A+K流量计算书中英文对照

VehicleSpeed车辆速度EngineSpeed发动机转速CalculateLoad计算负荷VehicleLoad车辆荷载MassAirFlowSensor质量空气流量传感器AtmosphericPressure大气压力EngineOilTemperatureSensor发动机机油温度传感器CoolantTemperature冷却液温度IntakeAirTemperature进气温度IntakeAirTemperatureB1S1(Turbo)进气温度b1s1（涡轮）EngineRunTime发动机运行时间IG-ONCoolantTemperatureig-on冷却液温度InitialEngineCoolantTemperature初始发动机冷却液温度IG-ONIntakeAirTemperatureig-on进气温度InitialEngineIntakeAirTemperature发动机进气温度BatteryVoltage电池电压BATTVoltage电瓶电压EngineOilPressure发动机机油压力AcceleratorPosition加速器位置AcceleratorPositionSensorNo.1Voltage% 油门位置传感器1电压AcceleratorPositionSensorNo.2Voltage% 加速器位置传感器2电压% AcceleratorPositionSensorNo.1Voltage 油门位置传感器1号AcceleratorPositionSensorNo.2Voltage加速器位置传感器2电压AcceleratorPositionSensorNo.1FullyClosedLearnValue 油门位置传感器1号全封闭学习值AcceleratorPositionSensorNo.2FullyClosedLearnValue 油门位置传感器2号全封闭学习值EngineStartingTorqueControlCount发动机起动转矩控制计数ThrottlePositionSensorNo.1Voltage%节气门位置传感器1电压% ThrottlePositionSensorNo.2Voltage%节气门位置传感器SystemGuard系统防护OpenSideMalfunction开侧故障ThrottleRequestPosition节气门位置ThrottleSensorPosition节气门传感器位置ThrottlePositionSensorNo.1Voltage节气门位置传感器ThrottlePositionSensorNo.2Voltage节气门位置传感器ThrottlePositionCommand油门位置指令ThrottlePositionSensorOpenPositionNo.1节气门位置传感器开启位置1 ThrottlePositionSensorOpenPositionNo.2节气门位置传感器开启位置ThrottleMotorCurrent节气门电机电流ThrottleMotorDutyRatio节气门马达占空比ThrottleMotorDutyRatio(Open)节气门电机占空比（开）ThrottleMotorDutyRatio(Close)节气门电机占空比（近）ThrottlePositionSensorFullyClosedLearnValue节气门位置传感器全封闭学习值+BMVoltage+骨髓电压ActuatorPowerSupply执行器电源ThrottleAirFlowLearnValue(Area1)节流空气流量学习值（面积1）ThrottleAirFlowLearnValue(Area2)节流空气流量学习值（面积2）ThrottleAirFlowLearnValue(Area3)节流空气流量学习值（面积3）ThrottleAirFlowLearnValue(CalculatedValue)节流空气流量学习值（计算值）ThrottleAirFlowLearnValue(AtmospherePressureOffsetValue) 节流空气流量学习值（大气压力偏移值）WastegateValveControlDutyRatio废气旁通阀控制占空比LowRevolutionControl低转速控制NRangeStatus氮范围状态EngineStallControlF/BFlow发动机档位控制ISCF/BLearnTorqueISC的F/B学习扭矩ISCTotalAUXSTorqueISC总auxs扭矩ISCF/BTorqueISC的F/B扭矩SumofISCF/BTorque(Recent)和F/BISC扭矩（最近的）ISCAUXSTorque(Alternator)ISCauxs扭矩（发电机）ISCAUXSTorque(AirConditioner)ISCauxs扭矩（空调）ThrottleAirFlowF/BValue节气门空气流量TargetFuelPressure(High)目标燃油压力（高）TargetFuelPressure(Low)目标燃油压力（低）FuelPressure(High)燃油压力（高）FuelPressure(Low)燃油压力（低）FuelPumpControlDutyRatio燃油泵控制占空比InjectorCylinder#1(Port)注射器筒#1（港）InjectionVolumeCylinder#1注射量缸#1 TargetFuelPressureOffset目标燃油压力偏移InjectionVolume注入量LowFuelPressureSensor低燃油压力传感器FuelPressureTargetDischarge燃油压力目标放电FuelPressureDischarge燃油压力放电HighFuelPressureSensor高压燃油压力传感器HighPressureFuelPumpDutyRatio(D4) 高压燃油泵占空比（D4）HighPressureFuelPumpDischargeRate 高压燃油泵流量InjectionMode注入方式InjectionSwitchingStatus注入切换状态InjectionTimingCylinder#1(D4)喷油定时气缸#1（D4）InjectionTimeCylinder#1(D4)注射时间缸#1（D4）CurrentFuelType当前燃料类型EVAP(Purge)VSVEVAPVSV（净化）TargetAir-FuelRatio目标空燃比A/F(O2)LambdaSensorB1S1A/F（O2）λ传感器b1sA/F(O2)SensorVoltageB1S1A/F（O2）传感器电压b1s1A/F(O2)SensorCurrentB1S1A/F（O2）传感器电流b1s1A/F(O2)SensorHeaterDutyRatioB1S1 A/F（O2）传感器加热器占空比b1s1 O2SensorVoltageB1S2氧传感器电压b1s2O2SensorImpedanceB1S2氧传感器的阻抗b1s2O2SensorHeaterB1S2氧传感器加热器b1s2O2SensorHeaterCurrentValueB1S2氧传感器加热器的电流值b1s2ShortFTBank1短尺1LongFTBank1长1英尺的银行TotalFTBank1金融总银行1FuelSystemStatusBank1燃油系统状态库1IgnitionTimingCylinder#1点火正时，气缸#1KnockF/BValue敲楼值KnockCorrectLearnValue正确的学习价值IdleSparkAdvanceControlCylinder#1怠速点火提前控制气缸#1 IdleSparkAdvanceControlCylinder#2怠速点火提前控制气缸#2 IdleSparkAdvanceControlCylinder#3怠速点火提前控制气缸#3 IdleSparkAdvanceControlCylinder#4怠速点火提前控制气缸#4 IntercoolerWaterPumpSpeed中间水泵转速IntercoolerWaterPump中冷器水泵MassAirFlowCircuit空气流量电路VVTAdvanceFailVVT提前失败IntakeVVTHoldCorrectLearnValueBank1(Area1) 进气VVT持有正确的学习价值银行1（1区）IntakeVVTHoldCorrectLearnValueBank1(Area2) 进气VVT持有正确的学习价值银行1（2区）IntakeVVTOCVControlDutyRatioBank1进气VVTOCV控制占空比银行1 ExhaustVVTOCVControlDutyRatioBank1排气VVTOCV控制占空比银行1 IntakeVVTTargetAngleBank1进气VVT目标角度银行1ExhaustVVTTargetAngleBank1排气VVT目标角度银行1TargetBoostPressure目标升压压力BoostPressureSensor增压压力传感器CatalystTemperatureB1S1催化剂温度b1s1CatalystTemperatureB1S2催化剂温度b1s2StarterSW起动软件NeutralPositionSW中立位置StopLightSW停止光ImmobiliserCommunication防盗通信TCTerminal终端MILONRunDistancemil运行距离RunningTimefromMILON运行时间从万美元TimeAfterDTCCleared在DTC清除时间DistancefromDTCCleared距离DTC清除WarmupCycleClearedDTC热身周期清除DTC DistanceTraveledfromLastBatteryCableDisconnect 从去年的电池电缆断开的距离IGOFFElapsedTime用过的时间TotalDistanceTraveled总距离IgnitionTriggerCount点火触发计数MisfireCountCylinder#1#1缸失火计数MisfireCountCylinder#2#2缸失火计数MisfireCountCylinder#3#3缸失火计数MisfireCountCylinder#4#4缸失火计数AllCylindersMisfireCount所有气缸失火计数MisfireRPM失火的转速MisfireLoad工作负荷MisfireMargin失火的边缘CatalystOTMisfireFuelCut催化剂不熄火断油CatalystOTMisfireFuelCutHistory催化剂OT失火燃料切断历史CatalystOTMisfireFuelCutCylinder#1 催化剂不停油气缸失火#1 CatalystOTMisfireFuelCutCylinder#2 催化剂不停油气缸失火#2 CatalystOTMisfireFuelCutCylinder#3 催化剂不停油气缸失火#3 CatalystOTMisfireFuelCutCylinder#4 催化剂不停油气缸失火#4 EngineSpeed(StarterOff)发动机转速（起动）StarterCount起动器计数RunDistanceofPreviousTrip上一次旅行的距离EngineStartingTime发动机起动时间EngineStartHesitation发动机起动犹豫LowRevolutionforEngineStart发动机起动低转速FuelCutElapsedTime燃油切断时间A/FLearnValueIdleBank1一个学习价值的空闲银行1A/FLearnValueLowBank1学习价值低的银行1A/FLearnValueMidNo.1Bank1一个学习价值中第一银行1A/FLearnValueMidNo.2Bank1一个学习价值中第二银行1A/FLearnValueHighBank1学习价值高的银行1A/FLearnValueLow(Dual)Bank1学习值低（双）银行1A/FLearnValueMid(Dual)No.1Bank1 学习价值中（双）第一银行1A/FLearnValueMid(Dual)No.2Bank1 学习价值中（双）第二银行1A/FLearnValueHigh(Dual)Bank1学习价值高（双）银行1 CompressionLeakageCount压缩泄漏计数RoughIdleStatus粗怠速状态PluralCylindersRoughIdle多缸粗怠速RoughIdleCylinder#1怠速气缸#1RoughIdleCylinder#2怠速气缸#2RoughIdleCylinder#3怠速气缸#3RoughIdleCylinder#4怠速气缸#4 CoolingFanDutyRatio冷却风机占空比BrakeOverrideSystem制动控制系统ImmobiliserFuelCutStatus防盗燃油切断状态ImmobiliserFuelCutHistory防盗燃油切断历史KeyUnlockSignal钥匙开锁信号EngineSpeedCylinder#1发动机转速#1缸EngineSpeedCylinder#2发动机转速#2缸EngineSpeedCylinder#3发动机转速#3缸EngineSpeedCylinder#4发动机转速#4缸AverageEngineSpeedofAllCylinder 平均发动机转速ReceivedMILfromECT从收到的MIL等OutputAxisSpeed输出轴转速NTSensorSpeed速度传感器ShiftSWStatus(PRange)转向西南状态（磷范围）ShiftSWStatus(RRange)转向西南状态（转）ShiftSWStatus(NRange)移软件状态（氮范围）ShiftSWStatus(N,PRange)转变西南状态（氮，磷的范围）SportShiftUpSW运动转换SportShiftDownSW运动下降ShiftSWStatus(SRange)转向西南状态（范围）SnowModeSW雪模式ShiftSWStatus(DRange)转向西南状态（三维）A/TOilTemperatureNo.1油温1号LockUpStatus锁定状态ShiftStatus移位状态Snowor2ndStartModeStatus雪或第二启动模式状态StopandStartSystemEngineStatus 停止和启动系统引擎状态AirBypassValveControl空气旁通阀控制。

