CA2270672C - Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system - Google Patents

Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system Download PDF

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Publication number
CA2270672C
CA2270672C CA002270672A CA2270672A CA2270672C CA 2270672 C CA2270672 C CA 2270672C CA 002270672 A CA002270672 A CA 002270672A CA 2270672 A CA2270672 A CA 2270672A CA 2270672 C CA2270672 C CA 2270672C
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Prior art keywords
fuel
air
oil
fuel oil
piping
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CA002270672A
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French (fr)
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CA2270672A1 (en
Inventor
Yukimasa Nakamoto
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Priority claimed from JP12603998A external-priority patent/JPH11324720A/en
Priority claimed from JP12604098A external-priority patent/JPH11324718A/en
Priority claimed from JP12734798A external-priority patent/JPH11324721A/en
Priority claimed from JP12893898A external-priority patent/JPH11324722A/en
Priority to CA002357492A priority Critical patent/CA2357492C/en
Priority to CA002357555A priority patent/CA2357555C/en
Priority to CA002357553A priority patent/CA2357553C/en
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to CA002357493A priority patent/CA2357493C/en
Publication of CA2270672A1 publication Critical patent/CA2270672A1/en
Publication of CA2270672C publication Critical patent/CA2270672C/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22Fuel supply systems
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01DNON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/002Cleaning of turbomachines
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/20Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products
    • F02C3/22Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products the fuel or oxidant being gaseous at standard temperature and pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/20Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products
    • F02C3/24Gas-turbine plants characterised by the use of combustion products as the working fluid using a special fuel, oxidant, or dilution fluid to generate the combustion products the fuel or oxidant being liquid at standard temperature and pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/22Fuel supply systems
    • F02C7/232Fuel valves; Draining valves or systems
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02CGAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/26Control of fuel supply
    • F02C9/40Control of fuel supply specially adapted to the use of a special fuel or a plurality of fuels
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05DINDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00Function
    • F05D2260/60Fluid transfer
    • F05D2260/602Drainage

Abstract

Plurality of fuel nozzles X1 and X2 in combustor X
are supplied with fuel gas from fuel gas system and fuel oil from fuel oil system, respectively. Gas turbine operation is done with fuel being changed over to either gas or oil.
Fuel oil distribution control system A controls oil flowing into plurality of fuel pipings. When oil is changed over to gas, fuel oil purge system B is supplied with air of appropriate temperature and pressure from purging air supply system C. This air flows into fuel oil pipings and nozzles X2 for purging residual oil therein. Fuel nozzle wash system D is supplied with water by-passing from wash water tank for compressor washing. This water flows through nozzles X2 for washing thereof.

