本文選題：履帶式聯(lián)合收割機 + 行走變速箱��； 參考：《江蘇大學(xué)》2017年碩士論文

【摘要】：履帶式聯(lián)合收割機是我國水稻收獲的主要工具,而隨著我國水稻連片種植面積的增加,對其作業(yè)效率和承載能力都提出了更加嚴(yán)格的要求。為適應(yīng)市場需求,水稻收割機械的割幅、喂入量、整機質(zhì)量都在逐漸增加,變速箱作為聯(lián)合收割機產(chǎn)品最重要的行駛性能控制部件和功率傳輸部件,其承載能力也需隨之增大,使之適配功率能夠達(dá)到85~95kW。因此,如何提高變速箱的承載能力成為了研究重點,對變速箱工作原理的研究、結(jié)構(gòu)創(chuàng)新的設(shè)計變得尤為重要。本文根據(jù)已有收割機行走變速箱峰值載荷的測試和適配功率達(dá)85~95kW的設(shè)計要求,設(shè)計一種JS90型履帶式聯(lián)合收割機變速箱�；诶碚撛O(shè)計計算,利用Pro/E對變速箱進(jìn)行建模;結(jié)合ADAMS與ANSYS,對變速箱傳動系統(tǒng)與關(guān)鍵部件進(jìn)行動力學(xué)分析和模態(tài)分析,與理論計算結(jié)果進(jìn)行對比,驗證變速箱的可行性;并對變速箱進(jìn)行試驗驗證。本文的主要研究內(nèi)容有:(1)針對現(xiàn)有履帶式聯(lián)合收割機變速箱由于過載工作導(dǎo)致齒面膠合、制動器殼破裂及制動片燒毀的現(xiàn)象,以江蘇沃得農(nóng)業(yè)機械有限公司生產(chǎn)的飛龍4LZ-4.0A型履帶式聯(lián)合收割機為試驗樣機,基于無線傳感技術(shù),對收割機行走變速箱動力輸出半軸的載荷進(jìn)行測定。選擇四種不同類型的路面、兩種不同傾角的路面對試驗車變速箱半軸的直線行駛載荷進(jìn)行測試,并在泥田路面對其進(jìn)行轉(zhuǎn)彎行駛載荷測試。測試數(shù)據(jù)表明,收割機在傾角為13°路面行駛時半軸扭矩峰值為1057.33 N·m,功率值為33.21kW;收割機在泥田路面轉(zhuǎn)彎行駛時半軸扭矩峰值為1660.2 N·m,功率值為31.29kW。這兩種工況下,半軸載荷超越了其承載能力,可知收割機在田間過埂或轉(zhuǎn)彎行駛時,行走變速箱處于過載狀態(tài),致使收割機變速箱存在可靠性低、故障率高的缺陷。(2)以4LD-5.0型履帶式聯(lián)合收割機底盤的性能參數(shù)為要求,提出變速箱的設(shè)計方案和傳動系統(tǒng)圖。確定其三個檔位傳動比分別為36.16、22.45、16.96�；诼膸к囕v行駛力學(xué),確定變速箱各檔位不同軸扭矩、功率及轉(zhuǎn)速等關(guān)鍵值。利用變速箱各零部件所受最大載荷值,對齒輪、軸及花鍵進(jìn)行理論設(shè)計計算和強度校核。由于小齒輪易發(fā)生根切、強度比大齒輪低,因此對變速箱齒輪系進(jìn)行變位處理,改善齒輪嚙合特性。根據(jù)齒輪、軸等部件設(shè)計計算的參數(shù)值,利用Pro/E三維制圖軟件對變速箱整體進(jìn)行建模與虛擬裝配。(3)為驗證變速箱的可行性,利用ADAMS仿真軟件對變速箱整體齒輪傳動機構(gòu)進(jìn)行動力學(xué)分析。以變速箱二檔工況為例,通過定義材料屬性、添加轉(zhuǎn)動副約束、施加扭矩載荷,最后添加轉(zhuǎn)速驅(qū)動,完成對虛擬樣機的前期處理。基于碰撞接觸理論,對變速箱的嚙合力進(jìn)行動力學(xué)分析,得到了變速箱最后一對傳動齒輪齒面嚙合力以及轉(zhuǎn)動角速度值,分別為24178.35N、748.32d/s,通過與理論計算值對比,數(shù)據(jù)基本相符,驗證了仿真結(jié)果的可靠性。為驗證齒輪、軸的可靠性,利用ANSYS仿真軟件中瞬態(tài)動力學(xué)分析模塊(Transient Structural)對模型進(jìn)行應(yīng)力分析,對齒輪和動力輸出半軸都施加隨時間改變的載荷,分析得到齒輪及動力輸出半軸的應(yīng)力云圖�？芍�,軸受到的最大應(yīng)力為450.32MPa,齒輪受到的最大應(yīng)力為385.54MPa,都小于材料的屈服極限值835MPa。為分析變速箱的固有頻率,利用ANSYS仿真軟件中模態(tài)分析模塊(Modal)對動力輸出半軸進(jìn)行模態(tài)分析,得到半軸的前四階模態(tài)振型,可知軸的一階固有頻率為182.49Hz,而該軸最高轉(zhuǎn)頻為121.04Hz,明顯低于一階模態(tài)的固有頻率值。(4)進(jìn)行JS90型變速箱加工與試制,并將裝配結(jié)束后的變速箱安裝在4LD-5.0型履帶式聯(lián)合收割機底盤上,組成JS90型變速箱性能驗證試驗車,整機滿載質(zhì)量達(dá)到7t。設(shè)置試驗方案來驗證變速箱的傳動性能和效率,選擇水泥路對收割機的直線行駛性能、轉(zhuǎn)彎行駛性能以及行走載荷進(jìn)行測試,并對試驗數(shù)據(jù)進(jìn)行分析。可知:收割機一檔的行駛速度為1.00m/s;二檔的行駛速度為1.54m/s;三檔的行駛速度為2.05m/s;轉(zhuǎn)彎角速度最快可以達(dá)到0.625rad/s;動力輸出半軸受到的最大扭矩為4293.29N·m。收割機的行駛速度要求均能正常實現(xiàn),且在試驗過程中,變速箱換擋平順,無任何異響和故障出現(xiàn),證明了設(shè)計變速箱的可行性。
[Abstract]:The caterpillar combine harvester is the main tool for rice harvest in China, and with the increase of rice area in China, the operation efficiency and carrying capacity are more strictly required. In order to meet the demand of the market, the cutting width, feeding quantity and the whole machine quality of rice harvesting machinery are increasing gradually, and the gearbox is used as a combine harvester. The most important driving performance control component and power transmission component of the product, its bearing capacity also need to increase, so that the matching power can reach 85~95kW., so how to improve the carrying capacity of the transmission has become the focus of research. It is very important to study the working principle of the gearbox and the new design of the structure. This paper is based on the existing harvest. The design of a JS90 type caterpillar combine gearbox is designed for the test of the peak load of the traveling gearbox and the design requirement of the suitable power of 85~95kW. Based on the theoretical design and calculation, the gearbox is modeled with Pro/E, and the dynamic analysis and modal analysis of the transmission system and the key components are carried out with the ADAMS and the ANSYS, and the theory is analyzed. The calculation results are compared to verify the feasibility of the transmission and test the gearbox. The main contents of this paper are as follows: (1) the phenomenon of the tooth surface gluing, the rupture of the brake shell and the burning of the brake disc caused by the overload work of the existing caterpillar combine harvester, is produced by the Jiangsu Wald cheerful agriculture machinery corp. Feilong 4LZ-4.0A type caterpillar combine harvester is an experimental prototype. Based on wireless sensing technology, the load of the dynamic output semi shaft of the walking transmission of a harvester is measured. Four kinds of different types of pavement are selected and two different angles are tested for the linear driving load of the semi axle