【摘要】：游梁式抽油機在現(xiàn)有采油機械中占絕大多數(shù),針對其傳統(tǒng)設(shè)計方法(自底向上)效率低,而采用自頂向下設(shè)計方法設(shè)計游梁式抽油機研究較少,因此本文根據(jù)抽油機基本參數(shù)信息,對游梁式抽油機進行自頂向下參數(shù)化設(shè)計,為減少設(shè)計成本,縮短產(chǎn)品設(shè)計周期具有重要意義。針對抽油機是個多構(gòu)件的系統(tǒng),其在工作過程中,抽油機的關(guān)鍵部件,尤其是連桿易在循環(huán)交變載荷下發(fā)生疲勞破壞。目前對抽油機關(guān)鍵部件進行疲勞預(yù)測一般采用靜態(tài)施加載荷方法,這種方法分析不夠準確,與實際不相符。因此如何使用動態(tài)方法對抽油機關(guān)鍵部件進行疲勞壽命研究,對其疲勞預(yù)測具有重要意義。本文以一種游梁式抽油機為研究對象,對其進行了自頂向下設(shè)計和聯(lián)合仿真研究,具體研究工作及成果,主要體現(xiàn)有以下幾個方面。(1)以Creo軟件為平臺,運用自頂向下的設(shè)計方法對該型游梁式抽油機進行參數(shù)化設(shè)計。針對抽油機結(jié)構(gòu)復(fù)雜性,對其劃分為四大模塊。對每個模塊建立子骨架模型,以此為中間樞紐傳遞頂層設(shè)計信息,保證了整個設(shè)計過程中數(shù)據(jù)緊密聯(lián)系。采用此設(shè)計方法實現(xiàn)了模型快速設(shè)計效果,縮短了產(chǎn)品設(shè)計周期,使游梁式抽油機的設(shè)計效率大幅提升。(2)利用Mathcad參數(shù)計算與Creo之間參數(shù)傳遞完成了游梁式抽油機設(shè)計計算和模型設(shè)計。此設(shè)計方法從游梁式抽油機參數(shù)計算到其裝配模型的形成,全過程若有參數(shù)計算,則其結(jié)果就能及時傳遞到幾何模型上,且快速又準確,此設(shè)計方法彌補了傳統(tǒng)設(shè)計計算的不足,促進了設(shè)計效率的提高。(3)基于AMESim軟件中建立了游梁式抽油機系統(tǒng)的1D仿真模型,仿真分析了懸點運動和動力特性,將仿真得出的懸點位移、速度、加速度和載荷結(jié)果,與理論計算進行了對比分析,驗證了其準確性。(4)在Motion軟件中建立了游梁式抽油機的多剛體動力學(xué)模型,并基于AMESim 1D和Motion 3D聯(lián)合仿真的方法,對游梁式抽油機進行了動力學(xué)仿真分析,得到了驢頭懸點的運動規(guī)律以及抽油機四連機構(gòu)各鉸接處受力、減速器齒輪嚙合力等主要動態(tài)作用力的時間歷程。(5)對連桿柔性化的游梁式抽油機進行了剛?cè)狁詈蟿恿W(xué)仿真分析,得到了連桿的固有特性,表明了連桿本體中部固有振幅最大。通過將剛?cè)狁詈蟿恿W(xué)仿真結(jié)果與剛體動力學(xué)仿真結(jié)果對比分析,發(fā)現(xiàn)連桿柔性化之后能夠更加真實地反映出連桿系的動態(tài)特性。對連桿進行應(yīng)力、變形分析表明,連桿上的最大應(yīng)力處位于連桿桿體結(jié)構(gòu)過渡圓角處,最大變形發(fā)生在連桿結(jié)構(gòu)兩端部。(6)利用剛?cè)狁詈蟿恿W(xué)計算的結(jié)果,得出連桿的模態(tài)參與因子,將模態(tài)參與因子與模態(tài)進行線性疊加,得到連桿的載荷歷程,并將其作為疲勞分析輸入數(shù)據(jù),利用Virtaul.Lab的Durability模塊對連桿進行了系統(tǒng)級疲勞分析,獲得準確地的連桿疲勞壽命值和損傷分布,確定了連桿疲勞損傷位置。研究結(jié)果可為抽油機關(guān)鍵部件疲勞壽命研究提供重要參考。此方法也為相似機械產(chǎn)品開發(fā)早期的疲勞損傷位置和疲勞壽命的預(yù)測提供了參考,同樣對其它相關(guān)領(lǐng)域很實用。
[Abstract]:The beam pumping unit occupies an overwhelming majority in the existing oil production machinery. In view of its traditional design method (bottom up), the efficiency is low, and the design of beam pumping unit with the top down design method is less. Therefore, based on the basic parameter information of the pumping unit, this paper makes a top-down parameterized design for the beam pumping unit, in order to reduce the design. It is of great significance to shorten the design cycle of the product. In the process of the pumping unit, the key components of the pumping unit, especially the connecting rod, are prone to fatigue damage under cyclic alternating load. At present, the fatigue prediction of the key components of the pumping unit is used as a static loading method, this method is analyzed. It is not accurate enough and does not agree with the actual situation. So how to use dynamic method to study the fatigue life of the key components of the pumping unit is of great significance to its fatigue prediction. In this paper, a beam pumping unit is used as the research object. The next few aspects. (1) take the Creo software as the platform, use the top-down design method to design this type of beam pumping unit. According to the complexity of the pumping unit, it is divided into four modules. A subframework model is set up for each module to pass the top layer design information for the middle hub and ensure the number of the whole design process. According to