DE102004040890A1 - Power station installation, has heat supply device arranged in waste gas path of gas turbo-group, upstream of heat transmission equipment - Google Patents

Abstract

A power plant installation has a gas turbine group (1) a pressurized air store (201) and at least one storage fluid expansion power machine (203) , in which the gas turbo group has at least one compressor (101) and at least one combustion chamber (102) and at least one first turbine (103). In the waste gas path of the gas turbine group, a heat supply device, in particular an additional heating device (4) is arranged upstream of the heat transfer equipment. An independent claim is also included for a method of operating a power station.

Description

technical area

The The present invention relates to a power plant according to the preamble of claim 1. It further relates to preferred methods for Operation of such a power plant.

Air reservoir turbines are well known in the art. When operating air storage turbines Air generally gets over compresses and dehumidifies several compressor stages with intercooling, and the compressed air is stored in a suitable memory, for example in an underground cavern, cached. The stored compressed air can be removed from the store if necessary and under the levy of shaft power in a storage fluid decompression engine to be relaxed. For better utilization of the stored volume it is still a common measure the air in advance the relaxation and / or during to warm the relaxation, what usually indirectly by means of heat exchangers he follows. This can be a Rauchgasbeaufschlagung the storage fluid expansion turbine can be avoided, and the storage fluid expansion turbine can be simpler and to be built cheaper; An internal firing is, of course, quite possible in the realm of possibility.

by virtue of the comparatively low outlet temperature of the compressed air are suitable air storage systems with hot air turbines and heating by external sources over Heat exchanger especially for use at low temperatures Warmth.

From the US 5,537,822 is such a system has become known in which the exhaust heat of a gas turbine group is used to heat the storage air. Here, however, the performance potentials are limited, because the available waste heat is limited. Overall, the following shearing occurs: In order to use the exhaust gas heat of the gas turbine group as efficiently as possible, a certain mass flow must flow through the storage fluid expansion turbine. However, there are no appreciable potentials anymore, regardless of the power of the gas turbine group to increase the performance of the storage fluid expansion turbine; a further independent increase in performance of the storage fluid expansion turbine without change in performance of the gas turbine group requires an increased withdrawal mass flow from the memory, associated with a decreasing inlet temperature of the storage fluid expansion turbine and thus a poor utilization of the stored fluid due to the low available mass-specific Enthalpiegefälles.

at the become known power plant it continues to prove as a disadvantage that the supercharger on a shaft train with the storage fluid expansion turbine are arranged, resulting in a suboptimal flexibility the load distribution between charging and power operation results.

Presentation of the invention

Here The invention aims to remedy this. The marked in the claims Invention is based on the object, a power plant and a Specify method of the type mentioned, which disadvantages of the prior art is able to avoid.

According to the invention this task using the entirety of the features of the claim 1 solved, and further using a method according to one the method claims.

core So it is the invention upstream in the flue gas path of the gas turbine group a heat transfer apparatus, which for heating the removed from the compressed air reservoir fluid by means of the waste heat of a Gas turbine group serves, a heat supply, in particular an additional firing, to order. This can be the air storage process to disposal standing heat most effective be decoupled from the performance of the gas turbine group. With the greatest advantage is in the fluid flow path between the compressed air reservoir and the storage fluid relaxation engine Shut-off and / or throttle organ arranged, which the regulation allows the fluid mass flow taken from the storage volume.

When Storage fluid relaxation engine finds according to a embodiment the invention, a turbine use, which hereinafter as a storage fluid expansion turbine is referenced. Of course can Other types of engine are used.

In one embodiment of the invention, a temperature measuring point is arranged in the flue gas path downstream of the heat transfer apparatus. The temperature measured there is used in a preferred operation as a controlled variable for a temperature controller, which changes the fluid mass flow by interfering with the throttle body so that the measured flue gas temperature remains at a desired value or in a desired value interval. for example, the exhaust gas temperature is adjusted so that it is a safety margin above a dew point temperature; This enables the best possible utilization of the waste heat potentials while at the same time ensuring safety against dew point falls below the exhaust gas. At the same time, the additional firing power is preferably operated with the power of the generator of the pressure accumulator system as a controlled variable.

It is in principle also possible the fluid mass flow over the capacity regulator and the firing capacity via the temperature controller too regulate.

Also in other modes of operation, it is advantageous to have the exhaust gas temperature downstream of the heat transfer apparatus to measure, and this in a safety logic of plant control to be included, in such a way that, when falling below a minimum value, the fuel-dependent can be given to trigger appropriate security measures, so a drop below the dew point of flue gas components is avoided.

In an embodiment The invention is a flue gas purification catalyst in the flue gas path arranged. Such a catalyst has a temperature window in which it must be operated, because at higher temperatures Damage occurs and no catalytic cleaning action at lower temperatures guaranteed can be. This temperature window is from the catalyst and the materials used, and is for example in the range of 250 ° C to 300 ° C. In general, the catalyst may therefore in no case directly from the gas turbine group or even be directly flowed from the additional firing with flue gas. According to the invention the catalyst is therefore arranged inside the heat transfer apparatus, such that the flue gas to the catalyst already a part of the heat transfer apparatus flows through and partially cooled Has. In a simplest embodiment the catalyst is downstream at a location of the heat transfer apparatus a first part of the heat transfer apparatus and arranged upstream of a second part of the heat transfer apparatus, at he at nominal operating conditions of the power plant a best operating temperature finds.

