300 MW機(jī)組循環(huán)水泵的在線優(yōu)化運行田小冬,劉福君唐山熱電公司,河北唐山063029[摘要] 介紹了300 MW機(jī)組循環(huán)水泵在線優(yōu)化運行的計算方法、模塊結(jié)構(gòu)及優(yōu)化實施方法。優(yōu)化系統(tǒng)投入后,解決了循環(huán)水泵起停的隨意性和盲目性,節(jié)電效果較好。[關(guān)鍵詞] 300MW機(jī)組;汽輪機(jī);凝汽器;循環(huán)水泵;在線優(yōu)化[中圖分類號] TK264. I[文獻(xiàn)標(biāo)識碼] B[文章編號] 1002 - 3364(2008)01 - 0083 - 02唐山熱電公司300 MW機(jī)組汽輪機(jī)為東方汽輪機(jī)式中:Dc為凝汽器蒸汽負(fù)荷,kg/s;Dw為循環(huán)水流廠制造的C30/220- 16. 7/0. 3/537/537型、亞臨界、- -量,kg/s;h,為排汽焓;h。為凝結(jié)水焓,kJ/kg。當(dāng)排汽次中間再熱.兩缸兩排汽、抽汽供熱式,配3臺長沙水泵壓力變化不大時,Oh=h,- he 近似不變,一般取Oh=廠生產(chǎn)的60LKXC - 26型立式混流循環(huán)水泵。2臺泵或2 250 kJ/kg。實測的不同臺數(shù)循環(huán)水泵運行時的循3臺泵運行時,凝汽器真空提高,供電煤耗下降,但循環(huán)環(huán)水流量和循環(huán)水泵總耗電量見表2。水泵耗電量大,使供電煤耗上升。因此，合理安排循環(huán)表2不同臺數(shù)循環(huán)水泵運行時的水泵的運行臺數(shù),對機(jī)組運行經(jīng)濟(jì)性具有重要意義。本循環(huán)水流量和循環(huán)水泵總耗電量文介紹了循環(huán)水泵運行臺數(shù)在線優(yōu)化的實施方法,以及項目，1號機(jī)組2號機(jī)組循環(huán)水系運行臺數(shù)123廠23在1號、2號機(jī)組上的應(yīng)用情況。循環(huán)水流量/t*h-I 17748 30240 40284 18212 30 96041 177循環(huán)水泵功率/kW 1237 2402 3498 1325 2579 3 6041循環(huán)水泵在線 優(yōu)化計算方法和步驟:(3)凝汽器端差8t計算: .(1)循環(huán)水人口水溫L為實測值與循環(huán)水泵運行8=一xA臺數(shù)對入口水溫影響的修正值相加。試驗測得不同臺eT8IF一1數(shù)循環(huán)水泵運行時修正數(shù)值見表1。式中:Aw為凝汽器冷卻面積(18000 m?);K為總體傳表1不同臺循環(huán)水泵運對循環(huán)水入口水溫的修正值熱系數(shù):K= 14 650qpw qqoqs ,其中:支循環(huán)水泵循環(huán)水泵循環(huán)水泵 循環(huán)水泵循環(huán)水泵φ-冷卻表面清潔程度修正系數(shù),開式循環(huán)時q=不由1臺改由2臺改由3臺改由2臺改0.8~0.85,閉式循環(huán)0. 75~0.8,不清潔時充運行臺數(shù)變至2臺變至3臺 變至2臺變至1臺0.65~0.75,選取φ=0.85;循環(huán)水入口溫度修正值/C+2+1.5-1.50.12q(1+0.152)q-一流速與管徑修正系數(shù):q°=(會)力(2)循環(huán)水溫升Ot計算由熱平衡方程可求得: .其中,Cw為循環(huán)水流速; d為冷卻水管內(nèi)徑;1電DcX(h,-h)為循環(huán)水入口水溫。DwX4. 187作者簡介:田小冬 ,唐山熱電公司副總工程師兼發(fā)電部部長。八E-mail:txd6280@dtts. cng.-水溫修正系數(shù):=1-.42√2(35-t1)21號機(jī)組DCS 2號 機(jī)組DCS1 000DCS路由器 |[ DCS路由器qo---流程修正系數(shù):q.=1+T(1 - t:/35),z為凝PI雙機(jī)服務(wù)器]C性能計算服務(wù)器汽器流程數(shù)。廠內(nèi)管理信息ps一 蒸汽負(fù)荷修正系數(shù):φs=δ(δ- 2),當(dāng)dc> de'系統(tǒng)(MIS)網(wǎng)l用戶用戶2][用戶3用戶]時,δ=1,否則8=dc/dc。其中,dc為單位面圖1生產(chǎn)管理系統(tǒng)網(wǎng)絡(luò)結(jié)構(gòu)積蒸汽負(fù)荷;de°為單位面積蒸汽負(fù)荷的臨界值,de =(0.9-0.012t )de ;dc'為設(shè)計單位面從實時數(shù)據(jù)庫中獲取計算所毒數(shù)據(jù)積蒸汽負(fù)荷,其值為30. 1 kg/m2.(4)計算不同臺數(shù)循環(huán)水泵運行時汽輪機(jī)排汽溫從給定數(shù)據(jù)中獲取計算所需數(shù)據(jù)度:t.=t+Ot+8t式中:,一汽輪 機(jī)排汽溫度(凝汽器壓力px對應(yīng)的出箱壞水入口水溫、循環(huán)水量變化飽和蒸汽溫度),C;(5)根據(jù)排汽溫度1,查出對應(yīng)不同臺數(shù)循環(huán)水泵通過凝結(jié)器變工況，計算出在假定的循環(huán)水泵運行臺數(shù)下排汽溫度運行時的排汽壓力p。。