DE102011007753A1 - Multi-pressure CAES process - Google Patents

Abstract

The present invention relates to a heat exchanger assembly (100) for heating a working gas for a turbine (130) of a compressed air storage power plant (120). The heat exchanger arrangement (100) has a first gas inlet (101) which can be coupled to a pressure chamber (160) of the compressed air storage power plant (120), so that a working gas having a first inlet temperature (T _E1 ) from the pressure chamber (160) to the heat exchanger arrangement (100) can be fed. Furthermore, the heat exchanger arrangement (100) has a first gas outlet (111), which can be coupled to the turbine (130), so that the working gas can be supplied to the turbine (130) with a first outlet temperature (T _A1 ) from the heat exchanger arrangement (100) is. Further, the Warmeübertrageranordnung (100) a second gas inlet (102) which can be coupled to the turbine (130) on, so that the working gas to a second input temperature (T _E2) from the turbine (130) to the Wärmeubertrageranordnung (100) fed is. Furthermore, the heat exchanger arrangement (100) has a second gas outlet (112) which can be coupled to the turbine (130), so that the working gas can be supplied to the turbine (130) at a second outlet temperature (T _A2 ) from the heat exchanger arrangement (100) is. A heating means can be supplied in such a way that the working gas can be heated from the first inlet temperature (T _E1 ) to the first outlet temperature (T _A1 ) and the working gas can be heated from the second inlet temperature (T _E2 ) to the second outlet temperature (T _A2 ).

Description

Technical area

The present invention relates to a heat exchanger assembly for heating a working gas for a turbine of a compressed air storage power plant.

Furthermore, the present invention relates to a compressed air storage power plant.

Furthermore, the present invention relates to a method for heating a working gas for a turbine of a compressed air storage power plant.

Background of the invention

The total electricity demand of many countries is increasingly covered by renewable energy sources, such as solar or wind energy. This leads to a multiplicity of smaller decentralized power plants, which are operated with regenerative energy sources. The power generated by power plants with renewable energy sources varies due to z. B. the weather, such as wind change or fluctuating sunshine periods.

Therefore, with an increasing number of power plants operated with regenerative energy sources, the use of storage power plants is required. In storage power plants, a surplus of energy produced is temporarily stored and, if necessary, retrieved for power generation. Known storage power plant types are, for example, pumped storage power plants and compressed air storage power plants. In a pumped storage power plant, water is pumped with the surplus energy generated in a high-level reservoir. When energy is needed, the water from the high-level reservoir via downpipes further downstream turbines is supplied to operate a power generator.

A compressed air storage (CAES) power plant uses the energy surplus to drive a compressor which pumps pressurized air in a pressure space, such as an underground cavern. If there is a higher power demand, the compressed air from the pressure space is used to operate a turbine, which in turn operates a coupled power generator.

In order to reduce a loss in buffering the energy in storage power plants, it is necessary to provide the storage power plants with high efficiency. Typically, in compressed air storage power plants to increase the efficiency of the working fluid is heated before entering a turbine.

In 5 is a conventional process of a compressed air storage power plant shown. The working fluid, such as compressed air, is from a pressure chamber 501 , such as an underground cavity, prior to entering a turbine 502 a conventional heat exchanger 500 fed. The working fluid indicates when entering the heat exchanger 500 a first input temperature T _E1 . The heat exchanger 500 a first heat energy Q _{zu, 1 is} supplied. By means of the heat energy Q _{to, 1} , the working fluid is heated to a first outlet temperature T _A1 . With this first outlet temperature T _A1 , the working fluid of the turbine 502 supplied at a first turbine stage. The excess heat energy in the heat exchanger 500 is discharged as the first waste heat Q _{ab, 1} . In the turbine 502 relaxes the working fluid and according to a conventional gas turbine process this produces mechanical work, with which a generator 503 is operable to generate electricity.

Presentation of the invention

It is an object of the present invention to provide a compressed air storage power plant with a high efficiency.

The object is achieved by a heat exchanger arrangement for heating a working gas for a turbine of a compressed air storage power plant, by a compressed air storage power plant and by a method for heating a working gas for a turbine of a compressed air storage power plant according to the independent claims.

