WO2014161904A1

WO2014161904A1 - Energy-conversion system and sub-assemblies therefor

Info

Publication number: WO2014161904A1
Application number: PCT/EP2014/056624
Authority: WO
Inventors: Axel Widenhorn; Thilo KISSEL; Daniel BARUNOVIC; Dominik LEBKÜCHNER
Original assignee: Dürr Systems GmbH
Priority date: 2013-04-05
Filing date: 2014-04-02
Publication date: 2014-10-09
Also published as: CN205047260U; DE102013206014A1; EP2981686A1

Abstract

The invention relates to an energy-conversion system (1) comprising an installation for converting energy (2), said installation providing a heat-conducting fluid flow consisting of a first fluid (22), and a heat transfer system (4) in the form of a boiler (40) which forms a heat-transfer relationship with the system for converting energy (2, 20, 20a, 20b, 20c) by means of the fluid flow consisting of the first fluid (22). According to the invention, the system for converting energy (2) is a gas turbine system (20, 20a, 20b, 20c) comprising a gas turbine burner (201), at least part of the exhaust gases (201c) of which can be supplied to a turbine (203) in order to provide and transfer mechanical energy to a power consumer (202, 204), in particular an electric generator (204), and at least part of the exhaust gases (201c, 203c) of which form the fluid flow consisting of the first fluid (22).

Description

Description: The invention relates to an energy converter system with an energy conversion plant providing a heat conducting fluid flow from a first fluid, and a heat transfer system in the form of a boiler connected to the energy conversion plant the fluid flow is in a heat transfer relationship. Moreover, the invention also relates to a method for providing electrical and thermal energy with an energy converter system according to the preamble of the independent claims.

Under an energy converter system is in particular a system for the simultaneous provision of mechanical and thermal energy, in particular a system of a boiler, in particular a hot water boiler, hot water boiler or a steam boiler, and understood at least one gas turbine plant. In this context, a hot water boiler is understood in particular to mean a device for heating a useful medium or useful fluid, preferably a boiler, for providing a useful medium or useful fluid, in particular a liquid, heated relative to an initial state, in particular to an ambient temperature. Under a hot water boiler is in particular a device for heating a Nutzmediums or Nutzfluids, preferably a boiler for providing a relation to an initial state, especially an ambient temperature strongly heated, preferably heated to near a boiling point useful or useful fluid, in particular a liquid understood. As a rule, in the case of a hot or hot water boiler, only a small portion of the useful medium or useful fluid undergoes a phase transition, in particular sublimation or evaporation. Under "a small part" is thereby in particular understood that at most an unsaturated vapor phase of the working medium or Nutzfluids arises. In the case of a hot or hot water boiler, in particular the useful medium or useful fluid in its liquid phase is provided as provided discharge fluid at a boiler outlet for subsequent use.

A steam boiler is understood to mean, in particular, a device for heating, heating or bringing about an at least partial phase transition of a useful medium, in particular a fluid, preferably a liquid. In this context, a partial phase transition means, in particular, liquefaction, evaporation and / or sublimation of parts of the useful medium.

A preferred working fluid or useful fluid may be water, ammonia, thermal oil, suitable hydrocarbons or another suitable medium which undergoes a phase transition, in particular from a liquid to a gaseous phase, in a boiler by supplying heat at a given temperature. Boilers of the types described above can be designed as a waste heat boiler, tubular water boiler or large-scale water boiler, whereby combined boiler with a heat recovery zone, pipe water zone and / or large-area zone can be useful. Under a waste heat boiler is in particular a boiler understood, which is heated by a waste heat of an upstream, heat generating unit and does not require its own heating burner. The same applies to a waste heat zone. A tubular water boiler is understood in particular to mean a boiler in which the useful medium or useful fluid, preferably water, is passed through a piping system in the boiler and is thereby heated or heated. A tubular water boiler or a pipe water zone can also be referred to as a water heater. In contrast, under a large-scale water boiler or a large area, in particular a boiler or understood a zone in the boiler, in which a reservoir of working fluid or Nutzfluid, preferably water is provided, is introduced into the heat for heating. In this case, the heat can preferably be transferred to the useful medium or useful fluid in the reservoir by means of heat radiation and / or contact heat transfer and / or convection and / or diffusion from a heat source, for example a boiler draw or line system. In this case, a reservoir is understood in particular to be a volume in which the useful medium or useful fluid is predominantly stored or stored in a stationary state.

In the prior art, a variety of energy converter systems for the simultaneous provision of mechanical and thermal energy are already known, which is usually a system for converting energy with a burner unit for the conversion of chemical energy into heat energy by exothermic oxidation of a fuel with an Oxi have dationmittel. Further, the prior art energy converter systems include a heat and power unit for converting a portion of the heat released in the energy conversion plant into mechanical energy and a heat transfer system for transferring a second portion of the released heat to a payload medium. The mechanical energy is often used to drive a generator for downstream conversion of the mechanical energy into electrical energy, as this can be advantageously transported over long distances and / or distributed. In a frequent application, the working medium is a fluid, preferably a liquid, which is excited by the heat input from the second part of the heat released to a phase transition, in particular comes to a liquefaction, evaporation and / or sublimation of a portion of the Nutzmediums which can then be made available to downstream processes. Known applications of this type are motor thermal power plants with a typical 40:55 (60) split between the provided mechanical / electro-mechanical and thermal energy content in brackets without transmission losses. However, if larger amounts of thermal energy are needed, these energy converter systems reach their limits. Another disadvantage of the motor cogeneration units is the almost equal distribution of the thermal energy provided between an exhaust gas flow, that is, a heat-conducting gaseous fluid, and a coolant flow, that is, a heat-conducting liquid fluid. The usable thermal energy is thus divided into two partial flows, the thermal energy of which can not or at least not without additional measures and associated significant losses as total thermal energy of the engine cogeneration plant can be used.

The energy converter system according to the invention with the features of the main claim has the advantage of being able to provide high thermal and mechanical power densities and / or high quality. This has the advantage of being able to make better use of available space with regard to the power to be provided, since the entire energy converter system can be made extremely compact for a given rated power. For this purpose, the inventive energy converter system includes - a system for the implementation of energy and

- A heat transfer system in the form of a boiler, in particular a steam boiler. In the plant for the conversion of energy, energy, eg chemical energy from a fossil energy source, is converted into heat and mechanical energy. The plant for the implementation of energy is also a heat transfer system. Here, heat is transferred to a fluid. The plant for the conversion of energy provides a first heat-conducting fluid flow. The boiler stands with the plant for the implementation of energy via the heat-conducting fluid flow in a heat transfer relationship. In particular, it is possible via the heat-conducting fluid flow Heat is transferred from the plant to the implementation of energy to the heat transfer system. According to the invention, it is provided that the plant is designed to convert energy as a gas turbine plant, preferably a micro gas turbine. The system in this case has a gas turbine burner whose exhaust gases for supplying and transmitting mechanical energy to a power consumer, in particular an electric generator, at least partially fed to a turbine and the exhaust gases at least partially form the heat-conducting fluid flow, in particular a first fluid. The heat transfer system in turn provides heat via a second fluid for subsequent use.

A particularly preferred further development of the energy converter system according to the invention can be achieved in that the gas turbine system is designed as a partially recuperated, in particular variably partially recuperated, micro gas turbine. In this case, the partially recuperated micro gas turbine has a compressor for providing a prestressed oxidizing agent stream, in particular fresh air stream, and a recuperator for preheating the prestressed oxidant stream by transferring part of the heat of the exhaust gas of the micro gas turbine, in particular from the first fluid stream to the prestressed oxidant stream , At the fluid output of the plant for the conversion of energy, a flue gas temperature between 200 and 700 ° C is established. Under a partially recuperated micro gas turbine is in particular a gas turbine plant with a recuperator for transfer of waste heat of the exhaust gas to an oxidant stream understood in which the heat transfer between the exhaust gas and the oxidant stream is limited by suitable limiting means or is that in the exhaust after passing the Rekuperators a significant proportion RNutz on a usable in a heat transfer system, in particular a boiler waste heat in the form of residual heat is present. This residual heat is in the According to the invention system via the heat-conducting fluid flow, the first fluid supplied to the heat transfer system as a heat source or provided. Under partially recuperated can alternatively or additionally also be understood that only a certain fraction RRekup a maximum transferable in such a heat exchanger heat energy within the heat exchanger, in particular the recuperator is transferred, so that at least a predetermined proportion RNutz remains at heat in the exhaust gas , In particular, neglecting always occurring losses and a non-usable residual heat applies: RNutz + RRekup ^ 1. The limiting means may be designed such that a contact and / or transfer surface, time or zone provided in the recuperator is / are defined correspondingly defined between the exhaust gas and the oxidant stream and / or means for at least partially bypassing the heat exchanger, Rekuperators or a heat transfer zone by the exhaust gas and / or the oxidant stream is / are provided.

The energy converter system according to the invention designed in this way has the advantage that the mechanical, electrical and thermal energy provided for use by the energy converter system with fixed primary energy expenditure over a very wide range of variance in its relative distribution between the different types of energy (mechanical, electrically and thermally) can be adjusted specifically. In particular, a ratio between R _Nu tz and RRekup can be set over a parameter range between 0:95 and 95: 0, preferably between 10:90 and 90:10, particularly preferably between 30:70 and 70:30. The fraction RRekup can also be called recuperation degree. He will usually reproduce in percentages. In the case of the partially recuperated micro gas turbine, the degree of recuperation is between 0 and 95%, preferably it can be adjusted and / or regulated between 0 and 95%. In particular, in a variable partially recuperated embodiment, such a setting can be made even after installation of the energy converter system. In a particularly preferred embodiment or mode of operation of the partially recuperated micro gas turbine, it can additionally be provided that the amount of heat available in the exhaust gas for a subsequent use can be kept essentially constant even with a variable degree of recuperation, such that a mass flow of the fuel supplied to the gas turbine combustor changes Recuperation level tracked, in particular lowered with increasing degree of recuperation and raised with decreasing Rekuperationsgrad. Compared to a motor CHP, in particular, the split between mechanical / electrical and thermal power supply can be variably varied between 10:85 and 40:55, preferably between 20:75 and 35:60. Alternatively or additionally, in a preferred embodiment or mode of operation of the partially recuperated micro gas turbine, it is possible to keep the mechanical / electrical energy provided substantially constant despite a varying requirement for thermal energy, in particular in the region of the rated power of the generator. The amount of heat in the exhaust gas which can be supplied for subsequent use is set via a variable degree of recuperation, while a mass flow of the fuel fed to the gas turbine burner follows up the changed degree of recuperation, in particular increases with increasing degree of recuperation and is lowered with decreasing degree of recuperation. Compared to a motor CHP can be adjusted in the range of mechanical / electrical rated power of the energy converter system in particular the division between mechanical / electrical and thermal power supply between 10:15 and 10:60, preferably between 10:20 and 10:50 be varied.

In summary, it can be stated that the energy converter system according to the invention with a partially recuperated micro gas turbine is thus characterized in that, as requirements for the quantities of mechanical / electrical and / or thermal energy to be provided by the energy converter system change, a recuperation rate of a nes recuperator of the gas turbine plant and / or a mass flow of a fuel of a gas turbine combustor to track or adjust the requirements. In particular, the thermal power can be varied even when kept in the rated power range electrical power between a 40% and a full thermal load. Preferably, this variation takes place almost continuously. Compared to a motor CHP, the proposed energy converter system according to the invention also has the advantage that the useful energy in each of the types of energy in a high quality, energy density and / or usability is provided.

In a preferred embodiment, the energy converter system according to the invention further comprises at least one further system for the implementation of energy, in particular a heating burner or a heat pump. The other system for the conversion of energy is also a heat transfer system in which heat is transferred to another, third fluid. The further system is in this case via a fluid flow with the heat transfer system in a heat transfer relationship. In particular, heat can also be transferred from the further system to the system or the heat transfer system via the third fluid. In this case, it is provided that the further system can be transferred via the third fluid heat from the other system to the heat transfer system. Furthermore, it can additionally be provided that the system for converting energy which provides the first fluid is also in a heat transfer relationship with the further system for converting energy, wherein in particular at least part of the first fluid is supplied to the further system.

Under a plant for the implementation of energy is understood in particular a system, a system and / or a device which / which input side at least one energy stream, in particular a stream of chemically and / or otherwise stored energy, preferably an incoming fluid stream such. B. a fuel and / or Oxidationsmit- Telstrom, receives, the energy extractable therefrom at least partially heat-forming, ie, exothermic converts, and the output side can serve as a heat source to a downstream heat consumer, in particular a heat consumer can provide a heat-conducting fluid flow. A heat-conducting fluid flow is understood in particular to mean a fluid which has been heated in the system for converting energy, in particular a heated fluid, and / or a flow of a vapor or at least one partially evaporating fluid. In particular, the input-side and output-side currents preferably have different temperature levels, more preferably an output temperature of the output-side fluid flow is greater than an input temperature of the input-side current. Installations of this type can be, for example, internal combustion engines, burners, in particular heating burners or gas turbine plants, but also heat pumps.

