手扶式插秧機(jī)設(shè)計(jì)【含CAD圖紙、說明書】

【溫馨提示】壓縮包內(nèi)含CAD圖有下方大圖片預(yù)覽，下拉即可直觀呈現(xiàn)眼前查看、盡收眼底縱觀。打包內(nèi)容里dwg后綴的文件為CAD圖，可編輯，無水印，高清圖，壓縮包內(nèi)文檔可直接點(diǎn)開預(yù)覽，需要原稿請自助充值下載，所見才能所得，請見壓縮包內(nèi)的文件及下方預(yù)覽，請細(xì)心查看有疑問可以咨詢QQ：11970985或197216396 摘 要本文重點(diǎn)介紹手扶式插秧機(jī)的研究，以及系統(tǒng)和理論計(jì)算的主要組成部分。整個(gè)結(jié)構(gòu)由柴油機(jī)進(jìn)行動(dòng)能提供。本文摘要：1手扶式插秧機(jī)整體結(jié)構(gòu)設(shè)計(jì)。2手扶式種植機(jī)的性能分析。3柴油發(fā)動(dòng)機(jī)選擇。4手扶式種植機(jī)，所述執(zhí)行單元和機(jī)架設(shè)計(jì)的傳輸。5設(shè)計(jì)元素設(shè)計(jì)分析和驗(yàn)證的計(jì)算。6來繪制整個(gè)裝配圖，裝配圖和零件圖的設(shè)計(jì)部分的重要組成部分。關(guān)鍵詞：手扶式插秧機(jī)；柴油機(jī)；機(jī)械設(shè)計(jì)AbstractThis paper focuses on walk-behind transplanter research, and major aircraft components and systems design agencies and Theoretical calculation.The whole structure is provided by the diesel engine.This thesis Abstract:(1) Walk-transplanter overall structural design.(2) Walk-transplanter performance analysis.Select (3) diesel engine.(4) Transmission of walk-behind transplanter, the execution unit and rack design.(5) Calculation of design parts design analysis and verification.(6) to draw the whole assembly drawings and assembly drawings and important parts of the design part of the part drawing.Key words:walk-behind transplanter; diesel engine; Machine Design壓縮包內(nèi)含有CAD圖紙和說明書,咨詢Q 197216396 或 11970985目 錄摘 要IVAbstractV第1章 緒論11.1 課題研究意義11.2 研究內(nèi)容11.3研究方法1第2章 手扶式插秧機(jī)系統(tǒng)總體設(shè)計(jì)22.1手扶式插秧機(jī)系統(tǒng)總體方案22.2 手扶式插秧機(jī)的動(dòng)力性能比較32.3 手扶式插秧機(jī)動(dòng)力的計(jì)算與選擇4第3章 帶傳動(dòng)的計(jì)算63.1 帶傳動(dòng)設(shè)計(jì)63.2選擇帶型73.3 確定帶輪的基準(zhǔn)直徑并驗(yàn)證帶速73.4確定中心距離、帶的基準(zhǔn)長度并驗(yàn)算小輪包角83.5 確定帶的根數(shù)z93.6 確定帶輪的結(jié)構(gòu)和尺寸93.7 確定帶的張緊裝置103.8計(jì)算壓軸力10第4章 軸的設(shè)計(jì)與校核124.1 軸的設(shè)計(jì)124.2 軸的校核15第5章 鍵的選擇與校核195.1 帶輪1上鍵的選擇與校核195.1.1鍵的選擇195.1.2 鍵的校核195.2 帶輪2上鍵的選擇與校核215.2.1 鍵的選擇215.2.2 鍵的校核21第6章 地輪和機(jī)架的設(shè)計(jì)246.1 地輪的設(shè)計(jì)246.2 機(jī)架部分的設(shè)計(jì)24結(jié) 論25參考文獻(xiàn)26致 謝27XII 第1章 緒論第1章 緒論1.1 課題研究意義 跟人工插秧比較，用插秧機(jī)插秧具有插秧精準(zhǔn)，插秧質(zhì)量好，排距均勻等優(yōu)點(diǎn)。并且插秧機(jī) 采用的是旱育秧苗，使之栽種后成活率較高增產(chǎn)效果顯著。水稻插秧機(jī)在已被廣泛接受的情況下，所以我們需要為了能增產(chǎn)更多而提高機(jī)插秧的工作效率。1.2 研究內(nèi)容本文著重研究步入式種植機(jī)，它具有重量輕，體積小，適應(yīng)力強(qiáng)，造價(jià)低等特點(diǎn) 實(shí)現(xiàn)了機(jī)械化插秧機(jī)的目的。其主要內(nèi)容如下：1符合條件插秧機(jī)農(nóng)業(yè)研究和確定最重要的參數(shù)機(jī)構(gòu)。2檢查和確定每個(gè)采集箱部件的結(jié)構(gòu)和結(jié)構(gòu)的理論分析，以獲得最佳性能。3靈活遞送系統(tǒng)。在輸送過程中秧苗容易損傷表皮，是十分有害的，因此，需要重新的創(chuàng)新。1.3研究方法1通過大量的文獻(xiàn)資料，吸收和借鑒國內(nèi)外步入式種植機(jī)等機(jī)械插秧機(jī)運(yùn)輸，研究并確定了步入式插秧機(jī)運(yùn)輸系統(tǒng)的關(guān)鍵參數(shù)。19 第2章 手扶式插秧機(jī)系統(tǒng)總體設(shè)計(jì)第2章 手扶式插秧機(jī)系統(tǒng)總體設(shè)計(jì)2.1手扶式插秧機(jī)工作原理和分類 圖2.1 手扶式括秧機(jī)其中： 1. 中間浮板， 2. 側(cè)浮板， 3. 機(jī)架， 4. 發(fā)動(dòng)機(jī)， 5. 驅(qū)動(dòng)輪傳動(dòng)箱， 6. 變速箱，7. 驅(qū)動(dòng)輪， 8. 移箱傳動(dòng)機(jī)構(gòu)下箱體， 9. 移箱傳動(dòng)機(jī)構(gòu)上箱體， 10. 栽植臂傳動(dòng)箱， 11. 栽植臂， 12. 秧針， 13. 渭道， 14. 扶手， 15. 秧苗箱， 16. 支架， 17. 備秧臺， 18. 上蓋， 19. 自動(dòng)潤滑裝置。水稻插秧機(jī)的設(shè)計(jì)是使用育苗塊的均勻切割原理實(shí)現(xiàn)幼苗分離和移植,設(shè)置線、深度、定點(diǎn)和Dingmiao種植的目的。只要幼苗的苗分布,定量地區(qū)開墾耙地幼苗針降低幼苗,幼苗數(shù)量每洞更均勻,因?yàn)橛酌玑樦饕欠蛛x的育苗塊,不是生命的幼苗,幼苗損傷的可能性大大降低。幼苗插秧機(jī)的工作當(dāng)針插入到土壤后抓住苗育苗塊量化塊,當(dāng)種植深度設(shè)置,種植幼苗從上插秧苗的針叉機(jī)制,插入到土壤,種植過程的完成。同時(shí),浮板和液壓系統(tǒng),浮板和幼苗的相對位置控制針,以便保持一致的種植深度。插秧機(jī)通常根據(jù)操作方式和移植速度分類。根據(jù)操作方式可分為車把方向步行式移栽機(jī)和圓盤的方向(騎)水稻插秧機(jī)。根據(jù)移植速度可分為普通水稻插秧機(jī)和高速插秧機(jī)。目前,步行式插秧機(jī)是普通水稻插秧機(jī)。2.2 手扶式插秧機(jī)的動(dòng)力性能比較表2-2 原動(dòng)機(jī)性能比較類別柴油機(jī)液壓馬達(dá)柴油機(jī)尺寸較大較小較大功率及取范圍功率大；0.31000KW，范圍廣功率最大；受實(shí)際油壓和馬達(dá)尺寸的限制功率大；538000KW重量大最大大輸出剛度硬較硬較硬運(yùn)行溫度控制溫度應(yīng)低于許應(yīng)值對油箱進(jìn)行風(fēng)冷或水冷調(diào)整方法和性能直流柴油機(jī)通過改變電樞電阻、電壓、變造通量方法;AC變頻柴油機(jī),變量或改變滑動(dòng)的方法通過閥或泵控制改變流量，調(diào)速范圍大較難噪聲小較大較大維護(hù)要求較少較多較多初始成本低高高運(yùn)轉(zhuǎn)費(fèi)用最低高高應(yīng)用很廣，需要?jiǎng)恿﹄娫摧^廣非常廣泛,如各種車輛、船舶、農(nóng)業(yè)機(jī)械、建筑機(jī)械和壓縮機(jī)等等2.3 手扶式插秧機(jī)動(dòng)力的選擇考慮到插秧機(jī)工作環(huán)境和工作要求關(guān)閉插秧機(jī)起動(dòng)轉(zhuǎn)矩和速度范圍,等等,我選擇了柴油機(jī)作為動(dòng)力在大多數(shù)情況下，插秧機(jī)一搬都在水下或泥土中工作，甚至在腐蝕等環(huán)境中工作，所以就要選擇特定的機(jī)器。這些類型包括：開放式，屏蔽，密封，防爆。要求的其他機(jī)構(gòu)運(yùn)行功率小，所以總P的粗略估計(jì)不超過10KW。品牌：常柴型號： S195分類：單缸柴油機(jī)配套功率：10.6KW/2200r/min 第3章 帶傳動(dòng)的計(jì)算第3章 帶傳動(dòng)的計(jì)算3.1 帶傳動(dòng)的設(shè)計(jì)單缸柴油機(jī)輸出功率P = 10.6千瓦,速度n1 = 2200 r / min表3-1 工作情況系數(shù) 根據(jù)V帶的負(fù)載平穩(wěn)，查機(jī)械設(shè)計(jì)P296表4，根據(jù)KA1.1。即3.2選擇帶的類型普通V帶根據(jù)小滑輪的力和速度上設(shè)置，見圖1311。