本文選題：深井泵 + 數(shù)值計(jì)算　； 參考：《江蘇大學(xué)》2017年碩士論文

【摘要】：作為一種提供高揚(yáng)程液體的通用機(jī)械,深井泵已被廣泛應(yīng)用于國(guó)民經(jīng)濟(jì)和社會(huì)生產(chǎn)的各個(gè)領(lǐng)域。由于泵體外徑受到井徑的限制,深井泵大多采用增加級(jí)數(shù)的方法來(lái)滿足總揚(yáng)程的需求,這會(huì)導(dǎo)致其軸向長(zhǎng)度較大,因而給深井泵的安裝與維修帶來(lái)不便。為了提高深井泵的單級(jí)揚(yáng)程、縮短其軸向長(zhǎng)度,提高其運(yùn)行轉(zhuǎn)速已成為深井泵設(shè)計(jì)的一大趨勢(shì)。本文以UG 8.0、ANSYS CFX 14.5等軟件為工具,完成了100QJ20型高速深井泵的水力設(shè)計(jì)與數(shù)值計(jì)算,并通過(guò)性能試驗(yàn)驗(yàn)證了數(shù)值計(jì)算的準(zhǔn)確性。主要研究?jī)?nèi)容與取得的研究成果如下:(1)回顧了深井泵產(chǎn)品的發(fā)展歷史,對(duì)其水力設(shè)計(jì)的相關(guān)研究做了簡(jiǎn)單的總結(jié),并介紹了近年來(lái)泵內(nèi)部流動(dòng)與泵轉(zhuǎn)速變化的研究現(xiàn)狀。(2)基于等比例縮放設(shè)計(jì)法完成了100QJ20型深井泵的水力設(shè)計(jì),并對(duì)初始模型(150QJ36型深井泵)與設(shè)計(jì)模型分別進(jìn)行了三維建模與各計(jì)算域的網(wǎng)格劃分,采用ANSYS CFX軟件分別完成了兩組模型的數(shù)值計(jì)算。兩組模型的外特性在0.4~1.6倍額定流量工況范圍內(nèi)基本滿足相似換算準(zhǔn)則,其內(nèi)部流場(chǎng)的分布規(guī)律具有較強(qiáng)的相似性與微小的差異性。對(duì)150QJ36型深井泵進(jìn)行了性能試驗(yàn),結(jié)果表明數(shù)值預(yù)測(cè)揚(yáng)程與功率略低于試驗(yàn)結(jié)果,預(yù)測(cè)的效率略高于試驗(yàn)值,但整體上兩者隨流量的變化趨勢(shì)基本一致,證實(shí)本文的數(shù)值模擬具有較高的精度。(3)對(duì)100QJ20型深井泵分別在三種不同轉(zhuǎn)速方案下進(jìn)行了多工況數(shù)值計(jì)算,分析了運(yùn)行轉(zhuǎn)速對(duì)深井泵性能的影響。結(jié)果表明不同轉(zhuǎn)速下的深井泵揚(yáng)程、功率預(yù)測(cè)值基本滿足相似換算準(zhǔn)則,泵效率則隨著轉(zhuǎn)速的提高而有所提升。這是由于不同轉(zhuǎn)速下泵內(nèi)的圓盤摩擦損失不符合相似換算準(zhǔn)則而造成的,隨著轉(zhuǎn)速的提高,圓盤摩擦損失在軸功率中所占的比重不斷下降。(4)在深井泵模型各計(jì)算子域中布置了多組監(jiān)測(cè)點(diǎn),完成了對(duì)深井泵模型在3種不同轉(zhuǎn)速下的非定常數(shù)值計(jì)算,獲取了各監(jiān)測(cè)點(diǎn)的壓力脈動(dòng)數(shù)據(jù)。通過(guò)對(duì)壓力脈動(dòng)數(shù)據(jù)的無(wú)量綱處理與快速傅里葉變換,獲得了壓力脈動(dòng)時(shí)域分布和頻域分布,對(duì)比發(fā)現(xiàn)泵內(nèi)壓力脈動(dòng)存在較為復(fù)雜的級(jí)間耦合與拍振現(xiàn)象。不同轉(zhuǎn)速下泵內(nèi)壓力脈動(dòng)的分布規(guī)律具有一定的相似性,但高轉(zhuǎn)速下泵內(nèi)壓力脈動(dòng)的主頻頻率要高于低轉(zhuǎn)速下的,且轉(zhuǎn)速的變化會(huì)引起某些監(jiān)測(cè)點(diǎn)壓力脈動(dòng)相位的改變。(5)確定了三種不同的轉(zhuǎn)速變化方式,并以此完成了不同轉(zhuǎn)速變化方式下深井泵模型的非定常數(shù)值計(jì)算。在三種方案中,直線加速過(guò)程與開(kāi)口向下的二次加速過(guò)程中,揚(yáng)程的波動(dòng)要弱于開(kāi)口向上的二次加速過(guò)程,且開(kāi)口向下的二次加速過(guò)程能夠最先達(dá)到揚(yáng)程要求;在泵加速過(guò)程中,葉輪流道內(nèi)的二次流會(huì)得到明顯的改善。
[Abstract]:As a kind of universal machinery to provide high head liquid, deep well pump has been widely used in various fields of national economy and social production. Because the outer diameter of pump body is limited by the well diameter, most deep well pumps adopt the method of increasing series to meet the demand of total head, which will lead to the large axial length of pump, which brings inconvenience to the installation and maintenance of deep well pump. In order to improve the single stage head of deep well pump, shorten its axial length and improve its running speed, it has become a major trend in the design of deep well pump. In this paper, the hydraulic design and numerical calculation of 100QJ20 type high speed deep well pump are completed with the software of UG 8.0 and ANSYS CFX 14.5, and the accuracy of numerical calculation is verified by performance test. The main research contents and results obtained are as follows: (1) reviewing the development history of deep well pump products, and briefly summarizing the relevant research on hydraulic design of deep well pumps. The research status of pump internal flow and pump speed change in recent years is introduced. The hydraulic design of 100QJ20 deep well pump is completed based on the equal