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Document typeNo.: STIM-03.006
Steam Turbine Information Manual Revision/Date: 14 2009-09-25
Issued by: P11P14
Title
Control Fluid Piping Design
Proj Code UA Content CodeUNID-Nr
Document Status: Preliminary Final ISO 9001 Clause & Title:
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Released by: Andreas Logar E F PR SU EN R&D 14 signed Logar 2009-09-29
Reviewed by: JrgenHavemann
E F PR SU EN NA signedHavemann 2009-09-29
Prepared by: Heinz Ltters E F PR SU EN R&D 14 signed Ltters 2009-09-25
Name Org. Unit Signature Date
REVISION SHEET
REVISION REISSUE
DATE
SECTION DESCRIPTION OF CHANGE
010 2007-05-31 2.23.1
3.2.13.3
4.1
6
Valve actuators addedParagraphs addedPED note deleted3.3.2: table with data for pressure surge added4.1 max. allowable pressure drop and viscosity added
Drawings added
011 2008-02-29 3.2
4.1
Design and test pressure changed
Butt weld requirement added
012 2008-07-04 4.3 Functional safety requirements added
013 2009-02-02 3.3
4.1
- Closing times of bypass valves for driving in openposition changed, see report R&D1-09-006.
- Requirement for seamless piping added
014 2009-09-25 3.3.2 - Table with data for pressure surge: variant for partialstroke testing added
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TABLE OF CONTENTS
SECTION PAGE
1.
SCOPE .......................................................................................................................................................5
1.1 Responsibilities of the pipe designer:.................................................................................................... 5
2. GENERAL ..................................................................................................................................................52.1 National Standards................................................................................................................................ 5
2.2 Piping Interfaces.................................................................................................................................... 6
3. DESIGN REQUIREMENTS FOR CONTROL FLUID SYSTEM.................................................................63.1 General Design Requirements .............................................................................................................. 6
3.2 Load case steady state.......................................................................................................................... 7
3.2.1 Operating pressure:..................................................................................................... 7
3.2.2
Design pressure (set pressure of pressure relief valve downstream main pumps):.... 73.2.3 Test pressure (1.5 x Design pressure): ....................................................................... 7
3.3 Load case pressure surge..................................................................................................................... 7
3.3.1 Pressure surge (operating pressure + pressure increase):......................................... 73.3.2 Table with data for pressure surge calculation............................................................ 8
3.4 Load case pressure variation .............................................................................................................. 10
3.5 Load case with temperature variation ................................................................................................. 10
3.6 Other Load cases ................................................................................................................................ 10
4. PIPING DESIGN REQUIREMENTS.........................................................................................................114.1 General requirements.......................................................................................................................... 11
4.2
Insulation and trace heating ................................................................................................................ 12
4.3 I&C measures for steam turbines........................................................................................................ 12
4.3.1 Steam turbine with two or more valve combinations (stop and control valve) perexpansion range ...................................................................................................................... 124.3.2 Steam turbines with one valve combination (stop and control valve) per expansionrange .................................................................................................................................. 15
5. PIPING SYSTEM FABRICATION REQUIREMENTS..............................................................................185.1 General ................................................................................................................................................ 18
5.2 Welding................................................................................................................................................ 18
5.3 Non Destructive Test ........................................................................................................................... 18
5.4 Testing ................................................................................................................................................. 18
6. INFORMATION PROVIDED BY SPG......................................................................................................186.1 Thermal Expansion.............................................................................................................................. 18
6.2 Volume flows for pressure drop and pressure surge calculation........................................................ 18
6.3 Purity after oil flushing ......................................................................................................................... 18
6.4 P&ID..................................................................................................................................................... 18
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1. SCOPE
This document covers the general requirements for the design of interconnecting piping for theTurbine Control Fluid Systems. The associated project specific document is drawing xxxxx-
980294. The specific scope of interconnecting piping is indicated on the Turbine Control FluidSystem Diagrams.
If required, the scope of the piping must be including the scope of the insulation, trace heating,trace heating related I&C.
