EP2045441A1 - Generator-gas turbine-turbo compressor line and method for operating the same - Google Patents

Generator-gas turbine-turbo compressor line and method for operating the same Download PDF

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Publication number
EP2045441A1
EP2045441A1 EP07019475A EP07019475A EP2045441A1 EP 2045441 A1 EP2045441 A1 EP 2045441A1 EP 07019475 A EP07019475 A EP 07019475A EP 07019475 A EP07019475 A EP 07019475A EP 2045441 A1 EP2045441 A1 EP 2045441A1
Authority
EP
European Patent Office
Prior art keywords
generator
steam turbine
steam
turbocompressor
train
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.)
Granted
Application number
EP07019475A
Other languages
German (de)
French (fr)
Other versions
EP2045441B1 (en
Inventor
Oliver Berendt
Jens Dr. Hampel
Olaf Schmidt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to PL07019475T priority Critical patent/PL2045441T3/en
Application filed by Siemens AG filed Critical Siemens AG
Priority to ES07019475T priority patent/ES2343336T3/en
Priority to DE502007004025T priority patent/DE502007004025D1/en
Priority to AT07019475T priority patent/ATE470049T1/en
Priority to EP07019475A priority patent/EP2045441B1/en
Priority to RU2010117378/06A priority patent/RU2478795C2/en
Priority to JP2010527443A priority patent/JP4940352B2/en
Priority to MX2010003515A priority patent/MX2010003515A/en
Priority to CN200880109922A priority patent/CN101815845A/en
Priority to BRPI0817803A priority patent/BRPI0817803A2/en
Priority to US12/680,973 priority patent/US8575774B2/en
Priority to KR1020107009661A priority patent/KR101531831B1/en
Priority to PCT/EP2008/063149 priority patent/WO2009043875A1/en
Publication of EP2045441A1 publication Critical patent/EP2045441A1/en
Application granted granted Critical
Publication of EP2045441B1 publication Critical patent/EP2045441B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/10—Adaptations for driving, or combinations with, electric generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D15/00—Adaptations of machines or engines for special use; Combinations of engines with devices driven thereby
    • F01D15/08—Adaptations for driving, or combinations with, pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D19/00—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/70—Application in combination with
    • F05D2220/72—Application in combination with a steam turbine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/40—Transmission of power
    • F05D2260/402—Transmission of power through friction drives
    • F05D2260/4023—Transmission of power through friction drives through a friction clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/85—Starting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/02—Purpose of the control system to control rotational speed (n)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/06—Purpose of the control system to match engine to driven device
    • F05D2270/061—Purpose of the control system to match engine to driven device in particular the electrical frequency of driven generator

