气体分馏装置节能降耗技术分析

洛阳分公司二套联合气体分馏装置原设计加工能力为30×104t/a,2008年扩能改造为65×104t/a,采用脱丙烷塔(T501)、脱乙烷塔(T502)、丙烯塔(T503AB/CD)、脱异丁烷塔(T504)四塔加工流程,目标产品是从液化石油气中分馏出99.6%的高纯度丙烯和氢氟酸烷基化原料。装置设计能耗为56.53kg标油/t原料。装置改造后,由于加工负荷小于设计值(仅为设计值的60%~80%),导致蒸汽、热水、电等动力能耗比设计值偏高;同时,原料中C2等轻组分多,造成瓦斯大量排放,导致装置加工损耗大,装置实际能耗比设计值高出4.87个能耗单位。为此,通过技术分析及实际论证,采用降压操作、工艺优化、热联合等措施,装置各动力消耗明显降低,装置能耗降低9.31kg标油/t原料。提出预热器E512加热流程改造、停用脱乙烷塔进料预热器、T501塔原料预热流程改造等节能新思路。     

荆门石化气体分馏装置流程模拟技术应用

荆门石化总厂气体分馏装置处理能力为55×104t/a,采用脱丙烷塔、脱乙烷塔、丙烯塔(两塔)三塔流程。以该气体分馏装置为研究对象,采用Aspen Plus流程模拟软件,建立与装置实际工况相符合的稳态流程模拟模型。利用此模型,对脱丙烷塔、脱乙烷塔、丙烯塔等进行灵敏度分析,研究各塔压力、热负荷、回流比等参数间的相互关系,并以模型为指导,对装置进行如下优化调整:脱丙烷塔顶控制压力由1.85MPa下调到1.40MPa,既能满足产品质量要求,又能大幅降低装置蒸汽消耗,塔顶温度和塔底温度均大幅下降,塔底温度由109℃降到95℃左右,蒸汽流量平均值下降约5t/h,使蒸汽单耗下降到约0.1kg标油/t,该装置综合能耗下降7.6kg标油/t。装置年开工时数按8400h计算,全年减少蒸汽消耗4.2×104t,蒸汽价格按150元/t计算,则全年共创节能效益630万元,装置能耗大幅降低。     

气体分馏装置的流程模拟与优化

国内某石化公司气体分馏装置处理能力为65×104t/a,采用先脱丙烷的四塔流程:脱丙烷塔、脱乙烷塔、丙烯塔(两塔)、脱异丁烷塔,主要产品为纯度99.2%(体积分数)以上的工业精丙烯和烷基化原料。以该气体分馏装置为研究对象,采用Aspen Plus流程模拟软件,建立与装置实际工况相符合的稳态流程模拟模型。利用此模型,对脱丙烷塔、脱乙烷塔、丙烯塔等进行灵敏度分析,研究各塔压力、热负荷、进料位置、进料温度、回流比等参数间的相互关系,并以模型为指导,对装置进行如下优化调整:脱丙烷塔顶回流量由60t/h下调到45t/h;脱乙烷塔顶回流量由25t/h下调到22t/h;脱乙烷塔顶压力控制在2.1～2.35MPa;丙烯精馏塔T503AB顶回流量由180t/h降至140t/h,丙烯精馏塔T503CD塔顶回流比(质量比)由23.5降至17,既能满足产品质量要求,又能保证装置能耗最低。提出调整丙烯精馏塔T503AB的进料位置,在125～135层板间再开1～2个进料口,降低装置能耗的建议。通过调整优化,装置能耗由50.26kg标油/t下降到45.28kg标油/t,且每年增产丙烯约1960t,产生经济效益1205万元。     