In contrast to systems for converting energy, a heat transfer system is understood to be systems, installations, devices and / or devices in which heat is transferred from a first inflowing fluid flow to a second inflowing fluid flow, so that these two fluid flows essentially only have a changed one on the output side have thermal state. Known heat transfer systems are flow apparatuses such as heat exchangers, boilers (without the possibly existing burner), in particular waste heat boilers, recuperators, evaporators, condensers and the like.

A fuel flow is understood in particular to mean a flow of a combustible fluid, preferably a combustible liquid or gas, and / or a supply of a solid fuel. Preferred combustible liquids may be petroleum, petroleum-derived mineral oil fuels, alcohols, biofuels and / or other combustible liquids. Preferred gases may be natural gas, biogas, bio natural gas, landfill, sewage and / or mine gas, hydrocarbon-containing exhaust gases and / or similar gases.

In this context, an oxidant stream is understood as meaning a supply of an oxidizing agent required for an exothermic chemical conversion of the fuel stream, in particular air or other oxygen-containing mixtures or compounds which undergo a redox reaction, particularly in the ambient conditions prevailing in the heat transfer system, in particular ambient pressure and ambient temperature react with the fuel stream with the release of heat energy.

According to the invention, preferably the output-side fluid flow of the system consists of the conversion of energy from exhaust gases of a gas turbine burner. In a preferred plant, the exhaust gases are characterized by a flue gas temperature of at least 200 ° C, in particular 250 ° C, preferably at least 300 ° C, more preferably at least 350 ° C. Particularly preferred is the flue gas temperature of the exhaust gases of the plant for the implementation of energy between 250 ° C and 800 ° C, in particular between 270 ° C and 700 ° C, ideally between 350 ° C and 650 ° C. Further, it is preferred if a mass flow of the exhaust gas between 0.2 kg / s and 3.0 kg / s, in particular between 0.3 kg / s and 2.0 kg / s, preferably between 0.4 kg / s and 1.5 kg / s, more preferably between 0.45 kg / s and 0.8 kg / s. According to the invention, the exhaust gases of the gas turbine burner to provide mechanical energy at least partially via a turbine, in particular a gas turbine, preferably a radial turbine relaxed, which converts a portion of the thermodynamic energy of the exhaust gases into a rotational energy of the turbine. This rotational energy can then be supplied to one, two or more mechanical power consumers. As a consumer of power, for example, come a compressor, an electric generator, a heat pump, a transmission device or Other known to those skilled, mechanically rotating devices drivable in question. In a preferred embodiment, the mass flow of the exhaust gases of the gas turbine burner can be almost completely, ideally completely guided over the turbine and used to drive them.

According to the invention further at least a portion of the exhaust gases, preferably all the exhaust gas of the gas turbine burner, in particular at least a portion of the already relaxed in the turbine exhaust gases as a first fluid stream from a first fluid of the input side of the heat transfer system and / or the other system for converting energy supplied or be forwarded.

The measures listed in the subclaims result in advantageous developments and improvements of the features specified in the main claim.

If the first fluid can be mixed with the third fluid at least partially in front of the heating burner a fuel and / or oxidant stream of the heating burner and / or in the heating burner, a fuel requirement of the heating burner at a given output side heat energy flow, in particular a given or required output side, third fluid stream of the further system for the implementation of energy advantageously reduced and / or a heat energy amount of the third fluid flow can be advantageously increased.

A further advantageous embodiment of the invention, which has a favorable effect on fuel demand and / or fuel efficiency, results if the first fluid can be fed at least partially to a preheating heat exchanger which is responsible for heat transfer to a fuel and / or oxidant stream, in particular one Fresh air flow, is provided. A fuel efficiency is in particular a ratio of one of the inventive energy converter system usable total energy, in particular the sum of usable mechanical, electrical and thermal energy, based on the amount of energy substantially chemically supplied by a fuel amount understood. In other words, with identical supply of energy, we will provide more usable energy. In this context, "low influencing" is understood to mean a reduction of a required fuel quantity, in particular a fuel mass and / or a fuel volume. "Favorably influencing" is an increased release of thermal and / or mechanical energy with a constant amount of fuel in terms of fuel efficiency Understood. Preferably, the preheating heat exchanger is provided for preheating the fuel and / or oxidant flow of the gas turbine combustor of the plant for the implementation of energy and / or the heating burner in the other plant for the implementation of energy.

A refinement of the energy converter system according to the invention which particularly advantageously influences the fuel demand and / or the fuel efficiency can be achieved by at least parts of the first and / or third fluid having been thermally cooled by heat transfer to the second fluid in the boiler via a Return line can be supplied to the heating burner for further implementation. Alternatively or additionally, it can also be provided that at least parts of the first and / or third fluid, after it has been thermally cooled by a heat transfer to the second fluid in the boiler, a second preheater heat exchanger, which for a heat transfer to a fuel and / or oxidant stream, in particular fresh air stream is provided, can be supplied as a heat source.

A particularly effective and efficient embodiment of the invention, which at the same time is cost-effective due to the reduced system overhead, provides that the third fluid can be admixed with the first fluid after it has been heated in the boiler by the heat applied to the second fluid. meübertrag reduced in its thermal energy content, in particular was cooled. If the first and the third fluid are mixed, a mass flow recirculated via the return line and / or supplied to the preheating heat exchanger (s) can be increased. As a result, an even more extensive use of a residual energy remaining in the first and third fluid flow can be achieved for advantageously influencing the fuel requirement and / or the fuel efficiency. This is possible in particular if the two plants for the conversion of energy have mutually compatible output-side fluids, in particular exhaust gases. By "compatible with one another" is meant in particular that the exhaust gases may be mixed under environmental law and / or no or at least not in critical amounts polluting the environment and / or the plant or damage products resulting from chemical reactions or otherwise the two fluids.

Furthermore, if a mixer is provided for forming an adjustable mixture of at least one of the fluid streams, in particular of the first and / or third fluid, and a fuel and / or oxidant stream, in particular a fresh air stream, at least one parameter of the energy converter system according to the invention can leave Product, in particular the second fluid and / or an escaping emission, can be controlled adjustable or regulated. In particular, a pollutant content (eg a CO, CO2, NO _x and / or hydrocarbon content), an emission temperature, a degree of saturation or the like, such as the products, in particular the second fluid and / or be understood the emission characterizing property sizes.

In another aspect, the invention relates to a burner, in particular a heating burner or gas turbine burner, for an inventive energy converter system with a burner module with at least one fuel supply and at least one oxidant supply. The burner according to the invention is characterized by a mixing unit for supplying a predominantly gaseous Brennhilfsfluids, in particular the first fluid stream or fluid of the energy converter system according to the invention from. The admixing unit according to the invention makes it possible to admix at least part of the auxiliary combustion fluid to the conversion or combustion process of the fuel and oxidant flow supplied to the burner such that a conversion rate of the fuel and oxidant flow, a conversion rate in and / or a temperature of the reaction resulting exhaust gas can be advantageously and inventively influenced.

The burner according to the invention advantageously allows this by virtue of the fact that the admixing unit can be structurally integrated into the burner. The admixing unit can be embodied as a separate module, for example as a mixing plate, or directly into a burner flange having a burner nozzle. The design as a separate module favors, among other things, the construction of mixing unit and burner flange / burner module made of individually selected materials. The integrated structure has the advantage of simplifying the handling of the burner during final assembly and / or maintenance.

A preferred admixing unit has a distributor channel, preferably an annular channel, and injection nozzles connected to the distributor channel for the release of a gaseous fluid present in the distributor channel in an injection direction. Furthermore, the distribution channel has at least one connection piece for the connection to a gaseous fluid-providing unit or line.

In addition to use, for example, as a heating burner in advantageous embodiments of energy converter systems according to the invention, the burner according to the invention can also be used advantageously as a burner in boiler installations, gas turbine installations or other burner-based systems known to the person skilled in the art Furnaces are used, which according to the invention is at least partially exhaust gas recirculation in the burner in common.

In a further aspect, the invention relates to an advantageous boiler for an inventive energy converter system. The boiler is in particular provided to change a second fluid by supplying heat at least with respect to a temperature state, in particular to increase a temperature state relative to an initial or ambient temperature and / or at least partially expose a phase transition, in particular the second fluid at least partially into one Steam phase or to transfer a vapor. An advantageous boiler in this case comprises a first conduit system for the passage of the first fluid, which is preferably at least partially formed as a first heat exchanger extending at least within a boiler room for transferring at least a portion of the heat of the first fluid to the second fluid. The first conduit system is expediently designed such that the first fluid, in particular an exhaust gas or flue gas, a temperature, in particular a flue gas temperature of at least 200 ° C, in particular 250 ° C, preferably at least 300 ° C, more preferably at least 350 ° C may have. Particularly preferably, the flue gas temperature of the first fluid is between 250 ° C and 800 ° C, in particular between 270 ° and 700 °, ideally between 350 and 650 ° C. It is further preferred if a mass flow of the exhaust gas between 0.2 and 3.0 kg / s, in particular between 0.3 and 2.0 kg / s, preferably between 0.4 and 1, 5 kg / s, more preferably between 0.45 and 0.8 kg / s. Preferably, a pressure loss between an inlet-side and an outlet-side connection of the conduit system, in particular a fluid inlet and a fluid outlet of the boiler is less than 10%, preferably less than 4%, more preferably less than 2%, ideally less than 0.5%. an input-side pressure level. The first line system can be considered as a train, in particular as a boiler train from the fluid inlet to the substantially in a boiler be formed housing opposite fluid outlet. In such a single boiler, the piping system has a substantially rectilinear extent through the boiler room. However, it may also be advantageous if a deflection, in particular a deflection chamber is provided in the conduit system, the flow direction of a fluid flowing in the conduit system from the fluid input in the deflection undergoes a change of direction, in particular almost completely reversing the direction. Fluid inlet and fluid outlet may be located on one side of the boiler housing in such a two-pass boiler. In an advantageous development, a second deflection, in particular a second deflection chamber, can be provided along the flow direction in the line system, in which the fluid flowing in the line system undergoes a renewed deflection. This is called a three-pass kettle. Two-, three- or mehrzügige boiler have the advantage that a fluid path for the heat-carrying, flowing through the conduit fluid within the boiler room extended, in particular that a heat of the flowing fluid-providing surface is advantageously increased. In a preferred embodiment, the boiler according to the invention comprises a second conduit system for the passage of the third fluid, which is preferably formed at least in sections as a second heat exchanger extending at least within a boiler room for transferring at least a portion of the heat of the third fluid to the second fluid. The second conduit system is expediently designed such that the third fluid, in particular an exhaust gas or flue gas, with a temperature, in particular a flue gas temperature between 250 ° C and 1400 ° C, preferably between 400 ° C and 1200 ° C, more preferably between 600 ° C and 900 ° C and a mass flow between 0.5 kg / s and 4.0 kg / s, in particular between 0.8 kg / s and 3.0 kg / s can be passed through the line system. In a particularly preferred manner, the second conduit system is designed such that the mass flow first and third fluid can be passed through the conduit system. Preferably, a pressure loss between an inlet-side and an outlet-side connection of the conduit system is less than 10%, preferably less than 4%, particularly preferably less than 2%, ideally less than 0.5% of an input-side pressure level. Also, the second conduit system can be formed or executed in an analogous manner to the first conduit system one, two, three or more.

If both the first line system and the second line system are single-entry, the boiler equipped in this way is itself double-threaded, with the two trains then extending separately through the boiler room. Analogously, a boiler with a single-pass first and a two-pass second line system is called a three-pass boiler - and so on.

In a further preferred embodiment of a boiler according to the invention, one of the line systems has two inputs and one output, wherein preferably the first input for the coupling of the first fluid and the second input for the coupling of the third fluid are provided. Preferably, this line system has a one, two or more deflections, in particular deflection chambers exhibiting pipe system, wherein the first input is formed by a piece of pipe, which opens management system side in one of the deflections. A preferred deflection chamber has a deflecting volume delimited by a wall with an inlet and an outlet, in which at least one flow-guiding element, such as a guide plate, a spoiler lip and / or a diffuser, is arranged, which serves to flow in via the inlet Efficiently redirecting fluid flow toward the exit. In this context, the term "efficiently deflecting" is understood as meaning, in particular, a flow deflection which keeps the thermodynamic properties-eg temperature, heat content and / or pressure-of the fluid flow virtually constant or at least does not change substantially. In this case, a change in the fluid flow between the inlet and outlet of the deflection chamber is understood to mean, in particular, less than 10%, in particular less than 5%, preferably less than 1%, particularly preferably less than 0.5%, of a value of the respective property Entrance of the deflection chamber is.

