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文献综述一、文献综述文献综述是研究者在其提前阅读过某一主题的文献后，经过理解、整理、融会贯通，综合分析和评价而组成的一种不同于研究论文的文体。综述的目的是反映某一课题的新水平、新动态、新技术和新发现。从其历史到现状，存在问题以及发展趋势等，都要进行全面的介绍和评论。在此基础上提出自己的见解，预测技术的发展趋势，为选题和开题奠定良好的基础。二、文献综述的格式文献综述的格式与一般研究性论文的格式有所不同。这是因为研究性的论文注重研究的方法和结果，而文献综述介绍与主题有关的详细资料、动态、进展、展望以及对以上方面的评述。因此文献综述的格式相对多样，但总的来说，一般都包含以下四部分：即前言、主题、总结和参考文献。撰写文献综述时可按这四部分拟写提纲，再根据提纲进行撰写工作。
文献调研即文献普查。根据科研工作或科研课题的需要，有计划、有组织地调查、收集有关文献资料的工作过程。
撰写文献综述步骤：1、搜索相关文献 在开始搜索文献之前，需要一个明确定义的主题。如果正在写论文或研究论文的文献综述部分，搜索与之相关的研究问题和问题。如果是以独立作业的形式写一篇文献综述，必须选择一个要点，并提出一个中心问题来指导的搜索。2、评价来源 可能无法完全阅读关于这个主题的所有文章，所以必须评估哪些文章与自己的问题最相关。确保使用的来源是可靠的，并确保阅读了自己所研究领域的任何里程碑式的研究和主要理论。可以找到一篇关于谷歌学术的文章，查看被引用了多少次，高引用数意味着这篇文章在该领域有影响力，当然应该被包括在自己的文献综述中。3、识别主题、辩论和差距 组织文献综述的论点和结构，需要理解所阅读的资料之间的联系和关系。根据阅读和笔记，帮助制定文献综述的结构，并展示自己的研究将如何对现有知识做出贡献。4、概述结构 有各种方法来组织文献综述的主体。在开始写作之前，应该对自己的策略有一个大致的了解。根据文献综述的长度，可以结合这些策略。5、写文献综述 文献综述应该有介绍、主体和结论，每篇文章中包含什么内容取决于文献综述的目标。当写完并修改完文献综述后，不要忘记在提交之前进行校对。
先交代调查的背景、目的及意义然后阐述调查的一系列概况，比如调查的目的、方法、手段、样本量、分析方法等第三块就是针对调查的具体内容详细展开第四块 总结与讨论
不同类型的调查报告，具体内容有所不同。但基本写法是相通的。 调查报告的写作方法，一是熟悉调查报告的结构特点；二要把握调查报告的写作程序。 （一）调查报告的结构 一般来说，调查报告的内容大体有：标题、导语、概况介绍、资料统计、理性分析、总结和结论或对策、建议，以及所附的材料等。由此形成的调查报告结构，就包括标题、导语、正文、结尾和落款。 标题 调查报告的标题有单标题和双标题两类。所谓单标题，就是一个标题。其中又有公文式标题和文章式标题两种。公文标题为“事由文种”构成，如《浙江省农村中学语文教学情况的调查报告》。文章式标题，如《××市的校办企业》；其二是标明作者通过调查所得到的观点的标题，如《调整教育政策，增加教育投入》。所谓双标题，就是两个标题，即一个正题、一个副题。如《为了造福子孙后代--××县封山育林调查报告》。 导语 导语又称引言。它是调查报告的前言，简洁明了地介绍有关调查的情况，或提出全文的引子，为正文写作做好铺垫。常见的导语有： ①简介式导语。对调查的课题、对象、时间、地点、方式、经过等作简明的介绍； ②概括式导语。对调查报告的内容（包括课题、对象、调查内容、调查结果和分析的结论等）作概括的说明； ③交代式导语。即对课题产生的由来作简明的介绍和说明。 正文 正文是调查报告的主体。它对调查得来的事实和有关材料进行叙述，对所做出的分析、综合进行议论，对调查研究的结果和结论进行说明。正文的结构有不同的框架。 ①根据逻辑关系安排材料的框架有：纵式结构、横式结构、纵横式结构。这三种结构，以纵横式结构常为人们采用。 ②按照内容表达的层次组成的框架有：“情况--成果--问题--建议”式结构，多用于反映基本情况的调查报告；“成果--具体做法--经验”式结构,多用于介绍经验的调查报告；“问题--原因--意见或建议”式结构，多用于揭露问题的调查报告；“事件过程--事件性质结论--处理意见”式结构，多用于揭示案件是非的调查报告。 结尾 结尾的内容大多是调查者对问题的看法和建议，这是分析问题和解决问题的必然结果。调查报告的结尾方式主要有补充式、深化式、建议式、激发式等。落款 调查报告的落款要写明调查者单位名称和个人姓名，以及完稿时间。如果标题下面已注明调查者，则落款时可省略。 （二）社会实践调查报告的写作程序 一般来说，社会实践调查报告写作要经过以下五个程序： 确定主题 主题是调查报告的灵魂，对调查报告写作的成败具有决定性的意义。因此，确定主题要注意： 报告的主题应与调查主题一致； 要根据调查和分析的结果，重新确定主题； 主题宜小，且宜集中；与标题协调一致，避免文题不副。 取舍材料 对经过统计分析与理论分析所得到的系统的完整的"调查资料"，在组织调查报告时仍需精心选择，不可能也不必都写上报告，要注意取舍。如何选择材料呢？ ①选取与主题有关的材料，去掉无关的，关系不大的，次要的，非本质的材料，使主题集中、鲜明、突出； ②注意材料点与面的结合，材料不仅要支持报告中某个观点，而且要相互支持，形成面上的“大气”； 在现有有用的材料中，要比较、鉴别、精选材料，选择最好的材料来支持作者的意见，使每一材料以一当十。 布局和拟定提纲 这是调查报告构思中的一个关键环节。布局就是指调查报告的表现形式，它反映在提纲上就是文章的"骨架"。拟定提纲的过程实际上就是把调查材料进一步分类，构架的过程。构架的原则是："围绕主题，层层进逼，环环相扣"。提纲或骨架的特点是它的内在的逻辑性，要求必须纲目分明，层次分明。 调查报告的提纲有两种，一种是观点式提纲，即将调查者在调查研究中形成的观点按逻辑关系一一地列写出来。另一种是条目式提纲，即按层次意义表达上的章、节、目，逐一地一条条地写成提纲。也可以将这两种提纲结合起来制作提纲。 起草社会实践报告 这是调查报告写作的行文阶段。要根据已经确定的主题、选好的材料和写作提纲，有条不紊地行文。写作过程中，要从实际需要出发选用语言，灵活地划分段落。 在行文时要注意：①结构合理（标题、导语、正文、结尾、落款）；②报告文字规范，具有审美性与可读性，如："制定优惠政策，引进急需人才"，"运用竞争机制，盘活现有人才"，（文章段落的条目观点）；③通读易懂。注意对数字、图表、专业名词术语的使用，做到深入浅出，语言具有表现力，准确、鲜明、生动、朴实。 修改社会实践报告 社会实践报告起草好以后，要认真修改。主要是对报告的主题、材料、结构、语言文字和标点符号进行检查，加以增、删、改、调。在完成这些工作之后，才能定稿向上报送或发表。 调查报告的标准格式： 题目 应以简炼,概括,明确的语句反映所要调查的对象,领域,方向等问题题目应能概括全篇,引人注目 前言(背景和目的) 主要包括研究背景和目的 背景介绍应简明,扼要,切题,背景介绍一般包括一部分重要的文献小结 调查目的:阐述调查的必要性和针对性,使读者了解概况,初步掌握报告主旨,引起关注 方法 详细描述研究中采用的方法,使读者能评价资料收集方法是否恰当这部分一般包括以下几方面: 地点 时间 调查对象 调查对象的选择(抽样方法),样本量的估计 调查方法:定性,定量 质量控制 结果与讨论 结果与讨论可以放在一起写,也可以分开写 结果和讨论分几节来完成一般采用描述,分析,讨论来写 描述: 描述事情的发生发展过程, 描述调查人群的人口社会学特征, 描述调查事物的特征 对比: 历史对比 他人研究对比 本调查中不同特征人群对比 推断: 在对比的基础上进行统计推断 (前提条件:调查样本具有代表性) 讨论:反映作者学术思想的深度和广度要紧紧围绕结果,以及可能有争议的主要问题进行讨论 讨论时应注意以下几点: 把调查结果上升到理论,去粗取精,去伪存真,由表及里,揭示内在联系 与他人结果相矛盾的地方,讨论发生的原因和理论依据 要有自己的看法和见解,论点明确 结论与建议 结论 用扼要的文句把论文的主要内容概括起来,切忌重复文章内容 文字结构应该准确,完整,精练,高度概括文章的主要目的和结果 建议 为政府决策提出科学建议 进一步深入研究提出建议 参考文献 列出主要理论依据和方法,以及有争议的论据 具体格式见文献综述中讲述的参考文献的格式 附录 在论文中只有局部使用或完全没有使用,但又与论文有关的具有科学价值的重要原始资料,数据,如调查问卷,访谈提纲,复杂的公式推导,计算程序,各类统计表,统计图等都可以放在附录中,有利于说明和理解调查报告,又可提供有用的科学信息
