EP1483490A1 - Systeme de production d'energie - Google Patents

Systeme de production d'energie

Info

Publication number
EP1483490A1
EP1483490A1 EP03714951A EP03714951A EP1483490A1 EP 1483490 A1 EP1483490 A1 EP 1483490A1 EP 03714951 A EP03714951 A EP 03714951A EP 03714951 A EP03714951 A EP 03714951A EP 1483490 A1 EP1483490 A1 EP 1483490A1
Authority
EP
European Patent Office
Prior art keywords
pressure
machine
heat
power generation
temperature
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Withdrawn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
EP03714951A
Other languages
German (de)
English (en)
Inventor
Rolf Dittmann
Hans Ulrich Frutschi
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.)
General Electric Technology GmbH
Original Assignee
Alstom Technology 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
Application filed by Alstom Technology AG filed Critical Alstom Technology AG
Publication of EP1483490A1 publication Critical patent/EP1483490A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C1/00—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid
    • F02C1/04—Gas-turbine plants characterised by the use of hot gases or unheated pressurised gases, as the working fluid the working fluid being heated indirectly
    • F02C1/10—Closed cycles
    • F02C1/105—Closed cycles construction; details
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T50/00—Aeronautics or air transport
    • Y02T50/60—Efficient propulsion technologies, e.g. for aircraft

