王麗紅，張 娜，坎 雜，李成松，朱興亮

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用于番茄果秧分離的多組非圓行星輪系振動(dòng)發(fā)生器設(shè)計(jì)

王麗紅1，張 娜1，坎 雜1※，李成松1，朱興亮2

（1. 石河子大學(xué)機(jī)械電氣工程學(xué)院，石河子 832000；2. 新疆農(nóng)業(yè)大學(xué)機(jī)械交通學(xué)院，烏魯木齊 830052）

針對(duì)現(xiàn)有用于番茄果秧分離的雙偏心塊振動(dòng)發(fā)生器運(yùn)動(dòng)參數(shù)易受載荷影響、分離滾筒易堵塞以及前期研究的單組非圓行星輪系振動(dòng)發(fā)生器傳動(dòng)部件載荷不均衡等問題，設(shè)計(jì)了一種三組非圓行星輪系振動(dòng)發(fā)生器。對(duì)雙偏心塊式振動(dòng)發(fā)生器驅(qū)動(dòng)下分離滾筒的運(yùn)動(dòng)進(jìn)行了分析，獲取了分離滾筒擬合角位移、角速度曲線，并將其作為三組非圓行星輪系振動(dòng)發(fā)生器的輸出目標(biāo)曲線。通過建立非圓齒輪傳動(dòng)比方程以及節(jié)曲線方程，確定了三組非圓行星輪系振動(dòng)發(fā)生器非圓齒輪的基本參數(shù)。搭建了分離滾筒運(yùn)動(dòng)測(cè)試試驗(yàn)臺(tái)，利用高速攝像系統(tǒng)在振動(dòng)發(fā)生器輸入轉(zhuǎn)速為111 r/min，高速攝像系統(tǒng)幀率為800 幀/s的參數(shù)條件下獲得實(shí)測(cè)角位移、角速度，通過MATLAB軟件獲取了分離滾筒在三組非圓行星輪系振動(dòng)發(fā)生器驅(qū)動(dòng)下的角位移和角速度擬合曲線，并分別與對(duì)應(yīng)的仿真曲線和目標(biāo)曲線進(jìn)行對(duì)比分析，結(jié)果表明：試驗(yàn)角位移和角速度曲線與仿真及目標(biāo)曲線基本吻合。驗(yàn)證了非圓行星輪系振動(dòng)發(fā)生器設(shè)計(jì)的合理性。通過ADAMS獲取了三組和單組非圓行星輪系振動(dòng)發(fā)生器的齒面接觸力，通過對(duì)比分析，發(fā)現(xiàn)單組非圓行星輪系振動(dòng)發(fā)生器的齒面接觸力變化范圍為0~200 000 N，三組非圓行星輪系振動(dòng)發(fā)生器齒面接觸力為0～125 N，驗(yàn)證了三組相對(duì)于單組非圓行星輪系振動(dòng)發(fā)生器更加均衡的特性。該研究為多組非圓行星輪系番茄果秧分離振動(dòng)發(fā)生器的開發(fā)提供參考。

振動(dòng)；分離；齒輪；收獲機(jī)；非圓齒輪；行星輪系；齒輪節(jié)曲線

0 引 言

新疆獨(dú)特的水土和光熱條件適宜優(yōu)質(zhì)番茄的生長(zhǎng)，已成為世界第二大加工番茄種植區(qū)[1-3]。近年來(lái)，新疆番茄機(jī)械化采收技術(shù)大面積推廣，果秧分離振動(dòng)發(fā)生器作為番茄果秧收獲機(jī)中的重要部件之一，其傳動(dòng)效果直接影響收獲機(jī)的工作性能[4]。

目前，果秧分離振動(dòng)發(fā)生器主要分為連桿式、凸輪盤式、鏈帶式和偏心塊式4種[5-6]，國(guó)內(nèi)外廣泛采用雙偏心塊式振動(dòng)發(fā)生器[7-13]，通過兩個(gè)對(duì)稱偏心塊旋轉(zhuǎn)產(chǎn)生變向力偶，從而驅(qū)動(dòng)分離滾筒進(jìn)行變速變向回轉(zhuǎn)運(yùn)動(dòng)，實(shí)現(xiàn)果秧分離。

