STIM-03.006-R14_CONTROL_FLUID_PIPING_DESIGN.pdf

Siemens Power Generation

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Document type No.: 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 Code

UNID-Nr

Document Status: Preliminary Final ISO 9001 Clause & Title:

Control Fluid Piping Design Steam Turbine Information Manual Document No.: STIM-03.006 Revision/Date: 14 2009-09-25 Page: 2 of 17



Released by: Andreas Logar E F PR SU EN R&D 14 signed Logar 2009-09-29

Reviewed by: Jrgen Havemann

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 2.2 3.1

3.2.1 3.3

4.1

6

Valve actuators added Paragraphs added PED note deleted 3.3.2: table with data for pressure surge added 4.1 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 open position 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 partial stroke testing added




TABLE OF CONTENTS

SECTION PAGE

1. SCOPE .......................................................................................................................................................5 1.1 Responsibilities of the pipe designer:.................................................................................................... 5

2. GENERAL ..................................................................................................................................................5 2.1 National Standards ................................................................................................................................ 5 2.2 Piping Interfaces .................................................................................................................................... 6

3. DESIGN REQUIREMENTS FOR CONTROL FLUID SYSTEM.................................................................6 3.1 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):.... 7 3.2.3 Test pressure (1.5 x Design pressure): ....................................................................... 7

3.3 Load case pressure surge ..................................................................................................................... 7 3.3.1 Pressure surge (operating pressure + pressure increase): ......................................... 7 3.3.2 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.........................................................................................................11 4.1 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) per expansion range ...................................................................................................................... 12 4.3.2 Steam turbines with one valve combination (stop and control valve) per expansion range .................................................................................................................................. 15

5. PIPING SYSTEM FABRICATION REQUIREMENTS..............................................................................18 5.1 General ................................................................................................................................................ 18 5.2 Welding................................................................................................................................................ 18 5.3 Non Destructive Test ........................................................................................................................... 18 5.4 Testing ................................................................................................................................................. 18

6. INFORMATION PROVIDED BY SPG......................................................................................................18 6.1 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




1. SCOPE

This document covers the general requirements for the design of interconnecting piping for the Turbine Control Fluid Systems. The associated project specific document is drawing xxxxx-980294. The specific scope of interconnecting piping is indicated on the Turbine Control Fluid System 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 the interconnecting piping systems per the requirements of ASME B31.1 or VGB R503 M, VGB R510 L and DIN EN13480-3 and this specification. This includes also the calculation of strength against pressure/pressure surges and pipeline flexibility for valve movement due to thermal expansion. The information, examples and remarks submitted do not relieve the designer of responsibility for the system.

2. GENERAL

2.1 National Standards

Specific standards issued by the following organizations must be applied where referenced in this specification. It is the Designer's responsibility to obtain copies of all referenced documents and drawings.

ANSI American National Standards Institute ASME American Society of Mechanical Engineers ASTM American Society of Testing Materials or where required DIN EN Deutsches Institut fr Normung / European Norm ISO International Standard Organisation EG Machine Directive 98/37/EG Pressure Equipment Directive (PED) 97/23/EG VGB R503 M, VGB R510 L




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.




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):


3.2.3 Test pressure (1.5 x Design pressure):


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




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 for

comparison 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 where L = pipeline section length m& = mass flow rate Fsurge = a . m& 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 of

valve (servo/solenoid valve and trip solenoid valves are connected to different control

systems). All actuators with solenoid trip valves are affected by this.




Valve Type Actuator Type Closing Time

ts [ms]

Occurrence per

lifetime1) Reason of pressure surge Volume flow to be considered [l/min]

200 10000 Closing time servo valve Main Steam Control Valve 6 1 Closing 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 valve

Main Steam 7) Stop Valve 6 1 Closing time servo valve failure mode See xxxxx-980294 chapter 3.4

200 10000 Closing time servo valve Hot Reheat Steam Control Valve 6 1 Closing time servo valve failure mode


Hot Reheat Steam Stop Valve 25 10000 Closing time solenoid valve 25

200 10000 Closing time servo valve Hot Reheat Steam 7) Stop Valve 6 1 Closing time servo valve failure mode


200 10000 Closing time servo valve LP Induction Steam Control Valve 6 1 Closing time servo valve failure mode


LP Induction Steam Stop Valve 25 10000 Closing time solenoid valve 25

200 10000 Closing time servo valve Intercept Control Valve

6 1 Closing 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 Valve 6 1 Closing time servo valve failure mode


Heat Extraction Control Control Valve - - No pressure surge expected -

Start-Up and Safety Stop Valve 40 10000 Closing time solenoid valve 20

6 100 Closing time servo valve 2) Hot Reheat Bypass

Single Stem Control Valve

6 300 Valve will be driven into full open end position 3)


