EP0319699A2 - Moteur à injection de vapeur avec une turbinne auxiliaire à vapeur à haute pression - Google Patents

Moteur à injection de vapeur avec une turbinne auxiliaire à vapeur à haute pression Download PDF

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Publication number
EP0319699A2
EP0319699A2 EP88118125A EP88118125A EP0319699A2 EP 0319699 A2 EP0319699 A2 EP 0319699A2 EP 88118125 A EP88118125 A EP 88118125A EP 88118125 A EP88118125 A EP 88118125A EP 0319699 A2 EP0319699 A2 EP 0319699A2
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EP
European Patent Office
Prior art keywords
steam
engine
turbine
high pressure
auxiliary
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP88118125A
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German (de)
English (en)
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EP0319699A3 (fr
Inventor
William Ronald Hines
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General Electric Co
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General Electric Co
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Publication date
Application filed by General Electric Co filed Critical General Electric Co
Publication of EP0319699A2 publication Critical patent/EP0319699A2/fr
Publication of EP0319699A3 publication Critical patent/EP0319699A3/fr
Withdrawn legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • F01K21/042—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas pure steam being expanded in a motor somewhere in the plant

Definitions

  • This invention relates to gas turbine engines, and more particularly, to a steam injected gas turbine engine having a small auxillary high pressure steam turbine for extracting additional horsepower output from the engine and improving cycle thermal efficiency.
  • Various boilers can be placed downstream of the power turbine where steam at intermediate and low pressure is generated, with the steam then injected into various parts of the engine.
  • the present invention achieves an improvement in both cycle thermal efficiency, as well as system power output of a steam injected gas turbine engine, by utilizing a high pressure boiler downstream of the power turbine to produce steam at very high pressure and temperature.
  • the steam then passes through a high pressure steam turbine which is non-condensing (hereinafter referred to as an auxiliary steam turbine) whereby horsepower is extracted from this superheated steam, resulting in much cooler steam which is still above saturation and still has enough pressure for combustor injection.
  • the cool steam can be either injected directly back into the combustor or can be reheated to a much higher superheat temperature and then injected into the combustor.
  • the cool steam could also be used for cooling static vane parts rather than being reheated.
  • Table 1 shows that at constant high pressure turbine rotor inlet temperature but with increased fuel flow to the engine system, that the same amount of uncondensed vapor leaves the open cycle. This will significantly improve cycle thermal efficiency.
  • the output from the auxiliary steam turbine can be merged into the direct output of the power turbine through an auxiliary turbine gear box whereby the system horsepower output is also improved.
  • Use of an auxiliary steam turbine would not require changes in engine control areas such as high pressure turbine, low pressure turbine, or power turbine nozzle diaphragm areas. However, the regenerator or boiler systems would have to be designed for using an auxiliary steam turbine.
  • Another object of the present invention is to provide a steam injected gas turbine engine utilizing an auxiliary steam turbine for extracting horsepower from steam produced in a high pressure boiler downstream of the power turbine.
  • Still a further object of the present invention is to provide a gas turbine engine having a high pressure boiler downstream of the power turbine and producing superheated steam at very high pressures which steam passes through an auxiliary steam turbine and is then injected back into the engine.
  • Yet a further object of the present invention is to provide a steam injected gas turbine engine having less uncondensed vapor lost in the exhaust from the engine for a given fuel flow rate to the engine system.
  • the present invention in one form provides a gas turbine engine having a compressor, a combustor, and a high pressure turbine in series combination.
  • the output from the engine is extracted through a power turbine.
  • Downstream of the power turbine is a high pressure boiler for providing superheated steam at very high pressures.
  • An auxiliary steam turbine receives the steam from the high pressure boiler and extracts power from the steam in addition to the power output extracted through the power turbine, to thereby increase the engine output power and thermal efficiency. The steam is then injected back into the engine.
  • the steam is reheated in a superheater prior to its injection back into the combustor.
  • the steam from the auxiliary steam turbine can also be used to cool static vane parts rather than being reheated in a superheater. Alternately, it can be injected directly into the combustor for cooling the combustor.
  • the present invention is directed towards a land or sea based gas turbine engine using boiler systems in order to provide for heat recovery in the exhaust.
  • the gas turbine typically includes compressors, such as low and high pressure compressors, followed by a combustor after which are turbines, such as the low and high pressure turbine.
  • the output is taken through a power turbine.
  • the present invention further includes a high pressure boiler downsteam of the power turbine designed to produce superheated steam at very high pressures. This steam passes through an auxiliary steam turbine which extracts horsepower from the steam. The steam is still left with enough pressure and at a temperature above saturation, so that it can be injected back into the combustor or other parts of the engine.
  • the cycle thermal efficiency of the engine increases, as well as its power output.
  • Such increase results from the reduction of uncondensed vapor lost in the exhaust at a referenced fuel flow rate.
  • the boiler has a capability of creating very high pressures with very low pump losses.
  • any pressure losses in the auxiliary steam turbine are not significant, since the boiler can easily make pressure at only a small loss in steam temperature or mass flow.
  • An additional benefit is the fact that a characteristic of superheated steam is that it is not a perfect gas. At constant temperatures, within the temperature range that is being operated on, its enthalpy is increased as the flow is throttled.
