Central Air Conditioners for Consumers(Are you a partner? For Partners)Heating and cooling costs the average homeowner about $1,000 a year — nearly half the home's total energy bill. If your central air conditioning unit is more than 12 years old, replacing it with an ENERGY STAR qualified model could cut your cooling costs by 30 percent. Earning the ENERGY STAR means products meet strict energy efficiency guidelines set by the US Environmental Protection Agency and the Department of STAR qualified central air conditioners have a higher seasonal efficiency rating (SEER) than standard models, which makes them about 14% more efficient than standard models. Remember, saving energy prevents pollution. By choosing ENERGY STAR and taking steps to optimize the performance of your cooling equipment, you are helping to prevent global warming and promoting cleaner air while enhancing the comfort of your may also be interested to know:Though these products can be more expensive to purchase up front, the cost difference will be paid back over time through lower energy bills. When buying new equipment, it is important to get a quality installation. Make sure you get a contractor who can do the job right. You can get better performance out of your cooling equipment by sealing your home and making sure your ducts don't leak. EPA offers additional suggestions for improving the performance of your cooling system as well as general home improvement advice. Finding Qualified EquipmentThe Consortium for Energy Efficiency (CEE) and the Air-Conditioning and Refrigeration Institute (ARI) have developed an online database which can be used to find qualifying ENERGY STAR equipment. All equipment listed in this online database meets the specification requirements for ENERGY STAR. This online database is solely maintained and operated by CEE and ARI.
英文文献？？？文献？？？？？你确定用词无错？
Introduction The financial manager plays a dynamic role in a modern company’s development．This has not always been the case．Until around the first half of the 1900s financial managers primarily raised funds and managed their firms’cash positions-and that was pretty much it．In the 1950s,the increasing acceptance of present value concepts encouraged financial managers to expand their responsibilities and to become concerned with the selection of capital investment projects． Today external factors have an increasing impact on the financial corporate competition，technological change，volatility in inflation and interest rates，world-wide economic uncertainty，fluctuating exchange rates，tax law changes，and ethical concerns over certain financial dealings must be dealt with almost daily．As a result，finance is required to play an ever more vital strategic role within the corporation．The financial manager has emerged as a team player in the overall effort Of a company to create value．The“old ways of doing things”simply are not good enough in a world where old ways quickly become obsolete．