6 100 Closing time servo valve 2) Supply Steam Bypass

Single Stem Control Valve

6 300 Valve will be driven into full open end position 3) See xxxxx-980294 chapter 3.4

6 100 Closing time servo valve 2) Hot Reheat Bypass Double Stem (2 welded angle valves /Boxberg

Design)

Control Valve Actuator with

spring 6 300 Valve will be driven into full open end position 3)


25 100 Closing time solenoid valve See xxxxx-980294 chapter 3.4 Hot Reheat Bypass

Double Stem (2 welded angle valves /Boxberg

Design)

Stop Valve Actuator with

spring 6 10000 Valve will be driven into full open

end position See xxxxx-980294 chapter 3.4

Hot Reheat Bypass

Double Stem (2 welded angle valves /Boxberg

Design)

Control and Stop Valve 6 1

Failure mode volume flow to stop and control valve added See xxxxx-980294 chapter 3.4

Hot Reheat Bypass

Double Stem (Z-valve design)

Control Valve Actuator without

spring 6 400 Valve will be driven into full end position 2)3)4)5) See xxxxx-980294 chapter 3.4

25 100 Closing time solenoid valve See xxxxx-980294 chapter 3.4 Hot Reheat Bypass


Stop Valve 6 10000 Valve will be driven into full open end position See xxxxx-980294 chapter 3.4

Hot Reheat Bypass


Failure mode volume flow to stop and control valve added 6) See xxxxx-980294 chapter 3.4




Valve Type Actuator Type Closing Time

ts [ms]

Occurrence per

lifetime1) Reason of pressure surge Volume flow to be considered [l/min]


Supply Steam Bypass


Control Valve Actuator without

spring 6 400 Valve will be driven into full end position 2)3)4)5)


25 100 Closing time solenoid valve 2) See xxxxx-980294 chapter 3.4 Supply Steam Bypass


Stop Valve 6 10000 Valve will be driven into full open end position See xxxxx-980294 chapter 3.4

Supply Steam Bypass



Failure mode volume flow to stop and control valve added 6) 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 between Load cycles

130bar (1885 PSI) and 160bar (2320 PSI)

The fatigue-strength under pulsating (oscillating, fluctuating) compressive stress must be guaranteed.

115bar (1668 PSI) and 160bar (2320 PSI) The load cycle of 10000 has to be considered.

0 bar (0 PSI) and 160bar (2320 PSI) The load cycle of 400 has to be 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.




4. PIPING DESIGN REQUIREMENTS

4.1 General requirements

Movement of the valves due to thermal expansion Due 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 control fluid pipes must have a short span between the valve and the first support due to the high forces of the pressure surge. However, due to the large movement of the valves there must be a certain distance between valve and first support to reduce the stress in the pipe. To fulfill both requirements vibration dampeners are necessary. This must be calculated in every case.

The following must be taken into consideration where calculating the thermal expansion of the connection points at the actuators: Main steam valve, Hot Reheat, Overload- and Intercept Steam Valve and Heat

Extraction Control valve The thermal expansion of the turbine, the steam valves itself and the adjoining pipes must be considered.

Bypass Valves The movement of the adjoining pipe and the movement of the condenser must be considered as well as the thermal expansion of the bypass valve itself.

LP Induction Valve If the valve is flanged at the turbine the thermal expansion of the turbine must be considered. If it part of the pipe, the movement of the pipe must be considered.

Start-Up and Safety Valve The movement of the adjoining pipe as well as the thermal expansion of the valve itself must be considered.

The pipes are pressure sensitive lines. Therefore the allowable pipe pressure drop is limited. The maximum allowable pressure drop values are: 5 bar for pressure pipes 2,5 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 reasonable temperature 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 and material, the piping must be supported by means of dampers and guides wherever there is a hazard that vibrations can arise.

!




Since it is not possible to anticipate if vibrations occur during the piping design, it is required that the piping will be checked during commissioning. Special attention must be paid 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 in the turbine building is expected to be at or below 5C (41F), the piping and the actuators must be provided with insulation and trace heating. Installation of trace heating systems is specified for 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 installed without thermal 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 not exceed 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 trace heating system, the closing function is then no longer assured for turbine valve actuators. Load rejection may then result in turbine overspeed with consequential catastrophic failure of the rotor. To reduce the hazard potential commensurately, appropriate protection circuits must be installed. These serve to close the affected valves before temperatures have fallen below safe temperature levels. 4.3 I&C measures for steam turbines

In case standards on Functional Safety apply (IEC61508, IEC61511, ISA S84.01, ....) the following description of I&C measures has to be completed by analysis, specification and validation measures as described in these standards.

