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主要内容应该围绕你在主持建筑工程中主要起到哪些重要的作用，解决了哪些技术难题，以及在组织施工管理中具有哪些特点等等。
1876年11月26日 (丙子年十月十一)，空调发明人威利斯·开利出生。威利斯·开利(Willis Haviland Carrier，1876年11月26日-1950年10月7日)，美国工程师及发明家，是现代空调系统的发明者。开利博士于1902年为纽约布鲁克林的一家印刷厂设计了一套空调系统，解决了因夏季湿度太高，而导致纸张变形无法印刷的难题。而后的100年间，开利和开利博士所设立的开利公司致力于空调技术的不断创新。
回答 空调培训心得体会范文篇1 11月初，我们物流和连锁班一起去南京苏宁实训，实训真的是一种经历，只有亲身体验才知其中滋味，课本上学到的知识都是最基本的知识，不管现实情况怎样变化，抓住了最基本的就可以“以不变应万变。虽然这次实训时间很短，但这短短的半个多月的生活却让我感触颇多。本次实习的单位是南京苏宁雨花物流实训基地。我想在这有必要提及苏宁的相关简介。 苏宁电器1990年创立于南京，是中国3c(家电、电脑、通讯)家电连锁零售企业的领先者，是国家商务部重点培育的“全国15家大型商业企业集团”之一。截至目前，苏宁电器连锁网络覆盖中国大陆30个省，300多个城市、香港和日本地区，拥有1000多家连锁店，80多个物流配送中心、3000家售后网点，员工18万多人，品牌价值68亿元，是中国最大的商业连锁企业，名列中国上规模民企前三，中国企业500强第54位，入选《福布斯》亚洲企业50强、《福布斯》全球2000大企业中国零售企业第一。 提问 空调的心得 回答 稍等，在整理 通过学习《暖通空调》，让我对这门]课程以及建筑环境与设备工程这个专业有了新的了解，尤其对生活中的空调应用有了新的了解。懂得何谓暖通空调及建筑环境这个专业和中央空调系统是我学习这门课程最大的收获。 暖通在学科分类中的全称为供热供燃气通风及空调工程，本科阶段为建筑环境与设备工程。 暖通空调是分户的中央空调，中央空调它最大特点，是能够创造一种舒适的室内环境。而家居一般的分体的空调，它只能解决冷暖问题，而解决不了空气处理过程。现在，有了那么暖通空调就不一样了。现在这个空气处理过程它有以下这些过程:首先是空气进来以后，除了引进新风以外，可以把空气进行冷却处理然后就进行过滤处理，过滤处理以后，增加 了几大特点: 第一就增加电子除尘器， 它主要可以捕捉非常小的颗粒的灰尘，一般来讲它可以捕捉一个微米的灰尘，而这个灰尘的范围 要可以捕捉非常小的颗粒的灰尘，一般来讲它可以捕捉一个微米的灰尘，而这个灰尘的范围内大部分都是细菌、病毒、烟尘，或者是异味这样就都可以过滤掉;另外就是会增加一种加湿设备，这个加湿器可以创造我们房间的加湿达到40%左右的相对湿度，这样人会感到很舒适。 暖通包括:采暖、通风、空气调节这三个方面，缩写HVAC那三个方面简称暖通空调。 网_上有这样的介绍暖通空调概念的“暖通空调是分户的中央空调，中央空调它最大特点，是能够创造一种舒适的室内环境。而家居一般的分体的空调，它只能解决冷暖问题，而解决不了空气处理过程。现在，有了那么暖通空调就不一样了。现在这个空气处理过程它有以下这些过程:首先是空气进来以后，除了引进新风以外，可以把空气进行冷却处理，然后就进行过滤处理，过滤处理以后，增加了几大特点:第一就增加电子除尘器，它主要可以捕 捉非常小的颗粒的灰尘，一般来讲它可以捕捉-个微米的灰尘，而这个灰尘的范围内大部分都是细菌、病毒、烟尘，或者是异味这样就都可以过滤掉;另外就是会增加一种加湿设备，这个加湿器可以创造我们房间的加湿达到40%左右的相对湿度，这样人会感到很舒适。” 称。 “暖通”是建筑设计中工种的一个分类的名 在我国的建筑行业，一直以“建筑设计院”牵头。一个建筑项目确立之后，首先由某个建筑设计院进行总体设计。建筑的总体设计包括许多分项，-般如下:建筑设计，结构设计， 基础设计，电力(强、 弱电)设计，给排水设计，暖通设计，配套园林绿化景观设计等等。暖通设计(如果该项目需要)是指该项目中的所需要的“空气调节系统”简称“空调系统”。一般“空调系统”包括制冷供暖系统，新风系统，排风(排油烟)系统等的综合设计。所以说“暖通”从功能上说是建筑的一个组成部分。从建筑设计来说，他是建筑设计的一个分项。并不是单指“空调”。需要说明的一-点是:“空调” 不是单指“空调”。需要说明的一点是:“空调”在一个建筑中可能是“中央空调系统”，也可能是“中央空调与独立空调的混合系统”，也可能全部是“独立空调的系统”。一切根据建筑的功能以及投资者的意向和实际需要而定。中央空调系统有主机和末段系统。按负担室内热湿负荷所用的介质可分为全空气系统、全水系统、空气-水系统、冷剂系统等。中央空调系统一 切实体现用户最高要求具有下列的优点 故在现 代建筑中广泛运用: O1经济节能:主机由微电脑控制，每个区间末端风机盘管可自行调节温度，区间无人时可关闭，系统根据实际负荷做自动化运行，开机计费，不开机不计费，有效节约能源和运行费用。O2环保:主机采用水源热泵型机组，电制冷，没有燃烧过程，避免了排污;整个系统为密闭式管路系统，可避免霉菌灰尘等杂质对系统的污染，使环境清新优美，特别适于高档别墅、高级公寓与写字楼的使用。 03节约空间:主机体积小巧，不设 机房，无需占用设备层，减少公用设施和土建投资，室内末端暗藏在吊顶内，极易配合屋 更多16条
