WO2022175411A1 - Échangeur de chaleur, procédé d'actionnement d'un échangeur de chaleur, procédé de production d'un échangeur de chaleur, machine frigorifique à gaz comprenant un échangeur de chaleur en tant que récupérateur, dispositif de traitement de gaz, et dispositif de ventilation et de climatisation - Google Patents

Échangeur de chaleur, procédé d'actionnement d'un échangeur de chaleur, procédé de production d'un échangeur de chaleur, machine frigorifique à gaz comprenant un échangeur de chaleur en tant que récupérateur, dispositif de traitement de gaz, et dispositif de ventilation et de climatisation Download PDF

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Publication number
WO2022175411A1
WO2022175411A1 PCT/EP2022/054002 EP2022054002W WO2022175411A1 WO 2022175411 A1 WO2022175411 A1 WO 2022175411A1 EP 2022054002 W EP2022054002 W EP 2022054002W WO 2022175411 A1 WO2022175411 A1 WO 2022175411A1
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WO
WIPO (PCT)
Prior art keywords
channels
heat exchanger
gas
outlet
recuperator
Prior art date
Application number
PCT/EP2022/054002
Other languages
German (de)
English (en)
Inventor
Holger Sedlak
Original Assignee
JustAirTech GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by JustAirTech GmbH filed Critical JustAirTech GmbH
Priority to EP22708876.2A priority Critical patent/EP4294639A1/fr
Priority to AU2022223205A priority patent/AU2022223205A1/en
Priority to JP2023549542A priority patent/JP2024506406A/ja
Publication of WO2022175411A1 publication Critical patent/WO2022175411A1/fr
Priority to US18/446,638 priority patent/US20230384038A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
    • F28F7/02—Blocks traversed by passages for heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0014—Recuperative heat exchangers the heat being recuperated from waste air or from vapors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/06—Constructions of heat-exchange apparatus characterised by the selection of particular materials of plastics material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/18—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes sintered

Definitions

  • Heat exchanger Method for operating a heat exchanger, method for producing a heat exchanger, gas refrigeration machine with a heat exchanger as a recuperator, device for treating gas and air conditioning device
  • the present invention relates to thermodynamic systems and in particular to heat exchangers for an air-to-air heat exchange process, e.g. B. for gas chillers can be used as a recuperator.
  • heat exchangers for an air-to-air heat exchange process e.g. B. for gas chillers can be used as a recuperator.
  • Air-to-air heat exchangers or gas-to-gas heat exchangers are needed in applications where there is a need to transfer thermal energy from one air or gas flow to another air or gas flow.
  • Such heat exchangers are used, for example, in heat recovery systems in which the flow of exhaust air from a building interacts with the flow of supply air into the building, so that the exhaust air is cooled in favor of the supply air or the supply air is heated in favor of the exhaust air. This avoids thermal losses, while at the same time an air exchange is achieved, ie used air is discharged and fresh air is supplied.
  • Such heat exchangers are z. B.
  • thermodynamic device designed as a plate heat exchanger, in which the air flow on the primary side, such as the exhaust side of the thermodynamic device is passed through a first number of plate-like channels, while the other air flow on the secondary side, ie z. B. the supply air side of the thermodynamic device is guided via a second number of plate-like channels without the two air or gas streams interacting directly, that is, being able to mix.
  • the warmer exhaust air flow gives off its thermal energy to the wall of the plate-like channels, while the supply air flow that is to be heated absorbs the thermal energy from this wall. This means that there is a continuous exchange of heat from the exhaust air flow to the supply air flow, without the two flows being able to mix from a molecular point of view.
  • An important aspect for such heat exchangers is the efficiency of the heat exchanger, i.e. how efficiently heat energy is transferred from one side to the other. Concomitant with efficiency is the volume of the heat exchanger, since the percentage of thermal energy transferred typically increases as the volume of the heat exchanger increases. For the volume, however, there is a limit on the one hand with regard to the possible size of the heat exchanger and on the other hand because an increasing size of the heat exchanger leads to an increasing flow resistance of the heat exchanger.
  • a gas-gas heat exchanger that is as good as possible should therefore have high efficiency on the one hand and low flow resistance on the other hand, since the heat exchanger has a good degree of heat transfer on the one hand and can be designed with a moderate volume, i.e. the smallest possible volume, on the other hand.