of the test vehicle, and they are faced in the mud field road. The test data show that the peak torque peak of the reaper is 1057.33 N / M and the power value is 33.21kW when the dip angle is 13 degrees, and the peak torque peak of the reaper is 1660.2 N. M when the harvester is turning on the mud field road, and the power value is 31.29kW.. The load of the semi shaft is beyond its bearing capacity. When the cutting machine is crossing or turning in the field, the walking transmission is in the overload state, which causes the defect of the gearbox of the harvester low reliability and high failure rate. (2) the design and transmission system of the gearbox are proposed with the performance parameters of the 4LD-5.0 type caterpillar combine harvester, and the transmission ratio of the three gear positions is determined to be 3, respectively. 6.16,22.45,16.96. is based on the driving mechanics of the tracked vehicle to determine the key values of torque, power and speed of the different gear axes of the gearbox. The theoretical design calculation and strength checking of the gear, shaft and spline are carried out by using the maximum load value of each component of the gearbox. The strength of the gear wheel is easy to take root and the strength is lower than that of the large gear. So the transmission box is made to the gearbox. The gear system is modified to improve the gear meshing characteristics. According to the parameter values of the gear, shaft and other parts, the Pro/E 3D drawing software is used to model and virtual assembly of the gearbox. (3) to verify the feasibility of the gearbox, the dynamic analysis of the gear transmission mechanism of the variable speed box is carried out by using the ADAMS simulation software. As an example of the second gear condition of the speed box, by defining the material properties, adding the rotation pair constraint, applying the torque load and adding the speed drive, the initial treatment of the virtual prototype is completed. Based on the collision contact theory, the dynamic analysis of the rodent force of the gearbox is carried out, and the meshing force and rotation angular speed of the last pair of transmission gear teeth are obtained. To verify the reliability of the gear and shaft, the reliability of the gear and shaft is verified by comparison with the theoretical calculation. In order to verify the reliability of the gear and shaft, the stress analysis of the model is carried out by the transient dynamic analysis module (Transient Structural) in the ANSYS simulation software, which is applied to the gear and the power output semi axis. It can be found that the maximum stress of the shaft is 450.32MPa and the maximum stress of the gear is 385.54MPa, which is less than the yield limit value 835MPa. of the material to analyze the inherent frequency of the gearbox, and uses the modal analysis module (Modal) in the ANSYS simulation software to drive the power transmission. The first four order modal vibration modes of the semi axle are obtained by modal analysis. The first order natural frequency of the axis is 182.49Hz, and the maximum frequency of the axis is 121.04Hz, which is obviously lower than the natural frequency value of the first order mode. (4) the processing and trial production of the JS90 type transmission box is carried out, and the gearbox after the assembly knot is installed in the 4LD-5.0 type caterpillar type joint reaping. On the machine chassis, the JS90 type transmission performance test vehicle is formed. The full load quality of the machine reaches the 7T. setting test scheme to verify the transmission performance and efficiency of the gearbox. It chooses the cement road to test the linear driving performance of the harvester, the turning performance and the walking load, and analyses the test data. We know that the harvester is one gear The driving speed is 1.00m/s, the driving speed of the second gear is 1.54m/s, the driving speed of the third gear is 2.05m/s, the turning angle speed can reach 0.625rad/s, and the maximum torque of the power output semi shaft is the normal realization of the driving speed of the 4293.29N. M. harvester, and in the test process, the gearbox has a smooth shift, without any abnormal sound and reason. The obstacle appeared, which proved the feasibility of the design of the gearbox.
【學(xué)位授予單位】：江蘇大學(xué)
【學(xué)位級別】：碩士
【學(xué)位授予年份】：2017
【分類號】：S225