单位转换1 in=2.54厘米（cm）,1 lb=0.454千克（kg）=0.454*9.807N换算公式面积换算1平方公里（km2）=100公顷（ha）=247.1英亩（acre）=0.386平方英里（mile2）1平方米（m2）=10.764平方英尺（ft2） 1平方英寸（in2）=6.452平方厘米（cm2）1公顷（ha）=10000平方米（m2）=2.471英亩（acre）1英亩（acre）=0.4047公顷（ha）=4.047×10-3平方公里（km2）=4047平方米（m2）1英亩（acre）=0.4047公顷（ha）=4.047×10-3平方公里（km2）=4047平方米（m2）1平方英尺（ft2）=0.093平方米(m2) 1平方米（m2）=10.764平方英尺（ft2）1平方码（yd2）=0.8361平方米（m2） 1平方英里（mile2）=2.590平方公里（km2）体积换算1美吉耳（gi）=0.118升（1） 1美品脱（pt）=0.473升（1）1美夸脱（qt）=0.946升（1） 1美加仑（gal）=3.785升（1）1桶（bbl）=0.159立方米（m3）=42美加仑（gal） 1英亩•英尺＝1234立方米（m3）1立方英寸（in3）=16.3871立方厘米（cm3） 1英加仑（gal）=4.546升（1）10亿立方英尺（bcf）=2831.7万立方米（m3） 1万亿立方英尺（tcf）=283.17亿立方米（m3）1百万立方英尺（MMcf）＝2.8317万立方米（m3） 1千立方英尺（mcf）=28.317立方米（m3）1立方英尺（ft3）=0.0283立方米（m3）=28.317升（liter）1立方米（m3）=1000升（liter）=35.315立方英尺（ft3）=6.29桶（bbl）长度换算1千米（km）=0.621英里（mile） 1米（m）=3.281英尺（ft）=1.094码（yd）1厘米（cm）=0.394英寸（in） 1英寸（in）=2.54厘米（cm）1海里（n mile）=1.852千米（km） 1英寻（fm）=1.829（m）1码（yd）=3英尺（ft） 1杆（rad）=16.5英尺（ft）1英里（mile）=1.609千米（km） 1英尺（ft）=12英寸（in）1英里（mile）=5280英尺（ft） 1海里（n mile）=1.1516英里（mile）质量换算1长吨（long ton）=1.016吨（t） 1千克（kg）=2.205磅（lb）1磅（lb）=0.454千克（kg）[常衡] 1盎司（oz）=28.350克(g)1短吨（sh.ton）=0.907吨（t）=2000磅（lb）1吨（t）=1000千克（kg）=2205磅（lb）=1.102短吨（sh.ton）=0.984长吨（long ton）密度换算1磅/英尺3（lb/ft3）=16.02千克/米3（kg/m3） API度＝141.5/15.5℃时的比重－131.51磅/英加仑（lb/gal）=99.776千克/米3（kg/m3） 1波美密度（B）＝140/15.5℃时的比重－1301磅/英寸3（lb/in3）=27679.9千克/米3（kg/m3） 1磅/美加仑（lb/gal）=119.826千克/米3（kg/m3）1磅/（石油）桶（lb/bbl）=2.853千克/米3（kg/m3）1千克/米3（kg/m3）=0.001克/厘米3（g/cm3）=0.0624磅/英尺3（lb/ft3）运动粘度换算1斯（St）=10-4米2/秒（m2/s）=1厘米2/秒（cm2/s）1英尺2/秒（ft2/s）=9.29030×10-2米2/秒（m2/s）1厘斯（cSt）=10-6米2/秒（m2/s）=1毫米2/秒（mm2/s）动力粘度换算动力粘度 1泊（P）＝0.1帕•秒（Pa•s） 1厘泊（cP）=10-3帕•秒（Pa•s）1磅力秒/英尺2（lbf•s/ft2）=47.8803帕•秒（Pa•s）1千克力秒/米2（kgf•s、m2）=9.80665帕•秒（Pa•s）力换算1牛顿（N）＝0.225磅力（lbf）=0.102千克力（kgf） 1千克力（kgf）=9.81牛（N）1磅力（lbf）=4.45牛顿（N） 1达因（dyn）=10-5牛顿（N）温度换算K＝5/9（°F+459.67） K=℃+273.15 n℃=(5/9•n+32) °F n°F=[(n-32)×5/9]℃1°F=5/9℃（温度差）压力换算压力 1巴（bar）=105帕（Pa） 1达因/厘米2（dyn/cm2）=0.1帕（Pa）1托（Torr）=133.322帕（Pa） 1毫米汞柱（mmHg）=133.322帕（Pa）1毫米水柱（mmH2O）=9.80665帕（Pa） 1工程大气压=98.0665千帕（kPa）1千帕（kPa）=0.145磅力/英寸2（psi）=0.0102千克力/厘米2（kgf/cm2） =0.0098大气压（atm）1磅力/英寸2（psi）=6.895千帕（kPa）=0.0703千克力/厘米2（kg/cm2）=0.0689巴（bar）=0.068大气压（atm）1物理大气压（atm）=101.325千帕（kPa）=14.696磅/英寸2（psi）=1.0333巴（bar）传热系数换算1千卡/米2•时（kcal/m2•h）=1.16279瓦/米2（w/m2）1千卡/（米2•时•℃）〔1kcal/(m2•h•℃)〕＝1.16279瓦/（米2•开尔文）〔w/(m2•K)〕1英热单位/（英尺2•时•°F）〔Btu/(ft2•h•°F)〕=5.67826瓦/（米2•开尔文）〔（w/m2•K）〕1米2•时•℃/千卡（m2•h•℃/kcal）=0.86000米2•开尔文/瓦（m2•K/W）热导率换算1千卡（米•时•℃）〔kcal/(m•h•℃)〕＝1.16279瓦/（米•开尔文）〔W/(m•K)〕1英热单位/（英尺•时•°F）〔But/(ft•h•°F) ＝1.7303瓦/（米•开尔文）〔W/(m•K)〕比容热换算1千卡/（千克•℃）〔kcal/(kg•℃)〕＝1英热单位/（磅•°F）〔Btu/(lb•°F)〕＝4186.8焦耳/（千克•开尔文）〔J/（kg•K）〕热功换算1卡（cal）=4.1868焦耳（J） 1大卡=4186.75焦耳（J） 1千克力米（kgf•m）=9.80665焦耳（J）1英热单位（Btu）＝1055.06焦耳（J） 1千瓦小时（kW•h）=3.6×106焦耳（J）1米制马力小时（hp•h）=2.64779×106焦耳（J） 1英尺磅力（ft•lbf）=1.35582焦耳（J）1英马力小时（UKHp•h）=2.68452×106焦耳1焦耳＝0.10204千克•米＝2.778×10－7千瓦•小时＝3.777×10－7公制马力小时＝3.723×10－7英制马力小时＝2.389×10－4千卡=9.48×10－4英热单位功率换算1英热单位/时（Btu/h）=0.293071瓦（W） 1千克力•米/秒（kgf•m/s）=9.80665瓦（w）1卡/秒（cal/s）＝4.1868瓦（W） 1米制马力（hp）=735.499瓦（W）速度换算1英里/时（mile/h）=0.44704米/秒（m/s） 1英尺/秒（ft/s）=0.3048米/秒（m/s）渗透率换算1达西＝1000毫达西 1平方厘米（cm2）＝9.81×107达西地温梯度换算1°F/100英尺＝1.8℃/100米（℃/m）1℃/公里＝2.9°F/英里（°F/mile）=0.055°F/100英尺（°F/ft）油气产量换算1桶（bbl）=0.14吨（t）（原油，全球平均）1万亿立方英尺/日（tcfd） =283.2亿立方米/日（m3/d）=10.336万亿立方米/年（m3/a）10亿立方英尺/日（bcfd）=0.2832亿立方米/日（m3/d） =103.36亿立方米/年（m3/a）1百万立方英尺/日（MMcfd）=2.832万立方米/日（m3/d）=1033.55万立方米/年（m3/a）1千立方英尺/日（Mcfd）=28.32立方米/日（m3/d）=1.0336万立米/年（m3/a）1桶/日（bpd）=50吨/年（t/a）（原油，全球平均）1吨（t）=7.3桶（bbl）(原油，全球平均)气油比换算1立方英尺/桶（cuft/bbl）=0.2067立方米/吨（m3/t）热值换算1桶原油＝5.8×106英热单位（Btu） 1吨煤=2.406×107英热单位（Btu）1立方米湿气＝3.909×104英热单位（Btu） 1千瓦小时水电＝1.0235×104英热（Btu）1立方米干气＝3.577×104英热单位（Btu）（以上为1990年美国平均热值）热当量换算1桶原油＝5800立方英尺天然气（按平均热值计算） 1立方米天然气＝1.3300千克标准煤1千克原油＝1.4286千克标准煤◆容积单位换算表公升Liter 公秉Kiloliter 美制加仑U.S.Gallon 英制加仑Imp.Gallon 美桶Barrel 立方寸Cubic Feet 立方尺◆重量单位换算表Kilogram 公吨Metric ton 磅Pound 短吨Short ton 长吨1市斤=0.5000公斤=1.1023磅◆长度单位换算表公里km 公尺m 公分cm 公厘mm 公寸in 英尺ft 英里mile1（英海）=1.150776英里=6076英尺=1.852公尺，1市尺=1.0936英尺◆面积单位换算表平方公尺m2 平方寸in2 平方尺ft2 英亩acre 平方英里sq-mile 平方公分cm2 平方公厘mm21公顷=100公亩=10.000平方公尺=2.471英亩=1.0310里 1里=96.99194公亩=2.3967英亩=2.934坪◆主要力量单位换算表（国际标准单位与公制单位壶算）力量名称国际单位-公制单位公制单位-国际单位空气压力 1MPa=10.2kgf/cm2 1kgf/cm2=0.098MPa荷重力1N•m=0.102kgf•m 1kgf=9.8N扭力1N •m=0.102kgf 1kgf•m=9.8N•m真空压力 -1KPa=-7.5mmHg -1mmHg=-0.133KPa惯性力距1Kg•m2=10.2kgf•cm•s 1kg•cm•s=0.098Kgf•m2◆压力单位换算表◆流量单位换算表◆容积单位换算表◆重量单位换算表◆长度单位换算表◆面积单位换算表◆主要力量单位换算表（国际标准单位与公制单位壶算）常用中英对照数学 mathematics, maths(BrE), math(AmE)公理 axiom定理 theorem计算 calculation运算 operation证明 prove假设 hypothesis, hypotheses(pl.)命题 proposition算术 arithmetic加 plus(prep.), add(v.), addition(n.)被加数 augend, summand加数 addend和 sum减 minus(prep.), subtract(v.), subtraction(n.)被减数 minuend减数 subtrahend差 remainder乘 times(prep.), multiply(v.), multiplication(n.)被乘数 multiplicand, faciend乘数 multiplicator积 product除 divided by(prep.), divide(v.), division(n.)被除数 dividend除数 divisor商 quotient等于 equals, is equal to, is equivalent to大于 is greater than小于 is lesser than大于等于 is equal or greater than小于等于 is equal or lesser than运算符 operator平均数mean算术平均数arithmatic mean几何平均数geometric mean n个数之积的n次方根倒数（reciprocal） x的倒数为1/x有理数 rational number无理数 irrational number实数 real number虚数 imaginary number数字 digit数 number自然数 natural number整数 integer小数 decimal小数点 decimal point分数 fraction分子 numerator分母 denominator比 ratio正 positive负 negative零 null, zero, nought, nil十进制 decimal system二进制 binary system十六进制 hexadecimal system权 weight, significance进位 carry截尾 truncation四舍五入 round下舍入 round down上舍入 round up有效数字 significant digit无效数字 insignificant digit代数 algebra公式 formula, formulae(pl.)单项式 monomial多项式 polynomial, multinomial系数 coefficient未知数 unknown, x-factor, y-factor, z-factor 等式，方程式 equation一次方程 simple equation二次方程 quadratic equation三次方程 cubic equation四次方程 quartic equation不等式 inequation阶乘 factorial对数 logarithm指数，幂 exponent乘方 power二次方，平方 square三次方，立方 cube四次方 the power of four, the fourth power n次方 the power of n, the nth power开方 evolution, extraction二次方根，平方根 square root三次方根，立方根 cube root四次方根 the root of four, the fourth root n次方根 the root of n, the nth rootsqrt(2)=1.414sqrt(3)=1.732sqrt(5)=2.236常量 constant变量 variable坐标系 coordinates坐标轴 x-axis, y-axis, z-axis横坐标 x-coordinate纵坐标 y-coordinate原点 origin象限quadrant截距(有正负之分)intercede（方程的）解solution几何geometry点 point线 line面 plane体 solid线段 segment射线 radial平行 parallel相交 intersect角 angle角度 degree弧度 radian锐角 acute angle直角 right angle钝角 obtuse angle平角 straight angle周角 perigon边 side高 height三角形 triangle锐角三角形 acute triangle直角三角形 right triangle直角边 leg斜边 hypotenuse勾股定理 Pythagorean theorem 钝角三角形 obtuse triangle不等边三角形 scalene triangle 等腰三角形 isosceles triangle 等边三角形 equilateral triangle 四边形 quadrilateral平行四边形 parallelogram矩形 rectangle长 length宽 width周长 perimeter面积 area相似 similar全等 congruent三角 trigonometry正弦 sine余弦 cosine正切 tangent余切 cotangent正割 secant余割 cosecant反正弦 arc sine反余弦 arc cosine反正切 arc tangent反余切 arc cotangent反正割 arc secant反余割 arc cosecant补充：集合aggregate元素 element空集 void子集 subset交集 intersection补集 complement映射 mapping函数 function定义域 domain, field of definition 值域 range单调性 monotonicity奇偶性 parity周期性 periodicity图象 image数列，级数 series微积分 calculus微分 differential导数 derivative极限 limit无穷大 infinite(a.) infinity(n.)无穷小 infinitesimal积分 integral定积分 definite integral不定积分 indefinite integral复数 complex number矩阵 matrix行列式 determinant圆 circle圆心 centre(BrE), center(AmE) 半径 radius直径 diameter圆周率 pi弧 arc半圆 semicircle扇形 sector环 ring椭圆 ellipse圆周 circumference轨迹 locus, loca(pl.)平行六面体 parallelepiped立方体 cube七面体 heptahedron八面体 octahedron九面体 enneahedron十面体 decahedron十一面体 hendecahedron十二面体 dodecahedron二十面体 icosahedron多面体 polyhedron旋转 rotation轴 axis球 sphere半球 hemisphere底面 undersurface表面积 surface area体积 volume空间 space双曲线 hyperbola抛物线 parabola四面体 tetrahedron五面体 pentahedron六面体 hexahedron菱形 rhomb, rhombus, rhombi(pl.), diamond 正方形 square梯形 trapezoid直角梯形 right trapezoid等腰梯形 isosceles trapezoid五边形 pentagon六边形 hexagon七边形 heptagon八边形 octagon九边形 enneagon十边形 decagon十一边形 hendecagon十二边形 dodecagon多边形 polygon正多边形 equilateral polygon相位 phase周期 period振幅 amplitude内心 incentre(BrE), incenter(AmE)外心 excentre(BrE), excenter(AmE)旁心 escentre(BrE), escenter(AmE)垂心 orthocentre(BrE), orthocenter(AmE)重心 barycentre(BrE), barycenter(AmE)内切圆 inscribed circle外切圆 circumcircle统计 statistics平均数 average加权平均数 weighted average方差 variance标准差 root-mean-square deviation, standard deviation 比例 propotion百分比 percent百分点 percentage百分位数 percentile排列 permutation组合 combination概率，或然率 probability分布 distribution正态分布 normal distribution非正态分布 abnormal distribution图表 graph条形统计图 bar graph柱形统计图 histogram折线统计图 broken line graph曲线统计图 curve diagram扇形统计图 pie diagramabscissa 横坐标absolute value 绝对值acute angle 锐角adjacent angle 邻角addition 加algebra 代数altitude 高angle bisector 角平分线arc 弧area 面积arithmetic mean 算术平均值（总和除以总数）arithmetic progression 等差数列（等差级数）arm 直角三角形的股at 总计（乘法）average 平均值base 底be contained in 位于...上bisect 平分center 圆心chord 弦circle 圆形circumference 圆周长circumscribe 外切，外接clockwise 顺时针方向closest approximation 最相近似的combination 组合common divisor 公约数，公因子common factor 公因子complementary angles 余角（二角和为90度）composite number 合数（可被除1及本身以外其它的数整除）concentric circle 同心圆cone 圆锥（体积＝1/3*pi*r*r*h）congruent 全等的consecutive integer 连续的整数coordinate 坐标的cost 成本counterclockwise 逆时针方向cube 1.立方数2.立方体（体积＝a*a*a 表面积＝6*a*a）cylinder 圆柱体decagon 十边形decimal 小数decimal point 小数点decreased 减少decrease to 减少到decrease by 减少了degree 角度define 1.定义 2.化简denominator 分母denote 代表，表示depreciation 折旧distance 距离distinct 不同的dividend 1. 被除数 2.红利divided evenly 被除数divisible 可整除的division 1.除 2.部分divisor 除数down payment 预付款，定金equation 方程equilateral triangle 等边三角形even number 偶数expression 表达exterior angle 外角face （立体图形的）某一面factor 因子fraction 1.分数 2.比例geometric mean 几何平均值（N个数的乘积再开N次方）geometric progression 等比数列（等比级数）have left 剩余height 高hexagon 六边形hypotenuse 斜边improper fraction 假分数increase 增加increase by 增加了increase to 增加到inscribe 内切，内接intercept 截距integer 整数interest rate 利率in terms of... 用...表达interior angle 内角intersect 相交irrational 无理数isosceles triangle 等腰三角形least common multiple 最小公倍数least possible value 最小可能的值leg 直角三角形的股length 长list price 标价margin 利润mark up 涨价mark down 降价maximum 最大值median, medium 中数（把数字按大小排列，若为奇数项，则中间那项就为中数，若为偶数项，则中间两项的算术平均值为中数。

