DE102010034231A1 - Method for recovering energy from effluent stream of e.g. petrol engine of motor car, involves guiding working medium to turbine in closed joule cyclic process, and arranging cooler between turbine and compressor - Google Patents

Abstract

The method involves supplying effluent stream (AG) to a heat exchanger (3) e.g. waste-gas heat exchanger, and supplying working medium e.g. helium, to the heat exchanger. An upstream compressor (4) is compressed in the heat exchanger and a downstream turbine (5) is unstressed in the heat exchanger. The working medium is guided from the heat exchanger to the turbine in a closed joule cyclic process (JK), and a cooler (6) is arranged between the turbine and the compressor. A lower pressure level is adjusted or held to a value over ambient pressure in the joule cyclic process. An independent claim is also included for a device for recovering energy from an effluent stream of an internal combustion engine.

Description

The invention relates to a method and a device for recovering energy from an exhaust gas stream of an internal combustion engine according to the preamble of claims 1 and 6, respectively.

Known techniques for generating energy from the exhaust stream of an internal combustion engine are the exhaust gas turbocharger and the heating systems for motor vehicles. In the exhaust gas turbocharger, the exhaust gas flow drives a turbine. The energy that the turbine supplies uses a compressor to compress the air supplied to the engine. The compression of the air increases the efficiency of the combustion and thus leads to a performance increase of the engine.

Alternatively, the internal combustion engine is followed by a cycle in which the hot exhaust gas flow and partly the coolant of a first internal combustion engine is used as a heat source for operating a second, downstream machine in the cycle. The cyclic process is usually a so-called Clausius-Rankine process, in which a liquid medium absorbs heat, which is predominantly evaporated with the supply of heat and then expanded in an expansion machine with release of mechanical energy to an output shaft. As a working medium come here organic agents, a mixture of such organic agents, alcohol mixtures or water-alcohol mixtures, water with certain additives into consideration.

Some work equipment for the downstream circuit, especially organic work equipment, are not suitable for arbitrarily high temperatures, as they z. B. become unstable and chemically disintegrate. This does not allow the use of this work equipment for appropriate temperatures, as z. B. occur when using exhaust heat. If the exhaust gas can not be used at a high temperature, this results in a correspondingly reduced efficiency of the downstream cycle process. Furthermore, these organic working materials can have harmful environmental effects when released. One possibility is the use of water in a downstream Rankine cycle. Pure water has the disadvantage that it freezes at minus temperatures and the water therefore additives must be added to prevent this. The content of these additives must then be checked again and corrected accordingly, resulting in a correspondingly high maintenance. Furthermore, there is the problem that the composition of the water and the additives used by their different properties (different boiling temperatures) different volatilize and change, which can affect the overall behavior of the working medium of the downstream Rankine cycle. Another problem arises from the fact that the volume of water in the evaporation increases very sharply, which ultimately leads to very large flow rates and thus large flow cross sections and a very large space requirement for the downstream Rankine cycle with water as the working fluid, which is particularly at the use in vehicles is disadvantageous.

Furthermore, the waste heat recovery units known from the general state of the art are in part relatively complex and complex in terms of their construction, which leads to a high space requirement and high complexity combined with high costs.

From the DE 199 60 762 A1 and the EP 1 408 224 A1 Devices are known in which a gas turbine process with a heat exchanger that uses the exhaust heat as an energy source, the internal combustion engine is connected downstream. The heat exchanger draws energy from the primary side supplied exhaust gas stream of the internal combustion engine in the form of heat, which is supplied to the secondary side guided working fluid in an open gas turbine system.

The invention has for its object to provide a method and apparatus for recovering energy from the exhaust stream of an internal combustion engine, in which the energy recovery is increased as compact as possible space of the device.

With regard to the method, the object is achieved by the features specified in claim 1. With regard to the device, the object is achieved by the features specified in claim 6.

Advantageous developments of the invention are the subject of the dependent claims.

In a method for recovering energy from the exhaust gas flow of an internal combustion engine, the exhaust gas flow is supplied to the primary side a heat exchanger to the secondary side, a working medium is supplied, which is compressed in a heat exchanger upstream compressor and expanded in a turbine downstream of the heat exchanger.

According to the invention, the working medium is guided on the secondary side in a closed Joule cycle, which consists of the heat exchanger, the turbine, one between the turbine and the Compressor arranged cooler and the compressor is formed. Instead of the turbine, another turbomachine can also be used.

