缽苗移栽機(jī)橢圓齒輪行星系植苗機(jī)構(gòu)運(yùn)動(dòng)學(xué)建模與分析外文翻譯、外文文獻(xiàn)翻譯、畢業(yè)中英文翻譯

Computer Aided Design of Oval Gear of Separating planting Mechanism with Planetary Gears of Non-eccentricity Abstract： Separating Planting Mechanism with Planetary Gears of Non-Eccentricity is a new type mechanism The mechanism is constituted by three parts they are oval gear transmission division， planetary gear transmission division and plant the arm Basic thought of designing is adopting oval gear transmission， choice the fit construction parameter to ensure Asymmetry transmission ratio and screw the angle relation of the request of transplant rice seedling The thesis will expatiate how to computer geometric pare meter of oval gear， analysis transmission character of oval gear， and ensure transmission ratio and Angle of pressure in the period of Engagement of oval gear. Key words： agricultural engineering； separating-planting mechanism with planetary gears of non-eccentricity； design； oval gear； computer aided design 1. Transplanting Mechanism with Planetary Gears works As shown in Figure 1, the diagram of The Planetary Gears rice transplanter transplanting mechanism make up with four congruent the Zhengyuan gear and 3 congruent oval gear. 3 rotation center of the oval gear are in the focus of the oval ear, They have same initial phase. The center oval gear (3) (also called sun wheel) fixed . Gearbox (equivalent carrier) is drived by the central axis, the equivalent of a prime mover pieces rotate around the rotation center 0 of the sun wheel. Since the two oval gears (3) and (4) engages that caused the change of the transmission ratio, so the two planets circle gear that symmetrical arrangement are swinging back and forth, seedling claw move at the required posture (Angular displacement and trajectory). The basic idea of the design is use the non-uniform drive of oval gear pair and select the appropriate structural parameters to find the work trajectory, the take seedlings angle and the planting angle that meet planting requirements. 1. Planetary circular gear 2. Intermediate circular gear 3 Central oval gear 4. Intermediate oval gear 5. Seedling needle Figure 1 a schematic diagram of planetary gears Transplanting Mechanism 2.Oval gear rotation relationship Figures 2 and 3 as a pair of congruent oval gear meshing relationship diagram Figure 2 is the initial position of the elliptical gear drive capstan do uniform motion, when the one pair of congruent oval gear, the rotational speed of the wheel from moving periodically changes. Thus, the geometric characteristics of the oval gear only with eccentricity and fixed axis rotation relationship of the gear train and a pair of larger eccentricity the oval gear Vice corner relations are quite. Therefore, appropriately changing the eccentricity of the elliptical gears can meet the requirements of transplanting angular relationship. Elliptical gear drive transmission nature has laid a theoretical foundation for this article Transplanting Mechanism oval gear design of planetary gears. Figure 2 starting position Figure 3 rotated position 3. Oval gear design 3.1 Oval gear pitch curve arc length calculation The origin of the polar coordinate is taken at the oval lower focus 