In a further aspect, the invention relates to an advantageous gas turbine plant for generating at least a portion of the stored chemical energy in a fuel. In particular, the gas turbine plant comprises a generator, a compressor and a turbine driving the generator and the compressor with an exhaust gas outlet for removing an exhaust gas from the turbine. The gas turbine plant according to the invention is intended for use in an energy converter system according to the invention and ideally in the exhaust gas outlet a first fluid, in particular a first exhaust gas, with a flue gas temperature in the Abgasausleitung of at least 200 ° C, in particular 250 ° C, preferably at least 300 ° C, more preferably at least 350 ° C from. Particularly preferably, the flue gas temperature of the first fluid is between 250 ° C and 800 ° C, in particular between 270 ° C and 700 ° C, ideally between 350 ° C and 650 ° C. Further, it is preferred if a mass flow of the exhaust gas between 0.2 kg / s and 3.0 kg / s, in particular between 0.3 kg / s and 2.0 kg / s, preferably between 0.4 kg / s and 1.5 kg / s, more preferably between 0.45 kg / s and 0.8 kg / s. Preferably, the gas turbine plant is designed as an already described partially recuperated micro gas turbine. In this case, in particular in an oxidant flow between the compressor and a gas turbine burner, a recuperator is arranged in which only a fraction of RRekup is transferred from heat from the exhaust gas stream to the oxidant stream, so that at least a proportion of useful heat remains in the exhaust gas stream. Preferably, further suitable limiting means are provided or arranged on the recuperator, so that in the exhaust gas flow as well after passing through the recuperator a significant proportion RNutz is present at a usable in the heat transfer system waste heat in the form of residual heat.

Moreover, the invention relates to an advantageous method for providing electrical and thermal energy with an energy converter system comprising a gas turbine plant. In the method according to the invention, a thermal and / or chemically stored energy of an exhaust gas stream of the gas turbine plant is at least partially fed to a boiler, to which heat is still supplied in parallel from a heating burner. The inventive method allows the provision of both electrical and thermal energy as high-quality useful energies, in particular with high energy density. Furthermore, it is thus possible to provide a relative proportion of the useful energies starting from the primary energy over a large ratio range that can be adjusted, controlled and / or regulated. The method also allows the use of different primary energy flows for the supply of the gas turbine plant on the one hand and the heating burner on the other hand, so that with a constant supply of the two primary energy flows a nearly constant release of the useful energies can be ensured.

In an advantageous development of the method according to the invention, it is provided that the exhaust gas stream of the gas turbine plant is at least partially fed to a heating system, in particular a heating burner of the heating system. As a result, an increased degree of utilization of the primary energy flow of the gas turbine plant can be brought about.

In a supplementary or alternative embodiment of the method according to the invention, it can be provided that the exhaust gas flow, in particular of the gas turbine plant and / or the heating burner, in an air preheater at least partially converts its thermal energy to a fresh air flow. carries, whereby an increased utilization rate of the primary energy flow and / or increased starting temperature can be achieved in the Nutzergiestrom.

In the following the invention will be explained in more detail with reference to the embodiments schematically illustrated in the drawings.

Show it:

Fig. 1a is a simplified circuit diagram of an inventive

Energy converter system in a first embodiment;

1 b shows a circuit diagram of the energy converter system according to FIG. 1 a with a first embodiment of a gas turbine plant, in particular a micro gas turbine without recuperator;

1 c shows a circuit diagram of the energy converter system according to FIG. 1 a with a second embodiment of a gas turbine plant, in particular a microturbine with recuperator; 1 d shows a circuit diagram of the energy converter system according to FIG. 1 a with a third embodiment of a gas turbine plant, in particular a micro gas turbine with at least partially bridged recuperator; Fig. 1 e is a simplified circuit diagram of an inventive

Energy converter system similar to Figure 1 a but with a zweizügigen boiler with a conduit system as a second embodiment. Fig. 1f is a simplified circuit diagram of an inventive

Energy converter system similar to Figure 1 a but with a dreizügigen boiler with a pipe system; Fig. 2a is a circuit diagram of an extended energy converter system according to the invention as a further variant; Fig. 2b is a circuit diagram similar to the circuit diagram of Fig. 2a of another energy converter system according to the invention as a third embodiment;

FIG. 2c shows a circuit diagram similar to the circuit diagram of FIG. 2b of a further energy converter according to the invention.

System as a fourth embodiment;

3a is a circuit diagram of another energy converter system according to the invention as a fifth embodiment;

Fig. 3b is a circuit diagram similar to the circuit diagram of Fig. 3a of another energy converter system according to the invention as a sixth embodiment; 3c shows a circuit diagram of a development of an energy converter system according to FIG. 3b;

4a is a circuit diagram of another energy converter system according to the invention as a seventh embodiment;

Fig. 4b is a circuit diagram similar to the circuit diagram of Fig. 4a of an energy converter system according to the invention as an eighth embodiment; Fig. 5 is a circuit diagram of an energy converter system according to the invention as a ninth embodiment; Fig. 6 is a circuit diagram of an energy converter system according to the invention as a tenth embodiment;

7 shows a modified circuit diagram of an inventive

Energy converter system of Fig. 6;

8a shows a further circuit diagram of an energy converter system according to the invention in a twelfth embodiment, wherein the first fluid flow is fed to a heating burner in an installation for converting energy;

Fig. 8b shows an embodiment of a heating burner according to the invention for use in a system according to Fig. 8a; and FIG. 9 is a circuit diagram of a first further development of the inventive energy converter system of FIG. 8a as a thirteenth embodiment.

First, examples of energy conversion systems from two coupled heat transfer systems will be presented, before discussing more complex systems.

Simple energy conversion systems

A first, circuit technology very simple embodiment of an energy converter system 1 according to the invention is shown in Fig. 1a as a circuit diagram.

The energy converter system 1 comprises a plant for the implementation of energy 2 and a heat transfer system 4. The plant for the implementation of energy 2 is designed as a gas turbine plant 20 and has a fluid idausgang 21, via which the system 2 a heat energy carrying fluid, in particular a substantially gaseous fluid, preferably can release or release an exhaust or flue gas. Not shown in this illustration are supply lines, in particular the / the one / two input / inputs for supplying at least one fuel and / or at least one oxidizing agent for the generation of thermal energy in the system 2 by an exothermic redox reaction, in particular a combustion of fuel. The resulting in the exothermic redox reaction, heat carrying fluid is discharged as the first fluid stream 22 - hereinafter also synonymously referred to as the first fluid 22 - discharged via the fluid outlet 21. The fluid outlet 21 is connected via a line 5 to a fluid inlet 41 of the heat transfer system 4.

The heat transfer system 4 according to the invention is designed as a boiler 40 with a line system 43 for the passage of a fluid, in particular the first fluid 22. The line system 43 is permeable to the fluid 22 substantially only in the flow direction indicated by the arrows from the respective fluid inlet 41, 42 to fluid outlets 45, 46 or is flowed through by the fluid 22 substantially in the direction indicated by arrows flow direction. In this case, under a "substantially only in the flow direction permeability" in particular for the fluid 22 in deviating directions from the flow direction dense, in particular diffusion-tight design of the conduit system 43, ie in particular a respective dense or diffusion-tight training of walls of pipelines In addition, elements or devices which favor a preferred flow direction may be provided in the line system 43. For example, at least one check valve and / or one or more flow guide elements such as diffusers could be provided Preferably, the line system 43, in particular as a part extending inside a boiler chamber 40a, is formed at least in sections as a heat exchanger 43a or a heat exchanger element 43a i, in particular, a spiral, fan-shaped ge, plate-shaped and / or corrugated shape of a portion of the conduit system 43 understood, which provides an enlarged relative to the rest of the conduit system 43 surface. The enlarged surface is intended to favor a heat entrained with the fluid 22 conducted through the conduit system 43 for heat transfer to a medium or fluid, in particular working medium or useful fluid, which is in contact with the heat exchanger element 43a.

In a simple embodiment of a boiler 40 according to the invention, designed in particular as a large-scale water boiler or large-capacity steam generator, a useful medium or useful fluid, which is characterized by a suitable heat input or heat transfer by means of the heat exchanger 43a or the heat exchanger element 43a, at least partially has a phase transition of be subjected to a second phase in a first phase. In a preferred manner, the useful medium or useful fluid passes through sublimation and / or evaporation at least partially into a vapor phase or a vapor. Via a boiler outlet 47 on the boiler 40 of the energy converter system 1 according to the invention, this steam is provided and / or removed as a second fluid stream 48 or as a second fluid 48 for further use.

Alternatively, the boiler 40 may be formed as a hot or hot fluid boiler, wherein a heat transfer from the first fluid 21 via the line 43, 43 a system is designed so that the Nutzmedium or Nutzfluid is not exposed to any appreciable phase transition, but only one Output temperature level exceeding the temperature level is heated or heated or should be, without this temperature level exceeds a phase transition temperature of the Nutzmediums or Nutzfluids. If the boiler is designed, in particular, as a pressurized-fluid or pressurized-water boiler, an internal pressure in the boiler chamber can be increased or become such that the phase transition temperature can be increased to a higher temperature. is shifted. This is particularly advantageous if, for a subsequent application of the second fluid 48, an overheating state of the second fluid 48 is desired or required. The first conduit system 43, 43a is expediently designed such that the first fluid 22, in particular an exhaust gas or flue gas, with a temperature, in particular a flue gas temperature between 300 ° C and 800 ° C, preferably between 350 ° C and 700 ° C and a mass flow between 0.5 kg / s and 4.0 kg / s, in particular between 0.8 kg / s and 3.0 kg / s by the conduit system 43, 43 a can be performed.

The line system 43, 43a is furthermore preferably designed such that a pressure drop of the fluid flow 22 between an input-side and an output-side connection 41, 45 of the line system 43, 43a is less than 10%, preferably less than 4%, particularly preferably less than 2%. , ideally less than 0.5% of an input pressure level. Conveniently, a boiler 40 according to the invention may further comprise a boiler inlet, not shown here, for supplying the useful medium or Nutzflu- ides, in particular the Nutzmediums or Nutzfluides in a first phase. The supply can take place at regular and / or irregular intervals and / or as a substantially permanent influx or permanent supply.

It is also preferred if the boiler chamber 40a has at least two volume zones, wherein in a first volume zone the useful medium or useful fluid is present substantially in its first phase and in a second volume zone the useful medium or useful fluid substantially in its second phase. The term "essentially in one phase" means in particular that the proportion of this phase in the total amount of ge, in particular the total mass and / or the total volume of the Nutzmediums or Nutzfluides in this volume zone of the boiler chamber 40a at least 50%, preferably at least 70% and particularly preferably at least 80%.

Advantageously, in addition, it may be provided that the fluid inlet 41 of the line system 43 with respect to the boiler space 40a in the first volume zone, i. in a portion of a boiler housing, which limits the first volume zone, is arranged. Conveniently, additionally or alternatively, the fluid outlet 45 can be positioned with respect to the boiler space 40a in the first or second volume zone, i. in a portion of a boiler housing, which limits the first or second volume zone, be arranged. Such a trained boiler 40 is also referred to as waste heat boiler. In this context, a waste heat boiler is understood in particular to mean a boiler 40, in which the heat transfer to the working fluid or useful fluid, in particular second fluid 48, essentially by thermal contact, convection and / or diffusion of the first fluid 22 flowing in the line system 43, 43a Nutzmedium or Nutzfluid takes place.

In particular, when forming the heat transfer system 4 as a steam boiler 40, the boiler outlet 47 is preferably in relation to the boiler room 40a in the second volume zone, i. in a portion of a boiler housing, which limits the second volume zone arranged.

In a likewise preferred embodiment of the heat transfer system 4 as a hot or hot water boiler 40, the boiler outlet is preferably arranged with respect to the boiler room 40a in the first volume zone, ie in a partial area of a boiler housing which delimits the first volume zone. In an exemplary embodiment of an energy converter system 1 according to the invention, the useful fluid is water. In the first volume zone, the water is essentially in liquid form. If the first fluid 22 of the system for converting energy 2, in particular an exhaust gas or flue gas of a gas turbine plant 20, flows into the first line system 43 as first fluid 22 via at least the first fluid inlet 41, the first fluid 22 flows via the or the heat exchanger elements 43a heat to the surrounding water in the boiler room 40a. 1b shows the energy converter system 1 from FIG. 1a with a preferred gas turbine installation 20. Identical or equivalent elements are given the same reference numerals as in FIG. 1a, with respect to their description at this point to the description of FIG a is referenced. The gas turbine plant according to FIG. 1b here comprises a gas turbine burner 201, a compressor 202, a turbine 203 and at least one further power consumer 204, in particular an electric generator 204a. Preferably, the compressor 202 and the turbine 203 are arranged on a common shaft 205. Such a gas turbine plant 20 is also referred to below as non-recuperated micro gas turbine 20a.