电缆载流量计算书电缆有限公司技术部2019/9/211.载流量计算使用条件及必要系数：1. 导体交流电阻 R的计算R=R＇(1+y s+y p)R＇=R0［1+α20(θ-20)］其中:其中：对于分割导体ks=0.435。

其中：d c:导体直径 （mm）s:各导体轴心之间距离 （mm） 对于分割导体ks=0.37。

2.介质损耗W d的计算W d=ωCU02tgδ其中：ω=2πfC:电容 F/mU:对地电压（V）其中：εD i为绝缘外径 （mm）d c为内屏蔽外径 （mm）3.金属屏蔽损耗λ1的计算λ1=λ1＇+λ1〃其中：λ1＇为环流损耗λ1〃为涡流损耗λ1〃的计算：其中：ρ：金属护套电阻率 (Ω·m)R：金属护套电阻 (Ω/m)t：金属护套厚度 (mm)D oc：皱纹铝套最大外径 (mm) D it：皱纹铝套最小内径 (mm)a.三角形排列时2b.平行排列时1)中心电缆△2=03)外侧滞后相4.铠装损耗λ2的计算λ2=05热阻的计算5.1热阻T1的计算热阻式中：ρT1 — 绝缘材料热阻系数 (k·m/w)d c — 导体直径 (mm)t 1 — 导体和护套之间的绝缘厚度 (mm)5.2热阻T 2的计算 热阻T 2=05.3外护套热阻T 3的计算其中：t s -外护套厚度 ρT3-外护套（非金属）热阻系数5.4外部热阻T 4计算5.4.1空气中敷设其中：D e *：电缆外径 (mm)h: 散热系数当空气中敷设时，回路数对载流量基本没有影响。