scale scaling design method. The initial model and the design model are modeled and meshed in each computing domain respectively. The numerical calculation of the two groups of models is completed by using ANSYS CFX software. The external characteristics of the two groups of models basically meet the similar conversion criterion in the range of 0.4 ~ 1.6 times rated flow rate, and the distribution law of internal flow field has strong similarity and small difference. The performance test of 150QJ36 type deep well pump is carried out. The results show that the predicted head and power are slightly lower than the test results, and the predicted efficiency is slightly higher than the experimental value, but on the whole, the variation trend of the two kinds of pumps with the flow rate is basically the same. It is proved that the numerical simulation in this paper has a high accuracy. The numerical calculation of 100QJ20 deep well pump under three different rotational speed schemes has been carried out, and the effect of running speed on the performance of deep well pump has been analyzed. The results show that the power prediction value of the deep well pump at different rotational speeds basically meets the similar conversion criteria, while the pump efficiency is improved with the increase of the rotational speed. This is caused by the fact that the friction loss of the disk in the pump does not conform to the similar conversion criteria at different rotational speeds, and with the increase of the rotational speed, The proportion of disk friction loss in shaft power is decreasing continuously. (4) multiple monitoring points are arranged in each calculation subdomain of deep well pump model, and the unsteady numerical calculation of deep well pump model under three different rotational speeds is completed. The pressure fluctuation data of each monitoring point are obtained. The time-domain and frequency-domain distributions of pressure pulsation are obtained by dimensionless processing and fast Fourier transform of pressure pulsation data. It is found that there are more complicated phenomena of interstage coupling and beat vibration in pump pressure pulsation. The distribution of pressure pulsation in the pump at different rotational speeds is similar, but the main frequency of the pressure pulsation in the pump at high rotational speed is higher than that at low rotational speed. And the change of rotational speed will cause the change of the phase of pressure pulsation in some monitoring points.) three different rotational speed change modes are determined and the unsteady numerical calculation of the deep well pump model under different rotational speed variation modes is completed. In the three schemes, the fluctuation of the head is weaker than the second acceleration up the opening in the linear acceleration process and the secondary acceleration process down the opening, and the secondary acceleration process down the opening can first meet the requirements of the lift. In the process of pump acceleration, the secondary flow in the impeller passage will be improved obviously.
【學(xué)位授予單位】：江蘇大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2017
【分類號(hào)】：TH38

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