EP2183529B1 - Method for converting thermal energy at a low temperature into thermal energy at a relatively high temperature by means of mechanical energy, and vice versa - Google Patents

Description

• reversible adiabate Verdichtung des Arbeitsmediums,
• isobare Wärmeabfuhr vom Arbeitsmedium,
• reversible adiabate Entspannung des Arbeitsmediums,
• isobare Wärmezufuhr zum Arbeitsmedium,

wobei zur Druckerhöhung bzw. -verringerung des Arbeitsmediums während der Verdichtung bzw. Entspannung das Arbeitsmedium in Bezug auf eine Drehachse im Wesentlichen radial nach außen bzw. nach innen geführt wird, wodurch eine Erhöhung bzw. Verringerung der auf das Arbeitsmedium wirkenden Zentrifugalkraft erzeugt wird.The invention relates to a method for converting low-temperature thermal energy into higher-temperature thermal energy by means of mechanical energy and vice versa, ie the conversion of high-temperature thermal energy to low-temperature thermal energy on delivery of mechanical energy, with a working medium undergoing a closed thermodynamic cycle , wherein the cycle process comprises the following steps:

• reversible adiabatic compression of the working medium,
• isobaric heat dissipation from the working medium,
• reversible adiabatic relaxation of the working medium,
• isobaric heat supply to the working medium,

wherein for increasing or decreasing the pressure of the working fluid during compression or expansion, the working fluid is guided radially in relation to an axis of rotation substantially radially inwards or inwards, whereby an increase or reduction of the force acting on the working medium centrifugal force is generated.

Furthermore, the invention relates to a device for carrying out a method according to the invention with a compressor, a relaxation unit and in each case a heat exchanger for heat supply or heat dissipation, wherein the compressor and the expansion unit are rotatably mounted about an axis of rotation and the compressor or the expansion unit are configured such in that the working medium in the compressor is guided essentially radially outwardly with respect to the axis of rotation or substantially radially inward in the expansion unit, so that an increase or decrease in pressure is produced by increasing or decreasing the centrifugal force acting on the working medium ,

Various devices, so-called heat pumps are known from the prior art, in which usually with the help of an engine, a working medium of low temperature is heated to higher temperature by increasing the pressure. In known heat pumps, the working medium is conducted in a thermodynamic cycle, wherein this thermodynamic cycle vaporizing, compressing, liquefying and expanding at a throttle of the working medium comprises; ie usually the physical state of the working medium changes.

In known heat pumps, the refrigerant R134a or a mixture consisting inter alia of R134a is used, which, although having no ozon destroying effect, however, has a 1300 times higher greenhouse-forming effect than the same amount of CO ₂ . Such processes, which are carried out essentially according to the Carnot process, have a theoretical coefficient of performance or COP (Coefficient of Performance), ie a ratio of the heat given off to the electrical energy used of approximately 5.5 (when "pumping" the working medium from 0 to 35 ° C). In practice, however, at best a performance factor of 4.9 has been achieved; As a rule, today's good heat pumps achieve a coefficient of performance of approx. 4.7.

From the DE 27 29 134 A1 a device is known with a hollow-shaped rotor, wherein here guide passages or guide vanes are provided, which are arranged on the outer circumference of the rotating body and consequently a high relative speed between the Leitdurchlässen and the working medium occurs. By such vanes also occur very high losses of the flow energy, which leads to a relatively low coefficient of performance.

In the DE 30 18756 A1 is disclosed for performing a thermodynamic cycle as ideal as possible to expose a gaseous working fluid to a strong centrifugal force field. The method shown is based on a Carnot cycle. Expansion of the gas is effected by passing the gas against the direction of centrifugal force; in an analogous manner, the gas is compressed as the gas flows in the direction of the centrifugal force. The heat supply or heat dissipation via heat exchangers.

In the DE 22 27 189 A1 Another thermodynamic method is described which makes use of the centrifugal force. A runner rotatable about a shaft has a compression channel or an expansion channel and a connecting channel, wherein a compression or expansion of a gaseous working medium is effected via the centrifugal action.