1.1 Responsibilities of the pipe designer:
The pipe designer is responsible for the design, analysis and specification of theinterconnecting piping systems per the requirements of ASME B31.1 or VGB R503 M, VGBR510 L and DIN EN13480-3 and this specification. This includes also the calculation ofstrength against pressure/pressure surges and pipeline flexibility for valve movement due to
thermal expansion. The information, examples and remarks submitted do not relieve thedesigner of responsibility for the system.
2. GENERAL
2.1 National Standards
Specific standards issued by the following organizations must be applied where referenced inthis specification. It is the Designer's responsibility to obtain copies of all referenced documentsand drawings.
ANSI American National Standards InstituteASME American Society of Mechanical EngineersASTM American Society of Testing Materials
or where required
DIN EN Deutsches Institut fr Normung / European NormISO International Standard OrganisationEG Machine Directive 98/37/EGPressure Equipment Directive (PED) 97/23/EGVGB R503 M, VGB R510 L
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2.2 Piping Interfaces
Piping Interfaces are located at the following equipment, depending on turbine type.:
Main Steam Valve Actuator
Hot Reheat Steam Valve Actuator
LP Induction Valve Actuator
Intercept Valve Actuator
Overload Valve Actuator
Heat Extraction Control Valve Actuator
Start-Up and Safety Valve Actuator
Bypass Valve Actuator
Hydraulic Supply Unit
3. DESIGN REQUIREMENTS FOR CONTROL FLUID SYSTEM
3.1 General Design Requirements
The electro-hydraulic valve actuators are provided with control fluid via one or more hydraulic
supply units (the quantity of units is depending on type of plant and quantity of valve actuators).
Valve vibrations must not affect the hydraulic supply unit. The control fluid is either mineral oil
or fire-resistant fluid (FRF).
The control fluid lines represent a very high risk potential due to the high operating pressure
and the additional pressure surges. Any leakages could lead to an oil fire in the potentially hot
surroundings. The control fluid line design must therefore be calculated with regard to strength
and restrained thermal expansion as well as the configuration of pipe supports such as fixed
points, guides and vibration dampeners.
Suitability of the pipeline wall thickness and pipe routing must be verified for the following load
cases given in chapter 3.2, 3.3 and 3.4.
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3.2 Load case steady state
3.2.1 Operating pressure:
p = 160 bar (2320 PSI) Temperature: = 60C (140F)
3.2.2 Design pressure (set pressure of pressure relief valve downstream main pumps):
p = 180 bar (2611 PSI) Temperature: = 70C (158F)
3.2.3 Test pressure (1.5 x Design pressure):
p = 270 bar (3916 PSI) Temperature: = 20C (68F)
3.3 Load case pressure surge
3.3.1 Pressure surge (operating pressure + pressure increase):
p = 160 + p bar (2320 PSI + p PSI) Temperature: = 60C (140F)
The pressure increase p on a sudden change in mass flow is based on the Joukowsky
pressure surge equation, the main equation from pressure surge theory. This provides
information on the possible pressure increase p on a sudden change in mass flow.
p = a . .w / 105 bar
where a = sound velocity, mineral oil and FRF : a = 1500 m/s (4921 ft/s)
w = change of velocity due to a sudden change of the mass flow
w = V& / A (m/s)
V& = flow rate (m3/s)
A = inner cross-sectional area (m2)
A= /4 . di
di = inner pipe diameter (m)
and = fluid density, mineral oil : = 900 kg/m3(56.2 lb/ft3)
FRF : = 1250 kg/m3 (78.0 lb/ft3).
This pressure increase propagates at the velocity of sound against the direction of flow of
the medium. The resulting shock forces on the piping system have to be used for specifying
the locations of guides, fixed points and vibration dampeners. The determination of the
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shock forces must be performed in accordance with standard industry analytical
techniques.