圖3-1 帶型圖按得出的數(shù)據(jù)Pd和小帶輪的轉(zhuǎn)速2200r每分鐘 ，從圖看得出來：，應(yīng)選擇A型V帶。3.3 確定帶輪的基準(zhǔn)直徑并檢驗(yàn)帶速從相關(guān)引用書目第頁表格中137找到，小帶輪基準(zhǔn)尺寸，設(shè)得dd1=90mm ddmin.=75毫米表3-2 V帶的槽式Y(jié)ZABCDE205075125200355500從機(jī)械設(shè)計(jì)書中第295頁13-4找出“V帶的基準(zhǔn)直徑”，設(shè)=250毫米 誤差比值判別： 為彈性滑動(dòng)率誤差 符合規(guī)定的要求 帶速 因?yàn)闈M足5m/sv(6.79m/s)25m/s的要求，所以帶速驗(yàn)算合適。3.4確定中心距、帶的基準(zhǔn)長度并驗(yàn)算小帶輪包角根據(jù)式可以得到0.790+250290+250即238680，選=340毫米 故有： 從相關(guān)書中引用第293頁的表格中132設(shè)Ld為1250mm。（其中a=實(shí)際中心距）所以條件滿足。表3-3. 包角校正系數(shù)包角220210200190180150170160140130120110100901.201.151.101.051.000.920.980.950.890.860.820.780.730.68表3-4. 彎曲影響系數(shù) 帶的類型ABCDE3.5 確定V帶的根數(shù)z根據(jù)公式 Z=三角帶數(shù)目 N1=三角帶傳動(dòng) N0=1根三角帶（根據(jù)長度的穩(wěn)定運(yùn)行，找到表格設(shè)出 N0=2.70） C1為包角系數(shù)，表格中指出，C1=0.98三角帶的功率算得N1=7.5 千瓦代到式子得出，所以需要4根V帶。3.6 確定帶輪的規(guī)模和結(jié)構(gòu)根據(jù)V帶輪結(jié)構(gòu)的選擇標(biāo)準(zhǔn)，電機(jī)的主軸直徑為28毫米；根據(jù)機(jī)械原理書中 ，“V帶輪的結(jié)構(gòu)”值：每次3ddd1(90毫米)300毫米，可以選擇H型孔板式或者P型輻板式帶輪，根據(jù)書中，所以選擇H型孔板式作為小帶輪。帶輪的材料：灰鑄鐵HT200。3.7 帶的張緊裝置決定采用構(gòu)造簡單的張緊裝置。3.8計(jì)算軸的壓力從書中找到，初拉力是，上面已得到=153.36o，z=4，所以計(jì)算得出，V帶輪按輪輻結(jié)構(gòu)的不同可分為以下幾種型式： 1 實(shí)心帶輪：用于較小尺寸的帶輪，見下圖。 2 腹板帶輪：用于中小尺寸的帶輪，見下圖。 3 孔板帶輪：用于尺寸較大的帶輪，見下圖 。 4 橢圓輪輻帶輪：用于尺寸大的帶輪，見下圖。a b c d圖3-2 帶輪結(jié)構(gòu)類型現(xiàn)在我們可以得出結(jié)果：小帶輪用實(shí)心帶輪,大帶輪選孔板帶輪。 第4章 軸的設(shè)計(jì)與校核第4章 軸的設(shè)計(jì)與校核4.1 軸的設(shè)計(jì)1 計(jì)算帶輪上的作用力根據(jù)上面得知，低速帶輪上的直徑為500 而 看圖確定的方向與4.1張緊裝置,可用循環(huán)力,徑向和軸向力。圖4-1 軸上力的載荷分布圖2 初設(shè)軸徑的最小值1首先從我們書目式子15-2毛估軸的最小直徑。選45鋼材質(zhì),調(diào)質(zhì)處理。從我們書本，設(shè)出，于是式子如下：11260.36 軸的結(jié)構(gòu)設(shè)計(jì)1以軸向定位為準(zhǔn)則，來設(shè)定軸的尺寸 先取滾動(dòng)軸承。具體是單列圓錐滾子軸承。根據(jù)工作要求和按照80毫米,最初從軸承產(chǎn)品目錄選擇0的基本組織間隙,標(biāo)準(zhǔn)水平的準(zhǔn)確性單列圓錐滾子軸承GB/T 297199430217型，它的尺寸是dDT85 mm150 mm30.5 mm，因此為85毫米；右端圓錐滾子軸承用套筒來實(shí)現(xiàn)定位，套筒寬設(shè)14 mm，因此為44.5毫米。 選安裝帶輪處的軸段為90毫米；帶輪和左軸承之間是以套筒來定位的。前面已經(jīng)提到，帶輪的寬度為90 毫米，為使套筒端面安全的壓緊帶輪，該軸應(yīng)當(dāng)微微比輪轂寬度小，所以設(shè)為86毫米。帶輪的右端是以軸肩來定位的，軸肩高h(yuǎn)0.07d，因此設(shè)得h為7毫米，式子為，得出104毫米。軸環(huán)寬度,設(shè)b為12毫米。 軸承端蓋總的寬度是37.5 mm。按相關(guān)要求，設(shè)端蓋的外端面與半聯(lián)軸器右端面間距為,所以選擇為67.5毫米。到這里為止，基本上都設(shè)定低速軸的各段直徑和長度。 圖4-2 低速軸的構(gòu)造設(shè)計(jì)示意圖（2） 軸上零件的周向固定按為90毫米，從我們書本上表格6-1可找出，平鍵截面是，bh25 mm14 mm，用鍵槽銑刀加工，長是70毫米，為與軸有很好的配合，因此選帶輪轂與軸的配合為；同理，半聯(lián)軸器與軸之間，是用平鍵為20 mm12 mm90 mm的尺寸來連接的。（3） 設(shè)置軸的圓周和倒角尺寸根據(jù)書上P365的表格15-2，知道軸的左端倒角2x45，和右端倒角是2.5x45。各軸肩的半徑是:處是R2，其它R2.5。（4） 計(jì)算得軸上的載荷 根據(jù)結(jié)構(gòu)圖在圖軸中作出計(jì)算。當(dāng)設(shè)定軸承的支點(diǎn)方位時(shí),應(yīng)從相關(guān)引用書目中a值。關(guān)于30217型圓錐滾子軸承，從相關(guān)引用書目中可找出a29.9 mm。因此，作為簡支梁的軸的支承跨距57.1+71.6128.7 mm。按軸的計(jì)算簡圖最后作出軸的彎矩圖和扭矩圖見圖7.1。從軸的結(jié)構(gòu)圖以及彎矩和扭矩圖中，我們看到截面是危險(xiǎn)截面。如下過程：57.1+71.6128.7 毫米表4-2 低速軸受力參數(shù) 負(fù)載水平面H垂直面V支反力4 966.34 N，3 960.59 N2 676.96 N，679.68 N彎矩283 578.014 152 854.416 486 65.09 總彎矩322 150.53 ,287 723.45扭矩T1 410 990 4.2 軸的校核 1、通過彎曲扭轉(zhuǎn)強(qiáng)度來校核軸的強(qiáng)度檢查軸的最大彎矩和扭矩截面。推薦的書籍的公式，查得表7.2中的數(shù)值，和單向旋轉(zhuǎn)，扭轉(zhuǎn)應(yīng)力脈動(dòng)循環(huán)應(yīng)力，設(shè)0.6，軸的計(jì)算 MPa12.4 MPa從我們書本上找出表格得出60MP。因此 ，證明軸是安全的。2，軸的疲勞強(qiáng)度精確控制1判決險(xiǎn)段軸的橫截面，B完全由扭矩應(yīng)力，雖然電壓花鍵軸肩和過渡配合通過濃縮，軸的疲勞強(qiáng)度都引起的，而是由于柄部的最小直徑衰減扭轉(zhuǎn)力決定A，B，無需檢查。在軸上，橫截面和的疲勞強(qiáng)度應(yīng)力集中的壓配合的截面C.等于剖應(yīng)力集中的影響，以及一個(gè)橫截面的最大載荷的載荷下所造成的最嚴(yán)重的，從點(diǎn)的應(yīng)力集中，但剖視圖對扭矩的影響，而在軸直徑大，這是沒有必要的強(qiáng)度檢查，這里的柄部的最大直徑，所以不需要截面C中，部分和顯然較少的控制必要的控制。從我們的第一章秀附錄3書籍與應(yīng)力集中系數(shù)比鍵槽小壓配合，從而軸段左側(cè)的控制比較正確即可。2截面的左側(cè)抗彎曲截面系數(shù) W0.10.161 412.5 抗扭距截面系數(shù) 0.20.2122 825 截面的右側(cè)的彎矩長度M為 90 834.04 截面上的扭矩長度為 1 410 990 截面上的彎曲應(yīng)力1.48 MPa截面上的扭轉(zhuǎn)應(yīng)力 11.48 MPa根據(jù)書上表格15-1可找到以下數(shù)據(jù)： 橫截面上由于軸肩而形成的理論應(yīng)力集中系數(shù)及，從書上我們找出附表格3-2可找到以下數(shù)據(jù)。因此，經(jīng)插值后找出數(shù)據(jù)為：1.9，1.29又從我們書本上附圖3-1找出軸的敏性系數(shù)是，0.88因此有效應(yīng)力集中系數(shù)從式子是：1.756從我們書本上附圖3-2的找到尺寸系數(shù)；從我們書本上附圖3-3找到系數(shù)。軸是按磨削加工的，根據(jù)書上的P44的圖3-4，得知軸的表面質(zhì)量系數(shù)為：軸是經(jīng)表面強(qiáng)化處理，就是，則從我們書本上找出式子3-12得出綜合系數(shù)是：又從我們書本上及3-2得出碳鋼的特性系數(shù)是，取，取再算安全系數(shù)值，從我們書本上找出式子得出：S65.66S16.9216.38S1.5 所以檢驗(yàn)合格。過盈配合處的，從我們書本上附表格3-8中用插值法求出，設(shè)得0.8，算式如下：3.24 0.83.242.59軸按磨削加工，從我們書本上附圖3-4找到表面質(zhì)量系數(shù)數(shù)據(jù)：軸為經(jīng)表面強(qiáng)化處理，就是，則從我們書本上找出式子3-12算出綜合系數(shù)為：3.332.68又從我們書本上及3-2找出碳鋼的特性系數(shù)數(shù)據(jù)：，設(shè)得，設(shè)得然后再算安全系數(shù)值，從我們書本上找出式子得出： 第5章 鍵的選擇與校核第5章 鍵的選擇與校核5.1 帶輪1上鍵的選擇與檢驗(yàn)5.1.1鍵的選擇鍵的選擇為A型的圓頭普通平鍵。