调查报告是为了深入地研究问题和事件，进行细致地调查研究写成的文件，是反映对某—问题、某一事件的调查研究结果的书面报告调查报告的标题：公文式，一般由事由和文种组成。正副式，正题揭示调查报告中心思想，副题用公文式。文章式，这类调查报告的标题比较灵活，有的是概括出调查报告的基本内容；有的是采取提问的形式调查报告的开头：有的交代调查本身情况，有的交代调查对象情况，有的对全文内容作出概括，也有的调查报告没有开头语，在标题下面分几部分直接写下去调查报告的正文：横式结构，把材料分成几个部分来写。纵式结构，按调查事件发生、发展的先后顺序加以阐明。综合式结构，兼有横式、纵式的特点调查报告的结尾：或是针对调查的内容，提出意见或深入研究的问题，或是概括全文的基本思想，深化调查报告的主题应注意的问题：必须掌握大量的第一手材料，善于作认真的分析与研究，文字要朴素、明确、实在视听智慧文化服务体系
testing of an air-cycle refrigeration system for road transportAbstractThe environmental attractions of air-cycle refrigeration are Following a thermodynamic design analysis, an air-cycle demonstrator plant was constructed within the restricted physical envelope of an existing Thermo King SL200 trailer refrigeration This unique plant operated satisfactorily, delivering sustainable cooling for refrigerated trailers using a completely natural and safe working The full load capacity of the air-cycle unit at −20 °C was 7,8 kW, 8% greater than the equivalent vapour-cycle unit, but the fuel consumption of the air-cycle plant was excessively However, at part load operation the disparity in fuel consumption dropped from approximately 200% to around 80% The components used in the air-cycle demonstrator were not optimised and considerable potential exists for efficiency improvements, possibly to the point where the air-cycle system could rival the efficiency of the standard vapour-cycle system at part-load operation, which represents the biggest proportion of operating time for most Keywords: Air conditioner; Refrigerated transport; Thermodynamic cycle; Air; Centrifuge compressor; Turbine expander COP, NomenclaturePRCompressor or turbine pressure ratioTAHeat exchanger side A temperature (K)TBHeat exchanger side B temperature (K)TinletInlet temperature (K)ToutletOutlet temperature (K)ηcompCompressor isentropic efficiencyηturbTurbine isentropic efficiencyηheat exchangerHeat exchanger IntroductionThe current legislative pressure on conventional refrigerants is well The reason why vapour-cycle refrigeration is preferred over air-cycle refrigeration is simply that in the great majority of cases vapour-cycle is the most energy efficient Consequently, as soon as alternative systems, such as non-HFC refrigerants or air-cycle systems are considered, the issue of increased energy consumption arises Concerns over legislation affecting HFC refrigerants and the desire to improve long-term system reliability led to the examination of the feasibility of an air-cycle system for refrigerated With the support of Enterprise Ireland and Thermo King (Ireland), the authors undertook the design and construction of an air-cycle refrigeration demonstrator plant at LYIT and QUB This was not the first time in recent years that air-cycle systems had been employed in NormalAir Garrett developed and commercialised an air-cycle air conditioning pack that was fitted to high speed trains in Germany in the As part of an European funded programme, a range of applications for air-cycle refrigeration were investigated and several demonstrator plants were However, the authors are unaware of any other case where a self-contained