本文選題：旋片泵 + 多體動(dòng)力學(xué)　； 參考：《東北大學(xué)》2014年碩士論文

【摘要】：由于旋片泵的工作原理及結(jié)構(gòu)特性,振動(dòng)和噪聲是不可避免的。國(guó)外廠家很早就注意對(duì)其進(jìn)行減振降噪,其產(chǎn)品的噪聲一般比國(guó)產(chǎn)泵低10dB(A)左右,國(guó)內(nèi)用戶近年來(lái)對(duì)減小振動(dòng)和噪聲的要求強(qiáng)烈,所以很有必要對(duì)其振動(dòng)噪聲進(jìn)行研究和控制。 本論文對(duì)VRD16旋片泵由于轉(zhuǎn)子慢偏心引起的振動(dòng)及腔體輻射噪聲、排氣噪聲、擋油罩和限位板的輻射噪聲進(jìn)行了數(shù)值化仿真分析研究和優(yōu)化設(shè)計(jì)。 運(yùn)用多體動(dòng)力學(xué)和油膜動(dòng)力潤(rùn)滑方法,對(duì)RD16旋片泵轉(zhuǎn)子系統(tǒng)進(jìn)行耦合數(shù)值化計(jì)算,其中油膜壓力數(shù)學(xué)模型采用Capone短軸承理論得到的解析解,并將得到的軸心運(yùn)動(dòng)參數(shù)與只進(jìn)行多體動(dòng)力學(xué)分析得到的數(shù)據(jù)進(jìn)行對(duì)比,可知將油膜動(dòng)力潤(rùn)滑引入到多體動(dòng)力學(xué)分析中更符合實(shí)際情況。對(duì)比兩種轉(zhuǎn)子系統(tǒng),可知兩軸垂直放置油膜壓力較大,將計(jì)算得到的油膜壓力進(jìn)行傅里葉變換,并將其施加到腔體上,以MPC節(jié)點(diǎn)耦合的方法模擬螺栓連接,運(yùn)用有限元方法,在頻域內(nèi)求得了腔體的振動(dòng)響應(yīng)。用最小二乘法對(duì)油膜壓力進(jìn)行擬合,濾掉其高頻振動(dòng),經(jīng)傅里葉變換后,其200Hz-400Hz處與實(shí)驗(yàn)不符,所以本論文對(duì)腔體的振動(dòng)響應(yīng)的計(jì)算考慮了油膜壓力的高頻部分。將400Hz以內(nèi)腔體的振動(dòng)響應(yīng)與實(shí)驗(yàn)進(jìn)行對(duì)比,其理論計(jì)算結(jié)果與實(shí)驗(yàn)數(shù)據(jù)基本符合,可間接證明整個(gè)頻帶內(nèi)的計(jì)算符合實(shí)際情況。由于油膜壓力頻帶較寬,激起了腔體的前14階共振模態(tài),所以腔體的振動(dòng)較大。以計(jì)算得到的腔體的振動(dòng)響應(yīng)為邊界條件,運(yùn)用邊界元方法,計(jì)算得到了腔體的輻射噪聲。通過(guò)改變油膜間隙的大小,對(duì)油膜壓力進(jìn)行調(diào)整改進(jìn),減小其幅值并穩(wěn)定其波動(dòng)量,從而減小腔體的振動(dòng)。 根據(jù)VRD16旋片泵的結(jié)構(gòu),計(jì)算了壓縮腔面積、入口壓力、排氣速度等參數(shù),并以此作為流場(chǎng)分析的邊界條件。運(yùn)用大渦模擬方法對(duì)VRD16旋片泵排氣腔流場(chǎng)進(jìn)行計(jì)算,得到排氣腔內(nèi)流場(chǎng)的壓力、速度等參數(shù)。將排氣腔內(nèi)的壁面壓力進(jìn)行傅立葉變換,生成偶極子噪聲源,運(yùn)用聲學(xué)有限元方法和LMS Virtual.Lab軟件中AML技術(shù)計(jì)算排氣腔遠(yuǎn)場(chǎng)噪聲。經(jīng)對(duì)比,在2500Hz以下高真空腔內(nèi)的氣動(dòng)噪聲明顯高于低真空腔內(nèi)的氣動(dòng)噪聲,而在2500Hz以上,兩腔內(nèi)氣動(dòng)噪聲值相差不是很大。通過(guò)對(duì)擋油罩內(nèi)的流場(chǎng)進(jìn)行分析,得出其由于壁面波動(dòng)而引起較多漩渦,所以將擋油罩內(nèi)流道進(jìn)行了優(yōu)化改進(jìn),改進(jìn)后部分監(jiān)測(cè)點(diǎn)的壓力波動(dòng)明顯降低,經(jīng)計(jì)算得到,高真空區(qū)域場(chǎng)點(diǎn)聲功率級(jí)平均降低7.70dB,低真空區(qū)域場(chǎng)點(diǎn)聲功率級(jí)平均降低6.92dB,高真空區(qū)域監(jiān)測(cè)點(diǎn)Field_Point聲壓級(jí)平均降低8.72dB,低真空區(qū)域監(jiān)測(cè)點(diǎn)Field_Point聲壓級(jí)平均降低7.83dB。通過(guò)增加排氣口的方法,對(duì)高真空腔流道進(jìn)行改進(jìn),經(jīng)計(jì)算高真空腔內(nèi)氣動(dòng)噪聲有明顯的降低,場(chǎng)點(diǎn)聲功率級(jí)平均降低31.62dB,監(jiān)測(cè)點(diǎn)Field Point聲壓級(jí)平均降低31.33dB。 運(yùn)用流固耦合技術(shù),對(duì)擋油罩和限位板的振動(dòng)響應(yīng)和輻射噪聲進(jìn)行了計(jì)算,得到了擋油罩和限位板的振動(dòng)響應(yīng),其振動(dòng)位移和速度在某一恒定值附近振蕩,所以擋油罩和限位板的振動(dòng)呈收斂狀態(tài),即最終擋油罩和限位板在氣流的作用下發(fā)生靜變形,所以由氣體壓力引起的固體振動(dòng)和輻射噪聲并不大。
[Abstract]:Vibration and noise are unavoidable due to the working principle and structural characteristics of the rotary pump. The noise and noise reduction of the foreign manufacturers are very early. The noise of the products is generally lower than 10dB (A) of the domestic pump. The domestic users have a strong demand for reducing the vibration and noise in recent years. So it is necessary to study the vibration and noise of the products. Control.
In this paper, the vibration and radiation noise of the cavity caused by the slow eccentricity of the rotor, the exhaust noise, the radiation noise of the oil shield and the limit plate are numerically simulated and optimized in this paper, which is caused by the slow eccentricity of the rotor VRD16.
Using the multi-body dynamics and the oil film dynamic lubrication method, the rotor system of the RD16 rotary blade pump is coupled numerically, in which the mathematical model of the oil film pressure is solved by the analytical solution of the Capone short bearing theory, and the obtained axis motion parameters are compared with the data obtained only by the multi-body dynamic analysis. Sliding into multi body dynamic analysis is more in line with the actual situation. Comparing the two rotor systems, it is known that the pressure of the oil film on the two axes is larger and the oil film pressure is calculated by Fourier transform, and it is applied to the cavity, and the bolt connection is