HIoPE 4. Part Load Operation of Steam Turbines Fully Open #1 #1 Partially Open #2 Closed Closed Stop V/V (1.5% p) Steam Turbine Steam Flow #2 #3 #4 Control V/V (1.5% p @ VWO) 4. Part Load Operation Nozzle Bucket First stage shell pressure 1 / 81 HIoPE 1 Basics for the Control of Steam Flow 2 Valves 11 3 Full Throttling 29 4 Partial Arc Admission 37 5 Sliding Pressure Operation 57 6 Hybrid Operation 64 7 Startup System of Steam Power Plants 73 8 Load Changes 76 Steam Turbine 4. Part Load Operation 2 2 / 81 Steam Turbine Control HIoPE hin hout Pm Change power by changing steam flow or steam inlet enthalpy (h ). rate (m) in Steam Turbine 4. Part Load Operation 3 / 81 Heat Balance - Design Condition HIoPE Steam Turbine 4. Part Load Operation 4 / 81 Heat Balance – Part Load Condition HIoPE Steam Turbine 4. Part Load Operation 5 / 81 A Basic Concept for Part Load Operation MS C/V R HP Turbine Pressure HIoPE LP Turbine 100% Power 75% Power 50% Power 25% Power Steam Turbine 4. Part Load Operation 6 / 81 HIoPE Output and Efficiency at Part Load Output and Efficiency at Part Load Example: 460 MW, supercritical power plant 500 440 Efficiency Power Power, MW 410 380 350 320 290 260 230 200 45 48.3 47.6 46.9 46.2 45.5 44.8 Efficiency, % 470 49.0 44.1 43.4 42.7 42.0 50 55 60 65 70 75 80 85 90 95 100 Load, % Steam Turbine 4. Part Load Operation 7 / 81 HIoPE Throttling Process Nozzle Row p0 h p1 p1’ T0 100% Bucket Row U p0: Inlet pressure p1: Throttle pressure 100% load 75% load Design-flow expansion line 50% load [ Velocity Diagram at Various Loads ] A turbine has different expansion lines as the load is decreased. But the part load expansion lines are generally parallel to the full load expansion line. This means that the internal efficiency under part load conditions is very close to that under full load conditions. That is, design efficiency of the turbine blades is maintained during part load operations by using the control valve. However, the cycle efficiency is reduced under part load conditions. Steam Turbine 1′ 4. Part Load Operation Partial-flow expansion line Available Energy U 25% 1 25% load Expansion lines are essentially parallel pc 2′ 2 [ Effect of Throttling on Non-Reheat Steam Turbine Expansion Line ] s 8 / 81 Control of Steam Flow in HP Turbines HIoPE 4 Methods Used in Steam Flow Control 1) Full throttling (= Single admission ) • Constant pressure mode • Throttling by pressure reducing valves • All control valves are activated at the same time • This is the simplest way to control the power, but this gives a large throttle (pressure) loss because of using the pressure throttle valves 2) Partial arc admission (Throttling by a control stage) • Constant pressure mode • Divided the first stage nozzle arc into several segments having its own control valve • Lower throttle loss • The control valves are activated in a sequential mode 3) Sliding (or variable) pressure operation • Variable pressure mode • Controlling throttle flow by varying boiler pressure 4) Hybrid operation • A combination of partial arc admission and sliding pressure operation Steam Turbine 4. Part Load Operation 9 / 81 HIoPE Exhaust Loss during Part Load m 1 0.01Y 3600 AAN = saturated dry specific volume AAN = annulus area Y = percent of moisture at ELEP [Exercise 4.1] 부분부하운전 시 배기손실 크기 변 화를 비교하시오. 아울러 그 결과를 heat balance에서 확인하시오. Steam Turbine 139 93 47 0 Exhaust Loss, Btu/lb VAN = annulus velocity m = steam mass flow rate 80 Thermodynamic Optimum Exhaust Loss, kJ/kg VAN 186 60 Total Exhaust Loss Axial Leaving Loss Economic Optimum 40 VAN proportional to: rating 1/exhaust pressure 1/exhaust area 20 0 0 1000 500 1500 Annulus Velocity (VAN), ft/s 2000 0 305 152 457 Annulus Velocity (VAN), m/s 610 4. Part Load Operation 10 / 81 HIoPE 1 Basics for the Control of Steam Flow 2 Valves 3 Full Throttling 4 Partial Arc Admission 5 Sliding Pressure Operation 6 Hybrid Operation 7 Startup System of Steam Power Plants 8 Load Changes Steam Turbine 4. Part Load Operation 11 / 81 HIoPE Valves Main Steam Steam Generator Crossover Stop V/V Control V/V Front Standard Cold Reheat HP IP LP Gen Exciter Ventilation V/V Reheat Stop and Intercept V/V Reheater Condenser Hot Reheat [ A Typical Power Plant Steam Flow Diagram ] Steam Turbine 4. Part Load Operation 12 / 81 Main Steam Valves HIoPE Siemens Steam Turbine 4. Part Load Operation 13 / 81 HIoPE Typical Individual Stop and Control Valve Assembly GE Generals Valve 개수(표준화력 500MW 기준) - Stop v/v : 2 - Control v/v : 4 Stop valve = on-off valve Control valve = throttle valve라고도 불리며, load 연동 MSV Actuator Typical closing time during emergency - Stop v/v : 0.09초 10% - Control v/v : 0.11초 10% MCV Actuator Steam Turbine 4. Part Load Operation 14 / 81 Main Stop Valves High-pressure steam is admitted to the main turbine through two parallel main stop valves. The primary function of the main stop valves is to quickly shut off main steam flow to the turbine under emergency conditions. [1/4] GE Steam Inlet The stop valves also provide a second line of defense against turbine overspeed in the event the control valves fail. The main stop valve bypass valves are also used for full arc operation during startup and shutdown of the turbine. The main stop valves are located in the main steam piping between the boiler and the turbine control valve chest. The outlet of each stop valve is welded directly to the valve chest. The main steam stop valves are operated and controlled by the turbines Electro Hydraulic Control System in concert with the units DCS control system. HIoPE Valve Seat Valve Disc Pressure Seal Head Steam Outlet Valve Stem Actuator The bypass valve disk is fastened to the end of the stem by special coarse threads strong enough to withstand full closing force, yet designed to permit freedom of disk movement relative to the stem so that the valve will seat. Steam Turbine Steam Strainer 4. Part Load Operation Closing Spring [ Main Stop Valve ] 15 / 81 Main Stop Valves HIoPE [2/4] The steam from the steam generator flows to the main steam stop or