Definitions

  • the invention relates to a generator-steam turbine-turbocompressor train and a method for operating the generator-steam turbine-turbocompressor train.
  • a turbocompressor is used, for example, in a plant of the chemical industry. Conventionally, there is a supply of thermal energy in the form of process steam in the plant.
  • the process steam is provided in a process steam system from which the process steam for driving a steam turbine can be taken.
  • the steam turbine is conventionally used to drive the turbocompressor.
  • the turbo-compressor is operated at different operating conditions, which may be associated with different speeds of the turbo-compressor.
  • the speed of the turbocompressor affects the drive power received by the turbocompressor, and the thermal power provided by the process steam system is conventionally greater than the power required to drive the turbocompressor. This power surplus increases with decreasing power consumption of the turbocompressor.
  • this power surplus is not used or converted into a steam turbine set consisting of a steam turbine and a generator that is additionally installed in the system.
  • a steam turbine kit comprising a generator 101 and a steam turbine 102 is shown.
  • the steam turbine 102 drives the generator 101 via a first clutch 104.
  • To drive the steam turbine 102 is from a live steam line 106 of the steam turbine 102 is supplied live steam.
  • the electric power generated by the generator 101 is output to an electric network 107.
  • a further steam turbine 108 is driven, which in turn is coupled via a clutch 105 with a turbo compressor 103 to its drive.
  • the rotational speed of the turbocompressor 103 is regulated by means of a rotational speed feedback device 109 which controls a live steam valve 108a.
  • the main steam valve 108a is controlled such that the supplied from the main steam line 106 of the steam turbine 108 steam amount is set such that the turbocompressor 103 is adjusted to the predetermined speed.
  • the steam turbine 108 is designed to drive the turbocompressor 103 oversized.
  • the steam turbine 108 has to provide a maximum required drive power of the turbocompressor 103 with minimal parameters of the live steam line 106.
  • the steam turbine 108 has to allow the start of the turbocompressor 103 even with reduced live steam parameters. In rated operation, the steam turbine 108 is therefore acted upon only about 70% of the maximum steam flow rate. This has the consequence that the steam turbine 108 is driven throttled in the majority of the operating time with the main steam valve 108a. As a result, the efficiency of the steam turbine 108 is far below its maximum efficiency.
  • the excess live steam which is available in the main steam line 106, is converted into electricity.
  • the additional provision of the steam turbine 102 and generator 106 in the plant is expensive and expensive.
  • a conventional train including a generator 101, a steam turbine 102, and a turbocompressor 103 is shown.
  • the steam turbine 102 is supplied with live steam from a live steam line 106 and is coupled by means of a clutch 104 to the generator 101 and by means of a clutch 105 to the turbo-compressor 103 for driving.
  • the electric power generated in the generator 101 is output to an electric network 107.
  • the turbocompressor 103 is operated at a constant speed.
  • the steam turbine 102 is driven throttled at rated load and partial load for the reasons mentioned above, so that the efficiency of the steam turbine 102 is also below its optimum efficiency. Furthermore, there is no possibility to regulate the turbocompressor 103 via the rotational speed, which leads to a loss of efficiency of the overall process.
  • the object of the invention is to provide a generator-steam turbine-turbocompressor train and a method for operating the same, wherein the generator-steam turbine-turbocompressor train has a high efficiency, good controllability and low investment costs.
  • the generator-steam turbine-turbocompressor train comprises a frequency-variable generator, a steam turbine and a turbo-compressor driven by the generator and / or the steam turbine, which are coupled together to form a shaft train, wherein the generator is electrically coupled to an electrical grid for feeding in the grid and the steam turbine can be connected to a live steam supply line for supplying live steam to the steam turbine, so that the generator-steam turbine-turbocompressor train can be speed-controlled via a variation of the mains supply and / or via the live steam supply.
  • the method according to the invention for operating the generator / steam turbine / turbocompressor train has the steps: Providing the generator-steam turbine-turbocompressor string; Vary the grid feed of the generator and / or vary the live steam supply to the steam turbine for speed control of the generator-steam turbine-turbocompressor train.
  • the turbocompressor In the generator-steam turbine-turbocompressor train, the turbocompressor is drivable from the steam turbine, completely converting the process energy provided to the train. Because the steam turbine drives the generator, an additional generator drive is not provided, so that the investment costs for the generator / steam turbine / turbocompressor train are low.
  • the steam turbine in the generator-steam turbine-turbocompressor train is mobile with a fully controlled steam control valve. This leads to a high efficiency of the steam turbine, so that the yield of the process energy is high.
  • the power of the turbocompressor in the generator-steam turbine-turbocompressor train is controllable by the variable speed, whereby the power control of the turbocompressor is effective.
  • the generator When starting the turbocompressor, the generator can be operated as a motor, whereby an additional drive power is provided when starting the turbocompressor by the generator.
  • the steam turbine need not be designed so that the start of the turbocompressor can be accomplished at any high steam power requirements of the turbocompressor in case of low steam parameters.
  • the steam turbine is inexpensive to carry out, whereby the investment costs for the steam turbine are low.
  • the steam turbine in normal operation is not or only slightly throttled mobile, whereby the efficiency of the steam turbine is high.
  • the steam turbine preferably has a live steam valve for supplying the live steam from the live steam supply device to the steam turbine, wherein the live steam feed can be regulated with the live steam valve, so that the generator steam turbine turbo compressor train can be speed controlled by means of the live steam valve.
  • the generator-steam turbine-turbocompressor train comprises a frequency converter, with which the generator is electrically coupled to the electrical network for feeding in the grid and the power of the generator is controllable, so that the generator-steam turbine-turbocompressor train by means of the frequency converter is speed controllable.
  • the power output of the generator is variable in the grid feed, so that the power requirement of the generator is adaptable to the power requirement of the turbocompressor.
  • the drive power of the steam turbine can be predetermined and thus adapted to the power supply of the live steam supply device.
  • the complete steam supply of the live steam supply device in the steam turbine can be expanded, the turbo compressor being operable at a desired operating state.
  • the generator is operable both in the generator mode and in the drive motor mode.
  • an additional drive power is provided by the generator.
  • This additional drive power can, for example be required when starting the turbocompressor, for example, if the steam supply of the live steam supply device is too low to start the turbo compressor. This makes it possible to start the turbocompressor yet, although the drive power of the steam turbine alone would not be enough.
  • the generator draws power from the grid.
  • the generator is a high-speed generator.
  • the steps are further preferred: providing the steam turbine with the live steam valve; Varying the position of the live steam valve to control the speed of the generator-steam turbine-turbocompressor train; In normal operation: operating the steam turbine with fully controlled live steam valve.
  • the steam turbine is operated at nominal load and not at partial load in normal operation, so that the efficiency of the steam turbine is high.
  • the steps of: providing the generator as operable in generator mode as well as in drive motor mode are preferred; During start-up operation: Operation of the generator in drive motor operation.
  • FIG. 1 has a generator-steam turbine-turbocompressor train 1 a generator 2, a steam turbine 3 and a turbocompressor 4, which form a shaft 5 strand.
  • the steam turbine 3 is coupled to drive the generator 2 with this means of a first clutch 5a and coupled to drive the turbocompressor 4 by means of a second clutch 5b.
  • the steam turbine 3 is operated with steam from a live steam supply device 7, the steam flow to the steam turbine 3 being controllable by a live steam valve 8.
  • the main steam valve 8 is coupled by means of a speed feedback device 10 with the rotational speed of the shaft train 5. By means of the speed feedback device 10, the main steam valve 8 can be controlled such that the shaft train 5 is speed-controlled.
  • the generator 2 is coupled via a frequency converter 9 to an electrical network 6 for feeding in the grid.
  • the frequency converter 9 is coupled by means of a speed feedback device 11 with the rotational speed of the shaft train 5.
  • the steam turbine 3 is set up by means of the live steam valve 8 and the speed feedback device 10 for speed-controlled drive of the turbocompressor 4. Furthermore, the steam turbine 3 is combined to drive the generator 2 on a shaft train 5.
  • the generator 2 and the frequency converter 9 can, if the boundary conditions require starting the turbocompressor 4 an additional power supply, also be operated by motor.
  • the steam turbine 3 is driven in normal operation with the fully controlled live steam valve 8, so that the steam turbine can be operated in nominal operation at high efficiency.
  • the frequency converter 9 is generated by the generator 2 three-phase current with the respective network frequency of the network 6, which can be fed into the network 6. If necessary, the generator 3 can provide an additional mechanical power for starting the turbocompressor 4 during engine operation.
  • the speed control of the shaft train 5 is carried out either via the adjustment of the grid feed power or at constant power of the generator 2 via the main steam valve 8 of the steam turbine 2.
  • the power control of the generator 2 takes place in the frequency converter.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
  • Control Of Eletrric Generators (AREA)
  • Supercharger (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

The line (1) has a turbo-compressor (4) driven by a generator (2) with a variable frequency, and a steam turbine (3), where the generator and steam turbine are coupled together to a shafting (5), and the turbine is driven with a steam control valve. The generator is electrically coupled to an electrical power supply system (6) for feeding power supply, and the steam turbine is connected to a live steam feeding device (7) for feeding live steam to the steam turbine such that the line has a rotational speed, which is controllable by varying the power supply feeding or live steam feeding. An independent claim is also included for a method for operating a generator-steam turbine-turbo-compressor-line.

Description

Die Erfindung betrifft einen Generator-Dampfturbine-Turboverdichter-Strang und ein Verfahren zum Betreiben des Generator-Dampfturbine-Turboverdichter-Strangs.The invention relates to a generator-steam turbine-turbocompressor train and a method for operating the generator-steam turbine-turbocompressor train.