Description

SPECIFICATION
GAS TURBINE FUEL SYSTEM COMPRISING FUEL OIL DISTRIBUTION
CONTROL SYSTEM, FUEL OIL PURGE SYSTEM, PURGING AIR SUPPLY
SYSTEM AND FUEL NOZZLE WASH SYSTEM
BACKGROUND OF THE INVENTION:
Field of the Invention:
The present invention relates generally to a gas turbine fuel system and more specifically to a gas turbine fuel system comprising a fuel oil distribution control system, a fuel oil purge system, a purging air supply system and a fuel nozzle wash system in which fuel oil distribution is controlled to. be done uniformly to a plurality of fuel nozzles with enhanced reliability of fuel distribution and residual oil in fuel pipings and nozzles when gas turbine operation is changed over to gas fuel from oil fuel is purged effectively so that load change caused by burning of the residual oil at the time of purging is prevented.
Description of the Prior Art:
Fig. 9 is a block diagram of an entire gas turbine fuel system comprising therein a fuel oil supply system, a fuel oil purge system, a purging air supply system and a compressor outlet wash system in the prior art. In Fig. 9, a combustor X comprises therein a plurality, about 20 pieces for example, of fuel nozzles X1, X2 disposed along an inner periphery thereof .
The fuel nozzles X1 are supplied with fuel gas from a fuel gas supply system and the fuel nozzles XZ are supplied with fuel oil from a fuel oil supply system G. These gas and oil are changed over to either one thereof to be supplied into the combustor X for combustion. The fuel oil supply system G, as mentioned, is a system for supplying therethrough fuel oil and a fuel oil purge system H is a system for purging oil remaining in the piping system or fuel nozzles when the fuel is changed over to gas from oil. A purging air supply system J supplies therethrough a purging air into the fuel oil purge system H.
A compressor outlet wash system K is a system for injecting water into a compressor outlet for washing this compressor outlet which communicates with the combustor. Description will be made further on each of the above systems.
The fuel oil supply system G will be described first.
In the gas turbine, a stable combustion is required for a wide range of fuel flow rate from ignition to power output.
Especially, in the low fuel flow rate range at the time of ignition etc. , there is only a small differential pressure of the fuel nozzles in the combustor, which results in an unstable combustion. In the recent gas turbine, there are provided a large number of fuel nozzles of about 20 pieces and there arises unbalance in the fuel flow rate by the influence of head difference between upper ones and lower ones of the fuel nozzles which are disposed up and down. For this reason, a flow divider is provided so that fuel is divided to be supplied uniformly to each of the fuel nozzles. But this flow divider is not necessarily of a sufficient reliability and thereby often caused are troubles in the fuel system.
Fig. 10 is a diagrammatic view of the fuel oil supply system G in the prior art. In Fig. 10, fuel oil is controlled of flow rate by a flow control valve 11 to then flow through a piping 12 and enters a flow divider 80 to be divided there to flow through a plurality of pipings 82 of about 20 pieces and to be supplied into each of the fuel nozzles X2 of the combustor X. The gas turbine fuel nozzles XZ are disposed in about 20 pieces along a circumference and there is a head difference of about 4 m between the nozzles of upper position and those of lower position. This head difference produces unbalance in the fuel flow rate, especially in the low fuel flow rate range at the time of ignition. For this reason, the flow divider 80 is provided but this flow divider 80 is constructed such that a spiral shaft is disposed in a cylindrical body and while this shaft is rotated, fuel oil is flown into the cylindrical body to be divided to flow through each of the plurality of pipings 82 uniformly. A motor 81 is operated only in the operation start time for ensuring a smooth start of rotation of the flow divider 80.
Fig. 11 is a view showing relation between load transition (fuel flow rate) and system differential pressure in the prior art gas turbine, wherein as load increases, fuel flow rate increases from gas turbine ignition time to to rated speed ( no load ) arrival time tl and further to time t2 when the system differential pressure including nozzle differential pressure comes to a necessary nozzle differential pressure V1.
That is, during the time T from to to t2, the system differential pressure does not reach the necessary nozzle differential pressure V1 but it reaches V1 at time tz to increase more thereafter. Accordingly, the nozzle differential pressure is low during the time shown by T and if there is a head difference between said plurality of fuel nozzles, there occurs unbalance of fuel flow rate between each of the fuel nozzles, hence the flow divider 80 is operated so that the unbalance of the fuel oil between each of the fuel nozzles may be eliminated. But this flow divider 80 has a very small gap between the inner rotational body and the stationary portion for its function and this makes control of foreign matters difficult and has been often causes of troubles in the fuel system.
Next, the fuel oil purge system H will be described.
Fig. 12 is a diagrammatic view of the fuel oil purge system in the prior art at the time when the gas turbine fuel is changed over. In Fig. 12, numeral 1 designates a flow control valve in a fuel gas system, numeral 2 designates a piping therefor, numeral 3 designates a fuel gas distributor, which distributes the fuel gas to the plurality of fuel nozzles X1 and numeral 4 designates a plurality of pipings, which supply therethrough the fuel gas from the fuel gas distributor 3 to the respective fuel nozzles X1.
Numeral 11 designates a flow control valve in a fuel oil system, numeral 12 designates a piping therefor, numeral 13 designates a header, which distributes the fuel oil from the piping 12 to the plurality of fuel nozzles XZ and numeral 14 designates a plurality of pipings, which are connected to the header 13 and supply therethrough the fuel oil distributed by the header 13 to the respective fuel nozzles X2. Numeral 26 designates a purging air system piping, numeral 25 designates an opening/closing valve, numeral 23 designates a drain valve piping and numeral 24 designates an opening/closing valve therefor. Combustor X comprises therein the fuel nozzles X1, X2.
In the mentioned system so constructed, while the operation is done with the fuel oil being burned, the fuel oil flowing through the flow control valve 11 and the piping 12 is distributed by the header 13 to flow through the plurality of pipings 14 to the respective fuel nozzles X2. The fuel oil so distributed is injected into the combustor X from the fuel nozzles Xz for combustion there.
When the operation is done with the fuel being changed over to gas from oil, the flow control valve 11 is closed and the fuel gas is led instead into the piping 2 to be supplied to the fuel nozzles X1 through the fuel gas distributor 3 and the piping 4. In this case, the previous fuel oil remains as it is in the pipings 12, 14 and this fuel oil, if left there, is carbonized to stick there with a fear to cause blockage of the pipings and nozzles . Hence, it is necessary to remove such residual oil when the fuel is changed over to gas.
Thus, the opening/closing valve 25 is opened so that purging air 40 is led into the piping 12 from the purging air system piping 26. The purging air 40 enters the header 13 through the piping 12 to then flow through the pipings 14 to the fuel nozzles XZ to be blown into the combustor X. Thereby, the fuel oil which remains in the piping 12 , header 13 , pipings 14 and fuel nozzles Xz is all discharged into the combustor X.
This purging of the residual oil is done while the operation is continued with the fuel gas being supplied and burned in the combustor X. But there is a considerable quantity of such residual oil itself in the piping 12, header 13, pipings 14 and fuel nozzles XZ and also there are provided a large number of the fuel nozzles X2 and same number of the pipings 14 connected to the respective fuel nozzles X2. Accordingly, if the residual oil in these portions is all discharged into the combustor X
and the operation is continued with the fuel gas so changed over, then the fuel oil so discharged into the combustor X burns so that the fuel increases beyond a planned supply value, which elevates combustion temperature to cause a large load change.
Hence, realization of a fuel oil purge system which does not cause such a load change has long been desired.
Next, the purging air supply system ,T will be described. In the recent gas turbine, there is realized an operation system wherein fuel is changed over to gas from oil, as mentioned above. This operation system comprises therein both of fuel oil system and fuel gas system and it is necessary to purge fuel pipings and nozzles on the side not used.
Especially in the fuel oil system, oil remains in the pipings and, if left as it is, is carbonized to stick there and there is a fear of blockage of the pipings and nozzles.
Fig. 13 is a diagrammatic view of the purging air supply system J in the prior art gas turbine. In Fig. 13, numeral 110 designates a gas turbine, numeral 42 designates a piping for taking out therethrough outlet air of air compressor and numeral 90 designates an air cooler, which comprises therein a multiplicity of tubes communicating with the piping 42. Numeral 91 designates a motor for rotating a fan 92 to thereby supply air to the air cooler 90 and numeral 43 designates a piping connecting to outlet of the air cooler 90.
Numeral 93 designates also a piping, which diverges from the piping 42 for obtaining air of the purge system and numeral 94 designates a cooler using water 95 for cooling the air from the piping 93. Numeral 96 designates a piping connected to outlet of the cooler 94, numeral_97 designates a drain separator, numeral 98 designates a piping connected to outlet of the drain separator 97, numeral 53 designates a pressure elevation compressor and numeral 99 designates a piping connected to outlet of the pressure elevation compressor 53. Numeral 100 designates a cooling using water 101 for cooling the air which has been heated to a high temperature by pressure elevation at the pressure elevation compressor 53 to an appropriate temperature as a fuel nozzle purging air. Numeral 48 designates a piping for supplying therethrough the air which has been cooled to the appropriate temperature as the purging air at the cooler 100.
In the mentioned system so constructed, the air of the compressor outlet of about 400°C is cooled at the air cooler 90 to about 200 to 250°C to be supplied into the gas turbine 110 as a rotor cooling air through the piping 43, wherein a portion of the air of the compressor outlet diverges from the piping 42 and is led into the cooler 94 through the piping 93 to be cooled to about 130°C to be then sent to inlet of the pressure elevation compressor 53. This air is removed of drain by the drain separator 97 disposed between the pipings 96 and 98. Then, the air is compressed to a predetermined pressure at the pressure elevation compressor 53 and its temperature is also elevated to about 200°C. This air of about 200°C is led into the cooler 100 through the piping 99 to be cooled there _ g _ to about 150°C which is appropriate for the purging and is then supplied to each of the fuel systems through the piping 48 as the purging air.
Thus, in the purging air supply system, as the inlet temperature of the pressure elevation compressor 53 becomes high, there is provided the cooler 94 for cooling the compressor outlet air of about 400°C to about 100 to 130°C. Also, as the air, when compressed at the pressure elevation compressor 53, is heated to about 200°C, it is cooled again at the cooler 100 to about 150°C. In this kind of system, therefore, there are needed the coolers 94, 100 or the like, which requires large facilities and spaces therefor. Hence, it has been needed to improve these shortcomings and to attain cost reduction.
Next, the compressor outlet washing system K will be described. Fig. 14 is a diagrammatic view of the compressor outlet wash system in the prior art. In Fig. 14, letter X
designates a combustor, numeral 112 designates a compressor outlet and numeral 113 designates a manifold for distributing wash water in an annular form, as described later. Numeral 114 designates a plurality of wash nozzles, which are provided along periphery of the manifold 113 for injecting therefrom wash water into the compressor outlet 112. Numeral 11 designates a flow control valve for fuel oil, numeral 12 designates a piping and numeral 13 designates a header for distributing fuel into a plurality of fuel supply pipings 14.
_ 9 Fuel oil is supplied from the respective fuel supply pipings 14 to a plurality of fuel nozzles Xz.
Numeral 60 designates an air control valve for leading a high pressure air into a wash tank 62 via a piping 61. The wash tank 62 stores therein the wash water for washing interior of the compressor outlet 112. Numeral 63 designates an opening/closing valve, through which the wash water flows to be supplied into the manifold 113 via a piping 64. The wash water supplied into the manifold 113 is injected from the plurality of wash nozzles 114 into the surrounding area for washing the interior of the compressor outlet 112. Numeral 65 designates an opening/closing valve and numeral 66 designates a piping for supplying therethrough the wash water in a necessary quantity into the wash tank 62.
In the gas turbine compressor outlet wash system so constructed, when the compressor outlet 112 is to be washed, the air control valve 60 is opened and the high pressure air is led into the wash tank 62 via the piping 61 so that interior of the wash tank 62 is pressurized. Then, the opening/closing valve 13 is opened and the wash water is supplied into the manifold 113 via the piping 64. The wash water is injected from the wash nozzles 114 for washing the interior of the compressor outlet 112.
On the other hand, as for the gas turbine operation, fuel oil is led into the header 13 via the flow control valve 11 and the piping 12 to be distributed there to flow into the plurality of fuel supply pipings 14 uniformly and is then supplied into the respective fuel nozzles XZ for combustion.
In the recent gas turbine, there is developed a dual fuel system in which both fuel oil and fuel gas are usable and the fuel is changed over to gas from oil, or to oil from gas, as the case may be. In such a system, if, for example, the operation done by oil is stopped or is continued with the fuel being changed over to gas from oil, the fuel oil remaining in the fuel pipings and nozzles is carbonized to stick there and there arises a fear of blockage of the fuel pipings and nozzles .
Thus, attempt is being done for providing large scale facilities by which the fuel pipings and nozzles are purged by air or the like. But these exclusive purging facilities require a large apparatus, which are naturally undesirable from viewpoint of cost reduction.
SUMMARY OF THE INVENTION:
In view of the problems in the prior art gas turbine fuel system, it is a principal object of the present invention to provide a gas turbine fuel system comprising a fuel oil supply system and a fuel gas supply system so that gas turbine operation may be done with fuel being changed over to either oil or gas and further comprising a control system in which fuel is distributed to each fuel piping of said fuel oil supply system uniformly in an appropriate flow rate and pressure as well as a purge system in which, while gas turbine operation is done with gas fuel, residual oil in said fuel oil supply system is purged effectively by air or water so that said residual oil may not be carbonized.
In order to provide said gas turbine fuel system, the present invention has objects to provide following first to fourth systems:
First one is a gas turbine fuel oil distribution control system in which a control valve is employed instead of a flow divider, said control valve being constructed such that differential pressure of each fuel nozzle is elevated at the initial time of gas turbine operation, as well as fuel oil is distributed so as to flow into each of fuel pipings connected to fuel nozzles as uniformly as possible so that unbalance in fuel oil flow rate caused by head difference between each fuel nozzle is dissolved and unusual elevation of the differential pressure at the time of high fuel flow rate is prevented.
Second one is a gas turbine fuel oil purge system in which, when gas turbine operation is done with fuel being changed over to gas from oil and residual oil in fuel pipings and nozzles is to be purged, quantity of the residual oil to be discharged into a combustor is made as small as possible as well as the residual oil is purged securely to be discharged.
Third one is a gas turbine fuel nozzle purging air supply system in which compressor outlet air of about 400°c is cooled at a rotor cooling air cooler to an appropriate temperature to enter a pressure elevation compressor, thereby some of coolers are made unnecessary so that construction of the purging air supply system is simplified, installation space thereof is reduced and cost of facilities is reduced.
Fourth one is a gas turbine fuel nozzle wash system in which existing gas turbine facilities may be used to be modified with a simple construction so that, when fuel is changed over to gas from oil, fuel nozzles are washed by water and residual oil in the fuel nozzles is washed out, resulting in contribution to cost reduction of the gas turbine plant.
In order to realize said objects, the present invention provides means of following (1) to (5):
( 1 ) A gas turbine fuel system comprising a fuel oil supply system for supplying fuel oil to a plurality of fuel nozzles and a fuel gas supply system for supplying fuel gas to said plurality of fuel nozzles so that gas turbine operation may be done with fuel being changed over to either one of oil and gas, characterized in further comprising a fuel oil distribution control system for controlling flow rate and pressure of fuel oil in each of fuel pipings connecting to said fuel nozzles within a predetermined range by a control means provided in said fuel oil supply system; a fuel oil purge system provided close to said fuel nozzles in said fuel oil supply system for purging residual oil in said fuel oil supply system and fuel nozzles by air; a purging air supply system for supplying air to said fuel oil purge system; and a fuel nozzle wash system for supplying wash water to upstream side of said fuel nozzles in said fuel oil supply system connected to said fuel nozzles.
In the invention of (1) above, the fuel oil distribution control system causes fuel oil to flow into the fuel oil supply system uniformly so that unbalance in the fuel flow rate in each of the pipings is dissolved and the fuel oil purge system purges effectively the residual oil in the fuel oil supply system and fuel nozzles so that the problem of pipings being blocked by carbonization of the fuel oil is dissolved. Also, the purging air supply system supplies air of appropriate temperature into the purge system so that air supply to the purge system is ensured. Further, the fuel nozzle wash system purges the residual oil by injecting water so that reliability of purging the residual oil is enhanced. Said air purge and water purge may be done by either of them being changed over to one from the other as the case may be.
(2) A gas turbine fuel oil distribution control system, characterized in that there are provided a series control valve comprising a plurality of valves for controlling pressure loss in a fuel oil supply system so as to correspond to a plurality of fuel nozzles, each of said plurality of valves being driven controllably at same time with same opening; a drive unit for driving said series control valve; and a control unit for controlling said drive unit, and said control unit is inputted with a system differential pressure signal and a load signal of said fuel oil supply system to put out to said drive unit a signal to throttle said series control valve approximately to an intermediate opening while the system differential pressure is a predetermined low differential pressure and a signal to open said series control valve fully for a predetermined time when said system differential pressure comes to a predetermined high differential pressure.
In the gas turbine fuel oil distribution control system of the invention of ( 2 ) above, while the series control valve is controlled of the opening by the control unit and the drive unit, the control unit is inputted with differential pressure signal and load signal of the fuel oil supply system or the fuel nozzles to put out to the drive unit a signal to throttle the series control valve approximately to an intermediate opening while the system differential pressure is a predetermined low differential pressure during the time from gas turbine ignition to rated speed arrival. In the high fuel flow rate area, when the system differential pressure comes to a predetermined high differential pressure, a signal to open the series control valve fully is put out to the drive unit.
Thus, the differential pressure each of the fuel nozzles is set to a higher differential pressure than the necessary nozzle differential pressure by the series control valve and the gas turbine operation is done with the fuel oil being so controlled that unbalance in the fuel flow rate as so far occurred in the low fuel flow rate area is reduced, hence the prior art flow divider becomes unnecessary and reliability of the fuel oil distribution is enhanced.
(3) A gas turbine fuel oil purge system in a gas turbine fuel oil supply system comprising a plurality of fuel oil supply pipings for supplying fuel oil to a plurality of fuel nozzles via a header; and a drain piping connected to said plurality of fuel oil supply pipings, characterized in that there are provided a sealing connection pipe close to said fuel nozzles in each of said fuel oil supply pipings between said header and fuel nozzles; and a purging air supply piping for supplying air to each said sealing connection pipe, and each said sealing connection pipe causes the air from said purging air supply piping to flow toward said fuel nozzles as well as to flow into said fuel oil supply pipings on the opposite side of said fuel nozzles to be discharged from said drain piping.
In the gas turbine fuel oil purge system of the invention of (3) above, the sealing connection pipe and the purging air supply piping are provided close to the fuel nozzles in each of the fuel oil supply pipings and air from the sealing connection pipe is injected from each.of the fuel nozzles so that the residual oil only in the very short piping between the sealing connection pipe and each of the fuel nozzles is discharged into the combustor. At the same time, the combustion gas in the combustor is prevented from flowing reversely into the fuel oil supply pipings by the air injected from the fuel nozzles, hence the air so injected has a function of sealing as well.
At the same time of said sealing function, the air also flows from the sealing connection pipe into the fuel oil supply pipings on the opposite side of the fuel nozzles and after flowing through the fuel oil supply pipings and the drain piping, it is discharged outside of the system. By this flow of air, all the residual oil in the fuel oil supply pipings is discharged outside of the system from the drain piping.
According to the invention of (3) above, therefore, when the fuel is changed over to gas from oil and the residual oil in the pipings is to be purged, the residual oil to be injected into the combustor is only the residual oil in the very short piping close to the fuel nozzles and other residual oil is discharged outside of the system from the drain piping, hence load change caused by burning of the residual oil is reduced.
(4) A gas turbine fuel nozzle purging air supply system in a gas turbine air system for supplying air, extracted from compressor outlet air and cooled at an air cooler, to a rotor as rotor cooling air as well as for supplying air, diverging from said air extracted from compressor outlet air and being elevated of pressure at a pressure elevation compressor, to be used as fuel nozzle purging air, characterized in that said air cooler comprises a first cooler and a second cooler, air cooled at said first cooler is used for said rotor cooling air and air diverging from the air cooled at said first cooler is sent to said second cooler to be cooled and then sent to said pressure elevation compressor.
In the gas turbine fuel nozzle purging air supply system of the invention of ( 4 ) above, the air cooler comprises the first and second coolers and the air cooled at the first cooler is used as the rotor cooling air to be supplied for rotor cooling. Further, a portion of the air cooled at the first cooler diverges to enter the second cooler to be cooled again, thus the compressor outlet air is cooled to a lower temperature and is led into the pressure elevation compressor. When the air is compressed to a higher pressure at the pressure elevation compressor, its temperature also is elevated, but as the air at the pressure elevation compressor inlet is cooled enough to the lower temperature at the first and second coolers, even if it is elevated of temperature, it can be used as the fuel nozzle purging air without being cooled further.
In the prior art system, air extracted from the compressor outlet air is cooled at a separate cooler and is led into the pressure elevation compressor to be compressed and thus to be elevated of temperature. This air so elevated of temperature is cooled again at another separate cooler to be adjusted to a lower temperature which is appropriate for the purging air. In the prior art system, therefore, separate coolers are needed and large facilities and space therefor are required. But in the invention of (4) above, the air cooler for the rotor cooling air is made in two units which are used for cooling the purging air as well, separate coolers are not needed, facilities are simplified and cost reduction is attained.
(5) A gas turbine fuel nozzle wash system in a gas turbine wash system comprising a fuel oil supply system for supplying fuel oil to fuel nozzles in a combustor; a compressor wash water supply system for supplying wash water to a compressor which supplies compressed air to said combustor; and a wash water tank for supplying the wash water to said compressor wash water supply system, characterized in that there are provided a wash water by-pass piping and an opening/closing valve between said fuel oil supply system and compressor wash water supply system and when said opening/
closing valve is opened, the wash water is supplied to said fuel nozzles from said wash water tank via said fuel oil supply system to be injected from said fuel nozzles so that said fuel nozzles are washable.
In the gas turbine fuel nozzle wash system of the invention of ( 5 j above, the wash water by-pass piping and the opening/closing valve are provided between the existing fuel oil supply system and compressor outlet wash system so that the wash water for compressor washing in the wash water tank is led into the fuel oil supply system. When the fuel is changed over to gas from oil, the oil remains in the fuel nozzles and is carbonized to stick there, which results in a fear of blockage of the fuel nozzles . Hence, when the fuel is changed over to gas, wash water for the compressor washing is led to the fuel nozzles via the wash water by-pass piping and fuel oil supply system to be injected from the fuel nozzles, thus the fuel nozzles are washed and fear of blockage of the nozzles is cleared. Accordingly, the existing pipings are made use of and wash water for the compressor washing is used for nozzle washing as well, thereby facilities cost is reduced and washing of the fuel nozzles with simple structure becomes possible.
BRIEF DESCRIPTION OF THE DRAWINGS:
Fig. 1 is a block diagram of an entire gas turbine fuel system comprising a fuel oil distribution control system, a fuel oil purge system, a purging air supply system and a fuel nozzle wash system of one embodiment according to the present invention.
Fig. 2 is a diagrammatic view of the fuel oil distribution control system of Fig. 1.