  • One area of use for such heat exchangers is as a recuperator in a gas refrigeration machine or cold-air refrigeration machine.
  • Cold air chillers are known and are used, for example, in space travel.
  • a cryocooler is disclosed in the technical publication "High-capacity turbo-Brayton cryocoolers for space applications", M. Zagarola et al., Cryogenics 46 (2006), pages 169 to 175.
  • a compressor compresses gas that circulates in the closed system. The compressed gas is cooled by a heat exchanger. The cooled gas is fed into a recuperator, which feeds the cooled gas to a turbine. Cold gas is emitted from the turbine, which absorbs heat via a heat exchanger or achieves a cooling effect. The gas leaving the heat exchanger providing the refrigeration effect, again warmer than the gas entering the same, is also fed into the recuperator to be reheated.
  • the temperature-entropy diagram of the cycle is known. An isentropic compression takes place through the compressor. Isobaric heat dissipation takes place through the heat exchanger for heat dissipation. Isobaric heat dissipation also takes place through the recuperator. Then an isentropic expansion takes place in the turbine. The cooling effect of the heat exchanger, in turn, represents an isobaric heat supply.
  • 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 relevant cycle without there being any transitions between the different states of aggregation.
  • very low pressures close to the vacuum are required for heat pumps, especially if climate-problematic refrigerants are to be dispensed with, which are necessary in the production, handling and maintenance during the Operating can lead to considerable effort, especially in terms of equipment. Nevertheless, the use of cold air chillers is limited.
  • a gas refrigerator is also described in German application 102020213544.4, which is not a prior publication and is hereby incorporated by reference.
  • a gas-gas heat exchanger is used as a recuperator in this gas refrigerating machine.
  • a gas-gas heat exchanger is used both for the heat source side and for the heat sink side and also for the recuperator. Especially when used as a recuperator, the efficiency of the heat exchanger makes a significant contribution to the efficiency of the overall system.
  • the object of the present invention is to create an improved heat exchanger concept.
  • the present invention is based on the finding that improved efficiency can be achieved by using a heat exchanger, also referred to as a fractal heat exchanger, with a first number of channels for a first fluid, which flow along a first direction of flow of the first fluid and extending in a first transverse direction, and having a second number of channels for a second fluid, extending along a second flow direction of the second fluid and in a second transverse direction, a wall structure is provided, which is formed such that it is with regard to the first number of channels for the first fluid varies transversely along the direction of flow, and/or that with regard to the second number of channels the wall structure in the second transverse direction, which is transverse to the second direction of flow of the second fluid, varies along the second direction of flow .
  • a heat exchanger also referred to as a fractal heat exchanger
  • the wall structure achieves that the first number of channels and the second number of channels are in thermal interaction with each other.
  • the wall structure is designed such that at a first point of the heat exchanger with respect to the first or second flow direction, the first transverse direction or the second transverse direction is or are different from the corresponding first or second transverse direction at a second point of the heat exchanger with respect to the first or second flow direction.
  • this means that the length of the channel varies along the direction of flow, preferably continuously, so that in preferred exemplary embodiments there are no sharp edges along the direction of flow that could lead to flow turbulence.
  • the wall structure is formed in such a way that the transverse direction of the channels changes from one point to another point from e.g. For example, it changes from a horizontal direction to a vertical direction and then progressively "goes back" to the horizontal direction again and then changes back to a vertical direction, and so on.
  • this is achieved in that a vector describing the transverse direction continuously "rotates", i.e. gradually increases in angle from a horizontal direction along the direction of flow, i.e. gradually z. B. transitions from an angle of 45 to an angle of 90, in which case the transverse direction is a vertical direction, i.e. perpendicular to the transverse direction at the beginning of the heat exchanger or at the previous point in relation to the flow direction of the heat exchanger, etc.
  • the heat exchanger is preferably designed such that the number of channels for the first fluid extends over a relatively large and preferably the entire width of a parallelepiped-shaped heat exchanger or around all or a large part of the circumference of a cylindrical heat exchanger, and that this also applies to the second number of channels for the second fluid, so that the channels have a relatively small height but a large width in the transverse or circumferential direction. A low flow resistance is thus achieved.
  • the wall structure is further designed such that when the channels change their transverse direction by e.g. B.
  • the channels extend over the entire height of a for example cuboid or cylindrical volume, so that again the channels are relatively narrow, but in the transverse direction at the second point are again relatively long, although the width again has small measure.
