本文選題：柔性鉸鏈可傾瓦軸承 + 動靜壓��； 參考：《山東大學》2017年碩士論文

【摘要】：柔性鉸鏈可傾瓦軸承不僅同普通可傾瓦軸承一樣有優(yōu)良穩(wěn)定性。同時可以克服普通可傾瓦軸承結構復雜,加工裝配要求高,支點易磨損,容易形成誤差累積,易產生軸瓦顫振等缺點。動靜壓軸承既有動壓性能也有靜壓性能,一些學者嘗試了將可傾瓦軸承和動靜壓軸承結合在一起,以使其兼具兩者優(yōu)點,并證明了將靜壓引入可傾瓦軸承的可行性以及其相對于普通可傾瓦軸承和動靜壓軸承的優(yōu)越性。但這些研究中軸承并沒有采用柔性鉸鏈結構,仍存在支點結構復雜、加工裝配要求高的問題。針對上述問題,本文在柔性鉸鏈可傾瓦軸承的基礎上引入靜壓腔,研究了帶有靜壓腔的柔性鉸鏈可傾瓦軸承。在柔性鉸鏈中加工進油孔,為靜壓腔供油。這樣就簡化了支點結構,克服了普通支點結構的諸多缺點。本文將從軸承的結構設計到軸承靜態(tài)特性分析,受載荷后軸心軌跡的響應以及對軸心振動的主動控制等方面進行研究,對該類新型可傾瓦軸承的工程應用提供了理論指導意義。主要內容如下:設計了該軸承的結構,設計了通過在柔性鉸鏈中加工進油孔的方式給軸承靜壓油腔供油。通過建立動靜壓柔性鉸鏈可傾瓦軸承計算模型,給出了油膜厚度表達式及潤滑雷諾方程。采用有限差分法,超松弛迭代法離散求解了雷諾方程,結合牛頓迭代法計算了軸頸軸瓦平衡時的軸承靜態(tài)性能。對比了不同偏心率、轉速和靜壓油腔尺寸的情況下軸承承載系數、流量系數、摩擦系數及功耗的變化,獲得了軸承在一定工況下的靜態(tài)性能參數。建立了軸承—轉子系統(tǒng)軸心軌跡和軸瓦擺動的計算模型。采用歐拉法計算了動載荷作用下非線性軸心軌跡及軸瓦擺動位移。分析了軸頸受階躍載荷、矩形脈沖載荷和三角脈沖載荷等非周期性載荷作用時的軸心軌跡瞬態(tài)特性,以及不平衡載荷作用時的軸心軌跡周期特性。分析比較了不同載荷對主要參數的影響。最后針對軸頸受動載荷時軸心發(fā)生的振動做了主動控制。通過主動控制軸瓦的擺動來改變油膜壓力,進而實現對軸頸振動的抑制。給出了兩種控制方法,即基于預定軌跡的控制方法和基于反饋調節(jié)的控制方法。給出了對軸心振動主動控制的實例,計算結果表明兩種控制方法均實現減小軸心振動的目的。
[Abstract]:Flexible hinged tilting pad bearings are not only as stable as ordinary tilting pad bearings. At the same time, it can overcome the disadvantages such as complicated structure of ordinary tilting pad bearing, high requirement of machining and assembly, easy wear and tear of fulcrum, easy to form error accumulation and easy to produce flutter of bearing bush. The hydrostatic bearing has both dynamic and static pressure performance. Some scholars have tried to combine the tilting pad bearing with the hydrostatic bearing to make it have the advantages of both. The feasibility of introducing static pressure into tilting pad bearing and its superiority over ordinary tilting pad bearing and hydrostatic bearing are proved. However, the flexure hinge structure is not used in these researches, and there are still some problems such as complex fulcrum structure and high requirement of machining and assembling. To solve the above problems, the static pressure chamber is introduced into the flexible hinged tilting pad bearing, and the flexible hinge tilting pad bearing with the static pressure chamber is studied in this paper. The oil intake hole is processed in the flexure hinge to feed oil to the hydrostatic chamber. This simplifies the fulcrum structure and overcomes many shortcomings of the ordinary fulcrum structure. In this paper, the structural design of the bearing, the analysis of its static characteristics, the response of the axis track after the load and the active control of the vibration of the shaft center are studied, which provides theoretical guidance for the engineering application of this kind of new tilting pad bearing. The main contents are as follows: the structure of the bearing is designed and the oil supply to the hydrostatic oil chamber of the bearing is designed by processing the intake hole in the flexure hinge. The formula of oil film thickness and the Reynolds equation of lubrication are given by establishing a dynamic and static pressure flexible hinge tilting pad bearing calculation model. The Reynolds equation is solved discretely by the finite difference method and the overrelaxation iteration method, and the static performance of the bearing is calculated with Newton iteration method. The bearing load coefficient, flow coefficient, friction coefficient and power consumption under different eccentricity, rotational speed and hydrostatic pressure cavity size are compared, and the static performance parameters of bearing under certain working conditions are obtained by comparing the variation of bearing load coefficient, flow coefficient, friction coefficient and power consumption. The calculation model of bearing-rotor system axis trajectory and bearing bush swing is established. The nonlinear axis trajectory and bearing displacement are calculated by Euler method. The transient characteristics of the axis locus under the action of step load, rectangular pulse load and triangular pulse load are analyzed, as well as the periodic characteristics of the axis trajectory under unbalanced loads. The effects of different loads on the main parameters are analyzed and compared. Finally, active control is made for the vibration of the shaft center when the journal is subjected to dynamic load. The oil film pressure can be changed by controlling the swinging of the bearing bush, and the vibration of the journal can be suppressed. Two control methods are presented, one is based on predetermined trajectory and the other is based on feedback regulation. An example of active control of axial center vibration is given. The calculation results show that both control methods achieve the purpose of reducing axis center vibration.
【學位授予單位】：山東大學
【學位級別】：碩士
【學位授予年份】：2017
【分類號】：TH133.3

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