Ein Turboverdichter findet beispielsweise in einer Anlage der chemischen Industrie Anwendung. In der Anlage liegt herkömmlich ein Angebot an thermischer Energie in Form von Prozessdampf vor. Der Prozessdampf wird in einem Prozessdampfsystem bereitgestellt, von dem der Prozessdampf zum Antreiben einer Dampfturbine entnommen werden kann. Die Dampfturbine dient herkömmlich zum Antreiben des Turboverdichters.A turbocompressor is used, for example, in a plant of the chemical industry. Conventionally, there is a supply of thermal energy in the form of process steam in the plant. The process steam is provided in a process steam system from which the process steam for driving a steam turbine can be taken. The steam turbine is conventionally used to drive the turbocompressor.

Herkömmlich wird der Turboverdichter bei unterschiedlichen Betriebszuständen betrieben, die mit unterschiedlichen Drehzahlen des Turboverdichters einhergehen können. Herkömmlich beeinflusst die Drehzahl des Turboverdichters die von dem Turboverdichter aufgenommene Antriebsleistung, wobei die von dem Prozessdampfsystem bereitgestellte thermische Leistung herkömmlich größer ist als die Leistung, die für den Antrieb des Turboverdichters benötigt wird. Dieser Leistungsüberschuss nimmt mit sinkendem Leistungsverbrauch des Turboverdichters zu.Conventionally, the turbo-compressor is operated at different operating conditions, which may be associated with different speeds of the turbo-compressor. Conventionally, the speed of the turbocompressor affects the drive power received by the turbocompressor, and the thermal power provided by the process steam system is conventionally greater than the power required to drive the turbocompressor. This power surplus increases with decreasing power consumption of the turbocompressor.

Herkömmlich wird dieser Leistungsüberschuss nicht genutzt oder in einem in der Anlage zusätzlich errichteten Dampfturbosatz bestehend aus einer Dampfturbine und einem Generator verstromt.Conventionally, this power surplus is not used or converted into a steam turbine set consisting of a steam turbine and a generator that is additionally installed in the system.

In Fig. 2 ist ein Dampfturbosatz aufweisend einen Generator 101 und eine Dampfturbine 102 gezeigt. Die Dampfturbine 102 treibt den Generator 101 via eine erste Kupplung 104 an. Zum Antreiben der Dampfturbine 102 wird von einer Frischdampfleitung 106 der Dampfturbine 102 Frischdampf zugeführt. Die von dem Generator 101 erzeugte elektrische Leistung wird an ein elektrisches Netz 107 abgegeben.In Fig. 2 a steam turbine kit comprising a generator 101 and a steam turbine 102 is shown. The steam turbine 102 drives the generator 101 via a first clutch 104. To drive the steam turbine 102 is from a live steam line 106 of the steam turbine 102 is supplied live steam. The electric power generated by the generator 101 is output to an electric network 107.

Ferner wird mit dem Dampf der Frischdampfleitung 106 eine weitere Dampfturbine 108 angetrieben, die ihrerseits via einer Kupplung 105 mit einem Turboverdichter 103 zu dessen Antrieb gekoppelt ist. Die Drehzahl des Turboverdichters 103 wird mittels einer Drehzahlrückkopplungseinrichtung 109 geregelt, die ein Frischdampfventil 108a steuert. Somit wird unter Vorgabe einer vorherbestimmten Drehzahl für den Turboverdichter 103 mittels der Drehzahlrückkopplungseinrichtung 109 das Frischdampfventil 108a derart angesteuert, dass die von der Frischdampfleitung 106 der Dampfturbine 108 zugeführte Dampfmenge derart eingestellt ist, dass der Turboverdichter 103 auf die vorherbestimmte Drehzahl eingeregelt wird.Furthermore, with the steam of the main steam line 106, a further steam turbine 108 is driven, which in turn is coupled via a clutch 105 with a turbo compressor 103 to its drive. The rotational speed of the turbocompressor 103 is regulated by means of a rotational speed feedback device 109 which controls a live steam valve 108a. Thus, under specification of a predetermined speed for the turbocompressor 103 by means of the speed feedback device 109, the main steam valve 108a is controlled such that the supplied from the main steam line 106 of the steam turbine 108 steam amount is set such that the turbocompressor 103 is adjusted to the predetermined speed.

Aus regelungs- und prozesstechnischen Gründen ist die Dampfturbine 108 zum Antrieb des Turboverdichters 103 überdimensioniert ausgelegt. Die Dampfturbine 108 hat bei minimalen Parametern der Frischdampfleitung 106 eine maximal erforderliche Antriebsleistung des Turboverdichters 103 bereitzustellen. Außerdem hat die Dampfturbine 108 auch bei reduzierten Frischdampfparametern das Anfahren des Turboverdichters 103 zu ermöglichen. Im Nennbetrieb wird die Dampfturbine 108 deshalb nur mit ca. 70 % des maximalen Dampfdurchsatzes beaufschlagt. Dies hat zur Folge, dass die Dampfturbine 108 in der überwiegenden Betriebszeit mit dem Frischdampfventil 108a gedrosselt gefahren wird. Dadurch liegt der Wirkungsgrad der Dampfturbine 108 weit unterhalb von deren Wirkungsgradmaximum.For control and process reasons, the steam turbine 108 is designed to drive the turbocompressor 103 oversized. The steam turbine 108 has to provide a maximum required drive power of the turbocompressor 103 with minimal parameters of the live steam line 106. In addition, the steam turbine 108 has to allow the start of the turbocompressor 103 even with reduced live steam parameters. In rated operation, the steam turbine 108 is therefore acted upon only about 70% of the maximum steam flow rate. This has the consequence that the steam turbine 108 is driven throttled in the majority of the operating time with the main steam valve 108a. As a result, the efficiency of the steam turbine 108 is far below its maximum efficiency.

Mittels der Dampfturbine 102 und des Generators 101 wird der überschüssige Frischdampf, der in der Frischdampfleitung 106 zur Verfügung steht, verstromt. Jedoch ist das zusätzliche Vorsehen der Dampfturbine 102 und des Generators 106 in der Anlage aufwendig und kostspielig.By means of the steam turbine 102 and the generator 101, the excess live steam, which is available in the main steam line 106, is converted into electricity. However, the additional provision of the steam turbine 102 and generator 106 in the plant is expensive and expensive.

