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离心泵相关国内国外的文献2篇

时间：2025-01-03 分类：国际英文期刊常识浏览量：

　　离心泵国内范文参考一：

　　随着工业现代化进程的不断加快，各种机械设备也不断应用于化工生产中，化工离心泵作为一种重要的流体运输设备，在化工企业生产中发挥着非常重要的作用。作为一种需要长期高负荷运转的机械设备，化工离心泵在使用过程中出现一些故障问题也是在所难免的，如运行异响、电机过载、轴承过热等，都是化工离心泵在使用过程中的常见问题。为提高离心泵的运行稳定性，通过找出具有针对性的故障诊断方法，满足企业生产对离心泵作用稳定性的需求。

　　2 化工用离心泵概述

　　为了保证化工生产的正常运行，离心泵的选型和安装必须达到化工生产的技术要求。对离心泵进行必要的维护保养，提高设备运行的效率，满足输送介质的需要。化工用离心泵在设计时，优先考虑防腐问题，优选耐腐蚀的离心泵，防止介质的高腐蚀性，而影响到离心泵的使用寿命。

　　在生产过程中，使用离心泵输送液体，油品中含有的杂质物质对离心泵具有腐蚀作用。加强对离心泵的维护保养，避免离心泵故障而影响到生产工艺的顺利进行。对离心泵的各个组成部件进行防腐处理，保养过程中检查离心泵部件的腐蚀程度，如果达不到设备的性能，需要及时进行更换，尤其针对离心泵的叶轮，一旦出现沙眼或者变形后，会影响到输送介质的流量和压力，必须更换新的叶轮，使离心泵运行时，达到输送介质

　　化工离心泵的基本工作原理。化工离心泵主要是应用了叶轮高速旋转产生离心力的原理，在泵内充满液体的情况下，由电动机通过联轴器带动叶轮高速旋转，使叶轮槽道中水在离心力的作用下向外甩出进入泵壳，完成对泵内液体的输送;同时，在离心机的作用下，叶轮中心的压力也会降低，并与进水管压力形成压差，水在压力差的作用下由吸水池不断被吸入叶轮，这样离心泵就可以不断地进行吸水和供水，从而满足化工生产需要。

　　3 离心泵故障成因

　　3.1 转子弯曲

　　该类故障的成因在于设备过长时间没有重启，一旦使用，就会出现转子弯曲现象。造成这一现象出现的原因是离心泵设备在停放过程中，未按照相关规范标准进行冷却处理或是在使用过程中转子的速度过快，会导致转子弯曲。

　　3.2 转子与定子摩擦

　　转子与定子间的摩擦故障分轻度与重度摩擦两种。轻度摩擦主要产生于联轴器的罩摩轴。重度摩擦故障则主要产生于电动机转子与定子间的接触。究其原因，是由于转子转动

　　3.3 转子不平衡

　　转子不平衡是由于转子部件出现不同程度的偏心，从而引起离心泵出现原始不平衡、渐发性不平衡以及突发性不平衡。离心泵的故障均可采用对应的控制措施来进行避免，为此，研究人员可从多角度出发，来选用故障诊断技术，以降低故障给企业生产加工过程带来的负面影响。

　　4 离心泵故障诊断措施

　　4.1 离心泵完好的标准

　　离心泵达到完好的标准，才能更好地为化工生产服务。离心泵运转正常，性能优良，压力平稳，输出功率在额定功率的90%以上。润滑系统和冷却系统运行正常，填料密封泄漏量满足生产需求，每分钟10-30滴。离心泵的机件无磨损，零部件齐全好用，能够满足正常输送介质的技术要求。化工生产用泵的特殊性，保证离心泵的抗腐蚀特性，对离心泵的部件进行防腐处理，提高防腐性能。离心泵运行过程中，防止发生泄漏，严重的泄漏事故会引发安全问题。尤其针对汽油、石脑油的生产加工，存在着易燃易爆有毒有害的物质，保证离心泵安全平稳运行，有利于提高化工生产的效率。

