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提供一些英语专业翻译方向的论文题目，供参考。 商务合同英汉互译技巧英文品牌汉译知识对于翻译的重要性中英文化差异及其对英汉互译的消极影响英语广告中修辞手法的应用及其翻译 <<红楼梦>>金陵判词两种译文的比较及评析从红楼梦诗词翻译看翻译中的文化补偿关于李后主“虞美人”的3种英译本的鉴赏跨文化交际与商标翻译中式菜肴的命名与翻译浅谈英语电影片名的翻译英文电影片名的翻译策略英文化妆品广告之美学翻译数字在中西文化中的内涵差异及数字习语翻译初探浅析原语文本在目标语文本中文体的适应性英语习用语翻译中的等效性研究论语境在英汉翻译中的作用浅析英语动画片翻译的基本原则中英服饰广告的翻译论英汉翻译中语篇连贯的重要性论译者的风格与译风经济英语中的隐喻及其翻译从翻译的美学角度浅析旅游资料的中英译
学术堂提供了十五个好写的英语翻译论文题目，供大家参考：1、谈英语谚语的翻译2、谈英语幽默的翻译3、英语汉译技巧初探4、地方名胜古迹汉译英5、翻译中常见错误分析6、中英思维方式的差异对翻译的影响7、会话含义的推导与翻译8、词汇的文化内涵与翻译9、语境在翻译中的作用10、翻译技巧探索11、商标词翻译12、广告语言的翻译13、论英汉互译中的语义等值问题14、英汉文化差异对翻译的影响15、英汉谚语的理解和翻译
翻译方向的.英语习语方面的.觉得这方面的很有趣,并且材料也很好搜集,写作角度也很广.在写作过程中,无论是从中西方文化方面还是从语言方面确实都学到不少东西. 每个人的兴趣不一样,不知道你会不会对这方面的感兴趣.“论电影片名的翻译”，这个题目比较好写，答辩的时候老师听的也比较有兴趣，资料也不难找。楼主可以试试。合同翻译中的经济、法律术语翻译如果以后要做翻译工作，也非常实用
testing of an air-cycle refrigeration system for road transportAbstractThe environmental attractions of air-cycle refrigeration are considerable. 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 unit. This unique plant operated satisfactorily, delivering sustainable cooling for refrigerated trailers using a completely natural and safe working fluid. 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 high. 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 : 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 effectiveness1. IntroductionThe current legislative pressure on conventional refrigerants is well known. 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 option. Consequently, as soon as alternative systems, such as non-HFC refrigerants or air-cycle systems are considered, the issue of increased energy consumption arises 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 transport. 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 transport. NormalAir Garrett developed and commercialised an air-cycle air conditioning pack that was fitted to high speed trains in Germany in the 90s. As part of an European funded programme, a range of applications for air-cycle refrigeration were investigated and several demonstrator plants were constructed. 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 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 packaging. 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 fluid. 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 manufacture. 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 optimal. In practical terms, this meant using the chassis and panels for an existing SL200 unit along with the standard diesel engine and circulation fans. 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 here. For anything other than the smallest flow rates, the most efficient machines available for the necessary compression and expansion processes are turbomachines. Considerations for the selection of turbomachinery for air-cycle refrigeration systems have been presented and discussed by Spence et al. [3]. a typical configuration of an air-cycle system, which is sometimes called the ‘boot-strap’ configuration. 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 compressor. Instead, the work recovered by the turbine during expansion is utilised in the secondary compressor. The two-stage compression also permits intercooling, which enhances the overall efficiency of the compression process. An ‘open system’ where the cold air is ejected directly into the cold space, removing the need for a heat exchanger in the cold space. 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 developed. The compression and expansion processes were modelled using appropriate values of isentropic efficiency, as defined in heat exchange processes were modelled using values of heat exchanger effectiveness as defined in The model also made allowance for heat exchanger pressure drop. 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 outlet. 