0, to the geometric center of the ellipse O, as the coordinate origin for a Cartesian coordinate system Oxy axis in the minor axis direction, Y axis in the long axis. That O center, the major axis of the ellipse radius for two circles radius a and minor radius b. Figure 4 shows the to diameter O i and the x-axis is y, it is the intersection of these two circles, respectively by i, i and j for the line parallel to the x axis, as a line parallel to the y axis by j the two lines intersect at M (x, y) based on the elliptical nature of the point M is a point on the ellipse. Terms of y angle variation of parameters, the parametric equation of the ellipse. Figure 4 oval gear pitch curve arc length Kinematics modeling and analysis of transplanting mechanism with planetary elliptic gears for pot seedling transplanter Abstract： To analyze the working performance of the transplanting mechanism with planetary elliptic gears for pot seedling trans planter which was proposed in this paper， the kinematic model of this mechanism was established， and the equations of(angular)displacement， (angular)velocity and(angular)acceleration for transplanting tip were deduced On this basis， the kinematic simulation and optimization software of the mechanism was compiled by Visual Basic 6.0 Besides， the influence of several main parameters on the working performance of the mechanism was analyzed by this software These main parameters included the semi major axis of elliptic gear， the ratio between minor axis and major axis， the initial installation angle of the planet carrier and row spacing And working perform ances included hole size， trajectory attitude of transplanting tip and its verticality， and operational stability of the mechanism According to the analysis results， a group of preferable mechanical parameters were obtained The corresponding working performance， such as the trajectory and posture of transplanting tip， can meet the agricultural demands of vegetable seedling transplanting with smaller speed fluctuation and acceleration fluctuation in comparison with reciprocating transplanting mechanism Key word： mechanisms， kinematics， models， pot seedling transplanter， transplanting mechanism， planetary elliptic gears, parametric analysis Indexing language About 60% of the global vegetable varieties grown by transplanting seedlings. China is the worlds largest vegetable production country, however, almost all seedling planting done by hand, not only labor-intensive, but another poor quality of the planting. Vegetable transplanting mechanization is the future direction of development. Uenae institutions is one of the core components of seedling transplanting machine. The 2 lines of semi-automatic vegetable transplanting machine of Japanese Iseki use seven institutions to achieve uenae,.I also proposed leveraged zero speed seedling transplanting mechanism. These two kinds of institutions are able to meet uenae agronomic requirements, but all of them belong to the reciprocating institutions.It is inertial force when operating and the machine vibration powerful. The hanging cup or basket Uenae institutions are rotary Uenae institutions. The advantage is that the force of inertia is small and planting mouth is always down in the