钵苗移栽机椭圆齿轮行星系植苗机构运动学建模与分析外文翻译、外文文献翻译、毕业中英文翻译

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. 正齿行星轮分插机构椭圆齿轮的计算机辅助设计 摘 要： 正齿行星轮分插机构是一种新型高速分插机构，由椭圆齿轮传动部分、正齿轮行星轮传动部分和栽植臂组 成 。其 设 计 的基 本 思想 采 用椭 圆 齿轮副传动，选择合适的结构参数来形成插秧要求的非匀速传动比及转角关系。为此，主要论述如何利用计算机确定分插机构中椭圆齿轮的几何参数、椭圆齿轮副的传动性质，以及轮齿的齿廓在啮合过程中能保证要求的转动比、合适的压力角等。 关键词： 农业工 程 ；正齿 行 星轮 分 插机 构 ；设计 ；椭 圆齿 轮 ；计算 机 辅助 设计 分插机构是水稻插秧机的核心部件，其性能的分插机构是水稻插秧机的核心 部 件， 其 性能 的 插机 构 是一 种 新型 高 速分 插 机 构 (专利 号 98245494 5)，其工作机理是通过椭圆齿轮的不等速传动比达到插秧所需的运动 轨迹 与 加工是正齿行星轮分插机构的重要组成部。 1 正齿行星轮分插机构工作原理 正齿行星轮水稻插秧机分插机构的简图如图 1所 示， 由 4个全等正圆齿 轮和 3个全 等 椭圆 齿 轮组 成。 3个 椭 圆齿 轮 的 回转 中 心均 在 椭圆 齿 轮的 焦 点上 ，初 始相位相同。中心椭圆齿轮 (3)(也 叫 太阳 轮 )固 定 不动 ， 工作 时 齿轮 箱 (相 当行星架 )在中心轴的 带动 下 ，相 当 于一 个 原动 件 绕 太阳 轮 的回 转 中心 0转 动 。由于是两个椭圆齿轮 (3)和 (4)啮合 ， 引起 传 动比 的 变 化， 因 此对 称 布置 的 两个行星圆齿轮做往复摆动，秧爪按要求的姿态 (角 位移 和 轨迹 )运 动 。其 设 计的基本思想为用椭圆 齿 轮副 非 匀速 比 传动 ， 通过 选 择 合适 的 结构 参 数， 就 可找到满足插秧要求的工作轨迹、取秧角和插秧角。 1.行星圆齿轮 2.中间圆齿轮 3.中心椭圆齿轮 4.中间 椭 圆齿 轮 5.秧针 图 1 正齿行星轮分插机构示意图 2 椭圆齿轮传动转角关系 图 2 和图 3 为一 对 全等 的 椭圆 齿 轮啮 合 关系 图 。图 2 是 椭圆 齿 轮传 动 的初 始位置当一对全等的圆齿轮传动时主动轮做匀速运动则从动轮的转速呈周期性变化椭圆齿轮副的传动比函数。由此可见椭圆齿轮的几何特性仅与偏心率有关且定轴轮系的转角关系 和 一对 偏 心率 较 大的 椭 圆 齿轮 副 的转 角 关系 相 当因此适当改变椭圆齿轮的偏心率就能满足插秧要求的转角关系椭圆齿轮传动这种传动性质为本文正齿行星轮分插机构椭圆齿轮的设计奠定了理论基础。 图 2 起始位置 图 3 旋转后位置 3 椭圆齿轮的设计 3.1 椭圆齿轮节曲线弧长的计算将极坐标的原点取在椭圆的下焦点 O 以椭圆的几 何 中心 O 为坐 标 原点 作直 角 坐标 系 O xy x 轴在 椭 圆短 轴 方向 y 轴在长轴方向以 O 为 圆 心椭 圆 的长 轴 半径 a 及短轴半径 b 为 半径作两个圆如图 4 所示 向径 O i与 x 轴的夹角为 y 它与上述两圆的 交 点分 为 i 及 j 由 i 作平行于 x 轴的线由 j 作平行于 y轴的线 两线交于 M(x, y) 则根据椭圆的性质 M 点是椭圆上的一 点因 此 若以 y角 为 参 变数 则 椭圆 的 参数 方 程为 图 4 椭圆齿轮节曲线孤长 钵苗移栽机椭圆齿轮行星系植苗机构运动学建模与分析 摘要： 为了分 析 该文 提 出的 钵 苗 移栽 机 椭圆 齿 轮行 星 系植 苗 机构 的 作业 性 能，建立了该机构的运动学模型，推导了栽植嘴的 (角 )位移 、 (角 )速 度和 (角 )加速度 方 程。 在 此基 础 上， 采 用 Visual Basic 6 0编写 了 该机 构 的运 动 学仿 真与优化软件，并利用该软件分析几个主要参数对该机构作业性能的影响，这些主要参数包括椭圆齿轮长半轴、椭圆齿轮短长轴之比、行星架初始安装角和株距，作业性能包括穴口大小、栽植嘴的轨迹姿态及其直立性和机构作业的稳定性等。由参数影响分析结果，得到一组较优的机构参数，其对应的栽植嘴轨迹和姿态等作业性能满足蔬菜钵苗移栽农艺要求，且与往复式的植苗机构相比具有较小的速度和加速度波动。 引 言 全球大约 60蔬菜 品 种是 通 过育 苗 移栽 方 式种 植 的 中国 是 世界 最 大的 蔬 菜生产国，然而秧苗栽植几乎全部由人工完成，不仅劳动强度大，而且栽植质量差。蔬菜移栽机械化是未来的发展方向植苗机构是钵苗移栽机的核心部件之一。日本井关的 2行半 自 动蔬 菜 移栽 机