可再生能源分布式能源冷热电联供
燃气轮机进空气冷却方式的经济性比选
郭甲生，刘育权”，包春，李勇”，刘伟
（1.上海航天能源股份有限公司，上海201201；2.航天智慧能源研究院，上海201201；3.广州供电局有限公司，广东广州510000：4.广州发展集团股份有限公司，广东广州510000;5.上海交通大学，上海201000)
摘要：以广州地区某园区燃气分布式能源站（以燃气轮机作为原动机）为例提出采用蒸汽型溴化锂吸收式冷水机组（以下简称吸收式冷水机组）、电制冷机组对燃气轮机进气（空气）进行冷却对两种制冷设备进行选型与造价测算.以燃气轮机发电机组在全年100%负荷率（指发电功率的负荷率）条件下测算燃气轮机进气冷却前后的燃气轮机耗气量、燃气轮机发电机组输出电功 率、余热锅炉蒸汽产量.计算采用两种制冷设备时的项目收益与静态投资回收期确定最佳制冷设备.吸收式冷水机组、电制冷机组的造价分别为420×10、350×10元，典型年项目收益分别为45.43×10*213.45×10元静态投资回收期分别为9.24、1.64a.采用电制冷机组冷却燃气轮机进气经济性比较理想.
关键词：燃气轮机：进气冷却：收益：静态投资回收期
DOI:10.13608/j-cnki.1000-4416.2019.03.006
中图分类号：TU995.7文献标志码：B文章编号：1000-4416（2019)03-0A22-03
燃气轮机耗气量、燃气轮机发电机组输出电功率、余热锅炉蒸汽产量，计算采用两种制冷设备时的项目 收益与静态投资回收期确定最佳制冷设备，本文对测算中的相关参数进行了简化处理将吸收式冷水机组的热力系数、电制冷机组制冷性能系数视为不随制冷设备的负荷率发生变化分别取1.4、4.0.
1概述
度升高时空气密度减小单位时间进入燃气轮机的 燃气轮机性能受环境温度影响较大，当环境温空气质量减少，从而使燃气轮机的输出功率下降.当环境温度升高时压气机的压缩比降低压气机的功耗也将增大，冷却燃气轮机进空气（以下简称进施[1-2] 气）是确保高温地区燃气轮机输出功率的有效措
2工程概况
广州地区某园区天然气分布式能源站以管道天然气作为燃料（低热值为34.18MJ/m）天然气经调压及计量后进入燃气轮机燃气轮机发电机组发电并入电网燃气轮机排放的高温烟气通过余热水通过凝结水管道回输至能源站、不足蒸汽利用燃 锅炉产生过热蒸汽供园区内用户使用用户处凝结气调峰锅炉提供.
本文以广州地区某园区燃气分布式能源站（以燃气轮机作为原动机）为例，提出采用蒸汽型溴化锂吸收式冷水机组（以下简称吸收式冷水机组）、电制冷机组对燃气轮机进气进行冷却，对两种制冷设 备进行选型与造价测算（不考虑制冷设备的备用）.以燃气轮机发电机组在全年100%负荷率（指发电功率的负荷率）下测算燃气轮机进气冷却前后的
能源站配置2台装机容量为14.4MW的燃气
轮机发电机组额定发电功率为13.95MW额定耗 气量4509m²/h.2台余热锅炉，供汽压力2.5MPa温度250°℃单台额定蒸发量27.4t/h1台燃气轮机配置1台余热锅炉.1台蒸发量为25t/h的燃气调峰锅炉用于补充不足蒸汽量.1台额定制t/h进汽压力为0.8MPa进汽温度为170°℃，为园 冷量为3867kW的吸收式冷水机组耗汽量为3.93区办公建筑供冷-
湿空气比h的计算式为[：
(1)
表1不同室外空气干球温度范围对应的待冷却温度
室外空气干球温度范围{ 待冷却温度/℃{θ ≤10 {10<{θ≤15 15 <{θ) ≤20 {5 1020<{ ≤25 {θ}102530 {θ20注：{θ=0/℃
3制冷设备选取
①负荷预测
量见图1、2数据来自中国建筑热环境分析专用气 广州地区典型年室外空气逐时干球温度、含湿象数据集）（中国建筑工业出版社2005年出版）.全年运行时间按8760h考虑图1.2中第1h表推.不同室外空气干球温度范围对应的待冷却温度 示[0:001:00）第2h表示[1:002:00），以此类见表1.