According to a first aspect of the present invention, a heat exchanger assembly for heating a working gas for a turbine of a storage power plant, in particular a compressed air storage power plant is described. The heat exchanger arrangement has a first gas inlet, a first gas outlet, a second gas inlet and a second gas outlet. The first gas inlet is coupled to a pressure chamber, so that a working gas with a first inlet temperature from the pressure chamber to the heat exchanger assembly can be fed. The first gas outlet can be coupled to the turbine, so that the working gas can be supplied to the turbine with a first outlet temperature from the heat exchanger arrangement. The second gas inlet can be coupled to the turbine, so that the working gas can be supplied to the turbine of the heat exchanger arrangement with a second inlet temperature. The second gas outlet can be coupled to the turbine, so that the working gas can be supplied to the turbine with a second outlet temperature from the heat exchanger arrangement. One Heating means can be supplied in such a way that the working gas can be heated from the first inlet temperature to the first outlet temperature. The working gas is further heated from the second input temperature to the second outlet temperature by means of a heating means.

In accordance with another aspect of the present invention, a compressed air storage power plant includes a pressure space, a turbine, and the heat transfer assembly described above.

In accordance with another aspect of the present invention, a method for heating a working gas for a turbine of a compressed air storage power plant is described. According to the method, a first working gas is supplied at a first inlet temperature from a pressure space to a first gas inlet of a heat exchanger arrangement. The working gas is heated from the first inlet temperature to the first outlet temperature by means of a heating means in the heat exchanger assembly. The working gas is supplied to the turbine at a first outlet temperature from the heat exchanger assembly. Further, the working gas is supplied at a second input temperature from the turbine to a second gas inlet of the heat exchanger assembly. The working gas is heated from the second input temperature to the second outlet temperature by means of a heating means. The working gas is supplied to the turbine at a second outlet temperature from the heat exchanger assembly.

According to a further exemplary embodiment, a compressed air storage power plant is described, which has the above-described pressure chamber, the turbine and the heat exchanger arrangement described above.

The heat exchanger assembly may include one or more heat transfer devices (recuperators). A recuperator serves to preheat the working gas by means of a heating means or by means of several different heating means.

In a compressed air storage power plant, a working gas from a pressure space, such as from an underground cavity, is conveyed and supplied to the turbine. The working gas from the pressure chamber has a high pressure. In the turbine, the working gas relaxes, so that the energy of the working gas is converted into mechanical work. The turbine in turn drives a power generator, which generates electricity. If less power is required, the working gas in the pressure chamber z. B. fed by means of a compressor, so that increases the pressure in the pressure chamber. In the pressure chamber, the working gas is stored under high pressure.

By expanding the working gas in the turbine, the working gas cools off sharply. The turbine has, for example, a first turbine stage (or a first thermodynamic expansion zone), a second turbine stage (or a second thermodynamic expansion zone) or a plurality of further turbine stages (or further thermodynamic expansion zones). The second turbine stage is downstream of the first turbine stage with respect to a flow direction of the working gas in the turbine downstream of the first turbine.

In order to increase the efficiency, the working gas in the heat exchanger assembly is heated from the first input temperature (temperature of the working gas in the pressure space) to a first outlet temperature higher than the first input temperature by means of a heating means.

In addition, the working gas, for example after the first or the second turbine stage of the turbine, removed and fed to the second gas inlet of the heat exchanger assembly. The heat exchanger assembly heats the working gas from a second input temperature to a second outlet temperature, which is higher than the second input temperature, by means of the heating means, and supplies the working gas to the turbine again. This interim removal of the working gas from the turbine, the intermediate heating and the subsequent return of the working gas with the second outlet temperature leads to an increase in the efficiency of the turbine. In particular, the pressure of the working gas between the bleed from the turbine, the supply to the second gas inlet and the supply of the heated working gas to the second gas outlet, which is in turn coupled to the turbine, kept almost constant. With such an intermediate heating, the efficiency of the turbine is increased. The intermediate heating can be carried out at several turbine stages of the turbine.