　　4.2 人工神经网络诊断

　　该方法基于模拟生物神经系统而构建的具有自适应效果的非线性动力学系统，具有较强的并行计算功能与学习性功能。由于该技术的应用具有知识表达形式的统一性，因此作用于实践，将提高故障诊断知识库组织管理水平以及通用性，从而实现移植与扩展工作开展的便捷性目标。此外，人工神经网络故障诊断方法，还能避免传统智能诊断系统的信息量庞大，导致系统瘫痪问题的出现。由于诊断过程中需要使用众多符号以及知识表达的处理，因此，研究人员还要不断深化其作用于实践的便捷性，从而提高故障诊断的效率。

　　4.3 离心泵的维护保养

　　对离心泵的日常维护保养，及时检查各个部件的运行情况，发现安全隐患及时处理，防止发生严重的事故，而影响到离心泵的正常运行。经常检查离心泵的润滑油，发现油质油位不合格必须及时进行更换，防止加剧机件的磨损，而降低离心泵的使用寿命。在日常的维护保养过程中，必须保持离心泵的清洁，紧固各部位的螺栓，保证无松动滑扣的现象。加注各种润滑油和润滑脂，确保离心泵机组不缺油不干磨。调整离心泵的运行参数，使其在最佳的工况下运行，达到平稳输送介质的目的。

　　对备用泵也需要进行盘车处理，定期对其进行运转，防止泵卡死，一旦运行泵出现故障，或者到维护保养周期需要停泵保养的时候，启动备用泵。对离心泵进行维护保养，是在理解离心泵的结构和工作原理的基础上进行的。对离心泵机械密封失效的解决措施，如果机械密封失效会导致离心泵泄漏，产生泄漏的原因是多方面的，如动环和静环密封面处发生泄漏，补偿环密封圈泄漏，都会引起机械密封的泄漏。一旦发生泄漏，查找原因，采取必要的修复措施，恢复机械密封的正常密封状态。

　　离心泵国外范文参考二：

　　**Abstract**: Marine centrifugal pump is one of the important factors that cause ship vibration, so the research on centrifugal pump vibration is particularly important. In this paper, in order to study the flow-induced vibration characteristics of centrifugal pump, a virtual prototype model of the centrifugal pump is established in finite element method. The theory of Computational fluid dynamics (CFD) is utilized to analyze the inner flow field of the centrifugal pump, and steady-state calculation and transient calculation of the flow field are completed. The fluid forces acquired from the transient calculation results of flow field are used as the excitation loads for the virtual prototype model of the centrifugal pump. The fluid-solid coupling model of the centrifugal pump is built, and the vibration acceleration of the centrifugal pump's foot is calculated, and the flow-induced vibration characteristics of the centrifugal pump are obtained. The data of the centrifugal pump measured in the experiment are consistent with the simulation results. This study provide reference for the fluid-solid coupling method in centrifugal pump fluid field prediction and flow-induced vibration research.

　　**Keywords**: Centrifugal pump, Vibration, Computational fluid dynamics, Finite element

　　## I. INTRODUCTION

　　Centrifugal pump as a widely used hydraulic equipment, a large number of studies have been devoted to the analysis of vibration reasons and regular characteristics of centrifugal pumps [1-3]. The fluid force is the main excitation source of centrifugal pump vibration, Computational fluid dynamics (CFD) is increasingly used to simulate fluid flow in the centrifugal pump [4-6]. The theory of CFD is utilized to analyze the inner flow field of the centrifugal pump, and analysis of vibration characteristics of the centrifugal pump. Regarding the influence of fluid excitation force on vibration, a large number of studies have begun to focus on the simulation of the internal flow field and the analysis of the law of pressure pulsation. The one-way fluid-structure interaction approach is presented to predict the vibrations at specific operating conditions[7,8].In order to determine the vibration of the pump rotor caused by the excitation force, Benra ed al.[9] uses one-way coupling and two-way coupling to solve the mechanical coupling of the flowfield in the pump and the structure of the pump rotor. Comparing the two calculation results with experiments and found that the latter calculation result is better. Si et al. [10] established a two-way fluid-solid coupling calculation model for the rotor system including the impeller and shaft, obtained the stress and deformation distribution of the rotor system, and proposed a set of optimization methods for the geometric parameters of the impeller.

　　In order to explore the vibration characteristics of the centrifugal pump, this paper simulates the internal flow field of the centrifugal pump based on the CFD theory. The fluid excitation of the internal flow field is calculated, the fluid-solid coupling model is established, the vibration acceleration of the centrifugal pump foot is calculated, and the flow-induced vibration characteristics of the centrifugal pump are obtained. The data of the centrifugal pump measured in the experiment are consistent with the simulation results. This study provide reference for the fluid-solid coupling method in centrifugal pump performance prediction and flow-induced vibration research.

