EP4295091A1

EP4295091A1 - Device and method for processing gas, and ventilation and air conditioning apparatus

Info

Publication number: EP4295091A1
Application number: EP22708875.4A
Authority: EP
Inventors: Holger Sedlak
Original assignee: Justairtech GmbH
Current assignee: Justairtech GmbH
Priority date: 2021-02-17
Filing date: 2022-02-17
Publication date: 2023-12-27
Also published as: DE102021201530A1; US20230384000A1; WO2022175403A1; AU2022224389A1

Abstract

The invention relates to a device for processing gas, comprising the following features: a compressor (40), which has a compressor inlet (41) and a compressor outlet (42); a heat exchanger (10), which has a heat exchanger inlet (11), a first heat exchanger outlet (12), a second heat exchanger inlet (13) and a second heat exchanger outlet (14), the heat exchanger being in the form of a gas-to-gas heat exchanger; a turbine (70), which has a turbine inlet (71) and a turbine outlet (72), the compressor outlet (42) being connected to the second heat exchanger inlet (13), and the second heat exchanger outlet (14) being connected to the turbine inlet (71); an inlet interface for coupling the compressor inlet (41) and the first heat exchanger inlet (11) to a gas feed; and an outlet interface (200) for coupling the turbine outlet (72) and the first heat exchanger outlet (12) to a gas discharge.

Description

Apparatus and method for treating gas and AHU

description

The present invention relates to devices and methods for treating gas and in particular to such devices which can be used separately or together with a ventilation and air conditioning device (AHU) for heating or cooling gas, such as air.

Related devices are cold air chillers. They are used, for example, in space travel. In the technical publication "High-capacity turbo-Brayton cryocoolers for space applications", M. Zagarola et al., Cryogenics 46 (2006), pages 169 to 175, a cryocooler is disclosed, which is shown schematically in Fig. 9. A compressor C compresses gas , which circulates in the closed system. The compressed gas is cooled by a heat exchanger, which is schematically referred to as "heat sink" or "heat release". The cooled gas is fed into a recuperator R, which feeds the gas cooled thereby to a turbine E Cold gas is discharged from the turbine E, which absorbs heat or achieves a cooling effect via a heat exchanger. The gas that exits the heat exchanger, which provides the cooling effect, and is again warmer than the gas at the same entrance, is also fed into the Fed in recuperator R to be reheated.

The temperature-entropy diagram of the cycle in FIG. 9 is shown in FIG. Compressor C performs isentropic compression as shown by the transition from transition point 1 to transition point 2. An isobaric heat dissipation takes place through the heat exchanger for heat dissipation, as illustrated by the transition from point 2 to point 3 in FIG. An isobaric heat dissipation also takes place through the recuperator R, as illustrated by the transition between point 3 and point 4 . Then an isentropic expansion takes place in the turbine 4, as represented by the transition between point 4 and point 5. The refrigeration effect of the heat exchanger, in turn, represents an isobaric heat input, as represented by the transition from point 5 to point 6. The heat dissipated in the heat exchanger is represented in the temperature-entropy diagram as the temperature difference between point 2 and point 3. Correspondingly, the temperature reduction achieved by the turbine expansion is represented by the temperature difference between point 4 and point 5. Finally, the temperature difference that can be used for cooling, thus represented as "available cooling", is shown between point 5 and point 6.

Other cold air chillers in various other designs are presented in the lecture "Air as a refrigerant - history of the cold air chiller" by I. Ebinger, held at the 2013 historians' conference in Friedrichshafen on June 21, 2013.

Compared to heat pumps, which are used for cooling and heating, gas chillers have the advantage that energy-intensive circulation of liquid refrigerant can be avoided. In addition, gas refrigeration machines do not require continuous evaporation on the one hand and continuous condensation on the other. Only gas circulates in the cycle shown in FIG. 9, without there being any transitions between the different states of aggregation. Furthermore, heat pumps require very low pressures close to vacuum, especially if climate-problematic refrigerants are to be dispensed with, which can lead to considerable expense, especially in terms of equipment, in the production, handling and maintenance during operation.

Such cold air chillers include a compressor, a turbine, a recuperator, and a heat exchanger. Heat is extracted by the heat exchanger in a cold air chiller and dissipated to a heat sink. This typically takes place in an air-to-liquid heat exchanger. Cold-air chillers, such as those described in German application 102020213544.4, can be used to work as an open system in order to use the air from a room as the working medium of the cold-air chiller in order to deliver appropriately cooled air to this room in the sense of an open system to give back. In particular, such a cold-air chiller includes a recuperator at the compressor inlet. A compressor-heat exchanger-turbine combination of such a gas refrigerator is connected to a recuperator outlet. This implementation involves a large number of components due to the use of a recuperator, a compressor, a heat exchanger, a turbine, and a heat sink, the coupling of which requires the heat exchanger to be configured as an air-to-liquid heat exchanger.

The object of the present invention is to provide a simpler concept for treating gas such as air. This object is achieved by a device for treating gas according to patent claim 1, a method for operating a device for treating gas according to patent claim 27, a method for producing a device for treating gas according to patent claim 28, or a ventilation and air conditioning device with such a method - Direction according to claim 22 solved.

The present invention is based on the finding that a simple and at the same time robust measure for treating gas is to use a compressor-heat exchanger-turbine combination in which the heat exchanger is designed as a gas-gas heat exchanger and is coupled on its primary side between the compressor outlet and the turbine inlet. Depending on the implementation, various different gas flows can be applied to the primary side of the gas-gas heat exchanger, which can also be referred to as a recuperator. In preferred embodiments, the compressor-gas-gas-heat exchanger-turbine combination is provided with an input interface and an output interface, the input interface being designed to couple the compressor input and the heat exchanger input on the primary side to a gas supply . The outlet interface is then designed to couple the turbine outlet and the heat exchanger outlet of the primary side of the heat exchanger to a gas outlet.

Depending on the implementation, the input interface and the output interface can be “hardwired”, i.e. permanently installed, in order to run the gas treatment device in “summer mode”, in which the focus is on the cooling capacity of the treatment device. In another implementation of the input interface and/or the output interface, the device for treating gas is "hardwired" into a "winter mode" in which the heating, ie the heating effect of the device, is the focus. In yet another embodiment, both the input interface and the output interface are designed to be controllable to control the input side of the gas treatment device and the output side of the gas treatment device depending on a control signal that can be detected manually or automatically to set to a cooling mode or to a heating mode. The detection of the environmental situation, such as a T emperature detection or a target temperature detection of a supply air for a room can be automatically using a T emperature sensor or a flow sensor or both sensors take place, or can be derived manually or depending on a larger, for example, a building control. Depending on the implementation, the input interface or the output interface can be set up as a two-way switch with two inputs and two outputs, whereby two connections can be switched back and forth from the inputs to the outputs. Alternatively, the interface can also consist of individual switching elements in order to connect an input to one of two outputs depending on a control signal.