In other words, according to the present invention, at a certain point of the expansion process of the working gas in the turbine, the working gas can be taken out and fed again to the heat exchanger arrangement. In the heat exchanger arrangement, the supplied working gas is reheated and fed as supply air back to the turbine. This increases the efficiency of the turbine. With the same Graßigkeit the Warmeubertrageranordnung the heat means in the heat exchanger assembly more heat can be withdrawn and thus allow efficient heating of the working gas.

The heating means may be taken, for example, from a heat generating device. The warming means is for example an exhaust gas of a gas turbine. Further, the heating means may be a heated oil or heated water, which is warmed up, for example, by solar power.

According to a further exemplary embodiment of the present invention, the heat transfer assembly further comprises a further second gas inlet, which is coupled to the turbine, so that the working gas with a further second input temperature from the turbine to the heat transfer assembly can be fed. Furthermore, the heat exchanger arrangement has a further second gas outlet, which can be coupled to the turbine, so that the working gas can be supplied to the turbine with a further second outlet temperature from the heat exchanger arrangement. The heating means can be supplied in such a way that the working gas can be heated from the further second inlet temperature to the further second outlet temperature.

For example, according to the embodiment described above, a plurality of taps may be established on the turbine to bleed working gas and supply it to the heat exchanger assembly. The tapped working gas is heated in each case in the heat exchanger arrangement and then fed back to the turbine.

According to a further exemplary embodiment, the heat exchanger arrangement has a first heat transfer device. The first heat transfer device includes the first gas inlet, the first gas outlet, and a first heat input. Furthermore, the heat exchanger assembly comprises a second or a plurality of further second heat exchanger devices, which in each case has the second gas inlet, the second gas outlet and a second heat medium inlet. The first heat transfer device may be structurally separate from the second heat transfer device. Furthermore, the first heat transfer device and the second heat transfer device can be arranged together in a common housing.

According to another exemplary embodiment, the first heat medium inlet and the second heat medium inlet are coupleable to a common heat generating device. For example, the first heat transfer device and the second heat transfer device may share a common heat medium which is heated by the common heat generating device. For example, as a heat generating device, a gas turbine may supply hot exhaust gas to the first heat transfer device and the second heat transfer device.

According to another exemplary embodiment, the first heat transfer device has a heat medium outlet for discharging the heating medium with a first waste heat. The Wärmemittelauslass and the second heat medium inlet are coupled together such that the heating means with the first waste heat can be supplied to the second heat medium inlet.

Thus, the Graderigkeit of the heat exchanger assembly, in particular the first heat transfer device and the second heat transfer device is improved. The heating means, which exits the first heat transfer device with the first waste heat, can be used efficiently as a heating means for the second heat transfer device. The overall efficiency of the heat exchanger assembly is thereby increased.

Additionally or alternatively, in a further exemplary embodiment, the first heat medium inlet can be coupled to the heat-generating device and the second heat medium inlet can be coupled to a further heat-generating device. For example, the first heat transfer device can be operated with a first heating means and the second heat transfer device with a second heating means.

As the first heating means, for example, the exhaust gas of a gas turbine can be used as a heat-generating device. As another warming agent, for example, exhaust gas of another gas turbine and / or hot oil or hot water which z. B. was heated in a solar power plant as another heat-generating device used.

The first gas outlet of the heat exchanger arrangement is coupled to the turbine such that the working gas can be supplied to the first outlet temperature of the first turbine stage. The second gas outlet of the heat exchanger arrangement is coupled to the turbine such that the working gas with the second inlet temperature between the first turbine stage and the second turbine stage can be removed and the heat exchanger assembly can be fed. The second gas outlet of the heat exchanger arrangement is coupled to the turbine such that the working gas can be supplied to the second outlet temperature upstream of the second turbine stage. In an exemplary embodiment, the working gas with the second outlet temperature can also be fed to a subsequent, arranged after the second turbine stage, turbine stage.

With the invention described above, various embodiments are explained in summary, with which the efficiency of a turbine is increased in a compressed air storage power plant. According to a first exemplary embodiment, a working gas is taken from the pressure chamber on the one hand and heated in the heat exchanger arrangement. In the same heat exchanger arrangement, a further working gas, which has been tapped from the turbine, is also supplied and heated in the same heat exchanger arrangement.