Fig. 3 is a view showing relation between load transition (fuel flow rate) and system differential pressure in the fuel oil distribution control system of Fig. 1.
Fig. 4 is a diagrammatic view of the fuel oil purge system of Fig. 1.
Fig. 5 is a diagrammatic view of the purging air supply system of Fig. 1.
Fig. 6 is a diagrammatic view of the fuel nozzle wash system of Fig. 1.
Fig. 7 is a diagrammatic view showing one application example of the fuel nozzle wash system of Fig. 6.
Fig. 8 is a diagrammatic view showing another application example of the fuel nozzle wash system of Fig. 6.
Fig. 9 is a block diagram of an entire gas turbine fuel system comprising a fuel oil supply system, a fuel oil purge system, a purging air supply system and a compressor outlet wash system in the prior art.
Fig. 10 is a diagrammatic view of the fuel oil supply system of Fig. 9.
Fig. 11 is a view showing relation between load transition (fuel flow rate) and system differential pressure in the fuel oil supply system of Fig. 9.
Fig. 12 is a diagrammatic view of the fuel oil purge system of Fig. 9.
Fig. 13 is a diagrammatic view of the purging air supply system of Fig. 9.
Fig. 14 is a diagrammatic view of the compressor outlet wash system of Fig. 9.
DESCRIPTION OF THE PREFERRED EMBODIMENTS:
Herebelow, description will be made concretely on embodiments according to the present invention with reference to figures. Fig. 1 is a block diagram of an entire gas turbine fuel system comprising therein a fuel oil distribution control system, a fuel oil purge system, a purging air supply system and a fuel nozzle wash system of one embodiment according to the present invention. Fig. l is a view of block diagram in contrast with that in the prior art of Fig. 9.
In Fig. 1, there are provided in a combustor X a plurality of fuel nozzles X1 and X2, respectively, and like in the prior art, fuel nozzles X1 and supplied with fuel gas from a fuel gas supply system and fuel nozzles Xz are supplied with fuel oil from a fuel oil supply system. Letter A designates a fuel oil distribution control system, which corresponds to the fuel oil supply system G of Fig. 9. Letter B designates a fuel oil purge system, which corresponds to the fuel oil purge system H of Fig. 9, letter C designates a purging air supply system, which corresponds to the purging air supply system J
of Fig. 9, and letter D designates a fuel nozzle wash system, which corresponds to the compressor outlet wash system K of Fig. 9. Letters E, F designates selector valves, respectively, wherein in case of air purge, the valve E is opened and the valve F is closed and in case of water purge, the valve E is closed and the valve F is opened, reversely, and purging may be done by either one of the air purge and the water purge or by combination thereof in which the water purge is done first and then the air purge is done.
Description will be made below on each of the mentioned systems. Fig. 2 is a diagrammatic view of the fuel oil distribution control system A of Fig. 1, which is a view of the system in contrast with that in the prior art of Fig.
10. In Fig. 2, parts having same functions as those of the prior art shown in Fig. 10 are given same reference letters or numerals with description thereon being omitted and characteristic portions of the present invention, that is, portions 10 to 14, 20 and 21, will be described in detail.
In Fig. 2, numeral 13 designates a header and numeral 14 designates a plurality of pipings connecting to the header 13. Numeral 10 designates a series control valve, which has a series of control valves in same number of pieces as that of the fuel nozzles X2 so that each of the valves is controlled at same time with same opening, that is, if the number of the fuel nozzles X2 is 20 for example, the series control valve 10 is a 20 series control valve. While illustration of the structure of the series control valve 10 is omitted, it is for example such that each of the valves is linked by a link mechanism such as a cylinder and opening of the valves is controlled simultaneously.
Numeral 21 designates a drive unit, which controls opening of the series control valve 10 simultaneously, as mentioned above, and comprises a hydraulic or pneumatic cylinder or an electromotive cylinder or the like. Numeral 20 designates a control unit, which puts out an output signal to the drive unit 21 so that opening of the series control valve 10 may be controlled, as described later.
In the construction as mentioned above, fuel-oil passes through a flow control valve 11 and a piping 12 to be led into the header 13 and is then supplied into the respective pipings 14 whose number of pieces is same as that of the fuel nozzles XZ. The respective pipings 14 connect to the respective valves of the series control valve 10 and the fuel oil is supplied through the series control valve 10 and pipings 15 to the respective fuel nozzles XZ for combustion in the combustor X.
The series control valve 10 is controlled of the valve opening via the drive unit 21 by signal from the control unit 20, as described later, such that while a nozzle differential pressure is low, the opening is throttled to an intermediate opening and when the nozzle differential pressure increases in a high fuel flow rate area, the valve is opened fully to make flow resistance smaller, thus unusual elevation of the system differential pressure is prevented.
Fig. 3 is a view showing relation between load transition (fuel flow rate) and the system differential pressure in the fuel oil distribution control system A of Fig. 2. In Fig. 3, while the system differential pressure is lower than the necessary nozzle differential pressure Vl from time to when the gas turbine is ignited to time tl when it arrives at rated speed ( no load ) , the series control valve 10 is throttled to an intermediate opening so that the system differential pressure is elevated higher than the necessary nozzle differential pressure V1, which is shown by broken line in Fig. 3, as fuel flow rate increases.
At the time tl, the system differential pressure arrives at differential pressure V2 beyond which there may occur an unusually large differential pressure. Then, the series control valve 10 is opened fully to make flow resistance smaller and the system differential pressure is reduced rapidly.
Then, at time tl', the series control valve 10 is throttled again to an intermediate opening. After the time tl', the system differential pressure goes up again as the fuel flow rate increases and when it arrives at V2, the series control valve 10 is opened fully again and thereafter same is repeated so that control is done.
The system differential pressures V1, V2 are set in the control unit 20 to be stored and when the control unit 20 is inputted with gas turbine load signal and system differential pressure signal, it checks the respective system differential pressures at times to, tl and tl' in the load transition and when the ignition is done at to, signal to throttle the opening of the series control valve 10 is put out to the drive unit 21 so that the opening of the series, control valve 10 is throttled to an intermediate level and when the system differential pressure comes to V2, signal to open the series control valve 10 fully is put out to the drive unit 21 so that the valve is opened completely and same control is repeated thereafter.
According to the fuel oil distribution control system A as described above, opening of the series control valve 10 is controlled by the control unit 20 and the drive unit 21 so that while the system differential pressure is low for the time of low load after the ignition, opening of the series control valve 10 is throttled to elevate the system differential pressure and unbalance in the fuel flow rate due to head difference of the fuel nozzles is dissolved thereby and in the high fuel flow rate area, the valve is opened fully and unusual elevation of the system differential pressure is prevented thereby. Thus, there is needed no such a flow divider as in the prior art, fuel oil flow unbalance between each of the fuel nozzles is prevented securely and reliability is enhanced.