throttle valves. The primary function of the stop valves is to provide backup protection for the steam turbine during turbine generator trips in the event the main steam control valves do not close. The energy contained in the main steam can cause the turbine to reach destructive overspeed quickly when generator loose the load. The main stop valves close from full open to full closed in 0.15 to 0.5 s. The main stop valves are closed on unit normal shutdown after the control valves have closed. A secondary function of the main stop valves is to provide steam throttling control during startup. The main stop valves typically have internal bypass valves that allow throttling control of the steam from initial turbine roll to loads of 15% to 25%. During this startup time, the main steam control valves are wide open and the bypass valves are used to control the steam flow. Some recent and current designs do not have these bypass valves. Initial turbine speed runup is controlled by the main stop valves. Steam Turbine 4. Part Load Operation 16 / 81 Main Stop Valves HIoPE [3/4] Bypass Valve GE The bypass valve is held in the valve disk by a bolted cap. Holes are located in the cap for steam entrance, and holes in the valve disk pass the steam when the bypass valve is utilized. When the stop valve is opened the bypass valve opens first as the valve stem moves in the open direction. When the bypass valve is fully open it contacts a bushing on the stop valve and pulls it open. When the stop valve is fully open, a bushing seats on the inner end of the valve stem bushing and prevents steam leakage along the valve stem. Bypass Valve Disc Main Stop Valve Disc Main Stop Valve Disc Seating Surface Bypass Valve Ports (8 ea) Main Stop Valve Stem [ Stop Valve Bypass ] Each stop valve has two steam leakoff points where the stop valve stem passes through the stop valve casing. The first leakoff point located closest to the stop valve is referred to as the high-pressure leakoff and is routed to the steam seal header. During startup or low loads steam is supplied to this leakoff to assure a seal. After the turbine is loaded, steam is fed through this line from the stop valve stem into the steam seal header. The second leakoff point is referred to as the low-pressure leakoff and is routed to the gland steam condenser. Steam Turbine 4. Part Load Operation 17 / 81 Main Stop Valves HIoPE [4/4] Bypass Valve Steam Turbine 4. Part Load Operation 18 / 81 Main Steam Control Valves The steam from the stop valves flows to the main steam control or governor valves. Steam from No.1 C/V HIoPE [1/3] Snout Pipes Steam from No.3 C/V Snout Pipe Seal Rings The primary function of control valves is to regulate the steam flow to the turbine and thus control the power output of the steam turbine generator. HP Inner Shell The control valves also serve as the primary shutoff the steam to the turbine on unit normal shutdowns and trips. 180 Degree Nozzle Box HP Inner Shell Actuator HP Inner Shell Upper Lower HP Inner Shell MSV HP Inner Shell 180 Degree Nozzle Box MCV Siemens Steam Turbine Actuator HP Inner Shell Snout Pipe Seal Rings MHI Steam from No.2 C/V 4. Part Load Operation Snout Pipes Steam from No.4 C/V 19 / 81 Main Steam Control Valves HIoPE [2/3] GE The control valves regulate the steam flow to the turbine to control the main turbine speed and/or load. The four control valves are mounted in line on a common external valve chest. Steam is supplied to the external valve chest through the main stop valves. The valve chest is separated from the turbine, and individual steam leads from the valve chest are provided from each control valve to the inlet of the HP turbine. Each control valve is operated by a hydraulic power actuator which positions the control valves in response to signals from the Electro Hydraulic Control System. During startup, the control valves are wide open (full arc), and the stop valves’ internal bypass valves control the steam flow to the turbine. Under these conditions, steam is admitted through all four steam leads around the entire periphery of the HP turbine inlet. The purpose of this full arc admission is to reduce thermal stresses caused by unequal steam flow through the nozzle sections. During full arc admission, throttling of the steam occurs at the stop valve bypass valves only, and there is uniform steam flow into the HP turbine. This also results in lower steam velocities at the turbine inlet. Because of the lower steam velocities the temperatures cannot change as rapidly. Full arc admission is used until the high transfer point is reached, at which time transfer to partial arc will occur. Steam Turbine 4. Part Load Operation Closing Spring Balance Chamber Valve Seat Steam Valve Chest Disc [ Main Steam Control Valve ] 20 / 81 Main Steam Control Valves HIoPE [3/3] GE During normal operation, the main stop valves are wide open and the control valves control steam flow to the turbine. The control valves operate sequentially to control steam flow to the turbine and the unit load. All four control valves are never open the same amount for any given load up to full load with wide-open control valves. This is referred to as partial arc admission. Transfer to partial arc admission is normally automatically performed by the low transfer and high transfer micro- switches but may also be initiated by the operator when the OK TO TRANSFER light comes on. The control valves are throttled until they have control of steam flow and the stop valves then automatically run full open. Number l and 2 control valves are balanced type, with internal pilot valves. Number 3 and 4 control valves are unbalanced single disk type. The balanced type valves are equipped with an internal pilot valve connected to the valve stem. When opening, the pilot valve is opened first to equalize the pressure across the main valve disk. Further opening of the stem opens the main disk. The disk of the unbalanced type valve is directly connected to the stem. Each control valve is provided