air-cycle unit has been developed for the challenging application of trailer Thermo King decided that the demonstrator should be a trailer refrigeration unit, since those were the units with the largest refrigeration capacity but presented the greatest challenges with regard to physical Consequently, the main objective was to demonstrate that an air-cycle system could fit within the existing physical envelop and develop an equivalent level of cooling power to the existing vapour-cycle unit, but using only air as the working The salient performance specifications for the existing Thermo King SL200 vapour-cycle trailer refrigeration unit are listed It was not the objective of the exercise to complete the design and development of a new refrigeration product that would be ready for To limit the level of resources necessary, existing hardware was to be used where possible with the recognition that the efficiencies achieved would not be In practical terms, this meant using the chassis and panels for an existing SL200 unit along with the standard diesel engine and circulation The turbomachinery used for compression and expansion was adapted from commercial Thermodynamic modelling and design of the demonstrator plantThe thermodynamics of the air-cycle (or the reverse ‘Joule cycle’) are adequately presented in most thermodynamic textbooks and will not be repeated For anything other than the smallest flow rates, the most efficient machines available for the necessary compression and expansion processes are Considerations for the selection of turbomachinery for air-cycle refrigeration systems have been presented and discussed by Spence et [3] a typical configuration of an air-cycle system, which is sometimes called the ‘boot-strap’ For mechanical convenience the compression process is divided into two stages, meaning that the turbine is not constrained to operate at the same speed as the primary Instead, the work recovered by the turbine during expansion is utilised in the secondary The two-stage compression also permits intercooling, which enhances the overall efficiency of the compression An ‘open system’ where the cold air is ejected directly into the cold space, removing the need for a heat exchanger in the cold In the interests of efficiency, the return air from the cold space is used to pre-cool the compressed air entering the turbine by means of a heat exchanger known as the ‘regenerator’ or the ‘recuperato ’ To support the design of the air-cycle demonstrator plant, and the selection of suitable components, a simple thermodynamic model of the air-cycle configuration shown in was The compression and expansion processes were modelled using appropriate values of isentropic efficiency, as defined in EThe heat exchange processes were modelled using values of heat exchanger effectiveness as defined in The model also made allowance for heat exchanger pressure The system COP was determined from the ratio of the cooling power delivered to the power input to the primary compressor, as defined in illustrate air-cycle performance characteristics as determined from the thermodynamic model:illustrates the variation in air-cycle COP and expander outlet temperature over a range of cycle pressure ratios for a plant operating between −20 °C and +30 °C The cycle pressure ratio is defined as the ratio of the maximum cycle pressure at secondary compressor