雙偏心塊式振動(dòng)發(fā)生器具有果實(shí)分離效率高、消耗功率低等優(yōu)點(diǎn)，技術(shù)相對(duì)比較成熟，但當(dāng)收獲機(jī)喂入量不均勻時(shí)，依據(jù)慣性原理實(shí)現(xiàn)運(yùn)動(dòng)需求的雙偏心塊式振動(dòng)發(fā)生器輸出的運(yùn)動(dòng)會(huì)由于負(fù)載的變化而變化，致使果秧分離效果受到影響，甚至產(chǎn)生堵塞[14]。

非圓齒輪傳動(dòng)具有傳動(dòng)平穩(wěn)、結(jié)構(gòu)緊湊、受載荷影響小的特點(diǎn)，能夠?qū)崿F(xiàn)變速變向的復(fù)雜運(yùn)動(dòng)[15]。國(guó)內(nèi)外非圓齒輪傳動(dòng)技術(shù)廣泛應(yīng)用在造紙、液壓馬達(dá)、插秧機(jī)、果品收獲和紡織機(jī)械等領(lǐng)域[16-22]。項(xiàng)目組[23]前期提出將非圓齒輪行星輪系應(yīng)用到番茄果秧振動(dòng)發(fā)生器的結(jié)構(gòu)設(shè)計(jì)當(dāng)中，通過全凸無(wú)內(nèi)凹的節(jié)曲線獲得的單組非圓齒輪行星輪系振動(dòng)發(fā)生器能夠?qū)崿F(xiàn)變速變向回轉(zhuǎn)運(yùn)動(dòng)，但輪系中傳動(dòng)部件載荷不均衡[24]。文獻(xiàn)表明在非圓輪系傳動(dòng)過程中，多組行星輪系相對(duì)單組而言傳動(dòng)部件受力更均衡，行星齒輪負(fù)荷更小[24-25]。鑒于此，本文提出采用W-W型三組非圓行星輪系的番茄果秧分離振動(dòng)發(fā)生器，驅(qū)動(dòng)分離滾筒實(shí)現(xiàn)變速變向回轉(zhuǎn)運(yùn)動(dòng)。

本文把通過雙偏心塊式振動(dòng)發(fā)生器獲得的分離滾筒運(yùn)動(dòng)曲線作為目標(biāo)曲線，通過具有凹性和全凸無(wú)內(nèi)凹的2種節(jié)曲線獲取非圓齒輪齒廓，結(jié)合SolidWorks三維建模并利用ADAMS對(duì)三組非圓行星輪系振動(dòng)發(fā)生器進(jìn)行仿真分析，試制三組非圓行星輪系番茄果秧分離振動(dòng)發(fā)生器物理樣機(jī)，替換雙偏心塊式振動(dòng)發(fā)生器進(jìn)行試驗(yàn)，通過CPL-MS70K型高速攝像系統(tǒng)拍攝分離滾筒的運(yùn)動(dòng)過程并進(jìn)行數(shù)據(jù)分析，得到分離滾筒的運(yùn)動(dòng)實(shí)測(cè)散點(diǎn)圖，將其擬合后與仿真曲線、目標(biāo)曲線進(jìn)行對(duì)比，以驗(yàn)證機(jī)構(gòu)設(shè)計(jì)的合理性。

1 三組非圓行星輪系振動(dòng)發(fā)生器的結(jié)構(gòu)及工作原理

三組非圓行星輪系番茄果秧分離振動(dòng)發(fā)生器主要由輸入軸總成1、系桿總成2、殼體3和輸出軸總成4組成（如圖1a），通過兩端的軸承座與機(jī)架連接，殼體通過螺栓與機(jī)架固定。