Next, the fuel oil purge system B will be described with reference to Fig. 4. In Fig. 4, parts shown by reference numerals or letters 1 to 4, 11 to 14, 23, X, X1 and Xz are same as those in the prior art shown in Fig. 12 with description thereon being omitted and characteristic portions of the present invention, that is, parts shown by reference numerals 30 to 33, will be described in detail.
In Fig. 4, numeral 30 designates a purging air system piping, numeral 31 designates an opening/closing valve, numeral 32 designates a plurality of sealing connection pipes and numeral 33 designates a plurality of pipings . Each of the pipings 33 connects at its one end to each of the fuel nozzles X~ and at its the other end to each of the sealing connection pipes 32 and length of each of the pipings 33 is made as shorter as possible preferably. Also, each of the sealing connection pipes 32 is a T type connection pipe which comprises ports connecting to the pipings 14 and 33 and the purging air system piping 30, respectively.
Thus, the purging air system piping 30 is connected closer to the fuel nozzles Xz, as compared with the prior art purging air system piping 26, between the header 13 and the fuel nozzles Xz, hence residual oil in the pipings to be discharged into the combustor X is reduced, as described later.
In the fuel oil purge system B constructed as above, while operation is done by fuel oil, the fuel oil passes through the flow control valve 11 and the piping 12 to enter the header 13 and is distributed there to flow through the plurality of pipings 14 and the sealing connection pipes 32 to be then supplied into the plurality of fuel nozzles XZ via the pipings 33 and is injected into the combustor X for combustion.
When operation is to be done with the fuel being changed over to gas from oil, the flow control valve 11 is closed and fuel gas is supplied instead through the flow control valve 1, piping 2, fuel gas distributor 3 and piping 4 to enter the respective fuel nozzles X1 to be burned in the combustor X. In this case, there remains the previous fuel oil in the piping 12, header 13, piping 14 and piping 33 and if this remaining fuel oil is left there as it is, it is carbonized to stick there, thus when the fuel oil has been stopped to be changed over to fuel gas, it is necessary to purge the remaining fuel oil while operation is being done by the fuel gas.
In case of the purging, the opening/closing valve 31 is opened first so that purging air 41 is led into the purging air system piping 30 to flow through one end each of the sealing connection pipes 32 and the piping 33 to enter the fuel nozzles XZ and is then injected into the combustor X from the fuel nozzles to be burned: At same time, the purging air 41 is also flown into the piping 14 through the other end each of the sealing connection pipes 32.
Further, the opening/closing valve 24 is also opened to communicate with the drain valve piping 23. Thus, the purging air 41 passes through the purging air system 30, sealing connection pipes 32 and pipings 14 and further through the header 13, piping 12, opening/closing valve 24 and drain valve piping 23 and is discharged outside. By said flow of the purging air 41, the fuel oil remaining in the pipings 33 is discharged into the combustor X and the fuel oil remaining in the pipings 14, header 13 and piping 12 on the opposite side is discharged outside of the system via the drain valve piping 23.
When the purging of the residual oil is to be done while the operation is being done with fuel gas, as the purging air 41 from the purging air system piping 30 flows through said one end each of the sealing connection pipes 32 toward the combustor X to be injected from the fuel nozzles XZ, the purging air 41 has a sealing function to prevent reverse flow of the combustion gas from the combustor X and in addition to this sealing function, the purging air 41 causes the residual oil in the pipings 14, header 13 and piping .12 on the opposite side of the sealing connection pipes 32 to be discharged outside of the system from the drain valve piping 23.
In the prior art case shown in Fig. 12, if the opening/closing valve 24 of the drain valve piping 23 is opened during the operation, there may arise a case that the combustion gas from the combustor X is sucked to flow reversely through the pipings 14, header 13 and piping 12 so that the residual oil in the pipings may burn by the high temperature combustion gas to damage the pipings, but in the system of the present invention, the purging air 41 is flown from the sealing connection pipes 32 toward the combustor X to be injected from the fuel nozzles XZ so as to seal the combustion gas, thus the shortcomings in the prior art is prevented.
According to the fuel oil purge system B as described above, the construction is made such that the purging air system piping 30 and the sealing connection pipes 32 are connected closer to the fuel nozzles XZ between the pipings 14 and the fuel nozzles XZ and the purging air 41 having the sealing function as well is injected from the fuel nozzles X2 so that the residual oil in the pipings 33 is discharged as well as the combustion gas from the combustor X is prevented from flowing reversely into the pipings 14 side.
Further, the purging air 41 from the sealing connection pipes 32 is flown through the pipings 14, header 13 and piping 12 to be discharged from the drain valve piping 23 so that the residual oil in these pipings is discharged outside of the system from the drain valve piping 23, thus when the fuel is changed over to gas from oil and residual oil in the pipings is to be purged, the residual oil to be discharged into the combustor X is only that remaining in the short pipings 33, thereby load change caused by combustion of the residual oil is reduced and a large load change is prevented.