Thus today's financial manager must have the flexibility to adapt to the changing external environment if his or her firm is to survive. The successful financial manager of tomorrow will need to supplement the traditional metrics of performance with new methods that encourage a greater role for uncertainty and multiple assumptions．These new methods will seek to value the flexibility inherent in initiatives—that is，the way in which taking one step offers you the option to stop or continue down one or more paths．In short，a correct decision may involve doing something today that in itself has small value，but gives you the option to do something of greater value in the future． If you become a financial manager，your ability to adapt to change，raise funds，invest in assets，and manage wisely will affect the success of your firm and，ultimately，the overall economy as well．To the extent that funds are misallocated，the growth of the economy will be slowed．When economic wants are unfulfilled，this misallocation of funds may work to the detriment of society．In an economy，efficient allocation of resources is vital to optimal growth in that economy；it is also vital to ensuring that individuals obtain satisfaction of their highest levels of personal wants．Thus，through efficiently acquiring，financing，and managing assets， the financial manager contributes to the firm and to the vitality and growth of the economy as a whole．简介 财务经理扮演一个积极的角色,在一个现代公司的并不总是周围 上半年,1900年财政管理,主要是筹集资金和管理,他们firms'cash阵地--这是相当 50年代起,越来越多的人接受目前的价值观念,鼓励财务经理,扩充自己的责任,很关心 e选择资本投资项目. 今天受外部因素的影响越来越大,财政企业竞争,技术变革,波动,通货膨胀率和利率上升,全球性的经济 不确定性,汇率波动时,税法的变化,和道德方面的某些金融交易必须处理几乎结果,是财政部 要发挥越来越重要的战略作用在转炉财务经理已经成为队球员 在整体的努力,公司创造"老办法办事"根本不是太好了 世界旧的方式迅速成为今天的财务经理必须要有一定的灵活性,以适应不断变化的外部 环境,只要他或她确实是为了生存. 成功的财务经理,明天将需要补充传统的度量的表现,与新方法,鼓励 更大的作用,对不确定性和多发性新方法将寻求价值的灵活性举措,即2001年的 在这一步,您可以选择停止或继续下跌的一个或多个总之, 正确的决定可能牵涉做一些事情,今天,在本身有小价值,而是让您选择做点事 更大的价值在未来. 如果你成为一个财务经理,你适应变
20分帮你手动翻译那么多东西。。。。。。这个是不可能的，没事做也不要这样自寻烦恼啊
暖通空调就很好了
《暖通空调》是本杂志，本专业的核心期刊，自己去随便下载几篇都是暖通行业相关的。 翻译借助百度翻译和自己那点水平，这小事儿还用求助..要原创的我可以提供
英文参考文献格式举例
参考文献是毕业论文的重要组成部分，对其进行统计分析，不仅有利于本科生的.教育和管理，而且能为图书馆文献保障和读者服务等工作提供一定的参考依据。下面是我整理的英文参考文献格式举例，希望大家重视。
一、参考文献的类型
参考文献(即引文出处)的类型以单字母方式标识，具体如下：M——专著C——论文集N——报纸文章J——期刊文章D——学位论文R——报告
对于不属于上述的文献类型，采用字母“Z”标识。对于英文参考文献，还应注意以下两点：
①作者姓名采用“姓在前名在后”原则，具体格式是：姓，名字的首字母.如：MalcolmRichardCowley应为：Cowley，.，如果有两位作者，第一位作者方式不变，&之后第二位作者名字的首字母放在前面，姓放在后面，如：FrankNorris与IrvingGordon应为：Norris，F.&.;
②书名、报刊名使用斜体字，如：MasteringEnglishLiterature，EnglishWeekly。
二、参考文献的格式及举例
1.期刊类
【格式】[序号]作者.篇名[J].刊名，出版年份，卷号(期号)：起止页码.【举例】
[1]王海粟.浅议会计信息披露模式[J].财政研究，2004，21(1)：56-58.[2]夏鲁惠.高等学校毕业论文教学情况调研报告[J].高等理科教育，2004(1):46-52.
[3]Heider，[J].ForeignLanguageTeachingandResearch，1999，(3):62–67.
2.专著类
【格式】[序号]作者.书名[M].出版地：出版社，出版年份：起止页码.【举例】[4]葛家澍，林志军.现代西方财务会计理论[M].厦门：厦门大学出版社，2001：42.
[5]Gill，[M].London:Macmillan，1985:42-45.
3.报纸类
【格式】[序号]作者.篇名[N].报纸名，出版日期(版次).【举例】
[6]李大伦.经济全球化的重要性[N].光明日报，1998-12-27(3).
[7]French，[N].AtlanticWeekly，198715(33).
4.论文集
【格式】[序号]作者.篇名[C].出版地：出版者，出版年份：起始页码.【举例】
[8]伍蠡甫.西方文论选[C].上海：上海译文出版社，1979：12-17.
[9]Spivak，G.“CantheSubalternSpeak?”[A].(eds.).VictoryinLimbo:Imigism[C].Urbana:UniversityofIllinoisPress，1988，.