with two steam leakoff points where the control valve stem passes through the external steam chest wall. The first leakoff point located closest to the external steam chest is referred to as the high-pressure leakoff and is routed to the hot reheat steam line. The second leakoff point is referred to as the low-pressure leakoff and is routed to the steam seal header. Steam Turbine 4. Part Load Operation 21 / 81 Reheat Stop and Intercept Valves HIoPE [1/4] [ Combined Reheat Stop and Intercept Valve, GE ] Steam Turbine 4. Part Load Operation 22 / 81 Reheat Stop and Intercept Valves Two combined reheat stop and intercept valves are provided, one in each hot reheat line supplying reheat steam to the IP turbine. As the name implies, the combined reheat intercept valve is actually two valves, the intercept valve (IV) and the reheat stop valve (RSV), incorporated in one valve casing. Although they utilize a common casing, these valves have separate operating mechanisms and controls. HIoPE [2/4] GE Steam Strainer Balance Chamber Steam In Intercept Disc Intercept Actuator Reheat Stop Disc The function of the intercept valves and reheat stop valves is to protect the turbine against overspeed from stored steam in the reheater. Steam Out Closing Spring [ Reheat Stop and Intercept Valves (SKODA) ] Steam Turbine 4. Part Load Operation Reheat Stop Actuator 23 / 81 Reheat Stop and Intercept Valves HIoPE [3/4] The intercept valve disk is located above the reheat stop valve disk, with its stem extending through the upper head. The reheat stop valve stem extends downward through the below-seat portion of the casing. Both valves share a common seat; however, the intercept valve is designed to travel through its full stroke regardless of the reheat stop valve position, while the intercept valve must be in the “closed” position for the reheat stop valve to open. During normal operation of the turbine-generator unit, the intercept valves are fully open. The purpose of the intercept valve is to shut off steam flow from the reheater, which, because of its large storage capacity, could possibly drive the unit to overspeed upon loss of generator load. The intercept valve is capable of reopening against maximum reheat pressure and of controlling turbine speed during reheater blowdown following a load rejection. The primary function of the reheat stop valves is to provide a second line of defense (backup protection) against the energy storage of the reheater in the event of failure of the intercept valves or the normal control devices. However, note that the reheat stop valves also close upon a routine shutdown, or by operation of certain boiler and electrical trips whenever the main stop valves are closed. The reheat stop valve power actuators are sized so that the reheat stop valves are capable of reopening against a steam pressure differential of approximately 15 percent of maximum reheat pressure. Steam Turbine 4. Part Load Operation 24 / 81 Reheat Stop and Intercept Valves HIoPE [4/4] The function of the reheat stop and intercept valves is similar to the main steam stop and control valves. The reheat stop valve offer backup protection for the steam turbine in the event of a unit trip and failure of the intercept valves to close. The intercept valves control unit speed during shutdowns and on large load changes, and protect against destructive overspeeds on unit trips. The need for these valves is a result of the large amount of energy available in the steam present in the HP turbine, the hot and cold reheat lines, and the reheater. On large load changes, the main steam control valves start to close to control speed, however, energy in the steam present after the main steam control valves may be sufficient to cause the unit to overspeed. The steam after the main steam control valves could expand through the IP and LP turbines to the condenser, supplying more power output than is required, causing the turbine to overspeed. The intercept valves are used to throttle the steam flow to the IP turbine in this situation to control turbine speed. During unit shutdowns, a similar situation could occur, and the intercept valves are used to control speed under these conditions as for the trip condition. During unit trips, both the reheat stop and the intercept valves close, preventing the reheat-associated steam from entering the IP turbine. During normal unit operation, the reheat stop and intercept valves are wide open, and load control is performed by the main steam valves only. Steam Turbine 4. Part Load Operation 25 / 81 Ventilation Valve During unit trips, the closure of the main stop and control valves and of the reheat stop and intercept valves traps steam in the HP turbine. During the turbine overspeed and subsequent coastdown, the HP turbine blades are subject to windage losses from rotating in this trapped steam. The windage losses cause the blades to be heated. This heating, in combination with the overspeed stress, can damage the HP turbine blades. To prevent this, a ventilation valve is provided to bleed the trapped steam to the condenser. On a unit trip, the valve is automatically opened. The bleeding action causes the trapped steam to flow through the HP turbine, maintaining the HP turbine temperature within acceptable limits by preventing heat buildup from the windage losses. Steam Turbine 4. Part Load Operation HIoPE [ Ventilation Valve, CCI ] 26 / 81 HIoPE Ventilation Valve Main Steam Crossover Stop V/V HP bypass station Control V/V HP IP LP Gen Ventilation Cold Reheat V/V Reheater Reheat Stop and Intercept V/V Condenser Hot Reheat HRH bypass station (HRH: Hot Reheat) [ Turbine Bypass Diagram ] Steam Turbine 4. Part Load Operation 27 / 81 HIoPE Pressure Drop in Valves The efficiency of a steam turbine is governed by the efficiency of the individual stages and the pressure drop through valves, cross-over pipes, and exhaust hoods. Throttle steam from the boiler first pass through the stop valve and then control valves. The stop valve pressure