In the US 2 393 338 A is a so-called "Roebuck method" described, which is based on an open thermodynamic process.

From the article "Modified Roebuck compression device for cryogenic refrigeration system of superconducting rotating machine" by Jeong et al. Another compressor is known, which exploits the centrifugal effect on a rotating gas for compression or expansion of a gas.

From the WO 1998/30846 A1 a device is known which can be used as a chiller or as a motor, in which case air is used as a working medium and this is sucked in from the environment and discharged to a compression or relaxation back to the environment. In such an open system disadvantageously, when the working medium enters the machine, an angular momentum is built up and when the working medium exits the machine, angular momentum is reduced so that considerable friction losses occur.

From the FR 2 749 070 A1 is merely a different heat pump with a conventional turbo compressor or with a toothed displacer known.

Moreover, from the GB 1 217 882 A Although a thermodynamic device is known, which basically makes use of the centrifugal force, but here also a throttle point is provided, so that considerable friction losses occur.

On the other hand, in the prior art, numerous methods are known, in which in particular the heat from geothermal liquid and geothermal steam is converted into electrical energy. In the so-called KALINA process, the heat is transferred from water to an ammonia-water mixture, so that even at significantly lower temperatures, steam is generated, which is used to drive turbines. Such a KALINA process is for example in the US 4,489,563 described.

In a variety of heat exchange methods theoretically the achievement of very high performance figures is possible, but usually have conventional compressors and expansion units in which the working medium in the gaseous region is compressed or relaxed, a relatively poor efficiency.

Accordingly, the object of the present invention is to improve the efficiency or the coefficient of performance in the conversion of low-temperature thermal energy into higher-temperature thermal energy by means of mechanical energy and vice versa.

This is inventively achieved in that the working medium during the closed cycle and the heat exchange media for heat supply and removal are passed around the axis of rotation, so that the flow energy of the working medium is maintained during the closed cycle process substantially. By utilizing the centrifugal acceleration and maintaining the flow energy of the working medium, a significantly higher efficiency is achieved compared to conventional compressors, in which the high velocity of the working medium is converted into pressure on the circumference of the compressor and thus a poor efficiency is achieved. Also, the efficiency of relaxation is increased when the pressure reduction of the working medium during relaxation is achieved by a reduction in the centrifugal force. As a result, the coefficient of performance and the efficiency of the entire process is substantially improved.

Furthermore, it is to improve the efficiency of advantage, when the working fluid is gaseous throughout the cyclic process, as in the expansion of the gaseous working medium can be recovered energetically useful work, which is energetically not relevant to liquid media. In addition, the influence on the efficiency in the gaseous range is greater than in the 2-phase range.

Concerning high compression by means of centrifugal acceleration it is advantageous to use gases with low specific heat capacity at constant pressure (cp) or high density. Accordingly, a noble gas, in particular krypton, xenon, argon, or radon or a mixture thereof is preferably used as the working medium. Furthermore, it has been found that it is favorable if the pressure in the closed cycle is at least 50 bar, in particular more than 70 bar, preferably substantially 100 bar, ie the pressure during the entire process is comparatively high. Due to the comparatively high pressure, the pressure loss in the heat exchanger can be kept low because the heat transfer at comparatively low flow rates is relatively high.

If the cyclic process is carried out in the vicinity of the critical point of the gaseous working medium, there results a further improvement in the overall efficiency or an increase in the coefficient of performance, the critical point being present at different pressure or temperature, depending on the working medium used. The total power efficiency is maximized by performing the relaxation in an entropy range which is as close as possible to the entropy of the respective critical point. Furthermore, it is advantageous if the lower relaxation temperature is just above the critical point. The critical point can be adjusted by gas mixtures to the desired process temperature.

A structurally simple and efficient cooling or heating of the working medium is given when a heat exchange medium with an isentropic exponent Kappa ~1, i. Such media in which at a pressure increase, the temperature remains substantially constant, in particular a liquid heat exchange medium, is used.