如圖1所示，系桿總成包括輸入系桿、系桿軸和輸出系桿3部分，兩系桿結(jié)構(gòu)對(duì)稱。輸入軸與輸入系桿通過鍵固結(jié)，輸出軸通過軸承分別與輸入軸及輸出系桿連接。系桿軸通過軸承與系桿總成連接。輸入系桿左側(cè)的定非圓齒輪與機(jī)架固接，三個(gè)均勻分布的行星非圓齒輪與定非圓齒輪外嚙合，并通過鍵與系桿軸固結(jié)。輸出系桿右側(cè)的輸出軸齒輪通過鍵與輸出軸連接，與之嚙合的三個(gè)行星圓齒輪通過鍵與系桿軸固結(jié)。當(dāng)動(dòng)力通過輸入軸帶動(dòng)系桿轉(zhuǎn)動(dòng)時(shí)，三個(gè)行星非圓齒輪和行星圓齒輪分別繞定非圓齒輪和輸出軸齒輪嚙合公轉(zhuǎn)，同時(shí)繞系桿軸自轉(zhuǎn)，由輸出軸輸出需要的傳動(dòng)比。

1. 輸入軸總成 2. 系桿總成 3. 殼體 4. 輸出軸總成 5. 輸入軸 6. 軸承座 7. 同步帶輪 8. 定非圓齒輪 9. 行星非圓齒輪 10. 輸入系桿 11. 輸出系桿 12. 行星圓齒輪 13. 輸出軸齒輪 14. 輸出軸 15. 法蘭

工作時(shí)動(dòng)力由同步帶輪輸入，經(jīng)輸入軸帶動(dòng)輸入系桿和輸出系桿同步轉(zhuǎn)動(dòng)，系桿軸上的行星非圓齒輪與定非圓齒輪嚙合轉(zhuǎn)動(dòng)，輸出軸齒輪與系桿軸上行星圓齒輪嚙合轉(zhuǎn)動(dòng)。通過輪系及非圓齒輪嚙合的瞬時(shí)傳動(dòng)比變化，使輸出軸獲得變速變向回轉(zhuǎn)運(yùn)動(dòng)，從而使得與輸出軸固結(jié)的法蘭帶動(dòng)分離滾筒做變速變向回轉(zhuǎn)運(yùn)動(dòng)。

2 三組非圓行星輪系振動(dòng)發(fā)生器運(yùn)動(dòng)模型的建立

非圓齒輪作為非圓行星輪系振動(dòng)發(fā)生器的重要零部件，直接影響輪系輸出運(yùn)動(dòng)。為確定非圓輪系的傳動(dòng)要求，本文利用現(xiàn)有的雙偏心塊式振動(dòng)發(fā)生器進(jìn)行運(yùn)動(dòng)需求獲取，在輸入、輸出角位移分段函數(shù)的基礎(chǔ)上，結(jié)合非圓齒輪角位移處處連續(xù)、可導(dǎo)的特性，擬合修正后獲取三組非圓齒輪傳動(dòng)比方程及節(jié)曲線方程。

2.1 振動(dòng)發(fā)生器輸出目標(biāo)曲線

項(xiàng)目組[26]通過高速攝像系統(tǒng)對(duì)采用雙偏心塊式振動(dòng)發(fā)生器時(shí)分離滾筒的運(yùn)動(dòng)進(jìn)行分析，獲得了分離滾筒角位移和角速度散點(diǎn)圖。利用MATLAB對(duì)分離滾筒的角位移、角速度散點(diǎn)圖進(jìn)行擬合，獲取圖2所示的擬合角位移、角速度曲線，角位移擬合曲線的擬合度2為0.923（≥0.85），角速度擬合曲線的擬合度2為0.879（≥0.85），將角位移和角速度擬合曲線作為三組非圓行星輪系振動(dòng)發(fā)生器的輸出目標(biāo)曲線。