drop is 2% and the control valves in the wide open position also have a pressure drop of 2%. Therefore, total pressure drop occurred in the valves is 4%. The total loss in overall heat rate of these pressure drops is about 0.4%. Throttle to bowl pressure drop (%) 8 6 4 2 0.2 Steam Turbine 0.4 0.6 Equivalent throttle flow ratio 4. Part Load Operation 0.8 1.0 28 / 81 HIoPE 1 Basics for the Control of Steam Flow 2 Valves 3 Full Throttling 4 Partial Arc Admission 5 Sliding Pressure Operation 6 Hybrid Operation 7 Startup System of Steam Power Plants 8 Load Changes Steam Turbine 4. Part Load Operation 29 / 81 HIoPE Concept of Full Throttling All control valves have a same position in full throttling operation #1 #1 Steam Flow #2 #3 #2 #4 Stop V/V (1.5% p) Control V/V (1.5% p @ VWO) Nozzle Bucket First stage shell pressure Steam Turbine 4. Part Load Operation 30 / 81 HIoPE Generals for Full Throttling p0 h 0 p1 1 p2 2 Initial (Main Steam) Throttling Ahead of First Stage Nozzles (Bowl Pressure) s 0 Steam condition entering the control valves 1 Steam condition entering the first stage 2 Steam condition entering the second stage After First Stage (Shell Pressure) Load Steam Turbine 4. Part Load Operation 31 / 81 HIoPE Generals for Full Throttling Full throttling is the simultaneous operation of all main steam control valves at the same time. The main steam supplied during part load operation has a same pressure with that supplied during full load operation. Therefore, throttling loss is occurred whenever the plant is operated with part load. The steam turbine output increases as the valves are opened and full load is reached when the valves are wide open. During the part load operation, full throttling is the least efficient of all control modes because the available energy in the expansion process is reduced greatly by the throttling process. For this reason, the HP turbine with full throttling has a greater entropy increase than that with partial arc admission. This method is also called as ‘full arc admission’, ‘single admission’, or ‘throttling control’ because of the steam admission to all portions of the control stage. During the startup of some units, the control valves are wide open. Steam is initially admitted to the turbine by throttling the steam flow by using the bypass valves internal to the main steam stop valves. This flow control method is used up to 15% to 25% load. Above this load, the main steam control valves are used to control the steam flow and the main steam stop valves are wide open. The complex control stage design is not required. Steam Turbine 4. Part Load Operation 32 / 81 HIoPE Advantages of Full Throttling For 50% reaction turbines with throttling control, the pressure ratio across the first stage is about 1.13 at all loads. This value of pressure ratio is too low to produce sonic velocity. Thus, an advantage of throttling control is no solid particle erosion in the first stage. The solid particle erosion would be in the control valves, which are less expensive to repair than the first stage. Another advantage of throttling control is lower stress levels due to low first stage velocities and the absence of inactive arcs. Steam Turbine 4. Part Load Operation 33 / 81 HIoPE Stage pressure is roughly proportional to the mass flow rate to the following stage, the throttle flow minus leakages, and all extractions from the preceding stages and stage in question, plus any steam returned to the turbine ahead of this stage. Therefore, mathematical relationship is pi pi ,d pi pi ,d m i m i ,d m i m i ,d = steam pressure at the nozzle of stage i = design steam pressure at the nozzle of stage i = steam mass flow rate to the stage i = steam mass flow rate to the stage i Absolute steam pressure Stage Pressure during Part Load m1 m0 [ Variation of stage-shell pressure ] Steam Turbine 4. Part Load Operation 34 / 81 HIoPE Stage Pressure during Part Load [Exercise 4.1] 아래 그림은 각각 설계조건과 부분부하운전조건에서 LP터빈 첫 번째 추기 지점에서의 조건이다. 부분부 하운전조건에서 추기압력을 계산하고 검토하시오. 3566457 lb/hr 2701136 lb/hr LP Turbine LP Turbine 131561 lb/hr 60.6 psia 105869 lb/hr 46.21 psia [ Full load ] Steam Turbine [ Part load ] 4. Part Load Operation 35 / 81 Stage Pressure during Part Load HIoPE [Solution] Design conditions are pd = 60.6 psia md = 3,566,547131,561 = 3,434,986 lb/hr md means the steam mass flow rate to the next stage. Under the part load conditions this mass flow rate becomes m = 2,701,136105,869 = 2,595,267 lb/hr Extraction pressure can be calculated pi pi ,d m i m i ,d p = 606.6 2,595,267/ 3,434,986 = 45.8 psia This calculated pressure is very close to extraction pressure shown in heat balance, 46.21 psia. Steam Turbine 4. Part Load Operation 36 / 81 HIoPE 1 Basics for the Control of Steam Flow 2 Valves 3 Full Throttling 4 Partial Arc Admission 5 Sliding Pressure Operation 6 Hybrid Operation 7 Startup System of Steam Power Plants 8 Load Changes Steam Turbine 4. Part Load Operation 37 / 81 Concept of Partial Arc Admission Fully Open #1 #1 Partially Open #2 Closed Closed Stop V/V (1.5% p) Steam Turbine HIoPE Steam Flow #2 #3 #4 Control V/V (1.5% p @ VWO) Nozzle Bucket First stage shell pressure 4. Part Load Operation 38 / 81 HIoPE Nozzle Box #1 #3 42 43 Turbine C.W. Number of nozzle 42 43 #4 #2 [ 500 MW (3,500 psig, 1,000F) ] Steam Turbine 4. Part Load Operation 39 / 81 Concept of Partial Arc Admission Full Arc Partial Arc (Single Admission) #3 v/v #1 v/v HIoPE #3 v/v #1 v/v Inactive arc #4 v/v #2 v/v #4 v/v #2 v/v The dimensions of turbine blades and flow channels are primarily a function of the volumetric flow rates passing through the machine Steam Turbine 4. Part Load Operation 40 / 81 HIoPE Pressure Variation Initial (Main steam pressure) Throttling Ahead of First Stage Nozzles (Bowl Pressure) Initial (Main steam pressure) Ahead of Nozzle Box #2 Ahead of Nozzle Box #3 Ahead of Nozzle Box #1 After First Stage (Shell Pressure) After First Stage Load Load Full Arc Steam Turbine Ahead of Nozzle Box #4 Partial Arc 4. Part Load Operation 41 / 81 HIoPE