The invention improves the energy recovery from the exhaust gas flow of internal combustion engines by a closed Joule cycle process is connected on the exhaust side of the internal combustion engine, in which the working fluid absorbs the heat energy from the exhaust gas flow, and it is heated and accelerated, so that high heat transfer capacities are possible. In this case, the heat exchanger replaces the known from an open gas turbine or Joule cycle combustion chamber in which heat energy is usually supplied to the compressed working medium. An energy recovery carried out in this way has a higher efficiency compared to conventional internal combustion engines. In addition, fuel savings are achieved and the costs are significantly reduced due to the compact design.

In a further development of the invention, the working medium is guided in a single-stage Joule cycle, wherein in the Joule cycle a lower pressure level is set or maintained at a value above the ambient pressure. In this case, the lower pressure level according to the invention refers to the set after the turbine and before the compressor pressure level. Due to the fact that the lower pressure level of the Joule cycle process is above, in particular clearly above the ambient pressure, relatively high mass flows can be moved in relation to corresponding volume flows within the cycle. For example, a lower pressure level greater than 2 bar, in particular in the range of greater than 5 bar, typically from 8 to 12 bar. It is also possible to set a range greater than 12 bar. In principle, the highest possible pressure level should be sought in order to increase the power density as much as possible. As a result, relatively small installation spaces, in particular pipe cross-sections, at the same time high mass flow through the device for energy recovery or within the closed Joule cycle process and thus relatively high power densities possible. Furthermore, the use of a high lower pressure level in the Joule cycle relatively high heat transfer capacities in the heat exchangers, such as the heat exchanger and the radiator of the subsequent Joule cycle process allows, resulting in a correspondingly reduced need for heat exchanger surfaces and thus the necessary installation space of the radiator and of the heat exchanger leads.

Preferably, the working fluid in the turbine is expanded to the lower pressure level. This allows easy adjustment and maintenance of the lower pressure level to a high value, in particular to a value above the ambient pressure. In addition, this allows a high mass flow and throughput of the working fluid through the components of the Joule cycle, in particular through the heat exchanger (also called exhaust gas heat exchanger), the radiator (also called waste heat exchanger), the compressor and the turbine with low space requirement.

Appropriately, the working fluid is compressed in the compressor to an upper pressure level.

Preferably, an inert, non-combustible medium, in particular a gas, such as helium, carbon dioxide, or a non-inert medium, in particular dry air, is used as the working medium. Such a medium allows high compression and has a high heat capacity.

The device for recovering energy from an exhaust gas stream of an internal combustion engine comprises an exhaust line which ends on the exhaust side of the internal combustion engine in a heat exchanger on the primary side upstream of a compressor for compressing a working medium flowing through the heat exchanger and a turbine for relaxation of the working medium is connected downstream. According to the invention, a cooler is arranged between the output side of the turbine and the input side of the compressor such that a closed joule cycle formed by the heat exchanger, the turbine, the cooler and the compressor is connected downstream from the internal combustion engine. By downstream of such a closed Joule cycle process abgasseitig the internal combustion engine, the efficiency of the entire unit (ie internal combustion engine and apparatus for energy recovery) can be increased.

Preferably, the Joule cycle is performed as a one-step Joule cycle, wherein in the Joule cycle, a lower pressure level is set to a value above the ambient pressure. By setting a high lower pressure level above the ambient pressure relatively high heat transfer capacities in the heat exchangers of the closed Joule cycle process or high power densities of the turbine and the compressor, so practically allows the entire closed Joule cycle.

In one embodiment of the invention, a recuperator is provided, which is connected on the primary side between the outlet of the turbine and the inlet of the cooler and the secondary side between the outlet of the compressor and the inlet of the heat exchanger. Such, realized within the closed Joule cycle process further Heat transfer allows an increase in the efficiency of the device and the entire aggregate, in particular the drive train. Since the pressure level of the working medium at the lower pressure level, ie after the turbine and before the compressor and thus in the recuperator, is set significantly above the ambient pressure, high heat transfer capacities are also made possible with the recuperator, whereby a high power density and a low space requirement are achieved ,

In a further advantageous development of the invention, the working medium emerging from the cooler can be fed to a generator for its cooling. In other words, the working medium can be fed to the generator for cooling after the re-cooling and thus at the coldest point in the closed joule cycle. This eliminates a separate cooling of the generator, whereby a simple structure, small space, low weight and low cost of the waste heat recovery device are ensured.