In the apparatus for carrying out the method according to the invention, the heat exchangers with the compressor and the expansion unit, in which the working medium is passed around the axis of rotation during the closed cycle process, are formed co-rotating, so that the flow energy of the working medium is essentially maintained during the closed loop process. As a result, as already described above in connection with the method according to the invention, a significant improvement in the efficiency in the compression and expansion of the working medium is achieved and thus significantly improves the coefficient of performance or the efficiency of the device according to the invention over known devices.

With regard to a structurally simple embodiment of the heat exchanger, it is advantageous if the heat exchangers each have at least one tube through which a liquid heat transfer medium flows.

With regard to the smoothest possible transition from the compressor to the expansion unit, i. In order to maintain the flow energy of the working medium, it is advantageous if the expansion unit connects directly to the compressor via the heat exchanger. With regard to a structurally simple embodiment of the device, it is advantageous if the wheels of the compressor and the expansion unit are mounted on a common rotary shaft.

In a structurally simple manner, the pressure increase of the working medium can be achieved via a centrifugal acceleration when a mitdrehendes with impellers of the compressor and the expansion unit housing is provided.

In order to achieve efficient cooling of the compressed working medium, it is advantageous if a co-rotating heat exchanger is accommodated in the housing. Advantageously, the co-rotating heat exchanger is circumferentially arranged outside.

However, instead of a co-rotating with the wheels housing, it is also conceivable that the wheels are surrounded by a stationary housing. As a result, the design effort can be reduced. However, friction losses of the working medium at one connected to the stationary housing Pipe of the heat exchanger to avoid, it is advantageous if the tube of the heat exchanger is partially received in the housing, wherein the surface of the stationary housing, with which the working medium comes into contact, is formed as smooth as possible.

In order to avoid external, rotating parts, it is favorable if a housing surrounding the compressor and the expansion unit is provided in a rotationally fixed manner.

In order to achieve efficient heat supply to the working medium, it is advantageous if the two heat exchangers are accommodated in the housing.

If at least one of the working medium in a circle leading, rotatably mounted piping system is provided, a device results in a comparatively low overall weight, since the wall thickness of the working medium leading tubes can be made smaller than those of the working medium receiving housings.

With regard to the compression of the working medium in the pipeline system by means of the centrifugal force, it is advantageous if the pipeline system has linear compression tubes extending in the radial direction.

In order to reliably guide the working medium in the pipeline system in a circle, it is advantageous if the pipeline system has curved expansion tubes against the direction of rotation of the rotary shaft. Here, the expansion tubes can be arcuately curved in cross section for the purpose of a structurally simple design. Alternatively, it is also possible for the expansion tubes to have a curvature in cross-section with a radius that constantly reduces towards the center of rotation. This can reduce any turbulence in the piping system.

Likewise, a flow of the working medium in the piping system is reliably ensured if, in the piping system, a blade wheel rotating relative to the piping system is included. Here, the paddle wheel, which is designed as a compressor, expansion turbine or stator, be rotatably disposed, resulting in a relative movement to the rotating piping system due to the rotationally fixed arrangement. It is also conceivable that, for example, the impeller is associated with a motor for generating or using a relative movement to the piping system or a generator which converts the shaft power generated by the relative movement of the impeller into electrical energy.

With regard to a simple and efficient heat supply and removal, it is advantageous if axially extending portions of the piping system are surrounded by coaxially arranged tubes of the heat exchanger.

In order to supply the difference between the necessary energy from the compression and the recovered energy from the relaxation of the device in operation as a heat pump, it is advantageous if a motor is connected to the rotary shaft or the piping system.

In order to convert the mechanical energy obtained from different temperature levels into electrical energy, i. When the device is used as a heat engine, it is advantageous if a generator is connected to the rotary shaft.

