本文選題：無(wú)過(guò)載　切入點(diǎn)：功率備用系數(shù)　出處：《蘭州理工大學(xué)》2012年碩士論文

【摘要】：無(wú)過(guò)載離心泵是指：泵的軸功率曲線有極值，即泵的軸功率在全流量范圍內(nèi)（從零流量到最大流量）都小于等于所配用電動(dòng)機(jī)的額定功率。在實(shí)際使用中為了減小配用電動(dòng)機(jī)的額定功率，要求全流量范圍內(nèi)泵的最大軸功率是設(shè)計(jì)點(diǎn)軸功率的某一倍數(shù)關(guān)系（一般是1.05~1.2倍）。為了滿(mǎn)足這一要求，保證泵的運(yùn)行可靠性，國(guó)內(nèi)外學(xué)者對(duì)高效無(wú)過(guò)載離心泵有了一定的研究。本文在前人研究成果的基礎(chǔ)上，通過(guò)理論公式的推導(dǎo)，研究了無(wú)過(guò)載離心泵性能與設(shè)計(jì)參數(shù)的關(guān)系，，主要工作和研究成果有： 1.根據(jù)無(wú)過(guò)載離心泵最大軸功率與額定軸功率比值（功率備用系數(shù)K）的公式，在滿(mǎn)足一定的條件下（葉片出口寬度符合低比轉(zhuǎn)速離心泵的經(jīng)驗(yàn)公式：b_2=00003752D_2n_s~(1.15)，此條件可以改變），通過(guò)推導(dǎo)得到：K值僅是比轉(zhuǎn)速、葉片出口角和葉片數(shù)的函數(shù)，依此函數(shù)利用MATLAB軟件編寫(xiě)程序，并繪出了不同葉片數(shù)下K值的三維曲面函數(shù)圖像，以及在不同葉片數(shù)下K值關(guān)于葉片出口角和泵比轉(zhuǎn)速的等高線。由等高線圖可見(jiàn)：K值和葉片數(shù)關(guān)系不大，葉片出口角、泵比轉(zhuǎn)速對(duì)K值影響較大；在相同的K值下，比轉(zhuǎn)速越高，可取的最大葉片出口角越大。由等高線圖可以根據(jù)比轉(zhuǎn)速、K值選擇合理的葉片出口角。 2.依上述函數(shù)及其等高線為依據(jù)，設(shè)計(jì)了三臺(tái)不同比轉(zhuǎn)速的無(wú)過(guò)載離心泵，分別為泵A（n_s=62）、B（n_s=53）、C（n_s=58）。利用Pro/E對(duì)所設(shè)計(jì)的三臺(tái)無(wú)過(guò)載離心泵進(jìn)行全流道建模，分別導(dǎo)入GAMBIT劃分網(wǎng)格，利用FLUENT進(jìn)行數(shù)值模擬。 3.通過(guò)數(shù)值模擬發(fā)現(xiàn)：設(shè)計(jì)的A、B、C三種不同比轉(zhuǎn)速離心泵均具備了無(wú)過(guò)載性能，且由A、B兩泵模擬得到的功率備用系數(shù)和其給定的功率備用系數(shù)基本吻合；而C泵其結(jié)果有一定差異。分析其誤差原因是由于C泵的葉片出口寬度不符合推導(dǎo)上述函數(shù)的假定條件（即b_2=00003752D_2n_s~(1.15)）。 4.只要保證在泵設(shè)計(jì)時(shí)，其葉片出口寬度符合經(jīng)驗(yàn)公式b=b_2=00003752D_2n_s~(1.15)，利用文中得到的函數(shù)關(guān)系式就可以成功的設(shè)計(jì)出功率備用系數(shù)符合設(shè)計(jì)要求的無(wú)過(guò)載離心泵；對(duì)于用其他方法設(shè)計(jì)的低比轉(zhuǎn)速無(wú)過(guò)載離心泵，如果其設(shè)計(jì)參數(shù)滿(mǎn)足條件（b_2=00003752D_2n_s~(1.15)），利用文中的得到的函數(shù)關(guān)系式就可以準(zhǔn)確的計(jì)算出其功率備用系數(shù)。 5.實(shí)例證明：文中方法能夠成功而快捷的實(shí)現(xiàn)無(wú)過(guò)載離心泵的設(shè)計(jì)，避免了傳統(tǒng)方法葉片出口角選擇的盲目性。
[Abstract]:Non-overload centrifugal pump means that the axial power curve of the pump has extreme value, That is, the axial power of the pump is less than or equal to the rated power of the motor used in the whole flow range (from zero flow to the maximum flow). In order to reduce the rated power of the motor in practical use, In order to meet this requirement, the maximum shaft power of the pump in the full flow range is a certain multiple of the shaft power at the design point (generally 1.05V 1.2 times). In order to meet this requirement, the pump is guaranteed to operate reliably. Scholars at home and abroad have a certain degree of research on high efficiency and no overload centrifugal pump. Based on the previous research results, through the derivation of theoretical formula, the relationship between the performance and design parameters of non-overload centrifugal pump is studied. The main work and research results are as follows:. 1. According to the formula of the ratio of maximum shaft power to rated shaft power (power reserve coefficient K) of non-overload centrifugal pump, Under certain conditions (the empirical formula of centrifugal pump with low specific speed for the width of blade outlet:: B _ S _ 2T _ 2T _ 2O _ 2 003752D _ 2N _ S _ T _ 2N _ S _ T), this condition can be changed. By deducing the function that the ratio K value is only the specific speed, the outlet angle of the blade and the number of blades, According to this function, the program is written by MATLAB software, and the 3D curved surface function image with K value under different blade number is drawn. From the contour diagram, we can see that the ratio of K to the number of blades is not related to the number of blades, the outlet angle of the blade and the specific speed of the pump have great influence on K value; at the same K value, the specific speed of the pump has a great influence on K value. The higher the specific speed is, the greater the optimum outlet angle of the blade is. According to the contour diagram, the reasonable outlet angle can be selected according to the specific rotational speed K value. 2. According to the above function and the contour line, three non-overload centrifugal pumps with different specific rotational speeds are designed, which are the pump Agnes, respectively. The whole channel model of the three non-overload centrifugal pumps designed by Pro/E is introduced into the GAMBIT grid, and the whole channel model of the three non-overload centrifugal pumps is constructed by using Pro/E. The numerical simulation is carried out by FLUENT. 3. Through numerical simulation, it is found that the designed three kinds of centrifugal pumps with different specific speeds have no overload performance, and the power reserve coefficients simulated by the two pumps are in good agreement with the power reserve coefficients given by the two pumps. The reason for the error is that the width of the vane outlet of the C-pump does not conform to the assumption of deducing the above function. 4. As long as the width of the vane outlet conforms to the empirical formula b / b / 2n003752D / D / s / d / 2nS / L / L / L, the power spare coefficient of the pump can be successfully designed by using the function relation obtained in this paper. For the non-overload centrifugal pump with low specific speed designed by other methods, if its design parameters satisfy the conditions of 200003752D, the power reserve coefficient can be accurately calculated by using the function relation obtained in this paper. 5. The example shows that the design of the centrifugal pump without overload can be realized successfully and quickly, and the blindness of choosing the outlet angle of the blade in the traditional method is avoided.
【學(xué)位授予單位】：蘭州理工大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2012
【分類(lèi)號(hào)】：TH311