Preferably, a generator is arranged in front of the compressor and the turbine on a common shaft with these. Such a generator-compressor-turbine arrangement prevents unwanted heat transfer between the individual components and thus heat losses. In addition, the arrangement is a simple construction. Alternatively, the generator may be disposed between the compressor and the turbine on a common shaft therewith.

Embodiments of the invention will be explained in more detail with reference to drawings.

Showing:

1 1 schematically shows an embodiment of a device for recovering energy from an exhaust gas stream of an internal combustion engine, with a closed Joule cycle process downstream from the internal combustion engine on the exhaust side,

2 1 schematically shows an alternative embodiment of a device for recovering energy from an exhaust gas stream of an internal combustion engine having a closed Joule cycle process with an integrated recuperator connected downstream of the internal combustion engine,

3 1 schematically shows a further alternative embodiment of a device for recovering energy from an exhaust gas stream of an internal combustion engine having a closed Joule cycle process with integrated recuperator downstream of the internal combustion engine and a generator cooled by means of the working medium cooled in the Joule cycle;

4 1 schematically shows a further alternative embodiment for a device for energy recovery from an exhaust gas stream of an internal combustion engine with a closed Joule cycle process connected downstream of the internal combustion engine with a generator-compressor-turbine arrangement on a common shaft,

5 1 schematically shows an alternative embodiment of a device for energy recovery from an exhaust gas stream of an internal combustion engine having a closed-loop Joule cycle process with a two-part cooler connected downstream of the internal combustion engine,

6 schematically an alternative embodiment of a device for energy recovery from an exhaust stream of an internal combustion engine with an exhaust side of the engine downstream closed Joule cycle with air as the working medium from the compressed air supply arrangement of a commercial vehicle and

7 schematically the alternative embodiment of a device for energy recovery from an exhaust stream of an internal combustion engine with a downstream exhaust gas from the engine closed Joule cycle with air as the working medium from the compressed air supply arrangement of a commercial vehicle according to 6 and with a compressor for compressing the air.

Corresponding reference numerals are provided with the same reference numerals in all figures.

1 shows a device 1 for energy recovery from the exhaust gas flow AG of an internal combustion engine 2 , In the internal combustion engine 2 it may be a diesel or gasoline engine or other combustion engine z. B. a vehicle, in particular a motor vehicle or commercial vehicle. 1 shows a 4-cylinder internal combustion engine.

According to the invention is the exhaust side of the engine 2 a closed Joule cycle JK downstream.

The Joule cycle JK is a thermodynamic cycle, according to physicist James Prescott Joule. The closed Joule cycle JK comprises a heat exchanger 3 , The primary side is flowed through by the exhaust stream AG and the secondary side is flowed through by a working medium AM of the Joule cycle JK. The heat exchanger 3 is also referred to as exhaust gas heat exchanger.

On the primary side, an exhaust pipe L1 opens into the heat exchanger 3 and starts from this again.

Secondary side is the heat exchanger 3 in the Joule cycle JK on the input side a compressor 4 upstream. On the output side is the heat exchanger 3 in Joule cycle JK a turbine 5 downstream. Between the turbine 5 and the compressor 4 is a cooler in the closed joule cycle JK 6 , in particular a recooler or gas cooler arranged. The compressor 4 and the turbine 5 are with the interposition of a generator 7 with this on a common wave 8th arranged. Instead of the turbine 5 It is also possible to use another turbomachine.

The invention is that the internal combustion engine 2 no so-called Rankine process is followed, but the closed Joule cycle JK, ie a closed gas turbine process.

In this case, the lower pressure level of the working medium AM is set or maintained in the downstream, closed Joule cycle JK significantly above the ambient or atmospheric pressure. For example, the lower pressure level of the working medium AM is at least 2 bar, in particular it is greater than 5 bar, typically 8 to 12 bar or greater.

The preferably used within the closed Joule cycle JK working medium AM (also called working gas or working fluid) is an inert, non-combustible gas, which at z. B. room temperature is gaseous. As a working medium AM, for example, a gas such as helium or carbon dioxide is used. Alternatively, as a non-inert gas z. As dry air can be used. These gases are characterized by the fact that they are chemically stable and can be exposed to very high exhaust gas temperatures without them decaying.