Generals for Partial Arc Admission The inlet annulus area of the first stage nozzle is divided into several segments (vary from 4 to 6 to 8) along tangential direction. Typically, the first stage divides the annulus into four to eight segments (arcs) having different angles depending on the guarantee points. Partial arc admission (PAA) is the sequential operation of the main steam control valves. PAA varies the output of the steam turbine by increasing or decreasing the arc of admission of steam flow to the turbine control (first) stage. (The first admission stage in steam turbines often referred to as governing or control stage) Each control valve feeds a separate segment of the control stage, and the amount of arc in use is determined by the number of valves open. The valves are opened in a particular order that is determined by the allowable stresses on the control stage. PAA is also called as governing control. Rated throttle conditions are used throughout the load range to the extent allowed by the steam generator. - to be continued Steam Turbine 4. Part Load Operation 42 / 81 HIoPE Generals for Partial Arc Admission The first stage is of impulse design because it gives only a small circumferential pressure gradient after nozzle so the spreading of the jets circumferentially may be attenuated. For the 50% reaction turbine, the first stage is the same as for the impulse turbine. Partial arc admission can cause high impulse loads on the nozzle and buckets, possibly leading to high cycle fatigue failures. If the partial arc admission is applied for small turbine, the blade height can be increased in order to increase stage efficiency. Normally, entropy production becomes higher for small turbines than large machines. This is because of higher endwall losses for shorter blades, and the substantial part of the endwall losses caused by the secondary flow formed in both nozzle and bucket row. One way to prevent this is to increase the dimension of the turbine blades and adopt partial admission. Even though extra losses due to the employment of partial admission is introduced, it might be beneficial due to the decreased endwall losses. Steam Turbine 4. Part Load Operation 43 / 81 HIoPE Secondary Vortices in Short and Long Blades Tip Tip Vortex Vortex Vortex Hub Hub Bucket efficiency (a) Short Blades Steam Turbine High Efficiency Radial height Radial height Vortex Bucket efficiency (b) Long Blades 4. Part Load Operation 44 / 81 HIoPE Advantages of Partial Arc Admission PAA is more efficient than full throttling because the throttling process loss is minimized by reducing the number of control valves throttling at any one time. #3 v/v If the PAA is employed, the inlet flow rate can be controlled and a high inlet pressure and temperature can be maintained as high as for the fully admitted arcs, even for low flow rates. Considerably less pressure is lost due to throttling by PAA so that more pressure is available to produce power in the first stage, with a corresponding improvement in overall heat rate. Steam Turbine 4. Part Load Operation #1 v/v Inactive arc #4 v/v #2 v/v 45 / 81 HIoPE Comparison of Throttling Methods h h p0 0 p0 p1 1 p1 1 0 p2 p2 2 2c 2b 2a s 0 1 2 s 01 Flow in the control valves 1 2b Steam condition entering the first stage Flow across the first stage in an arc segment 0 2a Steam condition entering the second stage Flow across the first stage in the fully opened segments 2c Steam condition into the second stage Steam condition entering the control valves (a) Full throttling Steam Turbine (b) Partial arc admission 4. Part Load Operation 46 / 81 HIoPE Turbine Section Efficiency 100 90 80 Efficiency [%] 70 60 50 40 IP Turbine 30 LP Turbine 20 HP 2nd Stage to Cold Reheat 10 HP 1st Stage 0 0 0.2 0.4 0.6 Throttle Flow Ratio Steam Turbine 4. Part Load Operation 0.8 1.0 (VWO) 47 / 81 HIoPE HP Turbine Efficiency 90 85 HP Turbine Efficiency [%] Partial Arc Admission 80 75 Full Throttling 70 65 60 55 0 0.2 0.4 0.6 Throttle Flow Ratio Steam Turbine 4. Part Load Operation 0.8 1.0 (VWO) 48 / 81 HIoPE Heat Rate Actual turbine cycle performance is shown on a valve loop basis heat rate curve. This curve reflects the steam throttling effect as the steam passes through a partially closed steam admission. The throttling pressure drop reduces the available energy of the steam as the throttled admission steam expands across the control stage. Valve Loop Basis (True Curve) Heat rate Mean of Valve Loop Basis Valve Point Basis (Locus-of-valve best points) 20 An alternative method of representing turbine heat rate impact due to turbine valve losses at part load is by a mean of valve loop method. This method is an approximation of the heat rate impact illustrated on the valve loop basis curve and represents a mean of the turbine heat rate and passes through the valve loop curve. Turbine heat balance developed on the basis of this assumption are considered to be on a locus-of-valve best points basis. This heat balances describe heat rates assuming an infinite number of small valves having a 3% pressure drop. Steam Turbine 0 4. Part Load Operation 60 40 Generator output 80 100 49 / 81 HIoPE Partial Admission The control stage should be designed with impulse turbine in order to avoid circumferential flow of steam after passing through the first stage nozzle Steam Turbine 4. Part Load Operation 50 / 81 Efficiency at Partial Arc Admission HIoPE 80 HP Turbine Efficiency [%] A B C D 70 A B E C F = 85/170 60 D E 50 0.3 0.4 0.5 0.6 Velocity Ratio [U/C] Steam Turbine 4. Part Load Operation 51 / 81 HIoPE Partial Admission Losses Stagnation Region Stagnation Region Tangential Ventilation Loss Steam Turbine Sector-End Loss 4. Part Load Operation Axial 52 / 81 Unsteady Forces HIoPE t=0 The large unsteady forces acting on the buckets in tangential direction are produced when the buckets enter and leave the admission jets t=1 Tref Tangential Blade Force under Partial Arc Admission over Time 0.30 t=2 Tref Force Acting on a Blade in Tangential Direction 0.25 