【參考文獻(xiàn)】

相關(guān)期刊論文 前10條

1 劉在倫,齊學(xué)義,鄭小榮;葉輪出口葉片間面積對(duì)潛水泵性能的影響[J];甘肅工業(yè)大學(xué)學(xué)報(bào);2002年02期

2 楊軍虎;張人會(huì);王春龍;馬靜先;王昕;;低比轉(zhuǎn)速離心泵的面積比原理[J];蘭州理工大學(xué)學(xué)報(bào);2006年05期

3 楊軍虎;吳俊輝;張人會(huì);;無(wú)過(guò)載離心泵內(nèi)部流場(chǎng)的三維數(shù)值模擬[J];蘭州理工大學(xué)學(xué)報(bào);2009年01期

4 聞建龍,沙毅,李傳君,王貞濤;無(wú)過(guò)載超低比轉(zhuǎn)速離心泵水力設(shè)計(jì)[J];江蘇大學(xué)學(xué)報(bào)(自然科學(xué)版);2003年06期

5 袁壽其,陳池,鄭銘,李f3;無(wú)過(guò)載離心泵葉輪內(nèi)三維不可壓湍流場(chǎng)計(jì)算[J];機(jī)械工程學(xué)報(bào);2000年05期

6 張淑佳;李賢華;朱保林;胡清波;;k-ε渦粘湍流模型用于離心泵數(shù)值模擬的適用性[J];機(jī)械工程學(xué)報(bào);2009年04期

7 黃思;吳玉林;;離心泵內(nèi)三維流場(chǎng)非對(duì)稱(chēng)性及泵受力的數(shù)值分析[J];流體機(jī)械;2006年02期

8 劉勝柱,郭鵬程,羅興

本文編號(hào)：1688687