暖通空调杂志就可以的
看大学教材吧 《建筑环境与设备工程专业英语》
在网上找本暖通英汉词典就行了吧
20分帮你手动翻译那么多东西。。。。。。这个是不可能的，没事做也不要这样自寻烦恼啊
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
1.从产品名称上,"格力"留给国人的印象就是格外有力,有劲、好使。比起初命名蕴含“快乐、伟大、绿色"的寓意更加简单、直接。买空调首选格力已成共识!2.从品质把控上,格力自始至终要求严格。不同的国产品牌,在同样的外部环境,同样的使用情况下,格力外机故障率最低,且不易锈蚀,而其它空调,早已绣蚀不堪。这就是质量,格力经得起风吹日晒雨淋的检验。3.从产品研发上,坚持走专业化战略,坚持自主研发创新,同时也在“技术、管理、营销、服务"等全方位坚持创新。技术层面,格力已申请专利近5万项,国际专利1千多项。自主研发的三缸双级压缩机、光伏直驱变频离心机、永磁同步变频离心机早已达到国际领先水平,还有一些最新技术正在研发。4.从广告宣传上,一句“好空调、格力造!"让无数消费者记住了格力;“格力
故障代码F0含义统缺氟或堵塞保护。解决办法：一先应该判断空调是乏。先打开空调开制冷，让空调压缩机连续运转15分钟以上，若制冷系统缺氟，会出现以现象：1.回气管发干，用手触摸无明显的凉感，也无结露现象。2.高压管结霜。。3.打开室内机面板，取下过滤网，可发现蒸发器仅少部分结霜或结露。4.室外机排风无热感。5.排水软管排水很少或根本不排水6.高压管结霜。如果空调却氟应该联系售后人员，避免加氟含量不合适影响空调使用寿命。二、判断管路是否堵塞。将压力表接在旁通充注阀上，指示为负压说明已经堵塞。若管路堵塞应该用真空泵抽干净内部潮湿空气，若仍不见效说明有异物堵塞，需要更换管路。
F0是系统缺氟/堵塞保护/检查误判，具体故障原因需要格力服务人员上门检测处理。请您点击这里或联系格力全国统一客户服务热线4008-365-315进行服务预约。
首该判断空调是否缺乏。 ?先空调开制冷，让空缩机连续运转15分钟以上，若制冷缺氟，会出现以现象： 回气管发干，用手触摸无明显的凉感，也无结露现象。
高压管结霜。打开室内机面板，取下过滤网，可发现蒸发器仅少部分结霜或结露。
室外机排风无热感，排水软管排水很少或根本不排水。
1.在堵或者缺氟状态下开机会出现此保护。2.收式/系统缺氟或堵塞，排气保护。3.代统缺氟或堵塞保护。：表示冷剂漏。新机如果不是安装出问题一般是不会漏。也有可能是零件故障引起的保护。5.室温传感器故障，打开面板，把传感器重新放置好。
FO故障代码：剂泄漏，这属于安装问题能管道硬件问题建议打客服报修。1.在阀门者缺氟状态下开机会出现此保护。2.收费模式/系统缺氟或堵塞保护，排气保护。3.代表系统缺氟或堵塞保护。：表示冷剂漏。新机如果不是安装出问题一般是不会漏。也有可能是零件故障引起的保护。5.室温传感器故障，打开面板，把传感器重新放置好。
格力故障代码显示F0表示收氟模式，也就是说系统压力偏低，通常是以下几个方面故障引起：1、室外机截止阀阀门没有打开或者没有开全；2、系统制冷剂泄漏；3、制冷系统有堵塞；4、检查室温管温传感器是否损坏
格力空现F0符号有以下三种可能
1力空调出现F0符号是环境传感器故障，出个情况，很可能是因为环境传感器损坏所导致的。可能是传感器的接线松脱或者接触不良导致的，使用时间长了传感器也会出现老化现象，检查一下电路板是否有故障。
2、如果空调内机的压缩机出现故障，空调也会显示f0，压缩机出现故障会使空调无法正常运作。