圖2 雙偏心塊振動(dòng)發(fā)生器驅(qū)動(dòng)下分離滾筒的擬合角速度、角位移曲線（目標(biāo)曲線）

2.2 非圓齒輪傳動(dòng)比方程

當(dāng)偏心塊式振動(dòng)發(fā)生器正常工作時(shí)，利用高速攝像系統(tǒng)拍攝分離滾筒上的運(yùn)動(dòng)情況，獲得其角位移散點(diǎn)圖，結(jié)合MATLAB軟件對(duì)分離滾筒的角位移散點(diǎn)圖進(jìn)行分析，獲得分離滾筒（即振動(dòng)發(fā)生器輸出軸）角位移擬合函數(shù)如式（1）。

（2）

2.3 非圓齒輪節(jié)曲線方程

結(jié)合三組非圓行星輪系結(jié)構(gòu)設(shè)計(jì)，輸入輸出軸的傳動(dòng)比4H可轉(zhuǎn)化為圖3a中定非圓齒輪1和輸出軸齒輪4之間的瞬時(shí)相對(duì)運(yùn)動(dòng)傳動(dòng)比，表達(dá)式為：

式中1、2、3、4分別為定非圓齒輪、行星非圓齒輪、行星圓齒輪、輸出軸齒輪的極徑，1、2分別對(duì)應(yīng)如圖3a中1、2的距離并隨著圖3a兩非圓齒輪的轉(zhuǎn)動(dòng)而變化；3、4分別對(duì)應(yīng)如圖3b中3、4的距離，由于行星圓齒輪、輸出軸齒輪均為圓齒輪傳動(dòng)，所以3、4距離保持不變。行星非圓齒輪與定非圓齒輪嚙合節(jié)曲線如圖3a所示，行星圓齒輪與輸出軸齒輪嚙合節(jié)曲線如圖3b所示。

注：為兩齒輪的中心距，mm；點(diǎn)是齒輪傳動(dòng)的節(jié)點(diǎn)；1、2、3、4分別為定非圓齒輪、行星非圓齒輪、行星圓齒輪、輸出軸齒輪的極徑，mm

Note:is the center distance between the two gear, mm;is the pitch point of gear transmission;1,2,3and4are the polar radius of fixed non-circular gear, planetary non-circular gear, planetary gear and output shaft gear, respectively, mm.

圖3 齒輪嚙合節(jié)曲線示意圖

Fig.3 Diagram of gears meshing pitch curve

又有

（5）

將式（2）、（4）分別帶入（5）可得出定非圓齒輪與行星非圓齒輪的節(jié)曲線方程表示為：

（7）

（9）

（11）

按照振動(dòng)發(fā)生器空間結(jié)構(gòu)要求，初定非圓齒輪m= 2.5 mm，定非圓齒輪齒數(shù)1=60，行星非圓齒輪齒數(shù)2=60，進(jìn)而根據(jù)弧長(zhǎng)公式=π，求得非圓齒輪中心距=143 mm，繪制三組非圓齒輪的齒廓如圖4所示。此時(shí)，圓齒輪模數(shù)=2.39 mm，行星圓齒輪齒數(shù)3=57，輸出軸齒輪4=63。

1. 定非圓齒輪 2. 行星非圓齒輪

3 仿真分析與試驗(yàn)驗(yàn)證

3.1 試驗(yàn)設(shè)計(jì)

本文從2個(gè)角度對(duì)三組非圓行星輪系番茄果秧分離振動(dòng)發(fā)生器設(shè)計(jì)的合理性進(jìn)行驗(yàn)證：1）將采用三組非圓行星輪系振動(dòng)發(fā)生器分離滾筒的角位移曲線（仿真所得及試驗(yàn)所得）與采用雙偏心塊式振動(dòng)發(fā)生器時(shí)分離滾筒的角位移曲線進(jìn)行擬合比較；2）用仿真分析方法將三組和單組非圓行星輪系振動(dòng)發(fā)生器時(shí)輸出軸齒輪上任意一個(gè)齒面在一個(gè)周期內(nèi)的受力情況進(jìn)行比較。