  • Such particularly flat but wide channels are particularly favorable for a heat exchange that takes place via the adjacent wall structure, but offer only a low flow resistance due to the high other dimensions.
  • the wall structure is preferably formed such that the first number of channels and the second number of channels extend completely through the volume at the first location in the first and second transverse directions and that the first number of channels and the second number of channels at the second location extend completely through the volume in the first and second transverse directions, the first and second transverse directions at the first location being different from the first and second transverse directions at the second location.
  • the two transverse directions can be vertical and in the second place horizontal in the case of a cuboid volume.
  • the two transverse directions may be vertical in the first place and circumferential in the second place, such that each channel has a radius and is circular in the case of a solid cylinder or spheroidal in the case of a sector of a cylinder.
  • the first two transverse directions are the longitudes of the sphere in the first place and the latitudes of the sphere in the second place.
  • the volume comprises at least 5 first and 5 second channels and in preferred embodiments at least 50 first and 50 second channels and in particularly preferred embodiments at least 100 first and 100 second channels.
  • all channels have a low flow resistance because they always extend through the entire volume again, i.e. at the first point, at the second point and along the direction of flow at further first or second points, the number of which depends on the number of periods .
  • the ongoing splitting and merging of the channels in a preferred embodiment also provides another valuable contribution to highly efficient heat transfer between the first and second fluids.
  • a large number of dividing sections are provided in the ducts in the transition from a horizontal transverse direction of the ducts to the vertical transverse direction of the ducts, in order to “divide” the relatively wide duct, which is therefore provided with a low flow resistance, into various partial ducts. .
  • This ensures that wall structures are provided in as many areas as possible within the channels in order to achieve good heat transfer from the first to the second number of channels.
  • the relatively long stretched channels in one direction only very small areas within the Reaches channels in which a fluid flowing in the channels is not in contact with a wall structure or is relatively far away from a wall structure.
  • the individual sub-channels are then reunited after they have been created by the splitting sections, but now in channels with a different transverse direction, ie a z. B. vertical transverse direction.
  • This in turn means that the fluid is only brought into contact with a wall structure in a relatively short flow section through the dividing sections in order to release the energy, and then to be reunited in a “large” channel so that the flow resistance nevertheless remains low .
  • the dividing sections also have the advantage that they lead to considerable stability of the heat exchanger, to the effect that the heat exchanger can be subjected to high pressures without it becoming problematically deformed. This is due to the additional support effect of the splitting and combining sections.
  • This large now z. B. vertical channel is then divided again in the further course and the individual sub-channels are in turn combined later in the course along the flow direction of the fluid in a turn large now but again horizontally located channel.
  • a certain number of channels which is preferably nested with the other number of channels in which the other fluid flows, which is intended to give off the heat or from where the heat transfer has to take place.
  • all the individual channels of the first number of channels are “short-circuited” to a certain extent along the heat exchanger, ie due to the constant division and combination of the channels in the individual regions.
  • all channels of the first fluid along the heat exchanger are preferably continuously short-circuited with one another, but not yet in a direct connection brought with the channels of the second number of channels in which the other fluid, such as the exhaust fluid flows.
  • the heat exchanger is designed as an elongated, for example cuboid or rectangular heat exchanger, so that the direction of flow is directed from a first end of the heat exchanger to a second end of the heat exchanger and the transverse direction is a direction perpendicular to this direction of flow.
  • the heat exchanger is designed as a rotationally symmetrical heat exchanger or as a heat exchanger in which the direction of flow is radial, i.e. from the outside to the inside in a cylindrical body, in which case the primary inlet takes place on the outside of the cylinder and the primary outlet takes place on the inside of the cylinder , and the secondary inlet and the secondary outlet also take place outside or inside the cylinder.
  • the first number of channels and the second number of channels are arranged interleaved with one another, so that there is always exactly one channel or at least one channel of the second number of channels between two channels of the first number of channels, regardless of this whether the first point of the heat exchanger or the second point of the heat exchanger or any point between the first and second point of the heat exchanger are considered.
  • the heat exchanger is also designed as a counterflow heat exchanger, so that at every point of the heat exchanger the first direction of flow of the fluid in the number of channels is aligned opposite to the second direction of flow, i.e. the direction of flow of the second fluid in the second number of channels.
  • the fluid can be a liquid, such as B. water, or a gas, such as. B. be air.