Definitions

  • the present invention relates to a power generation system, in particular a power plant, according to the preamble of claim 1. It also relates to a method for operating a power plant according to the invention.
  • Power plant systems in which a secondary machine of a gas turbine group acting as a primary machine is used for waste heat recovery are known per se as combined cycle power plants.
  • a waste heat steam generator is arranged in the exhaust tract of a gas turbine group, in which a quantity of steam is generated which is used to drive a steam turbine. Process or heating steam can also be withdrawn.
  • a power plant is known from EP 924 410, in which a secondary open gas turbine group is connected downstream of the primary gas turbine group. Both types show a comparatively poor scalability of the operation for different waste heat offers.
  • a downstream steam system for example, there must always be sufficient overheating of the live steam in order to avoid excessive wetness in the steam turbine. Avoid amplifiers.
  • the secondary steam circuit is therefore normally not operable below a minimum exhaust gas temperature of the primary engine.
  • large evaporative floods and a large condenser are necessary due to the usually low condenser pressure.
  • the gas turbine group is able to cope better with the decreasing temperature level of the exhaust gas from an operational point of view.
  • the supply of waste heat varies due to a preliminary row adjustment of the primary machine, and the temperature level of the waste heat remains approximately constant, the case will also occur that the secondary machine is no longer able to reach the possible upper process temperature.
  • the turbine inlet temperature of the secondary machine thus becomes lower than would be possible; as a result, the efficiency of the secondary gas turbine process drops. Due to the overall comparatively low temperature level, such effects quickly become significant.
  • the essence of the invention is therefore to arrange as a secondary machine a machine working with a gaseous process fluid with a completely closed fluid circuit. It is well understood that this process fluid, process gas, does not undergo a phase change during the entire cycle of the secondary machine.
  • the gaseous process fluid is first compressed, then passed on the secondary side through the exhaust gas heat exchanger of the primary gas turbine group, where it absorbs heat, relaxes, and is completely returned to compression, preferably before and / or during the compression, heat removal from the process fluid takes place in a heat sink.
  • the materially closed routing of the process fluid offers surprising advantages, particularly for the use of waste heat:
  • the process fluid can be freely selected in order, for example, to obtain thermodynamic properties of the process fluid that are particularly suitable for low-temperature use.
  • the mass flow of the circulating fluid can be changed, so that, for example, a decrease in the amount of waste heat, combined with a decrease in the exhaust gas mass flow at a substantially constant temperature, reacts with a substantially constant pressure ratio and thus still good efficiency of the secondary machine can be.
  • the circuit filling that is to say the entire pressure level of the process, is regulated in such a way that the upper process temperature of the secondary machine in stationary operation is never more than 50 ° C., preferably 30 ° C., below the exhaust gas temperature of the primary machine, and, in particular this temperature difference, which is necessary in order to provide a temperature gradient driving the heat transfer, is regulated in a range from 5 ° C to 20 ° C; the achievable value also depends on the size of the available heat transfer surfaces.
  • the secondary machine is implemented, in particular, by arranging at least one work machine for compressing the process fluid and at least one power machine for relaxing the process fluid.
  • At least one power machine with at least one work machine and / or a power consumer is preferably arranged on a common shaft, optionally also with an intermediate gear; single-shaft or multi-shaft embodiments of the secondary machine then result.
  • the power consumer one can think of a generator, for example, but also one
  • the engine driving the generator can also act on the generator of the primary gas turbine group via an automatically acting clutch; in principle, this results in the construction of a single-shaft combination system known per se.
  • flow machines, turbines and turbocompressors are preferably used as work and power machines. With small unit outputs / fluid volume flows, this can also be done Use of displacement machines have advantages, or a cascading circuit of turbo and displacement machines.
  • the working gas turbine group is familiar with the arrangement of the heat sink in the flow path from the turbine to the compressor.
  • at least one heat sink for example as an intercooler, is arranged in direct fluid communication with the means intended for compressing the process gas.
  • An isothermal or quasi-isothermal compression can thus be achieved.
  • the reduced final compression temperature enables improved waste heat utilization.
  • the heat sinks arranged in the compression path of the compression from the low pressure of the secondary process to the high pressure of the secondary process are regulated in such a way that the compression end temperature of the secondary machine is above the dew point temperature of the exhaust gases of the primary machine by a certain, but small, safety margin lies.
  • the final compression temperature can be set to 70 ° C to 75 ° C for a gas-fired and to 130 ° C to 150 ° C for an oil-fired primary machine.
  • the compression end temperature is less than 20 ° C, preferably 2 ° C to 10 ° C, above the dew point temperature of the exhaust gas of the primary machine.
  • the secondary machine has a heat sink in the low-pressure part, in the flow path from the last engine to the first machine, which is designed as a heat recovery steam generator.
  • the steam generated there is introduced into the gaseous process fluid by means of suitable means at a pressure which is above the low pressure of the secondary machine, and is expanded with this, giving off power, and in a heat sink on the low pressure essentially condensed again.
  • the condensate is then separated from the process fluid, processed, and returned to the heat recovery steam generator by suitable means, for example a feed pump.
  • suitable means for example a feed pump.
  • the cycle of this additional medium is also closed.
  • the process gas flows back into the compression medium with a low residual moisture.
  • Figure 1 shows a first power generation system according to the invention
  • FIG. 2 shows the changes in state in the power generation system from FIG. 1 in the T, s diagram
  • FIG. 1 A power plant system according to the invention is shown in FIG. As
  • a compressor 101 and two turbines 103 and 105 are arranged on a common shaft.
  • the compressor 101 draws in an amount of air 106 from the environment.
  • fuel is mixed in the first combustion chamber 102 and burned there.
  • the flue gas is partially expanded in the first turbine 103, for example with a pressure ratio of 2.
  • the flue gas which still has a high residual oxygen content of typically over 15%, flows into a second combustion chamber 104, where further fuel is burned.