• Fig. 1 schematisch ein Prozessblockschaltbild der erfindungsgemäßen Vorrichtung bzw. des erfindungsgemäßen Verfahrens beim Betrieb als Wärmepumpe;
• Fig. 2 eine Schnittansicht einer erfindungsgemäßen Vorrichtung mit einem mitdrehenden Gehäuse;
• Fig. 3 eine Schnittansicht einer erfindungsgemäßen Vorrichtung mit einem stillstehenden Gehäuse;
• Fig. 4 eine Schnittansicht ähnlich Fig. 3 jedoch mit einem im Inneren aufgenommenen Motor;
• Fig. 5 eine Schnittansicht eines weiteren Ausführungsbeispiels mit Rohrleitungen, in welchen das Arbeitsmedium geführt wird;
• Fig. 6 einen Schnitt gemäß der Linie VI-VI in Fig. 5;
• Fig. 7 einen Schnitt gemäß der Linie VII-VII in Fig. 5;
• Fig. 8 eine Schnittansicht eines weiteren Ausführungsbeispiels mit einem das Arbeitsmedium aufnehmenden Rohrleitungssystem;
• Fig. 9 eine perspektivische Ansicht der Vorrichtung gemäß Fig. 8;
• Fig. 10 eine Schnittansicht einer Vorrichtung ähnlich Fig. 5 jedoch mit einer stillstehenden Turbine; und
• Fig. 11 eine Schnittansicht ähnlich Fig. 10 jedoch mit einer relativ zum Rohrleitungssystem rotierenden Turbine.

The invention will be explained in more detail below with reference to preferred embodiments illustrated in the drawings, to which, however, it should not be restricted. Of course, combinations of the illustrated embodiments are possible. In detail, in the drawing:

• Fig. 1 schematically a process block diagram of the device according to the invention or the method according to the invention when operating as a heat pump;
• Fig. 2 a sectional view of a device according to the invention with a co-rotating housing;
• Fig. 3 a sectional view of a device according to the invention with a stationary housing;
• Fig. 4 a sectional view similar Fig. 3 however, with a motor housed inside;
• Fig. 5 a sectional view of another embodiment with pipes in which the working medium is guided;
• Fig. 6 a section along the line VI-VI in Fig. 5 ;
• Fig. 7 a section along the line VII-VII in Fig. 5 ;
• Fig. 8 a sectional view of another embodiment with a working fluid receiving piping system;
• Fig. 9 a perspective view of the device according to Fig. 8 ;
• Fig. 10 a sectional view of a device similar Fig. 5 however, with a stationary turbine; and
• Fig. 11 a sectional view similar Fig. 10 but with a relative to the pipeline system rotating turbine.

In Fig. 1 schematically a process block diagram of a thermodynamic cycle is shown, as this is basically known in the prior art. In the illustrated use as a heat pump, an isentropic compression of the gaseous working medium is initially carried out with the aid of a compressor 1. Subsequently, isobaric heat removal takes place via a heat exchanger 2, so that the thermal energy is delivered at high temperature via a circuit (with water, water / antifreeze or other liquid heat transfer media) to a heating circuit.

Subsequently, in a turbine formed relaxation unit 3 an isentropic relaxation is performed, whereby mechanical energy is recovered. Subsequently, an isobaric heat supply is performed via a further heat exchanger 4, whereby thermal energy of low temperature is supplied to the system via a circuit (with water, water / antifreeze, brine or other liquid heat transfer media). Typically, this thermal energy from well water, from so-called deep probes, in which the located in a heat exchanger located up to 200 m in the ground, the heat is removed and the heat pump is supplied or the thermal energy from just under the earth lying large heat exchangers (Piping) or taken from the air. After the isobaric heat supply, an isentropic compression is again effected with the aid of the compressors 1, as described above.

If the device according to the invention or the method according to the invention for converting higher-temperature thermal energy into low-temperature thermal energy is used, the cycle described above takes place in the reverse order. In the case of the operation as a heat pump, a motor 5 for driving a rotary shaft 5 'is provided; When operating as a heat engine, the engine is replaced by a generator 5 and motor generator 5.