In an embodiment is the heat transfer apparatus in two flows through in series independent Units are divided, between which the catalyst is arranged is.

In a further embodiment is essentially at the entrance to the catalyst or directly in the catalyst or on the catalyst material, a temperature measuring point arranged. In one embodiment The invention relates to the extracted from the compressed air reservoir mass flow regulated so that the temperature at the catalyst inlet by a steady controller is adjusted to a setpoint, or by a discontinuous two-position controller within a setpoint interval is regulated. The firing capacity of the additional firing then becomes in an operating variant with the power of the generator of the pressure storage process as a controlled variable operated.

alternative can the additional firing power as a function of the catalyst inlet temperature and the mass flow in dependence be regulated by the performance.

A Measurement and monitoring the catalyst inlet temperature is also in other operating methods an advantage in order to or falling below admissible Limits trigger interceptions, which, for example, an irreversible damage to the catalyst avoid assets.

In Another mode of operation of the inventive power plant is the power output of the accumulator process is not regulated. On the other hand will be at least one, preferably two, of the following temperatures measured: the temperature of the flue gas downstream of the heat transfer apparatus, the temperature of the catalyst or the flue gas substantially immediately upstream of the catalyst, and the temperature of the storage fluid at the exit from the heat transfer apparatus or at the inlet to the storage fluid relaxation engine. One of the Temperatures will be the norm for the Control of the additional heat to the flue gas, ie in particular the firing capacity of the additional firing, used. The second temperature is used as a controlled variable for the controller the storage fluid mass flow used. Other measured temperatures will be an advantage in the sense of protective measures as control parameters for border regulations concerning interventions on the additional heat and used the storage fluid mass flow.

In a further embodiment of the invention, a line is arranged, via which fluid from the compressed air reservoir to the gas turbine group can be conducted, and which opens downstream of the compressor and upstream of the combustion chamber in the flow path of the gas turbine group. Thus, the gas turbine process fluid can be made available for combustion and relaxation, which does not have to be compressed at the same time. This allows a further increase in output of the power plant, because either a lower mass air flow labor-intensive compressed in the compressor of the gas turbine group must be as is available for combustion and relaxation, or the turbine mass flow can be raised above the maximum compressor mass flow, from which on the increased flue gas mass flow in addition a higher waste heat potential for use in the pressure storage process is available. The fluid supplied to the gas turbine group is advantageously removed within the heat transfer apparatus, downstream of the heat transfer apparatus, or in a partially relaxed manner during the expansion process of the pressure storage process. It is advantageous if the removal point is arranged such that the removal temperature corresponds at least approximately to the temperature at the compressor outlet of the gas turbine group; This avoids excessive mixing losses. It is also advantageous if the withdrawal pressure at least approximately corresponds to the compressor discharge pressure and is slightly higher; this avoids unnecessarily high throttling losses.

In Another mode of operation of the inventive power plant is the storage fluid temperature at the exit from the heat transfer apparatus measured. This temperature can be used as a controlled variable either for the Accumulator taken mass flow or for the additional firing capacity be used. Complementary In addition, in one process variant, the power of the generator the pressure storage process as a controlled variable for the performance of the additional firing or for the fluid mass flow can be used.

The Measurement and monitoring this fluid temperature is independent from the described mode of operation also to advantage when crossing a maximum allowable Temperature triggering protective interventions.

The Charge compressor for charging the compressed air reservoir are preferred either independently of arranged the power generating components with their own drive motors, which allows a maximum flexibility of operation. In another preferred embodiment are the superchargers with the shaft train of the gas turbine group coupled. For this purpose, a generator is fixed in a first embodiment coupled with the gas turbine group. The generator has a second one Shaft end, which aufschaltbar on the compressors for charging the compressed air reservoir is. The shaft power of the gas turbine group can be adjusted by an adjustment the excitation of the generator and the operating point of the supercharger variably divided between these two power consumers become. In this case, the phase of the generator in the sense of a Reactive power control can be changed very flexible. In another embodiment is the generator designed in such a way that he is also operated by electric motor. In a third embodiment is a switchable coupling between the generator and the gas turbine group arranged such that the generator for the sole drive of Charge compressor can be operated by motor while the Gas turbine group stands.

