WO2022175403A1 - Vorrichtung und verfahren zum behandeln von gas und rlt-gerät - Google Patents
Vorrichtung und verfahren zum behandeln von gas und rlt-gerät Download PDFInfo
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- WO2022175403A1 WO2022175403A1 PCT/EP2022/053989 EP2022053989W WO2022175403A1 WO 2022175403 A1 WO2022175403 A1 WO 2022175403A1 EP 2022053989 W EP2022053989 W EP 2022053989W WO 2022175403 A1 WO2022175403 A1 WO 2022175403A1
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- Prior art keywords
- heat exchanger
- gas
- outlet
- inlet
- input
- Prior art date
Links
- 238000004378 air conditioning Methods 0.000 title claims description 26
- 238000009423 ventilation Methods 0.000 title claims description 19
- 238000000034 method Methods 0.000 title claims description 17
- 238000012545 processing Methods 0.000 title abstract description 4
- 230000008878 coupling Effects 0.000 claims abstract description 16
- 238000010168 coupling process Methods 0.000 claims abstract description 16
- 238000005859 coupling reaction Methods 0.000 claims abstract description 16
- 239000007789 gas Substances 0.000 claims description 200
- 238000001816 cooling Methods 0.000 claims description 23
- 239000007788 liquid Substances 0.000 claims description 19
- 238000010438 heat treatment Methods 0.000 claims description 18
- 230000001143 conditioned effect Effects 0.000 claims description 5
- 238000004519 manufacturing process Methods 0.000 claims description 4
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- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 2
- 229910052782 aluminium Inorganic materials 0.000 claims description 2
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 claims description 2
- 238000009833 condensation Methods 0.000 claims description 2
- 230000005494 condensation Effects 0.000 claims description 2
- 230000005294 ferromagnetic effect Effects 0.000 claims description 2
- 229910052760 oxygen Inorganic materials 0.000 claims description 2
- 239000001301 oxygen Substances 0.000 claims description 2
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- 238000004659 sterilization and disinfection Methods 0.000 claims 1
- 239000003570 air Substances 0.000 description 163
- 230000000694 effects Effects 0.000 description 10
- 230000007704 transition Effects 0.000 description 8
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 8
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- 239000003507 refrigerant Substances 0.000 description 3
- 239000012080 ambient air Substances 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 238000007791 dehumidification Methods 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
Definitions
- 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.
- AHU ventilation and air conditioning device
- 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.
- 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 .
- 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 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.
- the temperature reduction achieved by the turbine expansion is represented by the temperature difference between point 4 and point 5.
- the temperature difference that can be used for cooling is shown between point 5 and point 6.
- gas chillers 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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 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.
- 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.
- 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.
- 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.
- the heat exchanger which is a gas-gas heat exchanger
- the 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.
- the heat exchanger has a rotationally symmetrical shape with a first recuperator outlet in the middle of the recuperator.
- 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.
- 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.
- FIG. 1 shows a device for treating gas according to an embodiment:
- FIG. 2 shows a device for treating gas for “summer operation” according to an exemplary embodiment:
- FIG. 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
- 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
- FIG. 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;
- FIG. 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
- FIG. 10 shows a temperature-entropy diagram of the known cold-air refrigerating machine from FIG.
- 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.
- 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 .
- 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.
- 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.
- 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.
- 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.
- the compressor outlet 42 is connected to the second heat exchanger inlet 13 in the device 600 for treating gas.
- the second heat exchanger outlet 14 is connected to the turbine inlet 71 .
- the turbine output 72 is connected to the first output interface input 206 .
- the first heat exchanger outlet 12 is connected to the second outlet interface inlet 204 .
- 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.
- 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 .
- the output interface is designed to couple the input side of the output interface 200 to the output side of the output interface 200 .
- 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.
- the fixed coupling or the switchable coupling can take place via a further heat exchanger.
- 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.
- 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 Switzerlandaskanal 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.
- 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.
- 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.
- 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.
- 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.
- 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 .
- 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.
- 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.
- 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.
- 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.
- FIG. 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.
- handler 504 may be bypassed or omitted, as shown in phantom in Figure 6a.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- fan L 21 can also be placed at the outlet of the heat exchanger before connection A4.
- 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.
- 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.
- dehumidification of the supply air particularly for cooling operation e.g. B.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- 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.
- Fig. 5c 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.
- 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.
- 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 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. 8c shows a special embodiment of the heat exchanger 10 as a rotationally symmetrical heat exchanger in cross section.
- 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.
- 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.
- a blower which is not shown in FIG.
- FIG. 8b shows a schematic plan view of a preferred recuperator 10 with collection spaces on the secondary side as well.
- the device is completely closed at the top by a closed cover.
- Fig. 8b shows the situation when the lid is transparent.
- the intake area 30 is shown, which is delimited by the intake wall 31 .
- 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.
- 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.
- 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.
- the collection spaces 17, 18 are separated from the lines 15.
- 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 .
- 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.
- FIG. 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.
- 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.