3.1.1 運(yùn)動(dòng)學(xué)試驗(yàn)

將振動(dòng)發(fā)生器模型導(dǎo)入ADAMS中進(jìn)行仿真分析，設(shè)定模型輸入轉(zhuǎn)速參數(shù)為111 r/min，獲取三組非圓行星輪系番茄果秧分離振動(dòng)發(fā)生器輸出軸角速度、角位移曲線。

試制三組非圓行星輪系振動(dòng)發(fā)生器并替換FS-35振動(dòng)分離試驗(yàn)臺(tái)[27-28]上雙偏心塊式振動(dòng)發(fā)生器進(jìn)行試驗(yàn)，利用CPL-MS70K型高速攝像系統(tǒng)拍攝分離滾筒的運(yùn)動(dòng)情況[29-30]，將試驗(yàn)的轉(zhuǎn)速設(shè)定為111 r/min，高速攝像系統(tǒng)幀率設(shè)定為800幀/s。試驗(yàn)時(shí)調(diào)整高速攝像系統(tǒng)與機(jī)架的距離，以確保標(biāo)記的分離滾筒撥桿處于攝錄區(qū)域內(nèi)。

高速攝像系統(tǒng)拍攝分離滾筒的運(yùn)動(dòng)測(cè)試試驗(yàn)臺(tái)如圖5所示。

1. 變頻器 2. 電動(dòng)機(jī) 3. 非圓輪系振動(dòng)發(fā)生器 4. 試驗(yàn)臺(tái) 5. 標(biāo)記的分離滾筒撥桿 6. 高速攝像系統(tǒng)

3.1.2 齒面接觸力試驗(yàn)

為驗(yàn)證三組非圓行星輪系振動(dòng)發(fā)生器傳動(dòng)部件載荷較為均衡，將三組非圓行星輪系振動(dòng)發(fā)生器與單組非圓行星輪系振動(dòng)發(fā)生器輸出軸齒輪齒面的受力情況進(jìn)行比較。在ADAMS軟件中設(shè)定振動(dòng)發(fā)生器輸入轉(zhuǎn)速為111 r/min，分別獲得三組和單組非圓行星輪系振動(dòng)發(fā)生器行星齒輪與輸出軸齒輪嚙合的接觸力大小，導(dǎo)出數(shù)據(jù)并繪制三組和單組非圓行星輪系振動(dòng)發(fā)生器齒面接觸力隨時(shí)間變化的曲線。

3.2 試驗(yàn)結(jié)果與分析

3.2.1 運(yùn)動(dòng)學(xué)試驗(yàn)結(jié)果分析

利用高速攝像分析軟件Blaster Mas對(duì)攝錄視頻進(jìn)行分割、標(biāo)記并進(jìn)行逐幀追蹤，得到分離滾筒實(shí)測(cè)角位移散點(diǎn)圖，并求解出角速度散點(diǎn)圖。利用MATLAB和Origin9.0將散點(diǎn)擬合后得到實(shí)測(cè)擬合角位移、角速度曲線，擬合度2分別為0.861和0.981（均≥0.85）。為驗(yàn)證裝置的準(zhǔn)確性，將得到的實(shí)測(cè)擬合角位移、角速度曲線與目標(biāo)曲線和仿真曲線進(jìn)行對(duì)比，如圖6所示。

注：目標(biāo)曲線為雙偏心塊式振動(dòng)發(fā)生器曲線。

由圖6可知，三組非圓輪系振動(dòng)發(fā)生器輸出軸角位移曲線呈現(xiàn)擺動(dòng)增加趨勢(shì)，輸出軸角速度呈現(xiàn)周期性變化，且二者周期相同；實(shí)測(cè)曲線與仿真和目標(biāo)的角位移、角速度曲線存在微小誤差，角速度曲線峰值差小于0.4 rad/s，角位移峰值差小于0.05 rad，但各曲線變化趨勢(shì)及關(guān)鍵數(shù)據(jù)點(diǎn)仍較為接近。即從運(yùn)動(dòng)學(xué)分析可知，三組非圓輪系振動(dòng)發(fā)生器能產(chǎn)生保證果秧分離的運(yùn)動(dòng)需求，同時(shí)由于齒輪傳動(dòng)所具有的特性可保證果秧分離過程中運(yùn)動(dòng)參數(shù)不易受載荷影響而發(fā)生變化，從而避免發(fā)生阻塞。