Next, the purging air supply system C will be described with reference to Fig. 5. In Fig. 5, parts shown by reference numerals 110, 42, 43, 48 and 53 are same as those in the prior art shown in Fig. 13 with description thereon being omitted and characteristic portions of the present invention, that is, air coolers shown by reference numerals 50, 51 and pipings thereof as well as simplified system accompanied therewith, will be described in detail.
In Fig. 5, numeral 50 designates a first air cooler and numeral 51 designates a second air cooler. Both of the air coolers 50, 51 are cooled by air sent from a fan 45 driven by a motor 44. In these air coolers 50, 51, compressor outlet air is led into the first air cooler 50 via the piping 42 and the aid after cooled is led from outlet of the first air cooler 50 into the gas turbine 110 as rotor cooling air via the piping 43. At same time, a portion of the air at the outlet of the first air cooler 50 is extracted to be led into the second air cooler 51 via a piping 49.
The air cooled at the second air cooler 51 is led into a drain separator 52 via a piping 46 to be removed of drain and is then led into the pressure elevation compressor 53 via a piping 47 to be elevated of pressure and thereby to be heated to an appropriate temperature as purging air. Thus, this air is supplied as fuel nozzle purging air via the piping 48.
In the purging air supply system C constructed as above, the compressor outlet air is of about 400°C and is led into the first air cooler 50 via the piping 42 to be cooled to about 200 to 250°C by air sent from the fan 45 and is then supplied into the gas turbine 110 as the rotor cooling air like in the prior art.
The air cooled at the first air cooler 50 is of about 200 to 250°C and a portion thereof diverges into the piping 49 to enter the second air cooler 51. The air entering the second air cooler 51 is cooled, like in the first air cooler 50, by air from the fan 45 driven by the motor 44. The air so cooled is of about 60 to 80°C and is led into the drain separator 52 via the piping 46 to be removed of drain and then enters the pressure elevation compressor 53 via the piping 47 to be elevated of pressure and thereby to be elevated of temperature to about 100 to 130°C. This air of about 100 to 130°C is supplied to be used as the fuel nozzle purging air via the piping 48.
According to the purging air supply system C
described above, the air cooler for obtaining the rotor cooling air is constructed in two units of the first air cooler 50 and the second air cooler 51 and the compressor outlet air of about 400°C is cooled to about 200 to 250°C at the first air cooler 50 to be used as the rotor cooling air. At the second air cooler 51, the air so cooled to about 200 to 250°C is further cooled to about 60 to 80°C.
The air so cooled to about 60 to 80°C is used as inlet air of the pressure elevation compressor, hence the air after elevated of pressure is of temperature of about 100 to 130°C
which is appropriate as the fuel nozzle purging air. In the prior art case as shown in Fig. 13, the air entering the pressure elevation compressor 53, which is the compressor outlet air, is of a high temperature of about 400°C, hence it is cooled as first step to about 130°C at the cooler 94 and it is elevated of pressure at the pressure elevation compressor 53. But this air is thereby elevated of temperature to about 200°C, hence it is cooled again at the cooler 100 for obtaining air of about 150°C.
For this purpose, there are needed the coolers 94, 100 which are large facilities . But in the purging air supply system C of the present invention, the air cooler is made in two units of the first air cooler 50 for obtaining the rotor cooling air and the second air cooler 51 for obtaining the fuel nozzle purging air, thereby the coolers 94, 100 become unnecessary, which results in simplification of facilities, reduction of installation space and reduction of cost.
Finally, the fuel nozzle wash system D will be described with reference to Figs . 6 to 8 . In Figs . 6 to 8, same parts as those in the prior art shown in Fig. 14 are given same reference numerals or letters with description thereon being omitted and characteristic portions of the present invention, that is, portions shown by reference numerals 71 to 75, will be described in detail.
In Fig. 6, numeral 71 designates a by-pass piping, which connects to the upstream side of the opening/closing valve 63 so that wash water from the wash tank 62 flows therethrough to by-pass. Numeral 72 designates an opening/closing valve and numeral 73 designates a header for distributing the wash water. Numeral 74 designates a plurality of wash water supply pipings and numeral 75 designates a plurality of connection pipes which are connected to the respective fuel supply pipings 14.
The wash water led from the wash water tank 62 into the header 73 via the by-pass piping 71 is distributed to flow into the respective wash water supply pipings 74 and to further flow into the respective fuel supply pipings 14 via the connection pipes 75 and then enters the respective fuel nozzles XZ.
In the fuel nozzle wash system D constructed as above, when the fuel nozzles X2 are to be washed, the flow control valve 11 is closed, the opening/closing valve 63 is also closed, the opening/closing valve 72 is opened and the air control valve 60 is opened. Thus, high pressure air is led into the wash water tank 62 to pressurize the wash water in the tank so that the wash water is led into the header 13.
The wash water is distributed at the header 13 to flow into the respective wash water supply pipings and further to flow into the respective fuel supply pipings 14 via the connection pipes 75 and is then injected into the combustor X
from the respective fuel nozzles so that residual oil in the fuel nozzles XZ is washed and removed. The water containing the residual oil injected from the fuel nozzles X2 is so discharged into the combustor X and is vaporized by the high temperature there.
Fig. 7 is a diagrammatic view showing one application example of the fuel nozzle wash system D of the present invention. In Fig. 7, what is different from that shown in Fig.
6 is that the by-pass piping does not diverge from the piping 64 of the compressor wash system but is connected directly to the wash water tank 62 and the opening/closing valve 72 is provided in this by-pass piping 67, so that the fuel nozzle wash system is made in a separate system from the compressor wash system. Construction of other portions of Fig. 7 is same as that of Fig. 6. In the application example shown in Fig. 7 also, same function and effect of the invention as those of the wash system shown in Fig. 6 can be obtained.
Fig. 8 is a diagrammatic view showing another application example of the fuel nozzle wash system D of the present invention. In Fig. 8, what is different from that shown in Fig. 6 is that the by-pass piping is connected to the downstream side of the opening/closing valve 63 of the compressor wash system. In this system of Fig. 8, the compressor wash system and the fuel nozzle wash system are operated at same time by the single opening/closing valve 63, wherein the opening/closing valve 72 shown in Figs. 6 and 7 is eliminated. Construction of other portions of Fig. 8 is same as that of Figs . 6 and 7 . In the application example shown in Fig. 8 also, same function and effect of the invention as those of the wash system shown in Figs. 6 and 7 can be obtained.
According to the fuel nozzle wash systems D shown in Figs. 6_and 7, the construction is made such that there are provided the by-pass pipings 71, 67 for flowing therethrough the wash water from the wash water tank 62 of the compressor outlet wash system to by-pass and the wash water flows through the header 73, wash water supply pipings 74 and connection pipes 75 to the respective fuel supply pipings 14 and is then supplied into the fuel nozzles X2 for washing the residual oil in the fuel nozzles x2. Also, according to the fuel nozzle wash system D shown in Fig. 8, the construction is made such that the piping 64 of the compressor outlet wash system and the piping 68 of the fuel nozzle wash system are connected to the wash water tank 62 via the single opening/closing valve 63. Thus, by these constructions, washing of the fuel nozzles XZ can be done by the wash water from the wash water tank 62 of the compressor outlet wash system and there is needed no exclusive wash apparatus of the fuel nozzles XZ, hence the wash system can be -made in a simple piping structure, which contributes to cost reduction of the gas turbine plant.
It is understood that the invention is not limited to the particular construction and arrangement herein illustrated and described but embraces such modified forms thereof as come within the scope of the appended claims.