5.4.2土壤中敷设5.4.2.1管道敷设，有水泥槽。

5.4.2.1.1电缆和管道之间的热阻T4′：其中：U、V和Y是与条件有关的常数。

D e 为电缆外径。

θm 为电缆与管道之间介质的平均温度。

5.4.2.1.2管道本身的热阻其中：D o 为管道外径。

D d 为管道内径。

ρT4为管道材料的热阻系数。

5.4.2.1.3管道外部热阻ρe 管道周围土壤的热阻系数。

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atio‎n__\r‎\nCC‎T|电路_‎C ircu‎i t__\‎r\nC‎D|关命令‎_clos‎e_dem‎a nd__‎\r\n‎C D|已关‎,关状态_‎C lose‎d__\r‎\nCH‎A NL|通‎道_Cha‎n nel_‎_\r\n‎CHAR‎G E|充电‎_Char‎g e__\‎r\nC‎H EM-W‎T R-X|‎化水变_C‎h emis‎t_wat‎e r_xf‎m r__\‎r\nC‎H F|总_‎C hief‎__\r\‎nCHK‎|校正_C‎h eck_‎_\r\n‎CHK ‎V|逆止门‎_chec‎k_val‎v e,_n‎o n-re‎t urn_‎v alve‎__\r\‎n CIR‎|循环_c‎i rcul‎a ting‎__\r\‎nCIR‎WTR|‎循环水_c‎i rcul‎a ting‎_wate‎r__\r‎\nCL‎|闭式_c‎l osed‎__\r\‎nCL|‎关_clo‎s e__\‎r\nC‎L CIR‎WTR|‎闭式循环水‎_clos‎e d_ci‎r cula‎t ing_‎w ater‎__\r\‎n CL ‎S WTH|‎合闸_cl‎o se_s‎w itch‎__\r\‎nCLC‎T|收集_‎C olle‎c tion‎__\r\‎nCLE‎A N|净_‎c lean‎__\r\‎nCLF‎R|粗粉分‎离器_cl‎a ssif‎i er__‎\r\n‎C LG|冷‎却_coo‎l ing_‎_\r\n‎CLG ‎A IR F‎A N|冷却‎风机_co‎o ling‎_air_‎(blow‎e r)_f‎a n__\‎r\n C‎L NG|顶‎棚_cei‎l ing_‎_\r\n‎CLR|‎冷却器_c‎o oler‎__\r\‎nCMP‎S|合成_‎c ompo‎s e__\‎r\nC‎N D|凝结‎_cond‎e nsat‎e__\r‎\nCN‎D P|凝‎结水泵_c‎o nden‎s ate_‎p ump_‎_\r\n‎CND ‎W TR|凝‎结水_co‎n dens‎a ted_‎w ater‎__\r\‎nCNS‎R|凝汽器‎_cond‎e nser‎__\r\‎nCNT‎R|连通管‎_conn‎e ctor‎__\r\‎nCNV‎G|汇流_‎c onve‎r ge__‎\r\n‎C OAL ‎B LOCK‎|堵煤_c‎o al_b‎l ocki‎n g__\‎r\nC‎O AL C‎V R|输煤‎机_coa‎l_con‎v eyer‎__\r\‎nCOA‎L FDR‎|给煤机_‎(coal‎_)_fe‎e der_‎_\r\n‎COG|‎齿_cog‎__\r\‎nCOG‎|齿部_c‎o g__\‎r\nC‎O IL|线‎圈_coi‎l__\r‎\nCO‎L D AI‎R|冷风_‎c old_‎a ir__‎\r\n‎C OLLA‎R|轭部_‎c olla‎r__\r‎\nCO‎M|公用_‎C ommo‎n__\r‎\nCO‎M BNR|‎组件_Co‎m bine‎r__\r‎\nCO‎M P|复合‎_Comp‎l ex__‎\r\n‎C ONDT‎|导电度_‎c ondu‎c tivi‎t y__\‎r\nC‎O OL R‎H T|冷再‎热_coo‎l_reh‎e at__‎\r\n‎C ORE|‎铁芯_(_‎i ron_‎\r\n‎C P|关状‎态_Clo‎s ed_p‎o siti‎o n__\‎r\nC‎P LR|耦‎合器_co‎u pler‎__\r\‎nCPR‎E SS A‎I R|压缩‎空气_co‎m pres‎s ed_a‎i r__\‎r\nC‎R NR|角‎_corn‎e r__\‎r\nC‎R RT|电‎流_cur‎r ent_‎_\r\n‎CRVC‎|夹层_c‎r evic‎e__\r‎\nCR‎V C|间隙‎_crev‎i ce__‎\r\n‎C S|石子‎_Cobb‎l esto‎n e__\‎r\nC‎S EP|细‎粉分离器_‎c yclo‎n e_se‎p arat‎o r__\‎r\nC‎S V|联合‎汽门_co‎m bine‎d_ste‎a m_va‎l ve__‎\r\n‎C TL|控‎制_Con‎t rol_‎_\r\n‎CTL ‎B OX|控‎制箱_co‎n trol‎_box_‎_\r\n‎CTL ‎D MD|控‎制命令(对‎调节阀)_‎C ontr‎o l_de‎m and_‎_\r\n‎CTL ‎R OOM|‎控制室_c‎o ntro‎l_roo‎m__\r‎\nCT‎N BLD‎N|连排_‎c onti‎n ue_b‎l owdo‎w n__\‎r\nC‎T N BL‎D N FL‎T K|连排‎扩容器_c‎o ntin‎u e_bl‎o wdow‎n_fla‎s htan‎k__\r‎\n CT‎N R|罐_‎C onta‎i ner_‎_\r\n‎CTR|‎中心_Ce‎n ter_‎_\r\n‎CV|用‎户阀_cu‎s tome‎r_val‎v e__\‎r\nC‎X|公用变‎_comm‎o n_tr‎a nsfo‎r mer_‎_\r\n‎CYL|‎汽缸_cy‎l inde‎r__\r‎\nDC‎|直流_d‎i rect‎_curr‎e nt__‎\r\n‎D EA|除‎氧器_de‎a erat‎o r__\‎r\nD‎E MAG|‎消磁装置_‎d emag‎n etiz‎e r__\‎r\nD‎E MINE‎|除盐的_‎D emin‎e rali‎z ed__‎\r\n‎D EMIN‎R|除盐装‎置_Dem‎i nera‎l ized‎_devi‎c e__\‎r\nD‎I F PR‎S（DP）‎|差压（压‎差）_di‎f fere‎n tial‎_pres‎s ure_‎_\r\n‎DIFF‎|差动_d‎i ffer‎e ntia‎l__\r‎\nDI‎F F PR‎S|压差（‎差压）_d‎i ffer‎e ntia‎l_pre‎s sure‎__\r\‎nDIR‎T Y|脏_‎d irty‎__\r\‎nDIS‎C H|泄放‎_Disc‎h arge‎__\r\‎nDIS‎C H OI‎L|放油_‎D isch‎a rge_‎o il__‎\r\n‎D ISCH‎STM|‎放汽_Di‎s char‎g e_st‎e am__‎\r\n‎D ISCH‎WTR|‎放水_di‎s char‎g e_wa‎t er__‎\r\n‎D ISCO‎N|断线_‎d isco‎n nect‎i ng__‎\r\n‎D ISP|‎位移_di‎s plac‎e__\r‎\nDM‎D|要求_‎D eman‎d__\r‎\nDM‎D|指令,‎命令_De‎m and_‎_\r\n‎DMPR‎|挡板_d‎a mper‎__\r\‎nDN|‎下_dow‎n__\r‎\nDN‎C MR|下‎降管_do‎w ncom‎e r__\‎r\nD‎P HRM|‎隔膜_Di‎a phra‎g m__\‎r\nD‎R AFT|‎通风_Dr‎a ft__‎\r\n‎D RG|渣‎_Dreg‎s__\r‎\nDR‎N|疏水_‎d rain‎_wate‎r__\r‎\nDR‎N FLT‎K|疏水扩‎容器_dr‎a in_w‎a ter_‎f lash‎t ank_‎_\r\n‎DRN ‎T K|疏水‎罐_dra‎i n_ta‎n k__\‎r\nD‎R N V|‎疏水阀_d‎r ain_‎w ater‎__\r\‎nDRU‎M|传动_‎d rum_‎_\r\n‎DRUM‎|汽包_D‎r um__‎\r\n‎D RV_E‎|驱动端_‎d rive‎_end_‎_\r\n‎DSH|‎减温_De‎s uper‎h eat_‎_\r\n‎DSHR‎|减温器_‎D esup‎e rhea‎t er__‎\r\n‎D SL|柴‎油机_di‎e sel_‎e ngin‎e__\r‎\nDS‎P PR|消‎失_dis‎a ppea‎r__\r‎\nDS‎S LV|溶‎解_dis‎s olve‎d__\r‎\nDS‎T Y|浓度‎_Dens‎i ty__‎\r\n‎D TY O‎C|污油室‎_Dirt‎y_oil‎_cham‎b er__‎\r\n‎D UP|复‎_Dupl‎i cate‎__\r\‎nDWT‎R|脱水_‎D ewat‎e r__\‎r\nD‎Z|刀闸_‎D ao_z‎h a__\‎r\nE‎C NT|偏‎心度_Ec‎c entr‎i city‎__\r\‎nECO‎N|省煤器‎_Econ‎o mize‎r__\r‎\nEG‎F|排烟风‎机_exh‎a ust_‎g as_f‎a n__\‎r\nE‎L EC|电‎气_Ele‎c tric‎__\r\‎nEMG‎|紧急_E‎m erge‎n cy__‎\r\n‎E MG|事‎故_Eme‎r genc‎y__\r‎\nEM‎G RLV‎OIL ‎V|紧急放‎油阀_em‎e rgen‎c y_re‎l ieve‎_oil_‎v alve‎__\r\‎n END‎|结束_e‎n d__\‎r\nE‎N D FA‎C E|端_‎E nd_f‎a ce__‎\r\n‎E NST|‎蓄能器_e‎n ergy‎_stor‎a ge__‎\r\n‎E QPMN‎T|装置_‎e quip‎m ent_‎_\r\n‎EXCH‎R|交换器‎_exch‎a nger‎__\r\‎nEXC‎T|励磁_‎e xcit‎a tion‎__\r\‎nEXC‎T R|励磁‎机_exc‎i tato‎r__\r‎\nEX‎C TR S‎I DE|励‎端_exc‎i tato‎r_sid‎e__\r‎\nEX‎H|排风_‎E xhau‎s t__\‎r\nE‎X H OI‎L|排油_‎E xhau‎s t_oi‎l__\r‎\nEX‎H STM‎|排汽_E‎x haus‎t_ste‎a m__\‎r\nE‎X H WT‎R|排水_‎E xhau‎s t_wa‎t er__‎\r\n‎E XHR|‎排风机_E‎x haus‎t er__‎\r\n‎E XP|膨‎胀_exp‎a nsio‎n__\r‎\nEX‎P DIF‎F|胀差_‎e xpan‎s ion_‎d iffe‎r ence‎__\r\‎nEXT‎D|伸进_‎E xten‎d__\r‎\nEX‎T R|抽汽‎_extr‎a ctio‎n_ste‎a m__\‎r\nF‎/B|前后‎_fron‎t_\r\‎nFAI‎L|失败_‎f ailu‎r e__\‎r\nF‎A ST C‎L|速断_‎f ast-‎c losi‎n g__\‎r\nF‎A ULT|‎故障_Fa‎u lt__‎\r\n‎F D|送风‎_forc‎e d_dr‎a ft_a‎i r__\‎r\nF‎D BK|反‎馈_fee‎d back‎__\r\‎nFDF‎|送风机_‎f orce‎d_dra‎f t_fa‎n__\r‎\nFE‎E D WT‎R|给水_‎f eedw‎a ter_‎_\r\n‎FGHT‎|消防_f‎i re_f‎i ghti‎n g__\‎r\nF‎I NE T‎R MT|精‎处理_fi‎n e_tr‎e atme‎n t__\‎r\nF‎I RING‎|有火_f‎i ring‎__\r\‎nFLA‎N|法兰_‎f lang‎e__\r‎\nFL‎M|火焰_‎f lame‎__\r\‎nFLM‎INTS‎|火焰强度‎_flam‎e_int‎e nsit‎y__\r‎\nFL‎T K|扩容‎器_fla‎s h_ta‎n k__\‎r\nF‎L TR|过‎滤器_fi‎l ter_‎_\r\n‎FLTR‎|滤网_f‎i lter‎__\r\‎nFLU‎E GAS‎|排烟_f‎l ue_g‎a s__\‎r\nF‎L W|流量‎_flow‎__\r\‎nFNC‎|炉膛_f‎u rnac‎e__\r‎\nFO‎R CE|强‎制_for‎c e__\‎r\nF‎P O|抗燃‎油_fla‎m e_pr‎o of_o‎i l__\‎r\nF‎R|前_f‎r ont_‎_\r\n‎FREQ‎|频率_F‎r eque‎n cy__‎\r\n‎F UEL|‎燃料_Fu‎e l__\‎r\nF‎U EL-X‎|燃油变_‎F uel_‎x fmr_‎_\r\n‎FUSE‎|熔断_f‎u sibl‎e__\r‎\nFU‎S E|熔断‎器_fus‎i ble_‎c utou‎t__\r‎\nFV‎|定值_F‎i xed_‎v alue‎__\r\‎nGAS‎|气体_g‎a s__\‎r\nG‎A S|烟气‎_gas_‎_\r\n‎GAS ‎P ASS|‎烟道_ga‎s_pas‎s__\r‎\nGA‎S TEM‎|烟温_g‎a s_te‎m p__\‎r\nG‎D VN|导‎叶_gui‎d e_va‎n e__\‎r\nG‎E AR|齿‎轮_Gea‎r__\r‎\nGE‎N|发电机‎_gene‎r ator‎__\r\‎nGLD‎|汽封_s‎t eam_‎s eali‎n g,_s‎t eam_‎s eal_‎g land‎__\r\‎n GLD‎|轴封_G‎l and_‎_\r\n‎GND|‎接地_gr‎o und_‎_\r\n‎GP|组‎_Grou‎p__\r‎\nGV‎N|可调速‎的_gov‎e rnin‎g__\r‎\nGV‎N OIL‎(GO)|‎调速油_G‎o vern‎i ng_o‎i l__\‎r\nG‎V N V|‎调速汽门_‎g over‎n ing_‎v alve‎__\r\‎nGXU‎|发变组_‎g ener‎a tor_‎t rans‎f orme‎r_uni‎t__\r‎\nH2‎SPL|‎供氢_H2‎_supp‎l y__\‎r\nH‎2_S|氢‎侧_H2_‎s ide_‎_\r\n‎HD_C‎P LR|液‎力耦合器_‎h ydra‎u lic_‎c oupl‎e r__\‎r\n H‎D_MTR‎|油动机_‎h ydra‎u lic_‎s