  • the design of the heat exchanger as a counterflow heat exchanger is achieved in that the primary inlet and the primary outlet on the one hand and the secondary inlet and the secondary outlet on the other hand are assigned or connected accordingly, with corresponding gas connections or air connections in the case of an air-to-air heat exchanger or with appropriate air connections for a gas refrigeration machine if the heat exchanger is used as a recuperator in a gas refrigeration machine.
  • the wall structure is formed such that portions of the wall structure can be thought of as spirals that are "tailored" to fit into an overall rectangular pattern compared to a true circular spiral.
  • these individual "areas" are not separated from one another in terms of material, but are made in one piece with one another, as can be achieved, for example, by certain three-dimensional printing processes, or connected to one another in a gas-tight manner by means of a connecting means, such as by gluing, soldering, etc . can be reached.
  • the heat exchanger which is also known as a fractal heat exchanger due to its structure, provides a transparent and logical implementation that is also characterized by low flow resistance and high efficiency due to an optimally even distribution of the heat transfer effect over the entire volume of the heat exchanger.
  • One application of the heat exchanger according to the invention is the use of the same as a recuperator and/or as a heat exchanger in a gas refrigeration machine that is constructed in a particularly compact manner in order to prevent losses through lines, in particular in the recuperator or in the connection between the recuperator and the compressor.
  • the recuperator or heat exchanger is arranged in such a way that it extends around an intake area of the compressor, the intake area of the recuperator being delimited by an intake wall.
  • This integrated arrangement between the compressor with the intake area on the one hand and the recuperator on the other hand means that a compact structure can be achieved with optimal flow conditions in order to suck in gas present in the primary side of the recuperator through the recuperator.
  • the effect of the recuperator is important for the efficiency of the entire gas refrigeration machine, which is why the recuperator is arranged so that it extends at least partially and preferably completely around the intake area. This ensures that a considerable amount of gas is sucked out of the recuperator from all sides over the entire intake area, which extends away from the compressor inlet and is delimited by the recuperator by the intake wall.
  • the recuperator can take up a considerable volume, a compact construction is nevertheless achieved because the compressor is directly integrated with the recuperator.
  • this implementation also ensures that there is enough space for the secondary side in the recuperator, which must be in thermal interaction with the primary side in the recuperator, to carry the currents of the on the primary side to bring flowing warm gas and the streams of flowing on the secondary side warmer gas well in thermal interaction.
  • a direct current or countercurrent principle is used in the recuperator in order to achieve particularly good efficiency in this component.
  • the first inlet of the recuperator into the primary side thereof represents a gas or air inlet, so that the gas refrigerator can be operated in an open system.
  • the turbine outlet or the gas outlet is then also directed into a space, for example, into which the cooled air or, generally speaking, the cooled gas is brought.
  • the gas inlet on the one hand and the gas outlet on the other hand can be connected via a line system and a heat exchanger to a system that is to be cooled. Then the gas refrigerator according to the present invention is a closed system.
  • the entire gas refrigeration machine is preferably installed in a housing that is typically rotationally symmetrical, at least in its "inside”, with an upright shape and a greater height than diameter, i.e. as a slim, upright shape.
  • This housing contains both the gas inlet and the gas outlet and the recuperator, the compressor and the turbine and preferably also the heat exchanger.
  • the compressor is preferably arranged above the turbine.
  • the compressor includes a radial wheel and the turbine also includes a turbine wheel, wherein the compressor wheel and the turbine wheel are arranged on a common axis, and this axis further includes a rotor of a drive motor interacting with a stator of the drive motor.
  • the rotor is preferably arranged between the compressor wheel and the turbine wheel.
  • the recuperator is arranged in an outer area of the volume of the gas engine and the compressor inlet is arranged in an inner area of the volume of the gas engine, with the intake area also being located in the inner area of the volume.
  • the suction region preferably has an opening area that increases continuously from a first end to the second end, so that the suction wall is designed to be continuous, ie preferably without edges.
  • the end with the smaller opening area is with the compressor inlet connected and the end with the larger opening area is closed, so that the operation of the compressor creates a suction effect in the suction area, which extends via the primary outlet of the recuperator, which is fluidically coupled to the suction area, through the recuperator to the primary inlet of the recuperator, the is either designed directly as a gas inlet or is connected to a gas outlet in the housing.