3.2.2 齒面接觸力試驗(yàn)結(jié)果分析

將三組齒面接觸力變化曲線和單組的進(jìn)行比較，得到2個(gè)齒面接觸力的對(duì)比分布圖（如圖7所示）。

圖7 三組與單組非圓行星輪系振動(dòng)發(fā)生器齒面接觸力對(duì)比圖

從圖7可看出，單組非圓行星輪系振動(dòng)發(fā)生器的齒面接觸力變化范圍為0～200 000 N，三組非圓行星輪系振動(dòng)發(fā)生器的齒面接觸力變化范圍為0～125 N。因此，三組非圓行星輪系振動(dòng)發(fā)生器傳動(dòng)部件載荷相對(duì)于單組非圓行星輪系振動(dòng)發(fā)生器更加均衡。

4 結(jié) 論

1）設(shè)計(jì)了基于多組非圓行星輪系的番茄果秧分離振動(dòng)發(fā)生器，并通過分析其運(yùn)動(dòng)模型建立了非圓齒輪傳動(dòng)比方程和節(jié)曲線方程，進(jìn)而確定了非圓齒輪的基本參數(shù)。

2）搭建了分離滾筒運(yùn)動(dòng)測(cè)試試驗(yàn)臺(tái)，利用高速攝像系統(tǒng)獲取了分離滾筒在三組非圓行星輪系振動(dòng)發(fā)生器驅(qū)動(dòng)下的實(shí)測(cè)角位移和角速度曲線，并分別與對(duì)應(yīng)的仿真曲線和目標(biāo)曲線進(jìn)行對(duì)比分析，結(jié)果表明：試驗(yàn)角位移和角速度曲線與仿真和目標(biāo)曲線基本吻合，驗(yàn)證了非圓行星輪系振動(dòng)發(fā)生器設(shè)計(jì)的合理性。

3）獲取并對(duì)比分析了三組非圓行星輪系振動(dòng)發(fā)生器與單組非圓行星輪系振動(dòng)發(fā)生器的齒面接觸力，驗(yàn)證了三組非圓行星輪系振動(dòng)發(fā)生器傳動(dòng)部件載荷相對(duì)于單組非圓行星輪系振動(dòng)發(fā)生器更加均衡的特性。

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Design of tomato fruit separation vibration generator with multi group non-circular planetary gear

Wang Lihong1, Zhang Na1, Kan Za1※, Li Chengsong1, Zhu Xingliang2

(1.832000,; 2830052,)