Note:
The following Siemens standard for calculation of the shock forces can be used forcomparison purposes.
Determination of the shock forces is a function of critical pipe length Lcrit .
Lcrit= a.ts where ts= servo or solenoid valve closing time
Fsurge= L.m& / ts if L Lcrit
Verification of suitability of the pipework against stresses must be performed in accordance
with ASME B31.1 or DIN EN13480-3.
3.3.2 Table with data for pressure surge calculation
The pressure surge in the control fluid system is caused either by rapid shutting off the
short circuit volume flow by servo respectively solenoid valve or by sudden stop of the
control fluid column through driving valve or actuator against the end position.
Explanation of Short circuit volume flow: This is the maximum possible volume flow
through pressure and return lines occurring after Steam turbine trip until servo respectively
solenoid valve switch back. This happens, if a turbine trip is released during opening ofvalve (servo/solenoid valve and trip solenoid valves are connected to different control
systems). All actuators with solenoid trip valves are affected by this.
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Valve TypeActuator
TypeClosing Time
ts[ms]
Occurrence
perlifetime
1)
Reason of pressure surgeVolume flow to be considered
[l/min]
200 10000 Closing time servo valveMain Steam
Control Valve
6 1Closing time servo valve failure
mode
See xxxxx-980294 chapter 3.4
Main Steam Stop Valve 25 10000 Closing time solenoid valve 25
200 10000 Closing time servo valveMain Steam
7) Stop Valve
6 1Closing time servo valve failure
mode
See xxxxx-980294 chapter 3.4
200 10000 Closing time servo valveHot ReheatSteam
Control Valve6 1
Closing time servo valve failuremode
See xxxxx-980294 chapter 3.4
Hot ReheatSteam
Stop Valve 25 10000 Closing time solenoid valve 25
200 10000 Closing time servo valveHot ReheatSteam
7)
Stop Valve6 1
Closing time servo valve failuremode
See xxxxx-980294 chapter 3.4
200 10000 Closing time servo valveLP InductionSteam
Control Valve6 1
Closing time servo valve failuremode
See xxxxx-980294 chapter 3.4
LP Induction
Steam
Stop Valve 25 10000 Closing time solenoid valve 25
200 10000 Closing time servo valveIntercept Control Valve
6 1Closing time servo valve failure
mode
See xxxxx-980294 chapter 3.4
Intercept Stop Valve 25 10000 Closing time solenoid valve 25
200 10000 Closing time servo valve
Overload Control Valve6 1
Closing time servo valve failuremode
See xxxxx-980294 chapter 3.4
Heat ExtractionControl
Control Valve - - No pressure surge expected -
Start-Up andSafety
Stop Valve 40 10000 Closing time solenoid valve 20
6 100 Closing time servo valve2)Hot Reheat
BypassSingle Stem Control Valve 6 300Valve will be driven into full open
end position3)
See xxxxx-980294 chapter 3.4
6 100 Closing time servo valve2)Supply Steam
BypassSingle Stem
Control Valve6 300
Valve will be driven into full openend position
3)
See xxxxx-980294 chapter 3.4
6 100 Closing time servo valve2)
Hot ReheatBypass
Double Stem(2 welded anglevalves /Boxberg
Design)
Control ValveActuator with
spring 6 300Valve will be driven into full open
end position3)
See xxxxx-980294 chapter 3.4
25 100 Closing time solenoid valve See xxxxx-980294 chapter 3.4Hot ReheatBypass
Double Stem(2 welded anglevalves /Boxberg
Design)
Stop ValveActuator with
spring 6 10000Valve will be driven into full open
end positionSee xxxxx-980294 chapter 3.4
Hot ReheatBypass
Double Stem(2 welded anglevalves /Boxberg
Design)
Control andStop Valve
6 1Failure mode volume flow to stop
and control valve addedSee xxxxx-980294 chapter 3.4
Hot ReheatBypass
Double Stem(Z-valve design)
Control ValveActuator without
spring6 400
Valve will be driven into full endposition
2)3)4)5)
See xxxxx-980294 chapter 3.4
25 100 Closing time solenoid valve See xxxxx-980294 chapter 3.4Hot ReheatBypass