ervo‎m otor‎__\r\‎n HDR‎|集箱_h‎e ader‎__\r\‎nHDR‎|联箱_h‎e ader‎__\r\‎nHDR‎|母管_h‎e ader‎__\r\‎nHEA‎T STM‎|加热蒸汽‎_heat‎_stea‎m__\r‎\nHE‎A VY|重‎_heav‎y__\r‎\nHE‎S I|高能‎点火器_h‎i gh_e‎n ergy‎_spar‎k_ign‎i tor_‎_\r\n‎HIGH‎AUX|‎高辅_hi‎g h_pr‎e ssur‎e_aux‎i liar‎y__\r‎\nHI‎G H LM‎T|高限_‎h igh_‎l imit‎__\r\‎nHIG‎H PRS‎|高压力_‎h igh_‎p ress‎u re__‎\r\n‎H IGH ‎S PD|高‎速_hig‎h_spe‎e d__\‎r\nH‎I GH T‎E M|高温‎_high‎_temp‎e ratu‎r e__\‎r\nH‎I GH V‎O LT|高‎电压_hi‎g h_vo‎l tage‎__\r\‎nHIG‎H(HI)‎|高_Hi‎g h__\‎r\nH‎I PC|高‎中压缸_h‎i gh_i‎n term‎e diat‎e_pre‎s sure‎_cyli‎n der_‎_\r\n‎HLWB‎|高位水箱‎_high‎_leve‎l_wat‎e r_bo‎x__\r‎\nHM‎D T|湿度‎_humi‎d ity_‎_\r\n‎HORZ‎|水平(方‎向)的_h‎o rizo‎n tal_‎_\r\n‎HOT ‎A IR|热‎风_hot‎_air_‎_\r\n‎HOT ‎R HT|热‎再热_ho‎t_reh‎e at__‎\r\n‎H OT W‎E LL|热‎井_hot‎_well‎__\r\‎nHPC‎|高压缸_‎h igh_‎p ress‎u re_c‎y lind‎e r__\‎r\nH‎P H|高加‎_high‎_pres‎s ure_‎h eade‎r__\r‎\nHT‎G|采暖_‎H eati‎n g__\‎r\nH‎T R|加热‎器_hea‎t er__‎\r\n‎H VSX|‎高备变_h‎i gh_v‎o ltag‎e_sta‎n dby_‎t rans‎f orme‎r__\r‎\nHY‎D L OI‎L|液压油‎_hydr‎a ulic‎_oil_‎_\r\n‎HYDP‎|液压_H‎y drau‎l ic_p‎r essu‎r e__\‎r\nI‎D A|引风‎_indu‎c ed_d‎r aft_‎a ir__‎\r\n‎I DF|引‎风机_in‎d uced‎_draf‎t_fan‎__\r\‎nIGN‎T|点火_‎I gnit‎i on__‎\r\n‎I GNTR‎|点火器_‎I gnit‎o r__\‎r\nI‎M PDC|‎阻抗_im‎p edan‎c e__\‎r\nI‎N C|增加‎_incr‎e ate_‎_\r\n‎IND ‎W TR|工‎业水_in‎d ustr‎i al_w‎a ter_‎_\r\n‎ING|‎进_Ing‎o ing_‎_\r\n‎ING ‎L INE|‎进线_in‎g oing‎_line‎__\r\‎nINL‎|入口_i‎n let_‎_\r\n‎INL ‎S IDE|‎吸入端_i‎n let_‎s ide_‎_\r\n‎INN|‎内,内侧,‎内部_in‎n er__‎\r\n‎I NT V‎O LT|问‎询电压_i‎n terr‎o gati‎o n_vo‎l tage‎__\r\‎nINT‎M T|定期‎(排污)_‎i nter‎m itte‎n t__\‎r\nI‎N TMT ‎B LDN ‎F LTK|‎定期排污扩‎容器_in‎t ermi‎t tent‎_blow‎_down‎_flas‎h_tan‎k__\r‎\n IN‎T R PR‎S|中压_‎i nter‎m edia‎t e_pr‎e ssur‎e__\r‎\nIN‎T RCT|‎联络_in‎t erco‎n nect‎i on__‎\r\n‎I NTRL‎K|联锁_‎i nter‎l ock_‎_\r\n‎INVS‎|逆_in‎v erse‎__\r\‎nION‎|离子_i‎o n__\‎r\nI‎P C|中压‎缸_int‎e rmed‎i ate_‎p ress‎u re_c‎y lind‎e r__\‎r\n I‎S LN,I‎S LT|绝‎缘_Iso‎l atio‎n__\r‎\nIS‎L T|隔离‎_isol‎a te__‎\r\n‎I SLT ‎P LTN|‎分隔屏_i‎s olat‎i ng_p‎l aten‎__\r\‎nJAC‎K|顶轴_‎j acki‎n g__\‎r\nK‎W H|电度‎_elec‎t rica‎l_wor‎k__\r‎\nL_‎A|A层_‎L ayer‎_A__\‎r\nL‎_STG|‎末级_th‎e_las‎t_sta‎g e__\‎r\nL‎A YER|‎层_lay‎e r__\‎r\nL‎B TY S‎I DE|自‎由端_li‎b erty‎_side‎__\r\‎nLCL‎|就地_L‎o cal_‎_\r\n‎LE|左‎_Left‎__\r\‎nLEA‎K|泄漏_‎l eak_‎_\r\n‎LIFT‎|支撑_l‎i ft__‎\r\n‎L IFT ‎B EAR|‎支撑轴承_‎l ift_‎b eari‎n g__\‎r\nL‎I GHT|‎轻_lig‎h t__\‎r\nL‎M T|极限‎_Limi‎t__\r‎\nLM‎T|限_l‎i mit_‎_\r\n‎LOAD‎|负荷_L‎o ad__‎\r\n‎L OCK|‎闭锁_lo‎c k__\‎r\nL‎O CK C‎L|闭锁关‎_lock‎_clos‎e__\r‎\nLO‎C K OP‎N|闭锁开‎_lock‎_open‎__\r\‎nLOS‎E MAG‎|失磁_l‎o se_m‎a gnet‎__\r\‎nLOS‎E SYN‎|失步_l‎o se_s‎y nchr‎o nize‎r__\r‎\nLO‎W AUX‎|低辅_l‎o w_pr‎e ssur‎e_aux‎i liar‎y__\r‎\n LO‎W FRE‎Q|低频_‎l ow_f‎r eque‎n cy__‎\r\n‎L OW L‎M T|低限‎_low_‎l imit‎__\r\‎nLOW‎PRS|‎低压力_l‎o w__\‎r\nL‎O W SP‎D|低速_‎l ow_s‎p eed_‎_\r\n‎LOW ‎T EM|低‎温_low‎_temp‎e ratu‎r e__\‎r\nL‎O W VO‎L T|低电‎压_Low‎__\r\‎nLOW‎(LO)|‎低_Low‎__\r\‎nLPC‎|低压缸_‎l ow_p‎r essu‎r e_cy‎l inde‎r__\r‎\nLP‎H|低加_‎l ow_p‎r essu‎r e_he‎a ter_‎_\r\n‎LUB|‎润滑_lu‎b e__\‎r\nL‎U B OI‎L|润滑油‎_lube‎_oil_‎_\r\n‎LVL|‎液位_le‎v el__‎\r\n‎L WR|下‎层,低层_‎l ower‎__\r\‎nM_B‎L D|动叶‎片_mov‎i ng_b‎l ade_‎_\r\n‎MAG|‎电磁_el‎e ctri‎c_mag‎n etic‎__\r\‎nMAG‎V|电磁‎阀_ele‎c tric‎_magn‎e tic_‎v alve‎__\r\‎nMAI‎N|主_m‎a in__‎\r\n‎M AIN ‎S TM|主‎蒸汽_ma‎i n_st‎e am__‎\r\n‎M AIN ‎S TM V‎|主汽门_‎m ain_‎s team‎_stop‎_valv‎e__\r‎\nMA‎I N TU‎R B|主机‎_main‎_turb‎i ne__‎\r\n‎M AIN ‎X FMR|‎主变_ma‎i n_tr‎a nsfo‎r mer_‎_\r\n‎MAIN‎T ENAC‎E|检修_‎m aint‎e nanc‎e__\r‎\nMA‎N L|手动‎_Manu‎a l__\‎r\nM‎A TCH|‎满足_ma‎t ch__‎\r\n‎M AX|最‎大_Max‎i mum_‎_\r\n‎MCH ‎R M|机房‎_Mach‎i ne_r‎o om__‎\r\n‎M CHN|‎机械_me‎c hani‎c al__‎\r\n‎M CM|磁‎控表_Ma‎g neti‎c_con‎t rol_‎m eter‎__\r\‎nMCR‎|最大持续‎功率_ma‎x imum‎_cont‎i nuou‎s_rev‎o luti‎o n__\‎r\nM‎D FP|电‎动给水泵_‎m otor‎_driv‎e_fee‎d wate‎r_pum‎p__\r‎\nMD‎S GOP|‎电动调速油‎泵_Mot‎o r_dr‎i ve_s‎p eed_‎g over‎n ing_‎o il_p‎u mp__‎\r\n ‎M ESH|‎啮合_me‎s h__\‎r\nM‎F T|主燃‎料跳闸_m‎a ster‎_fuel‎_trip‎__\r\‎nMGN‎T|永励机‎_magn‎e to_g‎e nera‎t or__‎\r\n‎M ID|中‎间,中部_‎M iddl‎e__\r‎\nMI‎L L|磨煤‎机_coa‎l_mil‎l__\r‎\nMI‎N|最小_‎M inim‎u m__\‎r\nM‎K UP ‎O IL|补‎油_mak‎e-up_‎o il__‎\r\n‎M K UP‎WTR|‎补水_ma‎k e-up‎_wate‎r__\r‎\nMM‎T R|主电‎机_Mai‎n_ele‎c tric‎_moto‎r__\r‎\nMN‎T|力矩_‎M omen‎t__\r‎\nMN‎T R|监视‎_moni‎t or__‎\r\n‎M O|电动‎_moto‎r_ope‎r ated‎__\r\‎nMOD‎E|方式_‎m ode_‎_\r\n‎MOV|‎电动调节门‎_moto‎r_ope‎r ated‎_regu‎l atin‎g_val‎v e__\‎r\nM‎O V|电动‎门_mot‎o r_op‎e rate‎d_val‎v e__\‎r\nM‎S MNT ‎P NT|测‎点_mea‎s urem‎e nt_p‎o int_‎_\r\n‎MTL|‎金属_Me‎t al__‎\r\n‎M TR|电‎机(电动机‎)_ele‎c tric‎_moto‎r__\r‎\nMT‎R|马达_‎m otor‎__\r\‎nMTV‎|动力_m‎o tive‎_powe‎r__\r‎\nN_‎D RV_E‎|非驱动端‎_non_‎d rive‎_end_‎_\r\n‎N_SY‎M|不对称‎_non_‎s ymme‎t ry__‎\r\n‎N A|钠_‎n atri‎u m__\‎r\nN‎E T CT‎L ROO‎M|网控楼‎_netw‎o rk_c‎o ntro‎l_roo‎m__\r‎\n NO‎.|号（量‎词）_Nu‎m ber_‎_\r\n‎NODR‎|失灵_b‎e_out‎_of_o‎r der_‎_\r\n‎NON|‎非_Non‎__\r\‎nNOR‎M|正常_‎n orma‎l__\r‎\nNO‎Z ZLE|‎火嘴_No‎z zle_‎_\r\n‎N-SE‎Q|负序_‎n egat‎i ve_s‎e quen‎c e__\‎r\nN‎T RL P‎N T|中性‎点_Neu‎t ral_‎p oint‎__\r\‎nO_P‎W|工作电‎源_ope‎r atin‎g_pow‎e r__\‎r\nO‎2|氧_O‎2__\r‎\nO2‎CT|含‎氧量_ox‎y gen_‎c onte‎n t__\‎r\nO‎2 CT|‎氧量_ox‎y gen_‎c onte‎n t__\‎r\nO‎I L|油_‎o il__‎\r\n‎O IL B‎O X|油箱‎_Oil_‎b ox__‎\r\n‎O IL C‎L R|冷油‎器_oil‎_cool‎e r__\‎r\nO‎I L FL‎T R|滤油‎器_oil‎_filt‎e r__\‎r\nO‎I L P|‎油泵_oi‎l_pum‎p__\r‎\nOI‎L PIP‎E|油路_‎o il_p‎i pe__‎\r\n‎O IL P‎R S|油压‎_oil_‎p ress‎u re__‎\r\n‎O IL S‎P L|供油‎_oil_‎s uppl‎y__\r‎\nOI‎L STN‎|油站_o‎i l_st‎a tion‎__\r\‎nOIL‎TEM|‎油温_oi‎l_tem‎p erat‎u re__‎\r\n‎O IL T‎K|贮油箱‎_oil_‎t ank_‎_\r\n‎OIL ‎V LU|油‎量_Oil‎_valu‎e__\r‎\nON‎L Y|仅_‎O nly_‎_\r\n‎OPN|‎开式_op‎e n__\‎r\nO‎P N CI‎R|开式循‎环_ope‎n_cir‎c ulat‎i ng__‎\r\n‎O PN C‎I R WT‎R|开式循‎环水_op‎e n_ci‎r cula‎t ing_‎w ater‎__\r\‎n OPN‎DMD|‎打开命令_‎o pen_‎d eman‎d__\r‎\nOP‎N ED|开‎状态_op‎e ned_‎s tatu‎s__\r‎\nOP‎R|操作_‎o pera‎t ion_‎_\r\n‎ORT|‎方向_or‎i enta‎t ion_‎_\r\n‎OUT|‎外部_ou‎t er__‎\r\n‎O UTG ‎W IRE|‎出线_ou‎t goin‎g_wir‎e__\r‎\nOU‎T G WT‎R|出水_‎O utgo‎i ng_w‎a ter_‎_\r\n‎OUTL‎|出口_o‎u tlet‎__\r\‎nOUT‎L SID‎E|吐出端‎_outl‎e t_si‎d e__\‎r\nO‎V CRR‎T|过流_‎o ver_‎c urre‎n t__\‎r\nO‎V EXC‎T R|过励‎磁_ove‎r_exc‎i tato‎r__\r‎\nOV‎LOAD‎|过负荷_‎o ver_‎l oad_‎_\r\n‎OV L‎O AD|过‎载_ove‎r load‎__\r\‎nOV ‎S PD|过‎速_ove‎r_spe‎e d__\‎r\nO‎V VOL‎T|过压_‎o ver_‎v olta‎g e__\‎r\nO‎V ER S‎P D|超速‎_Over‎_spee‎d__\r‎\nOV‎E R TE‎M|超温_‎o ver_‎t empe‎r atur‎e__\r‎\nOV‎F