  • This reheated flue gas is expanded in the second turbine 105 to approximately ambient pressure - apart from pressure losses in the exhaust gas tract - and flows out of the gas turbine group as hot exhaust gas 107, at temperatures which are, for example, 550-600 ° C. under high load from.
  • means for using waste heat, heat exchanger 6 are arranged, in which the exhaust gas cools further before it flows into the atmosphere as cooled exhaust gas 108.
  • the heat exchanger 6 arranged as a means for utilizing waste heat transfers heat from the exhaust gas 107 of the open gas turbine group 100 to the circuit of a closed gas turbine group arranged as a secondary machine.
  • a turbine 2 is arranged with partial compressors 1a, 1b, 1c and a generator 3 on a common shaft.
  • the compressor consisting of several partial compressors 1a, 1b, 1c conveys a gas 21, in the present case air, from a low pressure upstream of the first partial compressor 1a to a high pressure downstream of the last partial compressor 1c.
  • Heat sinks, intermediate coolers 41 and 42 are arranged between the partial compressors and a coolant, for example cooling water, flows through them in countercurrent. Intercooling lowers the compressor's power consumption.
  • the compression end temperature is reduced, which in the present case also entails further advantages, which are explained below.
  • intercoolers 41 and 42 are provided with internal condensate separators 5a, 5b, the function of which will be explained below in connection with the compressor 45.
  • the compressed process gas, high-pressure process gas, 22 flows through the heat exchanger 6 in return for the exhaust gas 107; the cooled exhaust gas 108 from the primary gas turbine set flows into the atmosphere.
  • the heated high-pressure process gas 23 flows into the turbine 2 and drives it.
  • the process gas can be discarded via a shunt member 30 directly bypassing the turbine 2 on the low pressure side.
  • the expanded process gas 24 flows through a heat sink, recooler 13, and finally flows back into the compressor as low-pressure process gas 21.
  • the pressure of the low-pressure process gas 21 or the relaxed process gas 24 can be varied to control the output of the closed gas turbine group.
  • a compressor 45 conveys air to the low-pressure side of the closed gas turbine group via a non-return element 46.
  • gas is blown back into the atmosphere via a throttle and shut-off device 47.
  • Another control intervention to be implemented advantageously on the secondary cycle uses two temperature measuring points 49 for determining the temperature of the exhaust gas 107 before entering the heat exchanger 6 and 48 for determining the temperature of the heated high-pressure process gas 23 of the closed gas turbine group when it exits the heat exchanger. Both measured values are sent to a difference generator 50, where a temperature difference ⁇ T is formed. If this temperature difference exceeds a certain value, the throttle and shut-off device 47 is opened and the process pressure is reduced.
  • the mass flow of the process gas of the secondary machine drops, the compressed process gas is brought to a higher temperature and the temperature difference becomes smaller. If, however, the temperature difference falls below a lower limit value, the pressure level, in particular the pressure on the low-pressure side of the closed gas turbine group connected as a secondary machine, is increased via the compressor 45. The mass flow in the secondary machine circuit increases, and with it the temperature difference. Furthermore, the temperature of the heated high-pressure process gas 23 alone can be controlled in order to keep it constant at a desired value. Another control intervention on the lower process pressure would be the pressure ratio via the turbine 2, which is primarily is determined by the inlet volumetric flow, and is therefore dependent on the mass flow and the inlet temperature as well as the absolute pressure, to regulate to a constant value. It would also be conceivable to regulate the turbine outlet temperature of the secondary machine via the circulating mass flow. The connection of the described
  • the secondary machine is ideally operated downstream of the turbine without waste heat recuperation and with intermediate cooling in the compressor with a high design-pressure ratio of preferably 10 or more.
  • the outlet temperature from the turbine 2 and thus also the amount of heat to be dissipated in the recooler 13 is kept small at a predetermined inlet temperature into the turbine 2.
  • the associated changes in state are shown very schematically in the diagram in FIG. 2, temperature T over mass-specific entropy s.
  • the right circuit, labeled I is the circuit of the primary machine.
  • the air 106 is drawn in at a temperature TAMB and compressed by the compressor 101. Approximately isobaric heat is supplied in the combustion chamber 102 up to the maximum temperature TMAX.
  • the flue gas generated in the combustion chamber 102 is partially expanded and in the combustion chamber 104 reheated to the maximum temperature before relaxation to ambient pressure in the turbine 105 takes place.
  • the hot exhaust gas 107 has the temperature TEX.
  • the secondary cycle process II is shown to the left of the cycle process I - because it generally takes place at a superatmospheric pressure level. Its starting point is the process gas upstream of the compressor 21, which is essentially at ambient temperature and at the process low pressure.
  • the Process gas is compressed by a first partial compressor 1a, the temperature rising, then cooled in the intermediate cooler 41 to ambient temperature if possible, further compressed in a further partial compressor 1b, cooled in a second intermediate cooler 42, and in a last partial compressor 1c to a state 22 or 22 'compresses, which is on the process high pressure.
  • the cooling capacity in the last intercooler 42 is regulated in such a way that the compression end temperature of state 22 or 22 'is somewhat above the dew point temperature T D P G for gas firing or TQP O for oil firing. The lower the final compression temperature, the better the heat of the exhaust gas can be used.
  • the compressed process gas 22 absorbs heat from the exhaust gas 107 and is heated to a little below the exhaust gas temperature.
  • Exhaust gas 107 cools down as it flows through heat exchanger 6 to state 108 or 108 ′, which is due to the regulation of the compression end temperature of the secondary process with a small safety margin above the respective dew point temperature.
  • the heated process gas 23 is expanded to the state 24 in the turbine 2. Due to the high pressure ratio, this temperature is comparatively low, so that only little heat has to be removed in the recooler 13. With this design, the entire heat dissipation takes place at the lowest possible temperature, which speaks for a high degree of efficiency.
  • FIG. 1 A gas turbine group 100 of the type described above is again arranged as the primary machine.
  • a closed gas turbine group with waste heat recuperation is arranged as a secondary machine, which is described below. Since the exhaust gas heat is used, the secondary machine shown here is operated at a lower pressure ratio than the closed gas turbine group shown in connection with FIG. 1; a pressure ratio in the range from 4 to 10, in particular 6 to 8, would be regarded as typical.
  • the secondary machine is suitable for being operated with a process gas other than air.
  • the low-pressure process gas 21 of the secondary machine is compressed to a high pressure in a first partial compressor 1a and a second partial compressor 1b, between which an injection cooler 54 is arranged as an intermediate cooler.