The hot exhaust gas flow AG of the internal combustion engine 2 is used to heat the Joule cycle JK downstream (especially the closed gas turbine process). This is particularly advantageous because especially the hot exhaust gases from an energetic and thermodynamic point of view have a temperature level that is capable of working and thus can lead to a relatively high overall efficiency. This is also advantageous from the point of view of construction costs with less space requirement, lower costs, lower weight, since the expense for the downstream Joule cycle JK is indeed present, but by using the high and thus thermodynamically working temperature levels to a relatively high efficiency gain in comparison for non-use of the temperature level of the exhaust stream AG leads.

Because the lower pressure level of the Joule cycle JK is significantly above the ambient pressure, relatively high mass flows can be moved in relation to the corresponding volume flows within the Joule cycle JK, resulting in relatively small installation spaces (eg pipeline cross sections) at the same time high mass flow through the components, ie through the turbine 5 and the compressor 4 , and thus leads to relatively high power densities. Furthermore, the use of a high lower pressure level in the Joule cycle JK also allows relatively high heat transfer rates in the individual heat exchangers, such as the heat exchanger 3 and the radiator 6 , realize the downstream Joule cycle JK.

Moreover, there is no danger of so-called freezing when using an inert gas such as carbon dioxide or helium or when using dry air, as opposed to water.

In operation of the device 1 be in the heat exchanger 3 on the primary side, ie on the heat-emitting side, the very hot engine exhaust gases, ie the exhaust gas flow AG of the internal combustion engine 2 guided. Secondary, ie on the heat receiving side, of the heat exchanger 3 flows the highly compressed working fluid AM of the downstream Joule cycle JK.

The working medium AM (eg helium or CO ₂ ) is hereby passed through the compressor 4 raised to an upper pressure level. In the heat exchanger 3 the heat energy of the hot exhaust gas stream AG is transferred to the compressed working medium AM. The compressed and highly heated working medium AM becomes the turbine 5 , an expansion machine, fed and expanded there and in mechanical work on the shaft 8th the turbine 5 is released. The on the shaft 8th the turbine 5 Unlocking work / energy is used to drive the compressor 4 and second, the drive of the generator 7 , which converts mechanical energy into electrical energy used to drive aggregates, caching or propulsion of the internal combustion engine 2 can serve.

After the expansion of the working medium AM in the turbine 5 becomes the working medium AM in the radiator 6 (Recooler, gas cooler) recooled and turn the compressor 4 fed. The cooler 6 In this case, air can be directly flowed through and thus cooled or connected to a corresponding cooling circuit.

In the compressor 4 the working medium AM is compressed from the lower to the upper pressure level and then to the heat exchanger 3 supplied, in which the working medium AM absorbs the heat energy of the hot exhaust gas flow AG.

The working medium AM is in the turbine 5 expanded to a pressure level which is well above the ambient pressure. This allows a high mass flow rate of the working medium AM through the device 1 with low space requirement. Furthermore, the high gas density within the heat exchanger (heat exchanger 3 and coolers 6 ) to high heat transfer performance, resulting in low space of the individual heat exchanger.

2 shows one to 1 very similar construction of the device 1 , but with the difference that here also a recuperator 9 is provided, whose primary side between the outlet of the turbine 5 and the entrance to the radiator 6 and its secondary side between the outlet of the compressor 4 and the inlet of the heat exchanger 3 are arranged.

This process management with the recuperator integrated in the closed joule cycle JK 9 for "internal" heat transfer has an increased efficiency of the device 1 and thus the waste heat recovery device and thus an increased efficiency of the entire drive unit (ie internal combustion engine 2 and device 1 for energy recovery or waste heat recovery device).

That expanded, out of the turbine 5 emerging working medium AM becomes the recuperator 9 supplied in which in the working medium AM after the expansion still contained residual heat to that through the compressor 4 compressed working medium AM before entering the heat exchanger 3 is at least partially transmitted. The fact that the pressure level of the working medium AM at the lower pressure level (ie after the turbine and before the compressor) is set to a pressure level that is significantly above the ambient pressure, can be at the recuperator 9 realize high heat transfer performance, which in turn leads to a high power density and a low space requirement of the device 1 for energy recovery or waste heat recovery device leads.