In a further embodiment The invention is in the flow path of the storage fluid an additional heat supply arranged. This can be downstream of the heat transfer apparatus and upstream the decompression engine be arranged upstream of the heat transfer apparatus, or in a heat transfer apparatus immediate bypass line. The former embodiment has the advantage that the storage fluid heat supply device in the nominal Operation of the power plant is usable to the inlet temperature the storage fluid relaxation engine over in the heat transfer apparatus to increase the achievable mass. This is, for example, an operational concept possible, in the manner described above, the heat input to the flue gas and the storage fluid mass flow with the catalyst inlet temperature and the exhaust gas temperature downstream of the heat transfer apparatus controlled as controlled variables become; that is, it will be a catalyst and exhaust heat optimized Operating concept realized. Regardless of that can be about the additional heat to the storage fluid downstream of the heat transfer apparatus, which an additional Degree of freedom of process control represents the inlet temperature the storage fluid relaxation engine can be optimized.

The Storage fluid heat supply device can as directly into the flow path be implemented integrated firing device, or as a heat exchanger with an outside Firing. The first type has the advantage of being cheaper, and generally associated with lower pressure drops than one in the flow path arranged heat exchanger an external furnace. An external firing has the opposite Advantage that the storage fluid does not contaminate with flue gas components becomes. This has considerable advantages, for example, if one commercial Steam turbine as a storage fluid expansion engine application which is not for the application of aggressive hot flue gases provided is. If the power plant often with additional heat to be operated to the storage medium, and the considerable investment costs a smoke-gas resistant Storage fluid decompression engine to be avoided is the indirect heat supply to prefer. Here, however, must be for efficient use the available put heat Care should be taken.

Short description the drawing

The Invention will be illustrated below with reference to the drawing Embodiments explained in more detail. For the understanding of Invention not immediately necessary elements are omitted. The embodiments are purely instructive to understand, and are not intended to be limiting in the claims marked invention be used.

Way to execute the invention

A first embodiment of the invention is in 1 shown. The power plant includes a gas turbine group 1 , a storage facility 2 , as well as a charger 3 , The schematically illustrated gas turbine group 1 includes a compressor 101 , a combustion chamber 102 , a turbine 103 , as well as a generator 104 , The generator can often be operated by a motor as starting device for the gas turbine group. The gas turbine group is any gas turbine group as it is available on the market, which also includes the possibility of multi-shaft installations or gas turbine groups with sequential combustion, ie with two turbines connected in series and a combustion chamber arranged therebetween. Such a gas turbine group is out EP 620 362 known. Likewise, a transmission between the output shaft of the gas turbine group and the generator can be arranged; the illustrated type of gas turbine group is not meant to be limiting. In a known per se ambient air in the compressor 101 compressed, the compressed air in the combustion chamber 102 Heat supplied, and the resulting strained hot gas in the turbine 103 relaxed with delivery of a service. The turbine drives the compressor 101 as well as the generator 104 at. The generator 104 generates a net power P ₁ , which is detected and used for power control of the gas turbine group, which is shown very simplified. If the power decreases as a controlled variable, the fuel quantity actuator 6 open. Of course, such a power control still includes setpoint-actual value comparisons, limiters for temperatures and pressures, and much more, but which is familiar to the person skilled in the art and has therefore not been shown in the interest of clarity. Furthermore, the illustrated power plant includes a storage facility 2 whose core elements are the compressed air reservoir 201 and the storage fluid relaxation engine, here a storage fluid expansion turbine 203 , represent. As a storage fluid expansion turbine, for example, a marketable series steam turbine can be used, which requires only minor modifications; the pressure accumulator fluid flowing through is then preferably air or another non-aggressive gas in the sense of a long service life, at inlet temperatures of a maximum of approximately 550 ° C. to 650 ° C. The compressed air reservoir can be charged in a conventional manner with compressed air, which is preferably done at times of low electricity demand and low electricity market prices. In the example is a loading unit 3 shown, which is a first compressor 301 , an intercooler with dehumidifier 302 , a second compressor 303 , as well as a second air cooler / dehumidifier 304 contains. The drive is done by the motor 305 , When operating the compressor, compressed air is added to the storage volume 201 promoted; at standstill of the charging unit 3 prevents a check valve 306 a backflow of air. A shut-off and / or throttle organ 7 regulates the outflow of compressed air from the accumulator 201 to the storage fluid expansion turbine 203 , Fluid flowing out of the accumulator becomes in the turbine 203 under release of power, which is used to drive a generator 204 is used, which generates a power P ₂ . In a simplest case, this power can be used as a controlled variable for controlling the throttle element 7 be used. Since the temperature of the stored fluid in the compressed air reservoir is low, the mass flow-specific power output of the storage fluid expansion turbine is initially very low, resulting in an extremely poor utilization of the storage volume. Therefore, in the flow path between the compressed air reservoir 201 and the turbine 203 a heat transfer apparatus 202 arranged over the previous of relaxation in the turbine 203 Heat can be transferred to the storage fluid. Of course, the arrangement of an internal firing device in the flow path of the compressed air would be possible, which in turn makes necessary measures, which are not the subject of this invention. So then have to take appropriate measures on the turbine 203 be driven because it is traversed by heated air instead of flue gas. An embodiment in which power is removed from the heat transfer apparatus 202 and upstream of the storage fluid expansion turbine 203 a combustion chamber is arranged, but is also included in the scope of the claims quite well and is shown below, even if the illustrated embodiment with exclusively external heat transfer is generally considered to be advantageous. The low output temperature from the compressed air reservoir makes the pressure accumulator very attractive for use at low temperature level accumulating heat, such as solar heat or the waste heat of a gas turbine group, or other heat engine. Therefore, the heat transfer apparatus is in the flue gas path of the gas turbine group 1 arranged, and flows through this on the primary side, while the heat transfer apparatus on the secondary side in countercurrent to Flue gas is flowed through by the tensioned fluid from the compressed air reservoir. As it flows through the heat transfer apparatus thus flowing out of the compressed air reservoir fluid is heated using the waste heat of the gas turbine group, whereas the flue gases cool down. The best use of waste heat occurs when the flue gases are cooled as much as possible while avoiding falling below the dew point of the smoke components; In particular, in the combustion of sulfur-containing fuels, such as oil, otherwise serious corrosion damage can be the result. Downstream of the heat transfer apparatus is a temperature measuring point 8th arranged to measure the temperature of the flue gas. A control is constructed such that with the temperature measured there as a controlled variable, the throttle body 7 is controlled. With increasing flue gas temperature downstream of the heat transfer apparatus opens the throttle body 7 , whereby the secondary-side mass flow of the heat transfer apparatus increases, and the flue gas is cooled more. Of course, this control can be carried out by a person skilled in the art as a continuous control which keeps the temperature at an approximately constant desired value, or as an unsteady two-step controller which regulates the temperature between an upper limit and a lower limit. Furthermore, upstream of the heat transfer apparatus in the flue gas path is an additional firing device 4 arranged. This makes it possible to increase the inlet temperature of the flue gas into the heat transfer apparatus, and thus to decouple the power potential available for the downstream pressure storage process in a highly effective manner from the operating state of the gas turbine group. In the example shown, the fuel quantity actuator 5 the supplementary firing with the power P _{2 of} the generator 204 the pressure accumulator system controlled as a controlled variable: When the power drops, the actuator opens 5 , and the supplementary firing performance is increased. This increases the temperature at the entrance to the turbine for the time being 203 , which leads to a first increase in performance. In addition, the measuring point registers 8th an increase in the flue gas temperature, which by engaging the throttle body 7 the fluid mass flow is increased from the compressed air reservoir, which further leads to an increase in performance. The temperature of the fluid entering the storage fluid expansion turbine 203 decreases with appropriate dimensioning of the heat transfer apparatus 202 again. It is very advantageous and familiar to those skilled in the art, when the temperature of the compressed air at the exit from the heat transfer apparatus or at the inlet to the storage fluid expansion turbine 203 in a manner not shown, but familiar to those skilled, monitored and used as a controlled variable of a limit control, for example, by exceeding an allowable maximum value, the actuator 5 closed further or its opening is limited.

