数学 外文翻译 外文文献 真空压力播种机的数学建模

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基于ADAMS的精密播种机的运动仿真研究

基于ADAMS的精密播种机的运动仿真研究
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本科毕业论文外文翻译【范本模板】

本科毕业论文外文翻译【范本模板】

本科毕业论文外文翻译外文译文题目:不确定条件下生产线平衡:鲁棒优化模型和最优解解法学院:机械自动化专业:工业工程学号: 201003166045学生姓名: 宋倩指导教师:潘莉日期: 二○一四年五月Assembly line balancing under uncertainty: Robust optimization modelsand exact solution methodÖncü Hazır , Alexandre DolguiComputers &Industrial Engineering,2013,65:261–267不确定条件下生产线平衡:鲁棒优化模型和最优解解法安库·汉泽,亚历山大·多桂计算机与工业工程,2013,65:261–267摘要这项研究涉及在不确定条件下的生产线平衡,并提出两个鲁棒优化模型。

假设了不确定性区间运行的时间。

该方法提出了生成线设计方法,使其免受混乱的破坏。

基于分解的算法开发出来并与增强策略结合起来解决大规模优化实例.该算法的效率已被测试,实验结果也已经发表。

本文的理论贡献在于文中提出的模型和基于分解的精确算法的开发.另外,基于我们的算法设计出的基于不确定性整合的生产线的产出率会更高,因此也更具有实际意义。

此外,这是一个在装配线平衡问题上的开创性工作,并应该作为一个决策支持系统的基础。

关键字:装配线平衡;不确定性; 鲁棒优化;组合优化;精确算法1.简介装配线就是包括一系列在车间中进行连续操作的生产系统。

零部件依次向下移动直到完工。

它们通常被使用在高效地生产大量地标准件的工业行业之中。

在这方面,建模和解决生产线平衡问题也鉴于工业对于效率的追求变得日益重要。

生产线平衡处理的是分配作业到工作站来优化一些预定义的目标函数。

那些定义操作顺序的优先关系都是要被考虑的,同时也要对能力或基于成本的目标函数进行优化。

就生产(绍尔,1999)产品型号的数量来说,装配线可分为三类:单一模型(SALBP),混合模型(MALBP)和多模式(MMALBP)。

无油涡旋真空泵内部流场的计算机模拟与仿真

无油涡旋真空泵内部流场的计算机模拟与仿真

分类号密级UDC学位论文无油涡旋真空泵内部流场的计算机模拟与仿真作者姓名:李指导教师:杨副教授东北大学机械工程与自动化学院申请学位级别:硕士学科类别:工学学科专业名称:机械制造及其自动化论文提交日期:2008年2月20日论文答辩日期:2008年2月28日学位授予日期:2008年3月25日答辩委员会主席:评阅人:东北大学2008年2月A Dissertation in Mechanical Manufacturing and AutomationComputer simulation of oil-free scroll vacuumpump interior flow fieldby Li ChunyanSupervisor: Associate Professor Yang GuangyanNortheastern UniversityFebruary 2008独创性声明本人声明,所呈交的学位论文是在导师的指导下完成的。

论文中取得的研究成果除加以标注和致谢的地方外,不包含其他人己经发表或撰写过的研究成果,也不包括本人为获得其他学位而使用过的材料。

与我一同工作的同志对本研究所做的任何贡献均已在论文中作了明确的说明并表示谢意。

学位论文作者签名:日期:学位论文版权使用授权书本学位论文作者和指导教师完全了解东北大学有关保留、使用学位论文的规定:即学校有权保留并向国家有关部门或机构送交论文的复印件和磁盘,允许论文被查阅和借阅。

本人同意东北大学可以将学位论文的全部或部分内容编入有关数据库进行检索、交流。

(如作者和导师不同意网上交流,请在下方签名;否则视为同意。

)学位论文作者签名:导师签名:签字日期:签字日期:无油涡旋真空泵内部流场的计算机模拟与仿真摘要涡旋无油真空泵是一种容积式无油真空泵,具有结构简单、振动噪音小、可靠性高、抽气特性好等优越性能,由于这个原因,国内外许多电子工业部门广泛地采用这种真空泵。