  • a control chamber of the compressor is arranged in such a way that it guides the compressed gas outwards from the middle of the volume of the gas engine and feeds it there directly into a primary inlet of the heat exchanger.
  • the heated gas flows through the heat exchanger from the outside in and from there enters the secondary inlet or second inlet of the recuperator, which is preferably located inside the volume and extends around the intake area and in particular around the intake wall, but fluidly from the intake area is separated.
  • the gas fed into the secondary inlet flows from the inside to the outside in the secondary side of the recuperator and thus enables a counterflow principle, which is thermally particularly favorable, and then flows from the outside with respect to the recuperator, preferably into the intake area of the turbine, with the gas flowing from the outside to the inside to relax over the turbine wheel in the air outlet, which is preferably formed as a large area at the bottom of the gas refrigerator.
  • the gas inlet is formed in the lateral upper area of the gas refrigeration machine, namely by a large number of perforations which are connected to corresponding gas ducts and which form the gas inlet or the primary inlet into the recuperator.
  • Electronics required for controlling and operating the gas refrigerator are preferably arranged in an area below the turbine intake area, ie next to the air outlet, so that the cooled air can provide a cooling effect on electronic elements via the turbine outlet wall.
  • a cold-air chiller is technically less complex and therefore also less error-prone, for example in comparison to a heat pump.
  • higher efficiency can be expected since no work is required to move a significant amount of liquid refrigerant around the circuit.
  • One aspect of the present invention relates to the placement of the recuperator at least partially around the intake area.
  • Another aspect of the present invention relates to the arrangement of the Reku perators, the compressor, the heat exchanger, and the turbine in a single housing z. B. can be cylindrical and z. B. has an oblong shape that has a height that is greater than the diameter.
  • a further aspect of the present invention relates to the specific implementation in which the compressor is arranged above the turbine in order to achieve an optimal flow effect of the gas in the gas refrigerator.
  • a further aspect of the present invention relates to the placement of the compressor wheel and the turbine wheel on an axis on which the rotor of the motor is also arranged in order to create an optimal and efficient transmission of the power from the turbine to the compressor to save drive energy to be supplied as far as possible.
  • a further aspect of the present invention relates to the implementation of a rotationally symmetrical recuperator with the compressor and the turbine, whose axis of rotation coincides with the axis of the recuperator, whether to achieve efficient flow guidance in the gas refrigerator.
  • a further aspect of the present invention relates to the preferred arrangement and design of the heat exchanger in the gas refrigerator in order to achieve a space-saving gas refrigerator with efficient conversion of thermal energy.
  • Another aspect of the present invention relates to the placement of an electronic assembly in a cool area of the gas refrigerator z. B. between the compressor wheel and the turbine wheel or in thermal interaction with the restriction of the turbine inlet on the path of the gas from the recuperator outlet into the turbine or in the vicinity of the particularly cool turbine outlet.
  • a further preferred application of the heat exchanger of the present invention is its use in a compressor-heat-exchanger-turbine combination in order to obtain a simple and at the same time robust measure for treating gas, the heat exchanger being designed as a gas-gas heat exchanger and on its primary side is coupled between the compressor outlet and the turbine inlet. the 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.
  • 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 such as a temperature detection or a target temperature detection of a supply air for a room, can take place automatically using a temperature sensor or a flow sensor or both sensors, or can be derived manually or dependent 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 special rotor of the drive motor is 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 also 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 forming the primary side, are in thermal interaction with a plurality and in particular a large number of flow channels forming 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.
  • energy is extracted from the fresh air supplied and removed from the system via the exhaust air, which is already warm.
  • relatively "hot" fresh air can be used to generate even hotter exhaust air from the exhaust air, so that 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 feed-in current is preferably processed by a processor beitet, such as modified in terms of moisture, disinfected or enriched with oxygen but typically not thermally so actively changed in terms of 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. 1a shows a cross-sectional view of a heat exchanger at a first location along a direction of flow
  • 1b shows a cross-sectional view of the heat exchanger at a second location along a flow direction
  • 1c shows a cross-sectional view of the heat exchanger at a third location along a direction of flow
  • 1d shows a cross-sectional illustration of the heat exchanger at a fourth point along a direction of flow
  • 1e shows a cross-sectional view of the heat exchanger at a fifth point along a direction of flow
  • FIG. 2a shows a cross-sectional illustration of the heat exchanger at a sixth point along a direction of flow
  • FIG. 2b shows a cross-sectional illustration of the heat exchanger at a seventh point along a direction of flow
  • 2c shows a cross-sectional illustration of the heat exchanger at an eighth point along a direction of flow
  • 2d shows a cross-sectional illustration of the heat exchanger at a ninth point along a direction of flow
  • FIG. 3a shows a perspective representation of a section of the heat exchanger with an explanation of the locations of FIGS. 1a to 2d;
  • FIG. 3b shows a top view of the representation of FIG. 3a
  • FIG. 4a shows a plan view of a "half" of the representation of FIG. 3b
  • FIG. 4b is a perspective view of the top view of FIG. 4a;
  • Fig. 5a is a plan view of an "uncropped" representation of one half of Fig.