The compressor 202 is supplied via an air inlet 202a, a fresh air flow 202b, which is biased in the compressor 202 to a compressor pressure. An advantageous compressor pressure is between 2 and 6 bar, in particular between 3 and 5 bar, preferably between 3.5 and 4.5 bar, particularly preferably at about 4 bar. The thus biased fresh air stream 202c is then supplied to the gas turbine combustor 201 via an oxidant feed 201a as an oxidant stream. A fuel supply 201 b, the gas turbine combustor 201 further fuel, preferably a liquid and / or gaseous fuel supplied. In the gas turbine combustor 201, the fuel and the oxidizer are in an exothermic redox reaction, usually by combustion, in a smoke or exhaust gas 201 c converted. The resulting smoke or exhaust gas 201 c in this case preferably has a flue gas temperature between 400 and 1000 ° C, preferably between 500 and 950 ° C, more preferably from 600 to 750 ° C and preferably a relative to the compressor pressure further increased flue gas pressure. Via an exhaust pipe 201 d at least a portion of the smoke or exhaust gas 201 c, preferably substantially the entire smoke or exhaust gas 201 c passes to a turbine inlet 203 a. In the turbine 203, which is preferably designed as a radial turbine, the smoke or exhaust gas 201 c is relaxed so that the volumetric work released thereby drives the shaft 205 to rotate. The expanded smoke or exhaust gas 203c is then released via a turbine outlet 203b or fed to the heat transfer system 4, 40 as the first fluid 22 of the plant for converting energy 2, 20 in the inventive energy converter system 1 according to FIG.

A non-recuperated micro gas turbine 20a has the advantage that the expanded smoke or exhaust gas 201 c at the turbine outlet 203b still a high specific thermal energy density, in particular a flue gas temperature between 400 ° C and 1000 ° C, preferably between 500 ° C and 950 ° C, more preferably from 600 ° C to 750 ° C, ideally of about 650 ° C.

Otherwise, the exemplary embodiment of FIG. 1b corresponds to the more general example of FIG. 1a in the further construction and its functional relationships, so that reference is made to the detailed description of FIG. 1a for the further description which relates to the features of the invention described there in an analogous manner also apply to the example of FIG. 1 b, in particular to. FIG. 1 c shows the energy converter system 1 from FIG. 1 a with an alternative gas turbine installation 20. Identical or equivalent elements are given the same reference numerals as in the preceding FIGS. their description at this point to the description of Figures 1 a and 1 b reference is made.

The gas turbine plant according to FIG. 1c comprises a gas turbine burner 201, a compressor 202, a turbine 203 and at least one further power consumer 204, in particular an electric generator 204a. Preferably, the compressor 202 and the turbine 203 are arranged on a common shaft 205. In the gas turbine plant 2, 20b of FIG. 1 c of the compressor 202 biased fresh air flow 202c is passed through a recuperator 206 before it is supplied to the gas turbine combustor 201 via an oxidant supply 201 a as an oxidant stream. The recuperator 206 is a heat exchanger which transmits at least part of the heat of the expanded smoke or exhaust gas 203c of the turbine 203 to the prestressed fresh air flow 202c. The relaxed and in the recuperator 206 partly by heat transfer to the fresh air flow 202c cooled smoke or exhaust gas 206c is then released or as a first fluid 22 of the plant for the implementation of energy 2, 20 in the energy converter system 1 of FIG. 1 a the heat transfer system 4, 40, respectively. A gas turbine plant 20 according to FIG. 1c is referred to hereinafter as recuperated micro gas turbine 20b.

The flue gas temperature T of the first fluid 22 is reduced in a recuperated micro gas turbine 20b due to a heat withdrawal in the recuperator 206. Typically, the flue gas temperature reaches values between 200 ° C and 700 ° C, in particular between 250 ° C and 650 ° C, preferably between 270 ° C and 600 ° C, more preferably from 300 ° C to 400 ° C.

A recuperated micro gas turbine 20b has the advantage, inter alia, that a greater mechanical efficiency _{r.sub.cH is} achieved than with a non-recuperated micro gas turbine 20a. Under a mechanical efficiency r mech is thereby a ratio between a to the power consumer 204 understood mechanical energy and the gas turbine combustor 201 supplied primary energy, in particular chemical energy of a gas turbine fuel understood. A recuperated micro gas turbine 20b in an energy converter system 1 according to the invention is particularly advantageous if, given the dimensioning of the system 1 and the fuel for the burners 201, 30, a greater amount of mechanical energy is to be provided.

A sub-variant according to the invention of the recuperated micro gas turbine 20b in a circuit arrangement according to FIG. 1c is a fixed partially recuperated micro gas turbine 20bb, wherein a recuperator 206 is provided, which can bring about only a limited part of a possible, in particular maximum possible heat energy transfer to the fresh air stream 202c o- has a relation to a theoretically possible efficiency interpretation conditionally limited efficiency of heat transfer. Such a recuperator 206 can be achieved, for example, by designing a transmission surface provided and / or designed for the heat transfer to be smaller than would be required for a maximum efficiency of the heat transfer.

Incidentally, the exemplary embodiment of FIG. 1 c in the further construction and its functional relationships corresponds to the examples of FIGS. 1 a and 1 b described above, so that reference is made to the detailed description of FIGS. 1 a and 1 b for the further description which, with regard to the features of the invention described there, can also apply analogously to the example according to FIG. 1 c, in particular.

FIG. 1 d shows a particularly preferred inventive energy converter system 1 according to the functional diagram of FIG. 1 a with a particularly preferred embodiment of a gas turbine plant 20. Identical or equivalent elements are given the same reference numerals as in FIGS previous figures, with respect to the description of which reference is made at this point to the description of the preceding figures.

The gas turbine system 20 of FIG. 1 d differs from the recuperated micro gas turbine 20 b of FIG. 1 c in that at least one, preferably two bypass systems 207, 208 are provided for at least partially bypassing the recuperator 206.

A first bypass system 207 in this case comprises a bypass control element 207a, preferably a control and / or controllable valve or flap, which is / s provided and / or designed, at least one, preferably an adjustable or selectable partial flow 207c the fresh air stream 202c biased by the compressor 202 before the recuperator 206 and / or divert. Furthermore, the first bypass system 207 comprises a first bypass line 207b shown in dashed lines in FIG. 1 d, via which the partial flow 207c diverted and / or diverted from the bypass control element 207a is preferably led around the recuperator 206 and in particular downstream of the recuperator 206 Recuperator 206 can be supplied to the preheated in the recuperator 206 part of the prestressed fresh air flow 202c again. By way of the first bypass system 207, the amount of heat transferred to the fresh air stream 202c in the recuperator 206 can thus be advantageously set. The first bypass system 207 thus makes it possible to set a degree of recuperation or to make it adjustable, controllable and / or controllable.

A second alternative or supplemental bypass system 208 includes a bypass control element 208a, preferably a controllable and / or controllable valve or flap, which is provided and / or configured to at least one, preferably an adjustable or selectable one Partial flow 208 c of the relaxed from the turbine 203 smoke or exhaust gas 203 c before the recuperator 206 branch off and / or divert. Further, the second bypass system 208 comprises a second, shown in dashed lines in Fig. 1 d Bypass line 208b. In this case, the bypass line 208b can preferably lead the partial flow 208c branched off and / or out of the bypass control element 208a around the recuperator 206 and, in particular after the recuperator 206, be recirculated to the smoke or exhaust gas 206c at least partially cooled in the recuperator 206. In this way, an amount of the heat-conducting smoke or exhaust gas 203c can advantageously be set and / or regulated, so that a quantity of heat transferable to the final air flow 202c in the recuperator 206 can be set and / or regulated. The second bypass system 208, in turn, allows the degree of recuperation to be adjusted or adjusted, adjusted and / or regulated.

A gas turbine plant 20 according to FIG. 1 d, in particular with a first and / or second bypass system 207, 208 is referred to hereinafter as variably partially recuperated micro gas turbine 20 c. These are characterized in particular by an adjustable and / or controllable degree of recuperation, whereby a degree of recuperation is understood as the ratio of heat energy transferred in the recuperator to the maximum heat energy that can be transmitted in the recuperator. In the case of a variably partially recuperated micro gas turbine 20c, the ratio between the provision of mechanical energy, in particular electrical energy, and thermal energy can be advantageously set and / or regulated with an energy converter system 1 according to the invention via the adjustable and / or controllable degree of recuperation. In particular, depending on the load, a degree of utilization of primary energy in at least one of the plants for converting energy 2, 3 can be advantageously optimized. With a partially recuperated micro gas turbine 20c in an energy converter system 1 according to FIG. 1 d, it becomes possible for the first time to adapt the thermal power available for the operation of the boiler 40 via the first fluid 22 beyond the original design of the energy converter system 1 and / or fluctuations or tolerances during assembly or during operation, in particular in the fuel supply, the fuel quality, the power recalled on the boiler 40 or the like. chen, stabilizing and / or optimizing intervention. In particular, an advantageous variation of the operating point of the energy converter system 1 can be achieved via the degree of recuperation. Incidentally, the exemplary embodiment of FIG. 1 d in the further construction and its functional contexts corresponds to the examples of FIGS. 1 a to 1 c described above, so that for the further description reference is made to the detailed description of FIGS. 1 a, 1 b and 1 c, which, with regard to the features of the invention described there, can analogously also apply to the example according to FIG.

In the illustration according to FIGS. 1 a to 1 d, the line system 43, 43 a is shown in a single-entry configuration. However, it may also be advantageous that the conduit system 43, 43 a of the boiler 40 is formed two-, three- or mehrzügig. An energy converter system 1 with a boiler 40, the line system is formed zweizügig is shown in Fig. 1 e. The line system 43, 43 a has a first deflection or deflection chamber 43 b, in which a flow direction of the first fluid 22 is deflected. In this embodiment, the fluid inlet 41 and the fluid outlet 45 can advantageously be arranged on one side of a boiler housing. An energy converter system 1 with a boiler 40, whose line system is formed in three movements, is shown in FIG. 1f. In this case, a second deflection or deflection chamber 43c is provided in the line system 43, 43a. The second deflection chamber 43c is arranged downstream of the first deflection chamber 43b in the line system 43. With regard to their operation, these embodiments do not differ from the first embodiment of FIG. 1 a, so that reference is made in this regard to the preceding description.

More complex energy conversion systems

FIG. 2 a shows a preferred development of the energy converter system 1. The energy converter system 1 according to FIG. 2 a comprises in addition to the installation for converting energy 2 and the heat transfer system 4 at least one fluid output 21, 31, via which the plants 2, 3 each have a heat energy carrying fluid, in particular a substantially gaseous fluid, preferably an exhaust gas or can release or release flue gas. Not shown in this illustration are the at least one / two input / inputs for supplying at least one fuel and / or at least one oxidizing agent for generating thermal energy in the plants for converting energy 2, 3 by an exothermic redox Reaction, in particular combustion of the fuel. The resulting during the exothermic redox reaction, heat carrying fluid is discharged as a first or third fluid stream 22, 32 - also synonymously referred to as a first fluid 22 and third fluid 32 - via the fluid outputs 21, 31. The fluid outlets 21, 31 are connected via lines 5, 6 to a respective fluid inlet 41, 42 of the heat transfer system 4.

The plant 2 is preferably embodied as a gas turbine plant 20, in particular as a partially recuperated micro gas turbine 20c, the partially recuperated micro gas turbine 20c having the advantages according to the invention already described with reference to FIG. 1d. Alternatively, however, it would also be possible to use a non-recuperated micro gas turbine 20a or a recuperated micro gas turbine 20b, as shown in FIG. 1b or FIG. 1c. The heat transfer system 4 is preferably analogous to FIGS. 1 a to 1 d designed as a boiler 40.

In the representations of FIGS. 1 a or 2 a, as in all further described figures, only the switching-technical connection or lines necessary for the mediation of the respective idea of the invention or of the respective details of the invention are shown or indicated. Not shown are usually supply connections and lines for the supply of the individual systems 2, 3 with fuels and / or oxidants, in particular fresh air or disposal lines such. B. exhaust gas chimneys and / or exhaust aftertreatment systems, which, however, can be supplemented in a way that is obvious to a person skilled in the art.

The heat transfer system 4 is in this case designed as a boiler 40, in particular as a waste heat boiler or combination boiler with at least one waste heat zone, with at least two independent line systems 43, 44 for the passage of a respective fluid, in particular of the first and third fluid 22, 32. The line systems 43, 44 are permeable to the respective fluid 22, 32 substantially only in the flow direction indicated by the arrows from the respective fluid inlet 41, 42 to fluid outlets 45, 46. In this case, under a "substantially only in the flow direction permeability" in particular for the respective fluid 22, 32 in deviating from the direction of flow directions dense, in particular diffusion-tight design of the conduit systems 43, 44, ie in particular a dense or diffusion-tight training In addition, in at least one of the conduit systems 43, 44 elements or devices may be provided which favor a preferred direction of flow, for example at least one check valve could be provided and / or one or more flow-guiding elements, such as diffusers, are preferably the conduit systems 43, 44, in particular their part extending inside a boiler chamber 40a, at least in sections as a heat exchanger 43a, 44a or a heat exchanger ement 43a, 44a formed. In this context, a heat exchanger element 43a, 44a is understood as meaning, in particular, a spiral-shaped, fan-shaped, plate-shaped and / or corrugated shape of a section of the respective line system 43, 44, which provides an enlarged surface in relation to the rest of the line system 43, 44. The enlarged surface is provided for this purpose, a heat entrained with the fluid 22, 32 conducted through the line system 43, 44 for a heat transfer to one with the Wärmetauscherelennent 43a, 44a in a related medium or fluid, in particular beneficial medium or Nutzfluid favor.

