵流动诱导振动的重要性，第i个计算频率点幅值为第j个计算频率点幅值的a ij倍，以a ij构建中间判断层矩阵
    Figure PCTCN2018085521-appb-100006
    S2：使用规范列平均法对中间判断层A进行计算，获得各个计算频率点幅值的权重因子；
    首先对中间判断层矩阵A进行归一化处理，得到矩阵
    Figure PCTCN2018085521-appb-100007
    其中
    Figure PCTCN2018085521-appb-100008
    对B矩阵的每一行元素求和并进行归一化处理得到特征向量
    Figure PCTCN2018085521-appb-100009
    其中
    Figure PCTCN2018085521-appb-100010
    W矩阵中的元素即为各计算频率点的幅值对泵流动诱导振动的权重因子；
    S3：计算得出泵三阶综合振动压强
    Figure PCTCN2018085521-appb-100011
    其中ρ为流体密度；u为叶轮出口处监测点的圆周速度，L值越小代表泵流动诱导振动性能越好，L值越大代表泵流动诱导振动性能越差。
  6. 根据权利要求4所述的泵流动诱导振动性能综合评价方法，其特征在于，所述数据分析软件为MATLAB软件或ORIGIN软件。
PCT/CN2018/085521 2018-04-20 2018-05-04 一种泵流动诱导振动性能综合评价方法 WO2019200624A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
GB2016276.4A GB2586756B (en) 2018-04-20 2018-05-04 Comprehensive evaluation method for flow-induced vibration performance of pump

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201810361545.3 2018-04-20
CN201810361545.3A CN108664710A (zh) 2018-04-20 2018-04-20 一种泵流动诱导振动性能综合评价方法

Publications (1)

Publication Number Publication Date
WO2019200624A1 true WO2019200624A1 (zh) 2019-10-24

Family

ID=63780721

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2018/085521 WO2019200624A1 (zh) 2018-04-20 2018-05-04 一种泵流动诱导振动性能综合评价方法

Country Status (3)

Country Link
CN (1) CN108664710A (zh)
GB (1) GB2586756B (zh)
WO (1) WO2019200624A1 (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112539828A (zh) * 2020-12-08 2021-03-23 中水三立数据技术股份有限公司 基于曲线拟合对比分析的泵组设备诊断方法、系统、设备
CN112667958A (zh) * 2020-12-25 2021-04-16 淮安市水利勘测设计研究院有限公司 一种基于能量特征的出水流道脉动分析方法
CN114251277A (zh) * 2021-12-22 2022-03-29 南水北调东线江苏水源有限责任公司 一种通过对比泵段前后水流脉动情况监测水泵运行工况的方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2600280B (en) * 2019-09-25 2023-06-07 Halliburton Energy Services Inc Method of calculating viscous performance of a pump from its water performance characteristics and new dimensionless parameter for controlling and monitoring
CN115076085B (zh) * 2022-06-10 2023-06-23 西安理工大学 水泵站吸入管内部流动状态的压力脉动识别方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2169497B1 (en) * 2008-09-30 2013-07-10 Rockwell Automation Technologies, Inc. Dynamic vibration condition monitoring parameter normalization system and method
CN103631989A (zh) * 2013-10-23 2014-03-12 江苏大学 一种离心泵流动诱导噪声数值预测方法
CN106503323A (zh) * 2016-10-17 2017-03-15 江苏大学 一种多级离心泵流动诱导结构辐射噪声数值预测方法
CN107273565A (zh) * 2017-05-04 2017-10-20 江苏大学 一种基于les/lbm的离心泵内流动诱导噪声数值计算方法
CN107643180A (zh) * 2016-07-21 2018-01-30 北京航天动力研究所 基于小波分析的高速低温涡轮泵轴承保持架故障诊断方法