In preferred embodiments, the device for treating gas is designed to have a special compressor-turbine combination in which the compressor wheel and the turbine wheel are arranged on one axis, with a drive motor being arranged between the compressor wheel and the turbine wheel, and in particular, the rotor of the drive motor being arranged on the same axis on which the turbine wheel and the compressor wheel are also arranged.

In preferred exemplary embodiments of the present invention, the heat exchanger, which is a gas-gas heat exchanger, is designed in the manner of a recuperator, with a counterflow principle also preferably being used in which a plurality and in particular a large number of flow channels , which form the primary side, are in thermal interaction with a plurality and in particular a large number of flow channels which form the secondary side. Furthermore, it is preferred that the heat exchanger has a rotationally symmetrical shape with a first recuperator outlet in the middle of the recuperator.

In preferred exemplary embodiments of the present invention, the device for treating gas is coupled via the input and/or output interface to a ventilation and air-conditioning device, in particular to a ventilation and air-conditioning device that has an exhaust air connection, an air supply connection, and optionally also an exhaust air connection and offers a fresh air connection. The ventilation and air conditioning device, which typically discharges at least part of the exhaust air from a room to the outside as exhaust air, is supplemented by the device for treating gas in such a way that, for example for heating in the room, i.e. in winter operation, the thermal energy of the exhaust air is extracted and transferred to the supply air via the heat exchanger. So energy is also extracted from the supplied fresh air for cooling in the room and removed from the system via the exhaust air, which is already warm. With the compressor-ZT turbine combination, relatively "hot" fresh air can be used to generate even hotter exhaust air from the exhaust air, so that the supply air can still bring adequate cooling capacity into the room.

In a preferred exemplary embodiment, the ventilation and air-conditioning device has a divider, which divides exhaust air from the room into an exhaust air flow and a return flow. The reintroduction stream is preferably processed by a processor, such as modified in terms of moisture, disinfected or enriched with oxygen, but typically not thermally, ie actively modified with regard to its temperature. This processed air flow is fed to a combiner, which at the same time receives conditioned fresh air from the gas treatment device, which, depending on the implementation, is cold when the room is to be cooled, i.e. when the room supply air is to be colder than the room exhaust air, or which is warm if the room is to be heated, i.e. if the room supply air has to be warmer than the room exhaust air.

Preferred embodiments of the present invention are explained in detail below with reference to the accompanying drawings. Show it:

1 shows a device for treating gas according to an embodiment:

2 shows a device for treating gas for “summer operation” according to an exemplary embodiment:

3 shows a device for treating gas according to a further exemplary embodiment for “winter operation”: FIG. 4a shows an implementation of the input interface or the output interface;

4b shows a control table for configuring the interfaces in summer or winter mode:

Figure 5a shows an alternative implementation of the device for treating gas; Fig. 5b shows a control table for controlling the switches in Fig. 5a;

Fig. 5c an implementation of the input or the output interface as

two-way switch;

6a shows an exemplary embodiment of a ventilation and air-conditioning device that can be coupled to the device for treating gas; 6b shows a further exemplary embodiment of a ventilation and air-conditioning device which can be coupled to the device for treating gas;

7a is a perspective view of a preferred compressor-turbine combination;

FIG. 7b is a side view of the preferred compressor-turbine combination of FIG. 7a;

8a shows a schematic representation of a section through a preferred heat exchanger/recuperator with collection spaces on the secondary side and on the primary side;

FIG. 8b shows a schematic plan view of a preferred recuperator of FIG. 8c with collection spaces on the primary side and the secondary side;

8c shows an alternative implementation of the device for treating gas according to an embodiment;

9 shows a schematic representation of a known cold-air refrigerating machine; and

10 shows a temperature-entropy diagram of the known cold-air refrigerating machine from FIG.

1 shows an apparatus for treating gas 600 according to an embodiment of the present invention. The device 600 for treating gas comprises a compressor 40 with a compressor inlet 41 and a compressor outlet 42. The device also includes a heat exchanger 10 which is also referred to below as a recuperator and which has a first heat exchanger inlet 11 , a first heat exchanger outlet 12 , a second heat exchanger inlet 13 and a second heat exchanger outlet 14 . The heat exchanger 10 is designed as a gas-gas heat exchanger, to the effect that both on its primary side, which is formed by the first heat exchanger inlet 11 and the first heat exchanger outlet 12, and on its secondary side, which is formed by the second heat exchanger inlet 13 and the second heat exchanger outlet 14 is formed, the same type of gas is used, for example air. Regardless of whether a gas is used in the combination of compressor, heat exchanger secondary circuit and turbine and another gas flows in the primary side of the heat exchanger, the heat exchanger is still designed as a gas-gas heat exchanger.

In an alternative embodiment of the present invention, the heat exchanger can also be designed as a liquid/gas heat exchanger or solid/gas heat exchanger. At least one input interface or one output interface or both interfaces are then provided, which preferably couple a material supply, which is a gas supply or else a liquid supply. In both cases, the input or output interface can not only be switchable or hardwired, but the respective interface can also include a heat exchanger in order to bring thermal energy from the material feed into the heat exchanger or to remove thermal energy from the heat exchanger 10 .

In a preferred embodiment of the present invention, the device 600 for treating gas is supplemented by an input interface 100 or an output interface 200 or both interfaces. The input interface 100 is designed to couple the compressor input 41 and the first heat exchanger input 11 with a material supply, which is preferably a gas supply, which preferably consists of an exhaust air duct 102a and a fresh air duct 102b. The output interface 200 is also designed to couple the turbine output 72 and the first heat exchanger output 12 to a material discharge, which is preferably a gas discharge, which preferably has an inlet air duct 202a and an exhaust air duct 202b. In particular, the input interface includes an exhaust air input or duct 102a on an input side and a fresh air input 102b also on the input side. Furthermore, the input interface 100 includes a first input interface output 104 and a second input interface output 106 on an output side of the input interface 100. Furthermore, the output interface 200 preferably comprises a supply air output 202a and an exhaust air output 202b on an output side and a first output interface input 206 and a second output interface input 204 on an input side of the output interface 200.

As shown in FIG. 1 , the compressor outlet 42 is connected to the second heat exchanger inlet 13 in the device 600 for treating gas. Furthermore, the second heat exchanger outlet 14 is connected to the turbine inlet 71 . In a preferred embodiment of the present invention, the turbine output 72 is connected to the first output interface input 206 . Furthermore, the first heat exchanger outlet 12 is connected to the second outlet interface inlet 204 . Furthermore, the first input interface output 104 is connected to the first heat exchanger input 11 and the second input interface output 106 is connected to the compressor input 41 . The connections presented above are direct connections of one gas channel to another gas channel, so that the gas flows directly from the first input interface output 104 into the first heat exchanger input 11 on the primary side of the heat exchanger 10, for example.

In addition, the input interface 100 is designed to couple the input side of the input interface 100 to the output side of the input interface 100 . In addition, the output interface is designed to couple the input side of the output interface 200 to the output side of the output interface 200 .