  • the injection cooler 54 can also be readily designed so that it over-humidifies the process gas; water drops then penetrate into the following compressor stages and provide internal cooling there.
  • a corresponding injection device can also be arranged upstream of the first partial compressor. Due to the lower pressure ratio, complex additional cooler stages can be dispensed with. Nevertheless, it is advantageously ensured that the temperature of the high-pressure process gas lies above the dew point temperature of the exhaust gases 107, 108 of the primary gas turbine group.
  • the high-pressure process gas flows in countercurrent to the exhaust gases through the heat exchanger 6, which is divided into two partial heat exchangers 6a, 6b, before the heated high-pressure process gas flows through a turbine 2 with the performance of technical work.
  • the turbine 2 is with the
  • Partial compressors 1a and 1 b arranged on a common shaft, and drives them; furthermore, the power of the turbine can be transferred via an automatically acting clutch 109 to a common generator 113 of the primary and secondary machines.
  • Relaxed process gas 24 is returned to the initial state of the low-pressure process gas 21 in a heat sink designed as a heat recovery steam generator 11 and a recooler 13.
  • the heat recovery steam generator is under pressure on the secondary side standing feed water 12 - it can, because all media are conducted in a closed circuit, also act as a liquid other than water, in particular also toxic liquids.
  • the pressurized liquid is heated in the waste heat steam generator, evaporated, and the steam produced is at least slightly overheated.
  • the live steam 26 is introduced into the process gas at a temperature-adapted point of the exhaust gas heat exchanger 6, at which the steam temperature is below the exhaust gas temperature, and together with the latter flows through the second partial heat exchanger 6b.
  • the steam flows through the turbine together with the process gas, giving off power.
  • this steam including a quantity of steam which results from the liquid supply to the injection cooler 54, flows through the heat recovery steam generator 11 on the primary side, is cooled and condensed.
  • the condensation temperature is dependent on the partial pressure, corresponding to the dew point of the steam in the process gas. Further steam is condensed in the recooler 13. Condensate is separated from the process gas in the condensate separators 5a and 5b and collected in a container 17.
  • the condensate is conveyed back to the secondary side of the steam generator 11 via a pump 55 to the injection cooler 54 and in particular from a feed pump 18 as feed water 12.
  • the secondary machine is equipped with a system for varying the circuit filling and thus for varying the process pressure level.
  • a compressor 45 can branch off part of the high-pressure process fluid 22 from the circuit and convey it via a cooler 52, a separator 53 and a non-return element 46 into a high-pressure gas store 51. By shifting process fluid from the circuit into the gas storage 51, the filling of the circuit with circulating process fluid and thus the entire process pressure level is reduced.
  • the amount of fluid stored in the gas reservoir 51 can be returned to the circuit via the shut-off and throttling element 47, as a result of which the circuit filling and the pressure level increase again.
  • this variation of the circuit filling is particularly well suited for permanent power control of the secondary machine.
  • the energy stored in the high-pressure gas storage can be made available particularly quickly as useful power, since the tensioned gas acts almost directly on the turbine when the high-pressure gas storage is discharged. This spontaneous increase in output can be used particularly advantageously to support the frequency of an electricity network.
  • a wide variety of storage systems are known from the prior art, for example also storage with cascading pressure.
  • the circuit filling and thus the pressure level of the secondary machine can be regulated according to the criteria discussed in connection with FIG. 1, furthermore in such a way that a certain overheating of the steam at the turbine inlet is achieved.
  • the invention characterized in the claims can also be implemented if several primary machines act on a common secondary machine via a common heat exchanger; As has already been mentioned several times, the secondary machine of the power plant according to the invention is particularly suitable for reacting to a fluctuating amount of waste heat by operating different numbers of primary machines.
  • FIG. 4 shows an embodiment of the power plant system according to the invention, which is particularly good for small unit outputs, in connection with an industrial gas turbine or a so-called aeroderivate as the primary machine can be realized.
  • the gas turbine group 100 shown is a twin-shaft machine, with a high-pressure compressor 202 and a high-pressure turbine 203 on a common shaft and a low-pressure compressor and a low-pressure turbine on a second common shaft, which also serves as an output shaft for the useful power, and a combustion chamber.
  • Such low-power gas turbine groups usually run at a speed, which is far above the network frequency.
  • the output shaft therefore acts on the generator 113 via a reduction gear 114.
  • the mode of operation of the primary machine 100 is readily apparent in the light of the statements made above.
  • the waste heat from the hot, relaxed flue gas 107 is transferred in a heat exchanger to a secondary machine working with a gaseous process fluid in a closed circuit and is used there. Due to the small mass and volume flow of the secondary machine, a displacement machine is used to compress the process gas from low-pressure process gas 21 to high-pressure process gas 22 instead of a turbocompressor,
  • Screw compressor 1 arranged.
  • the high-pressure process gas 22 flows through a heat exchanger 6a and absorbs heat from the exhaust gas 107.
  • the heated high-pressure process gas 23 flows into a first engine designed as a displacement machine, screw expander 2a, and is expanded there to an intermediate pressure.
  • the screw expander 2 drives the screw compressor 1.
  • the intermediate pressure process gas 25 flows through a second partial heat exchanger 6b together with a fresh steam quantity 26 brought from a waste heat steam generator 11, and is reheated.
  • the now larger volumes require larger flow cross sections, which is why a turbine, in particular a radial turbine, is selected for the expansion of the intermediate pressure process gas and the steam to the low pressure.
  • This also drives the generator 113 via a second reduction gear 115 and an automatically acting clutch 109.
  • the expanded process gas 24 is returned to the
  • Initial state 21 is returned, and the steam is condensed and the condensate in the condensate separator 5 is separated from the process gas and is conveyed again by a feed pump 18 as feed water 12 to the heat recovery steam generator 11.
  • the secondary machine also has means for quick shutdown, in particular a shunt line with a
  • another power consumer in particular a mechanical drive, could also be arranged instead of a generator.
  • a mechanical drive could also be arranged instead of a generator.
  • One example would be a propeller.
  • I compression means displacement machine, screw compressor 1a, 1b, 1c compression means, partial compressor 2 expansion means, turbine