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 unity. 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 cycle. However,illustrates, there is a broad range of pressure ratio and duty over which the system can be operated with only moderate variation of class of turbomachinery suitable for the demonstrator plant required speeds of around 50 000 rev/min. To simplify the mechanical arrangement and avoid the need for a high-speed electric motor, the two-stage compression system shown was adopted. 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 exchangers. 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 two-stage system in incorporated an intercooler between the two compression stages. By dispensing with the intercooler and its associated duct work a larger aftercooler could be accommodated with improved effectiveness and reduced pressure loss. Analysis suggested that the improved performance from a larger aftercooler could compensate for the loss of the the impact of the recuperator effectiveness on the COP of the plant, which is clearly more significant than that of the other heat exchangers. As well as boosting cycle efficiency, increased recuperator effectiveness also moves the peak COP to a lower overall system pressure ratio. The impact of pressure loss in the recuperator is the same as for the intercooler and aftercooler shown in. The model did not distinguish between pressure losses in different locations; it was only the sum of the pressure losses that was significant. 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 specific cooling capacity of the air-cycle increases with system pressure ratio. Consequently, if a higher system pressure ratio was used the required cooling duty could be achieved with a smaller flow rate of air. shows the mass flow rate of air required to deliver 7,5 kW of cooling power for varying system pressure 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 rotors. and were based on efficiencies of 81 and 85% for compression and expansion, respectively. While such efficiencies are attainable with optimised designs, they would not be realised using compromised turbocharger components. For the design of the demonstrator plant efficiencies of 78 and 80% were assumed to be realistically attainable for compression and turbomachinery efficiencies corresponded to higher cycle pressure ratios and flow rates in order to achieve the target cooling duty. The cycle design point was also compromised to help heat exchanger performance. The pressure losses in duct work and heat exchangers increased in proportion with the square of flow velocity. Selecting a higher cycle pressure ratio corresponded to a lower mass flow rate and also increased density at inlet to the aftercooler heat exchanger. 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 exchanger. 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 space. 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 0,41. The system pressure ratio at the design point was 2,14 and the corresponding mass flow rate of air was 0,278 kg/ 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 reduced. Also, operating at part-load corresponded to lower flow velocities and anticipated improvements in heat exchanger performance. 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 plant. 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 the thermodynamic model, the pressure ratio for the primary compressor was 1,70. The centrifugal compressor required a shaft speed of around 55 000 rev/min. Other alternatives were evaluated for primary compression with the aim of obtaining a suitable device that operated at a lower speed. Other commercially available devices such as Roots blowers and rotary piston blowers were all excluded on the basis of poor one-off gearbox was designed and manufactured as part of the project to step-up the engine shaft speed to around 55 000 rev/min. 