Double Stem(Z-valve design)
Stop Valve6 10000
Valve will be driven into full openend position
See xxxxx-980294 chapter 3.4
Hot ReheatBypass Control andStop Valve 6 1 Failure mode volume flow to stopand control valve added6)
See xxxxx-980294 chapter 3.4
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Valve TypeActuator
Type
Closing Time
ts[ms]
Occurrenceper
lifetime1)
Reason of pressure surgeVolume flow to be considered
[l/min]
Double Stem(Z-valve design)
Supply SteamBypass
Double Stem(Z-
valve design)
Control ValveActuator without
spring6 400
Valve will be driven into full endposition
2)3)4)5)
See xxxxx-980294 chapter 3.4
25 100 Closing time solenoid valve2)
See xxxxx-980294 chapter 3.4Supply SteamBypass
Double Stem (Z-valve design)
Stop Valve6 10000
Valve will be driven into full openend position
See xxxxx-980294 chapter 3.4
Supply SteamBypass
Double Stem (Z-valve design)
Control andStop Valve
6 1Failure mode volume flow to stop
and control valve added6)
See xxxxx-980294 chapter 3.4
Notes: 1) Maximum expected loading combinations.2) Bypass Trip (e.g. due to loss of injection water or increasing condenser pressure).3) Full opening of bypass valve (e.g. load rejection and turbine trip under high loads).4) For bypass double stem control valves (Z-design, actuator without spring) there is no short circuit flow due to
design without trip valves.5) 400 loads = 300 loads full open + 100 loads full closed end position.
6) Trip actuation during opening of control valve causes switching of servo valve.7) Only for valves with partial stroke testing.
3.4 Load case pressure variation
Pressure variation betweenLoad cycles
130bar (1885 PSI) and 160bar (2320 PSI)
The fatigue-strength underpulsating (oscillating,fluctuating) compressivestress must be guaranteed.
115bar (1668 PSI) and 160bar (2320 PSI) The load cycle of 10000 hasto be considered.
0 bar (0 PSI) and 160bar (2320 PSI)The load cycle of 400 has tobe considered.
3.5 Load case with temperature variation
Temperature Load cycle of 7000 has to be considered (for temperature delta of 50 Kelvin).
All other temperature cycles below 50K must be guaranteed for life time of the piping.
3.6 Other Load cases
For additional loads caused by vibration of electro-hydraulic actuators, working platforms,earthquakes, etc.
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4. PIPING DESIGN REQUIREMENTS
4.1 General requirements
Movement of the valves due to thermal expansionDue to the high forces and the large movement of the valves, especial care must be taken,
when designing the first support of the control fluid pipe after the valve. The small controlfluid pipes must have a short span between the valve and the first support due to the highforces of the pressure surge. However, due to the large movement of the valves there mustbe a certain distance between valve and first support to reduce the stress in the pipe. Tofulfill both requirements vibration dampeners are necessary. This must be calculated inevery case.
The following must be taken into consideration where calculating the thermal expansion ofthe connection points at the actuators:
Main steam valve, Hot Reheat, Overload- and Intercept Steam Valve and HeatExtraction Control valve
The thermal expansion of the turbine, the steam valves itself and the adjoining pipesmust be considered.
Bypass ValvesThe movement of the adjoining pipe and the movement of the condenser must beconsidered as well as the thermal expansion of the bypass valve itself.
LP Induction ValveIf the valve is flanged at the turbine the thermal expansion of the turbine must beconsidered. If it part of the pipe, the movement of the pipe must be considered.
Start-Up and Safety ValveThe movement of the adjoining pipe as well as the thermal expansion of the valve itselfmust be considered.
