【摘要】：尾軸承作為船舶推進系統(tǒng)極其關(guān)鍵的設(shè)備之一,起著支撐尾軸和螺旋槳的重要作用。根據(jù)潤滑介質(zhì)不同,尾軸承一般可以分為油潤滑和水潤滑兩種。船用油潤滑尾軸承存在著結(jié)構(gòu)復(fù)雜、滑油泄漏污染和振動噪聲等缺點,而采用水潤滑則可以很好地避免這些問題。 但是由于水的粘度低,導(dǎo)致水潤滑橡膠尾軸承的承載能力小的缺點。另一方面,由于橡膠材料是一種高彈性、非線性、耐高溫能力較差的材料。著眼于橡膠材料的缺點,有必要開展水潤滑橡膠軸承的結(jié)構(gòu)-熱-流三場的耦合研究,以提高尾軸承的潤滑性能。這對于延長軸承使用壽命,減振降噪,實現(xiàn)“綠色航運”具有重要的理論意義和工程應(yīng)用價值。 文中以水潤滑橡膠軸承周向截面為研究對象,應(yīng)用大型有限元ADINA方法對水潤滑尾軸承彈流動壓潤滑問題進行了數(shù)值分析,揭示了其潤滑規(guī)律,探討了軸承的結(jié)構(gòu)形式和運行工況對其潤滑性能(軸承壓力分布、軸承溫度分布、摩擦系數(shù)等)的影響規(guī)律。主要的研究成果如下： (1)建立了船舶水潤滑橡膠軸承的平面CSD、CFD和TFSI模型,其中包括流體與固體之間耦合面的定義和熱場的設(shè)定與控制。 (2)水潤滑橡膠軸承的最大壓力隨水槽寬度的增大有下降趨勢,隨橡膠層厚度的增加而增大,軸承最大壓力隨軸承間隙的增大而減小,當軸承間隙小于或等于1mm時,軸承最大壓力下降較快,而軸承間隙大于1mm時,軸承最大壓力趨于平穩(wěn),變化不大；最高溫度均隨軸承水槽寬度增大而下降明顯,隨橡膠層厚度的增加而增加,隨軸承間隙的增大而減小。 (3)水潤滑橡膠軸承最大壓力隨偏心率的增大而增大,但并非是存在一個線性的關(guān)系,而是在偏心率小于0.6以前壓力上升比較緩慢,當偏心率大于0.6后,壓力變化的幅度加大,溫度最大值隨偏心率的變化曲線基本和壓力分布最大值曲線相似；軸承的最大壓力隨偏位角的增大而減小,但是減小的幅度很小,軸承的最大溫度變化也有相類似的變化。 (4)當轉(zhuǎn)速在400r/min以上時的彈性流體動壓潤滑的情況下,軸承的最大壓力和最高溫度均隨轉(zhuǎn)速的增加而增大；改變軸承的軸向流速,軸承的壓力分布基本不變；軸承最大壓力與最高溫度隨軸承工作的水域溫度的增加而增大。 (5)通過在尾軸承臺架試驗表明：在彈性流體動壓潤滑的情況下,軸承的摩擦系數(shù)較小。同時,隨著軸轉(zhuǎn)速的提高,軸承的摩擦系數(shù)先下降,后有小幅度的增加。潤滑出水管處的溫度隨軸轉(zhuǎn)速的增大而升高,但是升高的幅值較小。
[Abstract]:As one of the most important equipments in ship propulsion system, stern bearing plays an important role in supporting stern shaft and propeller. According to the lubricating medium, the tail bearing can be generally divided into oil lubrication and water lubrication. Marine oil lubricated tail bearings have some disadvantages such as complicated structure, oil leakage pollution and vibration noise, which can be avoided by water lubrication. However, because of the low viscosity of water, the bearing capacity of water lubricated rubber tail bearing is small. On the other hand, because rubber material is a kind of high elasticity, nonlinear, low resistance to high temperature. Considering the disadvantages of rubber materials, it is necessary to study the structure-heat flow coupling of water-lubricated rubber bearings in order to improve the lubricating performance of tail-bearing. It has important theoretical significance and engineering application value for prolonging bearing service life, reducing vibration and noise, and realizing "green shipping". Taking the circumferential section of water-lubricated rubber bearing as an object of study, the flow pressure lubrication problem of water-lubricated tail bearing is numerically analyzed by using large-scale finite element ADINA method, and the lubrication law is revealed. The influence of bearing structure and operating conditions on its lubricating performance (bearing pressure distribution, bearing temperature distribution, friction coefficient, etc.) is discussed. The main research results are as follows: (1) the plane CSD,CFD and TFSI models of marine water-lubricated rubber bearings are established, including the definition of coupling surface between fluid and solid and the setting and control of thermal field. (2) the maximum pressure of water-lubricated rubber bearing decreases with the increase of flume width, increases with the increase of rubber layer thickness, and decreases with the increase of bearing clearance. When the bearing clearance is less than or equal to 1mm, When the bearing clearance is larger than 1mm, the maximum bearing pressure tends to be stable, and the maximum temperature decreases obviously with the increase of bearing flume width, and increases with the increase of rubber layer thickness. It decreases with the increase of bearing clearance. (3) the maximum pressure of water-lubricated rubber bearing increases with the increase of eccentricity, but not with a linear relationship, but with the pressure rising slowly before eccentricity is less than 0.6. When the eccentricity ratio is greater than 0.6, the range of pressure change increases. The maximum temperature curve with eccentricity is basically similar to the maximum pressure distribution curve, and the maximum pressure of bearing decreases with the increase of offset angle, but the amplitude of decrease is very small, and the maximum temperature change of bearing is similar. (4) when the rotational speed is above 400r/min, the maximum pressure and temperature of the bearing increase with the increase of the rotational speed, and the pressure distribution of the bearing is basically unchanged when the axial velocity of the bearing is changed. The maximum bearing pressure and maximum temperature increase with the water temperature of the bearing working. (5) the test on the tail bearing bench shows that the friction coefficient of the bearing is small under the condition of elastohydrodynamic lubrication. At the same time, with the increase of shaft speed, the friction coefficient of bearing decreases first, then increases slightly. The temperature of lubricating outlet pipe increases with the increase of shaft speed, but the amplitude of increase is smaller.
【學(xué)位授予單位】：武漢理工大學(xué)
【學(xué)位級別】：碩士
【學(xué)位授予年份】：2012
【分類號】：TH133.3

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