0.20 t=6 Tref 0.15 0.10 0.05 t=7 Tref 0.00 - 0.05 t=8 Tref - 0.10 0 2 4 6 8 10 Time Steam Turbine 4. Part Load Operation 53 / 81 HIoPE Partial Arc vs. Single Admission Partial Arc Admission Single Admission • It can employ longer blades which give better aerodynamic turbine efficiency. • It gives smaller entropy increase during part load operation. • Therefore, the HP turbine efficiency is better during part load operation. • The better part load performance for partial admission must be balanced against the increased potential for high cycle thermal fatigue in the first stage. • As load is decreased on the single admission unit, an increasing amount of throttling takes place in the control valves. • It gives better efficiency than partial arc admission at VWO because there is no inactive arc. • Many of the large nuclear units are designed full throttling. • The first stage is called as governing stage or control stage. Steam Turbine 4. Part Load Operation 54 / 81 HIoPE Comparison of HP Turbine Performance The HP turbine efficiency is better during part load operation with sequential valve operation than throttling condition. However, at valve wide open, the throttling controlled turbine gives better performance. This is because single admission has no inactive arc. Valve-loops are the result of changes in HP turbine efficiency as the valve goes from closed to fully open. Steam Turbine 4. Part Load Operation 55 / 81 HIoPE Effect of Admission Modes 2400 psig/1000/1000F +4 Single Admission (Full Throttling) 4valves, first 3 valves open together +3 2 Admissions 4valves, first 2 valves open together +2 3 Admissions +1 4 Admissions 0 1st 1 2nd 3rd v/v pt. Base Line is Locus of “Valve Best Point” (Partial Arc Admission) 2 20 30 40 50 60 70 VWO Valve Loop 80 90 100 % VWO Load Steam Turbine 4. Part Load Operation 56 / 81 HIoPE 1 Basics for the Control of Steam Flow 2 Valves 3 Full Throttling 4 Partial Arc Admission 5 Sliding Pressure Operation 6 Hybrid Operation 7 Startup System of Steam Power Plants 8 Load Changes Steam Turbine 4. Part Load Operation 57 / 81 Sliding Pressure Operation HIoPE Comparison with Full Throttling Main Steam Main Steam Ahead of First Stage Nozzles Ahead of First Stage Nozzles After First Stage After First Stage Load [ Full Throttling ] Steam Turbine Load [ Sliding Pressure Operation ] 4. Part Load Operation 58 / 81 HIoPE Generals for Sliding Pressure Operation In a sliding pressure operation mode, which is also called as variable pressure operation, the steam flow is controlled by varying boiler pressure with the main steam control valves are always fully open. Therefore, no throttling occurs and control stage is not needed. The steam pressure is proportional to the load, not only within the turbine but also as the inlet to the turbine (main steam line), and in the steam generator. Main steam pressure is controlled by the boiler firing rate. The main advantage of sliding pressure operation is that the main steam temperature remains relatively constant across the load range which shortens startup times and increases turbine rotor life. The disadvantages of sliding pressure operation are poorer thermodynamic efficiency and limited load response capability. It may require a forced circulation boiler to have a fast response capability. A sudden load increase is not possible because all control valves are always fully open. The lower main steam pressures of this operating mode result in less available energy than in the partial arc admission operation, but more than in the full throttling operation. Both feed pump power and throttling losses in the turbine control valves can be reduced during the sliding pressure operation because of lower pressure. Steam Turbine 4. Part Load Operation 59 / 81 HIoPE Generals for Sliding Pressure Operation Sliding pressure operation has a reduced thermodynamic efficiency during part load operation because of reduced available energy caused by reduced boiler pressure. However, there are two important facts to be considered in terms of efficiency of plant. Firstly, boiler feedwater pump power at low load operation with variable pressure can be reduced significantly. Secondly, the moisture loss at low load operation with variable pressure can be reduced. These two facts contribute to increase efficiency of the plant. T 3 c decrease in wnet 2 increase in wnet 2 1 4 4 increase in qout a Steam Turbine 3 4. Part Load Operation b b s 60 / 81 HIoPE 효율변화 분석 결과 이유 효율변화 밸브 교축손실 모든 출력에서 VWO상태이기 때문에 교축손실 매 우 작음 HP Turbine 효율 HP 1단에서 full arc 운전이며, 밸브에서 교축손실 작음 Rankine cycle 효율 부분부하운전에서 사이클 압력 저하로 available energy 감소 부분부하운전에서 펌프 동력 절감 (출력이 낮아질 수록 보일러 운전압력이 낮아지기 때문에 펌프 동 력 절감 크기 증대) Items 급수펌프 동력 Steam Turbine 4. Part Load Operation 61 / 81 HIoPE First Stage Shell Temperatures Sliding pressure operation decreases the potential for low cycle thermal fatigue in the turbine during load changes as compared to constant initial pressure operation. In sliding operation, first stage exit temperature is almost constant over the load which reduces thermal stress. First Stage Exit Temperature Sliding Pressure 100% adm. 75% adm. 62.5% adm. 50% adm. Sliding Pressure Partial Arc Admission Throttle Flow Steam Turbine 4. Part Load Operation 62 / 81 HIoPE Comparison of Heat Rate +4 +3 Single Admission (Full Throttling) Constant Pressure Sliding Pressure 2 Admissions +2 3 Admissions +1 4 Admissions 0 1st 1 2nd 3rd v/v pt. Base Line is Locus of “Valve Best Point” (Partial Arc Admission) 2 20 30 40 50 60 70 VWO Valve Loop 80 90 100 % VWO Load Steam Turbine 4. Part Load Operation 63 / 81 HIoPE 1 Basics for the Control of Steam Flow 2 Valves 3 Full Throttling 4 Partial Arc Admission 5 Sliding Pressure Operation 6 Hybrid Operation 7 Startup System of Steam Power Plants 8 Load Changes Steam Turbine 4. Part Load Operation 64 / 81 HIoPE Hybrid Operation 2400 2000 3 2 1 1000 Variable Pressure Operation Mode 600 1. Full variable pressure with all control valve wide open. 2. Variable pressure with one control valve closed. 