本文選題：干氣密封 + 能量方程��； 參考：《蘭州理工大學(xué)》2014年碩士論文

【摘要】：螺旋槽干氣密封被廣泛應(yīng)用于石化行業(yè)中,其穩(wěn)定且可靠的的運(yùn)行直接關(guān)系到石油化工企業(yè)的安全問題。近年來,在干氣密封的密封性能方面有了更深入的研究,使干氣密封的應(yīng)用范圍得到了極大的提高,從運(yùn)行的低轉(zhuǎn)速和低壓力擴(kuò)大到高轉(zhuǎn)速和高壓力。在介質(zhì)壓力和運(yùn)轉(zhuǎn)速度較高的工作狀態(tài)下螺旋槽干氣密封的密封端面間會(huì)產(chǎn)生較大的熱量,從而使運(yùn)行不穩(wěn)定和泄漏量增大。本文通過引入螺旋槽干氣密封氣體流動(dòng)的二階速度滑移邊界條件,對(duì)干氣密封的密封端面間氣膜的非線性動(dòng)力學(xué)行為進(jìn)行研究,求得干氣密封中相應(yīng)的動(dòng)力學(xué)方程。同時(shí)引入溫度階躍邊界條件并推導(dǎo)出氣膜的能量微分方程。通過密封環(huán)的熱彈變形理論和二階非線性速度滑移邊界條件來分析研究螺旋槽干氣密封的密封性能,本文主要的研究內(nèi)容和結(jié)論如下： 在速度滑移邊界條件下,求出螺旋槽干氣密封密封端面間氣膜的壓力和速度,然后推導(dǎo)出氣膜的無熱耗散能量方程及有熱耗散能量方程,進(jìn)而利用氣膜的壓力、速度和能量方程,通過Maple和Matlab軟件求解槽內(nèi)氣膜的溫度分布。然后由氣膜溫度對(duì)密封環(huán)變形的影響,求出密封環(huán)的熱變形量,從而求出干氣密封密封端面間氣膜的厚度。最后利用由雷諾方程推導(dǎo)出的泄漏量方程求得螺旋槽干氣密封的理論泄漏量,并將理論泄漏量與實(shí)驗(yàn)測得的泄漏量作比較。研究結(jié)果表明：隨著密封氣體從密封環(huán)的外徑流入內(nèi)徑,干氣密封氣膜的溫度先升高,當(dāng)氣體到達(dá)槽根部附近時(shí)溫度達(dá)到最高,然后再隨著氣體的繼續(xù)流入氣膜溫度逐漸降低；密封環(huán)由溫度引起的幾何變形量與氣膜溫度的變化一致,然而密封端面間氣膜厚度的分布與密封環(huán)的熱彈變形量相反；隨著密封環(huán)熱彈變形量的增加,干氣密封中的泄漏量也隨之增大；考慮熱彈變形下的泄漏量與實(shí)驗(yàn)測得泄漏量數(shù)值較接近；熱耗散下考慮熱彈變形的泄漏量最接近于實(shí)驗(yàn)值。 根據(jù)速度滑移邊界條件,求出氣膜壓力和氣膜速度；然后推導(dǎo)出氣膜的能量微分方程,同時(shí)引入溫度階躍邊界條件,進(jìn)而利用氣膜的壓力、速度和能量方程,通過Matlab軟件數(shù)值計(jì)算得到三維坐標(biāo)下氣膜的溫度分布。研究結(jié)果表明：隨著氣體從密封環(huán)外徑流入內(nèi)徑,氣膜速度的分布規(guī)律是先降低后升高,槽根部周圍速度較低；隨著密封氣體從密封環(huán)的外徑流入內(nèi)徑,干氣密封氣膜的溫度先升高,當(dāng)氣體到達(dá)槽根部附近時(shí)溫度達(dá)到最高,然后再隨著氣體的繼續(xù)流入氣膜溫度逐漸降低,另外氣膜厚度方向上氣膜中間位置溫度較高;考慮溫度階躍下的溫度分布與不考慮溫度階躍下的溫度分布相差較小,因此在對(duì)干氣密封密封端面間氣膜溫度場研究時(shí)可以忽略溫度階躍對(duì)其的影響。 在流體的二階速度滑移邊界條件下對(duì)雷諾方程進(jìn)行推導(dǎo),得出修正的廣義雷諾方程,并通過PH線性化法和迭代法對(duì)修正型雷諾方程進(jìn)行求解,從而推導(dǎo)出氣膜的開啟力方程。然后由氣膜溫度對(duì)密封環(huán)變形的影響,求出密封環(huán)的熱彈變形量,從而得到干氣密封密封端面間氣膜的厚度。進(jìn)而利用氣膜剛度為開啟力與氣膜厚度之比求出氣膜剛度。然后通過建立熱彈變形下氣膜剛度和氣體泄漏量之間的協(xié)調(diào)函數(shù),對(duì)剛漏比目標(biāo)函數(shù)進(jìn)行數(shù)值計(jì)算,從而對(duì)干氣密封的螺旋角進(jìn)行優(yōu)化,得到特定工況下相對(duì)應(yīng)的最優(yōu)螺旋角。研究結(jié)果表明：隨著密封氣體從密封環(huán)的外徑流入內(nèi)徑,干氣密封的剛漏比先增大,當(dāng)氣體到達(dá)螺旋槽根部附近時(shí)達(dá)到最大值,隨著氣體的繼續(xù)流入剛漏比減小；剛漏比隨著螺旋角的變化成非線性趨勢,在剛漏比最大時(shí)得到優(yōu)化的最佳螺旋角。
[Abstract]:The spiral groove dry gas seal is widely used in the petrochemical industry. Its stable and reliable operation is directly related to the safety problem of petrochemical enterprises. In recent years, the sealing performance of dry gas seal has been studied more deeply, and the application range of dry gas seal has been greatly improved, from low running speed and low pressure. At high speed and high pressure, large heat is generated between the seal face of the spiral groove dry gas seal in the working state of high medium pressure and running speed, which makes the operation unstable and the leakage increase. In this paper, the seal end of dry gas seal is introduced by introducing the two order velocity slip boundary condition of the spiral groove dry gas seal gas flow. The nonlinear dynamic behavior of the air film is studied, and the corresponding dynamic equation in the dry gas seal is obtained. The temperature step boundary condition is introduced and the energy differential equation of the gas film is derived. The seal of the spiral groove dry gas seal is analyzed by the thermal elastic deformation theory of the seal ring and the two order nonlinear velocity slip boundary condition. The main contents and conclusions of this paper are as follows:
Under the velocity slip boundary condition, the pressure and velocity of the gas film between the seal face of the spiral groove dry gas seal are obtained. Then the heat dissipation energy equation and the heat dissipation equation are derived. Then the pressure, velocity and energy equation of the gas film are used to solve the temperature distribution of the gas film in the slot by Maple and Matlab software. Then the gas film is made by the gas film. The effect of temperature on the deformation of the seal ring is obtained. The thermal deformation of the seal ring is calculated, and the thickness of the gas film between the seal face of the dry gas seal is obtained. Finally, the leakage amount of the spiral groove dry gas seal is obtained by the leakage equation derived from Reynolds equation. The