为了满足我国开发研究生产这种泵的需要,本文对无油涡旋真空泵的封闭压缩腔压力场和排气口速度场进行了比较深入的研究与探讨。

【机械类文献翻译】播种机锯切防堵装置设计及其切割机理的研究

【机械类文献翻译】播种机锯切防堵装置设计及其切割机理的研究

Design of sawing anti-blocking mechanism forno-tillage planter and its cutting mechanismLiao Qingxi1,Gao Huanwen2,Shu Caixia1(1.Engineering and Technology College,Huazhong Agricultural University,Wuhan430070,China;2.Engineering College,China Agricultural University,Beijing100083,China)Abstract: Based on blocking issues of no-tillage planter for dry-land farming in two-crop-a-year region in North of China and shortcomings of anti-blocking mechanism developed, such as higher rotation speed (above 1500 r/min) and bigger power consumption (width power consumption per unit up to 16~41.74 kW/m, including traction power), a new sawing anti-blocking mechanism was developed and its cutting mechanism was investigated in this paper. Meanwhile stress distribution of the saw-tooth blade calculated by the ANSYS finity element software showed that the saw-tooth blade would be feasible to cut corn straws. Experimental results in the soil bin showed that: 1)The sawing anti-blocking mechanism with two cutting modes of sustaining and no-sustaining cut could realize an integrated function of cutting and directly throwing by reverse rotation, namely, it could throw straws directly to the rear of the opener by former angle of saw-tooth and thrower; 2)The cutting rate of straws would increase along with the rising of straw moisture and rotation speed, and higher moisture of straws would be of benefit to improving cutting quality; 3)The cutting rate of straws would decrease along with the rising of velocity of vehicle while interval of the moved and fixed blade was determined. And the sawing anti-blocking mechanism had higher cutting quality and lower power consumption without leaky cutting and tearing out with small interval of the moved and fixed blade. Compared with other driving anti-blocking mechanisms, theoretical analysis and experimental results showed that the sawing anti-blocking mechanism had fine cut capability and lower rotation speed (650 r/min) and lower power consumption (power consumption per unit width up to 2.95 kW/m) as well as stronger suitability to different stubbles mulch. Additionally, a new way was found out to improve anti-blocking performance of no-tillage planter.Key words: no-tillage planter; sawing anti-blocking mechanism; cutting mechanism; cutting rateCLC number: S223.2Document code: A Article ID:1002-6819(2003)05-0064-07 Received date:2003-06-151IntroductionAnti-blocking issue of no-tillage planter had become one of the key factors affecting production efficiency and seeding quality of two-crop-a-year region in North of China. It was because there was a great deal of crop stubbles and crop seeding was started shortly after crop had been harvested, leaving no time for crop stubbles to decay. At present, there are two methods to solve anti-blocking issue of no-tillage: 1) Straws were chopped by the straw chopper before seeding, it would lead to adding working procedure and increase costs of production as well as delaying seeding time; 2) Stubbles were cleared out by driving chopping mechanism fixed on no-tillage planter, such as Strip Wheat Spinning and Furrow Planter made in Hebei Nonghaha Machinery Ltd Corporation and 2BMDF-Corn Strip Chopper made in China Agricultural University[1]and so on. In practice the driving chopping mechanism had significant effect on anti- blocking, but also bigger vibration and noise as well as lower security because straws were chopped at high rotation speed.It was reported that the blade base linear velocity of several main straw chopping mechanisms was between 37~56 m/s[2], mostly chopping mechanism combined with cutting and striking had higher striking velocity and higher power consumption[3], e.g. the blade base linear velocity up to 34 m/s could obtain fine cutting effect for corn straws[4], and 24 m/s on rice and wheat straws by supporting pole, respectively[5]. Even if corn straws were cut by sliding cut with vertical blade, its velocity of cutting one straw, two straws and three straws must be up to10.3 m/s, 13.6 m/s, 15.8 m/s[6], respectively, and had higher power consumption. In a word, because the driving chopping mechanism developed presently had high rotation speed ( above 1500 r/min ) and higher power consumption (width power consumption per unit up to 16~41.74 kW/m, including traction power), to decrease rotation speed and power consumption would be urgent in practice.Based on practical problems, the objective in this paper is to find a way to solve the shortcoming that it 64 is difficult for common smooth blade to seize straws and it must run at higher rotation speed, decrease power consumption and improve cutting effect as well as anti-blocking performance of no-tillage planter. Additionally some experiments were done by selecting saw-tooth as cutting blade of no-tillage planter and cutting mechanism of the sawing anti-blocking mechanism was investigated.2Structure and cutting rule of the sawing anti-blocking mechanism2.1Structure and characteristicsThe sawing anti-blocking mechanism was made up of saw-tooth blade, throwing ban device, principal shaft, moved and fixed blade combination, covering shell, opener and working frame as well as transmission system. Sketch of the sawing anti-blocking mechanism is shown in Fig. 1. The main parts included saw-tooth blade, throwing ban device as well as fixed blade combinations. Diameter of saw-tooth with 60 teeth was 350 mm; throwing ban device with max 270 mm turning diameter was fixed on between adjacent saw-teeth; fixed blade combinations consisted of fixed blade with tooth and vertical type blade, and tooth type blade same to saw-tooth, Moreover, the vertical type blade would be used to obstruct straws without cutting from throwing area and participated in cutting straws. The sawing anti-blocking mechanism was fixed on the soil bin device, its width was 600 mm, the interval of adjacent openers was 200 mm. The sawing anti-blocking mechanism had many characteristics such as straws would be chopped by saw-tooth blade and fixed blade combinations, and had two cutting modes with susta-ining and no-sustaining cutting, the blade base line velocity of saw-tooth was lower to tossing blade type, namely, the sawing anti-blocking mechanism could change higher speed hewing into lower speed sawing.2.2Cutting principleThe sawing anti-blocking mechanism was driven to reverse rotation by power. First, straws were cut in no-sustaining mode by saw-tooth blades while saw-tooth blades touched straws, then after straws were completely cut down, they would be free and be thrown to the rear of opener by throwing ban device and inertial force. Second, straws not being completely cut down would be thrown to former upward and be cut in sustaining mode by fixed blade combinations until any of straws would be cut down, straws having been cut down were thrown to the rear of opener by throwing ban device and saw-tooth. In turn, time after time, straws would be carried out continuously to cut and throw by the sawing anti-blocking mechanism. The lowest point of the saw-tooth blades kept 15~30 mm interval from the soil. In terms of spreading status of straws in field existed perpendicularity or certain angle with marching direction, saw principal in landscape orientation had been determined for the sawing anti-blocking mechanism in order to decrease repeated cutting, leaky cutting and tearing out.Working procedures of the sawing anti-blocking mechanism were as follows: 1) no-sustaining cut phase: static straws relative to ground were cut firstly atNpoint by saw-tooth blades, then, straws would be cut down completely or embedded in saw-tooth. Straws being cut down completely would be free and 65Liao Qingxi et al: Design of anti-blocking mechanism for no-tillage planter dropped into adjacent saw-tooth; 2) dragging and delivering phase: after straws dropped into adjacent saw-tooth, they would be thrown to former upward by the throwing ban device, moreover, straws embedded in the saw-tooth would be thrown to former upward by the saw-tooth at higher speed rotation; 3) sustaining cut phase: straws not being cut down completely in no-sustaining cut phase would be cut in sustaining mode by fixed blade combinations atK point until any of straws would be cut down completely;4)throwing phase: straws being cut down were thrown directly to the rear of opener by tooth former slanting angleof the saw-tooth and throwing ban device, time and again, straws would be carried out continuously to cut and throw. The working principle of the sawing anti-blocking mechanism is shown in Fig.2.2.3Analysis of mechanics characteristics of saw-tooth bladeCutting properties of saw-tooth to cut straws belong to wriggly cut of no-metal materials, its ultimate objective is not only to improve surface cutting quality, but also to raise cutting efficiency, so it can decrease sawing force and power consumption[9]. Because the ratio of its diameter 350 mm to its thickness 1.8 mm is over 150, the saw-tooth blade belongs to exceed thin disc. It is as plane stress and no-axis symmetry problem according to elasticity theory. And because the saw-tooth blade was tighten by flange tray, six freedoms of its center hole were restricted, so its center parts could be regarded as restricted status completely not to bring any displacement and rotation. Saw-tooth blade belongs to excessive blade tools, it would bring to alternative sawing forces in cutting straws, The reasons lied in: 1) structure of straws with inner empty and outside hardness had determined micro-hardness un-uniformity distribution, so the single tooth force would be uncertain in cutting straws; 2) the total sawing forces of saw-tooth in horizontal direction would be uncertain because the tooth of saw-tooth blade is not continuous. These alternative characteristics would bring to transfiguration of the saw-tooth, moreover, the transfigured properties an size was relative to the stress properties and size of the saw-tooth in supporting outside loading. So, it was very essential to make clear stress distribution of the saw-tooth in order to ensure smooth cutting.The stress distribution of the saw-tooth blade was calculated by the ANASYS finity element software. Number of the tooth participating in cutting straws was determined to 2~3 teeth while diameter of straws was in 20~45 mm[11]. The saw-tooth made in 65Mn o fEequal to 210 GPa[12]andμto 0.28 was separated into 1200 cells and 1260 nodes by trapezia gridding. Thus the stress distributions ofX,YandXYplane had been obtained by the ANASYS software according to the most average wring value 26.8 Nm[13]of the saw-tooth to cut straws by the wring sensor. The stress distributions are shown in Fig.3. Calculated results showed: 1 ) the saw-tooth blade had acted as alternative stress from the whole stress distribution of sawtooth, tooth and around center hole of the saw-tooth had been distributed primary stress, the biggest pressing stress was up to 70776 Pa, moreover, the biggest pulling stress up to 19945 Pa. Compared with yield fatigue intension 735 MPa[12]of the saw-tooth, the saw-tooth blade was difficult to be destroyed, so it would be feasible to cut corn straws; 2)Fig.3 showed, around stress distribution of the saw-tooth blade was in symmetry distribution, the area of relative bigger stress only occupied 3.33% of the saw-tooth whole area, the other 96.67%; 3)the former tooth of saw-tooth supported the biggest forces among the whole saw-tooth while the former tooth of the saw-tooth touched firstly straws, and its stress value was the smallest before cutting straws, but when saw-tooth started to cut straws, the stress value would increase 66 V ol.19, No.5 Transactions of the CSAE Sept.2003sharply, its values would be over 105times comparing with the stress values before saw-tooth started to cut straws. However the stress would be down to the lowest point while saw-tooth had finished cutting straws. Thus, the saw-tooth was acted as alternative stress.3Materials and method3.1Experimental equipmentThe experiment was conducted in the soil bin device, of 20m-long, 0.89m-wide, 0.6m-high, the available working journey of vehicle was 16 m, and the working velocity of vehicle was from 0.12 m/s to 1.2 m/s. And other equipment included: AKC-205 type wring sensor, the sawing anti-blocking mechani-sm, control tank, computer operation platform, etc.3.2Experimental materialsThe average height and diameter of corn straw is 2.25 m, 25. 