outlet to the pressure at turbine For the ideal air-cycle, with no losses, the cycle COP increases with decreasing cycle pressure ratio and tends to infinity as the pressure ratio approaches However, the introduction of real component efficiencies means that there is a definite peak value of COP that occurs at a certain pressure ratio for a particular However,illustrates, there is a broad range of pressure ratio and duty over which the system can be operated with only moderate variation of COPThe class of turbomachinery suitable for the demonstrator plant required speeds of around 50 000 rev/ To simplify the mechanical arrangement and avoid the need for a high-speed electric motor, the two-stage compression system shown was The existing Thermo King SL200 chassis incorporated a substantial system of belts and pulleys to power circulation fans, which severely restricted the useful space available for mounting heat A simple thermodynamic model was used to assess the influence of heat exchanger performance on the efficiency of the plant so that the best compromise could be developed show the impact of intercooler and aftercooler effectiveness and pressure loss on the COP of the proposed The two-stage system in incorporated an intercooler between the two compression By dispensing with the intercooler and its associated duct work a larger aftercooler could be accommodated with improved effectiveness and reduced pressure Analysis suggested that the improved performance from a larger aftercooler could compensate for the loss of the shows the impact of the recuperator effectiveness on the COP of the plant, which is clearly more significant than that of the other heat As well as boosting cycle efficiency, increased recuperator effectiveness also moves the peak COP to a lower overall system pressure The impact of pressure loss in the recuperator is the same as for the intercooler and aftercooler shown The model did not distinguish between pressure losses in different locations; it was only the sum of the pressure losses that was Any pressure loss in connecting duct work and headers was also lumped together with the heat exchanger pressure loss and analysed as a block pressure The specific cooling capacity of the air-cycle increases with system pressure Consequently, if a higher system pressure ratio was used the required cooling duty could be achieved with a smaller flow rate of shows the mass flow rate of air required to deliver 7,5 kW of cooling power for varying system pressure Since the demonstrator system was to be based on commercially available turbomachinery, it became important to choose a pressure ratio and flow rate that could be accommodated efficiently by some existing compressor and turbine and were based on efficiencies of 81 and 85% for compression and expansion, While such efficiencies are attainable with optimised designs, they would not be realised using compromised turbocharger For the design of the demonstrator plant efficiencies of 78 and 80% were assumed to be realistically attainable for compression and Lower turbomachinery efficiencies corresponded to higher cycle pressure ratios and flow rates in order to achieve the target cooling The cycle design point was also compromised to help heat exchanger The pressure losses in duct work and heat exchangers increased in proportion with the square of flow Selecting a higher cycle