4.3.1 Steam turbine with two or more valve combinations (stop and control valve) per expansion range

A 1-out-of-2 temperature protection circuit (with monitoring of the trace heating)must be installed 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 causes response of this circuit and closure of this valve combination by initiation of individual trip in




good time (before control fluid temperature in the return line falls below a safe level: alarm signal issue at temperature below/equal to 10C (below/equal to 50F), trip signal issue at temperature below/equal to 8C (below/equal to 46F ) ).

Temperature measurement (clamping strap elements) for this temperature protection circuit 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 failure percentage 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-2 temperature protection circuit on both the stop valve actuator and the control valve actuator for configurations that feature two separate trace heating systems (for the stop valve and for the control valve). The associated temperature instrumentation must be installed on the operating cylinder (see diagram 1). In the event that a common trace heating system is implemented for the two actuators, a common additional 1-out-of-2 temperature protection circuit 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 the two LP (induction) steam valve actuators, a common additional 1-out-of-2 temperature protection circuit on the return line is then adequate. Temperature measurement for this temperature protection circuit 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.

To rule out control fluid degradation in the event of excess temperatures, alarms are derived from the separate temperature measurements in response to T> 70C (158F) in the 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 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).

Control Oil Piping Design Steam Turbine Information Manual Document No.: STIM-03.006 Revision/Date: 13 2009-02-02 Page: 13 of 17



Steam Turbine ProtectionScope of PG S

TemperatureProtection

From outside scopeof supplynot PG S

1 oo 2

Warningtemperature

protection circle

MP 4MP 1 MP 5MP 2

noncoincidencewarning

CentralControlRoom

trip oflow pressure

valvecombination

individual control of the5 valve combinations

2 out of 2for each protection circle with

noncoincidence monitoring

1 oo 2 1 oo 21 oo 2

>=1

2 Trip-Signals for each protection circlenormally energized

CONCEPT TEMPERATURE PROTECTION TRACE HEATING SYSTEMTurbine with two valve combinations (stop and control valve) per expansion range

2 out of 2 TRIP SIGNALSUPDATE: S32M3

Havemann17.07.2004

P P PPP

P PP P

T T T

TT

PT100 resistancethermometer

surface mounted

MP 1

Legend:

MP measuring-point

MP 2

MP 3

MP 4 MP 5

sensor 1sensor 2

protection circle MP3, MP6and MP7 depending from

trace heating line

MP 7MP 6


surface mounted


surface mounted


surface mounted


surface mounted


surface mountedMP 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 1 oo 2

trip ofhigh pressure

valvecombination 1

trip ofhigh pressure

valvecombination 2

trip ofintermediate

pressurevalve

combination 1

trip ofintermediate

pressurevalve

combination 2




4.3.2 Steam turbines with one valve combination (stop and control valve) per expansion

range

A 1-out-of-2 temperature protection circuit (with monitoring of the trace heating) must be installed 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 causes response of this circuit (before control fluid temperature in the return line falls below a safe level: alarm signal issue at temperature below/equal to 10C (below/equal to 50F), trip signal issue at temperature below/equal to 8C (below/equal to 46F ) ).

Temperature measurement (clamping strap elements) for this temperature protection circuit 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 failure percentage 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-2 temperature protection circuit on both the stop valve actuator and the control valve actuator for configurations that feature two separate trace heating systems (for the stop valve and for the control valve). The associated temperature instrumentation must be installed on the operating cylinder (see diagram 1). In the event that a common trace heating system is implemented for the two actuators, a common additional 1-out-of-2 temperature protection circuit 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 the two LP (induction) steam valve actuators, a common additional 1-out-of-2 temperature protection circuit on the return line is then adequate. To rule out control fluid degradation in the event of excess temperatures, alarms are derived from the separate temperature measurements in response to T> 70C (158F) in the 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) steam valve combination. 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.




Diagram 1




UPDATE: PG S32M3Havemann17.07.2004

Steam Turbine ProtectionScope of PG S

protection circle MP3, MP4and MP5 depending from

trace heating line

2 out of 2for each protection circle with

noncoincidence monitoring

TemperatureProtection

From outside scopeof supplynot PG S

1 oo 2

2 Trip-Signals for each protection circlenormally energized

O.K.-Signals

Freeze Protection Units

Warningtemperature

protection circle

MP 2MP 1MP 5MP 4

noncoincidencewarning

CentralControlRoom

trip oflow pressure

valve combination

individual control of the3 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


surface mounted


surface mounted


surface mounted

P

sensor 1sensor 2

trip ofsteam turbine

1 oo 2 1 oo 21 oo 21 oo 2

>=1 >=1

PT100 resistance thermometersurface mounted

MP4 and 5 depending fromtrace heating line




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 and Transmittal Drawings.

5.2 Welding

All welding must be per the requirements of ASME B31.1 or where required according VGB R503 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 hydrostatic pressure 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)

Documents

STIM-03.006-R14_CONTROL_FLUID_PIPING_DESIGN.pdf