6 mm, respectively. It is made up of leaves and skin and marrow. The weight of leaves and marrow occupy above 55% of whole straw and their mechanical intension are much lower; and the weight of skin made up of scarfskin and bunchy organization occupy 35% or so,the mechanical intension of skin is much higher up to 90 MPa of portrait resistant pulling intension and 3 MPa of landscape orientation resistant pulling intension by measurement, which was essential theory basis for the saw-tooth blade to select landscape orientation principle in order to decrease power consumption.3.3Experimental methodsThe sawing anti-blocking mechanism was hung up in the soil bin device, and its ascending was controlled by hydraulic pressure system, and the wringM measured by wring sensor was automatically noted in computer, repeat three times, and then the power consumption could be calculated by expressionP=M×n/9549, the cutting rateηcould be calculated by expressionη=(G-G0)/G×100%, where,G——the total mass of effective width/kg,G0——total mass of the straws cut down between adjacent openers.4Results and discussion4.1Experiments and analysis of rotation direction of the saw-tooth blade for cutting qualitySome experiments were done by clockwise and counter-clockwise rotation of the saw-tooth blade in the soil bin device. The results are listed in Table 1.Table 1Experimental results of rotation direction of the saw-tooth bladeTable 1 showed that the way of cutting straws at counter-clockwise rotation would be of benefit to improve cutting quality and throwing effect, and boost up adaptability of weight of different stubble mulch. Therefore, counter-clockwise rotation direction of the saw-tooth blade had been determined.4.2Effect of the rotation speed on cutting qualityThe experiments were done by selecting velocity 0.3 m/s of vehicle and interval 5 mm of the moved and fixed blade, and spacing 20 mm between the saw-tooth and ground as well as weight 11250 kg/hm2of the straws mulch, experimental results are shown in Fig.4. The results indicated that the power consump-tion and cutting rate would increase with rising of rotation speed of the saw-tooth blade. Because the wring values of cutting straws were equal basically on the same working condition, the cutting rate could be up to 100% while the rotation speed of the saw-tooth blade was above 650 r/min. It was because the probability rate of the saw-tooth blade to cut straws 67 Liao Qingxi et al: Design of anti-blocking mechanism for no-tillage planter would increase with rising of rotation speed whenweight of straws was fixed.Fig.4Relationships among rotation speed, cutting rate and power consumption4.3Effect of the straw moisture on cutting qualityThe straw moisture of the same crops is different for different autumn and reaping time. The moisture were 20%, 40.5%, 64.4% and 80.16% respectively, after corn straws had been placed in field for different periods. Experiments were done by selecting velocity 0.3 m/s of vehicle and interval 5 mm between the moved and fixed blade and spacing 20 mm between sawtooth and ground, and rotation speed 650 r/min as well as mass 11250 kg/hm2of straws mulch, the results were shown in Fig.5. Fig.5Results of straws moisture for cutting rate and power consumptionExperimental results show that power consumption decreased with increasing of straw moisture and cutting rate of straws increased with increasing of straws moisture on the same working condition, which had connected importantly with different moisture of straws. Straws would take on bigger hardness and best firmness and fine brittleness when straws moisture was in higher, which demonstrated that it had been easy to finish to cut straws. But straws would take on tired and soft status for fine flexible and toughness when straw moisture was lower, so it would be easy to bring to tearing and wrapping. The saw-tooth blade had fine cutting quality and higher cutting rate while straws moisture was up to 80.16% (Fig.6). However the saw-tooth blade had taken ontearing while straw moisture was up to 20%(Fig.7).4.4Effect of interval between the fixed and moved blade and velocity of vehicle on cutting qualityExperiments were done by selecting velocity 0.3 m/s of the vehicle and spacing 20 mm between saw-tooth and ground, and rotation speed 650 r/min as well as weight 11250 kg/hm2of the straws mulch, experimental results are shown in Fig.8. The results proved that power consumption increased with increasing of velocity of vehicle on the same working condition. The power consumption increased with increasing interval between the fixed and moved blade and no fixed blade, at the same time, power consumption with interval 10mm between the fixed and moved blade was equal basically to that of without the fixed blade, and the power consumption was decreased with interval 5 mm between the fixed and moved blade. At the same time, cutting quality of interval 5 mm between the fixed and moved blade was excel to that of above 5 mm interval. Its reasons liedin that straws would be cut down completely while the small interval between the fixed and moved blade, the bigger interval between the fixed and moved blade or near diameter of corn straws, corn straws could be embedded into saw-tooth and participated in cutting again, so feeding quantities of straws were increased. And straws could not be cut down completely which brought to rearing phenomenon. The cutting rate of 68 V ol.19, No.5 Transactions of the CSAE Sept.2003straws decreased with increasing of velocity of vehicle when the interval between the fixed and moved blade was determined, and cutting rate of straws with interval 5 mm between the fixed and moved blade was bigger than that with the interval 10 mm and no-fixed blade, its reasons lied in the probability of entering throwing area for straws not being cut down completely decreased while small intervalbetween the fixed and moved blade.5Conclusions1) A new type of sawing anti-blocking mechanism, which could get rid of some shortcoming that common smooth blade is difficult to seize straws as well as high rotation speed, was designed according to the anti-blocking requirements of no-tillage planter and need in practice. The sawing anti-blocking mechanism had strong capability to seize straws and lower rotation (650 r/min) speed and lower consumption (power consumption per unit width up to 2.95 kW/m) and higher cutting rate of straws, a new approach was provided for design and development of the anti-blocking mechanism of no-tillage planter.2) The stress distribution of the saw-tooth blade was calculated by the ANASYS finity element software. The results showed that its intension would be difficult to be destroyed and the sawtooth blade was feasible to cut corn straws.3) The sawing anti-blocking mechanism realized an integrated function of directly throwing and cutting straws by counter-clockwise. The straws could be cut down completely by two cutting modes of sustaining and no-sustaining cut. Meanwhile, the straws being cut down completely could be directly thrown to the rear of opener by the former tooth horn of sawtooth blade and throwing ban device.4) Experimental results showed in the soil bin device that: (1) Cutting rate of straws increased with increasing of rotation speed of saw-tooth blade and moisture of straws, and higher moisture of straws would be of benefit to improve cutting quality; (2) Power consumption increases along with increasing of rotation speed, and that decreased with increasing of moisture of straws; ( 3 ) Cutting rate of straws decreased with increasing of velocity of the vehicle while interval between the fixed and moved blade had been determined, and to decrease the interval between the fixed and moved blade would be of benefit to improve cutting quality of straws without phenomena of rearing out and leaky cut, and could decrease power consumption.Compared with the other driving anti-blocking mechanism, the theoretical analysis and experimental results showed that the sawing anti-blocking mechanism had better capability to cut and lower rotate speed and power consumption as well as stronger suitability for different stubbles mulch.[References][1]Zhang Jinguo, Gao Huanwen. Study on the strip chopping anti-blocking mechanism[J]. Transactions of the Chinese Society of Agricultural Machinery, 2000,31(4):33~35(in Chinese).[2]Luan Y uzhen, Tian Hongwei. Research on performance and matched pattern of chopper for cornstalk and root[J]. Transactions of Jilin Agriculture University,1991,13(3): 65~68(in Chinese).[3]Mao Hanping, Chen Cuiying. Research status of the straw chopper[J]. Transactions of the Chinese Society of Agricultural Machinery, 1996, 12 ( 2 ): 152~154 (in Chinese).[4]Mao Hanping, Chen Cuiying. Analysis of working mechanism and parameters of the straw chopper [J]. Transactions of the CSAE, 1995, 11 (4): 62~66 (in Chinese).[5]Wu Fengsheng, Jin Mei. Design of 4Q—31 chopper mechanism for rice and wheat stalk[J]. Transactions of the CSAE,1998,14(3):248~250(in Chinese).[6]Wu Ziyue, Gao Huanwen, Zhang Jinguo. Study on 69Liao Qingxi et al: Design of anti-blocking mechanism for no-tillage planter cutting velocity and power requirement in a maize stalk chopping process[J]. Transactions of the Chinese Society of Agricultural Machinery, 2001, 32 (2): 38~41 (in Chinese).[7]Li Jinyi, Wang Xiangfa. Cutting mechanism of forage harvester [ J ]. Agriculture Machinery and Food Machinery,1995(4):19~20(in Chinese).[8]Woodworker Machinery Compiled Group. Woodworkermachinery [ M ]. Beijing: China Forest Publishing Company,1998(in Chinese).[9]Zhou Canfeng, Chen Qingshou, Li Zuguang. Randomness of sawing forces and wear blade [J]. Explore MineEngineering,2000,(2):52~55(in Chinese).[10]Wang Longbu. Elasticity theory[M]. Beijing: Science Publishing Company, 1979(in Chinese).[11]Liao Qingxi, Gao Huanwen. Experimental study on anti-blocking mechanism of the sawing anti-blocking mechanism for no-tillage planter [J]. Transactions of China Agricultural University, 2003, (4): 45~48 (in Chinese).[12]Zhou Kaiqin. Handbook of mechanical parts [ M ]. Beijing:Advanced Education Publishing Company, 1994.[13]Liao Qingxi, Gao Huanwen. Experimental study on the sawing anti-blocking mechanism for no-tillage planter [J]. Transactions of the Chinese Society of AgriculturalMachinery,2003(6):to be published(in Chinese).[14]Yang Zhongpin, Yang Linqing, Guo Kangquan. A preliminary study on the technology of making cornstalk cuticles particleboard[J]. Transactions of Northwestern Agricultural University, 1995, 10 ( 3 ): 67~72 ( in Chinese).播种机锯切防堵装置设计及其切割机理的研究廖庆喜‘,高焕文2,舒彩霞(1.华中农业人学工程技术学院,武汉430070; 2. (中国农业大学工学院,北京100083)摘要:针对我国北方旱地一年两熟地区免耕播种机堵塞现象和已有卞动式防堵装置转速高( 1500 r/ min以上)、功耗人(单位幅宽达16- 41.74 kW/m,含牵引功率)的现实问题,设计了一种新型免耕播种机锯切防堵装置,分析了该装置的切割机理,应用有限元ANSYS软件计算了锯齿圆盘切刀的应力分布,得出了锯齿圆盘切刀川于玉米秸秆切割的可行性。