Depending on the implementation, this coupling can be a fixed coupling, as is presented, for example, in FIG. 2 or FIG 4a or in FIG. 5a, a changeover switch, such as that shown in FIG. 5c and in FIG. 4a, can be used to perform a corresponding changeover from one coupling to the other. This achieves, for example, a cooling mode or summer mode, as shown in FIG. 2, or a heating mode or winter mode, as shown in FIG. Alternatively or additionally, the fixed coupling or the switchable coupling can take place via a further heat exchanger. Fig. 1 also shows an implementation in which the input interface or the output interface can be controlled depending on a control signal 302, 304, the device having a controller 300 which is designed to receive a control input and to To deliver control signal 302, 304, wherein the controller 300 is designed to receive the control signal through a manual input or a sensor-controlled input.

Preferably, the controller 300 is designed to set the input interface parts 100 or the output interface 200 by the control signal 302, 304 in a summer mode for cooling a gas for a gas inlet channel 202a of the gas discharge, and to the input interface 100 or the Set output interface 200 by the control signal 302, 304 in a winter mode for heating a gas for the Zugaskanal 202a. The controller can, for example, keep a control table 301 from FIG. 4b or a control table 303 from FIG. 5b in a memory and use it accordingly.

In the exemplary embodiment of FIG. 2 of the device 600 for treating gas, the input interface 100 is designed as a fixed connection between the fresh air duct 102b and the compressor input 41 . This means that there is a direct connection between the second input interface output 106 and the fresh air duct 102b. Correspondingly, the exhaust air duct 102a is also directly connected to the first heat exchanger inlet 11 or to the second inlet interface part outlet 106 .

A corresponding direct connection also exists between the output interface input 206 and the supply air duct 202a on the one hand and the first heat exchanger output 12 or the output interface input 204 and the exhaust air output 202b, as shown in FIG.

Furthermore, FIG. 2 shows a coupling of the device 600 to a ventilation and air conditioning device, which is coupled to a room 400 via a room exhaust air duct 508 and a room air supply duct 510 . The air handling unit 500, which is explained in more detail in Fig. 6a or 6b, comprises a splitter 502, which optionally has a fan to draw air from the room and pump it into the input interface 100, an optional handler 504 and a combiner 506, which is preferably a fan 506a of FIG. 8c in order to pump the room supply air in the room supply air duct 510 into the room and to draw in the corresponding supply air from the supply air connection 202a.

2 further includes various exemplary temperature values to demonstrate the cooling effect of the gas treatment device. Relatively hot fresh air at 50° C. is sucked in by the compressor 40 via a fresh air inlet. Even in very hot regions in summer, it will rarely be the case that the temperature in the shade, i.e. the outside air, will be above 50°C. The compressor 40 is designed, for example, in such a way that it has a speed or a compression ratio that results in the air at the outlet of the guide chamber of the compressor, which is not shown in FIG. 2, having a temperature of 90°C. This temperature of 90°C is reduced in the heat exchanger 10 to 28°C at the second heat exchanger outlet 14 due to the heat transfer and thermal heat coupling with the primary side. The high pressure, now cooled, air at a temperature of about 28°C is relaxed in the turbine 70 to a temperature of, for example, 5°C, as a result of which a relaxation to the original pressure ratio is obtained.

The 5°C cold air is then fed into the supply air duct 202a and can be used for cooling purposes in the room 400. The primary side of the heat exchanger 10 receives warm air from the room at the inlet, for example at a temperature of 25°C, and this temperature is raised by the action of the heat exchanger 10 to a temperature of about 87°C, and this now becomes very hot air via the exhaust air duct 202b to the outside, for example to a shady side or a roof of a building. It turns out that even when the outside temperature is very high and is 50°C, the exhaust air is still significantly hotter than the ambient air at 87°C and therefore the energy dissipated via the exhaust air can be easily absorbed by the environment and no additional heat sink is required. Typical heat exchanger temperature differences of 3° C. were assumed for the heat exchanger 10, which are present between the inlet on the secondary side and the outlet on the secondary side or between the inlet on the primary side and the outlet on the secondary side.

By the combiner 506 of the ventilation and air conditioning device now mixing the 5°C cold air into the output of the processor 504 in the combiner 506, for example, 18°C cold air can be generated without any major problems, which can be used for cooling purposes in the room 400 can be fed, which, for example, a Room in a building, such as a conference room, room, hall, or something similar, or which may also be a "functional space" such as a data center.

FIG. 3 shows an alternative implementation of the device 600 for treating gas, which is now connected in a winter mode in which a heating effect is to be achieved in the space 400 . Here again it is assumed that it is too cold in the room, that is, for example, that air with a temperature of 18° C. is extracted from the room and fed into the divider 502 . The distributor 502 now feeds the exhaust air duct 102a, which is connected to the compressor 40. The compressor receives the 18°C warm air and increases the temperature of the air to 48°C, for example, due to its compression effect. This 48°C warm air is cooled down to about -27°C due to the action of the heat exchanger 10 . The -27°C cold air, which is still at a high pressure, which is present at the compressor outlet 42, is relaxed via the turbine 70 and cooled to a temperature of -57°C, for example. This very cold air is discharged to the environment via an exhaust air outlet, which already has a very cold temperature of -30° C. in the exemplary embodiment shown in FIG. The ambient air is fed into the primary-side inlet 11 of the heat exchanger 10 via the fresh air duct 102b and is heated to a temperature of 45° C. due to the effect of the heat exchanger. The 45° C. warm air is mixed via the combiner 506 with the 18° C. warm air at the outlet of the processor 504 in order to finally achieve a temperature of 25° C. in the room supply air duct 510, for example.

The temperature examples shown in FIG. 2 for cooling and in FIG. 3 for heating are extreme examples. However, the example in FIG. 2 shows that even with extremely hot outside temperatures of 50° C., a cooling effect is easily achieved and exhaust air can be generated that is 87° C. hot and can therefore be fed into the environment as a heat sink without further ado can.

The same applies to the temperature example shown in FIG. 3, in which very cold outside temperatures of -30° C. were assumed, with very cold Forti air of -57° C. being able to be generated, for example, by the compressor-heat exchanger-turbine combination according to the invention can easily be released into the -30°C cold environment. In other words, even supply air cold at -30° C. serves as a sufficient heat source to increase the fresh air temperature via the heat exchanger 10 to the temperature of 45° C., which is easily sufficient for heating. Although in the embodiment shown in Fig. 2 and Fig. 3 an interposition of a ventilation and air conditioning device with a divider 502 and a combiner 506 has been shown, it is readily apparent that even without the interposition of a divider 502 and a combiner 506, cooling in the room or heating in the room can be achieved if the warm air with a temperature of 45°C shown in Fig. 3, for example, is fed directly into the room, or if, as shown in Fig. 2, the 5°C cold air is fed directly is fed into the room. For compatibility with existing ventilation and air conditioning systems, in which only part of the air becomes exhaust air and another part is fed back in after processing in processor 504, the use of elements 502, 504, 506 is preferred according to the invention, as referred to below be shown in more detail with reference to Figure 6a.

It should be noted that when the outside temperatures are warmer than in FIG. 2 for heating or cooler than in FIG. 3 for cooling, the demands on the compressor and turbine become more relaxed. These more relaxed demands, or if current temperatures become more extreme in the other direction, more tense demands can be implemented by decreasing or increasing the speeds of the compressor and turbine.