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 unit. 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 installation. Consequently, both the secondary compressor and the turbine stage were specially chosen and developed to deliver suitable turbochargers use plain oil fed journal bearings, which are low-cost, reliable and provide effective damping of shaft vibrations. However, plain bearings dissipate a substantial amount of shaft power through viscous losses in the oil films. 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 power. Also, the clearances in plain bearings require larger blade tip clearances for both the compressor and the turbine with a consequential efficiency penalty. Given the pressurised inlet to the secondary compressor, the limited thrust capacity of the plain bearing arrangement was also a concern. A CAU utilising high-speed ball bearings, or air bearings, was identified as a preferable arrangement to plain bearings. Benefits would include greatly reduced bearing power losses, reduced turbomachinery tip clearance losses and increased thrust load capacity. However, adequate resources were not available to design a special one-off high speed ball bearing system. Consequently, a standard turbocharger plain bearing system was secondary compressor stage was a standard turbocharger compressor selected for a pressure ratio of 1,264. Secondary compressor and turbine selection were linked because of the requirement to balance power and match the speed. Since most commercial turbines are sized for high temperature (and consequently low density) air at inlet, a special turbine stage was developed for the application. Cost considerations precluded the manufacture of a custom turbine rotor, so a commercially available rotor was used. 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 velocity. The exhaust diffuser exited into a specially designed exhaust performance of the turbine stage was measured before the unit was incorporated into the complete demonstrator plant. The peak efficiency of the turbine was established at 81%.5. 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 exchangers. 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 cost. 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 different tube and fin heat exchangers were tested and used to validate a computational model. Once validated, the model was used to assess a wide range of possible heat exchanger configurations that could fit within the Thermo King SL200 chassis. 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 challenging. 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 chassis. The final selection comprised two separate aftercooler units, while the single recuperator was a large, triple pass unit. Based on laboratory tests and the heat exchanger model, the anticipated effectiveness of both the recuperator and aftercooler units was 80%.6. InstrumentationA range of conventional pressure and temperature instrumentation was installed on the air-cycle demonstrator plant. Air temperature and pressure was logged at inlet and outlet from each heat exchanger, compressor and the turbine. 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 counter. No air flow measurement was included on the demonstrator plant. 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 established. 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 units. The calorimeter was ideally suited for accurately measuring the refrigeration capacity of the air-cycle demonstrator plant. 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 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 assessed. 