In a simple embodiment of a boiler 40 according to the invention is in the boiler room 40a a Nutzmedium or Nutzfluid, which is characterized by a suitable heat input or heat transfer by means of the heat exchanger 43a, 44a and the heat exchanger element 43a, 44a at least partially a phase transition of a first phase to be subjected to a second phase. In a preferred manner, the useful medium or useful fluid passes through sublimation and / or evaporation at least partially into a vapor phase or a vapor. Via a boiler outlet 47 on the boiler 40 of the energy converter system 1 according to the invention, this steam is provided and / or removed as a second fluid stream 48 or as a second fluid 48 for further use.

The first conduit system 43, 43a is expediently designed such that the first fluid 22, in particular as an exhaust gas or flue gas, with a temperature, in particular a flue gas temperature between 300 ° C and 800 ° C, preferably between 350 ° C and 700 ° C. and a mass flow between 0.5 kg / s and 4.0 kg / s, in particular between 0.8 kg / s and 3.0 kg / s through the conduit system 43, 43 a can be performed.

The pipe systems 43, 43a; 44, 44a are further preferably designed such that a pressure loss of the respective fluid flow 22, 32 between an input-side and an output-side connection 41, 45; 42, 46 of the respective conduit system 43, 43a; 44, 44a is less than 10%, preferably less than 4%, more preferably less than 2%, ideally less than 0.5% of an input-side pressure level.

Conveniently, a boiler 40 according to the invention may further comprise a boiler input, not shown here, for supplying the useful medium or useful fluid. ides, in particular the Nutzmediums or Nutzfluides in a first phase. The supply can take place at regular and / or irregular intervals and / or as a substantially permanent influx or permanent supply.

It is also preferred if the boiler chamber 40a has at least two volume zones, wherein in a first volume zone the useful medium or useful fluid is present substantially in its first phase and in a second volume zone the useful medium or useful fluid substantially in its second phase. By "substantially in one phase" is meant in particular that the proportion of this phase in the total amount, in particular the total mass and / or the total volume, the Nutzmediums or Nutzfluides in this volume zone of the boiler room 40a at least 50%, preferably at least 70% and particularly preferably at least 80%.

Advantageously, it may furthermore be provided that at least one, preferably both fluid inlets 41, 42 of the line systems 43, 44 with respect to the boiler space 40a in the first volume zone, i. in a portion of a boiler housing, which limits the first volume zone, are arranged. Conveniently, additionally or alternatively, at least one, preferably both, fluid outlets 45, 46 with respect to the boiler space 40a in the second volume zone, i. in a portion of a boiler housing, which limits the second volume zone to be arranged.

Particularly when the heat transfer system 4 is designed as a steam boiler 40, the boiler outlet 47 can preferably be arranged with respect to the boiler space 40a in the second volume zone, ie in a partial area of a boiler housing which delimits the second volume zone. In a likewise preferred embodiment of the heat transfer system 4 as a hot or hot water boiler 40, the boiler outlet is preferably arranged with respect to the boiler room 40a in the first volume zone, ie in a partial area of a boiler housing which delimits the first volume zone.

In an exemplary embodiment of an energy converter system 1 according to the invention, the useful fluid is water. In the first volume zone, the water is essentially in liquid form. If the first fluid 22 of the system for converting energy 2, in particular an exhaust gas or flue gas of a gas turbine plant 20, flows into the first line system 43 via at least the first fluid inlet 41 as the first fluid 22, the first fluid 22 flows over the or the first fluid 22. the heat exchanger elements 43a heat to the surrounding water in the boiler room 40a.

In an analogous manner, via the second fluid inlet 42 of the boiler 40, the third fluid 32 of the further system for converting energy 3, in particular an exhaust gas or flue gas of the heating burner 30, can be flowed into the second line system 44 as a third fluid 32, the third fluid 32 Alternatively or in addition to the heat transfer of the first fluid 22 in turn via the or the heat exchanger elements 44a can deliver heat to the surrounding water in the boiler room 40a. Due to the heat transfer at at least one of the heat exchanger elements 43a, 44a, water is now evaporated, with the water vapor collecting in the second volume zone of the boiler chamber 40a. From there, the steam can then be supplied via the boiler outlet 47 as a second fluid 48 of the energy converter system 1 of a use. Depending on the use and / or content of thermal energy of the first and / or third fluid flow 22, 32, other useful fluids may also be considered instead of water. Thus, for example, ammonia, thermal oil, suitable hydrocarbons or other suitable useful medium or useful fluid can be provided, which in a boiler by heat at a given temperature, a phase transition, in particular from a liquid to a gaseous phase.

In the illustration according to FIGS. 2a to 2c, the line systems 43, 43a; 44, 44a in each case shown formed einschubig. However, analogously to the examples of FIGS. 1 a to 1 f, it can also be advantageous if at least one of the line systems 43, 43 a; 44, 44 a of the boiler 40 is two-, three- or mehrzügig trained. It may also be advantageous with regard to the further system for converting energy 3, 30 when a combustion or flame tube of the further system for converting energy 3, 30 at least partially, in particular at least 50% of a longitudinal extent of the combustion or flame tube, preferably almost the entire combustion or flame tube extends into the boiler chamber 40a, wherein it merges into the second line system 44, 44a at an end remote from the further system for converting energy 3, 30. This advantageously achieves that, in addition to the heat transfer from the third fluid 32 along the line system 44, 44a, a radiation-based heat transfer along the combustion or flame tube can take place. A third embodiment of the invention is shown in Fig. 2b. This embodiment differs from the circuit diagram according to FIG. 2a in that the first fluid stream 22 of the plant 2 for the conversion of energy 2 released at the boiler outlet 45 via a return line 50, in particular an exhaust gas recirculation line 50 of the further system for implementation of energy 3, in particular the heating burner 30 is supplied. The plant for converting energy 2 is preferably designed as a gas turbine plant 20, in particular as a partially recuperated micro gas turbine 20c, the partially recuperated micro gas turbine 20c having the advantages of the invention already described with reference to FIG. Alternatively, however, it would also be possible to use a non-recuperated micro gas turbine 20a or recuperated micro gas turbine 20b, as are known from FIGS. 1 b or 1 c. The Wärmeübertragungssystenn 4 is preferably carried out analogous to FIG. 2a as a boiler 40.

In this case, the first fluid flow 22 will continue to be used as a fuel and / or oxidant flow 30 a, depending on a remaining heating value and / or oxidant content of the further system for converting energy 3, 30. In a preferred embodiment, the first fluid stream 22 after heat release in the heat transfer system 4, 40 serves as a preheated oxidant stream in the other plant for the conversion of energy 3, 30. The third fluid 32 produced in the other plant for the implementation of energy 3, 30 is analogous 2a to the heat transfer system 4, 40 via a second fluid inlet 42 for heat transfer to the Nutzfluid and providing the second fluid stream 48 is supplied. Otherwise, the embodiment according to FIG. 2b corresponds to the configurations known from FIG. 2a, so that for the further description reference is made to the detailed description of FIG. 2a, which with respect to the features of the invention described there also applies analogously to the example according to FIG Fig. 2b may apply, in particular to. Fig. 2c shows a development of the embodiment of Fig. 2a as a fourth embodiment. Deviating from the embodiment according to FIG. 2 b, a branching element 51, in particular an adjusting, control or adjustable branching valve flap 51, is provided in the return line 50. By way of the branching element 51, the recirculated first fluid flow 22 can be divided into a first and a second partial flow 51 a, 51 b. Preferably, a quantitative ratio, in particular a Luftbzw. Flue gas mass ratio between the two partial flows 51 a, 51 b are set, controlled or regulated via the branching element 51.

The first partial flow 51 a is preferably supplied to the further system for converting energy 3, 30. In this case, this supply can be loger way to Fig. 2b done. However, as shown in FIG. 2c, it is also conceivable that in addition the feed to the further plant for converting energy 3, 30 is preceded by a mixer 52, the mixer 52 preferably comprising a mixture of an oxidant stream 52a and the first part stream 51 a brought about. This mixture can then be supplied to the further plant for converting energy 3, 30.

The second substream 51b can preferably be discharged from the inventive energy converter system 1 according to FIG. 2b, released and / or fed to a subsequent system, for example an exhaust gas treatment, for further use and / or after-treatment.

Incidentally, a simplified embodiment of an energy converter system 1 according to FIG. 2c can be achieved by using a simple line branching instead of an adjustable, controllable or controllable branching element. An adjustment of a mixing ratio between the first partial flow 51 a of the returned fluid and the oxidant onsmittelstrom 52 a can then be achieved via a controlled and / or controlled mixer 52.

Incidentally, the embodiment according to FIG. 2c corresponds to the configurations known from the preceding, so that for the further description reference is made to the detailed description there, which with respect to the features of the invention described there in an analogous manner for the example of FIG. 2a or 2b may apply, in particular In particular, an embodiment according to the invention of an energy converter system according to FIG. 2c may have a gas turbine plant designed as a partially recuperated micro gas turbine 20c, the partially recuperated micro gas turbine 20c having the advantages according to the invention already described with reference to FIG. Alternatively, however, a non-recuperated micro gas turbine 20a or recuperated micro gas turbine 20b could also be used, as are known from FIG. 1 b or FIG. 1 c. A modification of the preceding figures could consist in the fact that the two fluid flows leaving the fluid outlets 45, 46 of the heat transfer system 4, 40 are at least partially brought together after release in order to release together a further use and / or aftertreatment - for example, an exhaust gas treatment - to be fed. For this purpose, it may be advantageous if the two fluid outlets leaving the fluid outlets 45, 46 of the heat transfer system 4, 40 are guided via an additional mixer (not shown here pictorially). This may be particularly advantageous if the merged fluid streams at least partially via a return line 50 analogous to the embodiments of FIGS. 2a and 2b to be used. A fifth embodiment of an energy converter system 1 according to the invention is shown in FIG. 3a as a modification of the embodiment according to FIG. 2b. In this case, the first fluid flow recirculated from the first fluid outlet 45 of the heat transfer system 4, 40 to the return line 50 is used as a heat source for a heat exchanger 60 which supplies a fuel and / or oxidant flow 30a to the supply of the further energy conversion plant 3, in particular the heating burner 30 supplies heat, in particular preheats this. As a result of the preheating / preheating of the fuel and / or oxidant stream 30a of the further plant for converting energy 3, 30, an efficiency in the provision of heat by the further plant for converting energy 3, 30 can advantageously be increased. In particular, for a given amount of fuel advantageously higher amounts of heat in the third fluid 32 can be achieved. Otherwise, this embodiment corresponds to the known from Fig 2b and described there example, so that reference is made to the description there. Fig. 3b shows a first modification of the example of Fig. 3a as a sixth embodiment. In this case, the two fluid flows 22, 32 leaving the heat transfer system 4, 40 at the two fluid outlets 45, 46 are combined and fed via the return line 50 to the heat exchanger 60 as a heat source. As a result, an even higher heat transfer at the heat exchanger 60 can advantageously be achieved than in the example according to FIG. 3a, since the thermal energy entrained with both fluid streams 22, 32 is available in the heat exchanger 60 for heat transfer to the fuel and / or oxidant stream. An arrangement of this kind is advantageously possible in particular if the two fluid streams 22, 32 may be mixed with one another from the point of view of emissions law. If this is not possible, it may also be provided in a modification to use a heat exchanger, not shown here, wherein the two heat exchangers can then act on each one of the streams of fuel or oxidant heat transfer or on both.

Contains at least one of the recirculated fluid streams 22, 32 nor a significant calorific value and / or the other system for converting energy 3, 30 at least a portion of the recirculated fluid streams 22, 32 are fed directly, as provided in the example of FIG. 2b , a design based on a combination of the embodiments according to FIGS. 2b and 3b may also be used, as shown in FIG. 3c. Here, the first partial flow 51 a analogous to the example of FIG. 2b are fed to a mixer 52, while the second partial flow 51 b serves as a heat source for the heat exchanger 60 for preheating the fuel and / or oxidant stream 30a. The thus preheated fuel and / or oxidant stream 30a is then mixed in the mixer 52 with the first partial flow 51 a and fed in the premixed form of the other plant for the implementation of energy 3, 30.

An alternative embodiment not shown here, for example according to FIG. 3c, provides for each of the two at the fluid outlets 45, 46 of the heat exchanger. meübertragungssystems 4, 40 provided fluid streams 22, 32 before a separate return line. One of the two return lines supplies the heat exchanger 60, while the other return line is supplied to the mixer 52. Such a circuit is particularly preferred over the circuit according to FIG. 3 c, in particular, when the two fluid streams 22, 32 are not allowed to be mixed with one another from the point of view of emissions law.