L|溢_‎o verf‎l ow__‎\r\n‎O VFL ‎S TN|溢‎流站_ov‎e rflo‎w_sta‎t ion_‎_\r\n‎OX|工‎作变压器_‎o pera‎t ing_‎t rans‎f orme‎r__\r‎\nP|‎负压_ne‎g ativ‎e_pre‎s sure‎__\r\‎nP_L‎_XFMR‎|厂低变_‎p lant‎_serv‎i ce_l‎o wer_‎t rans‎f orme‎r__\r‎\n P_‎L_XFM‎R|厂高变‎_plan‎t_ser‎v ice_‎h ighe‎r_tra‎n sfor‎m er__‎\r\n ‎P_SHT‎R|屏式过‎热器_pl‎a ten_‎s uper‎h eat_‎_\r\n‎P_XF‎M R|厂变‎_plan‎t_ser‎v ice_‎t rans‎f orme‎r__\r‎\nPA‎|一次风_‎p rima‎r y_ai‎r__\r‎\nPA‎D|瓦(轴‎承)_pa‎d__\r‎\nPA‎D|瓦块_‎p ad__‎\r\n‎P AF|一‎次风机_p‎r imar‎y_air‎_fan_‎_\r\n‎PAO|‎一次油_p‎r imar‎y_oil‎__\r\‎nPB|‎按钮（键）‎_push‎_butt‎o n__\‎r\nP‎C LVL‎|粉位_P‎C_lev‎e l__\‎r\nP‎C E|排粉‎机_pul‎v eriz‎e d_co‎a l_ex‎h aust‎e r__\‎r\nP‎C S|制粉‎系统_Pu‎l veri‎z ed-c‎o al_s‎y stem‎__\r\‎nPCT‎|百分比_‎P erce‎n t__\‎r\nP‎H|相_p‎h ase_‎_\r\n‎PH D‎I FF|相‎位差_ph‎a se_a‎n gle_‎d iffe‎r ence‎__\r\‎nPH ‎L OSE|‎缺相_ph‎a se_l‎o se__‎\r\n‎P H MD‎F R|调相‎机_pha‎s e_mo‎d 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yor_‎_\r\n‎PULS‎E|脉冲_‎P ulse‎__\r\‎nPUR‎OC|净‎油室_Pu‎r ity_‎o il_c‎h ambe‎r__\r‎\nPU‎R GE|吹‎扫_pur‎g e__\‎r\nP‎U RITY‎|纯度_p‎u rity‎__\r\‎nPUT‎I N|投_‎p utti‎n g_in‎t o__\‎r\nP‎V L FD‎R|给粉机‎_pulv‎e rize‎d_coa‎l_fee‎d er__‎\r\n‎P W|电源‎_Powe‎r_sup‎p ly__‎\r\n‎P W|功率‎_Powe‎r__\r‎\nPW‎ON|有‎电_pow‎e r_on‎__\r\‎nR_P‎W|无功_‎r eact‎i ve_p‎o wer_‎_\r\n‎RAD ‎/ AXI‎|径向_r‎a dial‎_/_ax‎i al__‎\r\n‎R ATE|‎率_rat‎e__\r‎\nRA‎T IO|比‎_Rati‎o__\r‎\nRB‎|快速减负‎荷_run‎_back‎__\r\‎nRBB‎R BAL‎L|胶球_‎r ubbe‎r_bal‎l__\r‎\nRB‎C H|消泡‎箱_rid‎d ing_‎b ubbl‎e_cha‎m ber_‎_\r\n‎RBEA‎R|径向轴‎承_Rad‎i al_b‎e arin‎g__\r‎\nRC‎T F|整流‎的_rec‎t ifyi‎n g__\‎r\nR‎C TFR|‎整流器_r‎e ctif‎i er__‎\r\n‎R EAR ‎P LTN|‎后屏_re‎a r_pl‎a ten_‎_\r\n‎RECI‎R|再循环‎_reci‎r cula‎t e__\‎r\nR‎E CIR ‎V|再循环‎阀_rec‎i rcul‎a ting‎_valv‎e__\r‎\nRE‎D R|减少‎_Redu‎c e__\‎r\nR‎E F|参考‎_refe‎r ence‎__\r\‎nREL‎A Y|继电‎器_rel‎a y__\‎r\nR‎E MO|遥‎控_Rem‎o te__‎\r\n‎R ENEW‎|重新_r‎e new_‎_\r\n‎RETR‎|退回,缩‎回_ret‎r act_‎_\r\n‎RFF|‎回料风机_‎r etur‎n_fue‎l_fan‎__\r\‎nRGE‎N|再生_‎r egen‎e rati‎o n__\‎r\nR‎G L ST‎G|调节级‎_regu‎l atin‎g__\r‎\nRG‎L V|调‎节门_re‎g ulat‎e_val‎v e__\‎r\nR‎H T|再热‎_Rehe‎a t__\‎r\nR‎H T ST‎M|再热蒸‎汽_reh‎e ated‎_stea‎m__\r‎\nRH‎T R|再热‎器_reh‎e ater‎__\r\‎nRI|‎右_rig‎h t__\‎r\nR‎L TV E‎X P|相对‎膨胀_re‎l ativ‎e_exp‎a nsio‎n__\r‎\nRM‎T|远方_‎r emot‎e__\r‎\nRO‎T SPD‎|转速_r‎o tati‎n g_sp‎e ed__‎\r\n‎R OW|排‎(量词)_‎r ow__‎\r\n‎R RT|反‎转_rev‎e rsal‎_rota‎t ion_‎_\r\n‎RSET‎|复位_R‎e set_‎_\r\n‎RT|正‎转_rot‎a tion‎__\r\‎nRTN‎(OIL‎, WTR‎)|回(油‎,水)_r‎e turn‎_(oil‎,_wat‎e r)__‎\r\n ‎R TN A‎I R|回送‎风_ret‎u rn_a‎i r__\‎r\nR‎T R|转子‎_roto‎r__\r‎\nRU‎N|运行_‎R un__‎\r\n‎R UNP|‎运行状态_‎R unni‎n g_po‎s itio‎n__\r‎\nRV‎R S|反向‎_reve‎r se__‎\r\n‎R WG|反‎冲洗_Re‎v ersa‎l_was‎h ing_‎_\r\n‎S_A|‎A侧_si‎d e_A_‎_\r\n‎S_BL‎D|静叶片‎_stat‎i onar‎y_bla‎d e__\‎r\nS‎A|二次风‎_seco‎n dary‎_air_‎_\r\n‎SAD|‎二次风挡板‎_seco‎n dary‎_air_‎d ampe‎r__\r‎\nSA‎H|暖风器‎_stea‎m_air‎_heat‎e r__\‎r\nS‎B W|吹灰‎_soot‎_blow‎__\r\‎nSBW‎R|吹灰器‎_soot‎_blow‎e r__\‎r\nS‎C|短路_‎S hort‎_circ‎u it__‎\r\n‎S CHN|‎同步器,同‎操器_Sy‎n chro‎n izer‎__\r\‎nSCN‎R|火检_‎s cann‎e r__\‎r\nS‎C ORE|‎比_sco‎r e__\‎r\nS‎D|停止命‎令_sto‎p_com‎m and_‎_\r\n‎SDOP‎|汽动油泵‎_stea‎m-dri‎v en_o‎i l_pu‎m p__\‎r\nS‎E AL|密‎封_Sea‎l ing_‎_\r\n‎SEAL‎OIL|‎密封油_s‎e al_o‎i l__\‎r\nS‎E AL W‎T R|密封‎水_sea‎l_wat‎e r__\‎r\nS‎E L|选择‎_sele‎c t,_s‎e lect‎i on__‎\r\n‎S EP|分‎离器_Se‎p arat‎o r__\‎r\nS‎E T|设定‎_Set_‎_\r\n‎SFT|‎安全_Sa‎f ety_‎_\r\n‎SFT|‎保安_sa‎f ety_‎_\r\n‎SGNL‎|信号_s‎i gnal‎__\r\‎nSH|‎仓_Sto‎r ehou‎s e__\‎r\nS‎H|过热_‎s uper‎h eate‎d__\r‎\nSH‎STM|‎过热蒸汽_‎s uper‎h eate‎d_ste‎a m__\‎r\nS‎H ELL|‎壳体_sh‎e ll__‎\r\n‎S HFT|‎轴_Sha‎f t__\‎r\nS‎H KPRF‎|耐震_S‎h ockp‎r oof_‎_\r\n‎SHTR‎|过热器_‎s uper‎h eate‎r__\r‎\nSI‎D E|侧_‎S ide_‎_\r\n‎SIDE‎WALL‎|侧墙_s‎i de_w‎a ll__‎\r\n‎S LGRM‎V|出渣机‎，除渣机_‎s lag_‎r emov‎e r__\‎r\nS‎L OT|槽‎_slot‎__\r\‎nSLO‎W DN|‎减速_sl‎o w_do‎w n__\‎r\nS‎P|停止状‎态_sto‎p_pos‎i tion‎__\r\‎nSPD‎|速度_S‎p eed_‎_\r\n‎SPD ‎G VNR|‎调速器_s‎p eed_‎g over‎n or__‎\r\n‎S PD U‎P|加速_‎s peed‎_up__‎\r\n‎S PRAY‎|喷水_s‎p ray_‎_\r\n‎SRC|‎源_sou‎r ce__‎\r\n‎S SPB|‎滑动止推轴‎承_Sli‎d ing_‎s top_‎p ushi‎n g_be‎a ring‎__\r\‎n SSR‎|传感器_‎S enso‎r__\r‎\nST‎|状态_s‎t atus‎,_sta‎t e__\‎r\nS‎T AT|定‎子_sta‎t or__‎\r\n‎S TBY|‎备用_st‎a ndby‎__\r\‎nSTB‎Y PW|‎备用电源_‎s tand‎b y_po‎w er_s‎o urce‎__\r\‎nSTE‎P UP|‎升压_st‎e p_up‎__\r\‎nSTG‎|级_St‎a ge__‎\r\n‎S TG I‎|第一级_‎S tage‎_one_‎_\r\n‎STG ‎I|一级_‎S tage‎_one_‎_\r\n‎STM|‎汽_Ste‎a m__\‎r\nS‎T M HD‎R|集汽联‎箱_ste‎a m_he‎a der_‎_\r\n‎STM ‎R OOM|‎蒸汽室_s‎t eam_‎c hamb‎e r__\‎r\nS‎T M SP‎L|供汽_‎s team‎_supp‎l y__\‎r\nS‎T M TE‎M|汽温_‎s team‎_temp‎e ratu‎r e__\‎r\nS‎T MLP|‎导汽管_s‎t eam_‎l ead_‎p ipe_‎_\r\n‎STN|‎站_Sta‎t ion_‎_\r\n‎STR|‎开始_st‎a rt__‎\r\n‎S TR|启‎动_sta‎r t__\‎r\nS‎T RD|启‎动指令_S‎t art_‎d eman‎d__\r‎\nST‎R OKE|‎行程_st‎r oke_‎_\r\n‎SURG‎E|喘震_‎s urge‎__\r\‎nSWA‎Y|摆动_‎s way_‎_\r\n‎SWTH‎|开关_s‎w itch‎__\r\‎nSWT‎H|切换_‎S witc‎h__\r‎\nSY‎M|对称_‎s ymme‎t ry__‎\r\n‎S YNCH‎|同期_s‎y nchr‎o nous‎__\r\‎nSYS‎|系统_s‎y stem‎__\r\‎nT V‎|三通阀_‎T_val‎v e__\‎r\nT‎A|三次风‎_tert‎i ary_‎a ir__‎\r\n‎T AP|抽‎头_tap‎__\r\‎nTDF‎P|汽动给‎水泵_tu‎r bine‎-driv‎e n_fe‎e dwat‎e r_pu‎m p__\‎r\n T‎E M(T)‎|温度_t‎e mper‎a ture‎__\r\‎nTES‎T|检测_‎t est_‎_\r\n‎TEST‎|试验_t‎e st__‎\r\n‎T HRL|‎节流_Th‎r ottl‎e__\r‎\nTH‎S T|推力‎_thru‎s t__\‎r\nT‎H ST B‎E AR|推‎力轴承_t‎h rust‎_bear‎i ng__‎\r\n‎T HTTL‎|截止_t‎h rott‎l e__\‎r\nT‎O|至_t‎o__\r‎\nTO‎INDC‎T|仪（器‎）用_to‎_indi‎c ator‎__\r\‎nTOP‎|顶_to‎p__\r‎\nTO‎R OSC|‎扭振_to‎r sion‎a l_os‎c illa‎t ion_‎_\r\n‎TPLR‎|翻车机_‎t ippl‎e r__\‎r\nT‎R IP|跳‎闸_tri‎p__\r‎\nTR‎M T|处理‎_trea‎t ment‎__\r\‎nTUR‎B|(汽)‎机_tur‎b ine_‎_\r\n‎TURB‎|汽机_t‎u rbin‎e__\r‎\nTU‎R B SI‎D E|机端‎_turb‎i ne_s‎i de__‎\r\n‎T URN|‎盘车_tu‎r ning‎__\r\‎nTUR‎N|匝间_‎t urn_‎_\r\n‎TURN‎ROOM‎|转向室_‎t urni‎n g_ro‎o m__\‎r\nT‎V S|复速‎级_two‎-velo‎c ity_‎s tage‎__\r\‎nUNG‎E AR|脱‎扣_Ung‎e arin‎g__\r‎\nUN‎I T|机组‎_unit‎__\r\‎nUP|‎上,上部_‎u p__\‎r\nU‎P P|上层‎_uppe‎r__\r‎\nUS‎E|用（使‎用）_Us‎e__\r‎\nUS‎E R|用户‎_User‎__\r\‎nV|阀‎门_val‎v e__\‎r\nV‎A CM|真‎空_Vac‎u um__‎\r\n‎V ACM ‎B RK V‎|真空破坏‎阀_vac‎u um_b‎r eak_‎v alve‎__\r\‎nVAC‎M P|真‎空泵_va‎c uum_‎p ump_‎_\r\n‎VBRT‎|振动_v‎i brat‎i on__‎\r\n‎V ENT|‎排空_Ve‎n t__\‎r\nV‎E RT|立‎式_ver‎t ical‎_type‎__\r\‎nVER‎T|竖直(‎方向)的_‎v erti‎c al__‎\r\n‎V ICE|‎副_vic‎e__\r‎\nVO‎L T|电压‎_volt‎a ge__‎\r\n‎V OLT ‎L OOP|‎电压回路_‎v olta‎g e_lo‎o p__\‎r\nW‎A LL|墙‎_Wall‎__\r\‎nWAL‎L TEM‎|壁温_w‎a ll_t‎e mper‎a ture‎__\r\‎nWAS‎H|清洗_‎w ash_‎_\r\n‎WCL|‎有煤_wi‎t h_co‎a l__\‎r\nW‎H L DA‎Y|全天_‎w