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 point. The demonstrator plant operated satisfactorily, allowing sufficient measurements to be obtained at each of the three operating conditions. The recorded performance is summarised .In total, the unit operated for approximately 3 h during the course of the various tests. 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 stage. 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 achieved. A unique air-cycle refrigeration system had been developed within the same physical envelope as the existing Thermo King SL200 refrigeration unit, w
title是正常的用法
illustrated by the case of Chengduillustrated by the example of Chengdu 也可以。然后其实很多英文教材书名都会说： An Asia Perspective,你觉得你这里用A Chengdu Perspective如何呢。就是从成都的角度来分析。
我一般用这个 title 希望采纳 谢谢
topic 最好，比较学术
暖通专业在计算 方法 、程序编制和工程应用几方面都取得了显著成绩。下面是由我整理的暖通专业技术论文，谢谢你的阅读。
暖通空调技术与节能
摘要:随着人们生活水平的日益提高,人们生活的节奏逐渐加快及心理压力的不断增大,使得人们的工作生活环境应该予以重视。而在人们的工作生活环境中倡导环保和节能的生活方式越来越重要。本文主要是对暖通空调技术与节能进行分析。
关键词:暖通空调 技术 节能
2009年9月22日,国家主席胡锦涛在联合国气候变化峰会开幕式上发表题为《携手应对气候变化挑战――在联合国气候变化峰会开幕式上的讲话》的重要讲话,郑重承诺今后中国将进一步把应对气候变化纳入经济社会发展规划,并继续采取强有力的 措施 :一是加强节能、提高能效工作;二是大力发展可再生能源和核能;三是大力增加森林碳汇;四是大力发展绿色经济,积极发展低碳经济和循环经济,研发和推广气候友好技术。明确提出了建设生态文明的重大战略任务,强调要坚持节约资源和保护环境的基本国策,坚持走可持续发展道路,在加快建设资源节约型国家。可见节能对于一个国家乃至世界时是多么的重要。本文主要从节能方面浅谈暖通空调技术。
1.室内设计参数
常规情况下,在冬季供暖时,室内计算温度每降低1℃,能耗将减少约5%～10%;在夏季供冷时,室内计算温度每升高1℃,能耗将减少约8%～10%。室内设计参数必须在规定的参数范围内取值。近几年,低温地板辐射采暖系统已经取代散热器采暖,之所以采用这种方式,主要是因为这种方式具有能耗小、舒适性高、容易分户计量、不占用房间使用面积等优点。
2.采暖设计
采暖空调热负荷为12650KW,热指标为。热源由城市热网供给,一次水供回水温度为95/70℃,经热交换后,高温二次水供回水温度为85/60℃,供采暖系统及空气、新风处理机组使用。各类机房、自行车库等设5-8℃的值班采暖,人防掩蔽体采暖设计温度为18℃,厕所为16℃;低温二次水供回水温度为60/50℃,供风机盘管和汽车坡道化雪系统使用,或者化雪系统由于什么原因没有使用。为保证一层室内良好的温度环境,抵挡大门的冷风侵入,在各大门入口处均设置了热空气幕。
以空气为热泵的热源在寒冷地区进行采暖是当前研究的 热点 。因为它和以往的燃煤、燃油、直接用电等取暖方式比较的话,在环保、节能、安全使用,甚至经济等方面有突出的优点,其可推广性也超过了水源、地源热泵。
地板采暖的空气热泵机组容量的选择
机组容量(W)=当地建筑采暖设计负荷()×用户采暖的建筑面积()÷(1-)×
室外机最好安装在冬季主导风的背风面,应该设置遮雪蓬,机组如果安装在平台上,则底面应抬高至少20cm,以免化霜结冻,机组吸风口距障碍物至少25cm,双机之间距离至少20cm。
地板下埋管的设计
空气热泵作为热源时,供水温度或供回水平均温度应尽可能设计得低些,以使机组效率尽可能高,又由于工程实践证明本机组的供回水温差较少仅2℃-3℃,所以,选择地下埋管时可参照“低温热水地板辐射供暖应用技术规程”( DBJ/T01-49-2000)附录 E-1至 E-3中平均水温35℃一栏,按照地板所需散热量选择间距,然后,将管道直径放大到Φ20/16成间距缩小一档即可。
3.风系统设计
集中空调系统的排风热回收
一直以来,业内人士只是从经济方面的角度来衡量热回收装置的利弊,而环保与节能则被忽视。当今,业内人士考虑的角度有所转变,现在从环保和节能这个角度来衡量热回收装置的利弊。
空调区域排风中的热能量是非常多的,如果把这些热能量加以回收利用,那么环保和节能定会实现。如果新风和排风采用专门独立的管道输送,那么有利于集中热回收装置的设置。新风和排风采用热回收装置进行湿热或者全热交换,节能效果非常明显的表现出来。
空调风系统
(1)有资料显示,以我国南方地区为例,夏季室内设计温度如果每降低1℃或冬季设计温度每升高1℃,其工程投资将增加6%,能耗将增加8%。该数据很明显地说明,适当提高夏季以及降低冬季的室内空气温度,都将起到显著的节能效果。与此同时,为保证室内空气质量以及人们对新鲜空气的需要,现行《采暖通风与空气调节设计规范》对最小新风量作出明确规定,要求建筑满足国家现行有关卫生标准。研究表明,加大新风量能够在一定程度上解决室内空气质量问题,但增加了空调能耗。新风定值必须按照规范来确定,因为新风量对于能耗和人体健康有着非常重要的作用,如果人员密度较大时,新风的供应按人员的密度来进行的话是非常不经济的。我国建筑采用了新风需求控制(检测室内CO2浓度),值得注意的是:新风量变化,排风量随着也发生变化,否则造成负压,可能会适得其反。
(2)暖通设计师对于规范中新风量的规定表示赞同。暖通设计师认为,在目前中央空调清洗不够规范的背景下,加大新风量是必要的。不过,对于室内设计温度的要求,他们却持保留态度。业内人士有这样的一个说法:“如果说节能像一棵树,有很多枝杈可以作为思路,那么,业主方的意见更像那个根。他们的态度,将成为决定暖通专业乃至建筑节能的根本性因素。”业内人士表示,建设方的意见非常重要。
要想增加新风量或者增强风机盘管处理室内回风的能力,风机盘管加新风的新风口应单独或布置在盘管出风口的旁边,而不应该布置在盘管回风吸入口。
(3)房间面积或空间较大、人员较多或有必要集中进行温度控制的空气调节区,其空气调节风系统宜采用全空气空调系统,不宜采用风机盘管系统,以利于集中处理、调节,发挥有利因素,弥补之前产生的问题。
(4)建筑空间高度大于或等于10m、且体积大于时,宜采用分层空调系统。与全室性空调方式比,分层空调系统夏季可以节能30%左右,但是冬季并不节能。通常设计时,夏季的气流组织为喷口侧送,下回风,高大空间上部排风;而冬季一般在底层设置地板辐射或地板送风供暖系统,也可将上部过热的空气通过风道送至房间下部。
(5)多个空气调节区合用1个空气调节风系统,各区负荷变化较大、低负荷运行时间较长,且需要分别调节室内温度,在经济条件允许时,宜采用全空气变风量空气调节系统。设计时应注意:要求采用风机调速改变系统风量,而不能采用恒速风机而改变系统阻力调节;其次,应采取保证最小新风量的措施,避免因送风量减少,造成新风量减少而不满足卫生要求的后果;再者,调节末端送风口风量时,推荐采用串联式风机驱动型末端装置以保证室内的气流分布。
(6)在某些情况下,像屋顶传热量较大、吊顶内发热量较大、吊顶空间较大(此时的吊顶至楼板底的高度超过),如果采用吊顶内回风,导致空调区域增大、空调耗能上升,这样非常不利于节能。所以对于建筑顶层或者吊顶上部有较大热量、吊顶空间较高时,直接从吊顶回风是不合理的。
4.围护结构
北京市建筑设计研究院原院长、北京市建筑设计研究院顾问总工程师吴德绳认为,暖通专业既然是建筑节能的支柱力量,因此,目光不仅要盯住如何优化暖通空调系统设计,更应该有所转移,在围护结构设计方面重点考虑。
围护结构在节能工作中,扮演着愈来愈重要的角色。所谓围护结构节能,通常是指通过改善建筑物围护结构的热工性能,使得建筑在夏季隔绝室外热量进入室内,冬季防止室内热量泄出室外,以保持室内尽可能接近舒适温度,减少通过辅助设备来达到合理舒适室温的负荷,并最终达到节能的目的,如通过采暖、制冷设备达到节能。