simulated by the coupling of MPC nodes. The finite element method is used to obtain the cavity in the frequency domain. The vibration response of the body is used to fit the oil film pressure by the least square method and filter out its high frequency vibration. After Fu Liye transformation, the 200Hz-400Hz is not consistent with the experiment. So the vibration response of the cavity is calculated in this paper. The high-frequency part of the oil film pressure is taken into account. The theoretical calculation of the vibration response of the inner cavity of the 400Hz is compared with the experiment. The results are basically consistent with the experimental data, which can indirectly prove that the calculation in the whole frequency band is in accordance with the actual situation. Because the pressure band of the oil film pressure is wide, the first 14 modes of the cavity are aroused, so the vibration of the cavity is larger. The vibration response of the cavity is calculated as the boundary condition, and the cavity radiation is calculated by the boundary element method. Noise. By changing the size of the oil film gap, the oil film pressure is adjusted to improve, reduce its amplitude and stabilize its wave momentum, thereby reducing the vibration of the cavity.
According to the structure of the VRD16 rotating disk pump, the parameters of the area of the compressed cavity, the inlet pressure and the exhaust velocity are calculated and used as the boundary condition of the flow field analysis. The flow field of the exhaust cavity of the VRD16 rotary pump pump is calculated by the large eddy simulation method, and the pressure and velocity parameters of the flow field in the exhaust cavity are obtained. The wall pressure in the exhaust cavity is carried out by Fu Liye. Transform, generate the dipole noise source, use the acoustic finite element method and the AML technology in the LMS Virtual.Lab software to calculate the far field noise of the exhaust cavity. By contrast, the aerodynamic noise in the high true cavity below 2500Hz is obviously higher than that in the low true cavity, and the difference of the aerodynamic noise value in the two cavity is not very much above 2500Hz. The flow field in the hood is analyzed, and it is concluded that it causes more whirlpools due to the wall fluctuation. Therefore, the inner flow path of the oil shield is improved, and the pressure fluctuation of some monitoring points is obviously reduced. The sound power level of the high vacuum area field is reduced by 7.70dB, and the sound power level of the low vacuum area field is reduced by 6.92dB, as a result. The Field_Point sound pressure level of the high vacuum area monitoring point is reduced by 8.72dB, and the Field_Point acoustic pressure level of the low vacuum area monitoring point is reduced by the average 7.83dB.. Through the method of increasing the vent, the high true cavity flow channel is improved. The aerodynamic noise in the high true cavity is obviously reduced, the sound power level of the field point decreases 31.62dB, and the monitoring point Field The average reduction of Point sound pressure level by 31.33dB.
The vibration response and radiation noise of the oil shield and the limit plate are calculated by the fluid solid coupling technique. The vibration response of the oil shield and the limit plate is obtained. The vibration displacement and velocity oscillate near a constant value, so the vibration of the oil shield and the limit plate is convergent, that is, the final oil shield and the limit plate are under the action of the air flow. Static deformation occurs, so the solid vibration and radiation noise caused by gas pressure are not large.

【學(xué)位授予單位】：東北大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2014
【分類號(hào)】：TB535;TB752

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