In Fig. 2 a device according to the invention is shown in which by means of the motor 5 via the rotary shaft 5 ', a compressor 1 is driven with a co-rotating housing 6. With the driven by the electric motor 5 rotating shaft 5 'wheels 1' of the compressor 1 are also driven, so that in the closed, stationary housing 8 recorded noble gas, preferably krypton or xenon, is compressed due to the centrifugal acceleration in the co-rotating housing 6 ,

In the co-rotating housing 6, a spiral-shaped pipe 9 of the heat exchanger 2 is accommodated, in which a heat exchange medium, for example water, is accommodated. The comparatively cold water is introduced via an inlet 10 in the flow direction 10 'in the spiral pipe 9 and is circumferentially arranged in the co-rotating housing 6 to achieve isobaric heat removal from the working medium at the highest possible pressure of the working medium, so that at the output 11 a comparatively warm water can be removed.

The working medium then flows without significant flow losses to impellers 3 'of the expansion unit 3, via which mechanical energy is recovered. Subsequently, an isobaric heat supply takes place via a spiral-shaped pipe 12 of the further heat exchanger 4 in the stationary housing 8, before the working medium is again subjected to an adiabatic isentropic compression via the running wheels 1 'of the compressor 1.

However, it is only essential that the energy of the working medium, which is accommodated in the device forming a closed system, maintains its flow energy during compression in the compressor 1 and / or during expansion in the expansion unit 3 and only via a centrifugal acceleration of the gas molecules of the working medium an increase in pressure or reduction of the working medium is achieved. As a result, the efficiency or the coefficient of performance in the conversion of thermal energy of lower temperature into thermal energy of higher temperature by means of electrical or mechanical energy and vice versa can be substantially improved.

In Fig. 3 is shown a further embodiment, in which case a stationary inner housing 6 'is provided. As a result, the design complexity is simplified. In order to keep flow losses of the gaseous working medium low or to maintain the swirl of the working medium as possible, the stationary surfaces with which the working fluid is in communication, formed as smooth as possible and there are no transverse to the flow heat transfer tubes, which would further increase the pressure loss provided , Thus, the spiral-shaped pipe 9 of the heat exchanger 2 is not exposed, but received in the stationary housing 6 'with a smooth surface 2'. In order to increase the coefficient of performance or the efficiency of the overall device, an insulation 13 is accommodated in the interior of the stationary housing 6 '.

In Fig. 4 a further embodiment is shown, which is essentially that of Fig. 3 corresponds and only the arrangement of the motor 5 different; Namely, in this embodiment, the motor 5 is accommodated within the fixed housing 6.

In order to supply the motor 5 with power lines 14 are provided, which are guided by static pressure-resistant current feedthroughs 15 and a stationary motor shaft 16. The motor 5 is in this case connected to the compressor 1 or the expansion unit 3, so that they rotate together. As a result, advantageously dynamic seals (gas and liquid seals) can be omitted, and thus maintenance work can be reduced.

In the Fig. 5 to 7 a further embodiment of the device according to the invention is shown, in which case all under the pressure of the working fluid parts are formed as pipes or piping system 17, whereby the total weight of the device is reduced and the wall thickness of the tubes 17 may be made smaller than that of the in the Fig. 2 to 4 shown housing 6, 6 'and 8.

Here, the working fluid is first compressed in the radially extending compression tubes 18 of the piping system 17 of the compressor unit 1 due to the centrifugal acceleration. The heat exchanger 2 in this case has to the outer, extending in the axial direction portion of the tubes 17 coaxially arranged tubes 19 which enclose the respective tube 17, so that the heat of the compressed working medium is discharged in countercurrent to the liquid heat exchange medium of the heat exchanger 2.

Subsequently, the working medium is expanded in expansion tubes 20 (the expansion unit 3). The expansion tubes 20 are in this case curved counter to the direction of rotation 21 of the device, which due to the rearward tube curvature (see. Fig. 7 ) reliably results in a circulation of the working medium.

As in particular in Fig. 7 As can be seen, the expansion tubes 20 can be bent in a semicircular shape, so that they can be produced in a structurally simple manner. Subsequently, the working medium flows in the axial direction in the piping system 17, in which case the low-pressure heat exchanger 4 in turn has a coaxially arranged tube 19, so that heat from the liquid heat exchange medium to the cold, relaxed working medium is delivered.