传统住宅建筑的围护结构是普通黏土砖,简单架空屋面和单层玻璃钢窗,它们的传热系数分别为、和。而“节能住宅”的围护结构中外墙和屋面采取了保温措施,外窗采用中空塑钢窗或断热中空铝合金窗,它们的传热系数分别为 、和,使围护结构的节能贡献约占25%。采用能效比高的采暖、空调设备(按照国家标准,房间空调器的能效比:制冷>,采暖>),使采暖、空调设备的节能贡献约占25%,两者相加总体达到节能50%的目标。
据介绍,围护结构的节能设计应该从墙体、窗户、屋面等三个方面考虑。对于设计人员而言,如何处理建筑玻璃幕墙的问题,在业内一直存在很大争议。普通玻璃幕墙是建筑节能不能实现的因素之一。统计数据表明,夏季通过玻璃窗的日照热可占制冷机最大负荷的30%,冬季单层玻璃的热损失约可占锅炉负荷的20%。窗体节能技术主要从减少渗透量、减少传热量、减少太阳辐射能三个方面考虑。另外,在保证室内采光良好的前提下,合理确定窗墙比十分重要。当窗墙面积比超过50%时,负荷将明显增加。不仅是外围护结构,内围护结构在设计中同样重要。暖通设计师要比普通建筑师更懂得建筑节能的途径,所以暖通设计师和普通建筑师多进行沟通效果才会更好。
5.实现节能
暖通空调的设计师在方案设计时,首先应深入了解业主的能源状况以及对空调的使用状况和是否有余热、废气等条件,然后对各种能源方案进行合理综合的对比。设计师在设计时应考虑的重点是:如何利用可再生能源和低品位能源。
暖通设计师在设计阶段完成基础工作之后,最关键的就是环保和节能的实现,而环保和节能的实现是通过综合利用各种先进技术、利用各种可再生资源来实现的。
利用自然条件来满足人们对于室内温度的需求,这是最理想的方式。现在通过各种设备实现对温度的调节,只不过是对人们的过错进行补救。冷热源是设计师最关注的一点,因为其能耗往往能占空调系统总能耗的50%左右。
地源热泵系统就是在这种形势下快速发展起来的,它利用地下恒温层土壤热显著提高空调系统效率。同时,采用新能源利用的供给方式,实现冷、热、电三联供;利用燃气、汽、电力能量转换的原理联合循环使用,将工业流程最尾端的余热收集起来,用于供冷系统空调冷冻水和供热系统的生活热水,这样,能源的利用率可提高至70%～80%左右。这些都给暖通空调设计师提供了广泛的节能设计思路。
6. 总结
随着全球逐渐变暖这种现象的出现,空调现在已经是人们生活中不可或缺的一部分,它使人们工作生活更加舒适,人们对于空调也有了一定的依赖性。然而,环保和节能是当今非常重要的问题,因此,在暖通空调设计方面,暖通空调的环保和节能是目前空调技术方面发展的方向,也就是说,城市供热环保和节能是目前亟须加强和可持续发展的问题。
参考文献:
[1] 赵君利. 暖通空调节能从设计开始.中国建设报,2010,(03).
[2] 胡锦涛活动报道集,2009,(09)
[3] 刘金瑶,李婉茹,刘鹏华. 浅谈暖通空调的节能.暖通空调,2008,(04).
[4] 张莉,李尧,朱玉明.暖通空调节能设计分析.山西建筑,2010,(09).
[5]__荣.建筑工程的暖通空调设计.施工技术与设计,2008,(07).
[6] 万蓉. 基于气候的采暖空调耗能及室外计算参数研究.西安建筑科技大学, 2009,(08).
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建筑空调制冷系统施工中的管理摘要：如何就对随着科技的进步和人民生活水平的提高，人们对生活和生产环境的不断提高的同时，提高制冷系统的性能稳定，笔者就此提出了在施工阶段应注意的一些事项。关键词：空调制冷系统，施工，注意事项，管理要点制冷工程的施工质量好坏对制冷系统调试的成功与否关系极大。施工时支立管，干管甩口不准，支架托架失效，形成倒坡，导致窝风，影响水流循环，从而使水系统内部某些位置水温升高，甚至死水不畅，有时还产生水击声响，造成这些人为的施工缺陷后，调试时费时费力，甚至无法弥补，而改造不仅更麻烦，还会造成新的浪费。其次，在南方热带地区，空调系统的保温工艺问题是许多单位常年来十分头痛的问题，也是影响业主形象的大事。随着科技的进步和人民生活水平的提高，人们对生活和生产环境的要求也不断提高。空调系统作为智能建筑的重要组成部分，是楼宇自动化系统的主要监控对象，也是建筑智能化系统主要的管理内容之一。一、系统设计及其对调试效果的影响制冷工程的设计质量和施工质量对制冷效果影响极大，设计考虑不周，系统型式选择不当，设备部件本身的缺陷以及施工工序和施工质量的差异，施工材质和施工队伍的把关等都会给制冷系统初调和运行管理带来麻烦。制冷系统目前基本上都采用机械循环系统。这种系统的环路，支立管形成闭合的冷水循环管网。设计者应充分认识这一水力系统的特点，进行精心设计，应正确选择管网型式和系统划分，同时还必须把冷水流量按计算负载分到各用户，或各末端设备中去，这一点最为重要。设计时处理得好，系统运行时就容易调试；处理得不好，将成为系统水力平衡的先天性缺陷。与此同时，设计中还必须采取有效措施排除系统内的空气，否则也会造成冷热不均的现象。二、空调制冷系统在结构施工过程中应注意哪些空调专业负责现场施工的技术人员；要同空调专业设计，结构专业设计一起，根据设备生产厂家提供的技术资料，确定各种设备如制冷机组、各种水泵、冷却塔、膨胀水箱以及其他设备的基础处理方案，向工地的土建专业提供设备基础图，冷却塔要提供预埋件布置图，争取设备基础处理和土建结构同步施工。因制冷机组属大型设备，所以要根据土建专业的建筑和结构图纸，结合结构预留的设备吊装孔洞的位置，确定合理的大型没备运输通道的走向。以书面文字形式通知土建专业，在运输通道所经过路段的隔墙暂时不要砌筑。在垂直吊装子L洞上方的结构梁内。预留一个或几个能满足垂直运输大型设备的吊钩(要画图，并提出具体要求)。根据设备生产厂家和专业设计人员提供的资料，计算出大型设备在运输时，包括设备本身及垫木、滚杆需要占用的空间高度、宽度和长度。然后通知工地总包，由总包出面组织各安装专业的协调会。在运输通道内，凡是设备运输时所占用空间高度范围内的所有管道，包括给排水干管、电气专业的电缆桥架，采暖系统的干管，通风专业的各种风管、空调专业的干管以及其他专业的管道，都要做梯形翻弯处理，无压力的排水管道，要适当调整走向。躲开设备运输所占用的高度，所有管路的调整由土建总包确定方案，经过建设单位、工程监理和设计人员认可以后。各专业在管道安装时必须严格执行。需要说明的是管路的翻弯调整必须在施工前期处理好。如果要等到工程后朗，各专业管道通水或穿完电线以后再改动，困难很大。如果前朗不安装。等设备运输完成以后，再安装管道，就等于封堵了运输通道，这一方案也不可取，要考虑到日后设备的更换，设备通道的重复利用。结构施工期间，空调专业施工人员要按照专业施工图纸预留空调管道的楼板洞和过墙洞，一次结构施工完成以后，空调专业开始安装主立管和水平干管；如果条件具备，可分层分段分系统进行打压试水和保温，在立管井和吊顶内安装手动或电控阀门时，要考虑阀门的位置，手动开启的方向。要有一定的安装操作空间，要方便口后的维修和操作。三、项目经理如何重点把握管理工作要点了解设计意图、设计内容、建筑构造特点、设备技术性能、工艺流程及建设方的要求等。首先粗审图纸，搞清分部分项工程的数量和大致内容，诸如：风系统、水系统的工艺布局，建筑工程的形式、层数、楼梯和电梯的位置、数量、平面布局状况以及各层的层高，装修工程中墙、顶、地、门窗、击水排水的基本要求，防水工程情况等。细审图纸，掌握设计要求的尺寸。诸如风管各部断面尺寸及长度，水管管径及长度，制冷主机及制冷机房其他设备的相关尺寸；空调末端设备的规格、数量、安装部位及空调机房、新风机房的平面尺寸与高度等；还应了解各方面的技术要求、消防与电的具体布置及与土建工程的关系等；同时核对各专业图纸中所述相同部位、相同内容的统一性，掌握其是否存在矛盾和误差。结合设计情况、学习相应的标准图集、施工验收规范、质量验评标准和有关技术规定，在此基础上，形成项目经理自己对工程施工的总体印象和施工组织设想。这部分工作是创造性的，其中心是要考虑设计和规范要求是否可以得到施工方面的满足；自有的施工力量、施工队伍和技术、装备水平，是否及如何达到要求；设计要求与施工现实差距较大或施工操作困难的，在满足设计意图和质量要求的前提下，可否做出一向有利于施工组织、加快进度的变更；根据上述各项，施：正中应考虑采取哪些主要的技术、组织、供应、质量和安全措施。综合以上工作，对审查出的问题、不明的疑问及施工的合理化建议做出归纳总结，提交技术部门向业主和设计人员反映，尽量把问题解决在开工之前，为工程的施工组织提供尽可能准确、完整的依据。四、多于施工班组及相关人员交底及管理原则项目经理向施工班组及相关人员进行施工组织设计、计划和技术交底，目的是把拟建工程的设计内容、施工计划、进度、技术与质量标准、安全和消防要求等事项详尽地向施工人员说明，以保证严格地按照设计图纸、施工组织设计、安全操作规程和施工验收规范顺利进行施工。