6a shows a detailed representation of the ventilation and air conditioning device 500 with a room exhaust air duct 508 and a room air supply duct 510, both of which are connected to a room 400 to be air-conditioned. The ventilation and air conditioning device 500 includes the splitter 502, the optional processor 504 and the combiner 506. The splitter divides the air flow in the room exhaust air duct 508 into the exhaust air duct 102a and the return flow 512, with the exhaust air present in the exhaust air duct 102a being processed or air-conditioned to a certain extent exhaust air.

The portion of the room exhaust air in duct 508 that does not ultimately become exhaust air via duct 102a represents the reintroduction flow 512, which is typically not changed in temperature, but which can only be processed with regard to other air quality parameters in processor 504, such as oxygenated, moisture-enriched, or moisture-depleted. Other processing procedures consist of disinfecting the refeed stream or filtering the refeed stream for dust or biological particles, such as bacteria or viruses. However, handler 504 may be bypassed or omitted, as shown in phantom in Figure 6a.

In the combiner 506, the supply air in the supply air duct 202a, which is due to fresh air that has changed in terms of its temperature, is combined with the reintroduction flow directly or with the processed reintroduction flow and fed to the room 400 via the room inlet air duct 510. For this purpose, the combiner 506 preferably comprises a fan 506a of FIG. 8c, which can be used to draw in supply air via the supply air duct 202a, ie, referring to FIG. 8c, to draw it through the primary side of the heat exchanger. At the same time, a fan can also be present in the divider 502, which extracts the room exhaust air from the room 400 and feeds air into the exhaust air duct 102a in order to transport it through the heat exchanger 10 as exhaust air into the environment, for example during summer operation.

FIG. 6b shows a further exemplary embodiment of a ventilation and air-conditioning device that can be coupled to the device for treating gas. The device in Fig. 6b is similar to the device of Fig. 6a. However, the processor 505 is not located between the divider 502 and the combiner 506, but in the flow direction of the room supply air between the combiner 506 and the supply air inlet of the room 400. This ensures that, in contrast to the embodiment in Fig. 6a, not only the room exhaust air is processed, but also the supply air from connection 202a, which is conditioned fresh air. If the fresh air z. B. is odorous, as can occur for example in the vicinity of farms, then the processor 504 will be able to remove this odor pollution. In contrast to FIG. 6a, the processor 504 in FIG. 6a has to process less gas flow than in FIG. 6b, because in FIG entire gas flow has to be processed. However, since the splitter 502 in preferred embodiments makes more than 50 percent and preferably more than 70% or more than 80% of the exhaust gas flow into the feed flow 512, this point is not particularly important. Furthermore, it has proven to be advantageous that when the processor 504 is placed after the combiner 506, the same pressures prevail at the connections 102a and 202a, ie one and the same pressure area is present. Therefore, it is preferred to run the divider 502 without blower or fan, but z. B. passive. Then the optional fan L, indicated at 21 in Figure 5a, would be present, which need not otherwise be present, as shown schematically by dashed line 22. the alternative placement of the processor which preferably also has a fan in it to blow the conditioned air into the space while favoring a passive splitter 502 to allow the feed stream 512 to be drawn in by the fan in the processor 504 and the conditioned fresh air in the combiner 506 can also be used in FIG. 2 or FIG. Alternatively, fan L 21 can also be placed at the outlet of the heat exchanger before connection A4. However, the placement in Fig. 5a is preferred because here the gas flow is pushed through the heat exchanger and not sucked in, as is the case with the placement at connection A4.

It should also be noted that the room 400 can be any room, such as, e.g. B. a house, an office, an office space, but also a car or even the interior of a tumble dryer. Even a not completely separate space, such as a partially open outdoor space e.g. B. a restaurant can be air-conditioned according to the invention, such. B. be cooled or heated.

The present invention is further particularly advantageous because tasks to be normally performed in addition to air conditioning by the gas treatment apparatus, such as dehumidification of the supply air, particularly for cooling operation e.g. B. can be easily carried out in summer. With regard to the exemplary temperatures shown in FIG. 2, the dew point will occur in the outlet pipe of the turbine. There mist formation will take place. Controlled dehumidification can take place simply by placing a drip catcher in the outlet flow of the turbine 70, which catches a desired proportion of the droplets formed and discharges them to a condensed liquid disposal point.

On the other hand, air humidification, e.g. B. for heating in winter, as shown in Fig. 3, easily be obtained simply by that at the first outlet 12 of the heat exchanger 10, ie before the combiner, where the gas is relatively hot, such. B. 45 has an open water surface is placed, which is surrounded by z. B. a float construction with liquid can be automatically refilled. Due to the too-dry-for-temperature gas flowing out of the heat exchanger, liquid will readily evaporate from the open water surface. Alternatively, water can also be sprayed in at this point, which is also possible without great effort.

It should be noted that, unlike existing ventilation and air conditioning devices, which use heat recovery from the room exhaust air flow a heat pump takes place, which uses a liquid such as water as the working medium, the device according to the invention for treating gas does not require a liquid as the working medium, but solely uses gas as the working medium. Therefore, the device according to the invention for treating gas can be implemented in a particularly efficient and energy-saving manner, because all losses associated with the circulation of water or with the complex (due to a very low pressure required) and energy-intensive evaporation of water become obsolete. According to the invention, gas is used only both in the primary circuit of the heat exchanger and in the secondary circuit of the heat exchanger, so that the heat exchanger is implemented as a gas-gas heat exchanger. Throughout the entire device, only gas is used as the working medium, so that all the difficulties that occur with the use of a liquid as the working medium are eliminated. Such problematic and complex implementations when using liquid as a working medium can also be seen, for example, in the storage and sealing of liquids, even if environmentally friendly liquids such as water are used, and in the necessary measures to e.g. B. to evaporate water at low temperatures.

FIG. 4a shows an implementation of the input interface 100 or the output interface 200 as a two-way switch, as is shown schematically in FIG. 5c, for example. By rotating the switch 700 in Fig. 5c, a connection of port A1 to port A4 on the one hand and a connection of port A2 to port A3 on the other hand can be achieved, so that the exhaust air can be connected to port A1, which is at 104 in Fig. 4a is shown, and the fresh air is connected to port A3, as shown by the current "switch position" of switch 700. If, on the other hand, the changeover switch 700 is rotated by 90°, the fresh air duct is connected to the connection A1 and the exhaust air duct is connected to the connection A3.

The implementation of the output interface is corresponding, but here the lower labels in Fig. 5c are relevant. In the current position of switch 700, supply air 202a is connected to port A2, and exhaust air 202b is connected to port A4. If, on the other hand, the changeover switch 700 is turned through 90°, the supply air is connected to the port A4 and the exhaust air is connected to the port A2. Fig. 4b shows a corresponding control table that expresses that in summer operation, for example, which is shown in Fig. 2, the exhaust air is connected to port A1, the fresh air is connected to port A3, and the supply air is connected to port A2 is connected, and the exhaust air is connected to port A4. If, on the other hand, the device according to the invention for treating gas according to FIG. 3 is configured in winter mode, the exhaust air is connected to the port A3, the fresh air is connected to the port A1, the supply air is connected to the port A4, and the forti air is connected connected to port A2.

