300 MW 機組循環(huán)水泵的在線(xiàn)優(yōu)化運行

300MW機組循環(huán)水泵的在線(xiàn)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300MW機組循環(huán)水泵在線(xiàn)優(yōu)化運行的計算方法、模塊結構及優(yōu)化實(shí)施方法。優(yōu)化系統投入后,解決了循環(huán)水泵起停的隨意性和盲目性,節電效果較好。[關(guān)鍵詞]300MW機組;汽輪機;凝汽器;循環(huán)水泵;在線(xiàn)優(yōu)化[中圖分類(lèi)號]TK264.1[文獻標識碼]B[文章編號]1002-3364(2008)01-083-02唐山熱電公司300MW機組汽輪機為東方汽輪機式中:De為凝汽器蒸汽負荷,kg/s;Dw為循環(huán)水流廠(chǎng)制造的C300/220-16.70.3/537/537型、亞臨界、一量,kg/s;h,為排汽焓;h為凝結水焓,kJ/kg。當排汽次中間再熱兩缸兩排汽、抽汽供熱式配3臺長(cháng)沙水泵壓力變化不大時(shí),△h=h,-h近似不變,一般取△h=廠(chǎng)生產(chǎn)的60IKXC-26型立式混流循環(huán)水泵。2臺泵或2250kJ/kg。實(shí)測的不同臺數循環(huán)水泵運行時(shí)的循3臺泵運行時(shí),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(jiàn)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不同臺數循環(huán)水泵運行時(shí)的水泵的運行臺數,對機組運行經(jīng)濟性具有重要意義。本循環(huán)水流量和循環(huán)水泵總耗電量文介紹了循環(huán)水泵運行臺數在線(xiàn)優(yōu)化的實(shí)施方法,以及1號機組2號機組在1號、2號機組上的應用情況循環(huán)水泵運行臺數1循環(huán)水流量/t·h-1177483024040284182123096041177循環(huán)水泵功率/kW1237240234981325257936041循環(huán)水泵在線(xiàn)優(yōu)化計算方法和步驟(3)凝汽器端差計算:(1)循環(huán)水入口水溫t1為實(shí)測值與循環(huán)水泵運行臺數對入口水溫影響的修正值相加。試驗測得不同臺數循環(huán)水泵運行時(shí)修正數值見(jiàn)表1。式中:Aw為凝汽器冷卻面積(18000m2);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:K=14650999qu,其中循環(huán)水泵循環(huán)水泵循環(huán)水泵循環(huán)水泵循環(huán)水泵9冷卻表面清潔程度修正系數,開(kāi)式循環(huán)時(shí)中=交運行臺數由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(shí)流變至2臺變至3臺變至2臺變至1臺0.65~0.75,選取g=0.85;循環(huán)水人口溫度+2+1.5修正值/℃1.1Cw流速與管徑修正系數9((2)循環(huán)水溫升△t計算由熱平衡方程可求得:其中,Cw為循環(huán)水流速;d為冷卻水管內徑;h甫△-=x12中國煤化工CNMHG二00作者簡(jiǎn)介:田小冬,唐山熱電公司副總工程師兼發(fā)電部部長(cháng)xd6280@dtts.cnp—水溫修正系數:9=1-014249(3-4)號機組Ds2號機組DCS:g=1+x-2DCS路由DCS路由器流程修正系數10-(1-4/35),x為凝汽器流程數。P雙機服務(wù)器性能計算服務(wù)器廠(chǎng)內管理信息g蒸汽負荷修正系數:g=8(8-2),當dc>dc[用戶(hù)門(mén)[用2】[用戶(hù)3[用戶(hù)時(shí),=1,否則δ=dc/dc。其中,dc為單位面圖1生產(chǎn)管理系統網(wǎng)絡(luò )結構積蒸汽負荷;dcs為單位面積蒸汽負荷的臨界值,dcs=(0.9-0.012t1)d;dc為設計單位面積蒸汽負荷,其值為30.1kg/m2。(4)計算不同臺數循環(huán)水泵運行時(shí)汽輪機排汽溫度式中:t,——汽輪機排汽溫度(凝汽器壓力pk對應的假定循環(huán)水泵臺數改變后,查表得飽和蒸汽溫度),℃C;(5)根據排汽溫度t查出對應不同臺數循環(huán)水泵通過(guò)凝結器變工況,計算出在假定勺循環(huán)水泵運行臺數下排汽溫度運行時(shí)的排汽壓力p。(6)計算排汽壓力變化對機組熱耗影響。采用制造廠(chǎng)提供的額定工況下排汽壓力對熱耗影響的關(guān)系曲線(xiàn)與排汽量變化擬合方法計算。