Likewise, for the person skilled in the art in the light of these explanations, a regulation without any explicit representation is readily comprehensible, in which the inlet temperature of the storage fluid expansion turbine 203 as a controlled variable for the opening of the fuel quantity actuator 5 is used; such a control can be used for optimum utilization of the available storage volume, since the inlet temperature of the storage fluid expansion turbine can be regulated at a maximum, resulting in a maximum specific enthalpy gradient across the turbine 203 results. Ideally, the opening of the throttle body 7 in this case with the power of the generator 204 operated as a controlled variable, in that as the power decreases, the throttle body further opened, and vice versa is closed with increasing power. The fact that a setpoint-actual value adjustment of the controlled variable must take place is assumed to be known. Advantageously, even at this mode of operation at the measuring point 8th detected flue gas temperature used as a controlled variable of a limit control, such that, for example, in the event of imminent dew point undershoot the throttle body 7 is closed further.

According to a second embodiment, in 2 is shown in the flue gas path of the gas turbine group is a catalyst 205 arranged, which serves for flue gas cleaning. This is disposed within the heat transfer apparatus, downstream of a first part of the heat transfer apparatus and upstream of a second part of the heat transfer apparatus. The flue gas temperature gradient, which is established via the heat transfer apparatus, is thus distributed in such a way that the catalyst 205 is flowed to a temperature which is lower on the one hand, than that of the flue gas at the inlet to the heat transfer apparatus, but higher than that of the exhaust gas downstream of the heat transfer apparatus. By this arrangement, a good function of the catalyst can be ensured. This can be ensured especially well if, as shown, a temperature control of the catalyst inlet temperature is carried out. For this purpose, a temperature measuring point is essentially immediately upstream of the catalyst 10 arranged in the flue gas path, wherein the temperature measured there is regulated to a desired value or within a setpoint range. In the present example is with this controlled variable on the position of the throttle body 7 intervened. When the temperature at the catalyst inlet increases, the throttle body is opened further, whereby the secondary-side mass flow of the heat transfer apparatus increases, and in consequence - at the same time more constant Temperature of the flue gas entering the heat transfer unit - the temperature at the catalyst inlet drops. The fuel quantity actuator 5 the additional firing 4 comes with the power P _{2 of} the generator 204 the storage fluid expansion turbine 203 controlled as a controlled variable. An increase in the firing rate of the supplemental firing initially leads to an increase in the temperature at the catalyst inlet, and as a consequence of the temperature control mechanism described above, to an increase in the mass flow through the pressure accumulator. The illustrated embodiment further includes temperature measuring points explicitly illustrated 8th and 9, at which the temperature of the flue gas at the outlet of the heat transfer apparatus 202 respectively the temperature of the storage fluid exiting the heat transfer apparatus 202 respectively at the entrance to the storage fluid expansion turbine 203 is determined. Both are used in the sense of safety circuits as control variables for limit regulations. Exceeding a permissible maximum value at the measuring point 9 measured temperature limits the position of the Brennstoffmengenstellorgans 5 , or at least partially excludes this. An undershoot of a permissible minimum temperature at the measuring point 8th causes a limitation or closure of the throttle body 7 , It is clear that the control levels must be hierarchical, in the sense that a border control designed as a safety circuit has priority over the temperature and power control mechanisms described above.