FIG. 5a shows an alternative implementation of the input interface and the output interface, the input interface being implemented with two individual switches in contrast to a two-way switch of FIG. 4a. The input interface includes a first switch 100a for port A3 and a second switch 100b for port A1.

The output interface includes a first switch 200a for port A2 and a second switch 200b for port A4. The first switch 100a has a fresh air connection 308 and an exhaust air connection 320. The second switch 100b has an exhaust air connection 108 and a fresh air connection 120. The connection 108 and the connection 320 can be separate connections or all go back to the same exhaust air connection or exhaust air duct. The fresh air connection 120 and the fresh air connection 308 can in turn be different connections or go back to the same fresh air duct.

The changeover switch is controlled via a control signal 302b for the first control signal C1 and via a second control signal 302a via the control connection C3.

Analogous to this, the output interface 200 is implemented via a first changeover switch 200a and a second changeover switch 200b. The output interface includes a supply air duct 208 and an exhaust air duct 220 for the first switch and an exhaust air duct 400 and a supply air duct 420 for the second switch. The exhaust air duct 220 and the exhaust air duct 400 can be different ducts or one and the same exhaust air duct. The same applies to the supply air duct 420 and the supply air duct 208, which can be designed separately from one another or can open into a common supply air duct. The control takes place in turn via a control signal 304a for the second switch, ie for the control signal C2, and via a further control signal 304b for the control connection C4.

Fig. 5b shows another control table 303, which expresses how the individual control connections C1, C2, C3, C4 must be set in order to achieve either summer operation or winter operation, i.e. either cooling in the room, for example according to FIG. 2 or to achieve heating in the room according to FIG.

FIG. 8c shows another preferred implementation of an apparatus for treating gas, again comprising the turbine 70, the compressor 40 and the heat exchanger 10. FIG. However, FIG. 8c shows a special embodiment of the heat exchanger 10 as a rotationally symmetrical heat exchanger in cross section. Here, gas in the compressor outlet 42 is fed into the secondary or second heat exchanger inlet 13, which communicates via a collection space 18 with another collection space 17, via which the gas is then fed into the second heat exchanger outlet 14 and into the turbine inlet 71. At the same time, the first heat exchanger inlet 11 is supplied with gas via the connection A1 via a collection space 19a on the primary side, which extends around the other collection space 17 on the outside. The gas flows via the inlet A1 into the individual channels from the first heat exchanger inlet into the primary-side or first heat exchanger outlet 12 and collects in the intake area 30, which is delimited by a wall 31, the intake area 30 acting as a second primary-side collection space 19b. The gas sucked in there is brought into the room supply air duct via a blower 506a, which can be contained, for example, in the combiner 506 of FIG. 6a. Alternatively, a blower, which is not shown in FIG. 8c, can be mounted “above” the port A1, which could then be present in the divider 502, and which blows the gas from the primary inlet into the primary outlet or first heat exchanger outlet 12 or the Suction area 30 brings and pumps it from there into connection A4 and from there, depending on the output interface wiring, further into the room or into the environment.

FIG. 8b shows a schematic plan view of a preferred recuperator 10 with collection spaces on the secondary side as well. In the exemplary embodiment, the device is completely closed at the top by a closed cover. However, Fig. 8b shows the situation when the lid is transparent. In the middle, the intake area 30 is shown, which is delimited by the intake wall 31 . On the one hand, the boundary 18a for the inner collection space 18 and the boundary 17a for the outer collection space 17 extend around the intake area 30. The gas flow takes place from the outside take place inside, as shown by the arrows 50, namely from the first recuperator or heat exchanger inlet 11 to the first recuperator or heat exchanger outlet 12 for the primary side. Then the gas in the suction area 31 flows down as shown by the arrow ends 51 in the area 30 . Gas also flows on the secondary side into the second recuperator inlet 13 from the compressor outlet 42 . The gas then flows back out through the recuperator 10 into the collection space 17 and down there, as illustrated by the ends of the arrows 53 . The gas then passes from the collection chamber 17 via the recuperator or second heat exchanger outlet 14 into the turbine inlet 71.

It should be pointed out that the flow directions can also be implemented differently, depending on the implementation, as long as the lines 15 on the one hand and 16 on the other hand are separated from one another in the recuperator 10 so that essentially no short-circuiting of the gas flows takes place. Likewise, the collection spaces 17, 18 are separated from the lines 15. In the exemplary embodiment shown, the collection spaces 17 , 18 are assigned to the lines 16 which connect the second recuperator or heat exchanger inlet 13 to the second recuperator or heat exchanger outlet 14 . Alternatively, the implementation can also be such that the collection spaces are assigned to the first recuperator inlet and the first recuperator outlet and the second inlet and the second recuperator outlet are gas-insulated from the collection spaces.

8a also shows a schematic representation of a heat exchanger that, in contrast to FIG. 8c or FIG 11 gas flows into a first collection space 19a on the primary side, via the channels 15 to the first recuperator or heat exchanger outlet 12 and in particular to a second collection space 19b on the primary side, and from there it leaves the recuperator 10 via the second heat exchanger outlet 12. The secondary side includes a second recuperator or heat exchanger inlet 13 via which gas flows through the channels 16 from the collection space 18 into the other collection space 17 and from there via the second recuperator or heat exchanger outlet 14 leaves the recuperator 10 or heat exchanger. This achieves thermal interaction between the two channels, which, however, are gas-insulated from one another. Exactly so are the primary-side first collection space 19a and the second collection space 19b on the primary side is correspondingly gas-insulated from the collection spaces 17 and 18 on the secondary side, so that no short circuit occurs in the heat exchanger.

However, FIG. 8a also serves to show at least part of a rotationally symmetrical heat exchanger, as shown in FIG. 8b in a plan view from above, with the collection space 19a of FIG secondary-side collection space 17 and again further inside the other secondary-side collection space 18 is shown, with in particular the intake area 30 or the middle area representing the additional collection space 19b of the primary side. However, FIG. 8b shows the case where the first heat exchanger or recuperator outlet 12 is at the bottom with respect to the plane of the drawing, as illustrated by the flow 51 directed downwards in FIG. 8b, and as also illustrated schematically in FIG. 8c , if at least with regard to the heat exchanger 10 Fig. 8c shows the actual erection direction. The direction of installation is irrelevant for functionality, because gravity itself is not decisive for gas, compared to a heat pump implementation with liquid as the working fluid. Here, too, another advantage of the present invention over a heat pump with liquid as the working medium is evident, especially since the direction of installation plays an important role due to the high weight and the high density of liquid compared to gas, which is not the case with the present invention , which allows a much greater flexibility of application in the present invention.