材質(zhì)為45鋼，鍵的尺寸大小如下表：表5-1 帶輪1上鍵的尺寸軸鍵鍵槽半徑r公稱直徑d公稱尺寸bh寬度b深度公稱尺寸b極限偏差軸t轂一般鍵聯(lián)結(jié)軸N9轂9公稱尺寸極限偏差公稱尺寸極限偏差最小最大288780-0.0360.0184.0+0.2-03.3+0.2-00.250.45.1.2 鍵的檢驗(yàn)1.鍵的剪切強(qiáng)度檢驗(yàn)鍵在傳遞力的過程中，受力圖見下圖： 鍵的剪切受力圖鍵的剪切受力圖如上圖，鍵的許用剪切應(yīng)力是30 ，根據(jù)上圖得知，軸上受到的轉(zhuǎn)矩T為55 Nm ，根據(jù)鍵的剪切強(qiáng)度條件式子： 5-1 =10 M30 結(jié)構(gòu)合理2.鍵的擠壓強(qiáng)度檢驗(yàn)受力見下圖所示：鍵的許用擠壓應(yīng)力先選100 圖5-2 鍵擠壓受力圖根據(jù) =2000 N然后 8 符合要求5.2 帶輪2上鍵的選擇與檢驗(yàn)5.2.1 選擇的鍵根據(jù)帶輪1上鍵的選擇，可以看出鍵都選擇A型的圓頭普通平鍵。材質(zhì)為 45鋼，鍵的尺寸見下表：帶輪2上鍵的尺寸軸鍵鍵槽半徑r公稱直徑d公稱尺寸bh寬度b深度公稱尺寸b極限偏差軸t轂一般鍵聯(lián)結(jié)軸N9轂9公稱尺寸極限偏差公稱尺寸極限偏差最小最大35108100-0.0360.0184.0+0.203.3+0.200.250.405.2.2 鍵的檢驗(yàn)鍵的剪切受力圖如圖5-6所示，其中b=10毫米,L=50毫米.鍵的許用剪切應(yīng)力為=30 ，根據(jù)前面計(jì)算得知，軸上受到的轉(zhuǎn)矩T=110 Nm ，根據(jù)鍵的剪切強(qiáng)度條件： 其中D為帶輪輪轂直徑 5-4 =6.3 M30 符合要求檢驗(yàn)鍵的擠壓強(qiáng)度，它的受力如圖5-7，鍵的初選許用擠壓應(yīng)力=100 。根據(jù) =3150 牛然后根據(jù) 6.3 符合要求第6章 地輪和機(jī)架的設(shè)計(jì)6.1 地輪的設(shè)計(jì)地輪的最重要的作用是使插秧機(jī)在運(yùn)動(dòng)過程中平衡的支撐作用。該輪應(yīng)設(shè)計(jì)成具有良好的適應(yīng)性，并能確保在不平坦表面的情況下準(zhǔn)確地運(yùn)動(dòng)。您可以選擇鐵輪材料，結(jié)構(gòu)板狀腹釋放。設(shè)置在框架上的不同緊固位置可以適于工作深度。6.2 機(jī)架部分的設(shè)計(jì)插秧機(jī)單元性能的挖掘穩(wěn)定的深度，牽引單元，運(yùn)輸通過主要性能特征和相適應(yīng)的表面性能對懸浮液的裝置上的影響力。該設(shè)計(jì)使用植物機(jī)和懸掛器本體上的拖拉機(jī)的三點(diǎn)聯(lián)動(dòng)放置在一個(gè)空間機(jī)構(gòu)的一個(gè)三點(diǎn)懸置式機(jī)構(gòu)，可在垂直和水平四四桿連桿機(jī)構(gòu)中看到。兩個(gè)四連桿機(jī)構(gòu)在相反的效果的瞬時(shí)旋轉(zhuǎn)的各種力和力矩的相應(yīng)瞬時(shí)挖掘工作，以產(chǎn)生的趨勢都瞬時(shí)旋轉(zhuǎn)中心，以保持平衡。吊架部件和一般為矩形的管，因此，它可以節(jié)省的質(zhì)量和成本，而且結(jié)構(gòu)剛性和強(qiáng)度的要求。結(jié) 論經(jīng)過多月的努力，最終項(xiàng)目完成后，我發(fā)現(xiàn)寫論文是一個(gè)學(xué)習(xí)的過程。在大學(xué)四年里，我吸收了大量的機(jī)械技術(shù)和知識，通過畢業(yè)設(shè)計(jì)，讓我有了把的理論知識付諸實(shí)踐的機(jī)會(huì)。在今后的學(xué)習(xí)和生活，本次畢業(yè)設(shè)計(jì)的經(jīng)驗(yàn)將鞏固我在學(xué)校里學(xué)到的所有知識。通過這次畢業(yè)設(shè)計(jì)，我對機(jī)械傳動(dòng)部件的機(jī)電一體化系統(tǒng)設(shè)計(jì)和選用原則編制有一定的了解，機(jī)械傳動(dòng)部件和程序等方面的設(shè)計(jì)和計(jì)算原則有一定的了解。設(shè)計(jì)，我覺得最重要的是：不管什么情況，都要做出正確的態(tài)度，要善于學(xué)習(xí)，不斷地學(xué)習(xí)，有嚴(yán)格，認(rèn)真，仔細(xì)，不怕有困難，也創(chuàng)新精神。參考文獻(xiàn)1丁玉蘭人機(jī)工程學(xué)第三版 北京理工出版社, 20052 鄒慧君主編機(jī)械原理 北京高等教育出版社19993 申永勝主編機(jī)械原理教程 北京、清華大學(xué)出版社19994 張偉社主編機(jī)械原理 西北工業(yè)大學(xué)出版社20015 鄒慧君主編機(jī)械原理課程設(shè)計(jì)手冊 高等教育出版社19986 趙松年主編現(xiàn)代機(jī)械創(chuàng)新產(chǎn)品分析與設(shè)計(jì) 20007 楊家軍主編機(jī)械系統(tǒng)創(chuàng)新設(shè)計(jì) 華中理工大學(xué)出版社20008 張春林主編機(jī)械創(chuàng)新設(shè)計(jì) 機(jī)械工業(yè)出版社19999 機(jī)械設(shè)計(jì)手冊編委會(huì)機(jī)械設(shè)計(jì)手冊新版2，3卷 機(jī)械工業(yè)出版社，200410卜炎主編機(jī)械傳動(dòng)裝置設(shè)計(jì)手冊上冊 機(jī)械工業(yè)出版社1999 11何燦群人體工學(xué)與藝術(shù)設(shè)計(jì) 長沙湖南大學(xué)出版社，200412阮寶湘/郡祥華工業(yè)設(shè)計(jì)人體工程 北京機(jī)械工業(yè)出版社 2005.05 13 王三明主編機(jī)械原理與設(shè)計(jì)課程設(shè)計(jì) 北京機(jī)械工業(yè)出版社，200514.閆衛(wèi)工業(yè)產(chǎn)品造型設(shè)計(jì)程序與實(shí)例.機(jī)械工業(yè)出版社，2003.2，第一版15. 沈法，王慶斌，楊足，丁熊計(jì)算機(jī)輔助產(chǎn)品造型設(shè)計(jì)表現(xiàn)技法.人民郵電出版社，2002.9，第一版16.張展，王虹產(chǎn)品設(shè)計(jì).上海人民美術(shù)出版社，2002.1，第一版17.王玉林，蘇全忠，曲遠(yuǎn)方產(chǎn)品造型設(shè)計(jì)材料與工藝.天津大學(xué)出版社，1994.12，第一版18.程能林，產(chǎn)品造型設(shè)計(jì)手冊.機(jī)械工業(yè)出版社，1994.8，第一版19.朱序璋.人機(jī)工程學(xué).西安:西安電子科技大學(xué)出版社.1999年11月致 謝我不會(huì)忘記這難忘的幾個(gè)月，這其中有我難忘的回憶。我在書的海洋里找信息的日子，最難忘的是每次激動(dòng)和興奮地找到有用信息，記得最快樂的心情當(dāng)每一步實(shí)現(xiàn)小想法；趕論文我甚至寫到深夜，但每一個(gè)字的敲打，沒有疲勞，我的心充滿了歡樂。從我收集的信息，掌握了許多專業(yè)上的知識，也發(fā)現(xiàn)了自己仍有很多不足之處，所以我已經(jīng)學(xué)會(huì)知識鞏固和改善。我認(rèn)為這是一個(gè)鍛煉自己的機(jī)會(huì),能夠讓自己看到不足，讓自己能力真正的提升,而且在我未來的學(xué)習(xí)和工作有很大的幫助。在這里也要感謝我的指導(dǎo)老師毛老師的指導(dǎo)和照顧,付出了很多汗水以及辛勤工作。嚴(yán)格的審核我每一階段的任務(wù)。充滿責(zé)任感的老師,讓我我不僅學(xué)會(huì)了一個(gè)可靠的，廣泛的專業(yè)知識,還學(xué)會(huì)了生活中的真理。在這里我想向我的導(dǎo)師獻(xiàn)上我最真誠的感謝和深深的敬意。畢 業(yè) 設(shè) 計(jì)（論 文）任 務(wù) 書設(shè)計(jì)（論文）題目：手扶式插秧機(jī)設(shè)計(jì) 學(xué)生姓名： 學(xué) 號： 專 業(yè)： 所在學(xué)院： 指導(dǎo)教師： 職 稱： 20xx年 2月 27日任務(wù)書填寫要求1畢業(yè)設(shè)計(jì)（論文）任務(wù)書由指導(dǎo)教師根據(jù)各課題的具體情況填寫，經(jīng)學(xué)生所在專業(yè)的負(fù)責(zé)人審查、系（院）領(lǐng)導(dǎo)簽字后生效。此任務(wù)書應(yīng)在畢業(yè)設(shè)計(jì)（論文）開始前一周內(nèi)填好并發(fā)給學(xué)生。2任務(wù)書內(nèi)容必須用黑墨水筆工整書寫，不得涂改或潦草書寫；或者按教務(wù)處統(tǒng)一設(shè)計(jì)的電子文檔標(biāo)準(zhǔn)格式（可從教務(wù)處網(wǎng)頁上下載）打印，要求正文小4號宋體，1.5倍行距，禁止打印在其它紙上剪貼。3任務(wù)書內(nèi)填寫的內(nèi)容，必須和學(xué)生畢業(yè)設(shè)計(jì)（論文）完成的情況相一致，若有變更，應(yīng)當(dāng)經(jīng)過所在專業(yè)及系（院）主管領(lǐng)導(dǎo)審批后方可重新填寫。4任務(wù)書內(nèi)有關(guān)“學(xué)院”、“專業(yè)”等名稱的填寫，應(yīng)寫中文全稱，不能寫數(shù)字代碼。學(xué)生的“學(xué)號”要寫全號，不能只寫最后2位或1位數(shù)字。 5任務(wù)書內(nèi)“主要參考文獻(xiàn)”的填寫，應(yīng)按照金陵科技學(xué)院本科畢業(yè)設(shè)計(jì)（論文）撰寫規(guī)范的要求書寫。