The according to 3 illustrated embodiment differs in terms of the regulation to the effect that the catalyst inlet temperature as a controlled variable for the Brennstoffmengenstellorgan 5 is used while the throttle body 7 is controlled with the power P ₂ as a controlled variable. Furthermore, the loading unit 3 mechanically with the generator 104 the gas turbine group 1 coupled. In the illustrated embodiment, the generator 104 Fully electric motor operated, and is referred to in this context in general as an electric machine or motor / generator unit. The connection with the shaft of the gas turbo group 1 is via a switchable clutch 11 produced; Here also a fixed coupling can be present. At a second shaft end is the motor / generator unit 104 via a switchable coupling 12 with the loading unit 3 coupled. In a pure charging operation is the connection of the clutch 12 closed, and the connection of the clutch 11 open; the motor / generator unit 104 is operated purely by motor. In pure power mode is clutch 11 closed, and clutch 12 open; the engine / generator unit is powered by the gas turbo group 1 driven and works purely as a generator. In addition, there is an advantageous mode of operation in which both clutches are closed. The electric machine 104 It can then assume different operating states from motor to regenerative operation, and it can be varied steplessly between a power-consumption operation and a power-output operation. This mode of operation is perfectly suited to the phase of the electric machine 104 to vary, and thus to realize a reactive power compensation of a connected electricity network in an excellent manner. Furthermore, the power plant has an overflow line 13 with a shut-off and throttle organ 14 on. Fluid can be diverted from the pressure storage process via the overflow line and downstream of the compressor 101 and upstream of the combustion chamber 102 the gas turbine group 1 this be supplied. Thus, a higher mass flow is available for the combustion and expansion in the gas turbine group, as the compressor 101 promote what opens up further performance potential. In the figure, a removal is shown in an intermediate expansion stage of the storage process. The choice of suitable branching depends in particular on the nominal pressure ratio of the storage fluid expansion turbine 203 from; The extraction pressure should be greater than the compressor end pressure of the gas turbine group, but not too much, so that no unnecessarily large throttling losses must be taken into account. It is also a removal in the heat transfer apparatus or between the heat transfer apparatus 202 and the accumulator expansion turbine 203 possible. It is also advantageous if the removal point is selected such that the temperature of the withdrawn fluid at least approximately the temperature at the compressor outlet of the gas turbine group 1 equivalent.

An embodiment in which the overflow line branches off in the heat transfer apparatus is in 4 shown. In the flow direction of the flue gas, the removal point is arranged upstream of the catalyst, such that the temperature of the pressure storage fluid at this point in the range of preferably 350 ° C to 450 ° C or, at high pressure ratios of the gas turbine group, even at 500 ° C or above. This temperature is therefore generally higher than the temperature at the catalyst inlet, resulting in the illustrated preferred arrangement of the sampling point. Furthermore, the electric machine 104 directly coupled with the shaft of the gas turbo group. In this case, the full motor operability of the machine 104 not mandatory.

The following figures illustrate modes of operation of the power plant according to the invention, in which, in the interest of a thermodynamic optimization of the power plant for an explicit regulation Power output of the pressure accumulator system is omitted. The power output of the accumulator then adjusts itself as a result of the thermodynamic parameters.