  • the pressure has also been significantly decreased while passing through the auxiliary steam turbine and the imperfect gas is now at a higher enthalpy than it would have been if it were a perfect gas at the same temperature, but at a higher pressure.
  • a gas turbine engine at 10 which includes, in operating fluid sequence, a low pressure compressor means 12, followed by a high pressure compressor means 14.
  • a combustor 16 receives fuel, as is well known in the art, and generates combustor output products, which are sent into a high pressure turbine means 18 followed by a low pressure turbine means 20.
  • a dual shaft system is utilized with the inner shaft 22 from the low pressure turbine driving the low pressure compressor, and the outer shaft 24 from the high pressure turbine driving the high pressure compressor.
  • the operating fluid then passes from the low pressure turbine for expansion through a power turbine 26, which is then used to drive output devices through the output shaft 28.
  • a power turbine 26 which is then used to drive output devices through the output shaft 28.
  • steam would be injected into the combustor or other parts of the engine. Some of the steam would be exhausted from the system and leaves the open cycle as uncondensed vapor, which is a loss to the system, thereby reducing the cycle thermal efficiency.
  • the high pressure boiler 30 is designed to produce superheated steam at very high pressures.
  • the pressures can be in the range of 1500-3500 psia and superheated steam of at least 750° F.
  • An auxiliary steam turbine shown generally at 32 receives the steam output from the high pressure boiler. The steam passes through the auxiliary steam turbine 32 and then along line 34 is injected back into the combustor.
  • the auxiliary turbine can typically operate at about a 4 to 1 pressure ratio. In so doing, it would still leave the steam above saturation and still having enough pressure for combustor injection.
  • An advantage of this arrangement is that the superheated steam is not a perfect gas, and as a result, at the operating temperatures, its enthalpy is increased as the flow is throttled. At the output of the auxiliary turbines, the temperature of the steam has been reduced from its input. The pressure has also been significantly decreased. As a result, the steam, an imperfect gas, is now at a higher enthalpy than it would have been if it were a perfect gas at the same temperature but at a higher pressure.
  • the output from the auxiliary turbine 32 could be sent through a gear box 35 or a variable speed constant frequency device, or the like, in order to obtain desired speeds.
  • the gear box could use a 6 to 1 ratio to obtain speeds of 3,600 or 3,000 R. P. M. (60 Hz. or 50 Hz.).
  • the gear box 35 operates to merge the output from the auxiliary turbine with the main shaft 28 so as to operate the 60 Hz. generator 36.
  • the steam output from the auxiliary steam turbine 32 is injected directly into the combustor. Since the steam is at a rather cool temperature, it would serve to cool the combustor.
  • the output from the high pressure boiler 30 is sent to the auxiliary steam turbine 32 as before.
  • a superheater 40 which is placed between the power turbine 26 and the high pressure boiler 30.
  • the steam is reheated to a much higher superheat temperature and is then injected into the combustor.
  • the superheater also finds additional use should a supplementary burner be included after the power turbine. Such supplementary burner would increase the temperature at the output of the power turbine, which would raise the temperature substantially at the entrance to the high pressure boiler. Such high temperatures would require special boiler materials.
  • the high pressure superheater 40 would remove such heat before the boilers in order to reduce this temperature.
  • the cool steam as is produced directly from the auxiliary steam turbine could actually be used for cooling various engine parts, such as the static vane parts, rather than being reheated.
  • FIG. 2 there is also provided an intermediate pressure boiler 42 and a low pressure boiler 44.
  • the output from these boilers can be used to feed various turbines or other engine parts.
  • the steam from intermediate pressure boiler 42 is injected along line 46 to the low pressure turbine 20 and at line 48 into the power turbine 26.
  • the power turbine receives steam injection from the lower pressure boiler 44 along line 50.
  • Fig. 2 also shows the use of an intercooler, shown generally at 52.
  • auxiliary steam turbine 32 could also be used to drive auxiliary compressors, which could pressurize the intermediate and low pressure boiler steam from the boilers 42 and 44. This steam could then also be injected directly into the combustor. In this way, the auxiliary compressor losses would be recouped into the combustor.
  • auxiliary steam turbine The size of an auxiliary steam turbine is quite small.
  • a turbine approximately 7 inches long and 14 inches in diameter with one inch blading can put out approximately 6,600 horsepower with an efficiency of 0.875.
  • the auxiliary steam turbine output can be geared right into the main shaft of the electrical generator as shown in Fig. 1.
  • a 6 to 1 gearbox reduction to 3,600 R.P.M. can be utilized.
  • a two-stage gear reduction to 1,800 R.P.M. would be utilized.
  • Fig. 3 shows a T-S (temperature-entropy) drawing for the Rankine cycle passing through the engine heretofore shown in Fig. 1.
  • the steam injected into the main combustor would follow line 60 and reach point a .
  • the steam would then pass through the various turbines with the reduction of temperature and pressure as shown along line 62 to reach point b . Should a supplementary burner be included after the power turbine, the steam would increase its temperature to point c with the output of the steam then being exhausted back through the exhaust stack at point f.
  • steam would initially enter along line 64 and proceed along line 66 until it is injected into the main combustor. With the presence of the high pressure boiler, the steam proceeds along the curved line 68 until it reaches point d at the entrance to the auxiliary steam turbine. The temperature and pressure is then reduced through the auxiliary steam turbine along line 69 until point e is reached. At this point, the temperature and pressure is still adequate for main combustor heating.
  • the overall cycle thermal efficiency is improved. Additionally, direct recovery of horsepower can be made through the use of the high pressure boiler with the auxiliary steam turbine, whereby less uncondensed vapor leaves the exhaust at a given fuel flow rate.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP88118125A 1987-11-30 1988-10-31 Moteur à injection de vapeur avec une turbinne auxiliaire à vapeur à haute pression Withdrawn EP0319699A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US12608787A 1987-11-30 1987-11-30
US126087 1998-07-30