交底的主要内容有：计划交底，技术质量交底，定额交底，安全生产交底和各项管理制度交底。技术交底是指工程开工前，由各级技术负责人将有关工程施工的各项技术要求逐级向下贯彻，直到基层。其目的是使参与施工任务的技术人员和工人明确所担负工程任务的特点、技术要求、施工工艺等，做到心中有数，保证施工顺利进行。因此，技术交底是施工技术准备的必要环节。技术交底的注意事项：技术交底必须在该交底对应项目施工前进行，并应为施工留出足够的准备时间。技术交底不得后补；技术交底应以书面形式进行，并辅以口头讲解。交底人和被交底人应履行交接签字手续。技术交底及时归档；技术交底应根据施工过程的变化，及时补充新内容。施工方案、方法改变时也要及时进行重新交底；分包单位应负责其分包范围内技术交底资料的收集整理，并应在规定时间内向总包单位移交。总包单位负责对各分包单位技术交底工作进行监督检查。总结：在施工管理中要加强对施工单位的严格科学监理，认真控制每一工序，努力减少或消除施工缺陷。参考文献：[1]陈天豪.探讨空调制冷系统安装施工技术[J].城市建设与商业网站,2009,(27)[2]邵宗义.空调系统设计与施工解析[J].中国建设信息供热制冷，2008（04）[3]陈金鹏.空调制冷系统的施工及注意事项[J].制冷空调与电力机械，2009（03）[4]王淑敏.空调制冷系统设计与施工[J].暖通空调，2006（05）[5]周成愚.空调系统设计和施工中的几个问题[J].空调制冷系统设计与施工，2003（05）
本文是给那些正在搞电气自动化毕业设计和写电气自动化毕业论文的朋友提供一个电气自动化毕业设计的选题。1、加速中小型老旧变压器更新换代的节电降耗2、会议电视系统应用探讨3、关于住宅电气设计的探讨4、高压配电设备及其运行5、高速单凭机硬件关键参数设计概论6、照明电路发生故障的原因及排除方法7、代替小型PLC的单片控制器8、固态继电器及在应用中的一些问题探讨9、断线保护装置对人身和设备的保护10、发电机组和大型电动机测温装置的测试和改进11、对当前汽轮发电机在线监测应用的初步分析和建议12、对闭环运行方式配电自动化系统的探讨13、电气设备热故障分析及对策14、电气设备机房的电涌防护15、电锅炉房的电气设计16、大学图书馆电气设计17、配电自动化系统中的通信系统电气化毕业设计 电气自动化毕业论文选题21、人工智能在电气传动中应用的进展2、电气改造工程施工组织设计3、真空技术4、用于基本驱动系统的高性能比变频器SinamicsG1105、脉冲功率装置能源计算机控制技术6、交流调速的功率控制技术7、国外永磁传动技术的新发展8、变频器制动新思路、新方法9、变频器在锅炉给粉器上的应用10、变频器在运行过程中存在的问题及其对策11、变频器应用中的干扰及其抑制12、新世界多层住宅配电设计13、民用建筑应急照明的解析14、交流参数稳压电源及其对谐波的抑制15、建筑防雷综合述论16、建筑电气在住宅室内环境设计中的功能与应用电气化毕业论文 电气自动化论文 电气工程毕业设计 电子电气毕业论文31、GIS在交通中的应用与发展2、能提供低成本风电的新型风力机3、风力发电机组齿轮箱监控设施4、风力发电机组齿轮箱概述5、暖通空调系统故障预测维护与设备管理自动化6、计算机监控系统在化学水汽品质监督中的应用7、机电一体化智能大流量电动执行机构的研究8、机电一体化智能大流量电动执行机构9、富有感染力的灯光照明10、油井高含水计量技术探讨11、基于MSP430单凭机的实时多任务操作系统 12、电机转子动平衡半自动去中系统的研制13、中国电源产业的发展与分析14、运动控制新技术15、一种智能型伺服放大器的设计16、新进制造技术的新发展17、无轴承电机研究和应用前景18、我国机械制造业管理信息化特点及发展趋势19、数控化发展趋势——智能化数控系统20、柔性制造系统的关键技术及发展趋势
我是平院毕业的，只不过我和你不一个院，我是新传的。当时我们院的情况是给出了几个题目，让我们从中选择。我觉得你们院到时候也会这样啊，不着急的。最重要的是和你的导师做好沟通。有不懂的及时问他，及时和他联系。答辩很简单的，不难，很多问题都是在你论文中找的。祝你好运。另外多多珍惜你的大学生活，毕业了以后真的很怀念的。。。
英语翻译论文题目
写英语翻译的论文需要写哪些内容呢?选什么样的题目合适?下面是我为大家收集的关于英语翻译论文题目，欢迎大家阅读!
1、谈英语谚语的翻译
2、谈英语幽默的翻译
3、英语汉译技巧初探
4、地方名胜古迹汉译英
5、翻译中常见错误分析
6、中英思维方式的差异对翻译的影响
7、会话含义的推导与翻译
8、词汇的文化内涵与翻译
9、语境在翻译中的作用
10、翻译技巧探索
11、商标词翻译
12、广告语言的翻译
13、论英汉互译中的语义等值问题
14、英汉文化差异对翻译的影响
15、英汉谚语的理解和翻译
16、浅谈颜色词在英语中的翻译
17、中西文化差异与翻译障碍
18、英语比喻性词语中文化内涵及翻译
19、英语意义否定表现法及其汉译
20、浅谈新闻标题的翻译
21、互文性理论下的电影片名翻译
22、从唐诗《春望》英译比较看译者主体性
23、功能对等理论在英文电影字幕翻译中的应用-以《肖申克的救赎》为个案
24、语篇翻译中的衔接与连贯
25、从关联理论视角看汉语习语的英译
26、从目的论角度看新闻标题英汉翻译
27、目的论关照下的汉语标语翻译
28、影视翻译的特点及技巧-阿甘正传个案研究
29、The Characteristics of Athletic English and Its Translation体育英语的特点及翻译
30、Chinese Reduplicated Words and their Translation into English 汉语叠词及其英译
31、Non-Correspondence in English-Chinese Translation of Color Words中英文翻译中颜色词的非对应
32、On the Cultural Signification of Animal Idioms and Translation 动物俚语文化含义与翻译
33、Foreignizing and Domesticating Translations in Cross-cultural Vision跨文化视野中的异化和归化翻译
34、The Loss of Affective Meaning in Translation ―from the Perspective of Cultural Differences 从文化差异的角度看翻译中情感意义的丢失
35、On the Explicitness and Implicitness of Conjunctions in English-Chinese Translation Process 论连词再英汉翻译中的显性和隐性存在
36、Approaching Domestication and Foreignization in Translation from a Functional Perspective 从功能翻译角度看归化与异化
37、Conversion of Part of Speech in English-Chinese Translation 英译汉中词类的转换
38、The Transfer of Culture Image and of English and Chinese Idioms in Translating 论英汉习语翻译中的文化意象的转化 VI 旅游英语方向的选题
39、科技汉英翻译中的.修辞现象述评 ( An Overview of Rhetoric in Scientific English Translation )
40、科技英汉翻译中的虚实互化现象微探 ( Research on the Change from Abstractness to Concreteness in Scientific Translation )
41、翻译方法个案研究?如?“从海明威的短篇小说《一个 干净、明亮的地方》看简洁句的翻译”?
42、两个译本比较研究 ?或某 个译本翻译评论?
43、某个著名翻译家翻译方法或翻译风格研究
44、英汉习语翻译方法研究
45、广告翻译策略 研究
46、Culture Differences and Translation of English &Chinese Idioms
47、浅析应用文体之翻译
48、烹饪英语 翻译探微
49、科技英语翻译方法例析
50、中式菜谱的英译
51、汉语颜色 词的英译
52、福克勒小说的英译
53、英语俚语的汉译
54、论英语委婉 语的差异和翻译对策
55、实用文体翻译中的语 言、文化透视?结合语言学、跨文化交际等相关内容分析影响实 用文体翻译的因素?
56、关于对外交流翻译中不足 的反思?如?电影名的误译?旅游翻译的误译及其他。?