式中h 一湿空气比kJ/kg
d--空气逐时含湿量kg/kg
100%负荷率下，冷却后燃气轮机进气（干空气）质量流量保持44kg/s.根据图1、2及表1数据由式（1）可计算得到100%负荷率下冷却空气 的逐时冷负荷见图3.
图1广州地区典型年室外空气逐时干球温度
图3100%负荷率下冷却空气的逐时冷负荷
②制冷设备选型
单独配置.由图3可知在100%负荷率下冷却空设备的额定制冷量选取为3500kW. 气的最大逐时冷负荷为3159kW.考虑裕量制冷
4经济性分析
4.1造价与运行费用
①吸收式冷水机组
图2广州地区典型年室外空气逐时含湿量
吸收式冷水机组额定制冷量为3500kW，单位计算得到造价为420×10元 制冷量造价（含设备费、安装费）取1200元/kW可
吸收式冷水机组典型年耗汽量m的计算式为：
式中m--吸收式冷水机组典型年耗汽量
-时间h取1h
一第：小时冷却空气冷负荷kW
I---吸收式冷水机组的热力系数，本文取
Φ.1t/h蒸汽对应的热功率kWh/t，本文取700kWh/t
由图3数据及式（2），可计算得到吸收式冷水机组典型年耗汽量为10188t.蒸汽价格取348元/：可计算得到吸收式冷水机组典型年蒸汽费用为 354.54 ×10^元/a.
②电制冷机组
电制冷机组额定制冷量为3500kW单位制冷量造价（含设备费、安装费）取1000元/kW可计算得到造价为350×10元
电制冷机组典型年耗电量E的计算式为：
=式中E-电制冷机组典型年耗电量kWh
Ior--电制冷机组的制冷性能系数本文取
4.0
由图3数据及式（3），可计算得到电制冷机组典型年耗电量为250.38×10kWh.电价取0.745元/（kWh）可计算得到电制冷机组典型年电费为186.53×10元/a
4.2收益
不考虑空气含湿量对燃气轮机性能的影响在100%负荷率下燃气轮机单位时间耗气量V、燃气轮机发电机组输出电功率P、余热锅炉单位时间蒸汽产量随燃气轮机进气温度的函数关系分别为：
q =0. 002 20 0. 181 90 30. 167
式中V-燃气轮机单位时间耗气量m/h
(z）
(3)
V=0.440 40² -52.1248 5 218.6(4)
(5)
(6)
0-燃气轮机进气温度，C
q-余热锅炉单位时间蒸汽产量1/h
由图1、表1数据及式（4）-（6），可计算得到，采取进气冷却后燃气轮机耗气量增加317.28×10m/a燃气轮机发电机组输出电量增加1342.38 ×10*kWh/a余热锅炉蒸汽产量增加8813t/a
①吸收式冷水机组
采用吸收式冷水机组时，典型年的蒸汽缺口为1375可计算得到蒸汽费用为47.85×10元/a.天然气价格取2.858元/m，可计算得到由燃气轮机耗气量增加导致的天然气费用为906.79×10 元/a.由燃气轮机进气冷却获得的发电收益为1000.07×10元/a.由以上数据，可计算得到采用吸收式冷水机组时典型年项目收益为45.43×10元/a.
②电制冷机组
采用电制冷机组时燃气轮机发电机组增加的发电量除满足电制冷机组制冷外还剩余1092×10kWh.由已知数据可计算得到采用电制冷机组时典型年项目收益为213.45×10元/a
4.3静态投资回收期
吸收式冷水机组、电制冷机组的造价分别为420×10、350×10元，典型年项目收益分别为45.43×10、213.45×10元/a.可计算得到采用两种制冷设备的静态投资回收期分别为9.24、1.64a.由计算结果可知采用电制冷机组冷却燃气轮机进气时经济性比较理想.
5结论
吸收式冷水机组、电制冷机组的造价分别为420×10、350×10元，典型年项目收益分别为45.43×10、213.45×10元静态投资回收期分别为9.24、1.64a.采用电制冷机组冷却燃气轮机进 气经济性比较理想.