(6)計算排汽壓力變化對機(jī)組熱耗影響。采用制由排汽溫度計算出排汽樂力變化由排汽壓力變化，計算出對汽輪機(jī)熱耗的影響造廠提供的額定工況下排汽壓力對熱耗影響的關(guān)系曲線與排汽量變化擬合方法計算。計算出汽輪機(jī)熱耗變化后對經(jīng)濟(jì)性的影啊、循環(huán)水泵耗電量增加對經(jīng)濟(jì)性的影響(7)綜合比較汽輪機(jī)熱耗與循環(huán)水泵耗功的變化，給出在線優(yōu)化運行結(jié)果。給出優(yōu)化運行結(jié)論團(tuán)2循環(huán)水泵在線優(yōu)化程序 :2循環(huán)水泵在線優(yōu)化運行實現(xiàn)循環(huán)水泵優(yōu)化運行是在生產(chǎn)管理信息系統(tǒng)上實現(xiàn)3循環(huán)水泵優(yōu)化運行情況的,該系統(tǒng)的網(wǎng)絡(luò)結(jié)構(gòu)見圖1。唐山熱電公司1號、2號機(jī)組循環(huán)水泵優(yōu)化運行模循環(huán)水泵在線優(yōu)化運行計算機(jī)程序見圖2。塊于2006年10月30日投人運行,數(shù)據(jù)采樣和模塊運行周期為5 min。循環(huán)水泵優(yōu)化運行指導(dǎo)畫面見圖3。系統(tǒng)投運后,從根本上解決循環(huán)百查名條件水泵的隨意和盲目起停,保證了凝汽機(jī)組?；貦C(jī)組工重牧」器真空接近最佳值,大幅降低了廠用O鹵環(huán)術(shù)無房行把堂電,提高了機(jī)組運行經(jīng)濟(jì)性。2006 年當(dāng)前灣環(huán)水策運行方式(紅色表示運行，是色表示停止)1號浦環(huán)水豪運行2號佛環(huán)水柔送行3號德環(huán)水蒙運行11月循環(huán)水泵電耗為0.64%，同期電環(huán)水茶運行方式優(yōu)化建議耗為0, 76%,同比下降了0. 12%。T環(huán)水象百新運行狀者優(yōu)化計在區(qū)同蔡當(dāng)前26潘環(huán)水聚運行200元/小時203.77元/小時[參考文獻(xiàn)]流就定3臺鋪環(huán)水栗運行1] 剪天聰.汽輪機(jī)原理[M].北京:水-循環(huán)永茶雪托電斯金部優(yōu)化運行承農(nóng)益379.22元/小時66.72元/小時312.49元/小時力電力出版社,1992.熱南環(huán)水蜜和康K景實時熟務(wù)力政務(wù)單位代號[2] C300/220 - 16. 7/0. 3/537/537型10機(jī)舊有功功車汽輪機(jī)熱力特性書[Z]東方汽輪機(jī)電”101898.63kPa廠,2001.1都機(jī)組制追環(huán)水入口溫度10.171日機(jī)組B制事壞水入口溫度10.24[3]吳季蘭. 汽輪機(jī)設(shè)備及系統(tǒng)[M].北京:8中國電力出版社,006.(下轉(zhuǎn)第88頁)八圈3循環(huán)水泵運行 臺數(shù)優(yōu)化指示畫面CAUSE ANALYSIS FOR STALL OF AXIAL FANS OPERATING IN PARALLELHOU Fan- jun' ,GENG Li, WANG Jia - xin'1. Shandong Electric Power Research Institute, Jinan 250002，Shandong Province, PRC2. Huangtai Themal Power Plant, Jinan 250100, Shandong Province, PRCAbstract:The stall of a forced draft fan and a primary air fan for boiler no. 2 in one power plant has been analysed. Through test andinspection, it was found that the main cause leading to stall of the forced draft fan is reversely installed the outlet guide blades, andthat leading to stall of the primary air fan is most higher ventilation resistance and most higher outlet temperature of the coal pulveri-zer. After retrofitting, no stall appears again on the said forced draft fan and the primary air fan.Key words:axial fan; stall; guide blades; coal pulverizing system; ventilation resistance(上接第79頁)PROBLEMS EXISTING IN THE SPRAYING SYSTEM OFLARGE TOOTH GEAR IN