process of transplanting. But its trajectory is trochoidal, therefore it generates big Xuekou, specifically when large plant spacing the casing and the repression device immediately followed it is easy to tear down the seedling has been implanted in the soil.The single-line automatic vegetable transplanting machine ofJapan Yanmar use the planets round of connecting rod groove cam mechanism to meet the agronomic requirements of Uenae. It is complicated in structure. This paper presents a seedling transplanting machine elliptical the Planetary Gears rotary Uenae institutions. It is through establish analysis model and parameter optimization to let It meet agronomic requirements of the seedling transplanting and the operating speed and acceleration fluctuations is small, operation is stable, and high efficiency. 1.The seedling transplanting machine Elliptic Gears the galaxy Uenae institutions Planetary Elliptic Gears of seedling transplanting machine the rotary Uenae institutions diagram. Job oval sun gear 3 fixed fixed sprocket shaft 1, driven by Carrier Rotating 2, Oval sun gear, intermediate the oval gear 5 and planets oval gear meshing, 7 relative to the planet carrier of the planetary axle 2 to do the opposite direction of the non-uniform rotation, the absolute motion of non-uniform periodic swing.Since the planting mouth (including inner semi planting nozzle 8, the outer semi planting nozzles 9, the recess 10, the pin 11, roller 12 and the spring 14) consolidation in the the planetary axle 7 on . mouth and planetary axle 7, so planting do absolutelystatic trajectory and the trajectory of the swing movement for periodically non-uniform, forming a planting mouth. Inside and outside the two semi planting mouth respectively with a recess 10 and the pin 11, when planted nozzle 8 of the inner half-orbiting planet shaft 7 is rotated a certain angle, the outer half planted nozzles 9 in the opposite direction bypass the planetary wheel shaft 7 rotated samethe size of the angle to achieve together planting the mouth in the open.Inner half planting the opening of the nozzle 8 through which the upper roller L2 and fixed in the planet carrier 2, on the face cam 13 relative rotation to achieve, While the return is to rely on the elastic force of the spring 14, the spring 14, two respectively hanging inner semi planting planting mouth of the nozzle 8 and the outer half 9. When the planet carrier to the top (Figure 1a position), the take seedlings bodies will be removed from the bowl disc seedling into the planting mouth； planet carrier and then turned l 80o around, planting the mouth is in the lowest position and fully openown weight to be implanted into the excavated Xuekou seedling, and then make the casing filling pressure, to complete the planting process.Planting mouth opening closed in the direction perpendicular to the forward direction of the machine, not overturned has been implanted in the soil in the seedling.Uenae agencies revolution Uenae 2, high efficiency, small vibration. 2. The oval gear planetary Uenae institutions Kinematics Model As shown in Figure 1b, the establishment of the point D as the origin, the horizontal direction as an axis, the vertical direction as the y-axis coordinate system (due Uenae mechanism is symmetrical and therefore only the analysis unilateral, the other side differ by 180.)To facilitate analysis, the relevant parameters and their descriptions are listed in Table 1. 