In Fig. 3 ist ein herkömmlicher Strang aufweisend einen Generator 101, eine Dampfturbine 102 und einen Turboverdichter 103 gezeigt. Die Dampfturbine 102 wird mit Frischdampf aus einer Frischdampfleitung 106 gespeist und ist, mittels einer Kupplung 104 mit dem Generator 101 und mittels einer Kupplung 105 mit dem Turboverdichter 103 zum Antreiben gekoppelt.In Fig. 3 For example, a conventional train including a generator 101, a steam turbine 102, and a turbocompressor 103 is shown. The steam turbine 102 is supplied with live steam from a live steam line 106 and is coupled by means of a clutch 104 to the generator 101 and by means of a clutch 105 to the turbo-compressor 103 for driving.

Die in dem Generator 101 erzeugte elektrische Leistung wird an ein elektrisches Netz 107 abgegeben. Der Turboverdichter 103 wird bei konstanter Drehzahl betrieben.The electric power generated in the generator 101 is output to an electric network 107. The turbocompressor 103 is operated at a constant speed.

Die Dampfturbine 102 wird aus den vorher genannten Gründen bei Nennlast und Teillast gedrosselt gefahren, so dass der Wirkungsgrad der Dampfturbine 102 ebenfalls unterhalb ihres Wirkungsgradoptimums liegt. Ferner besteht keine Möglichkeit den Turboverdichter 103 über die Drehzahl zu regeln, was zu einem Wirkungsgradverlust des Gesamtprozesses führt.The steam turbine 102 is driven throttled at rated load and partial load for the reasons mentioned above, so that the efficiency of the steam turbine 102 is also below its optimum efficiency. Furthermore, there is no possibility to regulate the turbocompressor 103 via the rotational speed, which leads to a loss of efficiency of the overall process.

Aufgabe der Erfindung ist es einen Generator-Dampfturbine-Turboverdichter-Strang und ein Verfahren zum Betreiben desselben zu schaffen, wobei der Generator-Dampfturbine-Turboverdichter-Strang einen hohen Wirkungsgrad, eine gute Regelbarkeit und geringe Investitionskosten hat.The object of the invention is to provide a generator-steam turbine-turbocompressor train and a method for operating the same, wherein the generator-steam turbine-turbocompressor train has a high efficiency, good controllability and low investment costs.

Der erfindungsgemäße Generator-Dampfturbine-Turboverdichter-Strang weist einen frequenzvariablen Generator, eine Dampfturbine und einen von dem Generator und/oder der Dampfturbine antreibbaren Turboverdichter auf, die zu einem Wellenstrang zusammengekoppelt sind, wobei der Generator an ein elektrisches Netz zur Netzeinspeisung elektrisch koppelbar ist und die Dampfturbine an eine Frischdampfzuführleitung zum Zuführen von Frischdampf zu der Dampfturbine anschließbar ist, so das der Generator-Dampfturbine-Turboverdichter-Strang über eine Variation der Netzeinspeisung und/oder über die Frischdampfzufuhr drehzahlregelbar ist.The generator-steam turbine-turbocompressor train according to the invention comprises a frequency-variable generator, a steam turbine and a turbo-compressor driven by the generator and / or the steam turbine, which are coupled together to form a shaft train, wherein the generator is electrically coupled to an electrical grid for feeding in the grid and the steam turbine can be connected to a live steam supply line for supplying live steam to the steam turbine, so that the generator-steam turbine-turbocompressor train can be speed-controlled via a variation of the mains supply and / or via the live steam supply.

Das erfindungsgemäße Verfahren zum Betreiben des Generator-Dampfturbine-Turboverdichter-Strangs weist die Schritte auf: Bereitstellen des Generator-Dampfturbine-Turboverdichter-Strangs; Variieren der Netzeinspeisung des Generators und/oder variieren der Frischdampfzufuhr zu der Dampfturbine zum Drehzahlregeln des Generator-Dampfturbine-Turboverdichter-Strangs.The method according to the invention for operating the generator / steam turbine / turbocompressor train has the steps: Providing the generator-steam turbine-turbocompressor string; Vary the grid feed of the generator and / or vary the live steam supply to the steam turbine for speed control of the generator-steam turbine-turbocompressor train.

In dem Generator-Dampfturbine-Turboverdichter-Strang ist der Turboverdichter von der Dampfturbine antreibbar, wobei die dem Strang bereitgestellte Prozessenergie vollständig umgewandelt wird. Dadurch, dass die Dampfturbine den Generator antreibt ist ein zusätzlicher Generatorantrieb nicht vorzusehen, so dass die Investitionskosten für den Generator-Dampfturbine-Turboverdichter-Strang gering sind.In the generator-steam turbine-turbocompressor train, the turbocompressor is drivable from the steam turbine, completely converting the process energy provided to the train. Because the steam turbine drives the generator, an additional generator drive is not provided, so that the investment costs for the generator / steam turbine / turbocompressor train are low.

Die Dampfturbine in dem Generator-Dampfturbine-Turboverdichter-Strang ist mit einem voll ausgesteuerten Dampfregelventil fahrbar. Dies führt zu einem hohen Wirkungsgrad der Dampfturbine, so dass die Ausbeute der Prozessenergie hoch ist.The steam turbine in the generator-steam turbine-turbocompressor train is mobile with a fully controlled steam control valve. This leads to a high efficiency of the steam turbine, so that the yield of the process energy is high.

Ferner ist es ermöglicht; dass die Leistung des Turboverdichters in dem Generator-Dampfturbine-Turboverdichter-Strang durch die variable Drehzahl regelbar ist, wodurch die Leistungsregelung des Turboverdichters effektiv ist.It is also possible; that the power of the turbocompressor in the generator-steam turbine-turbocompressor train is controllable by the variable speed, whereby the power control of the turbocompressor is effective.

Beim Anfahren des Turboverdichters kann der Generator als ein Motor betrieben werden, wodurch beim Anfahren des Turboverdichters durch den Generator eine zusätzliche Antriebsleistung bereitgestellt ist. Dadurch braucht die Dampfturbine nicht derart ausgelegt zu sein, dass das Anfahren des Turboverdichters bei eventuell vorliegenden niedrigen Dampfparametern bei hohem Leistungsbedarf des Turboverdichters bewerkstelligbar ist. Somit ist die Dampfturbine kostengünstig ausführbar, wodurch die Investitionskosten für die Dampfturbine gering sind. Außerdem ist die Dampfturbine im Normalbetrieb nicht oder nur gering gedrosselt fahrbar, wodurch der Wirkungsgrad der Dampfturbine hoch ist.When starting the turbocompressor, the generator can be operated as a motor, whereby an additional drive power is provided when starting the turbocompressor by the generator. As a result, the steam turbine need not be designed so that the start of the turbocompressor can be accomplished at any high steam power requirements of the turbocompressor in case of low steam parameters. Thus, the steam turbine is inexpensive to carry out, whereby the investment costs for the steam turbine are low. In addition, the steam turbine in normal operation is not or only slightly throttled mobile, whereby the efficiency of the steam turbine is high.