3、制冷剂不足，制冷剂不足会严重影响空调的使用，降低制冷效率，及时的给空调加氟就好了。当然具体的空调型号不同可能故障代码的指代含义也有所差异。
扩展资料：
格力空调故障代码
参考文献：百度百科-格力空调故障代码
F0故障代码：制冷剂泄漏，：
1阀门堵或者缺氟状态下开机会出现护。
2、收费、系统缺氟或堵塞保护，排气保护。
3、代表系统缺氟或堵塞保护。
4、新机如果不是安装出问题一般是不会漏，也有可能是零件故障引起的保护。
5、空调传感器接线出现松脱、接触不良的现象，还有可能是传感器本身老化的问题。
扩展资料
格力空调出现F0符号解决办法：
一、首先应该判断空调是否缺乏。
先打开空调开制冷，让空调压缩机连续运转15分钟以上，若制冷系统缺氟，会出现以现象：
1、回气管发干，用手触摸无明显的凉感，也无结露现象。
2、管结霜。
3、打开室内机面板，取下过滤网，可发现蒸发器仅少部分结霜或结露。
4、室外机排风无热感。
5、排水软管排水很少或根本不排水6.管结霜。如果空调却氟应该人员，避免加氟含量不合适影响空调使用寿命。
二、判断管路是否堵塞。
将压力表接在旁通充注上，指示为负压说明已经堵塞。若管路堵塞应该用真空泵抽干净内部潮湿空气，若仍不见效说明有异物堵塞，需要更换管路。
F0是制冷剂泄漏/堵塞保护/检测误判，具体故障原因需要格力服务人员上门检测处理。请您点击这里或联系格力全国统一客户服务热线4008-365-315进行服务预约。
F0统缺氟或堵塞保护，也有可能表示冷。新机如果不是出问题一般是不会漏有可能是零件故障引起的保护。解决办法：1、先打开空调开制冷，让空调压缩机连续运转15分钟以上，若制冷系统缺氟，会出现以现象：①回气管发干，用手触摸无明显的凉感，也无结露现象。②高压管结霜。③打开室内机面板，取下过滤网，可发现蒸发器仅少部分结霜或结露。④室外机排风无热感。⑤排水软管排水很少或根本不排水。⑥高压管结霜。如果空调却氟应该联系售后人员，避免加氟含量不合适影响空调使用寿命。2、判断管路是否堵塞。将压力表接在旁通充注阀上，指示为负压说明已经堵塞。若管路堵塞应该用真空泵抽干净内部潮湿空气，若仍不见效说明有异物堵塞，需要更换管路。3、判断是否是误操作遥控器造成的新化霜功能打开。在遥控器关机情况下同时按下遥控器上“模式”键和“干燥。辅热”键，退出新化霜功能即可。
格力空调的宣传力度大！
格力空调你好我也好
随着改革开放逐步深化、国民经济的快速发展、人民对生活品质要求的提高，空调在现代建设中被广泛的应用。下面是我为大家精心推荐的空调节能技术论文，希望能够对您有所帮助。
空调节能技术浅谈
摘要：随着近年来社会经济的不断发展，人们生活品质的逐步提高，对于物质生活和环境舒适性的需求也更加苛刻，空调系统显然已经成为现代建筑行业中一个不可忽视的部分。但是，近年来能源危机突出和环境破坏对人类的影响逐步加深，已经让人类清晰的认识环境保护和能源节约的重要，国家也制定了一系列的法律法规和行业标准。因此，能源的有效节约、提高能源有效利用的方法和技术的研究成为了当今一项重要课题。本研究从影响空调系统的能耗的关键因素出发，提出了几项空调节能的可行性方案，最后探讨了空调节能的未来发展趋势。
关键词：空调系统;节能技术;措施建议
中图分类号：文献标识码： A
前言：
随着人们经济水平的不断提高，生活品质的提升，无论是生活环境还是工作环境，空调系统在现代建筑中的应用也越来越广泛。根据统计表明，在我国空调耗能占建筑物总能源消耗的60%～70%，因此，采取有效的节能措施，解决高层建筑节能问题符合我国经济的可持续发展的要求，对节能减排和建设环境友好型社会有着至关重要的意义。