- 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 recuperator extends a distance greater than 10 cm and preferably greater than 60 cm in the longitudinal direction of the cylinder.
- 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.
- the device is operated in such a way that gas-gas operation is achieved in the heat exchanger.
- the individual elements are designed and arranged in such a way that the special compressor-heat-exchanger-turbine arrangement is achieved.
- 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.
- 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.
- 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.
- 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
- 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.
- Embodiments are preferably used as bearings.
- 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.
- 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.
- FIG. 7b shows an exemplary preferred arrangement of an electronics assembly 102.
- 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.
- 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 .
- 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.
- annular assembly is shown in cross section in FIG. B. is mounted on the boundary 71a.
- 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.
- 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.
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Abstract
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EP22708875.4A EP4295091A1 (de) | 2021-02-17 | 2022-02-17 | Vorrichtung und verfahren zum behandeln von gas und rlt-gerät |
AU2022224389A AU2022224389A1 (en) | 2021-02-17 | 2022-02-17 | Apparatus and Method for Treating Gas and Air-conditioning Device |
US18/448,428 US20230384000A1 (en) | 2021-02-17 | 2023-08-11 | Apparatus and Method for Treating Gas and Air-Conditioning Device |
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DE102021201530.1A DE102021201530A1 (de) | 2021-02-17 | 2021-02-17 | Vorrichtung und verfahren zum behandeln von gas und rlt-gerät |
DE102021201530.1 | 2021-02-17 |
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US18/448,428 Continuation US20230384000A1 (en) | 2021-02-17 | 2023-08-11 | Apparatus and Method for Treating Gas and Air-Conditioning Device |
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US (1) | US20230384000A1 (de) |
EP (1) | EP4295091A1 (de) |
AU (1) | AU2022224389A1 (de) |
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WO (1) | WO2022175403A1 (de) |
Citations (3)
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GB2237373A (en) * | 1989-10-10 | 1991-05-01 | Aisin Seiki | Air conditioning systems |
US5121610A (en) * | 1989-10-10 | 1992-06-16 | Aisin Seiki K.K. | Air cycle air conditioner for heating and cooling |
DE102004063840B3 (de) * | 2004-12-23 | 2006-04-20 | Deh, Ulrich, Dr.-Ing. | Verfahren zur Klimatisierung eines Raumes und Kaltluft-Kältemaschinen-Anlagen zur Durchführung des Verfahrens |
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US4347714A (en) | 1980-07-25 | 1982-09-07 | The Garrett Corporation | Heat pump systems for residential use |
DE3544445A1 (de) | 1985-12-16 | 1987-06-25 | Bosch Siemens Hausgeraete | Kuehl- und gefriergeraet |
GB9409754D0 (en) | 1994-05-16 | 1994-07-06 | Air Prod & Chem | Refrigeration system |
US6381969B1 (en) | 1999-12-17 | 2002-05-07 | Honeywell International Inc. | ECS with 2-stage water separation |
US6301923B1 (en) | 2000-05-01 | 2001-10-16 | Praxair Technology, Inc. | Method for generating a cold gas |
US20060059936A1 (en) | 2004-09-17 | 2006-03-23 | Radke Robert E | Systems and methods for providing cooling in compressed air storage power supply systems |
US7621150B2 (en) | 2007-01-05 | 2009-11-24 | Delphi Technologies, Inc. | Internal heat exchanger integrated with gas cooler |
JP5934482B2 (ja) | 2011-08-26 | 2016-06-15 | 株式会社前川製作所 | 閉鎖型ガス循環式冷凍装置及びその運転方法 |
US10294826B2 (en) | 2015-08-12 | 2019-05-21 | Colorado State University Research Foundation | Ultra efficient turbo-compression cooling |
DE102020213544B4 (de) | 2020-10-28 | 2024-06-06 | JustAirTech GmbH | Gaskältemaschine, Verfahren zum Betreiben einer Gaskältemaschine und Verfahren zum Herstellen einer Gaskältemaschine mit einem Rekuperator um den Ansaugbereich |
-
2021
- 2021-02-17 DE DE102021201530.1A patent/DE102021201530A1/de active Pending
-
2022
- 2022-02-17 EP EP22708875.4A patent/EP4295091A1/de active Pending
- 2022-02-17 WO PCT/EP2022/053989 patent/WO2022175403A1/de active Application Filing
- 2022-02-17 AU AU2022224389A patent/AU2022224389A1/en active Pending
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2023
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GB2237373A (en) * | 1989-10-10 | 1991-05-01 | Aisin Seiki | Air conditioning systems |
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DE102004063840B3 (de) * | 2004-12-23 | 2006-04-20 | Deh, Ulrich, Dr.-Ing. | Verfahren zur Klimatisierung eines Raumes und Kaltluft-Kältemaschinen-Anlagen zur Durchführung des Verfahrens |
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EP4295091A1 (de) | 2023-12-27 |
US20230384000A1 (en) | 2023-11-30 |
DE102021201530A1 (de) | 2022-08-18 |
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