6有關(guān)年月日等日期的填寫，應(yīng)當(dāng)按照國標(biāo)GB/T 740894數(shù)據(jù)元和交換格式、信息交換、日期和時(shí)間表示法規(guī)定的要求，一律用阿拉伯?dāng)?shù)字書寫。如“2002年4月2日”或“2002-04-02”。畢 業(yè) 設(shè) 計(jì)（論 文）任 務(wù) 書1本畢業(yè)設(shè)計(jì)（論文）課題應(yīng)達(dá)到的目的： 通過畢業(yè)設(shè)計(jì)初步掌握機(jī)械設(shè)計(jì)的一般方法和步驟。同時(shí)提高分析解決問題的能力；提高綜合運(yùn)用所學(xué)知識的能力。2本畢業(yè)設(shè)計(jì)（論文）課題任務(wù)的內(nèi)容和要求（包括原始數(shù)據(jù)、技術(shù)要求、工作要求等）： 設(shè)計(jì)要求：1、插秧效果好、效率高、省力。 2、有一定的創(chuàng)新，價(jià)廉物美。 3、結(jié)構(gòu)合理、耐用。畢 業(yè) 設(shè) 計(jì)（論 文）任 務(wù) 書3對本畢業(yè)設(shè)計(jì)（論文）課題成果的要求包括圖表、實(shí)物等硬件要求： 一、 設(shè)計(jì)總裝配圖及主要零件圖二、 設(shè)計(jì)說明書一份三、 英文資料翻譯（3000字以上）4主要參考文獻(xiàn)： 1.詹友剛Creo2.0機(jī)械設(shè)計(jì)教程機(jī)械工業(yè)出版社（2013.5）2.陳立德機(jī)械設(shè)計(jì)制造技術(shù)基礎(chǔ)高等教育出版社（2013.11）3.姜繼海宋錦春等液壓與氣壓傳動(dòng)高等教育出版社（2013.12）4.宇海英劉占軍沖壓工藝與模具設(shè)計(jì)電子工業(yè)出版社（2011.8）5.林承全沖壓模具課程設(shè)計(jì)化學(xué)工業(yè)出版社（2008.1）6.齊曉杰塑料成型工藝與模具設(shè)計(jì)機(jī)械工業(yè)出版社（2012.5）7.劉晉春白基成特種加工機(jī)械工業(yè)出版社（2008.3）8.于永泗、齊民.機(jī)械工程材料.8版.大連：大連理工大學(xué)出版社.2010.9.哈爾濱工業(yè)大學(xué)理論力學(xué)教研室理論力學(xué)（1）高等教育出版社（2009.7）10.蔣曉、沈培玉、苗青.AutoCAD2008中文版機(jī)械設(shè)計(jì)標(biāo)準(zhǔn)實(shí)例教程.北京：清華大學(xué)出版社.2008.11.中國農(nóng)業(yè)機(jī)械化科學(xué)研究院.農(nóng)業(yè)機(jī)械設(shè)計(jì)手冊（上）S.北京：中國農(nóng)業(yè)科學(xué)技術(shù)出版社12.朱龍根.簡明機(jī)械零件設(shè)計(jì)手冊（第二版）.機(jī)械工業(yè)出版社13.李寶筏.農(nóng)業(yè)機(jī)械學(xué).北京.中國農(nóng)業(yè)出版社.2003年14.范欽珊殷雅俊材料力學(xué)（第2版）清華大學(xué)出版社（2008.7）畢 業(yè) 設(shè) 計(jì)（論 文）任 務(wù) 書5本畢業(yè)設(shè)計(jì)（論文）課題工作進(jìn)度計(jì)劃：20xx.12.16-20xx.1.10 領(lǐng)任務(wù)書、開題20xx.2.25-2.16.3.9 畢業(yè)實(shí)習(xí)調(diào)研，完成開題報(bào)告、中英文翻譯、論文大綱20xx.3.19-20xx.4.25 提交論文草稿，4月中旬中期檢查20xx.4.26-20xx.5.6 提交論文定稿20xx.5.6-20xx.5.13 準(zhǔn)備答辯20xx.5.13-20xx.5.26 答辯，成績評定，修改完成最終稿 所在專業(yè)審查意見：通過負(fù)責(zé)人： 年 月 日 畢 業(yè) 設(shè) 計(jì)（論 文）外 文 參 考 資 料 及 譯 文譯文題目： MECHANISMS AND MACHINE THEORY 機(jī)構(gòu)和機(jī)器原理 學(xué)生姓名： 學(xué) 號： 專 業(yè)： 所在學(xué)院： 指導(dǎo)教師： 職 稱： 20xx年 2月 27日 外文資料MECHANISMS AND MACHINE THEORY1.Introduction to Mechanism：The function of a mechanism is to transmit or transform motion from one rigid body to another as part of the action of a machine. There are three types of common mechanical devices that can be used as basic elements of a mechanism.1、Gear system, in which toothed members in contact transmit motion between rotating shafts. 2、Cam system, where a uniform motion of an input member is converted into a nonuniform motion of the output member. 3、Plane and spatial linkages are also useful in creating mechanical motions for a point or rigid body. A kinematic chain is a system of links, that is, rigid bodies , which are either jointed together or are in contact with one another in a manner that permits them to move relative to one another. If one of the links is fixed and the movement of any other link to a new position will cause each of the other links to move to definite predictable position, the system is a constrained kinematic chain. If one of the links is held fixed and the movement of any other link to a new position will not cause each of the other links to move to a definite predictable position then the system is an unconstrained kinematic chain,A mechanism or linkage is a constrained kinematic chain, and is a mechanical device that has the purpose of transferring motion and/or force from a source to an output. A linkage consists of links (or bars), generally considered rigid, which are connected by joints, such as pin Cor revolute) or prismatic joints, to form open or closed chains (or loops). Such kinematic chains, with at least one link fixed, become mechanisms if at least two other links remain mobility, or structures if no mobility remains. In other words, a mechanism permits relative motion between its rigid links; a structure does not. Since linkages make simple mechanisms and can be designed to perform complex tasks, such as nonlinear motion and force transmission they will receive much attention in mechanism study.Mechanisms are used in a great variety of machines and devices. The simplest closed-loop linkage is the four-bar linkage, which has three moving links (plus one fixed link) and four pin joints. The link that is connected to the power source or prime mover and has one moving pivot and one ground pivot is called the input link. The output link connects another moving