Claims

WHAT IS CLAIMED IS:
1. A gas turbine fuel nozzle wash system in a gas turbine wash system comprising a fuel oil supply system for supplying fuel oil to fuel nozzles (X2) in a combustor (X); a compressor wash water supply system (64) for supplying wash water to a compressor which supplies compressed air to said combustor (X); and a wash water tank (62) for supplying the wash water to said compressor wash water supply system (64), characterized in that there are provided a wash water by-pass piping (67, 68, 71) and an opening/closing valve (63, 72) between said fuel oil supply system and compressor wash water supply system (64) and when said opening/closing valve (63, 72) is opened, the wash water is supplied to said fuel nozzles (X2) from said wash water tank (62) via said fuel oil supply system to be injected from said fuel nozzles (X2) so that said fuel nozzles (X2) are washable.
CA002270672A 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system Expired - Fee Related CA2270672C (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
CA002357493A CA2357493C (en) 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system
CA002357492A CA2357492C (en) 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system
CA002357553A CA2357553C (en) 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system
CA002357555A CA2357555C (en) 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP12603998A JPH11324720A (en) 1998-05-08 1998-05-08 Gas turbine fuel oil purge system
JP10-126039 1998-05-08
JP12604098A JPH11324718A (en) 1998-05-08 1998-05-08 System for controlling fuel oil distribution for gas turbine
JP10-126040 1998-05-08
JP10-127347 1998-05-11
JP12734798A JPH11324721A (en) 1998-05-11 1998-05-11 Air supply system for gas turbine fuel nozzle purge
JP10-128938 1998-05-12
JP12893898A JPH11324722A (en) 1998-05-12 1998-05-12 System for cleaning gas turbine fuel nozzle

Related Child Applications (4)

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CA002357493A Division CA2357493C (en) 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system
CA002357492A Division CA2357492C (en) 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system
CA002357555A Division CA2357555C (en) 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system
CA002357553A Division CA2357553C (en) 1998-05-08 1999-05-04 Gas turbine fuel system comprising fuel oil distribution control system, fuel oil purge system, purging air supply system, and fuel nozzle wash system

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102678337A (en) * 2011-03-07 2012-09-19 通用电气公司 System and method for transitioning between fuel supplies for a combustion system