In a further exemplary embodiment, the heat exchanger arrangement is formed from, for example, two or more heat exchanger devices, with a first heat exchanger device (a first recuperator) allowing a first-time heating of the working gas. Another heat transfer device (another recuperator) receives the working gas drawn from the turbine, heats it and supplies the working gas to the turbine again. In the embodiment with different heat transfer devices, this opens up the possibility of operating each heat transfer device with an associated heat source (heat generating device). For example, the one heat transfer device can be operated by means of a gas turbine and the other heat transfer device by means of a solar power plant. In addition, this opens the possibility that the various heat transfer devices can operate at different temperature levels, since each heating means can have a different temperature.

According to a third embodiment of the present invention, the heat exchanger assembly may include a plurality of gas inlets which receive the working gas from the pressure space or from different turbine stages of the turbine to heat the working gas.

It should be noted that the embodiments described herein represent only a limited selection of possible embodiments of the invention. Thus, it is possible to combine the features of individual embodiments in a suitable manner with one another, so that for the person skilled in the art with the variants of embodiment that are explicit here, a multiplicity of different embodiments are to be regarded as obviously disclosed.

Brief description of the drawings

In the following, for further explanation and for better understanding of the present invention, embodiments will be described in more detail with reference to the attached figures.

1 shows a schematic representation of a compressed air storage power plant with a heat exchanger assembly according to an exemplary embodiment of the present invention;

2 shows a schematic representation of a compressed air storage power plant in which the heat exchanger assembly comprises a plurality of second gas inlets and a plurality of second gas outlets according to an exemplary embodiment of the present invention;

3 shows a schematic representation of a compressed air storage power plant with a heat exchanger assembly having a first heat transfer device and a second heat transfer device according to an exemplary embodiment of the present invention;

4 1 is a schematic of a compressed air storage power plant according to an exemplary embodiment of the present invention, wherein a heat exchanger assembly includes a first heat transfer device and a second heat transfer device coupled together; and

5 shows a schematic representation of a conventional heat exchanger assembly for a turbine.

Detailed description of exemplary embodiments

The same or similar components are provided in the figures with the same reference numerals. The illustrations in the figures are schematic and not to scale.

1 shows a heat exchanger assembly 100 for heating a working gas for a turbine 130 a compressed air storage power plant 120 , A working gas can come from a pressure chamber 160 , such as a subterranean cavity, and the heat exchanger assembly 100 be supplied at a first gas inlet with a first temperature T _E1 . Furthermore, the heat exchanger arrangement 100 with a heat generating device 140 coupled. From the heat generating device 140 For example, a first heat energy supply Q _{zu, 1 can be} provided. In particular, a warming means such as hot water or hot exhaust gas of a gas turbine becomes the first heat medium inlet 103 provided.

The working gas passes first to the pressure chamber 160 the heat exchanger arrangement 100 and is at a first outlet temperature T _A1 at the first gas outlet 111 the heat exchanger assembly 100 dissipated. The working gas is at the first outlet temperature T _{A1 of} the turbine 130 fed. The working gas passes through the individual turbine stages I to III in the flow direction until it finally leaves the turbine 130 flows. The energy of the working gas becomes mechanical work by means of the turbine 130 converted and thereby a generator 150 , in particular for power generation, operated.

To increase the efficiency of the turbine 130 the working gas with the second input temperature T _E2 at least partially removed and a second gas inlet 102 the heat exchanger assembly 100 fed. The working gas in turn passes through the heat exchanger assembly 100 and heats up to a second outlet temperature T _A2 . From a second gas outlet 112 becomes the working gas with the second outlet temperature T _{A2 of} the turbine 130 fed again. This intermediate heating of the working gas increases the efficiency of the turbine 130 ,

As in 1 shown, the turbine points 130 a first turbine stage I, a second turbine stage II and a third turbine stage III (or a further plurality of turbine stages). The turbine stages I to III are each successively in the flow direction of the working gas through the turbine 130 arranged. The working gas, which comes from the pressure chamber 160 is partially removed and after heating from the first gas outlet 111 is provided with a first outlet temperature T _A1 , the first turbine stage I is generally supplied. The bleed of the working gas and the supply to the second gas inlet 112 the heat exchanger arrangement 100 usually takes place in one of the following turbine stages II, III. For example, the working gas is taken between the first turbine stage I and the second turbine stage II and the second gas inlet 102 fed to. After heating the working gas from the second input temperature T _E2 to the second outlet temperature T _A2 , the heated working gas is at the second gas outlet 112 deployed and again the turbine 130 fed. In this case, the working gas with the second outlet temperature T _A2, for example, near the place of removal, that is supplied in the above example between the first turbine stage I and the second turbine stage II. Alternatively, the heated working gas can also be supplied to a subsequent turbine stage, for example between the second turbine stage II and the third turbine stage III.