As in particular in Fig. 7 it can be seen that thus result in 2 closed in plan view substantially aft loop-shaped piping systems 17 for the working medium, which are arranged offset by 90 ° to each other. Of course, the piping system 17 may also have a larger number of conduits 20, only the rotational symmetry of the arrangement is to be maintained due to the ease of balancing.

The coaxial with the axially extending portions of the tubes 17 arranged tubes 19 of the heat exchanger 2 and 4 are connected via lines 22, 23, 24, 25 fluidly connected to each other, said conduit system 22 to 25 is fixedly connected to the other device, so that the lines 22 to 25 are carried out co-rotating. The liquid heat transfer medium is supplied to the piping system 17 via an inlet 26 'of a static distributor 26; via a co-rotating manifold 27, the heat exchange medium is then supplied via the line 22 to the heat exchanger 2, in which it is heated by the line 23 in the co-rotating manifold 27 is recycled. The heated heat transfer medium is then fed to the heating circuit via the static distributor 26 or a drain 26 ".

The cold heat exchange medium of the heat exchanger 4 is passed via an inlet 28 'of a static distributor 28, conveyed with another co-rotating distributor 29 in this co-rotating line 25 to the low-pressure heat exchanger 4, where heat is released to the gaseous working medium. Subsequently, the heat exchange medium is supplied via the co-rotating line 25 to the co-rotating distributor 29 then the static manifold 28, and finally leaves via a drain 28 '' the device.

For driving compressor 1, heat exchanger 2, 4 and relaxation unit 3, in turn, a motor 5 is provided.

In FIGS. 8 and 9 is an embodiment similar to that of FIGS. 5 to 7 shown, but here are the expansion tubes 20 are not circular arc-shaped in cross-section, but have a continuously decreasing radius to the rotation axis center 30. As a result, a monotonically decreasing delayed movement of the working medium is achieved, whereby any turbulence can be reduced. In addition, in the in the FIGS. 8 and 9 shown embodiment, two offset by 60 ° to each other arranged independent piping 17, where per pipe system 17 three densifications, relaxations, etc. take place.

In Fig. 10 a further embodiment is shown, which is largely that according to the FIGS. 5 to 7 corresponds, however, the circulation of the working medium is not achieved due to the direction of rotation curved tubes 20, but with the help of a paddle wheel 31, which acts as a compressor or as a turbine. The impeller 31 is arranged stationary, wherein due to the relative rotational movement to the surrounding the impeller 31 tubes 17, a flow of the working medium in the tubes 17 is effected.

Here, the working medium is expanded in the tubes 17 of the expansion unit 3 and the impeller 31 is fed, wherein the impeller 31 is received in a Schaufelradgehäuse 32, which is closed by a cover 33. The impeller 31 is rotatably supported by bearings 34, however, has permanent magnets 35 which cooperate with non-rotatably mounted outside the Schaufelradgehäuses 32 permanent magnet 36, so that the impeller 31 is arranged rotationally fixed. The magnets 36 are held resting on a static shaft 37 here.

In Fig. 11 is one to the in Fig. 10 shown embodiment very similar trained device shown, but here the relative rotational movement of the paddle wheel 31 to the tubes 17 of the compressor and relaxation unit 1 and 3 by means of a motor 38 is generated. The motor 38 is rotatably connected to the co-rotating manifold 27. The power supply takes place via lines 39, which are accommodated in a shaft 40. For power transmission, the shaft 40 contacts 41. The motor 5 in this embodiment only provides power to overcome the aerodynamic drag of the rotating system.

This can therefore be omitted by the use of turbines in the circulation of the liquid heat transfer medium, which withdraw this power this cycle. The power required to overcome the air resistance is then additionally provided by the pumps, which drive the circulation of the liquid heat transfer medium.