The pipes are pressure sensitive lines. Therefore the allowable pipe pressure drop islimited. The maximum allowable pressure drop values are:
5 bar for pressure pipes2,5 bar for return pipes.
Pressure drop must be calculated with a fluid viscosity of 46 cSt. [Note: For ISO VG46 (either
mineral oil or FRF) fluid this is corresponding to a fluid temperature of 40C which is a reasonabletemperature when MAX system is in operation and bigger control valve movements may occur.]
The associated volume flow is given in xxxxx-980294, chapter 3.3.
The pipes must be routed with a constant pitch of 1 back to the hydraulic supply unit.
Vibrations can have several causes such as rotating machines like turbines and motors,flows through piping, valves and fittings etc. To avoid serious damage of welds andmaterial, the piping must be supported by means of dampers and guides wherever there isa hazard that vibrations can arise.
!
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Since it is not possible to anticipate if vibrations occur during the piping design, it isrequired that the piping will be checked during commissioning. Special attention must bepaid to high-frequency vibrations, because they quickly reduce the fatigue strength.
The pipe material must be stainless steel.
All welding seams of the pressure line must to be performed as butt weld.
Only seamless pipes are allowed
4.2 Insulation and trace heating
For outdoor units where the ambient temperature and for indoor units where the temperature inthe turbine building is expected to be at or below 5C (41F), the piping and the actuators mustbe provided with insulation and trace heating. Installation of trace heating systems is specifiedfor the following:
- Supply lines for control fluid system connecting tank to actuators- Actuators for turbine valves (main-, reheat-, LP induction steam)- Return lines connecting actuators to tank
Solenoid valves, servo valves on the control block and position transmitters must be installedwithoutthermal insulation
When trace heating is used, the max. pipe and actuator temperature must not exceed 25C(77F ). During operation with trace heating the control fluid temperature cycle must notexceed 20 Kelvin.
The temperature limits are valid for fluids according to STIM-05.002.
In the event that a trace heating system is not activated when needed or has failed of a traceheating system, the closing function is then no longer assured for turbine valve actuators. Loadrejection may then result in turbine overspeed with consequential catastrophic failure of therotor.
To reduce the hazard potential commensurately, appropriate protection circuits must beinstalled. These serve to close the affected valves before temperatures have fallen below safetemperature levels.
4.3 I&C measures for steam turbines
In case standards on Functional Safety apply (IEC61508, IEC61511, ISA S84.01, ....) thefollowing description of I&C measures has to be completed by analysis, specification andvalidation measures as described in these standards.
4.3.1 Steam turbine with two or more valve combinations (stop and control valve) perexpansion range
A 1-out-of-2 temperature protection circuit (with monitoring of the trace heating)must beinstalled for the return line of each HP steam, IP steam and LP (induction) steam valvecombination. Failure of the trace heating for the associated valve combination causesresponse of this circuit and closure of this valve combination by initiation of individual trip in
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good time (before control fluid temperature in the return line falls below a safe level: alarmsignal issue at temperature below/equal to 10C (below/equal to 50F), trip signal issue attemperature below/equal to 8C (below/equal to 46F ) ).
Temperature measurement (clamping strap elements) for this temperature protectioncircuit must be implemented by means of instrumentation installed under the thermal
insulation slightly ahead (about 0.5 m) of the tank for the control fluid supply system.The temperature protection circuit must be implemented such as to give a safe failurepercentage of better than 60%.
In the case of the LP (induction) steam valve combination, a temperature protection circuitfor the return line must be supplemented by installation of an additional 1-out-of-2temperature protection circuit on both the stop valve actuator and the control valve actuatorfor configurations that feature two separate trace heating systems (for the stop valve andfor the control valve). The associated temperature instrumentation must be installed on theoperating cylinder (see diagram 1). In the event that a common trace heating system isimplemented for the two actuators, a common additional 1-out-of-2 temperature protectioncircuit for the two actuators is then adequate. The associated temperature instrumentation
must be installed on the operating stop valve cylinder (see diagram 1).In the event that a common trace heating system is implemented for the return line and thetwo LP (induction) steam valve actuators, a common additional 1-out-of-2 temperatureprotection circuit on the return line is then adequate. Temperature measurement for thistemperature protection circuit must be implemented by means of instrumentation installedunder the thermal insulation slightly ahead (about 0.5 m) of the tank for the control fluidsupply system.