　　## II. MATERIALS AND METHODS

　　In this chapter, a virtual prototype model of the centrifugal pump is established in finite element method. Based on hydrodynamic theory, a calculation model for fluid field is established in the computational fluid dynamics software Fluent.

　　### A. Pump structure and parameters

　　The research object of this paper is a single-stage vertical electric centrifugal pump. The whole centrifugal pump unit is divided into two parts, the pump and the motor. The coaxial design is adopted to avoid the torque and bending moment caused by the misalignment of the rotor. The blade structure is 5 long blades and 5 short blades, and adopts a closed structure design. The main performance parameters of the pump are shown in Table 1. Virtual prototype model of the centrifugal pump is established shown in Fig. 1.

　　| --- | --- | --- | --- |

　　| 3 | 18 | 24.5 | 2950 |

　　![Figure 1. Total pump model](Figure 1. Total pump model)

　　### B. Numerical model

　　In order to establish a fluid-solid coupling model to analyze the vibration characteristics of the centrifugal pump, the centrifugal pump model and the fluid model of the centrifugal pump were established, and the preprocessing of the model was completed in the finite element software Ansys.

　　1) **Modeling and grid generation**

　　According to the prototype model of centrifugal pump, the 3D model of centrifugal pump is established. Considering the convenience of finite element mesh division and the improvement of calculation efficiency in the later stage of simulation software, the model was simplified reasonably, the pump shaft, sealing ring and sleeve adopt structured grids, and the front pump cover, pump casing, impeller and bracket adopt unstructured grids. Considering that the motor part is not the focus of this research, the motor shell is used as a rigid body. Several attempts have been made to determine the optimal control of the parts with a unit of 6mm size. The centrifugal pump grid model generates a total of 211,285 nodes and 125,152 elements. Most of the grid cells have a mass distribution between 0.7 and 1.0, which has a good grid quality. The model is shown in Fig. 2.

　　![Figure 2. Grid model of pump](Figure 2. Grid model of pump)

　　The watershed model be built, which mainly includes inlet pipeline, outlet pipeline, volute and impeller. Then the watershed model will be meshed in finite element software. According to the structural characteristics, finite element meshes of parts(including inlet pipeline and outlet pipeline) with regular geometric structure are generated in hex dominant method. And for volute and impeller with complex geometric structure, the finite element mesh is obtained in tetrahedralmesh method. After several tests, optimal grid size is determined as 2mm. The finished finite element watershed model is shown in Fig. 3. The finite element mesh of the centrifugal pump basin model generates 87,838 nodes and 302,556 elements, which meet the requirements of fluent mesh.

　　![Figure 3. Grid model of fluid domain](Figure 3. Grid model of fluid domain)

　　2) **Setting**

　　The calculation of the fluid force of the basin model requires parameters and boundary conditions. The model adopts the standard k-ε model, and the inlet and outlet conditions adopt mass flow inlet and pressure outlet. In order to get a better convergence result, the standard of the residual value is set to $10^{-5}$. Taking 0.001s as a time step, the number of iterations for each time step is set to 40. In order to make the flow field fully developed and stable, 300 iterations are performed first, and after the flow field has a sufficient number of iterations to eliminate the instability of the numerical calculation, the next 500 steps are calculated. The calculation results of each time steps are recorded in Fluent as the fluid excitation of the subsequent fluid-structure coupling model.

　　## III. RESULTS & DISCUSSION

　　In this chapter, based on the numerical model established above, steady-state calculation and transient calculation of the flow field are completed. Analyzed the internal flow field of the centrifugal pump, and the force of the fluid on the impeller is calculated. A fluid-solid coupling model is established, and the vibration characteristics of the centrifugal pump are solved based on the finite element theory.

　　### A. Analysis of internal flow field

　　The static pressure distribution on each wall of the centrifugal pump shown in Fig. 4. It can be seen that the pressure distribution of the centrifugal pump satisfies the following law: the pressure at the inlet is the smallest, and the pressure at the outlet is the largest. As the impeller rotates to do work on the fluid, the pressure of the flow field from the inlet section to the outlet extension section gradually increases. This pressure change indicates the process of pressurizing the fluid passing through the centrifugal pump.