57、对某一翻译的理解与 探讨?如“信、达、雅”的探讨与新解?等等
58、中国特色词汇及其英译
59、中英数字文化对比及其翻译策略
60、论小说风格的传译
61、英文小说中对话的翻译
62、英汉修辞格 的语篇衔接作用及其在翻译中的再现
63、文学翻译批评简论
64、英汉语篇衔接 作用及其翻译策略
65、汉语广告英译中的巧 译策略探微
A 从跨文化角度看英语电影片名的翻译策略On Translation Strategies of English Film Titles from a Cross-Cultural Perspective B 《生死疲劳》中文化负载信息的翻译研究 The Translation of Culture-loaded Information in Life and Death are Wearing Me Out C 喜剧字幕翻译的改写On Rewriting of Comedy Subtitle Translation D 儿童文学翻译中文化因素的汉译策略On Translation of Cultural Elements in Children s LiteratureE 从目的论视角看菜单翻译策略The Strategies on Translation of Chinese Menu from the Perspective of SkopostheorieF 中英文化差异带来的语言交流障碍及翻译问题Language Exchanging Barrier and Translation Problems Arising from Cultural DifferencesG 汉英方位词的文化对比与翻译Cultural Contrast and Translation of Chinese and English Location Words暂时就这么多吧，本科生都是能写出来的
英汉翻译的载体是 文化 ，并且英汉翻译还受到了文化因素的影响。在英汉翻译的论文中，题目占据了一半文的作用。为此我将为你推荐英汉翻译论文选题的内容，希望能够帮到你!英汉翻译论文选题(一) 1. 跨文化视角中的英汉 谚语 互译 2. 英译汉中名词的转译 3. 文学作品中的隐喻翻译 方法 4. 论正说反译、反说正译 5. 翻译选词如何避免 Chinglish 6. 如何正确使用直译和意译 7. 双面佳人——谈《喧哗与骚动》中凯萧的人物形象 8. 论英汉动物词的文化意象差异与翻译 9. 论非常规翻译的作用 10. 从文化差异中看商标翻译 11. 英汉语言的对比 12. 浅谈《宠儿》中母亲塞丝的形象 13. 《毛猿》中扬克的悲剧探微 14. 文学作品中汉语姓名的英译 15. 《远离尘嚣》对 典故 的运用 16. 英语新闻标题的翻译 17. 析《好人难寻》的主要人物 18. 《喧哗与骚动》的视角 19. 试析欧·亨利小说的写作风格 20. 商务合同中长句的翻译 21. 英译汉中词义的抽象化到具体化的转换 22. 论文化语境与翻译选词 23. 语言差异与翻译中的合理叛逆 24. 浅析《远大前程》主人公匹普的成熟过程 25. 论翻译中的中国英语 26. 翻译中的英汉文化差异 27. 劳伦斯笔下的悲剧性人物保罗 英汉翻译论文选题(二) 1. 语法翻译法在中学英语教学中的应用 2. 中学英语语法课堂多媒体技术运用的优势 3. 汉语宣传资料英译探讨 4. 体现在中英习语中的文化差异 5. 英语学习 中对美国 俚语 的认识 6. 电影片名英汉互译的归化与异化及翻译的相关技巧 7. 浅析中国英语 8. 大卫·科波菲尔中的批判现实主义 9. ”信”与英语比喻翻译 10. 佩科拉的悲剧探源 11. 论凯瑟琳·曼斯菲尔德《园会》中的艺术特色 12. 中学 英语阅读 教学中的文化差异渗透 13. 口译中的笔记及实际运用中的障碍 14. 浅析委婉语及其语用功效 英汉翻译论文选题(三) 1. 汉译英中的文化差异——词汇空缺与中国特色文化翻译 2. Questioning and Teaching of Reading 3. 英汉动物比喻的文化内涵及差异 4. (动物比喻在英汉两种文化的内涵及差异) 5. 哈代——具有乡土田园气息的作家 6. 英语语言中的性别歧视(主义) 7. 浅析英语语篇中的词汇衔接 8. 浅谈景点名称的英译 9. 英汉禁忌语和委婉语对比研究 10. 广告 翻译中的修辞手法 11. 不同语境中的翻译 12. 直译与意译 13. 浅谈中国式英语的现象 14. 英汉翻译中文化特性的处理 15. 英汉谚语比较 16. 英文广告中双关语及其翻译 17. 商标翻译中的文化因素 18. 英美文化差异与颜色词的翻译 19. 论英语俚语的汉译 猜你喜欢： 1. 翻译英语专业毕业论文选题 2. 翻译学术论文题目 3. 英语专业文化类毕业论文题目 4. 英语跨文化论文选题 5. 英汉语言对比方面论文参考目录
英语专业翻译方向毕业论文选题参考：地方名胜古迹汉译英探析语境在翻译中的作用商标的翻译广告语言的翻译论英汉互译中的语义等值问题中西文化差异与不可译性英汉谚语的理解和翻译浅谈颜色词在英语中的翻译英语比喻性词语中文化内涵及翻译英语意义否定表现法及其汉译浅谈新闻标题的翻译伟大的翻译家严复英语长句汉译简评《简•爱》的几种汉译本英语专业本科论文所涉及的专业方向 （一）英语语言习得理论研究 该方向着重研究英语语言学及语言习得的相关理论与实践，可着重讨论某一种语言现象产生的原因及具体表现或某一语言理论在实际生活、教学中的运用。学生可以进行：1．英语修辞研究；2．文体研究；3．英汉比较研究；4．各类语体研究；5．语法研究；6．词汇研究等。 （二）教学理论与教学法该方向主要研究英语教学的理论与实践以及相关的教学指导原则和具体的方法，选题应着重探讨英语教学的方法，可具体到某一课程的教学理念、策略和方法的应用及效度，现代教育技术在英语教学中的应用与探索。学生可以进行：1．英语学习策略研究；2．英语学习焦虑研究；3．英语测试研究；4．英语教学法研究；5．英语教学策略研究；6．计算机辅助英语教学研究等。 （三）商务英语文本研究该方向着重研究商务英语文本文体，语言特点及相关的翻译实践问题。学生可以进行：1．商务英语语言特征研究；2．商务英语文体研究；3．商务英语翻译理论研究；4．商务英语翻译时间探讨；5．商务英语翻译标准探讨等。 （四）翻译理论与实践该方向着重研究英汉互译过程中的口、笔译理论、翻译标准、原则、方法及技巧。论文选题可选择评论赏析某一翻译家或某一本（篇）著名的译作，或论述某一种翻译理论的技巧在实践中的运用，也可讨论某一翻译现象中所反映的文化内涵。学生可以进行：1．翻译理论研究；2．翻译家研究；3．翻译史研究；4．文学翻译研究；5．非文学翻译研究；6．翻译过程研究；7．翻译批评研究；8．翻译的接受与影响研究；9．翻译教学研究；10．翻译标准研究；11．典籍翻译研究等。 （五）英美人文与历史研究 该方向主要研究英美国家的社会、文化、人文、历史各个方面的具体内容，既可宏观也可微观地研究或比较英美国家的某一历史阶段的社会问题或文化现象或评论某一历史事件或历史人物，或跨文化交际方面的相关内容。学生可以进行：1．英美社会制度、社会问题研究；2．英美历史问题、历史人物研究；3．英美文化现象研究；4．西方宗教研究；5．西方影视作品研究；6．跨文化交际研究等。 （六）英美文学研究该方向主要研究英美文学史及各时期的文学流派，作家，作品的文体与写作风格。论文可选择做某一文学理论或作家作品的分析、评论，比较中西文学作品或作家，分析作品中的主题或人物角色。学生可以进行：1．文学流派研究；2．作家研究；3．作品评论或分析；4．文学批评理论研究；5．中西文学作品的比较研究等。