Bevorzugt weist die Dampfturbine ein Frischdampfventil zum Zuführen des Frischdampfs von der Frischdampfzufuhreinrichtung zu der Dampfturbine auf, wobei mit dem Frischdampfventil die Frischdampfzufuhr regelbar ist, so dass der Generator-Dampfturbine-Turboverdichter-Strang mittels des Frischdampfventil drehzahlregelbar ist.The steam turbine preferably has a live steam valve for supplying the live steam from the live steam supply device to the steam turbine, wherein the live steam feed can be regulated with the live steam valve, so that the generator steam turbine turbo compressor train can be speed controlled by means of the live steam valve.

Dadurch ist es ermöglicht, dass die Energiezufuhr zu der Dampfturbine mit dem Frischdampfventil regelbar ist, das dafür eine entsprechende Ventilstellung hat. Dadurch ist die Leistungsabgabe der Dampfturbine und somit die Drehzahl der Dampfturbine einfach regelbar.This makes it possible that the power supply to the steam turbine with the main steam valve is controllable, which has a corresponding valve position. As a result, the power output of the steam turbine and thus the speed of the steam turbine is easily controlled.

Ferner ist es bevorzugt, dass der Generator-Dampfturbine-Turboverdichter-Strang einen Frequenzumrichter aufweist, mit dem der Generator an das elektrische Netz zur Netzeinspeisung elektrisch koppelbar ist und die Leistung des Generators regelbar ist, so dass der Generator-Dampfturbine-Turboverdichter-Strang mittels des Frequenzumrichters drehzahlregelbar ist.Further, it is preferred that the generator-steam turbine-turbocompressor train comprises a frequency converter, with which the generator is electrically coupled to the electrical network for feeding in the grid and the power of the generator is controllable, so that the generator-steam turbine-turbocompressor train by means of the frequency converter is speed controllable.

Mittels des Frequenzumrichters ist die Leistungsabgabe des Generators bei der Netzeinspeisung variabel, so dass der Leistungsbedarf des Generators an den Leistungsbedarf des Turboverdichters anpassbar ist. Dadurch ist die Antriebsleistung der Dampfturbine vorgebbar und somit an das Leistungsangebot der Frischdampfzufuhreinrichtung anpassbar. Dadurch kann das vollständige Dampfangebot der Frischdampfzufuhreinrichtung in der Dampfturbine entspannt werden, wobei der Turboverdichter bei einem gewünschten Betriebszustand betreibbar ist.By means of the frequency converter, the power output of the generator is variable in the grid feed, so that the power requirement of the generator is adaptable to the power requirement of the turbocompressor. As a result, the drive power of the steam turbine can be predetermined and thus adapted to the power supply of the live steam supply device. As a result, the complete steam supply of the live steam supply device in the steam turbine can be expanded, the turbo compressor being operable at a desired operating state.

Bevorzugt ist es, dass der Generator sowohl im Generatorbetrieb als auch im Antriebsmotorbetrieb betreibbar ist.It is preferred that the generator is operable both in the generator mode and in the drive motor mode.

Wird der Generator im Antriebsmotorbetrieb betrieben, so ist von dem Generator eine zusätzliche Antriebsleistung bereitgestellt. Diese zusätzliche Antriebsleistung kann beispielsweise beim Anfahren des Turboverdichters erforderlich sein, wenn beispielsweise das Dampfangebot der Frischdampfzufuhreinrichtung zu gering zum Anfahren des Turboverdichters ist. Dadurch ist es ermöglicht, den Turboverdichter dennoch anzufahren, obwohl die Antriebsleistung der Dampfturbine alleine nicht ausreichen würde. Beim Antriebsmotorbetrieb bezieht der Generator Leistung aus dem Netz.If the generator is operated in drive motor mode, an additional drive power is provided by the generator. This additional drive power can, for example be required when starting the turbocompressor, for example, if the steam supply of the live steam supply device is too low to start the turbo compressor. This makes it possible to start the turbocompressor yet, although the drive power of the steam turbine alone would not be enough. During drive motor operation, the generator draws power from the grid.

Bevorzugt ist der Generator ein hochdrehender Generator.Preferably, the generator is a high-speed generator.

Bei dem Verfahren zum Betreiben des Generator-Dampfturbine-Turboverdichter-Strangs sind ferner die Schritte bevorzugt: Bereitstellen der Dampfturbine mit dem Frischdampfventil; Variieren der Stellung des Frischdampfventils zum Drehzahlregeln des Generator-Dampfturbine-Turboverdichter-Strangs; Beim Normalbetrieb: Betreiben der Dampfturbine mit voll ausgesteuertem Frischdampfventil.In the method for operating the generator-steam turbine-turbocompressor train, the steps are further preferred: providing the steam turbine with the live steam valve; Varying the position of the live steam valve to control the speed of the generator-steam turbine-turbocompressor train; In normal operation: operating the steam turbine with fully controlled live steam valve.

Dadurch wird im Normalbetrieb die Dampfturbine bei Nennlast und nicht bei Teillast betrieben, so dass der Wirkungsgrad der Dampfturbine hoch ist.As a result, the steam turbine is operated at nominal load and not at partial load in normal operation, so that the efficiency of the steam turbine is high.

Ferner sind bei dem Verfahren zum Betreiben des Generator-Dampfturbine-Turboverdichter-Strangs die Schritte bevorzugt: Bereitstellen des Generator-Dampfturbine-Turboverdichter-Strangs mit dem Frequenzumrichter; Variieren der Leistung des Generators mit dem Frequenzumrichter zum Drehzahlregeln des Generator-Dampfturbine-Turboverdichter-Strangs.Further, in the method of operating the generator-steam turbine-turbocompressor train, the steps of: providing the generator-steam turbine-turbocompressor train with the frequency converter; Varying the power of the generator with the frequency converter to control the speed of the generator-steam turbine-turbocompressor train.