pressure ratio corresponded to a lower mass flow rate and also increased density at inlet to the aftercooler heat The combined effect was a decrease in the mean velocity in the heat exchanger, a decrease in the expected pressure losses in the heat exchanger and duct work, and an increase in the effectiveness of the heat Consequently, a system pressure ratio higher than the value corresponding to peak COP was chosen in order to achieve acceptable heat exchanger performance within the available physical The below optimum performance of turbomachinery and heat exchanger components, coupled with excessive bearing losses, meant that the predicted COP of the overall system dropped to around 0, The system pressure ratio at the design point was 2,14 and the corresponding mass flow rate of air was 0,278 kg/By moving the design point beyond the pressure ratio for peak COP, it was anticipated that the demonstrator plant would yield good part-load performance since the COP would not fall as the pressure ratio was Also, operating at part-load corresponded to lower flow velocities and anticipated improvements in heat exchanger Part-load operation was achieved by reducing the speed of the primary compressor, resulting in a decrease in both pressure and mass flow rate throughout the Prime mover and primary compressorThe existing diesel engine was judged adequate to power the demonstrator The standard engine was a four cylinder, water cooled diesel engine fitted with a centrifugal clutch and all necessary ancillaries and was controlled by a microprocessor From the thermodynamic model, the pressure ratio for the primary compressor was 1, The centrifugal compressor required a shaft speed of around 55 000 rev/ Other alternatives were evaluated for primary compression with the aim of obtaining a suitable device that operated at a lower Other commercially available devices such as Roots blowers and rotary piston blowers were all excluded on the basis of poor A one-off gearbox was designed and manufactured as part of the project to step-up the engine shaft speed to around 55 000 rev/ The gearbox was a two stage, three shaft unit which mounted directly on the end of the diesel engine and was driven through the existing centrifugal Cold air unitThe secondary compressor and the expansion turbine were mounted on the same shaft in a free rotating The combination of the secondary compressor and the turbine was designated as the ‘Cold Air Unit’ (CAU) While the CAU was mechanically equivalent to a turbocharger, a standard turbocharger would not satisfy the aerodynamic requirements efficiently since the pressure ratios and inlet densities for both the compressor and the turbine were significantly different from any turbocharger Consequently, both the secondary compressor and the turbine stage were specially chosen and developed to deliver suitable Most turbochargers use plain oil fed journal bearings, which are low-cost, reliable and provide effective damping of shaft However, plain bearings dissipate a substantial amount of shaft power through viscous losses in the oil A plain bearing arrangement for the CAU was expected to absorb 2–3 kW of mechanical power, which represented around 25% of the anticipated turbine Also, the clearances in plain bearings require larger blade tip clearances for both the compressor and the turbine with a consequential efficiency Given the pressurised