正齒行星輪分插機(jī)構(gòu)橢圓齒輪的計(jì)算機(jī)輔助設(shè)計(jì) 摘 要： 正齒行星輪分插機(jī)構(gòu)是一種新型高速分插機(jī)構(gòu)，由橢圓齒輪傳動(dòng)部分、正齒輪行星輪傳動(dòng)部分和栽植臂組 成 。其 設(shè) 計(jì) 的基 本 思想 采 用橢 圓 齒輪副傳動(dòng)，選擇合適的結(jié)構(gòu)參數(shù)來形成插秧要求的非勻速傳動(dòng)比及轉(zhuǎn)角關(guān)系。為此，主要論述如何利用計(jì)算機(jī)確定分插機(jī)構(gòu)中橢圓齒輪的幾何參數(shù)、橢圓齒輪副的傳動(dòng)性質(zhì)，以及輪齒的齒廓在嚙合過程中能保證要求的轉(zhuǎn)動(dòng)比、合適的壓力角等。 關(guān)鍵詞： 農(nóng)業(yè)工 程 ；正齒 行 星輪 分 插機(jī) 構(gòu) ；設(shè)計(jì) ；橢 圓齒 輪 ；計(jì)算 機(jī) 輔助 設(shè)計(jì) 分插機(jī)構(gòu)是水稻插秧機(jī)的核心部件，其性能的分插機(jī)構(gòu)是水稻插秧機(jī)的核心 部 件， 其 性能 的 插機(jī) 構(gòu) 是一 種 新型 高 速分 插 機(jī) 構(gòu) (專利 號(hào) 98245494 5)，其工作機(jī)理是通過橢圓齒輪的不等速傳動(dòng)比達(dá)到插秧所需的運(yùn)動(dòng) 軌跡 與 加工是正齒行星輪分插機(jī)構(gòu)的重要組成部。 1 正齒行星輪分插機(jī)構(gòu)工作原理 正齒行星輪水稻插秧機(jī)分插機(jī)構(gòu)的簡(jiǎn)圖如圖 1所 示， 由 4個(gè)全等正圓齒 輪和 3個(gè)全 等 橢圓 齒 輪組 成。 3個(gè) 橢 圓齒 輪 的 回轉(zhuǎn) 中 心均 在 橢圓 齒 輪的 焦 點(diǎn)上 ，初 始相位相同。中心橢圓齒輪 (3)(也 叫 太陽 輪 )固 定 不動(dòng) ， 工作 時(shí) 齒輪 箱 (相 當(dāng)行星架 )在中心軸的 帶動(dòng) 下 ，相 當(dāng) 于一 個(gè) 原動(dòng) 件 繞 太陽 輪 的回 轉(zhuǎn) 中心 0轉(zhuǎn) 動(dòng) 。由于是兩個(gè)橢圓齒輪 (3)和 (4)嚙合 ， 引起 傳 動(dòng)比 的 變 化， 因 此對(duì) 稱 布置 的 兩個(gè)行星圓齒輪做往復(fù)擺動(dòng)，秧爪按要求的姿態(tài) (角 位移 和 軌跡 )運(yùn) 動(dòng) 。其 設(shè) 計(jì)的基本思想為用橢圓 齒 輪副 非 勻速 比 傳動(dòng) ， 通過 選 擇 合適 的 結(jié)構(gòu) 參 數(shù)， 就 可找到滿足插秧要求的工作軌跡、取秧角和插秧角。 1.行星圓齒輪 2.中間圓齒輪 3.中心橢圓齒輪 4.中間 橢 圓齒 輪 5.秧針 圖 1 正齒行星輪分插機(jī)構(gòu)示意圖 2 橢圓齒輪傳動(dòng)轉(zhuǎn)角關(guān)系 圖 2 和圖 3 為一 對(duì) 全等 的 橢圓 齒 輪嚙 合 關(guān)系 圖 。圖 2 是 橢圓 齒 輪傳 動(dòng) 的初 始位置當(dāng)一對(duì)全等的圓齒輪傳動(dòng)時(shí)主動(dòng)輪做勻速運(yùn)動(dòng)則從動(dòng)輪的轉(zhuǎn)速呈周期性變化橢圓齒輪副的傳動(dòng)比函數(shù)。由此可見橢圓齒輪的幾何特性僅與偏心率有關(guān)且定軸輪系的轉(zhuǎn)角關(guān)系 和 一對(duì) 偏 心率 較 大的 橢 圓 齒輪 副 的轉(zhuǎn) 角 關(guān)系 相 當(dāng)因此適當(dāng)改變橢圓齒輪的偏心率就能滿足插秧要求的轉(zhuǎn)角關(guān)系橢圓齒輪傳動(dòng)這種傳動(dòng)性質(zhì)為本文正齒行星輪分插機(jī)構(gòu)橢圓齒輪的設(shè)計(jì)奠定了理論基礎(chǔ)。 圖 2 起始位置 圖 3 旋轉(zhuǎn)后位置 3 橢圓齒輪的設(shè)計(jì) 3.1 橢圓齒輪節(jié)曲線弧長(zhǎng)的計(jì)算將極坐標(biāo)的原點(diǎn)取在橢圓的下焦點(diǎn) O 以橢圓的幾 何 中心 O 為坐 標(biāo) 原點(diǎn) 作直 角 坐標(biāo) 系 O xy x 軸在 橢 圓短 軸 方向 y 軸在長(zhǎng)軸方向以 O 為 圓 心橢 圓 的長(zhǎng) 軸 半徑 a 及短軸半徑 b 為 半徑作兩個(gè)圓如圖 4 所示 向徑 O i與 x 軸的夾角為 y 它與上述兩圓的 交 點(diǎn)分 為 i 及 j 由 i 作平行于 x 軸的線由 j 作平行于 y軸的線 兩線交于 M(x, y) 則根據(jù)橢圓的性質(zhì) M 點(diǎn)是橢圓上的一 點(diǎn)因 此 若以 y角 為 參 變數(shù) 則 橢圓 的 參數(shù) 方 程為 圖 4 橢圓齒輪節(jié)曲線孤長(zhǎng) 缽苗移栽機(jī)橢圓齒輪行星系植苗機(jī)構(gòu)運(yùn)動(dòng)學(xué)建模與分析 摘要： 為了分 析 該文 提 出的 缽 苗 移栽 機(jī) 橢圓 齒 輪行 星 系植 苗 機(jī)構(gòu) 的 作業(yè) 性 能，建立了該機(jī)構(gòu)的運(yùn)動(dòng)學(xué)模型，推導(dǎo)了栽植嘴的 (角 )位移 、 (角 )速 度和 (角 )加速度 方 程。 在 此基 礎(chǔ) 上， 采 用 Visual Basic 6 0編寫 了 該機(jī) 構(gòu) 的運(yùn) 動(dòng) 學(xué)仿 真與優(yōu)化軟件，并利用該軟件分析幾個(gè)主要參數(shù)對(duì)該機(jī)構(gòu)作業(yè)性能的影響，這些主要參數(shù)包括橢圓齒輪長(zhǎng)半軸、橢圓齒輪短長(zhǎng)軸之比、行星架初始安裝角和株距，作業(yè)性能包括穴口大小、栽植嘴的軌跡姿態(tài)及其直立性和機(jī)構(gòu)作業(yè)的穩(wěn)定性等。由參數(shù)影響分析結(jié)果，得到一組較優(yōu)的機(jī)構(gòu)參數(shù)，其對(duì)應(yīng)的栽植嘴軌跡和姿態(tài)等作業(yè)性能滿足蔬菜缽苗移栽農(nóng)藝要求，且與往復(fù)式的植苗機(jī)構(gòu)相比具有較小的速度和加速度波動(dòng)。 引 言 全球大約 60蔬菜 品 種是 通 過育 苗 移栽 方 式種 植 的 中國(guó) 是 世界 最 大的 蔬 菜生產(chǎn)國(guó)，然而秧苗栽植幾乎全部由人工完成，不僅勞動(dòng)強(qiáng)度大，而且栽植質(zhì)量差。蔬菜移栽機(jī)械化是未來的發(fā)展方向植苗機(jī)構(gòu)是缽苗移栽機(jī)的核心部件之一。日本井關(guān)的 2行半 自 動(dòng)蔬 菜 移栽 機(jī)