To rule out control fluid degradation in the event of excess temperatures, alarms arederived from the separate temperature measurements in response to T> 70C (158F) inthe case of mineral oil and in response to T>65C (149F) in the case of FRF.
A trip signal must be formed for each steam valve combination. This must be implementedin the form of binary, redundant signals routed along break-current circuitry (deenergize totrip) to the Siemens PG automation system scope of supply (see schematic).
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1 oo 2
MP 4MP 1 MP 2
trip of
low pressurevalve
combination
individual control of the
5 valve combinations
2 out of 2
for eachprotection circle with
noncoincidence monitoring
1 oo 2 1 oo 21 oo 2
>=1
2 Trip-Signals for eachprotection circle
normally energized
CONCEPT TEMPERATURE PROTECTION TRACE HEATING SYSTEM
Turbine with two valve combinations (stop and control valve) per expansion range
2 out of 2 TRIP SIGNALS
P P PPP
P PP P
T T T
TT
PT100 resistance
thermometer
surface mounted
MP 1
Legend:
MP measuring-point
MP 2
MP 3
MP 4 MP 5
sensor 1
sensor 2
protection circle MP3, MP6
and MP7 depending from
trace heating line
MP 7MP 6
PT100 resistance
thermometer
surface mounted
PT100 resistance
thermometer
surface mounted
PT100 resistance
thermometersurface mounted
PT100 resistance
thermometer
surface mounted
PT100 resistance
thermometersurface mounted
MP 6 and 7 depending from
trace heating line
O.K.-Signals
Freeze Protection Units
MP 6 MP 7
P
1 oo 2 1 oo 2
trip of
high pressure
valve
combination 1
trip ofhigh pressure
valve
combination 2
trip of
intermediatepressure
valve
combination 1
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4.3.2 Steam turbines with one valve combination (stop and control valve) per expansionrange
A 1-out-of-2 temperature protection circuit (with monitoring of the trace heating) must beinstalled for the return line of each HP steam, IP steam and LP (induction) steam valve
combination. Failure of the trace heating for the associated valve combination causesresponse of this circuit (before control fluid temperature in the return line falls below a safelevel: alarm signal issue at temperature below/equal to 10C (below/equal to 50F), tripsignal issue at temperature below/equal to 8C (below/equal to 46F ) ).
Temperature measurement (clamping strap elements) for this temperature protection circuitmust be implemented by means of instrumentation installed under the thermal insulationslightly ahead (about 0.5 m) of the tank for the control fluid supply system.The temperature protection circuit must be implemented such as to give a safe failurepercentage of better than 60%.
In the case of the LP (induction) steam valve combination, a temperature protection circuit
for the return line must be supplemented by installation of an additional 1-out-of-2temperature protection circuit on both the stop valve actuator and the control valve actuatorfor configurations that feature two separate trace heating systems (for the stop valve andfor the control valve). The associated temperature instrumentation must be installed on theoperating cylinder (see diagram 1). In the event that a common trace heating system isimplemented for the two actuators, a common additional 1-out-of-2 temperature protectioncircuit for the two actuators is then adequate. The associated temperature instrumentationmust be installed on the operating stop valve cylinder (see diagram 1).In the event that a common trace heating system is implemented for the return line and thetwo LP (induction) steam valve actuators, a common additional 1-out-of-2 temperatureprotection circuit on the return line is then adequate.
To rule out control fluid degradation in the event of excess temperatures, alarms arederived from the separate temperature measurements in response to T> 70C (158F) inthe case of mineral oil and in response to T>65C (149F) in the case of FRF.