偏三甲苯装置节能研究

在偏三甲苯装置常规双塔热集成精馏工艺基础上,分析了重沸器高温凝结水通过两级闪蒸发生1.0MPa蒸汽和0.4MPa蒸汽,比直接高温凝结水外送可降低能耗2.713kg标油/t原料;以产能5×104t/a的偏三甲苯装置为例,在脱轻塔顶设置热水换热器回收塔顶低温热产生热水,可回收热量10481kW,脱轻塔顶空冷风机大部分可以停开,节约用电153.3kW·h,可节约能耗24.22kg标油/t原料,节约操作费用925万元/a,该部分投资工程费约300万,回收期短;100×104t/a PX装置吸附分离单元抽余液塔顶气富裕热量5WM,该抽余液塔顶气直接供给偏三甲苯装置重沸器作热源,可代替3.5MPa蒸汽7.614t/h,扣除产1.0MPa蒸汽的能耗差值,可以节约能耗4.321kg标油/t原料;以上措施能耗合计降低31.254kg标油/t原料。还可通过优化换热流程、热进料热出料、采用节能设备、设置在线分析仪、装置卡边操作、改用导热油作热源等措施进一步稳定装置操作及降低能耗。这些节能方法投资回收期短,经济性好,可实施性强,对同类装置的工程设计及装置节能操作具有借鉴意义。     

洛阳石化延迟焦化装置节能分析

洛阳石化140×104t/a延迟焦化装置采用"一炉两塔"和"可灵活调节循环比"的工艺流程,2008年和2009年装置综合能耗分别为35.42kg标油/t和33.36kg标油/t,与设计值、中国石化平均水平(24.27kg标油/t)相比差距较大。综合分析,能耗较高的原因包括蜡油汽包产0.4MPa蒸汽未计入能耗、1.0MPa蒸汽放空、低温热回收系统未投用、蜡油热输出量小、装置加工负荷率低以及加热炉效率低等。为此,对装置采取用0.4MPa蒸汽替代1.0MPa蒸汽;回收分馏塔顶油气、接触冷却塔顶油气和冷焦水低温热量;增加稳定汽油热出料流程;增设节电变频设施,减少电耗;降低加热炉排烟温度和炉外壁温度;加热炉进料泵叶轮抽级或更换为小叶轮,降压节能;增上加热炉先进控制(APC)手段,保证加热炉最佳燃烧;加热炉出口管线保温及管托更新换型,增加空气预热器等措施,有效降低装置能耗。     

镇海炼化连续重整装置流程模拟与优化

中国石化镇海炼化Ⅳ套连续重整装置处理能力为120×104t/a,重整、催化剂再生部分采用美国UOP公司专利技术,其中预加氢分馏部分采用先汽提后分馏的两塔流程,重整油后分馏部分采用先脱丁烷的三塔流程:脱丁烷塔、脱己烷塔、脱戊烷塔,主要产品为高辛烷值重整汽油(芳烃)以及大量副产氢气。以该连续重整装置为研究对象,采用Aspen Plus流程模拟软件,建成了装置预分馏部分以及重整后分馏部分与实际工况相吻合的稳态流程模拟模型。利用此模型,对重整装置的汽提塔、石脑油分馏塔、稳定塔、脱己烷塔、脱戊烷塔进行综合分析。以节能降耗为目标,对稳定塔和脱己烷塔进行如下操作参数优化:脱丁烷塔顶压力由0.92MPa降至0.80MPa,脱己烷塔顶压力由0.03MPa降至0.01MPa。装置优化后,脱丁烷塔底蒸汽消耗减少2.2t/h,脱己烷塔底蒸汽消耗减少3.0t/h,合计装置节能2.55kg标油/t,全年可产生经济效益727万元。     