  • Fig. 5b is a perspective view of the top view of Fig. 5a;
  • Figure 5c is a "cropped" representation of a plan view of a coil of Figure 5a;
  • Figure 5d is a perspective view of the "cut coil" of Figure 5c;
  • FIG. 6a shows a perspective view of a heat exchanger according to an embodiment
  • FIG. 6b shows a further illustration of the heat exchanger from FIG. 6a
  • FIG. 7a shows a plan view of a cylindrical heat exchanger with radial directions of flow
  • Figure 7b is a cross-sectional view of the heat exchanger of Figure 7a at a point where the channels in the volume have a transverse direction which is horizontal;
  • FIG. 7c shows a general representation of a heat exchanger with a primary inlet, primary outlet, secondary inlet and secondary outlet according to the countercurrent principle
  • Fig. 8a shows an alternative implementation of the heat exchanger at the location relative to Fig. 2a, but with a greater number of vertical channels than in Fig. 2b;
  • Figure 8b shows the heat exchanger of Figure 8a but at the point relative to the heat exchanger of Figure 2b;
  • Fig. 9a shows an alternative implementation of the heat exchanger of Fig. 2a, but with more horizontal and vertical channels than in Fig. 1e;
  • Fig. 9b shows the heat exchanger at the location of Fig. 2d, but with a larger number of horizontal channels than in Fig. 2d;
  • FIG. 10 shows a basic circuit diagram of a gas refrigerator according to an embodiment of the present invention
  • 11a shows a sectional view of a fully integrated gas refrigerator with a heat exchanger according to the invention as a recuperator;
  • 11b shows a sectional illustration of a fully integrated gas refrigerator according to a further exemplary embodiment of the present invention with an alternative arrangement of the electronics assembly;
  • FIG. 12a shows a schematic representation of a section of a preferred recuperator with collection spaces on the secondary side
  • 12b shows a schematic plan view of a preferred recuperator with collection spaces on the secondary side
  • FIG. 13 shows a device for treating gas according to an embodiment
  • Figure 15 shows a device for treating gas according to a further exemplary embodiment for “winter operation”;
  • Figure 16a shows an implementation of the input interface or the output interface;
  • 16b shows a control table for configuring the interfaces in summer or winter operation
  • Figure 17a shows an alternative implementation of the device for treating gas
  • Fig. 17b shows a control table for controlling the switches in Fig. 17a;
  • 17c shows an implementation of the input or the output interface as a two-way switch
  • FIG. 18a shows an exemplary embodiment of a ventilation and air-conditioning device that can be coupled to the device for treating gas
  • FIG. 18b shows a further exemplary embodiment of a ventilation and air conditioning device which can be coupled to the device for treating gas
  • 19a shows a perspective view of a preferred compressor-turbine combination
  • FIG. 19b is a side view of the preferred compressor-turbine combination of FIG. 19a;
  • 20a 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;
  • 20b shows a schematic plan view of a preferred recuperator with collection spaces on the primary side and the secondary side;
  • Fig. 1a shows a cross-sectional representation or "starting view" of a heat exchanger having a first number of channels 101a, 101b, 101c for a first fluid, which extend along a first flow direction of the first fluid, and which also extend in a first transverse direction extend.
  • the first direction of flow goes into the plane of the drawing or out of the plane of the drawing.
  • the first transverse direction extends parallel to the wall structure 200a, 200b, 200c, 200d and 200e.
  • the first direction of flow is therefore either the direction in the z-direction of the coordinate system in Fig.
  • the first transverse direction is preferably the x-direction, but could also be the y-direction.
  • the second number of channels comprises channels 102a, 102b, 102c and the second number of channels is for a second fluid, the second number of channels extending along a second flow direction of the second fluid and in a second transverse direction.