The warming medium flows through the heat exchanger arrangement 100 and leaves it with a first waste heat Q _{from, 1} .

2 shows another exemplary embodiment of the present invention, wherein the working gas at multiple points of the turbine 130 is removed and by means of the heat exchanger arrangement 100 is warmed up. As in 2 is shown, first with the heat exchanger assembly 100 the working gas with a first inlet temperature T _E1 of the pressure chamber 160 the first gas inlet 101 the heat exchanger arrangement 100 provided. The heat exchanger arrangement 100 heated by means of the heating means, the working gas to the first outlet temperature T _A1 and provides this working gas to the first gas outlet 111 ready. From the first gas outlet 111 the working gas thus heated is supplied to the first turbine stage I.

The warming agent is in turn passed through a heat generating device 140 provided with a first heat energy Q _{to, 1} the heat medium inlet 103 fed.

After the first turbine stage I becomes (one part) of the working gas of the turbine 130 taken. This working gas is at a second inlet temperature T _E2 at the second gas inlet 102 the heat exchanger assembly 100 provided and heated in this. At a second gas outlet 112 the working gas has the second outlet temperature T _A2 , which is higher than the second inlet temperature T _E2 . The working gas is at the second outlet temperature T _{A2 of} the turbine 130 fed. In particular, the thus heated working gas is supplied in the vicinity of the working gas removal, ie also between the first turbine stage I and the second turbine stage II. The pressure of the working gas is kept almost constant between the removal after the first turbine stage I and the renewed supply of the second turbine stage II so as to avoid energy loss.

Further shows 2 a further removal (of a part) of the working gas after the second turbine stage II. The working gas is tapped again after the second turbine stage II and with a third inlet temperature T _E3 the further second gas inlet 201 the heat exchanger assembly 100 fed. The heating means heats the working gas to the third outlet temperature T _A3 . From another second gas outlet 202 the working gas is supplied to the third outlet temperature T _A3 between the second turbine stage II and the third turbine stage III.

Thus, a heat exchanger assembly 100 with a common heating medium between the working gas between a plurality of turbine stages I to III between warm, thus high efficiency of the turbine 130 to create. The heating means leaves the heat exchanger arrangement 100 With a first waste heat Q _{ab, 1} . Since the heating means several passes of the working gas through the heat exchanger assembly 100 , as in 2 shown, heated, the heating means can give more heat energy to the working gas, thereby increasing the efficiency of the heat exchanger assembly 100 is increased.

3 shows a further exemplary embodiment of the present invention, in which the heat exchanger assembly 100 a first heat transfer device 301 and a second heat transfer device 302 having.

The first heat exchanger device draws the working gas with the first inlet temperature T _E1 from the pressure chamber 160 , Further, at the first heat medium inlet 103 a heating means having a first heat energy Q _{to, 1} from the heat generating device 140 based. In the first heat transfer device 301 the working gas flows between the first gas inlet 101 to the first gas outlet 111 and is heated from the first input temperature T _E1 by means of the heating means to the first outlet temperature T _A1 . From the first gas outlet 111 the working fluid flows to the turbine 130 and in particular to the first turbine stage I, to the turbine 130 to operate.

After the heating medium has heated the working gas to the first outlet temperature T _A1 , this is dissipated with a first waste heat Q _{ab, 1} .

Further shows 3 a second heat transfer device 302 , The heat transfer device 302 has the second gas inlet 102 and the second gas outlet 112 on. From the turbine 130 the working gas can be tapped and by means of the second input temperature T _E2 the second gas inlet 102 to be provided. After heating the working gas to the second outlet temperature T _A2 , the working gas is the second gas outlet 112 deployed and again the turbine 130 fed.