基于Solidworks四行双箱小麦播种装置建模与仿真

基于Solidworks四行双箱小麦播种装置建模与仿真

2020年35期创新前沿科技创新与应用Technology Innovation and Application基于Solidworks 四行双箱小麦播种装置建模与仿真*赵鑫,李艳聪*,蒋华巍,蒋思念,钱正阳(天津农学院工程技术学院,天津300384)1概述精播机械可以保证按照规定播量、株距以及播深让麦种入地[1-4]。

为了更好的了解播种机工作原理,对其结构改进提供直观参考,可以借助三维设计软件建立播种机三维实体模型。

本文借助Solidworks 软件建立了四行双箱配套小麦播种机的零部件模型,整机模型,并进行了仿真,进而了解了播种机在运动时各部位的运动状态,对于后期研究播种机结构改进具有参考价值和实际意义。

2四行双箱小麦播种装置建模仿真该播种装置主要包括机架、种盒、地轮、落种口、圆盘开沟器等零部件。

该模型建立借助Solidworks 三维建模软件完成。

2.1四行双箱小麦播种机械主零件建模2.1.1种盒框架建模打开Solidworks ,在零件界面点击选择前视基准面,绘制草图,通过软件特征工具栏的拉伸命令,进行拉伸,再进行拉伸切除,再在上视基准面上进行抽壳、绘制草图拉伸切除后再其他面上进行穿孔就可得到两个相似的大小种盒框架(如图1)。

2.1.2种盒配合零件建模打开杂olidworks ,在草图绘制一个圆,在特征工具栏中选择拉伸后再以拉伸过的圆面为基准面绘制多个相同的多边形对称草图进行拉伸后可得到两个相似的种盒零件,如图2-5。

图2种盒零件12.1.3漏斗建模在草图绘制一个正方形对其拉伸切除得到基础立体底面后,再离所得立体底面一定距离建立基准面,草图绘制一个圆后进行上下面放样与上下面抽壳后就可得到基本漏斗立体外形。

如图6-7所示。

2.1.4播种机机架与种箱的建模建立草图与基准面先绘制出基本轮廓后使用特征工具栏中的放样后,再在其他面建立基准面、绘制草图后再拉伸、切除便可得到基本的立体模型,经过穿孔等修饰后便可得到机架与种箱两个模型(如图8-9)。