Preferably the recuperator extends a distance greater than 10 cm and preferably greater than 60 cm in the longitudinal direction of the cylinder. Furthermore, the gas ducts are arranged in such a way that they are essentially evenly distributed over the volume on all sides and can thus guide as much air as possible from the heat exchanger inlet 11 on the primary side into the intake area as efficiently as possible with little resistance.

In a method for operating the device according to the present invention, the device is operated in such a way that gas-gas operation is achieved in the heat exchanger.

In a method for manufacturing the device, the individual elements are designed and arranged in such a way that the special compressor-heat-exchanger-turbine arrangement is achieved. Although not illustrated in Figures 1-10, the recuperator 10 may be implemented with other heat exchange technologies, such as a heat exchanger that is not counter-current and does not have the gas channels parallel to or perpendicular to each other Housing direction or are arranged in a horizontal operating direction.

The compressor and the turbine do not necessarily have to be arranged on one and the same axis, but other measures can be taken in order to use the energy released by the turbine to drive the compressor.

Furthermore, the compressor and turbine need not necessarily be implemented as radial impellers, although this is preferred, since favorable power matching can be achieved by stepless speed control of the compressor via an electronics assembly 102 of FIG. 7b.

Depending on the embodiment, the compressor can be designed as a turbo compressor with a radial impeller and with a duct or duct which achieves a 180° deflection of the gas flow. However, other gas conduction measures can also be achieved by shaping the guide space differently, for example, or by shaping the radial impeller differently, in order to still achieve a particularly efficient structure that leads to good efficiency.

FIG. 7a shows a perspective view of a preferred compressor-turbine combination and FIG. 7b shows a side view of the preferred compressor-turbine combination from FIG. 7a. The combination is preferably embodied as a monolithic unit or in one piece from the same material. It includes an upper or first bearing area 40b to which the compressor wheel 40a is attached. Compressor wheel 40a merges into a first intermediate area 43a, which is also shown as axis 43. This axis area 43a in turn merges into the rotor 44, which in turn merges into a further intermediate area 43b. This is followed by the turbine wheel 70a, which can be suspended via a lower bearing section 70b. The hangers for the bearing areas are attached to the wall of the intake area 30 of FIG. Rolling or ball bearings are preferably used as bearings. At preferred! Embodiments is the combination of a material such. Br aluminum or plastic, the rotor 44 being surrounded by a ferromagnetic yoke ring on which the magnets are attached, for example by adhesive, in order to form a motor gap with a stator which is not shown in FIG. 7a or 7b.

As is further shown in Fig. 7b, the combination is dimensioned such that the diameter of the compressor wheel 40a is greater than the diameter of the rotor 44, and that the diameter of the rotor 44 (preferably without return path 44a and magnets 44b) is the same or is larger than the diameter of the turbine wheel 70a. This makes it possible to slide a return ring 44a over the turbine wheel 70a and to attach it to the rotor 44 at its circumference.

7b shows an exemplary preferred arrangement of an electronics assembly 102. Thus, the electronics assembly is arranged in the so-called "machine room" between the base of the compressor wheel 40a and the base of the turbine wheel 70a. In particular, the arrangement of the assembly 102 on the upper boundary 71a of the turbine inlet 71 at a distance from the rapidly rotating turbine wheel is advantageous because this area is well tempered due to the gas coming from the heat exchanger. Heat lost from the engine or waste heat from the electronics or sensors in the assembly is therefore easily dissipated via the turbine 70 .

Preferably, the electronics assembly 102 for the electrical supply of the device with energy and/or control signals has an opening in the center and is disc-shaped and extends around a stator of a drive motor for the compressor 40 or is designed to be integrated with the stator, and is also exemplified in FIG an area between a base of a compressor wheel 40a of the compressor 40 and a base of a turbine wheel 70a of the turbine.

Although an annular assembly is shown in cross section in FIG. B. is mounted on the boundary 71a. In this case, it is also preferred that the supply line for energy 101a and data 101b for the motor pass through the lateral boundary 14a of the second recuperator or heat exchanger outlet 14 and to be guided through the housing 100 at the appropriate point.

Although some aspects have been described in the context of a device, it is understood that these aspects also represent a description of the corresponding method, so that a block or a component of a device is also to be understood as a corresponding method step or as a feature of a method step. Similarly, aspects described in connection with a method step also constitute a description of a corresponding block or detail or feature of a corresponding device. Some or all of the method steps may be performed by (or using) hardware apparatus, such as a microprocessor, a programmable computer, or an electronic circuit. In some embodiments, some or more of the major process steps can be performed by such an apparatus.

Claims

patent claims

1. A device for treating gas, having the following features: a compressor (40) with a compressor inlet (41) and a compressor outlet (42); a heat exchanger (10) with a first heat exchanger inlet (11), a first heat exchanger outlet (12), a second heat exchanger inlet (13) and a second heat exchanger outlet (14), the heat exchanger being designed as a gas-gas heat exchanger; a turbine (70) with a turbine inlet (71) and a turbine outlet (72), the compressor outlet (42) being connected to the second heat exchanger inlet (13), and the second heat exchanger outlet (14) being connected to the turbine inlet (71). ; an input interface for coupling the compressor input (41) and the first heat exchanger input (11) to a gas supply, the input interface (100) having an exhaust gas input (102a) and a fresh gas input (102b) on an input side as the gas supply, and has a first input interface output (104) and a second input interface output (106) on an output side, the input interface (100) being designed to connect the input side of the input interface (100) to the output side of the input interface (100) to couple; and an outlet interface (200) for coupling the turbine outlet (72) and the first heat exchanger outlet (12) to a gas discharge, the outlet interface (200) having a first outlet interface inlet ( 204) and a second outlet interface inlet (206) and on an outlet side of the outlet interface (200) as the gas discharge has an inlet gas channel (202a) and an outlet gas channel (202b), the outlet interface (200) being formed to couple the input side of the output interface (200) to the output side of the output interface (200).

2. Device according to one of the preceding claims, which is designed for a cooling operation, wherein the input interface (100) is designed to connect the compressor input (41) to the fresh gas input (102b) of the gas supply, and to the first to connect the heat exchanger inlet (11) to the exhaust gas inlet (102a) of the gas supply, and wherein an outlet interface (200) is formed in order to connect the turbine outlet (72) to the inlet gas duct (202a) of the gas outlet, and to connect the first heat exchanger outlet ( 12) to be connected to the exhaust gas duct (202b) of the gas discharge.

3. Device according to claim 1, which is designed for heating operation, wherein the input interface (100) is designed to connect the compressor input (41) to the exhaust gas input (102a) of the gas supply, and to connect the first heat exchanger input (11) to connect to the fresh gas inlet (102b) of the gas supply, and wherein the outlet interface (200) is designed to connect the turbine outlet (72) to the exhaust gas channel (202b) of the gas outlet, and to connect the first heat exchanger outlet (12) to the Zugaskanal (202a) to connect the gas discharge.

4. Device according to one of the preceding claims, wherein the input interface (100) or the output interface (200) dependent on a control signal (302, 304) can be controlled, and wherein the device has a controller (300) which is adapted to receive a control input and to provide the control signal (302, 304) in response to the control input, wherein the controller (300) is adapted to receive the control signal (302, 304) through a manual input or a sensor-controlled input to obtain.