inlet to the secondary compressor, the limited thrust capacity of the plain bearing arrangement was also a A CAU utilising high-speed ball bearings, or air bearings, was identified as a preferable arrangement to plain Benefits would include greatly reduced bearing power losses, reduced turbomachinery tip clearance losses and increased thrust load However, adequate resources were not available to design a special one-off high speed ball bearing Consequently, a standard turbocharger plain bearing system was The secondary compressor stage was a standard turbocharger compressor selected for a pressure ratio of 1, Secondary compressor and turbine selection were linked because of the requirement to balance power and match the Since most commercial turbines are sized for high temperature (and consequently low density) air at inlet, a special turbine stage was developed for the Cost considerations precluded the manufacture of a custom turbine rotor, so a commercially available rotor was The standard turbine rotor blade profile was substantially modified and vaned nozzles for turbine inlet were designed to match the modified rotor, in line with previous turbine investigations at QUB (Spence and Artt,) An exhaust diffuser was also incorporated into the turbine stage in order to improve turbine efficiency and to moderate the exhaust noise levels through reduced air The exhaust diffuser exited into a specially designed exhaust The performance of the turbine stage was measured before the unit was incorporated into the complete demonstrator The peak efficiency of the turbine was established at 81% Heat exchangersDue to packaging constraints, the heat exchangers had to be specially designed with careful consideration being given to heat exchanger position and header geometry in an attempt to achieve the best performance from the heat Tube and fin aluminium heat exchangers, similar to those used in automotive intercooler applications, were chosen primarily because they could be produced on a ‘one-off’ basis at a reasonable There were other heat exchanger technologies available that would have yielded better performance from the available volume, but high one-off production costs precluded their use in the demonstrator Several different tube and fin heat exchangers were tested and used to validate a computational Once validated, the model was used to assess a wide range of possible heat exchanger configurations that could fit within the Thermo King SL200 Fitting the proposed heat exchangers within the existing chassis and around the mechanical drive system for the circulation fans, but while still achieving the necessary heat exchanger performance was very It was clear that potential heat exchanger performance was being sacrificed through the choice of tube and fin construction and by the constraints of the layout of the existing SL200 The final selection comprised two separate aftercooler units, while the single recuperator was a large, triple pass Based on laboratory tests and the heat exchanger model, the anticipated effectiveness of both the recuperator and aftercooler units was 80% InstrumentationA range of conventional pressure and temperature instrumentation was installed on the air-cycle demonstrator Air temperature and pressure was logged at inlet and outlet from each heat exchanger, compressor and the The speed of the primary compressor was