All of the abovementioned exemplary embodiments described above have in common that the plant for converting energy 2 preferably as a gas turbine plant 20, in particular as a non-recuperated micro gas turbine 20a, as a recuperated micro gas turbine 20b or as a variable partially recuperated micro gas turbine 20c is executed. The heat transfer system 4 is designed as at least two-tank boiler 40 - in particular large boiler, large-capacity boiler, waste heat boiler or steam generator - with at least two separate line systems 43, 44 for the passage of the first and third fluid 22, 32. However, analogously to the examples of FIGS. 1 a to 1 f, it can also be advantageous if at least one of the line systems 43, 43 a; 44, 44 a of the boiler 40 is two-, three- or mehrzügig trained. It may also be advantageous in terms of the further system for the implementation of energy 3, 30, if a fuel or flame tube of the other plant for the implementation of energy at least partially, in particular at least 50% of a longitudinal extent of the fuel or flame tube, preferably almost the entire Fire or flame tube extends into the boiler room 40a, wherein it merges at one of the other system for the implementation of energy 3, 30 remote end into the second conduit system 44, 44a. This advantageously achieves that, in addition to the heat transfer from the third fluid 32 along the line system 44, 44a, a radiation-based heat transfer along the combustion or flame tube can take place.

An alternative embodiment as the seventh embodiment of an energy converter system 1 according to the invention is shown in FIG. 4a. The energy Transducer system 1 according to FIG. 4a in this case comprises a first heat transfer system 2, a second heat transfer system 4 and a third heat transfer system 3, wherein the plant for converting energy 2 via a line 5 connected to the fluid outlet 21 with the further system for the implementation of Energy 3 is connected. The system for the conversion of energy 2 is analogous to the embodiments of the preceding figures as a gas turbine plant 20, in particular as a partially recuperated micro gas turbine 20c executed, wherein the partially recuperated micro gas turbine 20c already described for Fig. 1 d, inventive advantages ago having. Alternatively, however, it would also be possible to use a non-recuperated micro gas turbine 20a or recuperated micro gas turbine 20b, as are known from FIGS. 1 b or 1 c. A first fluid flow 22, in particular a smoke or exhaust gas stream 22 of the gas turbine plant 20, is supplied via the line 5 to the further plant for conversion of energy 3 designed as a heating burner 30.

Depending on a content of residual fuel and / or oxidizing agent, the first fluid stream 22 can be supplied or admixed in the heating burner 30 at least as a supplement to a supply stream of fuel and / or oxidant, not shown here, preferably essentially as a fuel stream or oxidant stream for supplying the heating burner 30 be used. In a particularly preferred embodiment, the first fluid flow 21 is added to a fresh air flow of the heating burner 30 or injected parallel to a fresh air flow into a combustion chamber of the heating burner 30.

After a further exothermic reaction, in particular exothermic redox reaction, preferably combustion of fuel with the oxidizing agent and the first fluid 21 in the heating burner 30, the smoke or exhaust gases thus produced are treated as a third fluid stream 32 via a fluid outlet 31 of the heating burner for further use from the heating burner issued. As an example of the inventive energy converter system 1 according to FIG. 4 a, the fluid outlet 31 of the further plant for converting energy 3, 30 is connected via a line 6 to a fluid inlet 41 of the heat transfer system 4.

Notwithstanding the examples according to FIGS. 2 a to 3 c, the heat transfer system 4 embodied as a boiler 40 has only one line system 43. The line system 43, in particular a part extending in the interior of a boiler chamber 40a, is formed at least in sections as a heat exchanger 43a, 44a or as a heat exchanger element 43a, 44a. In this context, a heat exchanger element 43a is understood as meaning, in particular, a spiral-shaped, fan-like, plate-shaped and / or corrugated shape of a section of the line system 43, which provides an enlarged surface in relation to the rest of the line system 43. The enlarged surface is intended to favor a heat entrained with the fluid 32 conducted through the conduit system 43 for heat transfer to a medium or fluid, in particular working medium or working fluid, which is in contact with the heat exchanger element 43a.

In a simple embodiment of a boiler 40 according to the invention according to FIG. 4a, a useful medium or useful fluid, which is characterized by a suitable heat input or heat transfer by means of the heat exchanger 43a or the heat exchanger element 43a, is at least partially in phase with a phase transition of one first phase to a second phase. In a preferred manner, the useful medium or useful fluid passes through a sublimation and / or evaporation at least partially a vapor phase or a vapor. Via a boiler outlet 47 on the boiler 40 of the energy converter system 1 according to the invention, this steam is provided and / or removed as second fluid stream 48 or second fluid 48 for further use. The line system 43, 43a is expediently designed such that the second fluid 32, in particular an exhaust gas or flue gas, with a temperature, in particular a flue gas temperature between 300 ° C and 1200 ° C, preferably between 350 ° C and 900 ° C, especially preferably between 350 ° C and 750 ° C, and a mass flow between 0.5 kg / s and 4.0 kg / s, in particular between 0.8 kg / s and 3.0 kg / s passed through the conduit system 43, 43a can be. The line system 43, 43a is further preferably designed such that a pressure drop of the respective fluid flow 32 between an input-side and an output-side connection 41, 45 of the line system 43, 43a is less than 10%, preferably less than 4%, particularly preferably less than 2 %, ideally less than 0.5% of an input-side print level.

Conveniently, a boiler 40 according to the invention may further comprise a boiler inlet, not shown here, for supplying the useful medium or Nutzflu- ides, in particular the Nutzmediums or Nutzfluides in a first phase. The supply can take place at regular and / or irregular intervals and / or as a substantially permanent influx or permanent supply.

It is also preferred if the boiler chamber 40a has at least two volume zones, wherein in a first volume zone the useful medium or useful fluid is present substantially in its first phase and in a second volume zone the useful medium or useful fluid substantially in its second phase. By "substantially in one phase" is meant in particular that the proportion of this phase in the Gesamtmen- ge, in particular the total mass and / or the total volume of the Nutzmediums or Nutzfluides in this volume zone of the boiler room 40 a at least 50%, preferably at least 70% and particularly preferably at least 80%.

Advantageously, in addition, it may be provided that the fluid inlet 41 of the line system 43, 43a with respect to the boiler space 40a in the first volume zone, i. in a portion of a boiler housing, which limits the first volume zone, are arranged. Conveniently, additionally or alternatively, the fluid outlet 45 may be positioned relative to the boiler space 40a in the second volume zone, i. in a portion of a boiler housing, which limits the second volume zone, be arranged.

In particular, with a design of the heat transfer system 4 as a steam boiler 40, the boiler outlet 47 is preferably with respect to the boiler room 40a in the second volume zone, i. in a portion of a boiler housing, which limits the second volume zone arranged.

In a likewise preferred embodiment of the heat transfer system 4 as a hot or hot water boiler 40, the boiler outlet is preferably with respect to the boiler room 40a in the first volume zone, i. in a portion of a boiler housing, which limits the first volume zone arranged.

In the circuit of an energy converter system according to the invention shown in FIG. 4a, the primary energy converted in the plant for converting energy 2, 20 is used on the one hand to generate mechanical energy and on the other hand to provide thermal energy via the heat transfer system 4, 40. Since the first fluid flow 22 carrying the heat energy is coupled into the heat transfer system 4, 40 via the further system for converting energy 3, 30 or is supplied to the heat transfer system 4, 40, the additional system can be provided via additional provision of further thermal energy for the conversion of energy 3, 30 the amount of heat energy provided in the third fluid stream 32 can be increased. In particular, in a controlled and / or regulated operation of the heating burner 30, the heat energy supplied to the heat transfer system 4, 40 between a lower limit, which essentially results from the amount of heat of the first fluid 21, and an upper limit, which is substantially from the thermal energy of the first fluid 21 and the maximum thermal energy of the heating burner 30 results modulated. Of particular advantage is the particularly simple construction of the Wärmeübertragungssys- system 3 as a einweriger boiler 40th

4b shows a first extension of the inventive energy converter system 1 according to FIG. 4a as the eighth exemplary embodiment. In this case, the cooled in the boiler 40 after heat to the working fluid or Nutzfluid in the boiler 40 third fluid 32 is supplied via the fluid outlet 45 to a downstream preheater 70 as a heat source. The preheater 70 is preferably constructed as a heat exchanger and provided to transfer at least a portion of the residual heat entrained with the third fluid 32 cooled in the boiler 40 to a fluid stream, in particular a fuel and / or oxidant stream 30a. According to FIG. 4 b, the fluid stream 3 b preheated in the preheater 70 is fed to the further system for converting energy 3, in particular the heating burner 30. Alternatively or additionally, the gas turbine burner of the gas turbine plant 20, 20a, 20b, 20c, not shown here, can also be supplied with the preheated fluid flow 3b, as shown by the dashed arrow. Preferably, a fresh air flow 3a is preheated to the fresh air supply of the heating burner 30 and / or the gas turbine burner in this way. In addition, this example corresponds to the embodiment of Fig. 4a, to the description of which reference is made at this point.

In the illustration according to FIGS. 4a, 4b, the line system 43, 43a is shown as being of single-formed design. But it can also be an advantage the conduit system 43, 43 a of the boiler 40 two-, three- or mehrzügig form.

A further alternative embodiment of an energy converter system 1 according to the invention is shown in FIG. 5 as a ninth exemplary embodiment. In contrast to the embodiments according to the preceding figures, the heat transfer system 3 is designed as a boiler 40, in particular as a large-capacity boiler, as a waste heat boiler or as a high-speed steam generator, which has at least a three-pass line system 43 for passing a heat-conducting fluid flow. In this case, the line system 43 has at least two fluid inlets 41, 42 and a fluid outlet 45. The at least part of the line system 43 arranged in the interior of a boiler chamber 40a can be formed at least in sections as a heat exchanger 43a or heat exchanger element 43a in the sense of the examples described above be. Analogous to the above-described embodiments of a heat transfer system 4 and a boiler 40, the boiler 40 is provided or designed according to FIG. 5 to heat a Nutzflu- id provided in the boiler room 40a, to heat and / or at least partially by sublimation and or to convert evaporation to a gas phase and to provide the gas phase or a fluid at least partially comprising the gas phase as the second fluid 48 via the boiler outlet 47 for further use. Against this background, the features relating to the arrangement of the fluid inlets 41, 42, of the fluid outlet 45 and / or of the boiler outlet 47 can also be taken from the description of the preceding examples.

The line system 43, 43a of the boiler 40 according to FIG. 5 has at least one, preferably at least two or more deflections or deflecting chambers 43b, 43c running inside the boiler chamber 40a. Under a deflection or deflection chamber 43b, 43c is in particular a limited by a conversion volume with an input and a In the output, the flow direction of a fluid flowing in the line system 43, 43a, when viewed from the fluid inlet, undergoes a change in direction, in particular an almost complete reversal of direction, in the deflection. In a simple embodiment, the deflections 43b, 43c can each be designed as a line or pipe section whose extension direction in a flow direction between an input side and an output side of the line or pipe section is aligned at least at an angle different from zero. In a preferred embodiment, the angle is between approximately 90 ° and 180 °. Alternatively, at least one deflection or deflection chamber 43b, 43c can also be designed as described in FIG. 1e or FIG. 1f.

The boiler 40 according to FIG. 5 is further characterized in that the first fluid inlet 41 opens directly into the conduit system 43, 43a. The second fluid inlet 42 is realized via a pipe section 42a, which protrudes on the input side as a second fluid inlet 42 from a boiler housing of the boiler 40 and the output side in the first deflection 43b opens. Conveniently, the pipe section 42a is designed such that a fluid flowing in via the second fluid inlet 42 intermixes at the mouth into the line system 43, 43a into the flow of the fluid already flowing in the line system 43, 43a, preferably almost without interference, but at least with little interference meddling. In this case, a disturbance is understood as meaning, in particular, the formation of an at least locally turbulent flow in the region of the confluence and / or an at least partial inflow of the inflowing fluid counter to the flow direction of the fluid already flown in via the first fluid inlet 41 in the line system 43. In order to promote a low-interference inflow of the fluid flowing in via the second fluid inlet 42, suitable means for suppressing turbulence in the region of the orifice - such as, for example, can be provided. B. Leitgitter or guiding elements - and / or mixing elements - such. B. a mixer - be provided. In the energy converter system according to the invention according to FIG. 5, the plant for converting energy 2, in particular the gas turbine plant 20, is connected to the second fluid inlet 42 of the boiler 40 via a line 5 connected to the fluid outlet 21. The gas turbine plant 20 is preferably embodied as a partially recuperated micro gas turbine 20c, the partially recuperated micro gas turbine 20c having the advantages according to the invention already described with reference to FIG. 1 d. Alternatively, however, it would also be possible to use a non-recuperated micro gas turbine 20a or a recuperated micro gas turbine 20b, as are known from FIGS. 1 b or 1 c.

The further system for converting energy 3, in particular the heating burner 30, is connected to the first fluid inlet 41 of the boiler 40 via a line 6 connected at its fluid outlet 31.

In a first section of the line system 43, 43a extending between the first fluid inlet 41 and the first deflection 43b, a heat transfer essentially takes place from the third fluid stream 32 to the useful medium or useful fluid in the boiler chamber 40a. After the confluence of the first fluid flow 22 in the first deflection 43b, a heat transfer from the now mixed first and third fluid 22, 32 to the useful medium or useful fluid can take place. In particular, the third fluid 32, which has already delivered heat energy to the useful medium or useful fluid in the first section, is also reheated by the contact with the not yet cooled first fluid 31, whereby a heat transfer can proceed in a more homogenized manner. This is particularly advantageous when there are large differences in temperature and / or heat capacity and / or amount of heat between the first and third fluid.