湛江东兴气体分馏装置流程模拟应用

以湛江东兴石化公司10×104t/a气体分馏装置为实施对象,运用Aspen Plus软件,以装置实际操作数据作为基础数据,建立气分装置流程模拟模型。利用模型和软件的灵敏度分析等功能,对脱丙烷塔、脱乙烷塔、精丙烯塔进行模拟分析,指导装置生产,实现装置优化、增效。2009年,根据模拟结果,对脱丙烷塔进行降温降压调整,结果显示:调整后脱丙烷塔顶压力从1.81MPa降至1.50MPa,塔底温度由104℃降至95℃,节约蒸汽0.6t/h,气分装置能耗下降3.8kg标油/t,测算可产生经济效益103.68万元。根据模拟结果,同时对脱丙烷塔、脱乙烷塔、精丙烯塔的回流量进行调整(降低),其中脱丙烷塔顶回流量由13.3t/h降至8.8t/h。另外,通过对脱丙烷塔降温降压操作的成功应用,可推及丙烯塔的操作中,如在催化裂化装置分馏塔低温热供给负荷较低时,可对丙烯塔进行降温降压操作,达到节能的效果。     

延迟焦化装置的能耗分析及节能优化实践

中国海油惠州炼油分公司420× 104t/a延迟焦化装置通过停用解吸塔上重沸器3.5MPa蒸汽、停用柴油汽提塔1.0MPa汽提蒸汽、降低循环比、采用先进控制(APC)提高加热炉热效率、降低高压水泵和罐区减渣原料泵电耗、提高水的回用率、加大装置处理量等工艺优化措施,装置综合能耗比设计能耗39.03kg标油/t原料降低3kg标油/t原料.为了进一步降低装置能耗,达到国内其他先进装置的能耗水平,该装置在2011年利用检修时机,通过加热炉节能改造降低排烟温度、利用柴油低温热发生0.45MPa蒸汽、焦化富气压缩机叶轮更换、焦炭塔区特阀汽封线改造等节能改造措施.加热炉热效率由89％提高至91.5％,节约3.5MPa蒸汽用量约6.5t/h,同时减少了燃料气、蒸汽和电的消耗,使装置能耗总体降低3.16kg标油/t原料.装置节能改造每年可增加4000万元的经济效益.     

蜡油加氢装置节能优化分析

中国石化洛阳分公司220×104t/a蜡油加氢装置设计年开工时数8400h,主要由反应部分(包括新氢、循化氢压缩机、循环氢脱硫)、分馏部分、富氢气体脱硫部分、热回收和产汽系统以及蜡油加氢处理装置公用工程部分等组成。主要生产低硫含量的精制蜡油,为催化裂化装置提供优质原料,同时副产少量石脑油和柴油,富氢气体经脱硫后去制氢装置作原料。装置于2009年5月20日一次开车成功,设计能耗为12.96kg标油/t。开工运行一周年以来,蜡油加氢处理装置通过开展装置优化,节水、节电、节气,增大装置加工负荷,大幅降低了能耗。2009年蜡油加氢处理装置累计综合能耗为12.46kg标油/t,达到设计要求。2010年,通过节能优化措施,综合能耗从2009年的12.46kg标油/t降至8.85kg标油/t,下降3.46kg标油/t,降幅达29%,在中国石化(Sinopec)同类装置中名列前茅。     

洛阳石化二套联合催化装置能耗升高的原因及对策

中国石化洛阳分公司二套联合催化装置设计为140×104t/a同轴式重油催化裂化装置。2008年5月进行FDFCC-Ⅲ技术改造,进料性质由减压蜡油改为加氢蜡油后,装置的能耗基本维持在65kg标油/t原料以下。2010年6~8月份能耗分别为66.51kg标油/t原料、79.90kg标油/t原料和71.3kg标油/t原料,均超出年度能耗目标值65kg标油/t原料。深度分析显示,装置设备运行异常,非计划停工、检修,是造成装置生焦率、电耗、蒸汽升高的主要原因;计量检测仪表不准,能耗统计、分摊及进出热物料的平衡计算是造成装置能耗升高的次要原因。通过提高设备检修质量,加强设备维护管理,避免非计划停工,以及认真统计、核算,上报相关数据等措施,9月份装置的能耗降为60.83kg标油/t,较8月份的71.3kg标油/t原料,降低了10.47kg标油/t原料。装置1~9月份累计能耗达到65.35kg标油/t原料,已接近2010年能耗目标值65kg标油/t原料。     