Außerdem sind bei dem Verfahren zum Betreiben des Generator-Dampfturbine-Turboverdichter-Strangs die Schritte bevorzugt: Bereitstellen des Generators als im Generatorbetrieb als auch im Antriebsmotorbetrieb betreibbar; Beim Anfahrbetrieb: Betreiben des Generators im Antriebsmotorbetrieb.In addition, in the method of operating the generator-steam turbine-turbocompressor train, the steps of: providing the generator as operable in generator mode as well as in drive motor mode are preferred; During start-up operation: Operation of the generator in drive motor operation.

Im folgenden wird die Erfindung anhand eines bevorzugten Ausführungsbeispiels des erfindungsgemäßen Generator-Dampfturbine-Turboverdichter-Strangs gezeigt. Es zeigt:

Fig. 1
eine schematische Darstellung des erfindungsgemäßen Generator-Dampfturbine-Turboverdichter-Strangs,
Fig. 2
einen Dampfturbine-Turboverdichter-Strang und einen Dampfturbine-Generator-Strang gemäß dem Stand der Technik und
Fig. 3
einen Generator-Dampfturbine-Turboverdichter-Strang gemäß dem Stand der Technik.
In the following the invention with reference to a preferred embodiment of the generator-steam turbine-turbocompressor train according to the invention is shown. It shows:
Fig. 1
a schematic representation of the generator-steam turbine-turbocompressor string according to the invention,
Fig. 2
a steam turbine-turbocompressor train and a steam turbine generator train according to the prior art and
Fig. 3
a generator-steam turbine-turbocompressor string according to the prior art.

Wie es aus Fig. 1 ersichtlich ist, weist ein Generator-Dampfturbine-Turboverdichter-Strang 1 einen Generator 2, eine Dampfturbine 3 und einen Turboverdichter 4 auf, die einen Wellenstrang 5 bilden. Die Dampfturbine 3 ist zum Antreiben des Generators 2 mit diesem Mittels einer ersten Kupplung 5a gekuppelt und zum Antreiben des Turboverdichters 4 mittels einer zweiten Kupplung 5b gekuppelt. Die Dampfturbine 3 wird mit Dampf von einer Frischdampfzufuhreinrichtung 7 betrieben, wobei die Dampfströmung zu der Dampfturbine 3 von einem Frischdampfventil 8 regelbar ist. Das Frischdampfventil 8 ist mittels einer Drehzahlrückkopplungseinrichtung 10 mit der Drehzahl des Wellenstrangs 5 gekoppelt. Mittels der Drehzahlrückkopplungseinrichtung 10 ist das Frischdampfventil 8 derart ansteuerbar, dass der Wellenstrang 5 drehzahlgeregelt ist.Like it out Fig. 1 As can be seen, has a generator-steam turbine-turbocompressor train 1 a generator 2, a steam turbine 3 and a turbocompressor 4, which form a shaft 5 strand. The steam turbine 3 is coupled to drive the generator 2 with this means of a first clutch 5a and coupled to drive the turbocompressor 4 by means of a second clutch 5b. The steam turbine 3 is operated with steam from a live steam supply device 7, the steam flow to the steam turbine 3 being controllable by a live steam valve 8. The main steam valve 8 is coupled by means of a speed feedback device 10 with the rotational speed of the shaft train 5. By means of the speed feedback device 10, the main steam valve 8 can be controlled such that the shaft train 5 is speed-controlled.

Der Generator 2 ist via einen Frequenzumrichter 9 mit einem elektrischen Netz 6 zur Netzeinspeisung gekoppelt. Der Frequenzumrichter 9 ist mittels einer Drehzahlrückkopplungseinrichtung 11 mit der Drehzahl des Wellenstrangs 5 gekoppelt.The generator 2 is coupled via a frequency converter 9 to an electrical network 6 for feeding in the grid. The frequency converter 9 is coupled by means of a speed feedback device 11 with the rotational speed of the shaft train 5.

Die Dampfturbine 3 ist mittels des Frischdampfventils 8 und der Drehzahlrückkopplungseinrichtung 10 zum drehzahlgeregelten Antrieb des Turboverdichters 4 eingerichtet. Ferner ist die Dampfturbine 3 zum Antrieb des Generators 2 auf einem Wellenstrang 5 kombiniert. Der Generator 2 und der Frequenzumrichter 9 können, falls die Randbedingungen bein Anfahren des Turboverdichters 4 eine zusätzliche Hilfsenergie erfordern, auch motorisch betrieben werden. Die Dampfturbine 3 wird im Normalbetrieb mit dem voll ausgesteuerten Frischdampfventil 8 gefahren, so dass die Dampfturbine im Nennbetrieb bei hohem Wirkungsgrad betrieben werden kann.The steam turbine 3 is set up by means of the live steam valve 8 and the speed feedback device 10 for speed-controlled drive of the turbocompressor 4. Furthermore, the steam turbine 3 is combined to drive the generator 2 on a shaft train 5. The generator 2 and the frequency converter 9 can, if the boundary conditions require starting the turbocompressor 4 an additional power supply, also be operated by motor. The steam turbine 3 is driven in normal operation with the fully controlled live steam valve 8, so that the steam turbine can be operated in nominal operation at high efficiency.

Die im Nennbetrieb der Dampfturbine 3 vorhandene Überschussleistung wird im Generator 2 zur Erzeugung von elektrischer Leistung genutzt.The existing in nominal operation of the steam turbine 3 excess power is used in the generator 2 for generating electrical power.

Mit Hilfe des Frequenzumrichters 9 wird durch den Generator 2 Drehstrom mit der jeweiligen Netzfrequenz des Netzes 6 erzeugt, der in das Netz 6 eingespeist werden kann. Im Bedarfsfall kann der Generator 3 im Motorbetrieb eine zusätzliche mechanische Leistung zum Anfahren des Turboverdichters 4 bereitstellen. Die Drehzahlregelung des Wellenstrangs 5 erfolgt entweder über die Anpassung der Netzeinspeiseleistung oder bei konstanter Leistung des Generators 2 über das Frischdampfventil 8 der Dampfturbine 2. Die Leistungsregelung des Generators 2 erfolgt im Frequenzumrichter 9.With the help of the frequency converter 9 is generated by the generator 2 three-phase current with the respective network frequency of the network 6, which can be fed into the network 6. If necessary, the generator 3 can provide an additional mechanical power for starting the turbocompressor 4 during engine operation. The speed control of the shaft train 5 is carried out either via the adjustment of the grid feed power or at constant power of the generator 2 via the main steam valve 8 of the steam turbine 2. The power control of the generator 2 takes place in the frequency converter. 9