FIG. 6 shows an alternative embodiment of the example according to FIG. 5 as a tenth embodiment of an energy converter according to the invention. Systems 1. By way of derogation, in the preceding example, the pipe section 42a forming the second fluid inlet 42 into the line system 43, 43a of the boiler 40 according to FIG. 6 only opens into the line system 43, 43a at the second deflection 43c. As a result, on the one hand, a more compact embodiment of the energy converter system 1 can be realized, since both can be arranged with primary energy supplied heat transfer systems 2 and 3 on one side of the heat transfer system 4, 40 and thereby the lines 5 and 6 can be kept as short as possible. Short lines 5, 6 also have the advantage of cost-effectively reducing any line losses incurred, in particular heat and / or pressure losses. Otherwise, the embodiment of FIG. 6 corresponds to that of the embodiment of FIG. 5. A first advantageous development of the embodiment of FIG. 6 is shown in Fig. 7. In this case, a branching element 80, in particular a control and / or controllable control valve / flap, is provided in the line 5 passing from the system for converting energy 2, 20 to the heat transfer system 4, 40. By means of the branching element 80, a first part of the first fluid 21 can be supplied to the further system for converting energy 3, in particular the heating burner 30, as already described in some of the preceding embodiments (see in particular FIGS. 2a-b, 3a-c) ) is similarly known. A second part of the first fluid 21 is supplied to the second input 42 of the heat transfer system 4, 40 as in FIG. Further alternative or supplementary embodiments based on the arrangement shown in FIGS. 5, 6 and 7 result, inter alia, by combination with the embodiments of FIGS. 2 a to 4 b, wherein in particular one or more return lines 50 and / or mixers acting on the fluid outlet 45 52 and / or heat exchanger 60 and / or preheater 70 may result in an advantageous embodiment of an inventive energy converter system 1 with a heat transfer system 4, 40 of FIG. 5 or 6. A circuit diagram of a particularly preferred embodiment of an energy converter system 1 according to the invention is shown as the twelfth embodiment in FIG. 8a. The energy converter system 1 according to FIG. 8a comprises a gas turbine plant 20, which is preferably designed as a partially recuperated micro gas turbine 20c, as a first Wärmeübertragungssys- tem 2. The energy converter system 1 contains a particularly closely coupled together embodiment of a heating burner 300 and a boiler 40, wherein the heating burner 300 the another plant for the implementation of energy 3 and the boiler 40, the heat transfer system 4 form. In this case, the partially recuperated micro gas turbine 20c has the advantages according to the invention already described with reference to FIG. Alternatively, however, it would also be possible to use a non-recuperated micro gas turbine 20a or a recuperated micro gas turbine 20b, as are known from FIG. 1 b or FIG. 1 c. A close coupling of the further plant for the implementation of energy 3 and the heat transfer system 4 is understood in particular an embodiment, wherein a flame or combustion tube 301 extends at least partially, in particular at least half, preferably almost completely up to the boiler room 40a. In this context, a flame or combustion tube 301 is understood as meaning, in particular, a hollow volume structure with a preferably cylindrical and / or polygonal cross section, in the interior of which an exothermic redox reaction, in particular combustion of at least one fuel with at least one oxidant, takes place. Particularly preferably, the flame or combustion tube 301 covers or comprises at least one flame and / or flame front forming during combustion. The close coupling has the particular advantage that a heat transfer to the working fluid or Nutzfluid in the heat transfer system 4, 40 can also be done by means of advantageous radiation transport. In this case, the volume structure preferably has a main extension direction, which preferably runs essentially parallel to a flame direction of the flame and / or flame front. At a first end face 301 a of the flame or combustion tube 301, a burner 310 is arranged. Preferably, the burner 310 substantially shuts off the flame or combustion tube 310 towards this side. The Fig. 8b shows a schematic side sectional illustration of a heating burner 300, in particular a burner 310, and a section of the flame or combustion tube 301 adjoining the burner 310. An end of the flame or combustion tube 301 facing away from the first end face 301a terminates within the boiler space 40a in a line system 43, which is preferably at least partially formed as a heat exchanger 43a or heat exchanger element 43a. In this case, a transition between the flame or combustion tube 301 and the line system 43 is preferably designed such that the smoke or exhaust gas produced in the reaction of the fuel and the oxidizing agent in the flame or combustion tube 301 passes almost completely, preferably completely, into the line system 43 can. The line system 43, 43a is embodied analogously to the exemplary embodiments described above, so that with regard to the features of the line system 43, 43a reference is made to the description there.

Within the scope of the energy converter system 1 according to the invention according to FIG. 8a, it is now provided that the first heat-carrying fluid 22, in particular smoke or exhaust gas 22, released via the fluid outlet 21, the plant for converting energy 2, 20, 20a, 20b, 20c is supplied via a line 5 to the heating burner 300 so that it can be injected or injected into the fuel or flame tube 301. In addition to the exothermic conversion, in particular the combustion by the burner 310, the first heat-carrying fluid 22 now contributes to a heating or enrichment with thermal energy of the third fluid 32 formed or forming in the flame or combustion tube 301. In this case, the third fluid 32 comprises the smoke or exhaust gases formed during the exothermic conversion by the burner 310, the first fluid 22 and / or, in particular gaseous, during the further conversion of the first fluid 22 in the flame or combustion tube 301 reaction products. In particular, the third fluid 32 is a mixture of the aforementioned fluids. A useful medium or useful fluid present in the boiler chamber 40a can experience heat transfer, in particular heat input, in two ways. On the one hand, heat exchange between the fluid present in the flame or combustion tube 301 and the useful medium or useful fluid can already take place via an outer jacket surface 301 b of the part of the flame or combustion tube 301 extending into the boiler chamber 40 a. For this purpose, the outer lateral surface 301b may be provided with a surface which promotes heat transfer, in particular a surface structure and / or with heat exchanger elements. For example, the outer lateral surface 301b could be at least partially a corrugated surface and / or porous, z. B. have honeycomb wall elements. Also, advantageously, a compensation structure in the lateral surface 301 b may be provided, which compensates for a thermally induced change in length of the longitudinal extent of the flame or combustion tube 301. In this case, the term "open-pore" is understood in particular to mean that the surface or structural elements having pores or pores are impermeable to the useful medium or useful fluid but impervious to the fluid present in the interior of the flame or combustion tube 301. On the other hand, there is at least one further heat transfer from the third fluid 32 to the useful medium or useful fluid via the line system 43, 43a adjoining the flame or combustion tube 301, as is already known from the preceding exemplary embodiments. Alternatively or additionally, a compensating structure can advantageously be provided in the lateral surface 301b, which compensates for a thermally induced change in length of the longitudinal extent of the flame or burner tube 301.

Furthermore, the heat transfer system 4, 40 does not differ from the embodiments in the previously described embodiments, in particular according to FIGS. 4a and 4b. The extensions and / or modifications described there can also be transferred in a very analogous manner to the heat transfer system 4, 40 of the embodiment according to FIG. 8a. conditions, so that with respect to such features reference is made to the description of the preceding embodiments.

FIG. 8b furthermore shows a particularly preferred embodiment of a burner 310 for use in an inventive energy converter system 1 according to FIG. 8a or the following FIG. 9. In addition, such a burner 310 can also be used, for example, in energy converter systems 1 according to FIGS Fig. 4a, 4b and be used in other Heizbrenner boiler combinations.

The burner 310 includes a flange unit 320 and burner module 330 with at least one fuel supply not shown here and an oxidant supply. Flange unit 320 is provided for fixing burner 310 to a heating-element housing 300 a, a boiler housing or another housing unit, in particular to fix it in a detachable or replaceable manner. The burner module 330 is provided to convert a fuel supplied to the burner module 310 via the fuel supply, in particular a fuel line, with an oxidant supplied via the oxidant supply in an exothermic redox reaction, in particular combustion, such that a heat-carrying fluid, in particular smoke or exhaust gas arises. A variety of different burner modules 330 is known to the person skilled in the art, the specific embodiment of which does not have any direct influence on the idea of the invention.

The burner 310 according to the invention additionally has an admixing unit 340 for supplying a predominantly gaseous fluid, in particular the first fluid 21. The gaseous fluid supplied via an admixing unit 340 remains separated from the at least one fuel and the at least one oxidizing agent until its exothermic conversion has at least begun in a flame region 331 adjoining the burner module 330. In the particularly preferred embodiment of a burner 310 according to the invention according to FIG. 8b, the admixing unit 340 is designed as a mixing plate 341. The mixing plate 341 in this case has a central bore 342, in which the combustion module 330 is received and preferably fixed. In particular, a burner nozzle 332 is guided through the mixing chamber 340 in the direction of the flame region 331 via the bore 342. In particular, when the burner module 330 has more than one burner nozzle 332, the mixing plate 341 may also have a suitable bore for receiving and passing the burner nozzles 331 for each of the burner nozzles 332. Alternatively or additionally, it may also be provided that the mixing plate 341 receives more than one burner module 330 and carries out its combustion nozzles 332 in the direction of the flame region 331. Furthermore, at least one injection nozzle 343 is provided in the end face of the mixing plate 341 facing the flame region 331, preferably there are two, three or more injection nozzles 343. An injection nozzle 343 is designed to be the gaseous fluid supplied to the admixing unit 340, in particular the first fluid 22 of the plant for the implementation of energy 2 in the flame area 331 injectable or injectable provide. Injectable or injectable is understood here in particular to allow a gaseous fluid to flow via a nozzle or an inlet valve into a volume region, in particular to discharge into the volume region under a pressure which is increased in relation to a pressure in the volume range. A suitable injection nozzle 343 may in particular have at least one inlet gap and / or one inlet opening. Furthermore, the injection nozzle 343 may have a valve and / or flap device for changing a flow. In a preferred embodiment, the injection nozzles 343 are distributed uniformly around the burner nozzle 332, in particular concentrically around the burner nozzle 332 and / or at uniform angular intervals over the burner nozzle 332 arranged around the burner nozzle 332 extending circumference of the flame region 331 facing the front side of the mixing plate 341. If more than one burner nozzle 332 is provided, an analog arrangement of the injection nozzles 343 around each of the burner nozzles 332 may be advantageous.

Further, it is preferred if the injection nozzle 343 is designed to be controllable and / or controllable. In this case, a control and / or controllable nozzle is understood in particular to mean a nozzle which can be influenced by a control or regulation unit in a flow or injection behavior. It can be provided that a flow or injection quantity or rate between at least two states -. Open / closed; open / partially open; open / partially open / closed - can be switched. It can also be provided that a flow rate or injection quantity or rate can be selected at least virtually continuously between 0 and 100% of the maximum possible flow rate.

In the example according to FIGS. 8a, 8b, the first fluid 22 is supplied to the admixing unit 340 via the line 5 from the system for converting energy 2, 20, 20a, 20b, 20c. In order to minimize as much as possible the wiring effort, at least one distributor channel 344 is provided in the mixing plate 341 in the preferred embodiment shown in FIG. 8b. The distribution channel 344 in this case has at least one supply input 345, via which the gaseous fluid is supplied to the admixing unit 340 and to which, in particular, the line 5 can be connected. The supply input 345 is preferably arranged on a side of the mixing plate 341 facing away from the flame region 331.

The injection nozzles 343 are in turn connected to the distribution channel 344, so that all the injection nozzles 343 can be supplied with the first fluid 22 via the distribution channel 344. The distribution channel 344 is preferably designed such that the first fluid 22 at each injection nozzle 343 with almost identical fluid properties, in particular temperature and pressure and / or chemical composition is applied. Preferably, the distribution channel 344 is designed as an annular channel. In this case, a cross-section of the annular channel may in particular have a profile profile over a circumferential direction in the annular channel, in particular to compensate for the local fluid properties.

With the aid of a heating burner 300 according to FIG. 8b, an inventive energy converter system according to FIG. 8a can be realized particularly advantageously and compactly.

A first extension of an inventive energy converter system 1 according to FIG. 8 a with a burner 300 according to FIG. 8 b is shown in FIG. 9. In this case, the embodiment according to FIG. 9 differs from the energy converter system according to FIG. 8a in that the third fluid 32 released at the fluid outlet 45 is at least partially returned to the heating burner 300 via a return line 50. In this case, provision is made for the recirculated part of the third fluid 32 to be admixed via a mixer 52 to a fuel or oxidant flow 52a, in particular to a fresh air flow 52a. This mixture is then fed to the heating burner 300, in particular the burner module 330.

The line system 43, 43a of the examples according to FIGS. 8 and 9 are each shown as one-off. However, it can also bring advantages if the line system 43, 43a is designed to be two, three or more generous, as has already been described in the descriptions of FIGS. 1a-f and 4a-b.