Families Citing this family (59)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000248964A (en) * 1999-02-26 2000-09-12 Honda Motor Co Ltd Gas turbine engine
US7516909B2 (en) * 2000-02-11 2009-04-14 United States Gypsum Company Continuous slurry dispenser apparatus
JP3690972B2 (en) * 2000-08-08 2005-08-31 三菱重工業株式会社 Steam cooled gas turbine
US6438963B1 (en) * 2000-08-31 2002-08-27 General Electric Company Liquid fuel and water injection purge systems and method for a gas turbine having a three-way purge valve
ITMI20011949A1 (en) * 2001-09-18 2003-03-18 Nuovo Pignone Spa SAFETY DEVICE FOR A WASHING SYSTEM FOR LIQUID FUEL BURNERS IN GAS TURBINES
JP3495730B2 (en) * 2002-04-15 2004-02-09 三菱重工業株式会社 Gas turbine combustor
US6932093B2 (en) 2003-02-24 2005-08-23 General Electric Company Methods and apparatus for washing gas turbine engine combustors
DE10345566A1 (en) * 2003-09-29 2005-04-28 Alstom Technology Ltd Baden Method for operating a gas turbine and gas turbine plant for carrying out the method
JP4728176B2 (en) * 2005-06-24 2011-07-20 株式会社日立製作所 Burner, gas turbine combustor and burner cooling method
AT502621A1 (en) 2005-09-28 2007-04-15 Blum Gmbh Julius HINGE FURNITURE
US7954310B2 (en) * 2006-06-16 2011-06-07 Siemens Energy, Inc. Fuel oil bi-directional flow divider
JP4865476B2 (en) * 2006-09-28 2012-02-01 三菱重工業株式会社 Gas turbine start / stop method and start / stop control device
WO2009065449A2 (en) * 2007-11-23 2009-05-28 Siemens Aktiengesellschaft Method and apparatus for cleaning a large-size high-temperature part
ES2387320T3 (en) * 2007-12-31 2012-09-20 Ansaldo Energia S.P.A. Method and device to control a gas turbine plant
GB0800294D0 (en) * 2008-01-09 2008-02-20 Rolls Royce Plc Gas heater
GB2457281B (en) * 2008-02-11 2010-09-08 Rolls Royce Plc A Combustor Wall Arrangement with Parts Joined by Mechanical Fasteners
JP4979615B2 (en) * 2008-03-05 2012-07-18 株式会社日立製作所 Combustor and fuel supply method for combustor
US8438830B2 (en) * 2008-05-05 2013-05-14 General Electric Company Primary manifold dual gas turbine fuel system
GB2460634B (en) * 2008-06-02 2010-07-07 Rolls Royce Plc Combustion apparatus
US9175606B2 (en) * 2008-06-09 2015-11-03 Siemens Aktiengesellschaft Method for rinsing a fuel system of a gas turbine and associated fuel system
US20100095649A1 (en) * 2008-10-20 2010-04-22 General Electric Company Staged combustion systems and methods
FR2938048B1 (en) * 2008-11-06 2015-03-06 Ge Energy Products France Snc SYSTEM AND METHOD FOR WASHING AND PURGING THE LIQUID COMBUSTIBLE CIRCUIT OF A TURBINE
EP2236793A1 (en) 2009-03-17 2010-10-06 Siemens Aktiengesellschaft Burner assembly
US20120174591A1 (en) * 2009-09-24 2012-07-12 Matthias Hase Fuel Line System, Method for Operating of a Gas Turbine, and a Method for Purging the Fuel Line System of a Gas Turbine
FR2966201B1 (en) * 2010-10-18 2015-10-16 Ge Energy Products France Snc PURGE DEVICE AND METHOD FOR A LIQUID FUEL INJECTION SYSTEM IN A GAS TURBINE
JP5571197B2 (en) 2010-10-28 2014-08-13 三菱重工業株式会社 Gas turbine and gas turbine plant equipped with the same
US9239013B2 (en) * 2011-01-03 2016-01-19 General Electric Company Combustion turbine purge system and method of assembling same
US8991188B2 (en) 2011-01-05 2015-03-31 General Electric Company Fuel nozzle passive purge cap flow
EP2549078A1 (en) * 2011-07-21 2013-01-23 Siemens Aktiengesellschaft Suction duct for intake air of a gas turbine and method for operating a stationary gas turbine
US9188061B2 (en) * 2011-10-24 2015-11-17 General Electric Company System for turbine combustor fuel assembly
US9650955B2 (en) 2011-11-10 2017-05-16 General Electric Company System for purging gas fuel circuit for a gas turbine engine
CN103162080B (en) * 2011-12-12 2015-08-19 金宝电子(中国)有限公司 Oil supply equipment
US8991190B2 (en) * 2012-01-31 2015-03-31 General Electric Company Fuel nozzle staging with water flowing prior to fuel in a main fuel circuit during start-up
JP5946690B2 (en) 2012-05-02 2016-07-06 三菱日立パワーシステムズ株式会社 Purge method and purge apparatus for gas turbine combustor
US9631512B2 (en) 2013-01-31 2017-04-25 Solar Turbines Incorporated Gas turbine offline compressor wash with buffer air from combustor
US8778091B1 (en) 2013-01-31 2014-07-15 Solar Turbines Inc. Compressor wash with air to turbine cooling passages
EP2959132B1 (en) * 2013-02-20 2020-09-09 United Technologies Corporation Self-purging fuel injector system for a gas turbine engine
US9371995B2 (en) * 2013-04-11 2016-06-21 General Electric Company Pulsed water flush of liquid fuel valves and combustion nozzles
US9086016B2 (en) * 2013-04-16 2015-07-21 Bell Helicopter Textron Inc. Fuel drain valve for a turbine engine
US9909499B2 (en) * 2014-04-04 2018-03-06 General Electric Company Fuel drainage and purge system and method
DE102014212824A1 (en) * 2014-07-02 2016-01-07 Siemens Aktiengesellschaft Method and device for flushing and / or blocking at least one burner of a gas turbine plant
CN104989464B (en) * 2015-05-25 2017-01-18 华润水泥技术研发有限公司 Cement kiln waste heat generation constant-voltage automatic generation control module and control method
US10247110B2 (en) * 2015-09-23 2019-04-02 General Electric Company Method and system for reliable gas to liquid transfer
JP6651389B2 (en) * 2016-03-08 2020-02-19 三菱日立パワーシステムズ株式会社 Fuel control device, combustor, gas turbine, fuel control method and program
US10378447B2 (en) 2016-09-30 2019-08-13 General Electric Company System and method for purging fuel or coolant from turbomachine
US20180313225A1 (en) 2017-04-26 2018-11-01 General Electric Company Methods of cleaning a component within a turbine engine
JP7193962B2 (en) * 2018-09-26 2022-12-21 三菱重工業株式会社 Combustor and gas turbine equipped with the same
US11707819B2 (en) 2018-10-15 2023-07-25 General Electric Company Selectively flexible extension tool
US11702955B2 (en) 2019-01-14 2023-07-18 General Electric Company Component repair system and method
CN110094267A (en) * 2019-06-04 2019-08-06 上海睿瑞航空设备科技有限公司 A kind of microminiature aero-turbine high-altitude fuel oil supply system
US11156163B2 (en) * 2019-10-04 2021-10-26 Hamilton Sundstrand Corporation Fluid injection systems having fluid line purging
US11692650B2 (en) 2020-01-23 2023-07-04 General Electric Company Selectively flexible extension tool
US11752622B2 (en) 2020-01-23 2023-09-12 General Electric Company Extension tool having a plurality of links
US11613003B2 (en) 2020-01-24 2023-03-28 General Electric Company Line assembly for an extension tool having a plurality of links
US11371437B2 (en) 2020-03-10 2022-06-28 Oliver Crispin Robotics Limited Insertion tool
US11654547B2 (en) 2021-03-31 2023-05-23 General Electric Company Extension tool
US11814972B2 (en) * 2021-06-03 2023-11-14 General Electric Company Systems and methods for addition of fuel additives to control turbine corrosion
CN114183209A (en) * 2021-11-25 2022-03-15 中盐华能储能科技有限公司 Cold-state purging method for air inlet pipeline of air turbine
US20230228217A1 (en) * 2022-01-06 2023-07-20 General Electric Company System and method for air cooling fuel purge flow