the close connection, the design method of the model can be realized quickly, the design cycle of the product is shortened and the design efficiency of the beam pumping unit is greatly improved. (2) the design calculation and model design of the beam pumping unit are completed by Mathcad parameter calculation and Creo parameter transfer. The design method is from the beam pumping unit parameters. To calculate the formation of the assembly model, if the whole process is calculated, the result can be transferred to the geometric model in time, and it is fast and accurate. The design method makes up the shortage of the traditional design and improves the design efficiency. (3) based on the AMESim software, the 1D simulation model of the beam pumping unit is built. The suspension point motion and dynamic characteristics are analyzed. The results of the suspended point displacement, velocity, acceleration and load are compared with the theoretical calculation. The accuracy is verified by the theoretical calculation. (4) the multi rigid body dynamic model of the beam pumping unit is established in the Motion software, and the beam pumping is based on the joint simulation of AMESim 1D and Motion 3D. The dynamic simulation analysis of the oil machine is carried out. The motion law of the hanging point of the donkey head and the time history of the main dynamic forces, such as the force of the hinge joints at the four linkage mechanism of the pumping unit, the gear meshing force of the reducer, etc.. (5) the rigid flexible coupling dynamics simulation analysis is carried out on the flexible beam pumping unit of the connecting rod, and the inherent characteristics of the connecting rod are obtained. It shows the maximum inherent amplitude in the central part of the connecting rod. By comparing the simulation results of rigid flexible coupling dynamics with the simulation results of rigid body dynamics, it is found that after the connecting rod is flexible, the dynamic characteristics of the connecting rod system can be more truly reflected. The stress on the connecting rod and the deformation analysis show that the maximum stress on the connecting rod is located in the rod body. The maximum deformation occurs at the two ends of the connecting rod structure at the transition angle of the structure. (6) the modal participation factor of the connecting rod is obtained by the results of the rigid flexible coupling dynamic calculation. The modal participation factor and the modal are linear superimposed, and the load history of the connecting rod is obtained, and it is used as the fatigue analysis input data, and the Durability module of Virtaul.Lab is used. The fatigue life value and damage distribution of the connecting rod are obtained, and the fatigue damage position of the connecting rod is determined. The results can provide an important reference for the study of the fatigue life of the key components of the pumping unit. This method also predicts the early fatigue damage position and fatigue life of the similar mechanical product. For reference, it is also useful for other related fields.
【學(xué)位授予單位】：西南石油大學(xué)
【學(xué)位級別】：碩士
【學(xué)位授予年份】：2017
【分類號】：TE933.1