参考文献：
[1]焦润平付忠广毕克等、燃气轮机机组进气冷却技术分析评估[J].热力发电200736（4)：18-23.[2]左政华资，燃气轮机进气冷却对冷热电联产性能的 影响[J].爆气与热力200424(7):369-371.[3]赵荣义范存养薛殿华等.空气调节[M].2版.北京：中国建筑工业出版社1994:6-9.
software to establish the overall model of the heating pipeline and the steel truss and caleulate the deformaheating pipeline has litle efeet on the deformation of tion. The calculation results show that the thrust of thethe truss and the deformation of the truss is posed mainly of the thermal expansion and contraction deformation caused by the seasonal temperature differ-the Midas software have the same deformation direc ence. The two methods of the mechanical formula andtion. The Darth software method has a snaller deform ation amount.
truss; deformation; fixed anchor thrust; Midas software Key words: heating pipeline; super-arge steelVentilation andThermalEnvironment BuildingHeating Air ConditioningInfluence of Occupant WindowingBehaviour on Comprehensive Heat Transfer Coefficient of Building Envelope
Abstract: Based on the heat balance analysis
q p eq q d ping envelope reflecting the insulation performance and air tightness of the building envelope as well as theprehensive heat transer coefficient prehensive- ly considering the insulation performance and air tightlation heat release caused by the occupant windowing ness of the building envelope and the winxlowing ventibehaviour are defined. Taking a resicdential building in Tianjin as an example the actual measurement andquestionnaire are used to analyze the influenee of oecu pant windowing behaviour on the prehensive heattransfer coefficient of the building envelope. As the in-door and outdoor temperature diference decreases ( the corresponding outdoor temperature rises on the premisethat the indoor temperature remains basically stable) the increase in the prehensive heat transfer coeffcient of the building envelope is caused by an increase in the occupant windowing behaviour. As the indoorand outdoor temperature difference increases the de- crease in the prehensive heat transfer coefficient ofthe building envelope is caused by a decrease in theoccupant windowing behaviour so that the prehen sive heat transfer coefficient of the building envelopeing envelope The resuls are basically consistent with Pq a po ta asn eq oeq ai o spdoor lemerature is higher theoccupant windowing the results of the resident questionnaire ( when the outperature is lower the windowing time is resluced or e- phenomenon is more mon; when the outdoor temhensive heat transfer coeficient of the building enve- ven the window is not opened). Taking the pre-lope under different indoor and outdoor temperaturetemperature diference at the inflection point of the oc cupant windowing behaviour is calculated by the Pear- differences as the data sample the indoor and outdoorson correlation analysis method. For the residentialbuilding the indoor and outdoor temperature difference at the inflection point of the oceupant windowing behaviour is 24 02 C.
Key words: behaviour prehensive heat residential building building entransfer coefficient
RenewableEnergyDistributed Energy Source and Combined Cooling Economic Comparison of Heating and Power
tion in a certain park in Guangzhou ( using gas turbine Abstract: Taking a gas distribated energy sta-the steam-type lithium bromide absorption chiller as the prime mower)as an example it is proposed thatelectric refrigeration unit are used to cool the gas tur- ( hereinafter referred to as absorption chiller) and thebine inlet air. The selection and cost estimation of twotypes of refrigeration equipment are performed. Under the condition of 100% annual load rate ( the load rateof power generatin)of the gas turbine generalor set the gas consumption of the gas turbine before and afterthe gas turbine inlet air cooling the output electric power of the gas turbine generator set and the steamproduction of the waste heat boiler are estimated. The project revenue and static investment payback periodcaleulated to determine the optimal refrigeration equip- when using two types of refrigeration equipment arement. The costs of the absorption chiller and the elec-tric refrigeration unit are 420 x 10* and 350 × 10* yuan respectively. The typical annual project inesare 45. 43 x 10* and 213. 45 × 10* yuan prespectively. The static investment payback perioxds are 9. 24 andis used to cool the gas turbine inlet air which is eco 1. 64 years zespectively. The electric refrigeration unitnomical.
Key words: gas turbine; inlet air cooling; in-e static investment payback period
and Gas Consumption Equipment Gas Combustion Gas Appliances
Development of Multi-gas Source Mixed Combustion Device
HOU Liquan SHI Lei ZHANG Changjian HOU Beiran XIONG Chuchao LIU Huan LUO Jinghui
gas are difficult to achieve good bustion results on Abstract: Coke oven gas mine gas and naturalriic values. In view of this a multi-gas souree mixed one boiler due lo their different pressures and low calobustion device ( has been authorized by the national invention patent )is developed. The multi-gas source mixed bustion device is mainly posed ofwer bustible gas and air ratio control device igni bustible gas mixing device diffusion bumer blotion gunfire detetion device vale grup main con- trol cabinet and so on. A buffer tank has been added tothe conventional sructural design equipped with a spe cial frequency converter fan and an electric ball valve which are automatically controlled by a program in the