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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)

Abstract

La présente invention concerne un système de production d'énergie, par exemple une centrale électrique destinée à produire du courant, dans lequel une machine secondaire (1a, 1b, 1c, 2) est connectée en aval d'un groupe de turbine à gaz ouvert (100) qui permet l'utilisation de la chaleur des gaz d'échappement (107). La machine secondaire est une machine fonctionnant en circuit fermé avec un fluide de traitement gazeux, par exemple un groupe de turbine à gaz fermé (1a, 1b, 1c) qui comprend des compresseurs (1a, 1b, 1c), des éléments destinés à réchauffer le gaz comprimé (6) qui permettent l'utilisation de la chaleur des gaz d'échappement (107) du groupe de turbine à gaz primaire (100), une turbine (2) et au moins un puits thermique (13). Dans un mode de réalisation, des refroidisseurs intermédiaires (41, 42) sont utilisés au cours du processus de compression. Un remplissage variable du circuit de la machine secondaire permet d'obtenir une meilleure flexibilité de l'utilisation de sources de chaleur récupérée d'origines très différentes.
EP03714951A 2002-03-14 2003-03-11 Systeme de production d'energie Withdrawn EP1483490A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH4442002 2002-03-14
CH4442002 2002-03-14
PCT/EP2003/050054 WO2003076781A1 (fr) 2002-03-14 2003-03-11 Systeme de production d'energie

Publications (1)

Publication Number Publication Date
EP1483490A1 true EP1483490A1 (fr) 2004-12-08

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EP03714951A Withdrawn EP1483490A1 (fr) 2002-03-14 2003-03-11 Systeme de production d'energie

Country Status (5)

Country Link
US (1) US20050056001A1 (fr)
EP (1) EP1483490A1 (fr)
CN (1) CN1653253A (fr)
AU (1) AU2003219157A1 (fr)
WO (1) WO2003076781A1 (fr)

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CN1653253A (zh) 2005-08-10
US20050056001A1 (en) 2005-03-17
WO2003076781A1 (fr) 2003-09-18

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