In the embodiment according to 5 is at a temperature measuring point 8th the flue gas temperature measured downstream of the heat transfer apparatus as exhaust gas temperature. At a temperature measuring point 9 becomes a temperature of the storage fluid at the entrance to the storage fluid expansion turbine 203 measured. The position of the fuel quantity actuator 5 the additional firing device 4 is controlled with the storage fluid turbine inlet temperature as a controlled variable. There is a regulation so that the temperature at the inlet into the storage fluid expansion turbine 203 always kept at a maximum; In this case, as already repeatedly described, a continuous control or a discontinuous control, in particular a two-step control, can be used. In this way, the specific enthalpy gradient across the storage fluid expansion turbine 203 largest, and that in the storage volume 201 stored fluid is used as best as possible for the production of electricity. At the same time the storage volume 201 taken mass flow through intervention on the position of the throttle body 7 adjusted so that the exhaust gas temperature associated with the measuring point 8th is maintained at a minimum permissible value, for example, by a safety margin of 20 ° C above the dew point temperature of a flue gas component. Ensuring the lowest possible exhaust gas temperature ensures the lowest possible exhaust gas heat losses and the best possible use of the flue gas heat. The catalyst 205 is optional. When it is present, it is advantageous to monitor its inlet temperature or material temperature. This happens with the temperature measuring point 10 , If a temperature is observed there which exceeds an upper limit permissible in the interest of system integrity, then the fuel quantity control element is used in the sense of a limit control 5 intervenes, and limits the opening, or the actuator is even closed a piece. In the interest of a protective circuit, this control intervention naturally takes precedence over the regulation of the storage fluid turbine inlet temperature. When the temperature at the measuring point 10 decreases below a value that can ensure a minimum cleaning function of the catalyst, the storage fluid mass flow is reduced, and thus reduces the flue gas temperature drop from the inlet of the heat transfer apparatus to the catalyst, and as a consequence, the catalyst temperature is raised again. In return, the temperature rises at the measuring point 8th and thus the exhaust heat losses; in the interest of a protective circuit, however, the limit control of the catalyst temperature has priority. As can be clearly seen, the limit control of the catalyst temperature is realized in such a way that control interventions always take place on the safe side in the interest of the integrity of the overall system; although the thermodynamic data is degraded, which is reversible, and the protective interventions can not lead to harmful consequences on other components of the power plant. This operation is called storage fluid utilization and exhaust heat optimized operation. The performance of the pressure accumulator results from the adjusting specific enthalpy gradient over the storage fluid expansion turbine 203 and the mass flow of the storage fluid. It would also be possible in principle, the temperature at the measuring point 9 by a change of the storage fluid mass flow with the position of the throttle body 7 to regulate as the manipulated variable, and vice versa, the exhaust gas temperature at the measuring point 8th to be controlled by intervention on the fuel quantity actuator. But it is easy to see that the dynamics of the controlled systems in the context of 5 described example is much easier to survey, which is why the scheme proposed there is the preferred.

According to the in 6 illustrated embodiment, the temperature of the storage fluid at the entrance to the turbine 203 , measured with the measuring point 10 , regulated, wherein the position of the fuel quantity actuator is the manipulated variable, and at the same time, the catalyst temperature or the flue gas temperature upstream of the catalyst, measured with the measuring point 10 , Regulated, wherein the position of the throttle body is the manipulated variable. At the same time, in the sense of protective circuits, limit regulations of the catalyst temperature or of the flue gas temperature are upstream of the catalyst, as well as of the measuring point 8th realized exhaust gas temperature realized. A limitation of the position of the fuel quantity actuator 5 with the temperature of the measuring point 10 as a controlled variable prevents overheating of the catalyst 205 , A limitation of the position of the throttle body 7 with the exhaust gas temperature as a controlled variable prevents a dew point below in the flue gas downstream of the heat transfer apparatus. This control ensures a maximum specific enthalpy gradient across the storage fluid expansion turbine 203 and at the same time the best possible catalytic effect. Accordingly, this operation is referred to as Speicherfluidnutzungs- and catalyst-optimized operation.

According to 7 the temperature is at the measuring point 10 with the position of the fuel quantity actuator 5 the additional firing device 4 regulated as manipulated variable. The exhaust gas temperature 8th is with the position of the throttle body 7 regulated as manipulated variable. This makes it possible to opti male catalyst temperature and the lowest possible exhaust gas temperature set. This is referred to as the catalyst and exhaust heat optimized operation. It is also a limit control of the storage fluid turbine inlet temperature, measured with the measuring point 9 , provided by optionally opening the fuel quantity actuator 5 is limited in terms of a protective circuit.