pivot to another ground pivot. The coupler or floating link connected the two moving pivots, thereby coupling the input to the output link.The four-bar linkage has some special configurations created by making one or more links infinite in length. The slider-crank (or crank and slider) mechanism is a four-bar chain with a slider replacing an infinitely long output link. The internal combustion engine is built based on this mechanism. Other forms of four-link mechanisms exist in which a slider is guided on a moving link rather than on a fixed link. These are called inversions of the slider-crank, produced when another link (the crank, coupler, or slider) is fixed link.Although the four-bar linkage and slider-crank mechanism are very useful and found in thousands of applications, we can see that these linkages have limited performance level. Linkages with more members are often used in more demanding circumstances. However it is often difficult to visualize the movement of a multiloop linkage, especially when other components appear in the same diagram. The first step in the motion analyses of more complicated mechanisms is to sketch the equivalent kinematic or skeleton diagram. The skeleton diagram serves a purpose similar to that of the electrical schematic or circuit diagram .Organization movement analysis second step: Draws a graphic chart, is must determine the organization the number of degrees of freedom. Based on degree of freedom, but Italy refers needs certain independent inputs the movement number, by determined organization all components are opposite in the ground position. The people have thousands of different types conceivably the link motion gear. You may imagine a bag containing massive link motion gear the component: Two pole groups, three pole groups, four pole groups and so on, as well as components, rotation, motion, cam follower, gear, tooth chain, chain wheel, leather belt, belt pulley and so on. (Sphere movement, screw vice-as well as the permission three dimensional relative motion other connections not yet includes, here, discusses in parallel planes merely plane motion). Moreover you conceivable put these components various types link motion gear possibility which forms in the same place. How exists helps the people to control forms these organizations the rule? In fact, the majority organization duty is requests a sole input to transmit to a sole output. Therefore the single degree of freedom organization uses most one kind of organization type. For example, namely may see by the intuition: Four pole organizations are a single degree of freedom link motion gear. The picture motion diagram and the determination organization degree of freedom process, is the movement analysis and the synthesis process first stage. In the movement analysis, adds on its characteristic according to the organization geometry shape which possibly knew (for example input angle, speed, angle acceleration and so on) studies the determination concrete organization. On the other hand, the movement synthesis is designs an organization to complete the duty process which an institute requests. In this, chooses the new organization the type and the size is a movement synthesis part. Conceives the relative motion ability, can guess the reason that designs an organization the reason and makes the improvement to a concrete design ability is like this a successful organization scientists symbol. Although these abilities come from the congenital creativity, however more is because has grasped the technology which enhances from the practice. 1.1The movement analysis： simple one of most useful organizations is four pole organizations. In on following elaboration majority of content centralism discussion link motion gear, but this procedure is also suitable for the more complex link motion gear. We already knew four pole organizations have a degree of freedom. About four pole organizations, has the useful more contents which must know? Indeed is some! These pull the Xiao husband criterion including the standard, the transformation concept, the blind spot position (divergence point), branch office, transmission angle, with theirs movement characteristic, including position, speed and acceleration. Four pole organizations may have