BALL MILLSLI Xiong :Guodian Anshun Power Plant, Anshun 561000 ,Guizhou Province, PRCAbstract: In operation of the spraying system for large tooth gear in the ball mills at Guodian Anshun Power Plant, some problems,such as troubles of the spraying oil pump frequently occurred, and the reversal valve of the spraying head can't automatically opera-ted etc. ，have often appeared. For this, analysis has been carried out, and corresponding measures being put forward. After imple-mentation, the troubles have been substantially reduced, ensuring normal operation of the system.Key words; ball mill; tooth gear; spraying oil pump; reversal system四0004000000000000400040.14(上接第82頁)COORDINATING APPLICATION OF FUEL GASCOMPRESSOR ON MICRO - GAS - TURBINEZUO Zhi -yuan, LI Xi-ya, YANG Xiao- xiDongguan College of Science & Technology ，Dongguan 523808 , Guangdong Province, PRCAbstract:The influence of fuel gas pressure upon the performance of micro - gas - turbine has been brielly discussed, the developmentsituation of fuel gas compressor applied in coordination with micro - gas - turbine being presented. Combined with actual situation ofthe designed pressure in pipelines of the natural gas transportation and distribution system and the end - pressure of customers, anapproach to the influence of fuel gas compressor upon the strategic decision of a micro - gas - turbine project has been made, and somerecommendations for equiping fuel gas compressor being put forward.Key words:fuel gas compressor; micro- gas - turbine; transportation and distibution of natural gas; distributed energy system; pipeline pressure交(上接第84頁)流ON - LINE OPTIMIZED OPERATION OF THE CIRCULATING WATERPUMP FOR 300 MW UNITTIAN Xiao- dong, LIU Fu- jun電Tangshan Thermal Power Co Ltd, Tangshan 063029, Hebei Province, PRCAbstract: The calculation method, module structure, and optimization - implementing method of the on - line optimized operation for circulating water pump of 300 MW unit have been presented. After putting the said optimization system into operation, the casualness and blindness八in start - up and shutdown of circulating water pump have been overcome, having better ectricity - saving ffectiveness.Key words:300 MW unit; steam turbine; condenser; circulating water pump; on - line optimization