theoretical leakage is compared with the measured leakage. The results show that the leakage of the seal ring is compared with the measured leakage. As the airtight gas flows from the outer diameter of the seal ring into the inner diameter, the temperature of the dry gas seal gas film rises first, the temperature reaches the highest when the gas reaches the root of the trough, and then gradually decreases with the continuous flow of gas into the gas film temperature, and the geometric deformation caused by the temperature of the seal ring is consistent with the change of the gas film temperature, but the seal face is between the end face. The distribution of gas film thickness is the opposite of the thermal elastic deformation of the seal ring; with the increase of the thermal elastic deformation of the seal ring, the leakage amount in the dry gas seal increases, and the leakage of the thermal elastic deformation is close to the experimental result, and the leakage amount considering the thermal elastic deformation is closest to the experimental value under the heat dissipation.
According to the velocity slip boundary condition, the gas film pressure and gas film velocity are obtained. Then the energy differential equation of the gas film is derived. At the same time, the temperature step boundary condition is introduced. Then the pressure, velocity and energy equation of the gas film are used to calculate the temperature distribution of the gas film under the three-dimensional coordinates through the Matlab software. The results show that the temperature distribution of the gas film is obtained by the numerical calculation. When the gas flows from the outer diameter of the seal ring into the inner diameter, the distribution of gas film velocity is reduced first and then rising, and the velocity of the groove is low around the root. As the sealing gas flows from the outer diameter of the seal ring into the inner diameter, the temperature of the dry gas seal gas film rises first, and the temperature reaches the highest when the gas reaches the root of the trough, and then goes into the gas film as the gas continues to flow into the gas film. The temperature gradually decreases, and the temperature distribution in the gas film thickness is higher in the direction of the gas film thickness. Considering the temperature distribution under the temperature step, the difference between the temperature distribution and the temperature step is small. Therefore, the temperature step can be ignored when the temperature field is studied between the seal face of the dry gas seal.
The Reynolds equation is derived from the two order velocity slip boundary condition of the fluid, and the modified generalized Reynolds equation is obtained. The modified Reynolds equation is solved by PH linearization and iterative method, and the opening force equation of the gas film is derived. Then the effect of the gas film temperature on the seal ring deformation is obtained, and the thermal elastic deformation of the seal ring is obtained. The film stiffness between the air film stiffness and the film thickness is obtained by using the film stiffness as the ratio of the opening force to the gas film thickness. Then by establishing the coordination function between the film stiffness and the gas leakage, the numerical calculation of the stiffness leakage ratio objective function is carried out, thus the spiral angle of the dry gas seal is obtained. The results show that as the sealing gas flows from the outer diameter of the sealing ring into the inner diameter, the stiffness leakage ratio of the dry gas seal increases first, when the gas reaches the root of the spiral groove, the maximum value is reached, and the stiffness leakage ratio decreases with the continuous flow of the gas, and the stiffness leakage ratio changes with the spiral angle. The optimal helix angle is obtained when the maximum leakage ratio is the largest.
【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】：2014
【分類號(hào)】：TH136

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