A common trip signal must be formed for the HP steam and IP steam valve combinations.This must be implemented in the form of binary, redundant signals routed along break-current circuitry (deenergize to trip) to the Siemens PG automation system scope of supply(see schematic).
A common trip signal must be formed for the two actuators of the LP (induction) steamvalve combination. This must be implemented in the form of binary, redundant signalsrouted along break-current circuitry (deenergize to trip) to the Siemens PG automation
system scope of supply.
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Diagram 1
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Siemens Power Generation This document contains proprietary information. It is submitted inconfidence and is to be used solely for the purpose for which it is furnishedand returned upon request. This document and such information is not to bereproduced, transmitted, disclosed, or used otherwise in whole or in partwithout written authorization.
protection circle MP3, MP4
and MP5 depending from
trace heating line
2 out of 2
for eachprotection circle with
noncoincidence monitoring
1 oo 2
2 Trip-Signals for each protection circle
normally energized
O.K.-Signals
Freeze Protection Units
MP 2MP 1MP 5MP 4
trip oflow pressure
valve combination
individual control of the
3 valve combinations
CONCEPT TEMPERATURE PROTECTION TRACE HEATING SYSTEMTurbine with 1 valve combination (stop and control valve) per expansion range
2 out of 2 TRIP SIGNALS
P PP
PP
T T
T
Legend:
MP measuring-point
MP 1
MP 3
MP 2
MP 5MP 4
PT100 resistance
thermometer
surface mounted
PT100 resistance
thermometer
surface mounted
PT100 resistance
thermometer
surface mounted
P
sensor 1
sensor 2
trip ofsteam turbine
1 oo 2 1 oo 21 oo 21 oo 2
>=1 >=1
PT100 resistance thermometer
surface mounted
MP4 and 5 depending from
trace heating line
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Siemens Power Generation This document contains proprietary information. It is submitted inconfidence and is to be used solely for the purpose for which it is furnishedand returned upon request. This document and such information is not to bereproduced, transmitted, disclosed, or used otherwise in whole or in part
5. PIPING SYSTEM FABRICATION REQUIREMENTS
5.1 General
The fabrication, inspection and testing of the piping system must be per the requirements of
ASME B31.1 or where required according VGB R503 M + VGB R510L, STIMs andTransmittal Drawings.
5.2 Welding
All welding must be per the requirements of ASME B31.1 or where required according VGBR503 M + VGB R510L and STIM-03.002.
5.3 Non Destructive Test
Siemens requires a non-destructive test for all lines within the control fluid system (MAX).The requirements are specified in the STIM-03.009.
5.4 Testing
The Control Fluid Pipes must be hydrostatic tested. The pressure of the hydrostaticpressure test must be 1.5 x design pressure.
6. INFORMATION PROVIDED BY SPG
6.1 Thermal Expansion
xxxxx-980255 MAIN STEAM VALVE
xxxxx-980256 REHEAT STEAM VALVE/INTERCEPT VALVE
xxxxx-980258 OVERLOAD VALVE
xxxxx-980321 HOT REHEAT BYPASS VALVE
xxxxx-980322 SUPPLY STEAM BYPASS VALVE
xxxxx-980360 LP INDUCTION VALVE
xxxxx-980332 HEAT EXTRACTION CONTROL VALVE
xxxxx-980355 START-UP AND SAFETY VALVE
6.2 Volume flows for pressure drop and pressure surge calculation
xxxxx-980294 REQUIREMENTS ON CONTROL FLUID SYSTEM
6.3 Purity after oil flushing
STIM-11.009 CONTROL FLUID SYSTEM FLUSHING AND CLEANING PROCEDURE
6.4 P&ID
xxxxx-983130 SYSTEM DIAGRAM CONTROL FLUID
xxxxx-983131 SYSTEM DIAGRAM CONTROL FLUID (BYPASS)