one kind of being called as crank rocker organization form, one kind of double rocking lever organization, one kind of double crank (tension bar) does the organization, which one form send in is called as the organization, is decided in two pole movement scopes which (fixed component) connects with the rack. The crank rocker organization input component, the crank may revolve through 360 and the continuous rotation, but outputs the component to make the undulation merely (i.e. swing member). As an exceptional case, in the parallel four pole organization, inputs the pole the length to be equal to outputs the pole the length, the go-between length and the fixed link (rack) length, also is equal. Its input and the output all may make the complete alternation rotation or transform the being called as antiparallel quadrangle organization the overlapping structure. The standard pulls the Xiao husband criterion (theorem) to indicate that,If in four pole organizations, between two poles can do willfully relatively rotates continuously, that, its longest pole length is smaller than sum of with the shortest pole length or is equal to sum of the other two pole length.Should pay attention: The same four pole organization, may have the different form, which pole is this decided in was stipulated (i.e. makes fixed link) as the rack. The movement transformation process is in the fixed organization transmission chain different member has the different organization rate process. Besides has about the component rotation scope knowledge, but also must have how causes the organization before the manufacture on energy “the revolution” the good measure, that will be very useful. Hardenbergh (Hartenberg) speaks of: “The revolution” is terminology, its significance passes to outputs the component the movement validity. It meant the revolution is steady, in which can in output in the component to have a strength or the torque biggest force component is effective. Not only although the final output strength or the torque are the connecting rod geometric figure functions, moreover also is generally the power or the force of inertia result, that is frequently big to like static strength several times. In order to analyze the idling or in order to easy to obtain how can cause any organization “the revolution” the index, the transmission angle concept is extremely useful. In organization movement period, the transmission angle value is changing. The transmission angle 0 may occur in the special position. Will output the pole but in this special position the movement with not to exert inputs on the pole the strength many to have nothing to do with greatly. In fact, as a result of the movement vice-friction influence, the general basis practical experience, with the transmission angle planning board which is bigger than the rating. The weight link motion gear transmission movement ability matrix foundation definition already studied. A determining factor value (it includes regarding some assigns organization graph, position output movement variable to input variable derivative) is a this link motion gear in concrete position mobility criterion. If the organization has a degree of freedom (e.g. four pole organizations), then stipulated a location parameter, if the input angle, completely determined this organization stops position (neglect branch offices possibility). We may study one about four pole organization component absolute angular position analysis expression. When analyzes certain positions and (or) certain different organization time, this will be must be much more useful than the geometric figure analysis program, because this expression will cause the automated computation easy to program. The realization organization speed analysis relative velocity law is the speed polygon is one of several effective methods. This end (goes against) the spot to represent on the organization all spots, has the zero speed. From this the line which stipples respectively to the speed polygon in is representing the absolute speed which this organization photograph well should select respectively. In a line connection speed polygon random two points represents is taking on this organization two corresponding spot relative velocity. Other method is the