Family Cites Families (52)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH248309A (en) * 1945-04-17 1947-04-30 Sulzer Ag Method for operating gas turbine plants and device for carrying out the method.
US2678531A (en) * 1951-02-21 1954-05-18 Chemical Foundation Inc Gas turbine process with addition of steam
US3623668A (en) * 1968-03-04 1971-11-30 Gen Electric Wash manifold
US3805519A (en) * 1972-05-05 1974-04-23 Westinghouse Electric Corp Fuel control system for a multi-fuel gas turbine
US3826080A (en) * 1973-03-15 1974-07-30 Westinghouse Electric Corp System for reducing nitrogen-oxygen compound in the exhaust of a gas turbine
DE2549790A1 (en) * 1975-11-06 1977-05-18 Bundesrep Deutschland Performance boost for flying boat turbine - uses compressor wash system to inject water and methanol into combustion chambers
US4041695A (en) * 1975-11-21 1977-08-16 The Garrett Corporation Fuel system pneumatic purge apparatus and method
US4314441A (en) * 1977-07-22 1982-02-09 Westinghouse Electric Corp. Gas turbine power plant control apparatus including an ambient temperature responsive control system
JPS5855332B2 (en) * 1978-06-07 1983-12-09 株式会社日立製作所 Purging method and device for dual-fuel firing pressure spray fuel nozzle
GB2035540B (en) * 1978-11-23 1983-02-09 Rolls Royce Gas turbine engine fuel injector
JPS56104122A (en) * 1980-01-23 1981-08-19 Hitachi Ltd Gas turbine with cleaning system
FR2528950A1 (en) * 1982-06-18 1983-12-23 Alsthom Atlantique DEVICE FOR ASSAYING AND DISTRIBUTING PRESSURIZED COMBUSTIBLE LIQUID BETWEEN SEVERAL BURNERS
JPS5915635A (en) * 1982-07-15 1984-01-26 Hitachi Ltd Gas turbine with spray air system
GB2134184A (en) * 1983-01-25 1984-08-08 Secr Defence Liquid fuel supply pressure compensator
JPS60104728A (en) * 1983-11-14 1985-06-10 Hitachi Ltd Purging for fuel oil in gas turbine
US4645415A (en) * 1983-12-23 1987-02-24 United Technologies Corporation Air cooler for providing buffer air to a bearing compartment
JPS61241425A (en) * 1985-04-17 1986-10-27 Hitachi Ltd Fuel gas controlling method of gas turbine and controller
IT210843Z2 (en) 1987-03-31 1989-01-11 Iveco Fiat GROUP FOR THE TREATMENT OF THE FUEL OF A DIESEL ENGINE
GB2219045B (en) * 1988-05-27 1992-06-03 Rolls Royce Plc Gas turbine engine fuel system
GB2227795A (en) * 1989-02-07 1990-08-08 Rolls Royce Plc Gas turbine engine fuel system
US5020315A (en) * 1989-08-08 1991-06-04 United Technologies Corporation Multiple function fuel valve and system
US5185997A (en) * 1990-01-30 1993-02-16 Hitachi, Ltd. Gas turbine system
GB9025778D0 (en) * 1990-11-27 1991-01-09 Rolls Royce Plc Improvements in or relating to gas generators
US5199255A (en) * 1991-04-03 1993-04-06 Nalco Fuel Tech Selective gas-phase nox reduction in gas turbines
US5235814A (en) * 1991-08-01 1993-08-17 General Electric Company Flashback resistant fuel staged premixed combustor
JP2758301B2 (en) * 1991-11-29 1998-05-28 株式会社東芝 Gas turbine combustor
US5247797A (en) * 1991-12-23 1993-09-28 General Electric Company Head start partial premixing for reducing oxides of nitrogen emissions in gas turbine combustors
US5255505A (en) * 1992-02-21 1993-10-26 Westinghouse Electric Corp. System for capturing heat transferred from compressed cooling air in a gas turbine
DE4210544A1 (en) * 1992-03-31 1993-10-07 Asea Brown Boveri Gas turbine plant
CA2093683C (en) * 1992-05-14 2002-10-15 William Miller Farrell Intercooled gas turbine engine
US6119445A (en) * 1993-07-22 2000-09-19 Ormat Industries Ltd. Method of and apparatus for augmenting power produced from gas turbines
US5628184A (en) * 1993-02-03 1997-05-13 Santos; Rolando R. Apparatus for reducing the production of NOx in a gas turbine
US5365732A (en) * 1993-04-19 1994-11-22 General Electric Company Retrofittable trim system for fuel-air optimization in cannular gas turbine combustors
US5324175A (en) * 1993-05-03 1994-06-28 Northern Research & Engineering Corporation Pneumatically operated reciprocating piston compressor
US5329758A (en) * 1993-05-21 1994-07-19 The United States Of America As Represented By The Secretary Of The Navy Steam-augmented gas turbine
US5339845A (en) * 1993-07-26 1994-08-23 Fuel Systems Textron, Inc. Cleaning apparatus and method for fuel and other passages
DE4335412B4 (en) * 1993-10-18 2005-01-27 Alstom Process and device for fuel distribution for annular combustion chambers of gas turbine plants
US5452573A (en) * 1994-01-31 1995-09-26 United Technologies Corporation High pressure air source for aircraft and engine requirements
US5617716A (en) * 1994-09-16 1997-04-08 Electric Power Research Institute Method for supplying vaporized fuel oil to a gas turbine combustor and system for same
JP3499026B2 (en) 1994-12-20 2004-02-23 株式会社東芝 Gas turbine fuel supply device
US5724806A (en) * 1995-09-11 1998-03-10 General Electric Company Extracted, cooled, compressed/intercooled, cooling/combustion air for a gas turbine engine
US5784875A (en) * 1995-11-27 1998-07-28 Innovative Control Systems, Inc. Water injection into a gas turbine using purge air
DE19605736A1 (en) * 1996-02-16 1997-08-21 Gutehoffnungshuette Man Process for rapid switchover from premix operation to diffusion operation in a combustion chamber of a gas turbine operated with fuel gas
DE19639329A1 (en) * 1996-09-25 1998-03-26 Asea Brown Boveri Flow-improvement method in distribution system preceding consumer system
US6092362A (en) * 1996-11-27 2000-07-25 Hitachi, Ltd. Gas-turbine combustor with load-responsive premix burners
DE59710054D1 (en) * 1997-11-10 2003-06-12 Alstom Switzerland Ltd Method for monitoring the supply system of a gas turbine with a multiple burner system and device for carrying out the method
EP0939220B1 (en) * 1998-02-26 2003-11-12 ALSTOM (Switzerland) Ltd Method for safely removing liquid fuel out of a gas turbine fuel system and device for carrying out the method
US6145294A (en) * 1998-04-09 2000-11-14 General Electric Co. Liquid fuel and water injection purge system for a gas turbine
EP0952317A3 (en) * 1998-04-21 2002-04-17 Mitsubishi Heavy Industries, Ltd. Purging system for a gas turbine fuel supply
US6079198A (en) * 1998-04-29 2000-06-27 General Electric Co. Pressure compensated fuel delivery system for the combustors of turbomachinery
US6000413A (en) * 1998-09-01 1999-12-14 Innova Electronics Corporation Fuel injector cleaning system
US6145318A (en) * 1998-10-22 2000-11-14 General Electric Co. Dual orifice bypass system for dual-fuel gas turbine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102678337A (en) * 2011-03-07 2012-09-19 通用电气公司 System and method for transitioning between fuel supplies for a combustion system

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