说到暖通空调，相信很多人跟小编一样都不是特别的了解。暖通空调顾名思义就是将采暖、通风和空气调节这三者合为一的空调器。暖通空调也被人们称作HVAC，这是由采暖、通风、空气通风这三个词的英文缩写组合而成。今天小编就来为大家介绍一下暖通空调系统设计原理及特点，希望可以为大家提供一定的帮助，也为有需要的人提供更多的了解。 一、原理 暖通空调是分户的中央空调，中央空调它最大特点,是能够创造一种舒适的室内环境。而家居一般的分体的空调，它只能解决冷暖问题，而解决不了空气处理过程。有了暖通空调就不一样了。其空气处理过程有以下步骤：首先是空气进来以后，除了引进新风以外，可以把空气进行冷却处理，然后就进行过滤处理，过滤处理以后，增加了几大特点：第一就增加电子除尘器，它主要可以捕捉非常小的颗粒的灰尘，一般来讲它可以捕捉一个微米的灰尘，而这个灰尘的范围内大部分都是细菌、病毒、烟尘，或者是异味这样就都可以过滤掉;另外就是会增加一种加湿设备，这个加湿器可以创造我们房间的加湿达到40%左右的相对湿度，这样人会感到很舒适。 二、特点 在现代化暖通空调系统中，变频技术的应用具有较强的必然性。通过变频技术，既可弥补空调系统的工艺问题，也可减少能源消耗，降低运行成本。一般情况下，空调系统仅按照事先设计的额定功率运行，在负荷较低的情况下，如果设备仍以额定功率实行全负荷运行，那么必然产生能源浪费。通过在暖通空调系统中应用变频技术，就可实现空调设备的输出功率随着负荷的变化情况而有所调节，发挥节能减排效果。结合空调的实际负荷状况，适当改变风流量或者水流量，实现节能目标。 一方面，变风量系统，利用空调系统的末端装置实现室内负荷的补偿机制，优化调整送风量，以保持合适的室内温度;与定风量系统相比较，变风量系统可节能约5O%;另一方面，变水量系统，主要通过控制数量来调节温度，比定流量系统更加省电。随着我国工业变频器的推广与使用，通过优化调节风量、水量及主机等，可实现与空调负荷的匹配运行，发挥良好的节能效益。 很多人可能人会问小编，暖通空调系统在生活中常见吗?相信很多人都没有注意，现在很多单位和公共场所都已经开始应用暖通空调系统。暖通空调技术可以选择热源系统的优化，也采用了节能技术。所以自从暖通空调系统面世以来，便受到了广大消费者的喜爱和追捧。小编今天为大家介绍的暖通空调系统设计原理和特点就到这里了，希望可以为大家带来帮助。
“暖通”是建筑设计中工种的一个分类的名称。 在我国的建筑行业，一直以“建筑设计院”牵头。一个建筑项目确立之后，首先由某个建筑设计院进行总体设计。 建筑的总体设计包括许多分项，一般如下：建筑设计，结构设计，基础设计，电力（强、弱电）设计，给排水设计，暖通设计，配套园林绿化景观设计等等。 暖通设计（如果该项目需要）是指该项目中的所需要的“空气调节系统”简称“空调系统”。一般“空调系统”包括制冷供暖系统，新风系统，排风（排油烟）系统等的综合设计。 所以说“暖通”从功能上说是建筑的一个组成部分。从建筑设计来说，他是建筑设计的一个分项。并不是单指“空调”。 得给出更具体的研究内容
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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
你是学建筑环境也设备工程的不
行业发展现状一般由企业发展概况、产品结构、市场格局、市场现状等方面构成，但是也会有一些差异，研精毕智对行业的产业链和市场现状进行分析，通过研究市场规模等数据，预测行业发展前景，报告分为很多个章节，当然也可以做个性化调研，之前他们就根据我的需求做了一份报告，内容完全都是我自己设定的，里面会涉及到很多市场数据，大多来自于年报和IPO数据，还有实地调研得到的，这都可以放心的，在这方面有团队去做的，最近百度官网不只有行业分析文章了，还新增了行业的监测内容，可以看看
这个上面你自己看下能不能用得上哦我不懂这个的
1，研究背景2，目的意义3，成员分工4，实施计划5，可行性论证6，预期成果及其表现形式要求：总结全文，深化主题，揭示规律，指明方向。注释和参考，1、内容：书籍、刊物、报纸、网络 ，完整注明出处附录，问卷、量表、研究材料、统计数据、方案、计划等。拓展资料：毕业论文（graduation study）是专科及以上学历教育为对本专业学生集中进行科学研究训练而要求学生在毕业前撰写的论文。毕业论文一般安排在修业的最后一学年（学期）进行，论文题目由教师指定或由学生提出，学生选定课题后进行研究，撰写并提交论文，目的在于培养学生的科学研究能力，加强综合运用所学知识、理论和技能解决实际问题的训练，从总体上考查学生大学阶段学习所达到的学业水平。
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多少字啊？什么方向的