instantaneous center law, namely the instantaneous center law, this method is extremely useful moreover is frequently when the complex link motion gear analysis quick method. The instantaneous center is a spot, this spot in that flash, on between the organization two components does not have the relative motion. In order to discover known organization certain instantaneous centers the position, Kennedy the (Kennedy) three center theories extremely are useful. It is said that,Each other relative motion three object three instantaneous centers are surely in a straight line. The organization various components acceleration is makes one be interested, because it affects the force of inertia, subsequently affects the machine part the stress, the bearing load, the vibration and the noise. Because the final goal is the machine and the organization force of inertia analysis, the all acceleration various components all should the disposable picture - - in the organization fixed component inertial coordinate system express in the identical coordinate system. Should pay attention: Is opposite in rotates on the vice-rotation rigid body an acceleration component usually to have two fixedly. A force component direction cuts in this path, its direction is same with this object angle acceleration direction, and is called the tangential acceleration. Its existence is completely because the angular speed rate of change causes. Another component, always aims at the object the center of rotation, is called the standard the centripetal acceleration, because this component the velocity vector direction has the change to exist. The movement comprehensiveGanization is forms many mechanisms the basic geometry structural units, these mechanisms including automatic packaging, printer, mechanical toy, textile machinery and other machineries and so on. The typical organization must design causes the movement which the rigid component relative datum component produces hoped. The organization movement design is the movement synthesis, first step frequently designs the entire machine first. When consideration stress, must ask dynamics aspect question, the bearing load, the stress, the lubrication and so on the similar question, but the major problem is the machine structure question. The movement scientist defines the kinematics as “the development facility movement and the foundation organization method”. This definition first part involves the kinematic analysis. The known organization, its constitution state of motion determined by the kinematic analysis. The narration movement analysis duty contains the organization between the main dimension, the component links mutually with the input movement technical characteristic or the actuation method. The goal is must discover the displacement, the speed, the acceleration, the impact or the beat (two step accelerations), with various components higher order acceleration which possibly occurs as well as describes the diameter mark and the movement which realizes by certain components. The definition second part of available following two aspect explained ：1. research produces with the aid of the organization assigns the movement the method. 2. research construction to be able to produce assigns the motion the method, but in two plans, the movement is assigns the organization is the foundation. This is the movement synthesis essence. Such movement synthesis involves to for assigns the performance the organization system design. The movement synthesis aspect may sum up as following two kinds: 1. types are comprehensive. The stipulation requests the performance, how is one kind of type organization appropriate? (Tooth gear train, link motion gear? Cam gear?)How many components but should the organization have? How many degrees of freedom needs? How outline structure is hoped? . About the member number and the degree of freedom consideration was usually considered is in the type synthesis is been called as for a quantity synthesis branch domain. 