hole‎_day_‎_\r\n‎WHL ‎P LNT|‎全厂_wh‎o le_p‎l ant_‎_\r\n‎WIND‎B OX|风‎箱_Win‎d box_‎_\r\n‎WND|‎绕组_wi‎n ding‎__\r\‎nWNU‎T|磨损_‎w orn_‎o ut__‎\r\n‎W ORK|‎工作_wo‎r king‎__\r\‎nWOR‎K SHOP‎|厂房_W‎o rksh‎o p__\‎r\nW‎T R|水_‎w ater‎__\r\‎nWTR‎BOX|‎水箱_wa‎t er_b‎o x__\‎r\nW‎T R CL‎C T|集水‎箱_wat‎e r_co‎l lect‎o r__\‎r\nW‎T R CU‎R TAIN‎|水幕_w‎a ter_‎c urta‎i n__\‎r\nW‎T R CU‎T|断水_‎c ut_o‎f f_th‎e_wat‎e r_su‎p ply_‎_\r\n‎WTR ‎L VL|水‎位_wat‎e r_le‎v el__‎\r\n‎W TR P‎|水泵_W‎a ter_‎p ump_‎_\r\n‎WTR ‎S EAL|‎水封_Wa‎t er_s‎e al__‎\r\n‎W TR S‎P L|上水‎_wate‎r-sup‎p ly__‎\r\n‎W TR T‎R MT|水‎处理_wa‎t er_t‎r eatm‎e nt__‎\r\n‎W TR W‎A LL|水‎冷壁_wa‎t er_w‎a ll__‎\r\n‎X FMR|‎变压器_t‎r ansf‎o rmer‎__\r\‎nXPR‎T|输送_‎t rans‎p ort_‎_\r\n‎02-D‎L-MU|‎#2机22‎0V直流系‎统→#2机‎220V直‎流动力母线‎电压→\r‎\n02‎-KZ-M‎U|#2机‎220V直‎流系统→#‎2机220‎V直流控制‎母线电压→‎\r\n‎S E1-2‎F-A1|‎#2发-变‎组系统→#‎2发电机定‎子电流 A‎→#2 G‎E N ST‎A T CR‎R T A\‎r\n S‎E1-2F‎-A2|#‎2发-变组‎系统→#2‎发电机定子‎电流B→‎#2 GE‎N STA‎T CRR‎T B\r‎\n SE‎1-2F-‎A3|#2‎发-变组系‎统→#2发‎电机定子电‎流C→#‎2 GEN‎STAT‎CRRT‎C\r\‎n SE1‎-2F-A‎4|#2发‎-变组系统‎→#2发电‎机负序电流‎→#2 G‎E N N‎-SEQ ‎C RRT\‎r\nS‎E1-2F‎-V1|#‎2发-变组‎系统→#2‎发电机定‎子三相电压‎AB→#‎2 GEN‎STAT‎T-PH‎VOLT‎AB\r‎\nSE‎1-2F-‎V2|#2‎发-变组系‎统→#2发‎电机定子三‎相电压 B‎C→#2 ‎G EN S‎T AT T‎-PHV‎O LT B‎C\r\n‎SE1-‎2F-V3‎|#2发-‎变组系统→‎#2发电机‎定子三相电‎压CA→‎#2 GE‎N STA‎T T-P‎H VOL‎T CA\‎r\nS‎E1-2F‎-V5|#‎2发-变组‎系统→#2‎发电机定子‎绝缘电压A‎相→#2 ‎G EN S‎T AT I‎S LNV‎O LT A‎-PH\r‎\nSE‎1-2F-‎V6|#2‎发-变组系‎统→#2发‎电机定子绝‎缘电压B相‎→#2 G‎E N ST‎A T IS‎L N VO‎L T B-‎P H\r\‎nSE1‎-2F-V‎7|#2发‎-变组系统‎→#2发电‎机定子绝缘‎电压C相→‎#2 GE‎N STA‎T ISL‎N VOL‎T C-P‎H\r\n‎SE1-‎2F-H1‎|#2发-‎变组系统→‎#2发电机‎频率→#2‎GEN ‎F REQ\‎r\nS‎E1-2F‎-H2|#‎2发-变组‎系统→22‎0KV南母‎频率→22‎0KV ‎S YS ‎F REQ\‎r\nS‎E1-2F‎-H3|#‎2发-变组‎系统→22‎0KV北母‎频率→22‎0KV ‎S YS ‎F REQ\‎r\nS‎E1-2F‎-W|#2‎发-变组系‎统→#2发‎电机有功功‎率→#2 ‎G EN A‎-PW\r‎\nSE‎1-2F-‎V a|#2‎发-变组系‎统→#2发‎电机无功功‎率→#2 ‎G EN R‎-PW \‎r\nS‎E1-2F‎-COS|‎#2发-变‎组系统→#‎2发电机功‎率因数(D‎C S计算实‎现)→#2‎GEN ‎P W CO‎S\r\n‎SE1-‎2FB-V‎1|#2发‎-变组系统‎→220 ‎k V南母母‎线电压→‎220KV‎S-BU‎S VOL‎T\r\n‎SE1-‎2FB-V‎2|#2发‎-变组系统‎→220 ‎k V 北母‎母线电压‎→220K‎V N-B‎U S VO‎L T\r\‎nSE1‎-2EX-‎1ZA|#‎2发-变组‎系统→#2‎发电机#1‎整流柜输出‎直流电流→‎#2 RC‎T F CA‎B OUT‎P DC ‎C RRT\‎r\nS‎E1-2E‎X-2ZA‎|#2发-‎变组系统→‎#2发电机‎#2整流柜‎输出直流电‎流→#2 ‎R CTF ‎C AB O‎U TP D‎C CRR‎T\r\n‎SE1-‎2EX-A‎1|#2发‎-变组系统‎→#2发电‎机转子电流‎→#2 G‎E N RT‎R CRR‎T\r\n‎SE1-‎2EX-A‎3|#2发‎-变组系统‎→#2发电‎机主励转子‎电压→#2‎GEN ‎M AIN ‎E XCTR‎RTR ‎V OLT\‎r\nS‎E1-2E‎X-A5|‎#2发-变‎组系统→#‎2发电机主‎励转子电流‎→#2 G‎E N MA‎I N EX‎C TRR‎T R CR‎R T\r\‎nSE1‎-2EX-‎V1|#2‎发-变组系‎统→#2发‎电机转子电‎压→#2 ‎G EN R‎T R VO‎L T\r\‎nSE1‎-2EX-‎V2 |#‎2发-变组‎系统→#2‎发电机付励‎定子电压→‎#2 GE‎N VIC‎E EXC‎T RS‎T AT V‎O LT\r‎\nSE‎1-2EX‎-V3|#‎2发-变组‎系统→#2‎发电机转子‎正对地电压‎→#2 G‎E N RT‎R P-‎V S-GN‎D VOL‎T\r\n‎SE1-‎2EX-V‎4|#2发‎-变组系统‎→#2发电‎机转子负对‎地电压→#‎2 GEN‎RTR ‎N-VS-‎G ND V‎O LT\r‎\nSE‎1-2EX‎-V6|#‎2发-变组‎系统→#2‎发电机功角‎(电压电势‎夹角)→#‎2 MAI‎N EXC‎TSTA‎T VOL‎T\r\n‎SE7-‎2GB-W‎|#2高厂‎变系统→#‎2高厂变有‎功功率→#‎2 P-H‎-XFMR‎A-PW‎\r\n‎SE7-‎2GB-V‎A R|#2‎高厂变系统‎→#2高厂‎变无功功率‎→#2 P‎-H-XF‎M R R-‎P W\r\‎nSE7‎-2GB-‎A1|#2‎高厂变系统‎→#2高厂‎变高压侧电‎流→#2 ‎P-H-X‎F MR H‎-VOLT‎CRRT‎\r\n‎SE7-‎2GB-A‎2|#2高‎厂变系统→‎613开关‎电流→61‎3 SWT‎H CRR‎T\r\n‎SE7-‎2GB-A‎3|#2高‎厂变系统→‎614开关‎电流→61‎4 SWT‎H CRR‎T\r\n‎SE7-‎B FA-A‎1|#2高‎厂变系统→‎603开关‎电流→60‎3 SWT‎H CRR‎T\r\n‎SE7-‎B FB-A‎1|#2高‎厂变系统→‎604开关‎电流→60‎4 SWT‎H CRR‎T\r\n‎SE7-‎2GB-V‎1|#2高‎厂变系统→‎6 kV ‎3段母线电‎压→6 K‎V #3 ‎B US V‎O LT\r‎\nSE‎7-2GB‎-V2|#‎2高厂变系‎统→6 k‎V 4段母‎线电压→6‎KV #‎4 BUS‎VOLT‎\r\n‎S E7-2‎G B-V5‎|#2高厂‎变系统→6‎kV 3‎段绝缘电‎压AN→‎6 KV ‎#3 IS‎L T VO‎L T AN‎\r\n ‎S E7-2‎G B-V6‎|#2高厂‎变系统→6‎kV 3‎段绝缘电压‎BN→6‎KV #‎3 ISL‎T VOL‎T BN\‎r\n S‎E7-2G‎B-V7|‎#2高厂变‎系统→6 ‎k V 3 ‎段绝缘电压‎CN→6‎KV #‎3 ISL‎T VOL‎T CN\‎r\n S‎E7-2G‎B-V8|‎#2高厂变‎系统→6 ‎k V 4 ‎段绝缘电压‎AN→6‎KV #‎4 ISL‎T VOL‎T AN ‎\r\n ‎S E7-2‎G B-V9‎|#2高厂‎变系统→6‎kV 4‎段绝缘电压‎BN→6‎KV #‎4 ISL‎T VOL‎T BN ‎\r\n ‎S E7-2‎G B-V1‎0|#2高‎厂变系统→‎6 kV ‎4段绝缘‎电压 CN‎→6 KV‎#4 I‎S LT V‎O LT C‎N \r\‎n SE8‎-3DB-‎V|#2机‎低压厂用电‎系统→38‎0V3段母‎线电压→3‎80V #‎3 BUS‎VOLT‎\r\n‎S E8-4‎D B-V|‎#2机低压‎厂用电系统‎→380V‎4段母线电‎压→380‎V #4 ‎B US V‎O LT\r‎\n SE‎8-3DB‎-A|#2‎机低压厂用‎电系统→#‎3低厂变高‎压侧电流→‎#3 P-‎L-XFM‎R H-V‎O LT ‎S IDE ‎C RRT\‎r\nS‎E8-4D‎B-A|#‎2机低压厂‎用电系统→‎#4低厂变‎高压侧电流‎→#4 P‎-L-XF‎M R H-‎V OLT ‎S IDE ‎C RRT\‎r\nS‎G Y-1C‎H-A|#‎2机公用及‎备用系统→‎1除灰甲开‎关电流→\‎r\nS‎G Y-2C‎H-A|#‎2机公用及‎备用系统→‎2除灰甲开‎关电流→\‎r\nS‎E4-ZM‎B-A|#‎2机公用及‎备用系统→‎照明检修变‎高压侧电流‎→M-L-‎X HIG‎H VOL‎T SID‎E CRR‎T\r\n‎SE4-‎Z MB-V‎|#2机公‎用及备用系‎统→照明检‎修段母线电‎压→M-L‎-X BU‎S VOL‎T\r\n‎SE5-‎02B-A‎|#2机公‎用及备用系‎统→#2低‎备变高压侧‎电流→#2‎ LVS‎X H-‎V SID‎E CRR‎T\r\n‎SE5-‎02B-V‎|#2机公‎用及备用系‎统→380‎V备2段母‎线电压→3‎80V S‎T BY #‎2 BUS‎VOLT‎\r\n‎S E1-2‎F B-R1‎|#2发-‎变组系统→‎#2主变油‎温1→#‎2 MAI‎N XFM‎R OIL‎TEM ‎1\r\n‎SE7-‎2GB-R‎1|#2高‎厂变系统→‎#2高厂变‎温度→#2‎P-H-‎X FMR ‎T EM\r‎\nSE‎8-3DB‎-R1|#‎2机低压厂‎用电系统→‎#3低厂变‎温度→#3‎P-L-‎X FMR ‎T EM\r‎\nSE‎1-2FB‎-R2|#‎2发-变组‎系统→#2‎主变油温2‎→#2 M‎A IN X‎F MR O‎I L TE‎M 2\r‎\nSE‎8-4DB‎-R1|#‎2机低压厂‎用电系统→‎#4低厂变‎温度→#4‎P-L-‎X FMR ‎T 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A＋K选型计算书中英文对照A+ FlowTek Program Suite Ver. #2.0.2Friday, July 11, 2008 3:55:41 PM______________节流装置：平衡流量计- 流体计算设计Flow Element: Balanced Flow Meter - Liq Mass Flow, Sizing and Design ______________工程师Engineer:项目名称Project Name:仪表位号Tag No.:项目编号Project Number:仪表型号Model:介质名称： Fluid:______________管道规格说明Pipe Specifications:(User Spec:)管道内径Pipe ID =管道直径Diameter =管道壁厚Schedule =管道粗糙度Pipe Roughness =管道材质Material =______________平衡流量计规格Balanced Flow Meter Specifications:取压口海拔高度变化（一般情况下，该值取0）Tap Elevation Change = 0 ftß值Beta Ratio =校准系数Calibration Factor =节流件厚度Plate Thickness = 3/8 Inch平衡流量计类型＝与雷诺数相匹配Balanced Flow Meter Type = Reynolds Number Matching (NRe)第一层孔的个数1st Ring Number of Holes =第二层孔的个数2nd Ring Number of Holes =孔的设计＝直角切孔Hole Design = Square cut holes.适合位置＝直管段>5 Fitting Location = Upstream fitting L/D > 5.加工类型＝无脏物类型Process Type = Non-fouling service.孔的设计＝孔的标准设计Hole Clearance Design = Hole layout based on standard design.______________流体过程数据Process Data at Flowing Conditions:刻度流量Mass Flow =温度Temperature =压力Pressure =密度Density =动力粘度Viscosity =蒸发压力Vapor Pressure =注意：流体状态计算包括管道/节流原件的热膨胀效应Note: Pipe/Flow-Element thermal expansion effects at flowing conditions included in sizing and fabrication specifications.______________平衡流量计基本设计数据Balanced Flow Meter Flow Element Design Basis:刻度差压Tap Pressure Drop =刻度差压Flow Pressure Drop =海拔高度对应的大气压相对变化Elevation Pressure Change =永久压力损失Permanent Pressure Loss =压力恢复Pressure Recovery =流出系数Total Cd =雷诺数Reynolds No. =。