【參考文獻】

相關(guān)期刊論文 前10條

1 高海軍;孫文磊;譚遠華;;基于剛?cè)狁詈系某橛蜋C多體系統(tǒng)動力學(xué)分析[J];機械設(shè)計與制造;2015年12期

2 方吉;兆文忠;樸明偉;;基于模態(tài)疊加法的焊接結(jié)構(gòu)疲勞壽命預(yù)測方法研究[J];振動與沖擊;2015年05期

3 呂國林;褚學(xué)寧;儲德新;沈靖;劉相振;;自頂向下設(shè)計的多骨架建模方法[J];計算機輔助設(shè)計與圖形學(xué)學(xué)報;2015年03期

4 崔娜娜;吳娟;崔海云;;基于Motion/AMESim的某變載機構(gòu)的建模與仿真分析[J];液壓氣動與密封;2013年09期

5 何畏;王向濤;孫宇;王鈺文;;抽油機連桿的力學(xué)分析及結(jié)構(gòu)改進[J];天然氣與石油;2013年03期

6 駱清國;王旭東;張更云;楊良平;冉光政;;變工況下的發(fā)動機連桿動態(tài)應(yīng)力與疲勞損傷分析[J];車用發(fā)動機;2012年04期

7 彭謙;馬晨光;楊雪梅;范瀅;;線性模態(tài)分析中的參與因子與貢獻因子[J];電網(wǎng)技術(shù);2010年02期

8 鄭滿圈;;游梁式抽油機運動規(guī)律的多體動力學(xué)分析[J];石油機械;2006年05期

9 王宏偉;邢波;駱紅云;;雨流計數(shù)法及其在疲勞壽命估算中的應(yīng)用[J];礦山機械;2006年03期

10 任尊松,孫守光,李強,毛娟;構(gòu)架結(jié)構(gòu)振動與動態(tài)應(yīng)力仿真研究[J];機械工程學(xué)報;2004年08期

相關(guān)博士學(xué)位論文 前2條

1 徐金超;游梁抽油機正扭矩調(diào)制方法及關(guān)鍵技術(shù)[D];中國石油大學(xué)(華東);2014年

2 繆炳榮;基于多體動力學(xué)和有限元法的機車車體結(jié)構(gòu)疲勞仿真研究[D];西南交通大學(xué);2007年

相關(guān)碩士學(xué)位論文 前10條

1 蔣帆;游梁式抽油機尾部支撐結(jié)構(gòu)的分析研究[D];蘭州理工大學(xué);2016年

2 常娟;基于NX自頂向下的后裝壓縮式垃圾車設(shè)計技術(shù)研究[D];安徽理工大學(xué);2015年

3 徐叢國;挖掘機回轉(zhuǎn)馬達總成技術(shù)研究及回轉(zhuǎn)系統(tǒng)機液聯(lián)合仿真[D];貴州大學(xué);2015年

4 謝寧;振動模態(tài)對高速列車車體疲勞壽命的影響分析[D];西南交通大學(xué);2015年

5 楊保貴;游梁式抽油機虛擬樣機測試及有限元仿真分析[D];長安大學(xué);2015年

6 羅愿欣;油氣緩沖器動態(tài)和靜壓曲線仿真計算及研究[D];西安工業(yè)大學(xué);2015年

7 王繼明;懸臂式掘進機機液聯(lián)合仿真研究[D];沈陽建筑大學(xué);2015年

8 邢金玲;柔性機構(gòu)在常規(guī)型抽油機中的應(yīng)用與研究[D];蘭州理工大學(xué);2014年

9 鄧朋儒;基于多體動力學(xué)的鐵路斜拉橋車—橋耦合分析及疲勞損傷評估[D];中南大學(xué);2014年

10 易yN;顎式破碎機自頂向下的參數(shù)化設(shè)計及其有限元分析[D];太原理工大學(xué);2014年

，

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