3 shows a further alternative embodiment of the device 1 according to 2 , Unlike the device 1 to 2 is the working medium AM after the re-cooling in the radiator 6 (and thus practically at the coldest point in the Joule cycle JK) and before entering the compressor 4 so guided that it is in the range of the electric generator 7 or be guided by it to cool it. This is for the cooling of the generator 7 no separate cooling more necessary, resulting in an overall relatively simple construction, small space, low weight and low cost of the device 1 leads.

4 shows a further alternative embodiment of the invention. In contrast to the structure of the device 1 according to 3 are the generator 7 , the turbine 5 and the compressor 4 in a different order on the common shaft 8th arranged. According to 3 is the generator 7 between the compressor 4 and the turbine 5 arranged. According to 4 is the generator 7 in front of the compressor 4 and the turbine 5 on the wave 8th arranged. That is, the arrangement of generator 7 , Compressor 4 and turbine 5 is preferably chosen so that the individual components (generator 7 , Compressor 4 and turbine 5 ) according to the temperature level occurring at or in the single component on the common shaft 8th are arranged.

This means: the generator 7 with the lowest temperature level before the compressor 4 with a medium temperature level and the turbine 5 with the highest temperature level on the shaft 8th arranged. This arrangement prevents thermal stresses within the engine assembly of the generator-compressor turbine. Thus, unfavorable heat transfer from the individual components to each other and heat losses are avoided.

By such an arrangement, the machine arrangement of generator-compressor turbine can be interpreted relatively easily or the construction can be relatively simple design and execute, since no special measures to prevent z. B. thermoelectric and heat losses within this machine assembly generator-compressor turbine must be taken. Thus, in this arrangement, the lengthening expansions resulting from the heating can be controlled relatively easily, without having to carry out any special design effort.

The dash-dot-dot line around the generator 7 , the compressor 4 and the turbine 5 shows that the machine assembly of generator-compressor turbine in hermetic construction is executed, which is particularly important from the viewpoint of tightness of particular importance. This means that from the hermetic unit in which the generator 7 , the compressor 4 and the turbine 5 are arranged, practically only the electrical lines of the generator 7 led out and appropriate connections for the piping to the heat exchanger 3 , Recuperator 9 or cooler 6 and back are present. This allows a optimum sealing of the engine assembly of generator-compressor turbine, so that the leakage losses of the working medium AM can be minimized.

In the 5 is additionally a cooling circuit KK (dashed line) with a pump 10 , z. B. a coolant pump, the engine 2 shown. By means of the coolant KM guided in the cooling circuit KK, the working medium AM of the Joule cycle JK is additionally cooled. This is the cooler 6 formed as a recooler, which is flowed through in countercurrent flow both by the coolant KM of the cooling circuit KK and by the working medium AM of the Joule cycle JK.

In the 5 arrangement shown allows the cooling circuit KK of the internal combustion engine 2 to warm up relatively quickly (by the recooling of the working medium AM of the waste heat recovery device), which is the warm-up phase of the internal combustion engine 2 shortened and thus leads to reduced consumption and reduced pollutant emissions in this operating range.

About the speed of the pump 10 and about the position of valves 11 and 12 in the cooling circuit KK of the internal combustion engine 2 can be the proportion of coolant KM, which via the recooler 6 to flow and which via a arranged in the cooling circuit KK main radiator 13 flow, adjust. So z. B. in the warm-up phase of the engine 2 the valves 11 . 12 and the pump 10 the cooling circuit KK be set so that a high proportion of the coolant KM through the radiator designed as a cooler 6 flows. In this case, the coolant KM takes a high proportion of the residual heat of the working medium AM of the device 1 for energy recovery or exhaust heat recovery device, which ultimately from the exhaust gases of the internal combustion engine 2 comes. The main cooler 13 is bypassed, so that the coolant KM is circulated and heated only in a "small" cooling circuit during the warm-up phase. This heats the exhaust stream AG of the internal combustion engine 2 the cooling circuit KK of the internal combustion engine 2 and thus the internal combustion engine 2 itself quickly, which leads to the above advantages.

The arrows P1 show the course of the coolant KM in the warm-up phase (arrow P1 - solid line) and during normal operation (arrow P2 - dashed line).

6 schematically shows an alternative embodiment for the device 1 , It is used in the Joule cycle JK air L, especially dried air as the working medium AM, for example, from a compressed air supply arrangement 14 with an air compressor 15 and a memory 16 of a commercial vehicle, not shown, the Joule cycle JK after the radiator 6 and in front of the compressor 4 is supplied. To adjust the supply of air L is another valve 17 intended.