In the embodiment according to 8th is downstream of the heat transfer apparatus 202 a heat exchanger 15 with an external firing 16 arranged in the flow path of the storage fluid. Of course, here also a firing device can be arranged directly in the storage fluid flow path; however, as mentioned above, this has implications for the operation or selection of the downstream storage fluid expansion turbine. In the case of an external firing arrangement, however, care must be taken to make explicit use of the thermal potentials provided by external firing. This is due to the fact that the storage fluid when flowing into the heat exchanger 15 already has an elevated temperature. That in the furnace 16 provided hot gas can but in the heat exchanger 15 only be cooled to this temperature. It is therefore according to the in 8th illustrated embodiment, the flue gas of the external firing device after flowing through the heat exchanger 15 into the flue gas path of the gas turbine group. The flue gas then flows through together with the flue gas of the gas turbine group, the heat transfer apparatus 202 , wherein the flue gas heat is used further. In the embodiment, the fuel supply to the external furnace 16 by intervening on the fuel quantity actuator 17 regulated to a constant maintenance of the inlet temperature of the storage fluid expansion turbine. The control of the fuel supply to the additional flue gas firing 4 and the storage fluid mass flow in the manner described above, with the catalyst temperature or catalyst inlet temperature as control variables. Furthermore, a shunt line 18 the storage fluid flow path arranged. By means of the directional valve 19 Optionally, the storage fluid mass flow may be through the secondary side of the heat transfer apparatus 202 or through the shunt line. This gives the system very good emergency power generation characteristics: In case of failure of the gas turbo group 1 storage fluid becomes the storage fluid expansion turbine 203 directed. Thus, the turbine is capable of the generator 204 To power, and thus electricity can be generated. When eliminating the heat in the heat transfer apparatus 202 can supply heat to the storage fluid in the heat exchanger 15 respectively; this increases the specific enthalpy gradient across the turbine 203 and thus the utilization of the stored fluid. The conduction of the fluid through the shunt line 28 on the one hand reduces the pressure losses in the flow path. On the other hand, the stored fluid can be used even when the flow path through the heat transfer apparatus 202 For example, as a result of a grosshavarie the gas turbine group is not available. It should not go unmentioned that, provided fluid in memory 201 stored, the storage fluid expansion turbine 203 only by opening the throttle body 7 and applying the turbine 203 can be approached with pressurized storage fluid without auxiliary power.

The preceding embodiments give the expert an instructive insight into the variety the possible embodiments within the scope of the invention and operating modes of a power plant of the type mentioned, the illustrated embodiments not exhaustive should and can be. In particular, you can Design features of the described embodiments almost arbitrary be combined with each other. The different ones described Regulatory mechanisms can be combined in a single plant, and it can Switched between the different operating and control modes be, even while of the operation.

The embodiments and described control variants show impressively on which options by the inventive Arrangement of a heat supply device, in particular an additional firing device, downstream of the gas turbine group, by which the operation of the downstream pressure accumulator system can be largely decoupled from the operation of the gas turbine group.

1

Gas turbine group

2

Pressure storage plant

3

loader for pressure accumulator

4

heat supply, Nachfeuerungseinrichtung

5

Fuel-volume control member

6

Fuel-volume control member

7

Shut-off and / or throttle body

8th

Temperature measuring point, for exhaust gas temperature

9

Temperature measuring point, for storage fluid temperature downstream

of Erhitzers and / or at the entrance to the

Accumulator fluid expansion engine

10

Temperature measuring point, for flue gas temperature upstream of one

catalyst or catalyst temperature

11

clutch

12

clutch

13

overflow

14

Shut-off and / or throttle body

15

Storage fluid additive heating device, heat exchangers

16

external heating

17

Fuel-volume control member

18

Shunt line

19

way valve

101

compressor

102

combustion chamber

103

turbine

104

electrical Machine, motor / generator unit, generator

201

storage volume

202

The heat transfer apparatus

203

Accumulator fluid expansion engine,

Accumulator fluid expansion turbine

204

generator

205

catalyst

301

compressor

302

Cooler and dehumidifiers

303

compressor

304

Cooler and dehumidifiers

305

drive motor

306

return unit

P ₁

generator power the gas turbine group

P ₂

generator power the accumulator system

Claims (18)