According to 3 For example, the working gas is taken from the second turbine stage II and fed to the subsequent third turbine stage III again. The second heat transfer device 302 can have a second heat input 303 For example, the heating means with the first heat energy supply Q _{to, 1} from the heat generating device 140 Respectively. In this embodiment, one and the same heat generating device 140 a variety of heat transfer devices 301 . 302 provide with heat.

Alternatively or additionally, for example, a further heat-generating device 340 be provided, which provides a further heat means with a second heat energy Q _{to, 2} the further heat medium inlet. After heating the working gas from the second input temperature T _E2 to the second outlet temperature T _A2 , the further heating means with a second waste heat Q _{ab, 2} from the second Warmeübertragervorrichtung 302 led away.

With this embodiment, it is possible to have several different heat-generating devices 140 . 340 to use. For example, the heat-generating device 140 represent a gas turbine and hot exhaust gas of the first heat transfer device 301 respectively. The further heat-generating device 340 For example, it may represent a solar power plant and heat by solar energy another heating means, such as water or oil, and this as a second heat energy supply Q _{to, 2 of} the second heat transfer device 302 respectively.

4 shows a further exemplary embodiment, which essentially the same features of the embodiment 3 having. The heat exchanger arrangement 100 has the first heat transfer device 301 and the second heat transfer device 302 on.

Additionally or alternatively to the exemplary embodiment 3 shows the exemplary embodiment 4 a Wärmemittelauslass 401 the first heat transfer device 301 , Over the Wärmemittelauslass 401 becomes the heating means after the working gas in the first heat transfer device 301 warmed up, with a first down heat Q _{off, 1} dissipated. The Wärmemittelauslass 401 and the second heat medium inlet 303 are coupled to each other such that the heat means having the first waste heat Q _{ab, 1} the second heat medium inlet 303 can be fed. The heat means with the first waste heat Q _{ab, 1} from the first heat transfer device 301 is thus supplied as a heat medium with a second heat energy Q _{to, 2} . Thus, more heat energy is removed from the heat medium in the overall process and reduces the unused waste heat. The overall efficiency of the heat exchanger arrangement 100 and thus the compressed air storage power plant 120 is increased by this.

In addition, it should be noted that "encompassing" does not exclude other elements or steps, and "a" or "an" does not exclude a multitude. It should also be appreciated that features or steps described with reference to one of the above embodiments may also be used in combination with other features or steps of other embodiments described above. Reference signs in the claims are not to be regarded as a limitation.

Claims (10)