Claims (15)

1. A method for converting thermal energy at a low temperature into thermal energy at a higher temperature by means of mechanical energy and vice versa with a working medium, which runs through a closed thermodynamic circulation process, wherein the circulation process exhibits the following working steps:

   - adiabatic compression of the working medium,

   - isobaric removal of heat away from the working medium by means of a heat exchange medium,

   - adiabatic relaxing of the working medium,

   - isobaric supply of heat to the working medium by means of a heat exchange medium,

   wherein, in order to increase or decrease the pressure of the working medium during compression or relaxation, respectively, the working medium is relayed essentially radially outward or inward in relation to a rotational axis, which generates an increase or decrease in the centrifugal force acting on the working medium, characterized in that the working medium during the closed circulation process as well as the heat exchange media are routed around the rotational axis for purposes of heat supply and removal, so that the flow energy of the working medium is essentially retained during the closed circulation process.
2. The method according to claim 1, characterized in that the working medium, preferably a noble gas, in particular krypton, xenon, argon, radon or a mixture thereof, is gaseous during the entire circulation process.
3. The method according to claim 1 or 2, characterized in that the pressure in the closed circulation process measures at least in excess of 50 bar, in particular in excess of 70 bar, preferably essentially 100 bar.
4. The method according to claim 2 or 3, characterized in that the circulation process is carried out in close proximity to the critical point of the gaseous working medium.
5. The method according to one of claims 1 to 4, characterized in that heat is removed and supplied using a heat exchange medium with an isentropic exponent kappa ∼1, in particular a liquid heat exchange medium.
6. A device for implementing a method according to one of claims 1 to 5, with a compressor (1), a relaxation unit (3) and respective heat exchangers (2, 4) for supplying or removing heat, wherein the compressor (1) and relaxation unit (3) are mounted so that they can rotate around a rotational axis, and the compressor (1) and/or relaxation unit (3) are designed in such a way that the working medium in the compressor (1) is essentially carried radially outward in relation to the rotational axis, or essentially carried radially inward in the relaxation unit (3), thereby increasing or decreasing the pressure by increasing or decreasing the centrifugal force acting on the working medium, characterized in that the heat exchangers (2, 4) are designed to rotate together with the compressor (1) and relaxation unit (3), in which the working medium is relayed around the rotational axis during the closed circulation process, so that the flow energy of the working medium is essentially retained during the closed circulation process.
7. The device according to claim 6, characterized in that the heat exchangers (2, 4) each comprise at least one pipe (9) that carries a liquid heat transfer medium.
8. The device according to claim 6 or 7, characterized in that the relaxation unit (3) connects directly to the compressor (1) via the heat exchangers (2, 4).
9. The device according to one of claims 6 to 8, characterized in that impellers (1', 3') of the compressor and of the relaxation unit (1, 3) are mounted on a shared torque shaft (5'), wherein a casing (6) is provided that co-rotates with the impellers (1') of the compressor (1', 3') and of the relaxation unit (3).
10. The device according to one of claims 5 to 9, characterized in that a casing (8) arranged to be torsion-resistant that envelops the compressor (1) and the relaxation unit (3) is provided, in which the two heat exchanges (2, 4) are incorporated.
11. The device according to one of claims 5 to 7, characterized in that at least one rotatably mounted pipeline system (17) that circulates the working medium is provided, wherein the pipeline system (17) comprises linear compression pipes (18) that run in a radial direction and/or relaxation pipes (20) bent against the rotational direction of the torque shaft (5').
12. The device according to claim 11, characterized in that the relaxation pipes (20) are circularly bent in cross section, wherein the relaxation pipes (20) comprise in cross section a bend with a radius that constantly diminishes towards the rotation center (30).
13. The device according to claim 11, characterized in that the pipeline system (17) incorporates a paddle wheel (31) that rotates relative to the pipeline system (17).
14. The device according to claim 13, characterized in that the paddle wheel (31) is arranged in a torsion-resistant manner.
15. The device according to one of claims 8 to 14, characterized in that an electric motor or generator (5) is connected to the torque shaft (5') and/or the pipeline system (17).

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