空调能耗的现状以及节能的重要性
随着改革开放逐步深化、国民经济的快速发展、人民对生活品质要求的提高，空调在现代建设中被广泛的应用。而在建筑能耗里，空调能耗已经占到建筑能耗的60%~70%左右，而且比重还在逐年上升。因此空调节能技术的发展对提高能源利用率、环境可持续发展有重要影响。
在我国现阶段中央空调系统的应用中，通常认为空调系统的温湿度控制以及空气品质的控制是最为重要的，进而忽略了空调系统的能源消耗情况。在我国，影响中央空调系统能源不能得到有效利用的主要因素有三方面，首先，在设计过程中重视投资成本，而忽略了能耗指标计算，在整个系统方案中，缺乏节能引导中央空调系统的经济性分析。导致在工程建筑方案的运行过程中，使用投资低、耗能大、运行费用高的空调系统。其次，对于中央空调而言，整个的系统工程相对复杂，所以对于中央空调能源有效利用的评价，要从整个系统全面来看，而不能单纯地停留在对机器设备本身的评价上，真正意义上的节能是与各个系统设计理念、施工优劣情况以及运行管理水平和建筑物热特性等因素息息相关，而不是只看重设备本身。最后，还有一个主要的因素，就是缺乏高素质运行管理人员和节能监控，致使空调系统在运行和管理的过程中没有得到很好地控制和监管，合格的管理人才可以大大改善运行不合理的地方，有利于节能。
建筑节能技术
空调系统的节能技术首先可以从建筑物本身入手，结合建筑、结构等相关知识，使建筑物在形状、色彩、方位及材料等方面为空调节能创造最基础的条件。对于空调位置的安排要进行合理布局，合理设计相关比例与系数，选择保温隔热性能良好的材料作为墙体和屋面，并提高改善建筑围护结构的性能等，都是建筑节能的可行性措施。
选择合理的室内设计参数
在整个建筑物中，主要的热损失来自于围护结构和门窗缝隙空气渗透。因此, 在建筑物进行建筑节能中，注重室内设计中加强围护结构，使用环保、节能型建筑材料, 可有效地减少通过围护结构的传热这一主要的空调负荷, 从而各主要设备的容量达到显著的节能效果。通过这种方法进行保温隔热，同时加强门窗的气密性。另外，在夏季空调供冷时，室内外侧玻璃受阳光照射，是空调冷负荷的主要部分，应采取必要的遮阳措施。而在冬季空调供热时，则要求改善窗户的保温效果，可以采用光热性能好的玻璃;为了减少窗的冷(热)桥传热，可以采用钢塑窗代替铝合金窗;同时还可以采用双层玻璃窗提高窗的保温性。在窗户的设计位置上要减小窗洞口与墙的面积比值减少空调房间两侧温差大的外墙面积及其薄弱环节窗的面积，利于空调建筑节能。
合理设计建筑结构
合理的设计建筑结构也是进行空调节能的一个有效途径之一。可以通过改善建筑的保温隔热性能，使房间内冷热量的损失通过房间的墙壁和门窗传递出去，这样可以有效地减少建筑物的冷热负荷。建筑物的朝向对空调冷负荷有很大的影响，根据我国的地理位置来分析确定良好的建筑朝向，一般建筑物为南朝向是我国建筑节能的必要条件，可以通过保持合理的建筑间距以及建筑群的错落布局，使建筑物接受适当的太阳辐射，同时有利于获得自然通风气流。
空调设计方面节能
在面积较大的空调房内，在空调房内区的负荷与周边区的相比较差距较大，如果两个区域选择使用一个空调系统进行制冷，两个空调房区域的房间的将会产生较大的温差，尤其是在冬季及过渡季节，所以同时处于两个不同区域的工作人员对环境空间的温度反映冷热温差较大，，根据我国在2001年版的《采暖通风与空气调节设计规范》新增条之规定,建筑物内负荷特性相差较大的内区与周边区,以及同一时间内必须分别进行加热与冷却的房间,宜分别设置空气调节系统.。内区系统主要处理室内负荷，与外区负荷相比，内区负荷则相对稳定，内区往往需要全年供冷，去除室内余热。外区系统主要处理外部得热，外区负荷波动大，外区新风来源一般是内区空调系统，与外区回风混合经风机盘管处理后达到送风点，外区冬季供暖，夏季供冷，从而满足舒适性要求。