Power plant comprising a gas turbine group ( 1 ), a compressed air storage ( 201 ), and at least one storage fluid relaxation engine ( 203 ), wherein the gas turbine group at least one compressor ( 101 ), at least one combustion chamber arranged downstream of the compressor ( 102 ), and at least one downstream of the combustion chamber arranged first turbine ( 103 ), and in which power plant downstream of the first turbine, a heat transfer apparatus ( 202 ), which is arranged on the primary side in the flue gas path of the turbine, and which on the secondary side in one of the compressed air reservoir ( 201 ) to the storage fluid relaxation engine ( 203 ) is arranged leading storage fluid flow path , characterized in that in the flue gas path of the gas turbine group upstream of the heat transfer apparatus, a heat supply device, in particular an additional firing device ( 4 ) is arranged. Power plant according to claim 1, characterized in that in the flue gas path of the gas turbine group downstream of the heat transfer apparatus ( 202 ) a temperature measuring point ( 8th ) is arranged for measuring the flue gas outlet temperature, that in the fluid flow path between the compressed air reservoir and the storage fluid-recirculation engine, a shut-off and / or throttle member ( 7 ) is arranged, and that a temperature controller is connected to the flue gas outlet temperature as a controlled variable and the position of the shut-off and / or throttle member as a manipulated variable. Power plant according to one of claims 1 or 2, comprising means ( 9 ) for determining the storage fluid temperature downstream of the heat transfer apparatus or at the outlet from the heat transfer apparatus, characterized in that a temperature controller with the determined storage fluid temperature as a controlled variable and with the position of a fuel mass flow actuator ( 5 ) of the supplementary firing device ( 4 ) is connected as a controlled variable. Power plant according to one of the preceding claims, characterized in that a power regulator with the electrical power (P ₂ ) of the generator ( 204 ) of the pressure accumulator system as a controlled variable and with the position of a fuel mass flow actuator ( 5 ) of the supplementary firing device ( 4 ) is connected as a manipulated variable. Power plant according to one of the preceding claims, characterized in that in the flue gas path of the gas turbine group a flue gas purification catalyst ( 205 ) is arranged. Power plant according to claim 5, characterized in that that the flue gas purification catalyst downstream of a first part the primary-side flow path of the heat transfer apparatus and upstream of a second portion of the primary side flow path of the heat transfer apparatus is arranged. Power plant according to one of claims 5 or 6, comprising a temperature measuring point ( 10 ) for measuring the temperature at the catalyst inlet and / or the catalyst temperature, characterized in that in the fluid flow path between the compressed air reservoir ( 201 ) and the storage fluid relaxation engine ( 203 ) a shut-off and / or throttle member ( 7 ), and, that a temperature controller is connected to the measured temperature as a controlled variable and the position of the shut-off and / or throttle member as the manipulated variable. Power plant according to one of claims 5 or 6, comprising a temperature measuring point ( 10 ) for measuring the temperature at the catalyst inlet and / or the catalyst temperature, characterized in that a temperature controller with this measured temperature as a controlled variable and the position of a fuel mass flow actuator ( 5 ) of supplementary firing ( 4 ) connected as a manipulated variable is. Power plant according to one of the preceding claims, characterized characterized in that in the storage fluid flow path upstream of the storage fluid relaxation engine and downstream of the heat transfer apparatus an additional heat supply for the Storage fluid is arranged. Power plant according to claim 9, characterized in that the additional heat supply means an external firing device ( 16 ) and a heat exchanger ( 15 ), and that a flow path for the flue gas of the external firing device ( 16 ) passes through the heat exchanger and downstream of it into the flue gas path of the gas turbine group opens, such that the flue gas of the external Feuerugseinrichtung together with the flue gas of the gas turbine group the heat transfer apparatus ( 202 ) flows through. Power plant according to one of claims 9 or 10, comprising means ( 9 ) for determining the temperature of the storage fluid at the inlet to the storage fluid expansion engine ( 203 ), characterized in that a temperature controller with the determined storage fluid temperature as a controlled variable and with the position of a fuel quantity actuator ( 17 ) of the additional heat supply device is connected as a manipulated variable. Power plant according to one of claims 9 or 10, characterized in that a power regulator with the electrical power (P ₂ ) of the generator ( 204 ) of the pressure accumulator system as a controlled variable and with the position of a fuel mass flow actuator ( 17 ) of the additional heat supply device is connected as a manipulated variable. Power plant according to one of the preceding claims, characterized in that a line ( 13 ) is arranged, via which fluid from the compressed air reservoir ( 201 ) to the gas turbine group ( 1 ) and which line downstream of the compressor ( 101 ) and upstream of the combustion chamber ( 102 ) opens in the gas turbine group. Power plant according to one of the preceding claims, characterized in that a shunt line ( 18 ), which upstream of the heat transfer apparatus ( 202 ) branches off the storage fluid flow path and downstream of the heat transfer apparatus ( 202 ) and upstream of the storage fluid relaxation engine ( 203 ) opens again in the storage fluid flow path. Power plant according to one of the preceding claims, characterized in that for charging the compressed air reservoir compressor ( 301 . 303 ) with compressor drives ( 305 ) arranged by the gas turbine group ( 1 ) and the storage fluid relaxation engine ( 203 ) are arranged completely separated. Method for operating a power plant, which method comprises: the flue gas of a gas turbine group through the primary side of a heat transfer apparatus ( 202 ) to direct; a storage fluid mass flow from a compressed air storage volume ( 201 ), the storage fluid mass flow through the secondary side of the heat transfer apparatus ( 202 ) and to heat in heat exchange with the flue gas; the heated storage fluid mass flow in at least one storage fluid expansion engine ( 203 ) to relax; characterized by the further step, the flue gas downstream of the gas turbine group ( 1 ) and upstream of the heat transfer apparatus ( 202 ) Heat, in particular by an additional firing ( 4 ) in the flue gas path. Process according to Claim 15, further comprising at least one of the following Measure temperatures: the storage fluid temperature at the outlet from the heat transfer apparatus, the flue gas temperature upstream of a catalyst; the temperature the catalyst; the flue gas temperature downstream of the heat transfer apparatus; a measured temperature as a controlled variable for the heat supply to use flue gas; the heat supply to the flue gas so too regulate that the controlled variable held at a setpoint or within a setpoint interval becomes. Process according to Claim 15, further comprising at least one of the following Measure temperatures: the storage fluid temperature at the outlet from the heat transfer apparatus, the flue gas temperature upstream of a catalyst; the temperature the catalyst; the flue gas temperature downstream of the heat transfer apparatus; a measured temperature as a controlled variable for the off to use the mass flow taken from the accumulator volume; to regulate the mass flow taken from the accumulator volume so that the controlled variable held at a setpoint or within a setpoint interval becomes.