2. sizes are comprehensive. The movement synthesis second predominant type is the best method which determined through the goal law. The size synthesis attempts to determine the organization the important size and the starting position, this organization is conceives beforehand for the realization stipulation duty and the anticipated performance. Of the so-called important size meanings are refer about two poles, three poles and so on between the length or the pole are away from, angle between number of articles and spool thread, cam contour size, cam follower diameter, eccentricity, gear quota and so on. Expected the organization type possibly is the crank slide organization, four pole organizations, the tape reel from the moving parts cam gear, but or is non-has some kind of structure shape more complex link motion gear because by the analysis situs method which the inferior analytic method determined. Is comprehensive regarding the movement, in the convention has three duties: Function production, path production and movement production. Inputs and outputs the component in the function production organization the rotation or the migration must be the interdependence. Regarding arbitrary function y=f(x), a movement synthesis duty possibly is designs a link motion gear to cause the input and the output establishes the relations in order to cause in the xoxxn-1 scope to input according to x movement, but outputs according to the y=f(x) movement. In the input and in the output gyroscopic motion situation, the corner phi and phi respectively is x and the y linear simulation. When inputs rotates to an independence x value, in one “black box” in the organization, causes to output which the component to change to corresponds in the value which by function y=f(x) decided. This may consider is the mechanical analogy computer simple situation. Each kind of different organization all may contain in this “the black box” in, however produces regarding the arbitrary function non-error, four pole organizations are helpless, possibly matches merely in the limited precision with it. It widely uses in the industry, because four pole organizations in the construction and the service all are simple. In the path production organization, in “floats the walking beam” on a spot to have to draw one to be opposite in a fixed coordinate system determination path. If this path spot is both must and have to be related with the time correlation with the position, this duty is called it the predetermined cyclical path production. A path production organization example is the design throws the baseball or the tennis four pole organization. In this case, will select P the path will be this: Picks a ball in the predetermined position, and transmits in the predetermined time cycle along the predetermined diameter mark the ball, can achieve the appropriate speed and the direction. In the mechanism design has many situations, both must guide the rigid body in these situations through a series of stipulations, the independent position which limits, and must limit in the reduction when independent position number, to the vehicle speed and (or) the acceleration restrains, that is necessary. Movement production or rigid body guiding organization request: A complete object must guide passes a predetermined movement sequence. Took the object which guides usually is “the fluctuation component” not only a part, that is the target point P path, also is and inserts in this object through this spot the line rotation. For example, this possibly represents in the automated machinery a carrier, but that has a predetermined path in a carrier on spot this carrier also to have a predetermined angle position. The predetermined way charger cableway bucket movement is the movement production organization another example. The cableway bucket end path has the limit. Because its port must realize the excavation path, is following close on the path which must realize promotes and falls in torrents. The cableway bucket angle position to guaranteed fights the material to fall in torrents from the correct position similarly is (but actually) important.The cam and the gearcam gear is changes one kind of movement Cheng Ling one kind of movement the convenience installment. This kind of machine part has the curved surface or the trough surface, this curved surface or the trough surface with passes to from the moving parts appropriate match merge the movement from the moving parts. The cam movement (usually is rotation) is transmitted for does fr