Publications (2)

Publication Number Publication Date
EP0319699A2 true EP0319699A2 (fr) 1989-06-14
EP0319699A3 EP0319699A3 (fr) 1989-09-20

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EP88118125A Withdrawn EP0319699A3 (fr) 1987-11-30 1988-10-31 Moteur à injection de vapeur avec une turbinne auxiliaire à vapeur à haute pression

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EP (1) EP0319699A3 (fr)
JP (1) JPH01208524A (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994008128A1 (fr) * 1991-04-02 1994-04-14 Dah Yu Cheng Cycle de regeneration a deux fluides de type cheng
EP0676532A1 (fr) * 1994-04-08 1995-10-11 Westinghouse Electric Corporation Système de turbine à gaz avec injection de vapeur et avec une turbine à vapeur à haute pression
WO2010098709A1 (fr) * 2009-02-24 2010-09-02 Euroturbine Ab Procédé d'exploitation d'une centrale électrique à turbines à gaz et centrale électrique à turbines à gaz
US7987677B2 (en) 2008-03-31 2011-08-02 Mccutchen Co. Radial counterflow steam stripper
CN102325978A (zh) * 2009-02-24 2012-01-18 欧洲涡轮机公司 运行燃气轮机发电站的方法及燃气轮机发电站
US10537840B2 (en) 2017-07-31 2020-01-21 Vorsana Inc. Radial counterflow separation filter with focused exhaust

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105756732B (zh) * 2016-03-14 2017-07-18 东南大学 一种lng/液氧直燃混合工质动力循环发电装置