  • the second transverse direction is preferably also the same transverse direction as the first transverse direction when the channels are parallel and interleaved.
  • alternative implementations could also be designed with non-constant wall thickness or multiple walls between the channels, where e.g. B. the first transverse direction would extend in an x-y direction, e.g. B. would be +30° and the second channels would extend in the transverse direction by -30°, for example.
  • 1a is preferred, in which the channels are interleaved with one another, so that a channel of the other number is always arranged between two channels of one number.
  • a channel of the other number is always arranged between exactly two channels of the other number, as is shown, for example, in FIG. 1a, in which the channel 102b is arranged between the channels 101a and 101b.
  • the first transverse direction varies along the first flow direction and the second transverse direction also varies along the second flow direction, as can be seen by looking at FIGS Fig. 3a is illustrated using an example section, which is illustrated in Figs. 1a to 2d by the four individual regions arranged side by side, which are illustrated at 301, 302, 303 and 304 in Fig. 1b, for example.
  • points are included in FIGS. 1a to 2d. is drawn around which the arrows are shown to symbolize an axis of rotation of a respective spiral around which individual wall structure areas extend along the extension of the heat exchanger in the respective direction of flow or counter to the respective direction of flow.
  • the wall structure 200a to 200e is designed in such a way that at the first location (Fig. 1a) of the heat exchanger with respect to the first or second flow direction there is a first transverse direction or a second transverse direction which is aligned along the x-direction or the y-direction .
  • the two transverse directions are preferably the same at the first point, that is to say they are formed, for example, in the x-directions of FIG. 1a.
  • the first and second transverse directions are now no longer aligned in the x-direction but in the y-direction.
  • the channels no longer extend horizontally as in Fig. 1a, but now vertically as in Fig. 1c.
  • the wall structures 200a to 200e of FIG. 1a have now changed into a vertical wall structure 202a, 202b, 202c, 202d. Nevertheless, the two fluid regions “1” for the first number of channels and “2” for the second number of channels are separated from one another throughout and are designed as they are drawn in FIG. 1c.
  • FIG. 1a to 2d represent only the detail of a section of the heat exchanger, which can be made much larger, for example with 10 to 100 channels per number of channels or with an even larger number and length or a radius as required for the corresponding application.
  • FIG. 1b shows the “transition” between the formation of horizontal channels and the formation of vertical channels, ie between the cross section of FIG. 1a and the cross section of FIG. 1c.
  • the individual areas 301, 302, 303, 304 are rotated from their position in FIG. 1a, for example in the respective direction of rotation, with the areas constantly “touching” each other.
  • the channel 102b of the second number of channels is thus “divided” into sub-channels 103a, 103b, with the now rhombic wall structure shown in FIG. Accordingly z. B. the overlying channel 101a of Fig. 1a divided into the sub-channels 104a, 104b, 104, again in that the individual wall structure areas of Fig.
  • FIGS. 1e and 1a it now becomes apparent that the “occupancy” of the individual channels has now changed.
  • the first fluid was present in Figure 1a
  • the second fluid is now present in Figure 1e and vice versa.
  • wall structure areas 200a and 200b in FIG. 1e there is now a channel of the second number of channels, while between these structure areas in FIG. 1a there was a channel of the first number of channels.
  • the further development of the heat exchanger along the first and second flow direction is shown in Fig. 2a.
  • the corresponding vertical channels are again divided into individual vertical sub-channels, so that vertical sub-channels are already "touching" but are not yet united. This combination takes place in the transition from FIG. 2a to FIG.
  • the "occupancy" of the individual structures is opposite to the occupation in FIG. 1c.
  • the structures 202d and 202c in FIG. 2b is a channel of the first number of channels for the first fluid, as represented by “1”, while between these two structures in FIG. 1c there is a channel of the second number of channels was present for the second fluid.
  • FIG. 2c The vertical channels of FIG. 2b are in turn, as shown in FIG. 2c, again divided into individual vertical partial areas, partial areas of the same fluid area now already touching horizontally but not yet being united. This union then takes place again in the transition between FIG. 2c and FIG. 2d, and the "occupancy" of the individual areas is now exactly the same as in FIG. 1a.
  • the heat exchanger therefore has a period T in the first or second flow direction in preferred exemplary embodiments of the present invention.
  • the starting situation is shown in FIG. 1a, where the period starts.