5. The device according to claim 4, wherein the controller (300) is designed to the input interface (100) or the output interface (200) by the control signal (302, 304) in a summer mode for cooling a gas for the Zugaskanal (202a) to adjust the gas discharge, and to the input interface (100) or setting the output interface (200) to a winter mode for heating a gas for the supply gas duct (202a) by the control signal (302, 304).

6. Device according to one of the preceding claims, in which the input interface (100) has a two-way switch which has the exhaust gas input (102a) and the fresh gas input (102b) for the gas supply, and which has the first input interface output (104), which is connected to the first heat exchanger inlet (11), and the second input interface outlet (106), which is connected to the compressor inlet (41), wherein the two-way switch is designed to the exhaust gas inlet (102a) to either the first input interface output (104) or the second input interface output (106), and to connect the fresh gas input (102b) to either the second input interface output (106) or the first input interface output (104 ) connect to.

7. Device according to one of the preceding claims, wherein the output interface (200) has a two-way switch which has the Zugaskanal (202a) and the Ausgaskanal (202b) for the gas discharge, wherein the two-way switch is designed to connect the exhaust gas duct (202a) to the turbine outlet (72) and the exhaust gas duct (202b) to the first heat exchanger outlet (12), or to connect the exhaust gas duct (202b) to the turbine outlet (72) and the exhaust gas duct (202a) to connect to the first heat exchanger outlet (12).

8. Device according to one of claims 1 to 5, or 7, wherein the input interface (100) has a first switch (100b) or a second switch (100a), wherein the first switch has an output (A1) which is connected to the first heat exchanger inlet (11), and wherein the first switch (100b) has a first inlet, which is connected to the exhaust gas inlet (102a) of the gas supply, and a second inlet, which is connected to the fresh gas inlet (102b) of the gas supply is connected, wherein the first switch (100b) by a control signal (302b) is controllable to connect either the first input or the second input to the output, or wherein the second switch (100a) has an output (A3) which is connected to the compressor input (41), and wherein the first switch (100b) has a first input which is connected to the exhaust gas input (102a) of the gas supply and a second input which is connected to the fresh gas input (102b) of the gas supply, the first switch (100b) being activated by a control signal ( 302a) is controllable to connect either the first input or the second input to the output.

9. Device according to one of claims 1 to 5, 7, 9, in which the output interface (200) has a first changeover switch (200a) or a second changeover switch (200b), the first changeover switch (200a) having an input ( A2) which is connected to the turbine outlet (72), and wherein the first changeover switch (200a) has a first outlet which is connected to the intake gas channel (202a) of the gas discharge and a second outlet which is connected to the exhaust gas channel (202b ) is connected to the gas outlet, the first changeover switch (200a) being controllable by a control signal (304a) in order to connect either the first output or the second output to the input, or the second changeover switch (200b) having an input (A4) which is connected to the second heat exchanger outlet (12), and wherein the second changeover switch (200b) has a first outlet which is connected to the inlet gas duct (202a) of the gas outlet, and a second outlet which is connected to the exhaust gas duct (202b) the gas discharge v is connected, wherein the first changeover switch (200a) can be controlled by a control signal (304b) in order to connect either the first output or the second output to the input.

10. Device according to one of the preceding claims, in which the supply gas is supply air, in which the exhaust gas is exhaust air, in which the fresh gas is fresh air, and in which the exhaust gas is exhaust air, or which is designed for cooling operation and a drip catcher device is arranged in an outlet flow of the turbine (70) in order to remove and discharge the condensation liquid droplets from the outlet flow, or which is designed for heating operation and at the first heat exchanger outlet (12). humidification device is arranged, which brings the liquid to be evaporated into contact with the gas flow at the first heat exchanger outlet (12), or in which a fan (21) is arranged at the first heat exchanger inlet (11) in order to blow gas into the first heat exchanger inlet (11). press, or in which a fan is arranged at the first heat exchanger outlet (12) in order to suck gas from the first heat exchanger outlet (12).

11. The device according to claim 10, which is designed to be coupled to a ventilation and air conditioning device (RLT device), the ventilation and air conditioning device having an exhaust air connection (102a), an air supply connection (202a), an exhaust air connection (202b) and a fresh air connection ( 202a), wherein the device for treating gas can be coupled to the air conditioning device via the input interface (100) or the output interface (200).

12. Device according to one of the preceding claims, in which the compressor (40) is arranged above the turbine (70) in the operating direction.

13. Device according to one of the preceding claims, wherein the compressor (40) has a compressor wheel (40a) and the turbine (70) has a turbine wheel (70a), wherein the compressor wheel (40a) and the turbine wheel (70a) on a ge are arranged on a common axis, with a rotor (44) of a drive motor being arranged on the common axis, which rotor interacts with a stator of the drive motor, or in which a compressor wheel (40a) has a larger diameter than a rotor (44) of a drive motor or a larger one Has diameter than a turbine wheel (70a) of the turbine (40).

14. Device according to claim 13, in which the rotor (44) is arranged between the compressor wheel ~ (40a) and the turbine wheel (70a), or in which the compressor wheel (40a), a first axis section (43a), a rotor (44 ), a second axle section (43b) and the turbine wheel (70a) are formed in one piece, or in which a first bearing section (40b) is formed on the compressor wheel (40a) and a second bearing section (70b) is formed on the turbine wheel (70a), or wherein the rotor (44) is made of a non-ferromagnetic material, such as. B. aluminum, is formed and a ferromagnetic return element (44a) around the rotor (44) is attached and magnets (44b) on the return element (44a) are arranged.

15. Device according to one of the preceding claims, wherein the shear heat exchanger (10) has a volume shape having a central opening located in a central region, which forms a suction region (30), wherein a suction wall (31) from a first end of the central opening extending to a second end closed by a cover (32).

16. Device according to one of the preceding claims, in which the heat exchanger (10) is rotationally symmetrical, with an axis of symmetry of the heat exchanger (10) being aligned with an axis of the compressor (40) or an axis of the turbine (70) or an axis of the gas outlet ( 5) or the gas inlet (2) or with an axis of an intake area (30) essentially coincides.

17. Device according to one of the preceding claims, wherein the heat exchanger (10) comprises a countercurrent heat exchanger.

18. The device according to claim 19, which is designed so that in the heat exchanger (10) gas moves from the first heat exchanger inlet to the first heat exchanger outlet (12) from outside to inside and gas from the second heat exchanger inlet to the second heat exchanger outlet (14) from moved inside out.

19. Device according to one of the preceding claims, in which the heat exchanger (10) has a volume which has a countercurrent heat exchanger structure in an outer area and adjoins an intake area (30) in an inner area, the first heat exchanger inlet (11 ) is arranged externally on the outer area, the first heat exchanger outlet (12) being arranged on the inner area to direct gas into the intake area (30), the second heat exchanger inlet (13) also being arranged on the inner area and the second heat exchanger outlet (14) is also arranged on the outer area, with the first heat exchanger inlet (11) and the second heat exchanger outlet (14) being fluidically separated in the heat exchanger (10) and the first heat exchanger outlet (12) and the second heat exchanger inlet (13) in the heat exchanger (10) are fluidically separated.