Claims (9)

Generator-Dampfturbine-Turboverdichter-Strang (1) mit einem frequenzvariablen Generator (2), einer Dampfturbine (3) und einem von dem Generator (2) und/oder der Dampfturbine (3) antreibbaren Turboverdichter (4), die zu einem Wellenstrang (5) zusammengekoppelt sind, wobei der Generator (2) an ein elektrisches Netz (6) zur Netzeinspeisung elektrisch koppelbar ist und die Dampfturbine (3) an eine Frischdampfzufuhreinrichtung (7) zum Zuführen von Frischdampf zu der Dampfturbine (3) anschließbar ist, so dass der Generator-Dampfturbine-Turboverdichter-Strang (1) über eine Variation der Netzeinspeisung und/oder über die Frischdampfzufuhr drehzahlregelbar ist.Generator-steam turbine-turbocompressor train (1) with a variable-frequency generator (2), a steam turbine (3) and one of the generator (2) and / or the steam turbine (3) drivable turbocompressors (4), which form a shaft train ( 5) are coupled together, wherein the generator (2) is electrically coupled to an electrical network (6) for feeding in the grid and the steam turbine (3) to a live steam supply means (7) for supplying live steam to the steam turbine (3) is connectable, so that the generator-steam turbine-turbocompressor train (1) is variable in speed via a variation of the mains supply and / or via the live steam supply. Generator-Dampfturbine-Turboverdichter-Strang (1) gemäß Anspruch 1, wobei die Dampfturbine (3) ein Frischdampfventil (8) zum Zuführen des Frischdampfs von der Frischdampfzufuhreinrichtung (7) zu der Dampfturbine (3) aufweist, wobei mit dem Frischdampfventil (8) die Frischdampfzufuhr regelbar ist, so dass der Generator-Dampfturbine-Turboverdichter-Strang (1) mittels des Frischdampfventils (8) drehzahlregelbar ist.Generator-steam turbine-turbocompressor train (1) according to claim 1, wherein the steam turbine (3) has a live steam valve (8) for supplying the live steam from the live steam supply device (7) to the steam turbine (3), wherein with the live steam valve (8) the live steam supply is controllable, so that the generator-steam turbine-turbocompressor train (1) can be speed-controlled by means of the live steam valve (8). Generator-Dampfturbine-Turboverdichter-Strang (1) gemäß Anspruch 1 oder 2, wobei der Generator-Dampfturbine-Turboverdichter-Strang (1) einen Frequenzumrichter (9) aufweist, mit dem der Generator (2) an das elektrische Netz (6) zur Netzeinspeisung elektrisch koppelbar ist und die Leistung des Generators (2) regelbar ist, so dass der Generator-Dampfturbine-Turboverdichter-Strang (1) mittels des Frequenzumrichters (9) drehzahlregelbar ist.Generator-steam turbine-turbocompressor train (1) according to claim 1 or 2, wherein the generator-steam turbine-turbocompressor train (1) comprises a frequency converter (9), with which the generator (2) to the electrical network (6) Mains supply is electrically coupled and the power of the generator (2) is adjustable, so that the generator-steam turbine-turbocompressor train (1) by means of the frequency converter (9) is speed controlled. Generator-Dampfturbine-Turboverdichter-Strang (1) gemäß einem der Ansprüche 1 bis 3, wobei der Generator (2) sowohl im Generatorbetrieb als auch im Antriebsmotorbetrieb betreibbar ist.Generator-steam turbine-turbocompressor train (1) according to one of claims 1 to 3, wherein the generator (2) is operable both in the generator mode and in the drive motor mode. Generator-Dampfturbine-Turboverdichter-Strang (1) gemäß einem der Ansprüche 1 bis 4, wobei der Generator (2) ein hochdrehender Generator ist.A generator-steam turbine-turbocompressor string (1) according to any one of claims 1 to 4, wherein the generator (2) is a high-speed generator. Verfahren zum Betreiben eines Generator-Dampfturbine-Turboverdichter-Strangs (1) gemäß einem der Ansprüche 1 bis 5, aufweisend die Schritte: - Bereitstellen des Generator-Dampfturbine-Turboverdichter-Strangs (1); - Variieren der Netzeinspeisung des Gerators (2) und/oder Variieren der Frischdampfzufuhr zu der Dampfturbine (3) zum Drehzahlregeln des Generator-Dampfturbine-Turboverdichter-Strangs (1). A method of operating a generator-steam turbine-turbocompressor string (1) according to any one of claims 1 to 5, comprising the steps of: - providing the generator-steam turbine-turbocompressor train (1); - Varying of the mains supply of the gerator (2) and / or varying the live steam supply to the steam turbine (3) for speed control of the generator-steam turbine-turbocompressor train (1). Verfahren gemäß Anspruch 6, mit den Schritten: - Bereitstellen der Dampfturbine (3) mit dem Frischdampfventil (8); - Variieren der Stellung des Frischdampfventils (8) zum Drehzahlregeln des Generator-Dampfturbine-Turboverdichter-Strangs (1); - Beim Normalbetrieb: Betrieben der Dampfturbine (3) mit voll ausgesteuertem Frischdampfventil (8). Method according to claim 6, comprising the steps: - Providing the steam turbine (3) with the main steam valve (8); - varying the position of the live steam valve (8) for speed control of the generator-steam turbine-turbocompressor train (1); - In normal operation: Operate the steam turbine (3) with fully controlled live steam valve (8). Verfahren gemäß Anspruch 6 oder 7, mit den Schritten: - Bereitstellen des Generator-Dampfturbine-Turboverdichter-Strangs (1) mit dem Frequenzumrichter (9); - Variieren der Leistung des Generators (2) mit dem Frequenzumrichter (9) zum Drehzahlregeln des Generator-Dampfturbine-Turboverdichter-Strangs (1). Method according to claim 6 or 7, comprising the steps: - Providing the generator-steam turbine-turbocompressor train (1) with the frequency converter (9); - Varying the power of the generator (2) with the frequency converter (9) for speed control of the generator-steam turbine-turbocompressor train (1). Verfahren gemäß einem der Ansprüche 6 bis 8, mit den Schritten: - Bereitstellen des Generators (2) als im Generatorbetrieb als auch im Antriebsmotorbetrieb betreibbar; - Beim Anfahrbetrieb: Betreiben des Generators (2) im Antriebsmotorbetrieb. Method according to one of claims 6 to 8, comprising the steps: - Providing the generator (2) as operable in the generator mode and in the drive motor operation; - During start-up operation: Operation of the generator (2) in drive motor operation.
EP07019475A 2007-10-04 2007-10-04 Generator-gas turbine-turbo compressor line and method for operating the same Not-in-force EP2045441B1 (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
ES07019475T ES2343336T3 (en) 2007-10-04 2007-10-04 VAPOR-TURBOCOMPRESSOR GENERATOR-TURBINE ALIGNED ASSEMBLY AND PROCEDURE TO OPERATE THE SAME.
DE502007004025T DE502007004025D1 (en) 2007-10-04 2007-10-04 Generator-steam turbine-turbocompressor string and method of operating the same
AT07019475T ATE470049T1 (en) 2007-10-04 2007-10-04 GENERATOR STEAM TURBINE TURBO COMPRESSOR STRAIN AND METHOD FOR OPERATING THE SAME
EP07019475A EP2045441B1 (en) 2007-10-04 2007-10-04 Generator-gas turbine-turbo compressor line and method for operating the same
PL07019475T PL2045441T3 (en) 2007-10-04 2007-10-04 Generator-gas turbine-turbo compressor line and method for operating the same
JP2010527443A JP4940352B2 (en) 2007-10-04 2008-10-01 Generator / steam turbine / turbo compressor line and method for operating generator / steam turbine / turbo compressor line
RU2010117378/06A RU2478795C2 (en) 2007-10-04 2008-10-01 Line of generator-steam turbine-turbocompressor and method for its operation
MX2010003515A MX2010003515A (en) 2007-10-04 2008-10-01 Generator-steam turbine-turbocompressor-line and method for the operation thereof.
CN200880109922A CN101815845A (en) 2007-10-04 2008-10-01 Generator-steam turbine-turbocompressor-line and method for the operation thereof
BRPI0817803A BRPI0817803A2 (en) 2007-10-04 2008-10-01 turbine line - steam generator turbocharger and method for operating it
US12/680,973 US8575774B2 (en) 2007-10-04 2008-10-01 Generator-stream turbine-turbocompressor string regulated by variation of a mains power supplied and by a live steam feed and method for operating the same
KR1020107009661A KR101531831B1 (en) 2007-10-04 2008-10-01 Generator-steam turbine-turbocompressor-line and method for the operation thereof
PCT/EP2008/063149 WO2009043875A1 (en) 2007-10-04 2008-10-01 Generator-steam turbine-turbocompressor-line and method for the operation thereof