一个P(o)lya罐子模型的停时问题

一个P(o)lya罐子模型的停时问题

一个P(o)lya罐子模型的停时问题
祝东进
【期刊名称】《淮北师范大学学报(自然科学版)》
【年(卷),期】2002(023)002
【摘要】本文讨论一个P(o)lya罐子模型,得到了该模型停时N的分布,进而证明了EN有限.
【总页数】3页(P6-8)
【作者】祝东进
【作者单位】安徽师范大学数学系,安徽,芜湖,241000
【正文语种】中文
【中图分类】O211
【相关文献】
1.关于罐子模型一个极限分布的注记 [J], 努尔买买提·斯拉吉;杨纪龙;米辉
2.一个Pólya罐子模型的极限定理 [J], 胡学平;姚劢
3.Pólya罐子模型证明的一些探讨 [J], 徐香勤;张小勇
4.一个pólya罐子模型的强大数定律 [J], 祝东进
5.基于带停时的奇异型随机控制问题的投资决策模型 [J], 于洋
因版权原因,仅展示原文概要,查看原文内容请购买。

气吸式播种器排种盘结构参数分析及优化——基于Fluent软件

气吸式播种器排种盘结构参数分析及优化——基于Fluent软件任永飞;林蜀云;汤耿;李坦东;徐良【摘要】根据气吸式播种器的结构及原理,运用流体知识建立数学模型,分析了真空室速度与负压的影响因素,并运用Gambit、Fluent软件模拟仿真及验证数学模型分析的可行性.同时,进行了排种器性能试验,结果表明:排种盘上吸种孔壁与轴心夹角在0°~45°增大过程中,有利于种子吸附,以及风机选型与动力匹配;排种盘上吸种孔壁与轴心夹角为30°~45°时,排种器排种效果最好.最后,分析得出数学模型、模拟数据和试验数据,为今后排种盘的设计制造及气吸式播种机动力选型提供理论依据.【期刊名称】《农机化研究》【年(卷),期】2018(040)006【总页数】5页(P24-28)【关键词】播种器;气吸式;吸种孔角度;Fluent【作者】任永飞;林蜀云;汤耿;李坦东;徐良【作者单位】贵州省山地农业机械研究所,贵阳 550002;贵州省山地农业机械研究所,贵阳 550002;贵州师范大学,贵阳 550002;贵州省山地农业机械研究所,贵阳550002;贵州省山地农业机械研究所,贵阳 550002【正文语种】中文【中图分类】S223.2;S220.30 引言随着现代化农业的发展,农作物生产逐步走向规模化、集约化经营道路,对于山地的农作物种植条件及机械化水平要求越来越高。

精密播种机可以分为机械式播种机和气吸式播种机。

目前,西南山地主要使用的是机械式播种机。

机械式播种机具有受土质条件影响大、对种子外形尺寸要求高、播种密度不稳定等缺点。

因此,发展山地小型气吸式播种机能够提高播种精度,具有更好的适应性。

本文根据气吸式播种器的结构特点,设计差异性吸种孔壁夹角的播种盘,通过数学模型分析气吸式播种器中气流速度与真空室负压的影响因素;利用Gambit建立气吸式全流道三维模型及网格划分,通过Fluent软件模拟排种器真空室内部流场速度与负压,分析出影响排种盘主要的结构参数,有利于排种盘的设计制造。

播种机实验报告(3篇)

第1篇一、实验目的1. 了解播种机的工作原理和结构组成。

2. 掌握播种机的操作方法,提高播种效率。

3. 通过实验验证播种机在不同播种量下的播种效果。

二、实验原理播种机是一种用于作物播种作业的机械,主要由种子箱、排种器、输种管、开沟器、覆土器、行走轮等组成。

机械播种可一次完成播种作业的开沟、排种、输种和覆土等工序,播种进度快,能保证适时播种,提高播种质量,为作物获得良好的生长条件打下基础。

三、实验设备与材料1. 实验设备:播种机、量筒、土壤、种子、秒表、皮尺等。

2. 实验材料:玉米种子、小麦种子、土壤。

四、实验步骤1. 准备工作:选择适宜的土壤,准备种子,检查播种机各部件是否完好。

2. 设置播种量:根据实验要求,设置不同的播种量,例如每米播种10粒、20粒、30粒等。

3. 播种实验:a. 将土壤摊平,准备播种。

b. 将种子放入播种机的种子箱中。

c. 开启播种机,按照设定的播种量进行播种。

d. 播种过程中,观察播种机的工作状态,确保播种均匀。

4. 数据记录:记录播种时间、播种量、播种效果等数据。

5. 分析结果:对实验数据进行整理、分析,得出结论。

五、实验结果与分析1. 播种时间:播种时间随着播种量的增加而增加,例如播种10粒玉米种子用时2分钟,播种30粒玉米种子用时4分钟。

2. 播种效果:播种效果与播种量有关,播种量越大,播种效果越好。

例如,播种10粒玉米种子时,播种深度较浅,种子发芽率较低;播种30粒玉米种子时,播种深度适中,种子发芽率较高。

3. 播种均匀性:播种均匀性较好,播种机在播种过程中能保证种子均匀分布。

六、实验结论1. 播种机是一种高效、便捷的播种工具,能够提高播种效率,保证播种质量。

2. 播种效果与播种量有关,播种量越大,播种效果越好。

3. 播种机在播种过程中能保证种子均匀分布。

七、实验讨论1. 播种机在实际应用中,应选择合适的播种量和播种速度,以保证播种效果。

2. 播种机在使用过程中,应注意维护保养,确保其正常运行。

2019年全国大学生数学建模竞赛题目A:高压油管的压力控制优秀论文范例三篇(含源代码)

2019年全国大学生数学建模竞赛题目A:高压油管的压力控制优秀论文范例三篇(含源代码)1. 引言高压油管是发动机燃油喷射系统中的重要组成部分,其压力的控制对于发动机的运行稳定性非常关键。

在2019年全国大学生数学建模竞赛中,针对高压油管的压力控制问题,我们进行了一系列研究和分析,探索了解决该问题的优秀方法。

本文将介绍三篇优秀论文范例,并提供源代码供读者参考。

2. 论文一:基于PID控制算法的高压油管压力控制2.1 问题描述本文从数学建模的角度出发,针对高压油管的压力控制问题提出了一种基于PID控制算法的解决方案。

该问题的要求是在给定的工况下,通过控制高压油泵的开关方式,使得一段时间内高压油管内的压力保持在一个预定的范围内。

2.2 算法设计本文提出了基于PID控制算法的高压油管压力控制方案。

PID控制是一种常用的反馈控制算法,通过不断调整控制器的参数,根据当前误差来调整控制信号。

在该方案中,我们将高压油管的压力误差作为PID控制器的输入,根据控制器输出的控制信号,调整高压油泵的开关状态。

通过不断的反馈调整,使得高压油管内的压力稳定在预定范围内。

2.3 仿真与实验结果本文通过对所提出的高压油管压力控制方案进行仿真与实验,验证了该方案的可行性和有效性。

仿真结果表明,通过PID控制算法,可以在较短的时间内将高压油管内的压力控制在预定范围内。

实验结果也进一步验证了方案的有效性。

2.4 源代码# PID控制算法实现def pid_control(p_error, i_error, d_error):Kp =0.5# 比例系数Ki =0.2# 积分系数Kd =0.1# 微分系数control_signal = Kp * p_error + Ki * i_error + Kd * d_errorreturn control_signal# 高压油管压力控制主程序def pressure_control(target_pressure, current_pre ssure, time_step):p_error = target_pressure - current_pressurei_error = p_error * time_stepd_error = (p_error - d_error_prev) / time_ste pcontrol_signal = pid_control(p_error, i_error, d_error)d_error_prev = p_errorreturn control_signal# 实际应用中的使用示例target_pressure =100# 目标压力current_pressure =0# 当前压力time_step =0.1# 时间步长while True:control_signal = pressure_control(target_pres sure, current_pressure, time_step)# 根据控制信号调整高压油泵的开关状态# 更新当前压力值3. 论文二:基于模型预测控制的高压油管压力控制3.1 问题描述本文针对高压油管的压力控制问题,提出了一种基于模型预测控制(MPC)的解决方案。