20. Device according to one of the preceding claims, in which the heat exchanger (10) has interconnected first gas ducts (15) from the first heat exchanger inlet (11) to the first heat exchanger outlet (12) and interconnected second gas ducts (16) between the second heat exchanger inlet (13) and the second heat exchanger outlet (14), the first gas channels (15) and the second gas channels (16) being arranged in thermal interaction, the heat exchanger (10) having a first collection area (18 ) which connects the second gas ducts (16) on one side and which extends along the inner region and forms the second heat exchanger inlet (13), and has a second collection region (17) which connects the second gas ducts on another side and itself extends along an edge area of the outer area and forms the second heat exchanger outlet (14), wherein a suction wall (31) d delimited en first collection area and the first collection area (18) from a suction area (30) separates.

21. Device according to one of the preceding claims, wherein an electronic assembly (102) for supplying a drive motor for the compressor (40) with energy or for the delivery of control data to an element of the device or for acquiring sensor data from an element of the device is arranged in a region of the device that is designed to cool the electronic assembly group, or in which an electronic assembly (102) for the electrical supply of the device with energy and/or control signals in a Area between the turbine outlet (72) and the gas outlet (5) and a housing wall of the housing (100) outside of the gas outlet (5), or in which an electronic assembly (102) for the electrical supply of the device with energy and/or control signals in an area between a base of a compressor wheel (40a) of the compressor (40) and a base of a turbine wheel (70a) of the turbine, or in which an electronics assembly (102) for the electrical supply of the device with energy and/or control signals is arranged on a limiting element (71a) of a turbine inlet (71) of the turbine (70) is arranged, wherein the electronics assembly further except half of the turbine inlet (71) of the turbine (70), or in which an electronics assembly (102) for the electrical supply of the device with energy and/or control signals has an opening in the middle and is disc-shaped and is arranged around a stator of a drive motor for extends around the compressor (40) or is formed integrally with the stator, and is arranged, for example, in an area between a base of a compressor wheel (40a) of the compressor (40) and a base of a turbine wheel (70a) of the turbine (70). .

22. Air conditioning device with the following features: a room exhaust air connection (508); a room supply air connection (510); and A device according to any one of claims 1 to 23, wherein the room exhaust air connection (508) is coupled to the gas supply and the room supply air connection (508) is coupled to the gas discharge.

23. Air conditioning device according to claim 22, having the following features: a divider (502) for dividing air from the room exhaust air connection (508) into an exhaust air stream for an exhaust air duct (102a) and a feed stream (512); a conditioner (504) for conditioning the feed stream (512); and a combiner (506) for combining an output of the processor (504) with a supply air flow from a supply air duct (202a) in order to feed air into the room supply air connection (510), wherein the gas supply of the device is designed to combine the exhaust air flow from the exhaust air duct (102a ) and wherein the gas discharge is designed to deliver the supply air flow for the supply air duct (202a), or a divider (502) for dividing air from the room exhaust air connection (508) into an exhaust air flow for an exhaust air duct (102a) and a injection current (512); a combiner (506) for combining the feed flow (512) with a supply air flow from a supply air duct (202a) to obtain a combined air flow; and a processor (504) for conditioning the combined airflow to obtain a conditioned airflow that is fed into the room supply air port (510); and wherein the gas supply of the device is designed to receive the exhaust air flow from the exhaust air duct (102a), and wherein the gas outlet is designed to supply the supply air flow for the supply air duct (202a).

24. Air conditioning device according to claim 23, in which the processor (504) is designed to process the feed flow in terms of oxygen, moisture or disinfection.

25. Air conditioning device according to one of Claims 23 or 24, in which the divider (502) or the combiner (506) can be controlled in order to determine a ratio between an air volume in the exhaust air flow or an air quantity in the feed flow or a ratio between an air quantity of the output of the processor (504) and an air quantity of the supply air flow.

26. Air conditioning device according to one of claims 23 to 25, in which the combiner (506) has a fan (506a) to suck in the supply air flow in the supply air duct (202a), or in which the divider (502) has a fan to to pump the flow of exhaust air into the exhaust duct (102a), or in which the splitter (502) has a flow control, due to an action of the compressor (40) of the device, to draw air from the room into the splitter (502) via the room exhaust air connection (508) and move into the compressor inlet (41).

27. A method for operating a device for treating gas, with a compressor (40) with a compressor inlet (41) and a compressor outlet (42); a heat exchanger (10) with a first heat exchanger inlet (11), a first heat exchanger outlet (12), a second heat exchanger inlet (13) and a second heat exchanger outlet (14), wherein the heat exchanger is designed as a gas-gas heat exchanger; a turbine (70) having a turbine inlet (71) and a turbine outlet (72), an inlet interface for coupling the compressor inlet (41) and the first heat exchanger inlet (11) to a gas supply, the inlet interface (100) being on a has an exhaust gas inlet (102a) and a fresh gas inlet (102b) as the gas supply on the inlet side, and has a first inlet interface outlet (104) and a second inlet interface outlet (106) on an outlet side, the inlet interface (100) being formed , to connect the input side of the input interface (100) to the output side of the input ' interface (100) to couple; and an outlet interface (200) for coupling the turbine outlet (72) and the first heat exchanger outlet (12) to a gas discharge, the outlet interface (200) having a first outlet interface inlet ( 204); couple the input side of the output interface (200) to the output side of the output interface (200), comprising the steps of:

Feeding compressed gas from the compressor outlet (42) into the second heat exchanger inlet (13); and

Feeding gas from the second heat exchanger outlet (14) into the turbine inlet (71) and relaxing the gas in the turbine (70).

28. A method for producing a device for treating gas, with a compressor (40) with a compressor inlet (41) and a compressor outlet (42); a heat exchanger (10) with a first heat exchanger inlet (11), a first heat exchanger outlet (12), a second heat exchanger inlet (13) and a second heat exchanger outlet (14), the heat exchanger being designed as a gas-gas heat exchanger; and a turbine (70) with a turbine inlet (71) and a turbine outlet (72), with the following steps:

Connecting the compressor outlet s (42) to the second heat exchanger inlet (13); and

Connecting the second heat exchanger outlet (14) to the turbine inlet

(71);

Coupling the compressor inlet (41) and the first heat exchanger inlet (11) with a gas supply with an inlet interface, the inlet interface (100) having an exhaust gas inlet (102a) and a fresh gas inlet (102b) on an inlet side as the gas inlet, and on an output side a first input interface output (104) and a second input Interface output (106), wherein the input interface (100) is designed to couple the input side of the input interface (100) to the output side of the input interface (100); and coupling the turbine outlet (72) and the first heat exchanger outlet (12) to a gas discharge with an outlet interface (200), wherein the outlet interface (200) on an inlet side of the outlet interface (200) has a first outlet interface inlet ( 204); couple the input side of the output interface (200) to the output side of the output interface (200).