The processing tomato planting area is increasing year by year in Xinjiang, and mechanized harvesting has become an important mean of tomato harvesting. Fruit seedling separation device is one of the core working parts of processed tomato harvesting machine. At present, double eccentric block type of fruit seedling separating vibration generator is widely used. However, there are still some problems with this relatively matured technology, such as motion parameters are easily affected by load, device is easily blocked and so on, which strongly affect the performance of processing tomato harvesting machine. Some scholars proposed to apply non-circular planetary gear to the structure design of tomato fruit seedling vibration generator, but this type of tomato fruit seedling vibration generator has a problem that its transmission components load is imbalanced. To solve above problems, in this study, we put forward multiple-group non-circular planetary gear of tomato fruit seedling vibration generator. The research results published from other scholars about trajectories of separation roller and conditions of tomato harvesting vibration were used when we designed tomato fruit separation vibration generator base on multi-group non-circular planetary gear. Trigonometric function and MATLAB software were exploited to fit separate roller angular velocity and angular displacement scatter curve. Then fitting curve of angular displacement and angular velocity were obtained as well as input and output angular displacement fitting function type, which served as the objective function of tomato fruit separation vibration generator based on multi-group non-circular planetary gear. The fitting degree with no more than 0.85 of angular displacement and velocity were obtained. The OriginPro9.0 was used to obtain angular velocity and angular displacement fitting function. According to the method of theoretical mechanics and dynamics, the theoretical equation of dynamics and kinematics were established to obtain the transmission ratio and pitch-curve equation of the non-circular gear train. Non-circular gears based on three groups were designed and gear tooth profiles of non-circular gear were generated by using gear’s pitch curve got from MATLAB. Then, the whole structure of fruit seedling vibration generator base on three group non-circular planetary gear was designed according to the selected type and corresponding parameters of gear train, which was mainly composed of input shaft assembly、tie rod assembly、shell and output shaft assembly. When this vibration generator working, power was input from the input shaft uniformly and transferred to the separation roller by transmission of this vibration generator. In this way, the uniform motion of input shaft was transformed into variable speed rotary motion of output shaft to drive the separation roller achieving the separation of fruit and stem seedlings. The model of vibration generator based on multi-group non-circular planetary gear was constructed, and this model was analyzed by simulating in the ADAMS at speeds of 111 revolutions per minute. The contrast figure of non-circular gear vibration generator and three groups non-circular gear vibration generator’s tooth surface contact force diagram was obtained by analyzing the tooth surface contact force between the planet gear and the output shaft gear, which showed that the vibration generator possessed uniform stress, and small vibration and the correctness of the model were verified. Finally, the physical prototype of vibration generator based on multi-group non-circular planetary gear was developed, and then tomato fruit seedling separation test was conducted in the way that replacing double eccentric block vibration generator with vibration generator based on multi-group non-circular planetary gear on tomato fruit seedling separation test platform, in this test, the motion process of separating drum was tracked shot using CPL-MS70k high speed camera system, whose frame rate was set to 800. The test data were analyzed and we found that the actual motion curve of drum separation fitted better with simulation curve and objective motion curve, from which maximum error was less than 0.4 rad/s, showing that the mechanism design was reasonable. This study provides a new idea for the improvement of processing tomato fruit seedling separation device.

vibration; separation; gears; harvesters; non-circular gear; planetary gear train; gear pitch curve

10.11975/j.issn.1002-6819.2017.12.005

S225.99

A

1002-6819(2017)-12-0034-06

2016-09-06

2017-06-02

國(guó)家自然科學(xué)基金資助項(xiàng)目（51265046）

王麗紅，女，河北邯鄲人，博士，教授，主要研究方向?yàn)檗r(nóng)業(yè)裝備工程。石河子 石河子大學(xué)機(jī)械電氣工程學(xué)院，832003。 Email：wlh_shz@163.com

坎 雜，男，新疆精河人，博導(dǎo)，教授，主要研究方向?yàn)檗r(nóng)業(yè)裝備工程。石河子 石河子大學(xué)機(jī)械電氣工程學(xué)院，832003。 Email：kz-shz@163.com

王麗紅，張 娜，坎 雜，李成松，朱興亮．用于番茄果秧分離的多組非圓行星輪系振動(dòng)發(fā)生器設(shè)計(jì)[J].農(nóng)業(yè)工程學(xué)報(bào)，2017，33(12)：34－39. doi：10.11975/j.issn.1002-6819.2017.12.005 http://www.tcsae.org

Wang Lihong, Zhang Na, Kan Za, Li Chengsong, Zhu Xingliang. Design of tomato fruit separation vibration generator with multi group non-circular planetary gear[J]. Transactions of the Chinese Society of Agricultural Engineering (Transactions of the CSAE), 2017, 33(12): 34－39. (in Chinese with English abstract) doi：10.11975/j.issn.1002-6819.2017.12.005 http://www.tcsae.org