determined from the speed measurement on the diesel engine control unit, while the cold air unit was equipped with a magnetic speed No air flow measurement was included on the demonstrator Instead, the air flow rate was deduced from the previously obtained turbine performance map using the measurements of turbine pressure ratio and rotational System testingDuring some preliminary tests a heat load was applied and the functionality of the demonstrator plant was Having assessed that it was capable of delivering approximately the required performance, the plant was transported to a Thermo King calorimeter test facility specifically for measuring the performance of transport refrigeration The calorimeter was ideally suited for accurately measuring the refrigeration capacity of the air-cycle demonstrator The calorimeter was operated according to standard ARI 1100-2001; the absolute accuracy was better than 200W and all auxiliary instrumentation was calibrated against appropriate The performance capacity of transport refrigeration units is generally rated at two operating conditions; 0 and −20 °C, and both at an ambient temperature of +30 °C Along with the specified operating conditions of 0 and −20 °C, a further part-load condition at −20 °C was Considering that the air-cycle plant was only intended to demonstrate a concept and that there were concerns about the reliability of the gearbox and the cold air unit thrust bearing, it was decided to operate the plant only as long as was necessary to obtain stabilised measurements at each operating The demonstrator plant operated satisfactorily, allowing sufficient measurements to be obtained at each of the three operating The recorded performance is summarised In total, the unit operated for approximately 3 h during the course of the various While the demonstrator plant operated adequately to allow measurements, some smoke from the oil system breather suggested that the thrust bearing of the CAU was heavily overloaded and would fail, as had been anticipated at the design Testing was concluded in case the bearing failed completely causing the destruction of the entire CAU There was no evidence of any gearbox deterioration during Discussion of measured performanceFrom the calorimeter performance measurements, the primary objective of the project had been A unique air-cycle refrigeration system had been developed within the same physical envelope as the existing Thermo King SL200 refrigeration unit, w
这个东西很难啊 我还有论文没有写呢 在网上都找不到
外文文献有，翻译没有，翻译得靠你自己了，希望能满足你的需要，能帮到你，如果需要直接百度Hi中留言同时贴出问题的链接地址和邮箱地址即可，或者告知其他安全可靠方式提供，多多给点悬赏分吧，急用的话请多选赏点分吧，这样更多的知友才会及时帮到你，我找到也是很花时间的如果需要直接百度Hi中添加我好友，留言同时贴出问题的链接地址和邮箱地址即可，或者告知其他安全可靠方式提供近期好像百度Hi无提示信息留下邮箱地址如dgfgafd的126\q邮箱一六*零****八二*二QQ邮箱
调研文章种类不同，其格式与写法总体上相同，但由于强调的重点和要求不完全一样，因此，每种调研文章格式的写法也有一定的区别。从报告类别看，按调查报告内容的性质可分为5种，下面具体谈谈：反映基本情况的调研报告 由于这类调研报告格式的主体内容涉及面一般都比较宽，因此，这类调研报告格式在写作上往往采用横向结构。如综合反映一个地区的情况，可从经济建设、政治建设、文化建设、社会建设、组织领导等若干方面来撰写；如反映某一方面的情况，则可分为基本概况、主要成绩、突出问题等若干层次。当然，每个大的部分中还可以分为若干个小的问题来写。总结典型经验的调研报告这类调研报告格式的标题一般要反映主题。前言大多采用概述主要成绩、发展变化，并提示基本经验的写法。主体部分需要充分展开，不仅要写具体做法，而且要写切身体会；不仅要写感性认识，而且要上升到理性认识。这两方面是相辅相成、缺一不可的，没有具体做法，体会就是空的；上升到理性认识，感性认识就难以具有广泛的指导意义和推广价值。结尾可以归纳全文、强调主旨，或者指出不足、展望未来。反映新生事物的调研报告这类调研报告格式写作的特殊性上，都缘于一个“新”字，不仅要说明新生事物的孕育、产生和发展过程，而且要指出它的背景。也就是说要指出它是在什么样的环境和条件下产生的，经历了什么样的发展过程，遇到了那些矛盾、困难和问题;不仅要说明它的性质和特点，而且要指明它的作用和意义，包括对其发展前景的预测和未来发展方向的展望。由于新生事物处于不断发展和完善的过程中，往往不够成熟，所以在结尾时，一定要如实指出它需要进一步完善的地方和可能带来的新问题，以便进一步改进和完善。揭露问题的调研报告揭露问题的调研报告格式上，标题往往多采用揭露式的，有的标题甚至还带有一定的感情色彩。主体部分所反映的如果是一个具体事件，一般采用纵向结构;如果反映的是一种倾向和状况，多采用横向结构。在叙述完问题的主要事实后，要写出问题产生的原因、性质和危害程度。结束语可呼吁对问题予以重视或关注，可扼要提出解决办法或处理意见。考察历史事实的调研报告在这类调研报告格式在写作时，事实真相与被歪曲的情况相矛盾的地方，尤其要叙述清楚，要说明事实被歪曲的原因和有关的责任者。写处理意见时，态度要明确，办法要具体。如果问题正在处理和解决中，就要把进展情况写出来;如果尚有阻力，就要把问题尖锐地提出来，敦促有关部门尽快予以解决。