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EP (1) EP2045441B1 (en)
JP (1) JP4940352B2 (en)
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AT (1) ATE470049T1 (en)
BR (1) BRPI0817803A2 (en)
DE (1) DE502007004025D1 (en)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102330573A (en) * 2010-10-22 2012-01-25 靳北彪 Pressure gas turbine booster system
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ITFI20120245A1 (en) 2012-11-08 2014-05-09 Nuovo Pignone Srl "GAS TURBINE IN MECHANICAL DRIVE APPLICATIONS AND OPERATING METHODS"
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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS585407A (en) 1981-07-01 1983-01-12 Ishikawajima Harima Heavy Ind Co Ltd Equipment for driving by exhaust gas
JPS6299602A (en) 1985-10-24 1987-05-09 Toshiba Corp Steam turbine control device
WO2006084809A1 (en) 2005-02-10 2006-08-17 Alstom Technology Ltd Method for activating a pressure storage system, and a pressure storage system

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4441028A (en) * 1977-06-16 1984-04-03 Lundberg Robert M Apparatus and method for multiplying the output of a generating unit
DE3437872C1 (en) 1984-10-16 1986-05-28 M.A.N.-B & W Diesel GmbH, 8900 Augsburg Control device for an internal combustion engine with an exhaust gas turbocharger
JPS62131798A (en) 1985-11-28 1987-06-15 Fuji Electric Co Ltd Generator apparatus
SU1623077A1 (en) * 1989-03-21 1995-08-20 А.К. Васильев Shipboard power plant with shaft generator
JP2593578B2 (en) * 1990-10-18 1997-03-26 株式会社東芝 Combined cycle power plant
DE19757588A1 (en) * 1996-12-24 1998-07-02 Hitachi Ltd Electricity generating system with gas turbine and energy storage
EP1189336A1 (en) * 2000-09-14 2002-03-20 Abb Research Ltd. Generator system with gas-turbine
US6750557B2 (en) * 2001-09-06 2004-06-15 Energy Transfer Group, L.L.C. Redundant prime mover system
CH696980A5 (en) 2003-12-22 2008-02-29 Alstom Technology Ltd Method for starting power station installation in deactivated electricity network, involves forming connection between generator of pressure store-relaxation turbine and start device of gas turbine group
US7526926B2 (en) * 2003-11-06 2009-05-05 Exxonmobil Upstream Research Company Method for efficient nonsynchronous LNG production
EP1917428B1 (en) * 2005-08-23 2017-12-13 General Electric Technology GmbH Method of operating a power plant which comprises a pressure storage vessel
US7681401B2 (en) * 2006-08-24 2010-03-23 General Electric Company Methods and systems for operating a gas turbine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS585407A (en) 1981-07-01 1983-01-12 Ishikawajima Harima Heavy Ind Co Ltd Equipment for driving by exhaust gas
JPS6299602A (en) 1985-10-24 1987-05-09 Toshiba Corp Steam turbine control device
WO2006084809A1 (en) 2005-02-10 2006-08-17 Alstom Technology Ltd Method for activating a pressure storage system, and a pressure storage system

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102330573A (en) * 2010-10-22 2012-01-25 靳北彪 Pressure gas turbine booster system
EP3301267A1 (en) * 2016-09-29 2018-04-04 Siemens Aktiengesellschaft Method and device for operating a turbo set
WO2018059864A1 (en) * 2016-09-29 2018-04-05 Siemens Aktiengesellschaft Method for operating a turbogenerator

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ES2343336T3 (en) 2010-07-28
US20100213709A1 (en) 2010-08-26
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RU2010117378A (en) 2011-11-10
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EP2045441B1 (en) 2010-06-02
KR20100065394A (en) 2010-06-16

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