3. Variable pressure with two control valves closed. 20 40 60 80 100 % VWO Load With a partial admission unit, it is attractive to close one or two valves and then vary pressure with one or two valves closed. This is called as hybrid operation. Steam Turbine 4. Part Load Operation 65 / 81 HIoPE Korea Standard 500MW Fossil Power 분류 VWO MGR NR Constant Pressure Operation 75 50 30 Sliding Pressure Operation 출력 (kW) 550,000 (110%) 541,650 (108.3%) 500,000 (100%) 375,000 (75%) 250,000 (50%) 150,000 (30%) 유량 (lb/hr) 3,757,727 (112.7%) 3,684,046 (110.5%) 3,335,116 (100%) 2,389,835 (71.7%) 1,564,131 (46.9%) 980,271 (29.4%) 복수기 압력 (in.Hga) 1.5 1.5 1.5 1.5 1.5 1.5 주증기 온도 (F) 1000 1000 1000 1000 1000 1000 주증기 압력 (psia) 3514.7 (100%) 3514.7 (100%) 3514.7 (100%) 2860.2 (81.38%) 1870.2 (54.47%) 1152.6 (32.79%) 1st STA Bowl P. (psia) 3409.3 (100%) [97.00%] 3409.3 (100%) [97.00%] 3409.3 (100%) [97.00%] 2774.4 (81.39%) [97.00%] 1814.7 (54.49%) [97.03%] 1118.0 (32.79%) [97.00%] 1st STA Shell P. (psia) 2630.8 (113.9%) 2573.8 (111.5%) 2309.0 (100%) 1683.5 (72.9%) 1128.0 (48.9%) 723.9 (31.4%) FWPT 동력 (kW) 18,755 (3.41%) 18,390 (3.40%) 16,611 (3.32%) 9,622 (2.57%) 4,125 (1.65%) 1,523 (1.02%) Steam Turbine 4. Part Load Operation 66 / 81 HIoPE Hybrid Operation The hybrid operation adopts advantages of both sliding pressure operation and partial arc admission through the combination of partial arc admission operation and sliding pressure operation. Sliding pressure operation has the advantage of no throttling loss, and partial arc admission operation has the advantage of fast load response. At low loads, some of the main steam control valves are wide open and steam flow is controlled by sliding pressure operation. The main steam pressure is increased with steam turbine load until the main steam pressure rated conditions. The steam turbine load is increased further by maintaining the rated main steam pressure and sequential opening of the remaining main steam control valve as in the partial arc admission operation. Starting from full load, load reductions are initially achieved by closing control valves sequentially and maintaining constant initial pressure. When a particular valve point is reached, further load reductions are achieved by holding valve position constant and decreasing initial pressure. The best point for the change from constant to sliding pressure depends on the boiler characteristics and the value of design initial pressure. The optimum point usually occurs at about 50 to 60% load. Steam Turbine 4. Part Load Operation 67 / 81 Hybrid Operation Steam Turbine 4. Part Load Operation HIoPE 68 / 81 HIoPE Comparison of Heat Rate +4 +3 Single Admission (Full Throttling) Constant Pressure Sliding Pressure 2 Admissions Hybrid Operation +2 3 Admissions 1 +1 4 Admissions 2 0 1st 1 2nd 3 3rd v/v pt. Base Line is Locus of “Valve Best Point” (Partial Arc Admission) VWO Valve Loop 2 20 30 40 50 60 70 80 90 100 % VWO Load Steam Turbine 4. Part Load Operation 69 / 81 HIoPE Comparison of Heat Rate The full throttling has the worst overall heat rate because of throttling losses. The sliding pressure operation has a slightly better heat rate than full throttling operation, but still has poor performance because of the lower main steam pressures. The partial arc admission operation shows the best heat rate at higher loads because of the high main steam pressures and minimized throttling losses resulting from throttling with only one control valve at a time. The hybrid operation gives the most efficient operation because the unit life is extended by maintaining relatively constant temperatures at low loads, reducing cycling effects. Heat rate for the partial arc admission is typically plotted as a “locus of best valve points,” that is, the line passing through the heat rate points where any valves open are wide open. The actual heat rate curve for the partial arc admission is represented by a valve loop that incorporates the throttling losses associated with a valve throttling between full closed and full open. Theoretically, the more control valves, the smaller valve loop, the greater the possibility of operating without throttling, and the better the heat rate. Steam Turbine 4. Part Load Operation 70 / 81 HIoPE Modified Sliding Pressure Operation Modified sliding pressure operation uses throttle valve reserve so the valves are slightly closed at 90% to 95% load and some boiler stored energy can respond more quickly to rapid load change near full load. • Today, modern power plants are operated in natural sliding pressure mode or modified sliding pressure mode. 100 Fixed Pressure Mode Main Steam Pressure, % • Primary electrical power response (additional electrical power within seconds) is produced by condensate throttling. 75 50 Fixed Pressure Mode 25 • At a certain part load, the control valves can to be throttled to improve the primary response capacity 0 0 20 40 60 80 100 Steam Turbine Load, % Steam Turbine 4. Part Load Operation 71 / 81 HIoPE Effect of Operating Mode on Steam Turbine Design Steam Turbine 4. Part Load Operation 72 / 81 HIoPE 1 Basics for the Control of Steam Flow 2 Valves 3 Full Throttling 4 Partial Arc Admission 5 Sliding Pressure Operation 6 Hybrid Operation 7 Startup System of Steam Power Plants 8 Load Changes Steam Turbine 4. Part Load Operation 73 / 81 Startup System of Steam Power Plants HIoPE Boiler-internal startup systems and unit startup system The purpose of boiler-internal startup systems is to drain off the excess water discharged from the evaporator and to ensure flow through once-through evaporators. Excess water is defined as the quantity of water which must be removed from a water-filled heat-exchange system due to increased volume as a result of steam formation and increased temperature. Steam Turbine 4. Part Load Operation 74 / 81 HIoPE Startup System of Steam Power Plants Natural-circulation boilers only have equipment for removing the excess water from the drum. During startup of once-through boilers, a circulation flow