余热回收用热管及热管式换热器的研究

简要介绍了热管及热管式换热器的工作原理,热管式换热器在工业余热回收中的应用,以及热管式换热器运行过程中防止积灰和低温腐蚀等问题的有效措施。     

On the steady‐state modelling of a two‐stage evaporator system

We develop and validate against experimental measurements a steady‐state two‐stage flooded refrigerant evaporator model for a heat pump drying system. A prototype two‐stage heat pump dryer test facility was designed, built and instrumented to provide the required measurements for the validation of the model. Repeatability and data quality tests were conducted to evaluate the accuracy of measurements. Experimental data could be reproduced to within ±6.5 per cent of replicated air and refrigerant side measurements for the same evaporator's air inlet conditions while the discrepancy of energy balance at the air‐side and refrigerant‐side was observed to be within ±8.9 per cent. The two‐stage evaporator model predicted the air‐side total heat and latent heat transfer of the two‐stage evaporator to within (?6.3 per cent, 7.6 per cent) and (?11.5 per cent, 9.5 per cent), respectively. On the refrigerant‐side, the model enabled the calculation of the degree of superheat to within (?10.6 per cent, 1.7 per cent). The model has shown that there is significant improvement in the heat recovered from a two‐stage evaporator system compared to a single evaporator system. In addition, the model demonstrated that the improvement in total heat recovery could be as high as 40 per cent over its base‐value when the latent to total load at the two‐stage evaporator is increased. Copyright © 2001 John Wiley & Sons, Ltd.     

显热储热材料的制备及性能研究

采用水泥作为材料的胶凝剂,添加热容、热导率大的物质作为骨料来制备混凝土储热材料。研究表明:当铝酸盐水泥含量为10%时,材料的抗压、抗折强度能满足工业需求;材料的比热容随温度的升高先增大,在500℃时达到最大,后随着温度的升高反而降低;材料的热导率随着石墨粉含量的增加几乎成直线上升,当石墨含量为5%时材料的热导率大于1.7W/(m·K)。     

间歇式热处理炉传热计算与分析

建立了台车式热处理炉炉膛传热数学模型和辐射换热器工作模型,分析了换热器的传热特性（空气预热温度、壁温、传热系数）随炉况的变化。结果表明,辐射换热器的传热特性随炉子的升温及保温过程变化而波动很大,因而对炉子的热工性能产生了影响。     

Quantification of the European industrial heat demand by branch and temperature level

We present the first comprehensive estimate of the final energy demand for heat in all EU28 member states for the reference year 2012, differentiated by temperature levels, comparing two different approaches. Two different calculation approaches based on different data sets yielded estimates of the total final energy demand for heat in the EU28 of 8150 PJ and 8518 PJ in 2012, respectively. Approach 1 distinguishes between three different process heat (PH) temperature levels and results in final energy demand for heat <100°C: 2077 PJ, 100–400°C: 2214 PJ and >400°C: 3859 PJ. The second approach distinguishes between low temperature space heat and hot water (<100°C: 1161 PJ) and four different PH temperature levels with a resulting energy demand of <100°C: 1027 PJ, 100–500°C: 1785 PJ, 500–1000°C: 1679 PJ and >1000°C: 2865 PJ. The high share of high‐temperature heat illustrates the limits to the potential decarbonisation of industrial thermal processes with renewable energy sources such as (non‐concentrating) solar thermal, geothermal or environmental heat. Therefore specific information on required temperature levels is of the essence. This, in turn, points out the relevance of renewable electricity and synthetic fuels based on renewable power for a significant reduction of CO₂ emissions from the industry sector in Europe. Considering current data quality, it is recommended to develop a consistent, comprehensive methodology to significantly improve the data basis on industrial heat demand. Copyright © 2015 John Wiley & Sons, Ltd.     