农业用机械设备外文文献翻译、中英文翻译、外文翻译

农业用机械设备外文文献翻译、中英文翻译、外文翻译在公元前1世纪,中国已经开始推广使用耧,这是世界上最早的条播机具,在北方旱作区仍然得到应用。

1636年,希腊制造了世界上第一台播种机。

1830年,俄国人在畜力多铧犁上加装播种装置制成了犁播机。

1860年后,英美等国开始大量生产畜力谷物条播机。

20世纪后,牵引和悬挂式谷物条播机以及运用气力排种的播种机相继出现。

50年代,精密播种机开始得到发展。

中国从20世纪50年代开始引进谷物条播机、棉花播种机等。

60年代,中国先后研制成了悬挂式谷物播种机、离心式播种机、通用机架播种机和气吸式播种机等多种类型,并研制成了磨纹式排种器。

到70年代,中国已经形成了播种中耕通用机和谷物联合播种机两个系列,并成功研制出了精密播种机。

播种机具有播种均匀、深浅一致、行距稳定、覆土良好、节省种子、工作效率高等特点。

正确使用播种机应注意以下10个要点:1)在进田作业前,要清理播种箱内的杂物和开沟器上的缠草、泥土,确保状态良好。

对拖拉机及播种机的各传动、转动部位,按照说明书的要求加注润滑油,尤其是每次作业前要注意传动链条润滑和张紧情况以及播种机上螺栓的紧固情况。

2)机架不能倾斜,播种机与拖拉机挂接后,不得倾斜,工作时应使机架前后呈水平状态。

3)搞好各种调整,按照使用说明书的规定和农艺要求,将播种量、开沟器的行距、开沟覆土镇压轮的深浅调整适当。

Seeder Tips1.Pay n to adding good quality seeds to the seed box to XXX。

Make sure there are no small。

broken。

or impure seeds。

Also。

XXX.2.Before large-scale seeding。

conduct a 20-XXX.3.Choose a suitable route for the seeding machine to move ina straight line at a constant speed。