【參考文獻(xiàn)】

相關(guān)期刊論文 前10條

1 王仰龍;馮曉靜;劉俊峰;劉偉;;果園風(fēng)送噴霧機風(fēng)機葉片模態(tài)分析——基于ANSYS Workbench[J];農(nóng)機化研究;2015年03期

2 陳慶文;韓增德;崔俊偉;王國新;喬曉東;張子瑞;韓科立;甘邦興;;自走式谷物聯(lián)合收割機發(fā)展現(xiàn)狀及趨勢分析[J];中國農(nóng)業(yè)科技導(dǎo)報;2015年01期

3 牟鵬博;陶鳳和;賈長治;馬萬里;;履帶車輛變速箱齒輪嚙合過程分析及壽命預(yù)測[J];機械傳動;2014年01期

4 朱昊;盧澤民;李耀明;;履帶式聯(lián)合收獲機械差動變速箱的設(shè)計與仿真[J];農(nóng)機化研究;2014年01期

5 王剛;吳崇友;伍德林;;我國通用型聯(lián)合收割機現(xiàn)狀與發(fā)展思考[J];中國農(nóng)機化學(xué)報;2013年06期

6 王飆;劉峰;李云伍;;我國水稻收割機的發(fā)展現(xiàn)狀及發(fā)展方向[J];農(nóng)機化研究;2013年10期

7 李海同;黃鵬;舒彩霞;;我國稻麥油機械化收獲技術(shù)研究現(xiàn)狀與趨勢[J];農(nóng)業(yè)工程;2013年05期

8 王峗;;聯(lián)合收割機變速箱工藝革新技術(shù)[J];農(nóng)業(yè)與技術(shù);2013年08期

9 林宇鋼;劉麗敏;周益君;王琛;方向;;4LYWB-33型履帶自走式聯(lián)合收割機變速控制系統(tǒng)設(shè)計[J];農(nóng)機化研究;2013年03期

10 馮江;蔣亦元;;水稻聯(lián)合收獲機單邊驅(qū)動原地轉(zhuǎn)向機構(gòu)的機理與性能試驗[J];農(nóng)業(yè)工程學(xué)報;2013年04期

相關(guān)博士學(xué)位論文 前1條

1 佴軍;近30年江蘇省水稻生產(chǎn)的時空變化與效益分析[D];揚州大學(xué);2013年

相關(guān)碩士學(xué)位論文 前9條

1 張國鑫;某履帶車輛傳動系統(tǒng)動態(tài)扭矩測試與數(shù)據(jù)預(yù)處理[D];北京理工大學(xué);2016年

2 胡際勇;重型履帶車輛軟地面行駛性能研究[D];吉林大學(xué);2012年

3 陳媛媛;履帶車輛行動系統(tǒng)動力學(xué)仿真分析[D];沈陽理工大學(xué);2012年

4 王廣敏;5t裝載機變速箱的改進(jìn)與試驗研究[D];吉林大學(xué);2011年

5 耿興春;機械式變速箱建模及虛擬樣機性能仿真[D];南華大學(xué);2010年

6 傅友賓;基于PRO/E和ADAMS的變速器動力學(xué)仿真[D];大連理工大學(xué);2007年

7 鄭鳳新;大功率行走機械自動變速箱的設(shè)計與研究[D];蘭州理工大學(xué);2006年

8 劉莉;重型履帶車輛行走裝置設(shè)計理論與方法研究[D];吉林大學(xué);2005年

9 康正生;TY420履帶式推土機行星齒輪變速箱設(shè)計研究[D];大連理工大學(xué);2003年

，

本文編號：1951856