Heat exchanger arrangement ( 100 ) for heating a working gas for a turbine ( 130 ) of a compressed air storage power plant ( 120 ), the heat exchanger arrangement ( 100 ) having a first gas inlet ( 101 ), which with a pressure chamber ( 160 ) of the compressed air storage power plant ( 120 ) can be coupled so that a working gas having a first inlet temperature (T _E1 ) of the pressure chamber ( 160 ) to the heat exchanger assembly ( 100 ), a first gas outlet ( 111 ), which with the turbine ( 130 ) is coupled, so that the working gas with a first outlet temperature (T _A1 ) of the heat exchanger assembly ( 100 ) to the turbine ( 130 ), a second gas inlet ( 102 ), which with the turbine ( 130 ) is coupled, so that the working gas with a second input temperature (T _E2 ) from the turbine ( 130 ) to the heat exchanger assembly ( 100 ), a second gas outlet ( 112 ), which with the turbine ( 130 ) is coupled, so that the working gas with a second outlet temperature (T _A2 ) of the heat exchanger assembly ( 100 ) to the turbine ( 130 ), wherein a heating medium can be fed in such a way that a) the working gas can be heated from the first inlet temperature (T _E1 ) to the first outlet temperature (T _A1 ), and b) the working gas can be heated from the second inlet temperature (T _E2 ) second outlet temperature (T _A2 ) is heated. Heat exchanger arrangement ( 100 ) according to claim 1, further comprising a further second gas inlet ( 201 ), which with the turbine ( 130 ) is coupled so that the working gas with a further second input temperature (T _E3 ) from the turbine ( 130 ) to the heat exchanger arrangement ( 100 ) is fed, and another second gas outlet ( 202 ), which with the turbine ( 130 ) can be coupled, so that the working gas with a further second outlet temperature (T _A2 ) of the heat exchanger arrangement ( 100 ) to the turbine ( 130 ), wherein the heating means can be fed in such a way that c) the working gas can be heated from the further second inlet temperature (T _E3 ) to the further second outlet temperature (T _A3 ). Heat exchanger arrangement ( 100 ) according to claim 1 or 2, further comprising a first heat transfer device ( 301 ), which the first gas inlet ( 101 ), the first gas outlet ( 111 ) and a first heat medium inlet ( 103 ), and a second heat transfer device ( 302 ), which the second gas inlet ( 102 ), the second gas outlet ( 112 ) and a second heat medium inlet ( 303 ) having. Heat exchanger arrangement ( 100 ) according to claim 3, wherein the first heat medium inlet ( 103 ) and the second heat medium inlet ( 303 ) with a heat generating device ( 140 ) can be coupled. Heat exchanger arrangement ( 100 ) according to claim 3 or 4, wherein the first heat transfer device ( 301 ) a Wärmemittelauslass ( 401 ) for discharging the heating medium with a first waste heat (Q _{ab, 1} ), wherein the Wärmemittelauslass ( 401 ) and the second heat medium inlet ( 303 ) are coupled to one another in such a way that the heating means with the first waste heat (Q _{ab, 1} ) the second heat medium inlet ( 303 ) is feedable. Heat exchanger arrangement ( 100 ) according to claim 3, wherein the first heat medium inlet ( 103 ) with a heat generating device ( 140 ), and wherein the second heat medium inlet ( 303 ) with another heat generating device ( 340 ) can be coupled. Compressed air storage power plant ( 120 ), comprising a pressure chamber ( 160 ), a turbine ( 130 ), and a heat exchanger arrangement ( 100 ) according to one of claims 1 to 6. Compressed air storage power plant ( 120 ) according to claim 7, wherein the turbine ( 130 ) has a first turbine stage (I) and a second turbine stage (II), wherein the second turbine stage (II) with respect to a flow direction of the working gas in the turbine ( 130 ) is arranged downstream of the first turbine stage (I), wherein the first gas outlet ( 111 ) of the heat exchanger arrangement ( 100 ) so with the turbine ( 130 ), that the working gas with the first outlet temperature (T _A1 ) of the first turbine stage (I) can be supplied, wherein the second gas inlet ( 102 ) of the heat exchanger arrangement ( 100 ) so with the turbine ( 130 ), that the working gas with the second inlet temperature between the first turbine stage (I) and the second turbine stage (II) can be removed and the heat exchanger assembly ( 100 ), and the second gas outlet ( 112 ) of the heat exchanger arrangement ( 100 ) so with the turbine ( 130 ) is coupled, that the working gas with the second outlet temperature (T _A2 ) of the second turbine stage (II) can be fed. Compressed air storage power plant ( 120 ) according to claim 7 or 8, wherein the pressure chamber ( 160 ) is formed in an underground cavity. Method for heating a working gas for a turbine ( 130 ) of a compressed air storage power plant ( 120 ), the method comprising supplying the working gas with a first inlet temperature (T _E1 ) from a pressure chamber ( 160 ) of the compressed air storage power plant ( 120 ) to a first gas inlet ( 101 ) a heat exchanger arrangement ( 100 ), Heating the working gas from the first input temperature (T _E1 ) to a first outlet temperature (T _A1 ) by means of a warming means, supplying the working gas with the first outlet temperature (T _A1 ) from the heat exchanger arrangement ( 100 ) to the turbine ( 130 ), Supplying the working gas with a second input temperature (T _E2 ) from the turbine ( 130 ) to a second gas inlet ( 102 ) of the heat exchanger arrangement ( 100 ), Heating the working gas from the second input temperature (T _E2 ) to a second outlet temperature (T _A2 ) by means of the warming means, and supplying the working gas with the second outlet temperature (T _A2 ) from the heat exchanger arrangement ( 100 ) to the turbine ( 130 ).

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