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010277249A (ja) * 2009-05-27 2010-12-09 Toshiba Corp 飛しょう体の形状決定方法及び形状決定装置
CN105465037B (zh) * 2015-12-01 2017-11-17 中国农业大学 一种双吸离心泵叶轮的水力优化方法以及装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2169497B1 (en) * 2008-09-30 2013-07-10 Rockwell Automation Technologies, Inc. Dynamic vibration condition monitoring parameter normalization system and method
CN103631989A (zh) * 2013-10-23 2014-03-12 江苏大学 一种离心泵流动诱导噪声数值预测方法
CN107643180A (zh) * 2016-07-21 2018-01-30 北京航天动力研究所 基于小波分析的高速低温涡轮泵轴承保持架故障诊断方法
CN106503323A (zh) * 2016-10-17 2017-03-15 江苏大学 一种多级离心泵流动诱导结构辐射噪声数值预测方法
CN107273565A (zh) * 2017-05-04 2017-10-20 江苏大学 一种基于les/lbm的离心泵内流动诱导噪声数值计算方法

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112539828A (zh) * 2020-12-08 2021-03-23 中水三立数据技术股份有限公司 基于曲线拟合对比分析的泵组设备诊断方法、系统、设备
CN112667958A (zh) * 2020-12-25 2021-04-16 淮安市水利勘测设计研究院有限公司 一种基于能量特征的出水流道脉动分析方法
CN114251277A (zh) * 2021-12-22 2022-03-29 南水北调东线江苏水源有限责任公司 一种通过对比泵段前后水流脉动情况监测水泵运行工况的方法

Also Published As

Publication number Publication date
CN108664710A (zh) 2018-10-16
GB2586756B (en) 2021-09-08
GB202016276D0 (en) 2020-11-25
GB2586756A (en) 2021-03-03

Similar Documents

Publication Publication Date Title
WO2019200624A1 (zh) 一种泵流动诱导振动性能综合评价方法
Wang et al. Numerical and experimental study on the pressure fluctuation, vibration, and noise of multistage pump with radial diffuser
Bin et al. Early fault diagnosis of rotating machinery based on wavelet packets—Empirical mode decomposition feature extraction and neural network
CN108959778B (zh) 一种基于退化模式一致性的航空发动机剩余寿命预测方法
WO2020019681A1 (zh) 采油设备故障诊断方法及装置
WO2023010658A1 (zh) 一种基于时间扩张卷积网络的压气机旋转失速预警方法
CN109000921B (zh) 一种风电机组主轴故障的诊断方法
Lu et al. Fault diagnosis of rolling bearing based on improved VMD and KNN
CN108645620A (zh) 一种基于信息熵和多尺度形态学的滚动轴承早期故障诊断方法
US11740122B2 (en) Autonomous discrimination of operation vibration signals
WO2023093315A1 (zh) 振动信号的特征提取方法、设备分析方法及装置
CN110610026B (zh) 一种航空发动机喘振先兆的在线识别方法
Muralidharan et al. Wavelet decomposition and support vector machine for fault diagnosis of monoblock centrifugal pump
Zhang et al. A new regularized adaptive windowed Lomb periodogram for time–frequency analysis of nonstationary signals with impulsive components
Zheng et al. Hydrodynamic feature extraction and intelligent identification of flow regimes in vaneless space of a pump turbine using improved empirical wavelet transform and Bayesian optimized convolutional neural network
Zheng et al. Zero-phase filter-based adaptive Fourier decomposition and its application to fault diagnosis of rolling bearing
Bianchi et al. Demonstration of a stall detection system for induced draft fans
CN112528805A (zh) 一种水轮机压力脉动分析方法、装置、设备及存储介质
Cheng et al. Convolutive blind source separation in the frequency domain of mechanical noise for gas turbines based on bounded component analysis
CN110162813B (zh) 一种叶轮机械气动阻尼计算方法
Liu et al. An approximate maximum likelihood estimator for instantaneous frequency estimation of multicomponent nonstationary signals
CN111158974B (zh) 一种面向云服务器的硬件感知cpu能耗测算方法
Li et al. Fault feature extraction method based on EWT-SMF and MF-DFA for valve fault of reciprocating compressor
CN117349661B (zh) 柱塞泵振动信号特征提取方法、装置、设备和存储介质
Liu et al. Cavitation diagnosis method of centrifugal pump based on characteristic frequency and kurtosis

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18915698

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 202016276

Country of ref document: GB

Kind code of ref document: A

Free format text: PCT FILING DATE = 20180504

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18915698

Country of ref document: EP

Kind code of ref document: A1