Heat pump dryer Part 1: Simulation of the models

Heat pump dryer is a complex system because of the interaction of heat and mass transfer of the working fluids. Since the system cannot be completely close, ambient conditions (temperature and humidity) influence the performance of the system. To investigate the performance of the heat pump dryer thoroughly, simulation models of heat pump dryer components have been developed. The finite-difference method was employed in the simulation to examine the state of the working fluids and heat and mass transfer. The simulation of each component can be used to construct different system configurations the results of which are reported in Part 2.     

国内分离式热管概况与热环研究的小结及展望

本文对我国分离式热管技术的研究进行了简要概况,针对工程中热源在上,冷源在下及冷热源相距较远时的热量传递问题,在分析了一般分离式热管及“水回路”等技术的基础上,对一种新型分离式热管－泵或风机驱动的动力型分离式热管（简称热环）的研究进行了小结和展望。     

Field test of a novel combined system of a high-efficiency heating/cooling heat pump and a clathrate cool storage unit

The Research Laboratory of Kyushu Electric Power Co., Inc. (KEPCO) installed a novel system in March 1992 which is a combination of a super heat pump with about twice the performance of a conventional one and a compact chemical storage-type clathrate cool storage unit. A field test was implemented by integrating these units into an actual air-conditioning system. As a result of the test, system performance was determined and the effectiveness of the system was confirmed. © 1998 Scripta Technica. Heat Trans Jpn Res, 26(6): 410–418, 1997     

Augmentation of heat transfer through passive techniques

The thermal performance of energy preservation systems is greatly improved by increasing miniaturization and boosting. These are imaginative (or Promethean) techniques to enhance heat transfer. Enhancement methods of heat transfer draw great attention in front of the industrial sector because of their ability to provide energy savings and raise the economic efficiency of thermal systems. Three techniques these methods are categorized; those are active, passive, and compound. Different types of components are used in passive methods because of the transfer/working fluid flow path to the enhancement of the heat transfer rate. In this article, the subject of the review was the passive heat transfer enhancement methods including inserts (conical strips, winglets, twisted tapes, baffles), porous materials, coil/helical/spiral tubes, rough surfaces (corrugated/ribbed surfaces), extended surfaces (fins) and nanofluids (mono and hybrid nanofluid). Recent passive heat transfer enhancement techniques are studied in this article as they are cost-effective and reliable, and also comparably passive methods do not need any extra power to promote the energy conversion systems' thermal efficiency than active methods. In the passive approaches, various components are applied to the heat transfer/working fluid flow path to improve the heat transfer rate. The passive heat transfer enhancement methods studied in this article include inserts (twisted tapes, conical strips, baffles, winglets), extended surfaces (fins), porous materials, coil/helical/spiral tubes, rough surfaces (corrugated/ribbed surfaces), and nanofluids (mono and hybrid nanofluid). From the pioneers' research work, it is clear that a lower twist ratio and lower pitch, lesser winglet angles can provide more heat transfer rate and a little bit more friction factor. In the case of nanofluids, a little bit of pumping power is enhanced. Finally, heat transfer enhancement is compared with the thermal performance factor, which is more than unity.     

Heat-spreading analysis of a heat sink base embedded with a heat pipe

A simplified model predicting the heat transfer performance of a heat sink base with a high thermal conductivity was developed. Numerical analysis was performed using the commercial software FLUENT. The investigation indicates that for heat sink bases with a high effective thermal conductivity, such as the base embedded with a typical heat pipe, the entire heat sink can be modeled as a flat plate with a uniform temperature and an effective convection heat transfer coefficient. This simplified model can be used to determine the heat transfer performance of a heat sink embedded with a typical heat pipe or vapor chamber.