Further modifications and further developments of an energy converter system 1 according to the invention can result inter alia by combining different development features of the embodiments described above. In addition to the one or two-pass boilers shown in the examples as the second heat transfer system 4, 40 can also be used in three or more spacious boilers. Also, by supplementing an energy converter system 1 according to the invention with at least one additional system for converting energy 2, 3, advantageous developments can result.

It may also be advantageous if the gas turbine burner 201 and / or the heating burner 30, 300 is / are designed as bi- or tri-valent burners for two or three fuels or even as multi-fuel burners.

Further modifications and / or expansion possibilities will become apparent to the person skilled in the art through the use of the inventive energy converter system 1, in particular according to one of the previously described examples, in an application situation.

In summary, the following preferred features of the invention are to be noted in particular: An energy conversion system 1 comprises a first heat transfer system 2, in particular a gas turbine plant 20, 20a, 20b, 20c, and a second heat transfer system 4 in the form of a boiler 40. The plant for converting energy 2 , 20, 20a, 20b, 20c stands with the heat transfer system 4, 40 via a fluid stream 22 in a heat transfer relationship, in particular via a first fluid 22 heat from the plant for the implementation of energy 2, 20, 20a, 20b, 20c to the heat transfer system 4, 40 can be transmitted. It is proposed that the plant for converting energy 2, 20, 20a, 20b, 20c comprises a gas turbine burner 201, the exhaust gases 201 c for providing and transmitting mechanical energy to a power consumer 202, 204, in particular an electric generator 204, at least partially fed to a turbine 203 and its exhaust gases 201 c, 203c at least partially the one fluid stream 22, in particular form the first fluid 22. In particular, it is proposed to carry out the gas turbine plant 20 of the energy converter system 1 according to the invention as a partially recuperated micro gas turbine 20c.

LIST OF REFERENCE NUMBERS

1 energy converter system

2, 3 Annex to the implementation of energy

4 heat transfer system

5, 6 line

20 gas turbine plant

20a non-recuperated micro gas turbine

20b recuperated micro gas turbine

20bb fix partially recuperated micro gas turbine

20c partially recuperated micro gas turbine

21 fluid outlet

22 fluid, fluid flow

30 burners (heating burner)

30a oxidant stream

31 fluid outlet

32 fluid

40 heat transfer system (boiler, especially steam boiler)

40a boiler room

41 fluid inlet (connection)

42 fluid inlet (connection)

42a pipe section

43 pipe system

43a heat exchanger (heat exchanger element)

43b, 43c diversion

44 pipe system

44a pipe system (heat exchanger)

45 connection (fluid outlet, boiler output)

46 connection (fluid outlet)

47 boiler output

47 boiler room 48 fluid, fluid flow

50 return line (exhaust gas recirculation line)

51 branching element

51 a partial flow

51 b partial flow

52 mixers

52a oxidant stream (fresh air stream)

60 heat exchangers

70 preheat, heat exchanger (preheater) 80 branching element

201 burner (gas turbine burner)

201 a Oxidant supply

201 b fuel supply

201 c exhaust gas (smoke or exhaust gas)

201 d exhaust pipe

202 compressors

202a air intake

202b fresh air flow

202c oxidant stream (fresh air stream)

203 turbine

203a turbine inlet

203c exhaust gas (heat-conducting smoke or exhaust gas)

204 power consumers

204a electric generator

205 wave

206 recuperator

206c cooled smoke or exhaust gas

207 bypass system

207a Bypass control

207b bypass line

207c partial flow 208 Bypass system

208a Bypass control

208b bypass line

208c partial flow

300 heating burners

301 flame or combustion tube 301 a end face

301 b lateral surface

310 burners

320 flange unit

330 burner module

331 flame area

332 burner nozzle

340 admixing unit

341 mixing plates

342 bore

343 injection nozzle

344 distribution channel

345 supply input

Claims

An energy converter system (1) comprising an energy conversion unit (2) providing a heat conducting fluid flow from a first fluid (22) and a heat transfer system (4) in the form of a boiler (40) connected to the installation for conversion of energy (2, 20, 20a, 20b, 20c) via the fluid flow from the first fluid (22) in a heat transfer relationship, characterized in that the plant for the conversion of energy (2) a gas turbine plant (20, 20a, 20b, 20c) with a gas turbine burner (201), the exhaust gases (201 c) for providing and transmitting mechanical energy to a power consumer (202, 204), in particular to an electric generator (204a), at least partially a turbine (203) are supplied wherein the exhaust gases (201c, 203c) flowing from the turbine (203) at least partially form the fluid flow from the first fluid (22).

Energy converter system (1) according to claim 1, characterized in that the gas turbine plant (20) as a partially recuperated micro gas turbine (20bb, 20c) is formed, a compressor (202) for providing a biased oxidant stream (202c) and a recuperator (206) for preheating the biased oxidant stream (202c) by transferring a portion of the heat of the exhaust gases (201c, 203c) flowing out of the turbine (203) to the biased oxidant stream (202c); idausgang (21), via which the heat-conducting fluid flow from the first fluid (22) is discharged from the gas turbine plant (20).

Energy converter system (1) according to claim 2, characterized in that the micro gas turbine is a variably partially recuperated micro gas turbine (20c).

Energy converter system according to claim 3, characterized in that the micro gas turbine includes a bypass system (207) for at least partially bypassing the recuperator (206), wherein the bypass system (207, 208) at least a partial flow (207c) of in one Compressor biased oxidant stream (202c) around the recuperator (206) leads around.

Energy converter system (1) according to claim 4, characterized in that the bypass system (207) comprises a bypass control element (207a) and a bypass line (207b), wherein the bypass control element (207a) serves to the Partial flow (207c) perform adjustable or selectable, and wherein the bypass line (207b) serves a branched by means of the bypass control element (207a) from the turbine (203) flowing exhaust gases (201 c, 203c) and / or diverted sub-stream (207c) around the recuperator (206) and recirculated to the preheated, pre-charged fresh air stream (202c) in front of the gas turbine combustor (201).

Energy converter system according to one of claims 3 to 5, characterized in that the micro gas turbine includes a bypass system (208) for at least partially bypassing the recuperator (206), wherein the bypass system (208) at least a partial flow (208c) of the Exhaust gas (203c) around the recuperator (206) leads around.

Energy converter system (1) according to claim 6, characterized in that the bypass system (208) has a bypass control element (208a) which is provided to make the partial flow (208c) adjustable or selectable, and a bypass Line (208b) contains, over which of the by the bypass control element (208a) branched off and / or diverted partial flow (208c) of the exhaust gases (203c) around the recuperator (206) guided around and after the recuperator (206) in the recuperator (206 ) At least partially cooled exhaust gases can be fed back.

Energy converter system (1) according to one of the preceding claims, characterized by a further system for the conversion of energy (3), in particular a system with a heating burner (30) or with a heat pump, wherein the further system (3, 30) with the Heat transfer system (4, 40) via a further fluid flow from a flowing further fluid (32) in a heat transfer relationship, and in particular via the further fluid (32) heat from the further plant for the implementation of energy (3, 30) to the heat transfer system (4, 40) can be transmitted.

Energy converter system (1) according to claim 8, characterized in that in addition via the first fluid heat to the further plant for the implementation of energy (3, 30) can be transferred.

0. energy converter system (1) according to any one of the preceding claims, characterized in that as the first fluid substantially in the turbine (203) relaxed exhaust gases (203c) of the gas turbine combustor (201) and the further fluid are the exhaust gases of the heating burner (30) are. Energy converter system according to claim 9 or 10, characterized in that the first fluid at least partially in front of the heating burner (30) a fuel and / or oxidant stream (30a, 52a) of the heating burner (30) or in the heating burner (30) the further fluid (32) can be mixed.

Energy converter system according to one of claims 1 to 1 1, characterized in that the first fluid (22) at least partially a preheat heat exchanger (60) can be supplied, which for heat transfer to a fuel and / or oxidant stream (30a, 52a), in particular fresh air flow, is provided.

Energy converter system according to one of claims 1 to 12, characterized in that at least parts of the first and / or further fluid (22, 32), after it by a heat transfer to another fluid (48) in the boiler (40) thermally was cooled, via a return line (50) the heating burner (30) for a further implementation and / or a second preheat heat exchanger (70), which for a heat transfer to a fuel and / or oxidant stream (30a, 52a), in particular fresh air flow is provided, can be supplied as a heat source.

Energy converter system according to one of claims 1 to 13, characterized in that the third fluid (32) can be added to the first fluid (22) after it in the boiler (40) by the heat transfer to the other fluid (48) was thermally cooled.

Energy converter system according to one of the preceding claims, characterized in that further comprises a mixer (52) for forming an adjustable mixture of at least one of the fluid streams, in particular from the fluid stream from the first and / or a A further fluid (22, 32), and a fuel and / or Oxidationsmit- current (30a, 52a), in particular a fresh air flow is provided.

16. Burner (310), in particular heating burner (30, 300) or gas turbine burner (201), for an energy converter system (1) according to one of the preceding claims with a burner module (330) with at least one fuel supply and an oxidant supply, characterized by a Admixing unit (340) for supplying a predominantly gaseous fluid, in particular the first fluid (22).

A boiler (40) for an energy converter system (1) according to any one of claims 1 to 14, characterized by a first conduit system (43) for passing the first fluid (22), which is preferably at least partially as at least within a boiler space (40a ) extending first heat exchanger (43a) for transferring at least a portion of the heat of the first fluid (22) to a further, second fluid (48) is formed.

A boiler (40) according to claim 17, characterized by a second conduit system (44) for passing a further, third fluid (32) which preferably at least in sections as at least within a boiler room (40a) extending second heat exchanger (44a) for carrying at least a portion of the heat of the further, third fluid (32) is formed on the further, second fluid (48).

A boiler (40) according to any one of claims 17 or 18, characterized in that at least one of the piping systems (43) has two entrances (41, 42) and one outlet (45), an inlet (41; 42) for coupling in the first fluid (22) and the other input (42; 41) for the coupling of the further, third fluid (32) is provided. Boiler according to claim 19, characterized in that the line system (43) has one, two or more deflections (43b, 43c) having piping system, wherein the first input (41) is formed by a piece of pipe, the line system side in one of the deflections ( 43b, 43c) opens.

Gas turbine plant (20, 20a, 20b, 20c) with a gas turbine burner (201), the exhaust gases (201 c) for providing and transmitting mechanical energy to a power consumer (202, 204), in particular to an electric generator (204a), at least partially a turbine (203) for a trained according to one of claims 1 to 14 energy converter system (1) characterized by a compressor (202) for providing a biased Oxidati- onsmittelstroms (202c) and a recuperator (206) for preheating the biased oxidant stream (202c) by transferring a portion of the heat of the exhaust gases (201c, 203c) flowing from the turbine (203) to the biased oxidant stream (202c), and through a fluid exit (21) for discharging the gas from the turbine (203 ) flowing exhaust gases as a heat-conducting fluid stream (22) from the first fluid, wherein the micro gas turbine, a bypass system (207) for at least partially Umgehun g of the recuperator (206), and wherein the bypass system (207, 208) at least a partial stream (207c) of the compressor in a biased oxidant stream (202c) around the recuperator (206) around.

Gas turbine plant according to claim 21, characterized in that the recuperator (206) only a fraction of RRekup the heat of the turbine (203) flowing exhaust gases (201 c, 203c) on the Oxida- tion medium flow (202c) transmits, so that at least a proportion RNutz of usable heat in the exhaust gases (203c) remains.

Gas turbine plant (20, 20b, 20c) according to claim 21, characterized by limiting means arranged on the recuperator (206), which cause a significant increase in the exhaust gas (203c) flowing out of the turbine (203) after passing through the recuperator (206) Proportion Rutz is present at a heat transfer system (4, 40) usable waste heat in the form of residual heat.

A method for generating electrical and thermal energy with an energy converter system (1) comprising a gas turbine plant (20, 20a, 20b, 20c), in particular according to one of claims 1 to 14, with a turbine (203), one from the turbine (203) providing heat-conducting fluid flow from a first fluid (22), characterized in that the energy thermally and / or chemically stored in the heat-conducting fluid flow from the first fluid (22) is at least partially associated with a boiler (40). is supplied.

A method according to claim 24, characterized in that for the flue gas temperature T of the first fluid (22) of the boiler (40) supplied heat-carrying fluid flow is: 200 ° C <T <700 ° C.

A method according to claim 24 or 25, characterized in that the boiler (40) additionally heat from a heating burner (30, 300) is supplied.

Method according to one of claims 24 to 26, characterized in that with changing requirements of the by the Energy conversion system (1) to be provided amounts of mechanical / electrical and / or thermal energy Rekuperationsgrad a recuperator (206) of the gas turbine plant (20c) and / or a mass flow of a fuel of a gas turbine combustor (201) tracked or adjusted the requirements.

28. The method according to any one of claims 24 to 27, characterized in that the heat-conducting fluid flow from the first fluid (22) at least partially a heating system (3, 30), in particular a heating burner (30, 300) is supplied.

29. The method according to any one of claims 24 to 28, characterized in that in a formed as an air preheater heat exchanger (60, 70) from the heat-conducting fluid stream heat to a heating system (3, 30) supplied fresh air stream transfers.