　　![Figure 4. Pressure distribution of flow field](Figure 4. Pressure distribution of flow field)

　　### B. Fluid excitation

　　When the transient flow field calculation converges, the radial resultant force and axial closing moment are recorded to obtain the periodic fluid excitation load on the impeller. After Fourier transform, the frequency domain distribution of fluid exciting force on impeller is obtained shown in Fig. 5. The radial fluid force on the impeller alternates in its rotational frequency (48 Hz). The blade passing frequency is 240Hz and 480Hz, corresponding to the frequency domain peak distribution of the axial total moment. Proven the accuracy of the calculation model.

　　![Figure 5. The fluid force on the impeller](Figure 5. The fluid force on the impeller)

　　### C. Characteristics of flow-induced vibration

　　The fluid forces acquired from the transient calculation results of flow field are used as the excitation loads for the virtual prototype model of the centrifugal泵, and realize the fluid-structure coupling calculation by applying the flow field load at each time step shown in Fig. 6.

　　![Figure 6. Fluid-solid coupling model](Figure 6. Fluid-solid coupling model)

　　Based on finite element theory, use the node near the fixed bolt on the bracket as the vibration measurement point of the centrifugal pump and record it transient response data, the measurement point shown in Fig. 7.

　　![Figure 7. Monitoring point](Figure 7. Monitoring point)

　　The vibration acceleration response is shown in Fig. 8. The main peak points in the three directions of the vibration frequency域 are located at 192 Hz, 240 Hz, and 480 Hz. Compared with other peak points, the 240Hz peak point corresponds to a larger amplitude. The pressure pulsation of the flow field in the centrifugal pump is mainly caused by the rotation of the blades, so the main peak point of the flowinduced vibration response of the centrifugal pump appears at the blade frequency.

　　![Figure 8. Spectrogram of vibration response](Figure 8. Spectrogram of vibration response)

　　### D. Test

　　Fig. 9 shows the test bench device for centrifugal pump. During the test, the vibration sensor is arranged at the four machine feet of the bracket to collect the vibration data of the centrifugal泵. Four acceleration sensors are installed beside the four bolts of the bracket. The experimental results is expressed as acceleration level (La), its unit is decibel(dB).

　　![Figure 9. Vibration test table](Figure 9. Vibration test table)

　　As the difference of vibration acceleration level between acceleration sensor No. 1, No. 2, No. 3 and No. 4 is not obvious, hence mainly analyzing the test data of sensor No. 2. The spectrogram of experimental results and simulation results in the Z direction shown in Fig.10.

　　![Figure 10. Spectrogram of experiment and simulation](Figure 10. Spectrogram of experiment and simulation)

　　The vibration acceleration level peaks at the measuring points mostly appear near the fundamental frequency of 48 Hz, 5 times of 240 Hz, and 10 times of 480 Hz, which verifies the conclusion of the frequency domain analysis. The amplitude of the simulation calculation result is generally smaller than the test result. This is because in the simulation calculation, the rotor system is an ideal structural model, and there is no unbalanced mass. The comparison diagram of simulation calculation results and test results can be seen that the key peak points of 48Hz, 192hz, 240Hz and 480Hz are in great agreement with the test results, and the distribution and change of the overall peak points are consistent with the test results.

　　## IV. CONCLUSIONS

　　Based on hydrodynamic theory, a calculation model for fluid field is established in the computational fluid dynamics software Fluent, and obtains the pressure distribution and the excitation force of the internal flow field. The fluid-solidcoupling model is established, the vibration acceleration of the centrifugal pump's foot is calculated, and the flow-induced vibration characteristics of the centrifugal pump are obtained. The data of the centrifugal pump measured in the vibration experiment are consistent with the simulation results. the conclusions as following:

　　The radial fluid force on the impeller alternates in rotational frequency(48Hz). The blade passing frequency is 240Hz and 480Hz, corresponding to the frequency domain peak distribution of the axial total moment.

　　Centrifugal pumps will vibrate strongly at the rotation frequency(48Hz) and blade passing frequency (240Hz and 480Hz) within 500hz. It is recommended to take vibration damping measures for the vibration at the rotation frequency and blade passing frequency in the actual installation.