計算出汽輪機熱耗變化后對經(jīng)濟響、循環(huán)水泵耗電量增加對經(jīng)濟(7)綜合比較汽輪機熱耗與循環(huán)水泵耗功的變化給出在線(xiàn)優(yōu)化運行結果。[出優(yōu)化運行結論圖2循環(huán)水泵在線(xiàn)優(yōu)化程序2循環(huán)水泵在線(xiàn)優(yōu)化運行實(shí)現循環(huán)水泵優(yōu)化運行是在生產(chǎn)管理信息系統上實(shí)現3循環(huán)水泵優(yōu)化運行情況的,該系統的網(wǎng)絡(luò )結構見(jiàn)圖1。唐山熱電公司1號、2號機組循環(huán)水泵優(yōu)化運行模循環(huán)水泵在線(xiàn)優(yōu)化運行計算機程序見(jiàn)圖2。塊于2006年10月30日投入運行,數據采樣和模塊運行周期為5min。循環(huán)水泵優(yōu)化運行指導畫(huà)面見(jiàn)圖3。系統投運后,從根本上解決循環(huán)查看條件水泵的隨意和盲目起停,保證了凝汽機組,[機熱器真空接近最佳值,大幅降低了廠(chǎng)用環(huán)水運行導電,提高了機組運行經(jīng)濟性。2006年環(huán)水行方式色表示行色表永停環(huán)水系行運行11月循環(huán)水泵電耗為064%,同期電環(huán)家壇行狀數耗為0.76%同比下降了0.12%。當前2臺水索交圖環(huán)水耗電折量金參考文獻流[1]剪天聰.汽輪機原理[M].北京:水鵡⊙汽力電力出版社,1992位代號[2]C30022016.7/0.3/537/537型1#機組有功巧率汽輪機熱力特性書(shū)[Z].東方汽輪機組么環(huán)水入口溫度中國煤化工輪機設備及系統[M北京:CNMHG出版社,2006(下轉第88頁(yè))圖3循環(huán)水泵運行臺數優(yōu)化指示畫(huà)面CAUSE ANALYSIS FOR STALL OF AXIAL FANS OPERATING IN PARALLELHOU Fan-jun, GENG Li", WANG Jia1. 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-er. 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 resistance②必必辦必必必必必必必必必必必必必辦必必辦必必辦少②小必辦必(上接第79頁(yè))PROBLEMS EXISTING IN THE SPRAYING SYSTEM OFLARGE TOOTH GEAR IN BALL MILLSLi Xionglodian 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 problemsuch 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少①少①必必①小必辦(上接第82頁(yè))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 briefly 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, aapproach 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 distribution of natural gas: distributed energy system: pipeline pressure技術(shù)交流D必必必必①必①①必②必分①辦必必辦必①必小必必①必必必(上接第84頁(yè))ON- LINE OPTIMIZED OPERATION OF THE CIRCULATING WATERPUMP FOR 300 MW UNITTIAN Xiao-dong, LIU Fu-junTangshan Thermal Power Co Ltd, Tangshan 063029, Hebei Province, PRcAbstract: The calculation method, module structure, and optimization中國煤化工 imized operation for circulting water pump of 300 Mw unit have been presented. After putting theCNMHGthe casualness and blindnessA n start-up and shutdown of circulating water pump have been overcomebetter electricity- saving effectivenesKey words: 300 Mw unit; steam turbine; condenser: circulating wateron-line optimization