is combined with the once-through flow in the economizer and evaporator until the minimum evaporator flow level. The water that does not evaporate is separated from the steam in HP separators and then fed either to a recirculation pump, a drain heat exchanger, the feedwater tank, or an atmospheric flash tank. The unit startup system ensure cooling of the superheater heating surfaces and supplies steam to the turbine at the required startup pressure and temperature. In modern power plants, separate turbine bypass systems for the HP and IP/LP casings of the turbine, respectively, are seeing increased use. Essential advantages of this system are the result of the uniform heatup of the superheater heating surfaces – preventing flaking of the protective coating on the inside of the tubes caused by thermal shock and carryover of corrosion products into the turbine (solid particle erosion) – short startup time, and the same basic startup procedure for cold, warm and hot starts. If bypass systems are dimensioned appropriately ( 60% steam flow at full load), the steam generator can be kept in operation even when there is a turbine-generator load rejection to the station auxiliary power level, thus in most cases preventing a unit trip. Steam Turbine 4. Part Load Operation 75 / 81 HIoPE 1 Basics for the Control of Steam Flow 2 Valves 3 Full Throttling 4 Partial Arc Admission 5 Sliding Pressure Operation 6 Hybrid Operation 7 Startup System of Steam Power Plants 8 Load Changes Steam Turbine 4. Part Load Operation 76 / 81 Load Changes HIoPE Sudden loss of other power plants or grid disturbances require step increase of the load in those power plants still on line of about 2 to 5% within seconds to maintain a stable grid frequency. Since it takes 2 to 3 minutes for increased firing in coal-fired units to achieve the desired electric power output, the storage capacity of the water/steam system is used for making such step load changes. The various methods applied vary with regard to dynamic behavior and economics: 1) Opening the control valves: A drop in pressure upstream of the turbine activates the storage capacity of the main steam line and the steam generator. The magnitude of the possible load step increase depends on the throttle setting on the turbine valves, while the duration of the load step change depends on the storage capacity. The storage capacity of a drum boiler is about 2 to 3 times that of a oncethrough boiler. On the other hand, the permissible pressure transient is only 6 to 8 bar/min as apposed to 20 to 30 bar/min for a once-through boiler. The curve given in the figure depicts throttling corresponding to 5% of the main steam pressure at 100% load. Dynamic impact of various measures taken to activate load reserves Steam Turbine 4. Part Load Operation 77 / 81 HIoPE Load Changes 2) Opening of multistage valve: With respect to the load step change, the behavior of the multistage valve is similar to throttling of the turbine control valves. Compared to throttling of the turbine control valves, however, the implementation of the multistage valve requires additional investment cost, but on the other hand provides a lower heat rate in steady-state operation. 3) Condensate throttling: Reducing the condensate flow reduces the extraction-steam flow and therefore increases the steam turbine output. A steam-side shutdown of the LP feedwater heaters is also possible and makes the additional output available somewhat more quickly than does the throttling of the condensate. The heat rate in steady-state operation is not affected by this measure, and only a small additional investment is required. 4) Shutdown of HP feedwater heaters: This measure can be applied without duration restrictions. Initially, however, it causes considerable thermal stress in the thick-walled components of the steam generator due to the large feedwater temperature transients. In normal operation, the heat rate is not affected. 5) Increased injection flow into the steam generator: This measure primarily makes use of the thermal storage capacity of the heating surfaces and the headers based on a reduction of steam temperature. The heat rate in steady-state operation is not affected. Steam Turbine 4. Part Load Operation 78 / 81 Load Changes HIoPE During load changes, temperature changes occur in the turbine and in the steam generator which cause temporary thermal stresses in the thick-walled components and which thus limit the load transients. In the HP turbine, the temperatures change on constant-pressure mode. In Fig. 3.49, the values are plotted downstream of the first stage. In sliding-pressure mode, in which no throttling takes place, the temperatures are nearly constant. Sliding-pressure mode is therefore the more favorable operating mode for the steam turbine. Steam Turbine 4. Part Load Operation 79 / 81 Load Changes HIoPE The temperature in the steam generator remain nearly constant in constant-pressure mode but change in sliding-pressure mode due to the pressure-dependent saturated-steam temperature in the evaporator and the primary superheater region. Moreover, a load increase in sliding-pressure mode as a result of increased pressure stores energy in the system, which also reduces the load transients. For the drum-type boiler with its thick-walled drum and the large storage capacity of the evaporator system, constant-pressure mode is therefore the more favorable operating mode. The once-through boiler is well suited for either operating mode. Unit behavior under continuous load changes is determined by the two main components the boiler and the turbine as well as the control system on the one hand, and by the operating mode on the other. Table 3.11 shows the feasible load transients for these two main components and the resulting unit values. Steam Turbine 4. Part Load Operation 80 / 81 HIoPE 질의 및 응답 작성자: 이 병 은 (공학박사) 작성일: 2015.02.11 (Ver.5) 연락처: ebyeong@daum.net Mobile: 010-3122-2262 저서: 실무 발전설비 열역학/증기터빈 열유체기술 Steam Turbine 4. Part Load Operation 81 / 81