空调系统中的节能技术
空调系统如何适应在低负荷下高效节能运行及在系统设计中对设备进行节能选配就成为空调节能的关键。
4. 1 加强中央空调的运行管理和控制设备的调节控制
提高空调能源的有效利用，需提高操控人员的职业素质，避免由于管理不善而引起的空调耗能。操控人员要做好设备运行记录，分析机组各种压力表、温度计、流量计的读数是否正常准确，并根据空调负荷的变化调节机组，确保机组运行在节能状态，而且定期保养检查，及时更换磨损的零件。
4. 2 设备及管道的保温及水质处理
要实现降低能量的过多耗费这一目标，就要做好设备及管道的保温。保温的目的是为了阻绝内外温度传递，如果室外的温度小于空调排水的温度加保温是为了防止空调水管结冰冻裂水管，如果环境温度大于空调排水温度加保温是为了防止有冷凝水造成漏水。空调设备和管道的保温，对于节省能量消耗、降低运行费用也是相当重要的。空调能耗高还有一个重要的原因，就是空调系统中水管中水质的污染。
5、建筑空调系统设备的节能运行技术
设备的节能运行技术在建筑空调系统综合节能技术中, 其也至关重要。主要技术包括: 蓄能空调技术、热回收技术、变频技术等。
蓄能空调技术
蓄能系统就是储蓄在不需要的冷/热量或需要的冷/热量减少的时间的过程中,制冷/热设备将蓄冷/热介质中所移出的热量，并在空调处于用冷/热或工艺性的用能高峰时，启动此能量。这样既减少了能源的流失，又可以有效地利用能源，既有经济效益又有社会效益, 是一项双赢的节能举措。
热回收技术
热回收技术包括排风余热回收和制冷机组的冷凝热回收。排风余热回收充分利用排风的能量, 对其进行回收，从而对新风进行预冷或预热,减小新风负荷是暖通空调节能的重要途径。制冷机组的冷凝热回收系统既可以避免冷凝热排放到大气中造成热污染, 又可以节省为提供热水而设的锅炉及其附属设备, 避免了由于燃料的燃烧向大气排放的有害物, 应该说是一种效果明显, 又有环保作用的节能技术。
变频技术
随着电力电子技术和计算机控制技术的不断发展，在空调控制系统中变频器也得到了广泛的应用，它的应用主要是针对空调控制系统的特点而进行控制。不同类型的冷水机组都有较完善的自动控制调节装置, 能随负荷变化自动调节运行状况, 保持高效率运行，从而实现了一种既能达到控制要求又能节约能源的方法。
太阳能空调技术
太阳能是绿色能源中最重要的能源, 太阳能的热利用是目前建筑中利用太阳能的主要利用形式。它包括被动式和主动式两种形式。被动式太阳能房的结构相对简单、造价低、不需要任何辅助能源, 通过建筑方位合理布置和建筑构件的恰当处理, 以自然热交换方式来利用太阳能。主动式太阳房结构较为复杂,造价较高,需要用电作为辅助能源。采暖降温系统由太阳集热器、风机、泵、散热器及储热器等组成。在建筑外围护结构中还可采用太阳能集热墙, 利用太阳能采暖。
6、结束语
能源问题是我国实现经济发展的重点问题之一，建筑空调节能技术是节约能源、改善环境、促进经济可持续发展的有效措施。空调系统在高负荷下高效节能运行以及在系统设计中选配节能设备是建筑空调节能的关键因素， 这对于节约能源、降低运行费用、促进国民经济发展具有十分重要的意义。在未来的建筑物中，在空调系统设计方面，要在节约能源以及有效利用能源这两方面引起高度重视。只要各方共同努力，空调系统的节能降耗问题的解决指日可待。