7 shows an alternative embodiment for the device 1 according to 6 with an additional compressor 18 for the compression of the air L. That is, already in the compressed air supply arrangement 14 compressed air L is a further, small and rarely operated auxiliary compressor 18 , in particular a compressor, raised to a higher pressure level. The valve 17 may be formed as a check valve to set or maintain the Joule cycle JK to a correspondingly high pressure level. As a result, any leakage losses occurring in the closed Joule cycle JK can be compensated.

LIST OF REFERENCE NUMBERS

1

Apparatus for energy recovery

2

internal combustion engine

3

heat exchangers

4

compressor

5

turbine

6

cooler

7

generator

8th

wave

9

recuperator

10

pump

11

Valve

12

Valve

13

main cooler

14

Compressed air supply arrangement

15

air compressor

16

Storage

17

Valve

18

auxiliary compressor

AG

exhaust gas flow

AT THE

working medium

JK

Brayton cycle

KK

Cooling circuit

KM

coolant

L

air

L1

exhaust pipe

P1

arrow

P2

arrow

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 19960762 A1 [0006]
• EP 1408224 A1 [0006]

Claims (10)

Method for recovering energy from an exhaust gas flow (AG) of an internal combustion engine ( 2 ), wherein the exhaust gas stream (AG) on the primary side a heat exchanger ( 3 ) is supplied to the secondary side, a working medium (AM) is supplied, which in a heat exchanger ( 3 ) upstream compressor ( 4 ) and in a heat exchanger ( 3 ) downstream turbine ( 5 ) is relaxed, characterized in that the working medium (AM) is guided in a closed Joule cycle (JK), which from the heat exchanger ( 3 ), the turbine ( 5 ), one between the turbine ( 5 ) and the compressor ( 4 ) arranged cooler ( 6 ) and the compressor ( 4 ) is formed. A method according to claim 1, characterized in that the working medium (AM) is guided in a single-stage Joule cycle (JK), wherein in the Joule cycle (JK), a lower pressure level is set or maintained at a value above the ambient pressure. A method according to claim 2, characterized in that the working medium (AM) in the turbine ( 5 ) is expanded to the lower, pressure level. Method according to one of the preceding claims, characterized in that the working medium (AM) in the compressor ( 4 ) is compressed to an upper pressure level. Method according to one of the preceding claims, characterized in that the working medium (AM) is an inert, non-combustible medium, in particular a gas, such as helium, carbon dioxide or dried air is used. Contraption ( 1 ) for energy recovery from an exhaust gas stream (AG) of an internal combustion engine ( 2 ), with the exhaust side of the internal combustion engine ( 2 ) an exhaust pipe (L1) on the primary side in a heat exchanger ( 3 ), the secondary side a compressor ( 4 ) for the compression of a heat exchanger ( 3 ) flowing through working medium (AM) upstream and a turbine ( 5 ) for the relaxation of the working medium (AM), characterized in that between the output side of the turbine ( 5 ) and the input side of the compressor ( 4 ) a cooler ( 6 ) is arranged such that the exhaust side of the internal combustion engine ( 2 ) one from the heat exchanger ( 3 ), the turbine ( 5 ), the cooler ( 6 ) and the compressor ( 4 ) is formed downstream, closed Joule cycle (JK). Apparatus according to claim 6, characterized in that the Joule cycle (JK) is designed as a single-stage Joule cycle, wherein in the Joule cycle (JK), a lower pressure level is set to a value above the ambient pressure. Apparatus according to claim 6 or 7, characterized in that a recuperator ( 9 ) is provided, the primary side between the outlet of the turbine ( 5 ) and the entry of the cooler ( 6 ) and on the secondary side between the outlet of the compressor ( 4 ) and the inlet of the heat exchanger ( 3 ) is switched. Device according to one of the preceding claims 6 to 8, characterized in that the from the cooler ( 6 ) leaving working medium (AM) a generator ( 7 ) can be supplied to its cooling. Device according to one of the preceding claims 6 to 9, characterized in that a generator ( 7 ) between the compressor ( 4 ) and the turbine ( 5 ) or in front of the compressor ( 4 ) and the turbine ( 5 ) on a common wave ( 8th ) is arranged with these.

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