ACCURATE CALCULATION OF PIPELINE TRANSPORT CAPACITYLeif Idar Langelandsvik 1, Willy Postvoll1, Britt Aarhus1, Kristin Kinn Kaste11. Gassco ASKeywords: 1. natural gas; 2. pipeline capacity; 3. friction; 4. ambient temperature, 5. operational data1 AbstractGassco is the operator of the largest sub-sea transportation system for natural gas in the world. This implies selling transport capacity to shippers of natural gas. Once a pipeline is built, the physical capacity is determined by boundary conditions such as available inlet and outlet pressure. In order to achieve optimal utilization of the pipelines and hence optimal return of invested capital, it is of great importance to calculate this capacity as accurately as possible. Failing to meet booked capacities will result in penalties and poorer reputation while under estimation of the capacity can possibly trigger too early investments in new infrastructure. Both situations are strongly unwanted. Gassco has therefore developed a well proven methodology for transport capacity calculation, which will be elaborated in this paper.Over the last years Gassco has improved the former approach of capacity calculation, namely a capacity test. This improvement has involved further development of the models, particularly by means of heat transfer, which now makes the models more accurate than before and even better suited to calculate transport capacity. Incorporation of real-time modelled sea-bottom temperatures from the UK Meteorological Shelf-seas model provides the models with the best available now-casts and two-day-forecasts of the sea- bottom temperature across most of the North Sea. Better estimates of actual sea-bottom temperatures on certain days in the past combined with short-term forecasts updated every day reduce margins and utilize day-to-day variations in capacity induced by the ambient temperature. Eventually instead of using one single capacity-test point, Gassco has now extended this methodology to make use of steady-state operational data periods in the past, which one-by-one is treated like a capacity test. The results are then averaged to reduce the random error uncertainty in the estimate.Basically these measures have increased the accuracy of the transport capacity calculations. It is however also seen that the result is increased transport capacity which can be sold to the shippers. Altogether the methodology outlined in this paper probably represents the best practice in gas industry with respect to transport capacity calculation. The benefit is increased capacity and consequently flexibility for the shippers, increased income for the infrastructure owners and reduced unit tariff for the shippers.2 Introduction/BackgroundNatural gas plays an important role in the energy supply of Europe and the world. Natural gas accounts for almost a quarter of worl d’s energy consumption. According to energy statistics f rom , total world production in 2008 was 3,065 billion cubic meters, i.e. 3.1·1012 MSm3, of which Norway contributed 3.2% (99.2 billion Sm3). Natural gas is mainly transported in pipelines, either onshore or offshore.The Norwegian gas transportation system is illustrated in Figure 1 and consists of 7,800 km of pipelines, processing plants, riser platforms and receiving terminals, yielding a very complex network which is the largest offshore transportation system in the world. United Kingdom and continental Europe are supplied through seven large diameter subsea pipelines covering around 15% of the European natural gas consumption. The export pipelines are between 500 and 800 km long with a typical inner diameter of 1 m. Security of supply for the customers requires reliable and optimal operation of the transport system.Figure 1 Overview of the trans portation system operated by Gassco.After a reorganization of the infrastructure on the Norwegian Continental Shelf in 2001, the state- owned company Gassco was appointed the operator of the transportation system. The ownership of the infrastructure is organized in a joint-venture, Gassled, where the different companies’ interest is determined based on their historical investments. Gassco is thus responsible for redelivering the requested amount ofgas at the different exit points. The shippers have a certain capacity right, a booked capacity, at each exit point. They can then nominate up to this amount of gas at each exit point, as long as they make the same amount of gas available at an entry point. The shipper may be a producer of gas, or it may have purchased the gas upstream the entry point. The capacity is sold as non-interruptable.Transportation capacity is made available for shippers in dedicated booking rounds, where capacity can be booked on long-term, medium-term or short-term. This will be elaborated later. The unit price of capacity is fixed and regulated by Norwegian government. All the capacity is sold at nearly all exit points, even though it is only fully exploited perhaps a few weeks during a year.High accuracy in the pipeline transport capacity calculations is of crucial importance in order to ensure optimal utilization of invested capital in the pipeline infrastructure. One wants the calculations to be as close to, but not larger than, the true capacity as possible. This will ensure optimal utilization of invested capital. As soon as a pipeline is built, the true capacity is determined by the diameter, length, available inlet compression, minimum delivery pressure and other physical parameters. In Gassco it is the job of scientists to estimate this figure exactly before the commercial department sells the capacity to the shippers. This paper explains the elaborate process used by Gassco to calculate an exact hydraulic capacity. A process that leads to a very accurate hydraulic capacity, and which has been used with great success.The Gassco operated pipelines are often single-leg with one supply point and one delivery point. Since the pipelines are sub-sea, instrumentation is also only found at the inlet and outlet. The methodology is therefore most elaborate for this kind of pipeline. Nonetheless, it also covers pipelines with branches.a. Capacity DefinitionsGassco uses several definitions for pipeline transport capacity. The hydraulic capacity is the calculated maximum physical throughput using maximum inlet pressure and minimum outlet pressure. Available Technical Capacity accounts for limitations in system boundary conditions, eg. caused by limited inlet pressure due to dependency with other pipelines. A fuel factor is also deducted to account for metering errors and fuel gas consumption in either compressors or heating stations. The committable capacity is the capacity that is available for stable deliveries. An operational flexibility (opflex) of 1 or 2 % is usually deducted from the available technical capacity to ensure that small operational disturbances do not lead to loss of delivered gas. Gassco has the mandate to hold back capacity for certain periods. When this hold back is deducted, the bookable capacity is obtained. This is the capacity that is offered to the shippers.b. Pipeline SimulatorsThe transport capacity of Gassco operated pipelines is calculated by using computer simulation models. A detailed model of the pipeline is implemented in a commercially available simulation software. The methodology described in this paper is independent of the chosen software, and should work equally well with most available pipeline simulation software packages. Great care is taken to ensure that all pipeline parameters such as pipeline length, diameter, thickness of different wall layers, elevation profile and burial depth on the sea bed are correct. After the pipeline is installed, the design data is combined with survey data to obtain the best possible data.The simulation software uses the Benedict-Webb-Ruben-Starling (BWRS) equation of state. Great effort has been put into tuning the coefficients to ensure it predicts the density of typical North Sea gases well. The predictive power of the viscosity correlation Lee-Gonzalez-Eakin (LGE) has also been analyzed. The correlation has a simple structure which makes it attractive for use in real-time systems. And it has also proved to predict viscosity for natural gas mixtures well. Gassco has initiated a measurement series of viscosity, and has also proposed a new set of coefficients for the LGE-correlation based on these measurements.The heat transfer model is important in order to simulate the gas temperature correctly. This will be discussed later in the paper.All pipeline simulators use a friction factor correlation which takes wall roughness as input, and calculates the friction factor which gives the wall friction in the model. One of the main uncertainties when modelling pipeline flow, is which roughness factor to use and how the friction shall be calculated based on it. This is also discussed below.c. InstrumentationIn order to achieve the desired accuracy of the transport capacity calculations, Gassco has put a lot of effort into the instrumentation of the pipelines. All pipelines are equipped with state-of-the-art flow meters and pressure transmitters at all supply and delivery points. The pressure transmitters usually have an absolute uncertainty of 52 mBar within a range of 0-200 barg or 0-400 barg depending on the application. The flow meters are either qualified as fiscal or have a similar uncertainty. Usually they are ultrasound⎧ metering stations with an uncertainty of 0.5-0.8 %. Both pressure transmitters and flow meters are calibrated sufficiently often to maintain this uncertainty level over time.Temperature transmitters and gas chromatographs are not that important for the capacitycalculations, but the quality is still very good. The temperature elements are mounted in the gas and close to the real gas flow, and yet keeping the pipelines pigable without damaging the elements. Skin temperature meters are not used as boundary conditions for the models.3Capacity Calculation MethodologyWhen a new pipeline is planned, it is designed to meet a transport capacity need. This means thatafter finding the optimal route from the supply point to the delivery point and the length of this route, the diameter is chosen such that the requested capacity is obtained. This is performed using a pipeline simulator with all design data as input, a slightly conservative ambient temperature estimate and the standard Colebrook-White friction factor correlation with design roughness of 5 micron. Flow coated inner walls is assumed. Originally Gassco, and the previous operators of the transportation system, used 10 micron as the design roughness. Studies however revealed that 5 micron is closer to the true value, and still on the conservative side. The design capacity is used in the first booking rounds for a new pipeline.After the pipeline has commenced operation a capacity test is performed to find the hydraulicroughness in a real test of the pipeline, which is elaborated below.Over the last years the capacity calculation methodology employed by Gassco has been improved inseveral ways. The two major improvements are use of historical operational data periods to improve the accuracy even more and the use of up-to-date ambient sea bottom temperatures from a real time model run by the UK Meteorological Office. These improvements are described below.First of all in this section, some introductory information about wall friction and pressure drop inpipelines is given.a. Friction factor and roughnessThe set of equations describing flow of natural gas in a pipeline can be used to show that the mainresistance to flow in a pipeline is friction against the wall. Almost all the pressure drop is therefore used to overcome frictional forces. Getting the frictional forces correct is hence very important in getting the pressure drop versus flow rate and transport capacity correct.For decades the Colebrook-White correlation (see Colebrook (1939)) has been widely acceptedmore or less as an industry standard in calculating the friction factor (f ) based on roughness (µ, often denoted hydraulic roughness), Reynolds number (Re , turbulence intensity) and inner diameter (D ). Moody plotted the correlation in a semi-logarithmic diagram, known as Moody-diagram, which made it easily accessible without much computation (see Figure 4).1= 2 log 2.51 +Eq. 1f Re f 3.7DExperiments have however shown that different surfaces give different friction factor characteristics.This is particularly valid for the transition region, where the flow changes from smooth turbulent to fully rough turbulent. None has succeeded in explaining why the different surfaces give exactly the friction factor characteristics they give, or predicting friction factor based on measurements of the physical wall surface.Even if accepting the Colebrook-White correlation as the valid one, it remains to find the hydraulicroughness (µ). This can differ significantly from the physically measured wall roughness. Research has proposed to set hydraulic roughness equal 1.5-5 times the measured wall roughness (see e.g. Langelandsvik et al. (2008) and Shockling et al. (2006)). The physical roughness height in commercial steel pipes is very low. Gassco has measured it to be in the range of 2 to 5 micron. When scanned by a human finger most observers would characterize this as perfectly smooth. However, at high enough Reynolds numbers, the laminar sublayer next to the wall diminishes making the roughness elements protrude through this layer and into the turbulence and adding resistance, which is what defines the transition region.The uncertainty associated with a priori calculation of wall friction and pressure drop in a pipelinemakes it necessary to have the friction or roughness tuned in a full-scale test in either way. The methods employed by Gassco are described below.b. Capacity TestWhen the pipeline is installed more accurate as-laid data with respect to length, wall layerthicknesses and burial depths are available and these data are used to update the computer simulator. Shortly after start-up a so-called capacity test is performed. Particular care is taken by all supply and delivery points to operate the pipeline very steady for a period of 1-5 days. The best period of approximately 12 hoursduration is chosen as the official test period, and assumed to represent a steady-state condition in the pipeline.Single-legFor a single-leg pipeline the hydraulic roughness µis mainly a function of the following parameters⎧=f (P in , P out , Q,T in ,T ambient , C ) Eq. 2 where P denotes the pressure, Q is the standard volumetric flow rate, T is the temperature and C is the gas composition.The averaged boundary pressures from the test period are used as boundary conditions in a steady- state simulation. The hydraulic roughness can be determined through iterative model simulations where the roughness is adjusted until the simulated flow rate equals the weighted average of the measured flow rates from the test period. The resulting hydraulic roughness is then said to be this pipeline’s hydraulic roughness. The procedure is illustrated in the figure below.Figure 2 Illustration of capacity test methodology.The other parameter that can be used to check if the model is a good representation of the physical pipeline is the simulated outlet temperature versus the measured one. A deviation can have three different causes. First is obviously the ambient temperature used in the model. If this deviates from the actual temperature at the time of the test, it will usually result in a different modeled temperature. Second are the pipeline parameters like wall data and burial depth. The modeled heat transfer and subsequently the temperature will be affected if these parameters are incorrect in the model. Last come the equations in the simulator software. If they fail to model the heat transfer between the surroundings and the gas, the joule- thompson cooling or the frictional heating effect correctly, the temperature will be affected. And an inaccurate simulated gas temperature along (parts) of the pipeline will affect the calculated hydraulic roughness. Care must therefore be taken to reduce the possible deviation between simulated and measured outlet temperature. Gassco has checked the equations in the simulator, so focus is on the two first causes when we see a temperature deviation in a capacity test.The capacity test is often performed at flow rates significantly lower than the maximum capacity, due to limited amount of gas available early in a pipeline’s lifetime. The simulator is hence used to calculate the hydraulic capacity by using maximum inlet pressure and minimum outlet pressure. This implies extrapolatingthe friction factor along the specific Colebrook-White line for this roughness in the Moody diagram to find the friction factor at maximum capacity. It hence relies on the accuracy of the Colebrook-White correlation, and will be further described in a later section.Network with several supply and delivery pointsThe method for estimating the effective roughness for a pipeline network is more complicated than for a single pipeline. Figure 3 shows a schematic example of a pipeline network which consists of a main pipeline and three branches. The tie-in points are denoted A, B and C. A compressor, K, is also represented. The main pipeline and the branches may have different physical properties like diameter, physical roughness etc.Inlet 2Inlet 3COutlet 1 Inlet 1 KA BOutlet2Figure 3 Example of a pipeline network.As shown in Figure, the network can be considered as a connection of the following single-leg pipelines:Table 1: Network elements in the example network of Figure 3.If measurements are available at the tie-in points A and B as well as upstream and downstream the compressor, an effective roughness can be determined for each “si ngle-l eg”that constitutes the network. The methodology is then similar to the one described above.When there are no pressure instruments at the tie-in points, the single-leg tuning approach is impossible. The following parameters are then necessary in order to determine the effective roughness in the different parts of the network:Pressure at the network inlets: P in,i , where i = inlet numbe r 1,2,…,n inPressure at the outlets: P out,j where j = outlet numbe r 1,2,…,n outFlow rate at the inlets: Q in,iFlow rate at the outlets: Q out,jTemperature at the inlets: T in,iAmbient temperature along the pipeline: T ambient(x,y) Composition at the inlets: C in,iIn other words,⎧=f (Qin ,i , Qout , j, Pin ,i, Pout , j, Tin ,i, Tambient, Cin ,i)Eq. 3The boundary conditions that are recommended to use in the model simulations when the effective roughness is adjusted are shown in Table 2.Table 2: Boundary conditions to use in the simulations.To achieve a steady state solution, the model needs either pressure or flow at each inlet and outlet, where the pressure has to be provided for at least one inlet/outlet. The other pressure and f low measurements are redundant. The boundary conditions selected in Table 2 represent what is usually chosen in a capacity study. Other boundary conditions would have worked equally well. Each redundant measurement can be used to tune one parameter, usually one effective roughness.To match the test data measurements from the capacity test, it is necessary to perform iterative simulations to find the matching simulation parameters shown in Table 3.Table 3: Simulation output parameters.The flow at the last outlet is determined by the flow at the other inlets and outlets, keeping in mind that at steady-state the total inlet flow must equal the total outlet flow.Lack of knowledge on the real system (burial depth, ambient temperature, material etc.) might result in poor outlet temperature predictions. Nevertheless, the simulated outlet temperature must be checked against specified pipeline temperatures to ensure that the simulated gas transport scenarios give acceptable results.For pipelines without compressors, the effective roughness of the leg considered to be the main pipeline in the network is found when the simulated and measured pressures at the main pipeline inlet are the same. This leg should be tuned before starting with the branches. In Figure 3, the main pipeline will be the pipeline running from Inlet 1 to Outlet 1.When the effective roughness is determined for the main pipeline, the simulation also gives the pressures at the tie-in points. Possible deviations between the simulated and the real tie-in point pressures (which are not measured) will obviously not be detected.To match the test data measurements at the other branches, it is necessary to perform iterative simulations for each branch to match the simulated and measured inlet pressures.Two methods of matching the pressure measurements at the branches are given in prioritized order here:1. Tune separate effective roughness for each branch connected to the main pipeline.2. Use a chosen effective roughness for each branch and tune a flow resistance element at theend of each branch. The modelled resistance coefficient must be tuned to match the desiredpressure drop.For both alternatives an iteration process is necessary to match the measurements. In case of relatively short branches with low flow rates, the adoption of the second approach may become necessary since very large changes in roughness are needed to achieve the desired flow resistance in the branch pipeline at low flow rates.Often the most important aim of a capacity test is to estimate the roughness of the main pipeline, and subsequently find the capacity of the main pipeline, i.e., the output capacity.Steady-state flow weighingIn a steady-state simulation, the sum of flow into the network needs to equal the sum of the flow out of the network. This is not necessarily the case for the real pipeline during the capacity test, either due to small remaining transients or due to metering errors. The flow rate that shall be obtained in the steady-state simulation is calculated by weighing the different metered flow rates. For a single-leg pipeline this means flow rate is calculated by:Qmean =w ⊕Qin+ (1 w) ⊕QoutEq. 4where the weight w is calculated based on the flow m eters’ uncertainties to minimize the uncertainty in Q m ean. It can be shown that this is obtained by selecting:u 2 w =outu 2 +u 2Eq. 5in outwhere u denotes the uncertainty.For a pipeline network with several supply points and/or several delivery points the calculation is similar, though a bit more complex.c. Operational DataThe two major drawbacks with the capacity test approach described above are that it relies on one testing point and that it often is performed at a low flow rate and therefore relies on extrapolation of the friction factor along a Colebrook-White curve. The approach described here adds useful knowledge about the pipeline and its capacity in addition to that obtained from a capacity test.Uncertainty analysis quantifies the capacity calculation uncertainty from a capacity test. This uncertainty comprises both systematic error and random error. The categorization of systematic and random error is often difficult, and one usually only obtain a vague idea of their relative contribution to the total uncertainty figure. It is well known that the random error can be minimized and eventually be made neglible if more testing points are averaged to find a pipeline’s hydraulic roughness. Gassco’s capacity calculation methodology has therefore been extended to average a set of steady-state period data points to calculate the hydraulic roughness. And instead of organizing an elaborate capacity test to obtain every single data point, a data base of historical operational data for the pipeline is used. This data base contains logged data from all pressure and temperature transmitters, gas chromatographs, flow meters and other instruments connected to the pipeline. All data are usually logged with intervals of approximately 1 minute. This data base is searched to find good steady-state operational periods which have occurred arbitrarily in the daily operation of the pipeline. A certain set of criteria has been developed for the periods to qualify as a steady- state period. Each of these periods is then treated exactly like a capacity test period, and have a roughness tuned.The Colebrook-White friction factor correlation has been accepted as an industry standard for decades, even though many research groups have proved it to be wrong in their specific tests. The reason it is still well accepted is that none has succeeded in explaining why the Colebrook-White correlation fit or does not fit to their experiments and how different wall surface structures lead to different transition regions (see e.g. results from American Gas Association in the 1960s in Uhl et al. (1965) and more recent experiments in Superpipe at Princeton University by Shockling et al. (2006)). The uncertainty associated with extrapolating along a Colebrook-White curve can be almost entirely removed by selecting steady-state periods with high flow rates. Therefore only steady-state periods with a flow rate of more than approximately 80% of the pipeline’s expected capacity are used when averaging the hydraulic roughness. Most of the Gassco operated pipelines are in the early phase of the transition region from smooth turbulent flow to fully rough turbulent flow, where Colebrook-White is mostly questioned. Evaluating only steady-state periods with high flow rates makes this uncertainty neglible.Figure 4 shows steady-state periods that have been collected and simulated for one specific export pipeline, denoted pipeline A. We see that all the data points have a roughness in the range of 1.5 to 3.0 micron. The average roughness of the data points with highest Reynolds number seems to be approximately 2.2 micron. Imagine the encircled data point which have a roughness close to 3 micron was a capacity-test data point. Extrapolating along the corresponding Colebrook-White curve would have yielded a too large friction factor (marked with red unfilled circle) at maximum capacity and thus predicting a too low capacity. The red filled circle illustrates the recommended friction factor based on averaging steady-state operational data periods. Vice verca would a low capacity test result over predict capacity and result in over booking.This illustrates the reduced uncertainty that is gained by averaging a set of high-flow data points, even though this example shows data points that do not deviate a lot from the Colebrook-White trends.One can also obtain an experimental friction factor curve for the pipeline in question by fitting a line to the plotted friction factors from the steady-state periods. For a limited range of Reynolds number, e.g. between 10 and 40·106, which is the operating range for pipeline A and most others Gassco operated pipelines, it is usually sufficient to use a straight line. Regression analysis can be used to find the line. For pipeline A such a line would be quite parallel to the Colebrook-White lines. If the steady-state periods do not cover flow rates close to the maximum flow rate, even extrapolation along a fitted pipeline specific friction factor curve would imply uncertainty, since one cannot predict the behaviour of the friction factor for larger flow rates.The physical roughness for pipeline 1 has not been measured. But based on measurements on other pipelines which have been manufactured according to the same specifications, it is believed that the root mean square roughness is around 2-3 micron. This is about the same value as the hydraulic roughness estimated to be 2.2 micron in this case. This unexpected low hydraulic roughness may indicate that the friction factor characteristics will deviate from the Colebrook-White lines for larger Reynolds numbers. This is discussed in more detail in Langelandsvik (2008).Figure 4 Moody-diagram where the lines are given by the Colebrook-white correlation for different relative roughnesses. Data points from simulation of steady-state periods for the export pipeline A.In a capacity test, the instruments are usually calibrated beforehand, and special effort is taken by the field and plant operators to ensure steady-state conditions in the pipeline during the test. In operational steady-state periods none of these keys to success are present. But despite this, the benefits of the new approach more than outweigh these drawbacks.The increased accuracy and reduced margins have lead to an increase in calculated transport capacity of in total 4.6 MSm3/d for five export pipelines. It should be noted that one pipeline contributes 2.7 MSm3/d to this number. The basis for this pipeline’s capacity was design capacity and not capacity test capacity as for the other pipelines, ie. the capacity was even more conservative before the application of the described methodology.Requirements for steady-state periodsIt is important that the operational period is a good steady-state representation of the pipeline for the given flow rate. The steady-state periods are therefore found in a two-step procedure. The database that contains the operational data provides a powerful search tool, which can suggest a set of steady-stateperiods based on criteria set by the user. But every single period is also checked visually by Gassco’s。