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目录1.Introduction (3)引言 (17)2.Materials and methods (4)材料和方法 (18)3.Results and discussion (7)结果与讨论 (21)4. Conclusions (13)结论 (26)5.Acknowledgements (13)鸣谢 (26)Mathematical Modelling of Vacuum Pressure on a Precision SeederD. Karayel 1, Z. B. Barut 2 and A. Özmerzi 11 Akdeniz University, Faculty of Agriculture, Department of Agricultural Machinery, 07070, Antalya, Turkey2 Çukurova University, Faculty of Agriculture, Department of Agricultural Machinery, Adana, Turkey; e-mail of corresponding author: dkarayel@.trReceived 9 July 2003; accepted 19 January 2004. Available online 13 April 2004. AbstractThe purpose of this research was to determine the optimum vacuum pressure of a precision vacuum seeder and to develop mathematical models by using some physical properties of seeds such as one thousand kernel mass, projected area, sphericity and kernel density. Maize, cotton, soya bean, watermelon, melon, cucumber, sugarbeet and onion seeds were used in laboratory tests. One thousand kernel mass, projected area, sphericity and kernel density of seeds varied from 4.3 to 372.5 g, 5–77 mm2, 38.4–85.8% and 440–1310 kg m−3, respectively. The optimum vacuum pressure was determined as 4.0 kPa for maize I and II; 3.0 kPa for cotton, soya bean and watermelon I; 2.5 kPa for watermelon II, melon and cucumber; 2.0 kPa for sugarbeet; and 1.5 kPa for onion seeds.The vacuum pressure was predicted by mathematical models. According to the results, the final model could satisfactorily describe the vacuum pressure of the precision vacuum seeder with a chi-square of 2.51×10−3, root mean square error of 2.74×10−2 and modelling efficiency of 0.99.NomenclatureNomenclaturea, b, c, d, e regression coefficientsE m modelling efficiencyE rms root mean square errork exp experimental vacuum pressure, kPak exp, mean mean value of experimental vacuum pressure, kPak pre predicted vacuum pressure, kPaL length, mmm1000one thousand kernel mass, gN number of observationn number of constants in the modelP projected area, mm2P v vacuum pressure, kPap probabilityR2coefficient of determinationT thickness, mmW width, mmφsphericity, %χ2chi-squareρk kernel density, kg m−3Article OutlineNomenclature1. Introduction2. Literature review3. Materials and methods4. Results and discussion5. ConclusionsAcknowledgementsReferences1. IntroductionPrecision sowing has been a major thrust of agricultural engineering research for many years; however, most of the research and development work has dealt with seeders for agronomic crops.The main purpose of sowing is to place the seed to a certain space and a depth in the seedbed. Precision seeders place seeds at the required spacing and provide a better growing area per seed. There are two common types of precision seeders: belt and vacuum. Precision vacuum seeders have a metering plate with metering holes on a predetermined radius. A vacuum is applied to these metering holes by means of a race machined in a backing plate. As the plate rotates, the vacuum applied to the metering holes enables them to pick up seeds from the seed hopper. Precision vacuum seeders have the following advantages over the mechanical seeders: better working quality,more precise seed rates with lower rate of seed damage, better control and adjustment of upkeep and drift of seeds, and broader spectrum of applicability (Soos et al., 1989).A seeder should place a seed in an environment in which the seed will reliably germinate and emerge. A number of factors affect the spacing of plants. The seed selection mechanism may fail to select or drop a seed resulting in large spacing between seeds. The mechanism may select and drop multiple seeds resulting in small spacings between seeds. Seed quality, soil conditions, seeder design and the skill of the operator all play a part in determining the final plant stand.The physical properties of seeds are essential for the design of equipment for handling, processing, storing and sowing the kernels. Various types of cleaning, grading, separation and sowing equipment are designed on the basis of the physical properties of seeds. However, no model has been found to describe seeder parameters such as vacuum pressure related with physical properties of seeds.The physical properties of the seeds are the most important factors in determining the optimum vacuum pressure of the precision vacuum seeder. In this study, using some of these, e.g. one thousand kernel mass, projected area, sphericity and kernel density, mathematical models were developed to predict optimum vacuum pressure. The experimental values of vacuum pressure were determined from laboratory test procedure.2. Materials and methodsThe laboratory test procedure involved testing the metering uniformity of the seeder at the different vacuum pressure with the different seeds: two different maize varieties (maize I and maize II), cotton, soya bean, two different watermelon varieties (watermelon I and watermelon II), melon, cucumber, sugarbeet and onion. These seeds represent several seed shapes varying from spherical (soya bean, maize II) to flat and elongated (maize I, melon, watermelon, cucumber). Two different varieties of maize and watermelon seeds were selected, because of the more diverse range of one thousand kernel mass, projected area, sphericity or kernel density than other seeds. All seeds used in this research were uncoated seed. The main dimensions of the seeds are given in Table 1. The seeder was set to space the seeds as closely to the recommended spacing as possible.Table 1. Means and standard errors of the seed dimensionsA grease belt test stand was used to determine sowing uniformity of each seed at the different vacuum pressures. This particular test stand had a 150 mm wide belt with a 7·5 m long horizontal viewing surface. A seeder row unit was mounted on a greased belt test stand which utilised an adjustable speed drive mechanism to operate the seed metering devices at a known constant speed. Sufficient oil was added to the top surface of belt to capture the seed as it was released from seeder unit without rolling or bouncing of seed on the belt surface. A wide variety of measures were used to qualify seeder performance with regard to plant spacing (Brooks & Church, 1987; Karayel & Özmerzi, 2001; Jasa & Dickey, 1982). Some tests used performance measures involving distance between plants in the field. Other tests used performance measures involving distance between seeds on grease belt test stand or by opto-electronic sensor system ( Bracy et al., 1998; Smith et al., 1991; Lan et al., 1999). A few tests used performance measures involving distance between seeds sown into soil ( Panning, 1997).A precision vacuum seeder unit was operated in all treatments (Fig. 1). The seeder unit was a general purpose seeder designed for row crops such as maize and soya beans. Three different vacuum plates with different hole diameters were used in the metering mechanism. The diameter of vacuum plates were 230 mm. The holes were drilled along a 200 mm diameter pitch circle. The holes of the vacuum plate were 3·5 mm in diameter for maize I, II, soya bean and cotton; 2·5 mm in diameter for watermelon I, II, melon, and cucumber and 1·5 mm in diameter for sugarbeet and onion. The seed plate operated in a vertical plane. Air suction from the holes of the seed plate caused the seed to stick to the holes. The stuck seed was released from the rotating plate by temporarily preventing airflow. The absence of suction allowed the seed to be dropped into soil. It had no seed tube and the seed fall height (12 mm) of the seeder was kept low in order to reduce the chance of non-uniform spacing which can occur due to the bouncing of seed, if dropped from high plane. The vacuum level was regulated by adjusting the size of an opening in the vacuum line of seeder and measured with a manometer.Fig. 1. The metering mechanism of the precision vacuum seeder: 1, vacuum plate; 2, seed; 3, seed box; 4, air suction canal; 5, air cut; 6, furrow openerThe seeder was operated over the greased belt at a ground speed of 1 m s−1 and adjusted to four vacuum pressures 2.0, 3.0, 4.0 and 5.0 kPa for maize I, II, soya bean and cotton; 2.0, 2.5,3.0 and 3.5 kPa for melon, watermelon I, II and cucumber; 1.0, 1.5, 2.0 and 2.5 kPa for sugarbeet and onion seeds. Seed spacings were measured over a distance of 7 m. The seeder was adjusted to deliver a nominal seed spacing of 230 mm for maize I and II, 170 mm for cotton, 105 mm for soya bean, 550 mm for watermelon I, II, melon and cucumber, 150 mm for sugarbeet and 85 mm for onion.The sowing uniformity was analysed using the methods as described by Kachman and Smith (1995). The multiple index is the percentage of spacings that are less than or equal to half of the theoretical spacing and indicates the percentage of multiple seed drops. The miss index is the percentage of spacings greater than 1.5 times the theoretical spacing and indicates the percentage of missed seed locations or ‘skips’. Quality of feed index is the percentage of spacings that are more than half but no more than 1.5 times the theoretical spacing. Quality of feed index is 100% minus miss and multiple index and indicates the percentages of single seed drops. Preciseness is the coefficient of variation of the spacings that are classified as singles after omitting the outliers consisting of misses and multiples.Kachman and Smith (1995)recommended using miss index, multiple index, quality of feed index and preciseness for summarising the uniformity of seeder metering rather than mean or sample coefficient of variation. They concluded that several measures were needed to give a true picture of seeder uniformity. For this study, miss index, multiple index, quality of feed index and preciseness are reported.Various physical properties of seeds including kernel density, projected area, sphericity and one thousand kernel mass are the most important factors in determining the optimum vacuum pressure of the precision vacuum seeder (Barut, 1996). The physical properties of the seeds were determined by the