参考文献：
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你这问题难度太大因为中央空调的维护是一个系统工程涉及到很多工序
1 王鹏英.新编空气调节[M].上海：上海工程技术大学机械工程学院，20033 陈沛霖，岳孝.空调与制冷技术手册[M].上海：同济大学出版社，19904 郑爱平.空气调节工程[M].北京：科学出版社，2002
空调有利于热量从车内删除。其原理是，采用热传导和对流删除。这是冷的蒸发器吸收的是通过它，然后冷空气强行通过内部由鼓风机电动机车的通风口出空气中的热量。这是通过加压制冷剂（134a）用压缩机与制冷剂，然后释放里面的空调蒸发器（134a）用。汽车空调系统一些汽车都配备了自动气候控制系统来调节车内温度自动。气候控制模块是一台电脑的显示器并调整到用户设定的温度。温度由加热器控制，实现了理想的温度由冷空气从空调，热风组合。鼓风机电机速度控制的固态速度控制器。该控制器的电气控制风机电机的转速，并取代传统的电阻器鼓风机马达系统。典型的空调系统配置空调和供热单位提供了热感舒适，里面无论什么温度外面的乘客。内的空气可以被加热，冷却，消毒或通风。气候控制功能有助于保持理想的温度。该系统提供制冷，制热和气候控制的空调（供暖，通风，空调）系统而闻名。流体力学，热力学与传热的基本原理提供冷，热特定的系统。你的气候控制设置允许所有三到携手合作，实现良好的室内空气质量，热舒适性和最佳的压力。气候控制系统故障码可以存储问题时，在系统检测。你可以通过按控制面板上在同一时间两个或多个按钮的代码。要了解如何为您检索故障码车辆检查您的用户手册或请教维修手册。当代码检索系统启用了故障代码将出现在温度控制头。维修后已作出系统将需要重新启用，这是通过断开45秒重新连接电池和蓄电池进行。测试可以随时中止转动钥匙到关闭的位置。压缩机空调压缩机是空调系统的制冷剂泵。压缩机压缩制冷剂，并在系统内部循环到冷凝器，然后到蒸发器。蒸发器制冷剂在被释放的压力，造成了在寒冷的蒸发器造成的压力下降，低压制冷剂，然后返回到压缩机被重新加压。空调压缩机是由一个驱动器带，是由发动机和可从事电磁线圈和脱离对压缩机的前面。空调压缩机为了维持空调系统的压缩机驱动皮带应定期检查效率。如果磨损或退化，应更换。该系统的软管应恶化，气泡，裂纹和硬化或油质残留检查，所有可能泄漏的迹象。正确的制冷剂充应始终保持低系统制冷剂充是一个弱交流系统的共同事业。气味会发达的空调系统时，对真菌生长的蒸发器的核心。温暖潮湿的环境提供了真菌，它具有吸湿成长完美的温床。气雾消毒剂可用于纠正这种状况。虽然空调系统上运行的全高设置激活recirculation功能，喷雾消毒（来苏，Ozium）进入了交流系统入口（根据对乘客的侧划线），要知道无论你喷将出来上部通风口，所以你可能不希望在任何通风孔前你的脸时，做此过程。气味可以防止重复整个夏季，这个程序会定期返回。基本维护汽车充电套件可在任何汽车配件商店，在建议购买可与荧光染料制冷剂，可以帮助指出任何制冷剂泄漏的位置。该套件将指示添加制冷剂安全。防护眼镜时，应使用冷媒罐加压处理。有时错误，树叶和尘埃颗粒可以停留在冷凝器翅片。异物和污垢，可清洗花园的压缩空气软管帮助或强行通过散热器及冷凝器直至干净倒退。注：空调系统始终在压力之下，直至系统完全放电，没有维修或拆卸应该执行。保护眼睛应始终修理或维修时穿的空调系统。