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB713553A (en) * 1950-11-16 1954-08-11 Maschf Augsburg Nuernberg Ag Improvements in or relating to gas turbine installations
GB746377A (en) * 1953-04-29 1956-03-14 Allan Barker Improvements in or relating to gas turbine installations
GB932718A (en) * 1960-05-24 1963-07-31 Head Wrightson & Co Ltd Combined gas turbine and steam turbine power plant
GB1093682A (en) * 1966-07-22 1967-12-06 Rolls Royce Improvements in or relating to power plants
FR1530850A (fr) * 1967-07-07 1968-06-28 Aeg Kanis Turbinenfabrik G M B Installation de turbine à gaz ouverte
GB1143469A (en) * 1966-11-11 1969-02-19 Head Wrightson & Co Ltd Combined gas turbine and steam turbine power plant installation
DE2138664A1 (de) * 1971-07-23 1973-03-08 Sulzer Ag Verfahren zum gemischten gas- und dampfbetrieb einer gasturbinenanlage
DE3331153A1 (de) * 1983-08-30 1985-03-14 Brown, Boveri & Cie Ag, 6800 Mannheim Gasturbinenanlage fuer offenen prozess
EP0184137A1 (fr) * 1984-12-03 1986-06-11 General Electric Company Unité intégrée de gazéification de charbon et système à cycle combiné avec dérivation d'air et injection de vapeur

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB713553A (en) * 1950-11-16 1954-08-11 Maschf Augsburg Nuernberg Ag Improvements in or relating to gas turbine installations
GB746377A (en) * 1953-04-29 1956-03-14 Allan Barker Improvements in or relating to gas turbine installations
GB932718A (en) * 1960-05-24 1963-07-31 Head Wrightson & Co Ltd Combined gas turbine and steam turbine power plant
GB1093682A (en) * 1966-07-22 1967-12-06 Rolls Royce Improvements in or relating to power plants
GB1143469A (en) * 1966-11-11 1969-02-19 Head Wrightson & Co Ltd Combined gas turbine and steam turbine power plant installation
FR1530850A (fr) * 1967-07-07 1968-06-28 Aeg Kanis Turbinenfabrik G M B Installation de turbine à gaz ouverte
DE2138664A1 (de) * 1971-07-23 1973-03-08 Sulzer Ag Verfahren zum gemischten gas- und dampfbetrieb einer gasturbinenanlage
DE3331153A1 (de) * 1983-08-30 1985-03-14 Brown, Boveri & Cie Ag, 6800 Mannheim Gasturbinenanlage fuer offenen prozess
EP0184137A1 (fr) * 1984-12-03 1986-06-11 General Electric Company Unité intégrée de gazéification de charbon et système à cycle combiné avec dérivation d'air et injection de vapeur

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994008128A1 (fr) * 1991-04-02 1994-04-14 Dah Yu Cheng Cycle de regeneration a deux fluides de type cheng
EP0676532A1 (fr) * 1994-04-08 1995-10-11 Westinghouse Electric Corporation Système de turbine à gaz avec injection de vapeur et avec une turbine à vapeur à haute pression
US5564269A (en) * 1994-04-08 1996-10-15 Westinghouse Electric Corporation Steam injected gas turbine system with topping steam turbine
US7987677B2 (en) 2008-03-31 2011-08-02 Mccutchen Co. Radial counterflow steam stripper
US8474264B2 (en) 2008-03-31 2013-07-02 Mccutchen Co. Radial counterflow steam stripper
WO2010098709A1 (fr) * 2009-02-24 2010-09-02 Euroturbine Ab Procédé d'exploitation d'une centrale électrique à turbines à gaz et centrale électrique à turbines à gaz
CN102325978A (zh) * 2009-02-24 2012-01-18 欧洲涡轮机公司 运行燃气轮机发电站的方法及燃气轮机发电站
CN102325979A (zh) * 2009-02-24 2012-01-18 欧洲涡轮机公司 运行燃气轮机发电站的方法及燃气轮机发电站
CN102325979B (zh) * 2009-02-24 2014-07-30 欧洲涡轮机公司 运行燃气轮机发电站的方法及燃气轮机发电站
US9062607B2 (en) 2009-02-24 2015-06-23 Euro-Turbine Ab Method of operating a gas turbine power plant and gas turbine power plant
US10537840B2 (en) 2017-07-31 2020-01-21 Vorsana Inc. Radial counterflow separation filter with focused exhaust

Also Published As

Publication number Publication date
EP0319699A3 (fr) 1989-09-20
JPH01208524A (ja) 1989-08-22

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