可以找清北医学翻译，这家收费不贵，价格也合适。
好办，翻译是双语，双文，双文化的产物。因此，好的翻译只能脱裤子放屁重复学习同样的知识技能。比如物理学，在中国物理大学毕业，还要在美国达到物理大学毕业水平，也只能翻译英中/中英的物理大学毕业水平以下的资料，硕士/博士级别的，根本就别想了！是不是一个重要的题目？
问题一：毕业论文 用英语怎么说？ Graduation thesis 问题二：论文题目中的“以...为例”怎么翻译？ illustrated by the case of Chengdu illustrated by the exampl俯 of Chengdu 也可以。 然后其实很多英文教材书名都会说： An Asia Perspective,你觉得你这里用A Chengdu Perspective如何呢。就是从成都的角度来分析。 问题三：论文题目英文翻译 Cultivation of Senior Students' Ability in Solving Chemistry Problems --- Examples with Chemical Flow Diagrams 问题四：写论文时，要英文题目。那么 论 字如何翻译？ 一般不翻译，若翻译可用 On \ talk about \ A report about \ A report on 恭 sth. report 也可换成talk 建议用On 希望有帮助 问题五：论文题目的英语翻译 Analytical research report on the particularities of major traffic accidents(或 incidents) in our country recently. 我国近年来重大交通事故的特征分析 问题六：论文标题翻译成英语 1、Research on Process Reengineering of Corporate Payment Based on Bank-pany Direct Linkage 2、Research on Process Reengineering of Corporate Payment Based on Bank-pany Direct Linkage-A Case of pany A 问题七：在学士论文英文题目翻译中以…为例英文和汉语格式是怎样的? take A for example 问题八：英语论文一级标题二级标题怎么表示 A Contrastive Study between English and Chinese Idioms （题目：二号，黑体，加粗，居中,除了英语小词外，其他单词首字母都要大写；另外：除了题目外，论文中所有英文的字体均采用“Times New Roman”） （学院、专业、学号、作者姓名、指导教师姓名（小四号宋体字，加粗），依次排印在论文题目下，上空二行，居中） 【Abstract】 This paper centers on the different expressions of …… （英文摘要：上空二行；题目采用五号“Times New Roman”字体，加粗，置于粗体方括号【】内，顶格放置；随后的内容与前面的粗体方括号【】之间空一格，不用其他任何标点符号；采用五号“Times New Roman”字体，不加粗；单倍行距。） 【Key Words】 idiom; parison; English; Chinese （英文关键词：题目采用五号“Times New Roman”字体，加粗，两个单词的首字母要大写，置于粗体方括号【】内，顶格放置；随后的内容与前面的粗体方括号【】之间空一格，不用任何其他标点符号，采用五号“Times New Roman”字体，不加粗，除了专有名词外，其他单词的首字母不大写，各单词之间用分号“；”隔开，分号之后空一格；最后一个关键词之后不用任何标点符号；单倍行距。） 1. Introduction (顶格，除了第一个单词及专有名词外，其他单词首字母都不要大写；标题最后不用任何标点符号，上空两行) In both English and Chinese, …. So, this essay is trying to focus on the differences between Chinese and English idoms in terms of their essential meaning, customary usage and typical expression (Chang Liang, 1993:44; Li Guangling, 1999). (段落第一行缩进4个英文字符；夹注的标注法：出现在夹注中的作者必须与文后的参考文献形成一一对应关系；注意一个或多个作者间的标点符号，时间、页码等的标注法；另外，汉语参考文献的作者要以拼音形式出现，不能出现汉语姓氏；夹注出现在标点符号之前) 2. The similarities between English idioms and Chinese idioms In English, …. And it can be clearly seen in the below examples: (1) I don’t know。我不知道。 (2) I am not a poet. 我不是诗人。 (正文中的例子以（1），（2）…为序号排列，直至最后一个例子；而①, ②…则为脚注或尾注的上标序号) 3. The differences between English idioms and Chinese idioms The characteristics of English idioms （正文章节序号编制：章的编号：1. ，2.， 3.，…；节的编号：…，…；小节的编号为：, …。小节以下层次，采用希腊数字加括号为序，如（i），（ii）…；之后再采用字母加括号，如(a),......>> 问题九：论文题目英语怎么说 the title of the dissertation 论文题目 the title of the dissertation 论文题目 问题十：论文题目英文翻译 Cultivation of Senior Students' Ability in Solving Chemistry Problems --- Examples with Chemical Flow Diagrams