回答 您好，您的问题我已经看到了，正在整理问题答案，请稍后！ 调研文章种类不同，其格式与写法总体上相同，但由于强调的重点和要求不完全一样，因此，每种调研文章格式的写法也有一定的区别。 调查研究门类繁多，表现各异：既有揭示问题调研（也叫专题调研），也有综合调研；既有理论研究调研，也有实际建议调研；既有历史情况调研也有总结经验调研，等等。 从报告类别看，按调查报告内容的性质可分为5种： ①反映情况的调查报告。 ②总结经验的调查报告。 ③宣传新事物的调查报告。 ④揭露问题的调查报告。 ⑤历史事件的调查报告 更多7条
这种是需要有利润形式的，然后列出你的论点和论据调查的结果，起因调查的方式就写完了。
论文调查报告，我觉得我们在写的过程当中写一写调查的目标，然后写一写它的方法和适用度
论文格式要求一、论文篇幅：3000—4500字，论文必须包含200字左右的中、英文摘要及3-4个关键词。二、论文格式：（一）题目、署名及层次格式、文字、字数要求：1、文稿采用A4幅面word文档；中文标题为三号黑体，如有副标题，另起一行，字体为四号宋体；正文为小四号仿宋体；英文字体为Times New Roman，标题字号为三号，字母全部大写；如有副标题，另起一行，首字母大写，正文为小四号字体；文稿应加注页码。2、题目居中，作者署名（五号、仿宋体）及单位信息（五号、仿宋体）标在题目下，（当作者单位不同时，应用1、2……标识区别）。需做作者简介时，可在当页下方划一条横线，在横线下加说明。3、摘要和关键词（五号、黑体）写在题目后、正文前，摘要和关键词的内容部分为五号仿宋体。如下图所示：数字城市化进程王**1 杨**2 张**1（****大学，北京 100001；****研究院，天津 300001）摘 要：**********************************************************************************************************************************************************关键词：*** *** ***4、论文的层次，统一要求采用：1 *******1 *******(占一行或接排。 当接排时，标题后要加标点。一级标题采用四号黑体，二级标题采用小四号黑体，三级标题采用小四号宋体加粗)1 *******1*******（二）文稿和图稿其它要求：1、正确阐述技术内容。名词术语应符合国家有关标准、规范。如所采用的名词术语尚未编定时，可采用各业务部门和科研单位常用的名词术语，不要任意用简称、方言。2、准确使用标点符号，注意：（1）标题、图题、表名后及公式后不用标点；（2）阿拉伯数字的起止（范围）号用“~”，如：“20~30”，“8%~10%”，“0~10oC”3、对正文中的某些问题需加以说明时，可用“呼应注”（也叫脚注），即在所要加注处的右上角标注“①、②……”，同时在本页末留出位置，划一横线与正文隔开，在横线下注明“①、②……”。4、计量单位采用国务院颁发的《中华人民共和国法定计量单位》，一律用拉丁文书写。5、要将中文图表中的英文说明翻译成中文（英文不保留）。6、外文字母写成印刷体，同时注意将正斜体、大小写分清楚。7、数字的书写（统计数、各种计量及图表编号等各种顺序号）均用阿拉伯数字，世纪、年代、月、日和时刻均用阿拉伯数字，并一概用全称。8、表格、公式、样图均要编号，每篇论文加注流水号，例如：图1、图2，表1、表2，公式⑴、公式⑵。9、照片要求清晰、层次分明，本论文集为非彩印书，请尽量用黑白照片，应尽量避免以颜色做区分的柱状图、线条图等。墨线图要大小适当，图线要规整，文字及数字应采用六号字体。照片、图稿等电子文件需备份一份随稿件一并提交。10、稿件为中文的英文摘要或稿件为英文的中文摘要，要放在正文后，参考文献前。包括题目、作者信息及摘要、关键词。格式如下：PAPER TITLEWang **1 Yang **1 Zhang **2（**** College，北京 100001；**** Academe，天津 300001）Abstract:**********************************************************************************************************************************************************Keywords： *** *** ***11、参考文献的项目要列全，格式如下：[1]*****主编 建筑结构（文献名称） 北京（出版城市）：*****出版社，2003（出版年限）[2]*****主编城市规划上海：*****出版社， 2001 （三）文稿最后应有附件页，注明作者个人信息，内容见下表：作者基本情况表姓名 性别 职称 工作单位 职务 联系电话 （固定电话请注明本地区号） 传真 通信地址 邮编 E－mail
论文的写作一般包括题目、署名、摘要、关键词、引言、材料方法、实验结果、讨论、结论、参考文献、致谢、附录等部分。
课题论文的写法跟我们平常的论文写法大致是相同的，但是课题必须要有研究性，要有数据作为基础
1、必须包含标题、摘要、关键词、正文四个部分；如有引用他人文章的还要加注参考文献，具体顺序如下： 1） 标题 2） 摘要 3） 关键词 4） 正文 2、标题的写法 （1）标题。建议采用规范化的标题格式，基本格式为 “关于××××的调查报告”、“××××调查”等，如《关于××公司人力资源管理情况调查》；也可采用正副标题结合式，正题陈述调查报告的主要结论或提出中心问题，副题标明调查的对象、范围、问题，如《企业 发展重在制度创新――××公司管理制度建设实践思考》等。3、摘要的写法 摘要包括以下三方面内容：第一，简要说明调查目的，即简要说明调查的原因；第二，简要介绍调查的对象和调查内容。包括调查时间、地点、对象、范围、调查要点及所要解答的问题；第三，简要介绍调查研究的方法。介绍调查研究的方法，有助于使确信调查结果的 可靠性，并说明选用该方法的原因。3、关键词的写法关键词是从论文标题、内容提要或正文中提取的、能表现该论文主题的、具有实质意义 的词语，通常不超过4个，中间空1个字符距离。4、正文的写法 正文一般分前言、主体、结尾三部分。1）前言。有几种写法：第一种是写明调查的起因或目的、时间和地点、对象或范围、经过与方法，以及人员组成等调查本身的情况，从中引出中心问题或基本结论来；第二种是写明调查对象的历史背景、大致发展经过、现实状况、主要成绩、突出问题等基本情况，进而提出中心问题或主要观点来；第三种是开门见山，直接概括出调查的结果，如肯定做法、指 出问题、提示影响、说明中心内容等。前言起到画龙点睛的作用，要精练概括，直切主题。2）主体。这是调查报告最主要的部分，这部分详述调查研究的基本情况、做法、经验， 以及分析调查研究所得材料中得出的各种具体认识、观点和基本结论。3）结尾。结尾的写法也比较多，可以提出解决问题的方法、对策或下一步改进工作的建议；或总结全文的主要观点，进一步深化主题；或提出问题，引发人们的进一步思考；或展 望前景，发出鼓舞和号召。我要调查网，让调查更简单方便！