following methods: Linear dimensions, i.e.length, thickness and width were measured by using a vernier caliper with a sensitivity of 0.01 mm. Sphericity φ were calculated by using the following equation (Mohsenin, 1970):(1) where: L is the length; W is the width; and T is the thickness in mm.One thousand kernel mass was measured by an electronic balance with a sensitivity of 0.001 g.Kernel density was measured by the liquid displacement method. Toluene (C7H8) was used rather than water because it was not absorbed by fruits (Mohsenin, 1970; Ögöt, 1998).Projected area was determined by using a digital camera (Kodak DC 5000) and Sigma Scan Pro 5 program.For the estimation of the vacuum pressure, in relation to kernel density, projected area, sphericity and one thousand kernel mass, mathematical models were developed. The suitability of the final model was compared and evaluated using chi-square, root mean square error and modelling efficiency. Chi-square χ2, root mean square error E rms and modelling efficiency E m were calculated as follows:(2)(3)(4) where: k exp is the experimental vacuum pressure in kPa; k exp,mean is the mean value of experimental vacuum pressure in kPa; k pre is the predicted vacuum pressure in kPa; N is the number of observations; and n is the number of constants in the model.Reduced chi-square is the mean square of the deviations between the experimental and calculated values for the models and, is used to determine the goodness of the fit. The lower values of the reduced chi-square, the better the goodness of the fit. The root mean square error shows the deviations between the calculated and experimental values and it requires to reach zero. The modelling efficiency also shows the ability of the model and its highest value is 1 (Yaldiz et al., 2001; Ertekin & Yaldiz, 2004).Each experiment was arranged as a randomised complete block (Neter et al., 1990) and replicated five times. An analysis of variance method was applied to analyse data sets using a statistical software package SAS. Duncan's multiple-range tests were used to identify significantly different means within dependent variables.3. Results and discussionThe effect of vacuum pressure on sowing uniformity of the vacuum seeder was analysed relating to the multiple index, miss index, quality of feed index and preciseness. Multiple index, miss index and quality of feed index were combined for analysis of variance to determine the significant difference in the variability among the parameters. The results of this analysis are given in Table 2, Table 3 and Table 4. All measurement of sowing uniformity of the vacuum seeder were affected by vacuum pressure.Table 2. The sowing uniformity of the vacuum seeder with maize I and II, cotton and soya bean seeds for different vacuum pressureNote: Means within a group followed by same letter are not significantly different at probability p=0·05, by Duncan's multiple range test.Table 3. The sowing uniformity of the vacuum seeder with watermelon I and II, melon and cucumber seeds for different vacuum pressureNote: Means within a group followed by same letter are not significantly different at probability p=0·05, by Duncan's multiple range test.Table 4. The sowing uniformity of the vacuum seeder with sugarbeet and onion seeds for different vacuum pressureNote: Means within a group followed by same letter are not significantly different at probability p=0.05, by Duncan's multiple range test.The optimum vacuum pressure was determined for each seed according to quality of feed index and preciseness. As can be seen from laboratory study results in Table 2, Table 3 and Table 4, the highest seed spacing uniformities (quality of feed index) and the lowest preciseness values were obtained at the vacuum pressure of 4.0 kPa for maize I and II; 3.0 kPa for cotton, soya bean and watermelon I; 2.5 kPa for watermelon II, melon and cucumber; 2.0 kPa for sugarbeet and 1.5 kPa for onion seeds. The most uniform sowing uniformity was obtained with soya bean seeds at any vacuum pressures. Uniform, spherical seeds such as soya bean and maize II were easy to meter with the vacuum metering system.The miss index decreased and the multiple index increased with increasing vacuum pressure for all seeds. Multiple seed drops were more common than misses for watermelon I and II, melon, cucumber, onion and sugarbeet seeds. Few ‘skips’ or multiple drops occur at any vacuum pressure for maize I and II, cotton and soya bean seeds.Loss of uniformity of the vacuum seeder was probably a combination of several factors. The results support reports from Barut (1996)who found that the pattern efficiency of the vacuum plate differed most at lower or higher vacuum pressures and faster wheel speeds. In this research, preciseness and quality of feed index of the vacuum seeder were poorer at the lower and higher vacuum pressures than optimum vacuum pressure.One thousand kernel mass, projected area, sphericity and kernel density of seeds are given in Table 5. One thousand kernel mass, projected area, sphericity and kernel density of seeds varied from 4.3 to 372.5 g, 5–77 mm2, 38.4–85.8% and 440–1310 kg m−3, respectively.Table 5. Means and standard errors of the seed dimensionsThe relationship between one thousand kernel mass, projected area, sphericity and kernel density with vacuum pressure presented in Fig. 2, Fig. 3, Fig. 4 and Fig. 5. For the determination of the relationship between the one thousand kernel mass and the projected area with vacuum pressure, the power model was used. For the determination of relationship between the sphericity and the kernel density with the vacuum pressure, the linear model was used. The diagrammatic representation of the models results in a curve that fits well for the description of the vacuum pressure. The relationship between one thousand kernel mass with vacuum pressure is better than the others with the highest coefficient of determination of 0.92.Fig. 2. Vacuum pressure of precision vacuum seeder as a function of one thousand kernel mass; R2, coefficient of determinationFig. 3. Vacuum pressure of vacuum seeder as a function of projected area; R2, coefficient of determinationFig. 4. Vacuum pressure of vacuum seeder as a function of sphericity; R2, coefficient of determinationFig. 5. Vacuum pressure of vacuum seeder as a function of kernel density; R2, coefficient of determinationAll possible combinations of the different variables were tested and included in the regression analysis. The multiple combinations of one thousand kernel mass, projected area, sphericity and kernel density that gave the lowest root mean square error and chi-square and the highest modelling efficiency were finally included in the final model. Based on the multiple regression analysis the accepted model constants, coefficients, chi-square χ2, root mean square error E rms and modelling efficiency E m were as follows: P v=a+b m10000·27+cP−0·02−dφ+eρkwhere: P v is the vacuum pressure in kPa; m1000 is one thousand kernel mass in g; P is the projected area in mm2; φ is the sphericity in %; ρk is the kernel density in kg m−3. The optimum values of the coefficient a, b, c, d, and e, namely 1.00, 0.72, 2.09×10−3, 0.01 and 0.37×10−3, respectively, gave values for χ2 of 2.51×10−3, for E rms of 2.74×10−2, and for E m of 0.99.Validation of the established final model was evaluated by comparing the computed vacuum pressures with the observed vacuum pressures. The performance ofthe model was illustrated in Fig. 6. The predicted data generally banded around the straight line which showed the suitability of the final model in describing vacuum pressure of the seeder.Fig. 6. Experimental versus predicted vacuum pressure values by final model; R2, coefficient of determination4. ConclusionsIn laboratory tests, the optimum vacuum pressure of a precision vacuum seeder was determined as 4.0 kPa for maize I and II; 3.0 kPa for cotton, soya bean and watermelon I; 2.5 kPa for watermelon II, melon and cucumber; 2.0 kPa for sugarbeet and 1.5 kPa for onion seeds.In order to predict vacuum pressure in relation to one thousand kernel mass, projected area, sphericity and kernel density of seeds, mathematical models were developed. The relationship between one thousand kernel mass with vacuum pressure was better than the others with the highest coefficient of determination. The final model could satisfactorily describe the vacuum pressure of the precision vacuum seeder with a chi-square of 2.51×10−3, root mean square error of 2.74×10−2 and modelling efficiency of 0.99.AcknowledgementsThe corresponding author acknowledge the help of Dr. Can ERTEKIN in developing the mathematical models.ReferencesBarut Z B(2006). Farkli tohumlarin ekiminde kullanilan düsey plakali, hava emisli hassas ekici düzenin uygun çalisma kosullarinin saptanmasi. [Determination of the optimum working parameters of a precision vacuum seeder.] PhD Thesis, University of Cukurova, Adana, TurkeyBracy R P; Parish R L; McCoy J E (1998). Precision seeder uniformity varies with theoretical spacing. ASAE Paper No. 981095. ASAE, St. Joseph, MIBrooks D; Church B(1997). Drill performance assessments: a changed approach. British Sugar Beet Review, 50(3), 13–15Çarman K(1996). Some physical properties of lentil seeds. Journal of Agricultural Engineering Research, 63, 87–92Ertekin C; Yaldiz O (2004). 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Bulletin of the University of Agricultural Science, Gödöllo, 1, 166–170Wanjura D F; Hudspeth E B(2005). Performance of vacuum wheels metering individual cottonseed. Transactions of the ASAE, 12(6), 775–777Yaldiz O; Ertekin C; Uzun H I (2006). Mathematical modelling of thin layer solar drying of sultana grapes. Energy, 26, 457–465真空压力播种机的数学建模D. Karayel 1, Z. B. Barut 2 and A. Özmerzi 11 Akdeniz University, Faculty of Agriculture, Department of Agricultural Machinery, 07070, Antalya, Turkey2 Çukurova University, Faculty of Agriculture, Department of Agricultural Machinery, Adana, Turkey; e-mail of corresponding author: dkarayel@.tr引言这项研究的目的是确定最佳的精密真空压力播种机。

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