  • Figures 1b to 2d each indicate an eighth of the period. If a period is designated as 360°, an angle of 45° or one eighth of a period is "swept over" from each partial image to the next partial image.
  • a perspective view of the heat exchanger is shown in Figures 6a and 6b, where the "frame" 600 for the heat exchanger can be the wall portion of the heat exchanger.
  • the frame is open at the top (and bottom) through openings which in an actual implementation are closed.
  • the heat exchanger in FIGS. 6a and 6b can also function as a section in a much larger heat exchanger structure without the frame 600 .
  • Fig. 6a the same wall structures of Fig. 1a are shown. Furthermore, the individual horizontal channels, which are occupied by the corresponding fluids, are drawn in. In particular, the channels labeled “1” are occupied by the first fluid and the channels labeled “2” are occupied by the second fluid. The direction of flow is into or out of the image plane shown in Figure 6a.
  • the heat exchanger is used as a counterflow heat exchanger, so that in the channels marked "1" the fluid flows into the plane of the drawing, and that in the channels marked with "2" are designated, the fluid flows out of the plane of the drawing.
  • the corresponding arrangement of the vertical channels is shown through the openings shown in the frame 600 at the top.
  • the position of the heat exchanger shown at 602 in or against the corresponding direction of flow shows the position in FIG. 1c, ie after a quarter period or after a 90° rotation. Accordingly, the location shown at 604 shows the situation of Figure 2b.
  • Position 603 is located between position 602 and 604 in the direction of flow of the heat exchanger, at which, as shown in FIG. 1e, the channels are again horizontal, as shown in FIG. 6a, but with different occupancies in terms of height of the individual structures 200a to 200e.
  • the structures 200a to 200e do not of course extend continuously, but rather vary as illustrated with reference to FIGS. 1a to 2d.
  • FIG. 6a shows a somewhat enlarged illustration of FIG. 6a.
  • the four elements 301, 302, 303, 304 are drawn in schematically with respect to FIG 6b for the situation to a certain extent “inside” the heat exchanger, namely at a position of 45° rotation or an eighth period.
  • FIG. 7a and 7b show a plan view of a heat exchanger which, in contrast to FIG Fluid and from the inside out for the other fluid when the heat exchanger of Fig. 7a and Fig. 7b is designed as a counterflow heat exchanger.
  • Fig. 7b shows a schematic cross-section along the location shown in Fig. 7a.
  • the cross-section in Figure 7b is illustrative only should be what the directions of flow are.
  • the extent of the channels along the direction of flow is exactly the same as that set forth with reference to FIGS. 1a to 2d or as set forth with reference to FIGS. 8a to 9b.
  • the channels therefore change along the flow direction from a horizontal extension parallel to a cover 700 of the heat exchanger or to a bottom 702 of the heat exchanger of FIG. 7a into vertical channels.
  • this constant back and forth change from channels extending in one horizontal transverse direction to vertical channels extending in the transverse direction is not plotted in Figure 7b.
  • FIG. 7a shows how the number of channels per angular range can change from the outside to the inside or from the inside to the outside. More channels can be converted into fewer channels or vice versa at certain interfaces per angular range, in order to adapt the situation to the fact that the diameter of the heat exchanger, when fluid flows through it in the radial direction, decreases from the outside to the inside.
  • the radial and also circumferential lines shown in FIG. 7a are therefore not visible when the cover 700 is in place, but would be visible if the heat exchanger were viewed without the cover or were "cut open” at any point on its height. Due to the changing transverse direction of the channels, however, the radially extending lines symbolizing the individual channels would not be visible in FIG. 7a, since there is an alternation between horizontally and vertically extending channels all the time.
  • the lines in FIG. 7a therefore only schematically show channels in a top view, which are operated in the radially directed direction of flow.
  • the vertical channels also have the advantage that a discharge of condensed liquid, such. B. condensation, can be easily achieved. Since there are two areas within a period that run vertically through the entire heat exchanger from top to bottom, condensed water, which will typically appear as small drops at the splitting sections, will simply flow off downwards.
  • the wall structure is preferably formed such that the first number of channels or the second number of channels have one or more sections which are vertical in the direction of operation of the heat exchanger and which extend through the heat exchanger from top to bottom, and at the bottom of the one or a condensed liquid discharge device is formed in the plurality of vertical areas in order to discharge condensed liquid present in the one or more vertical areas.
  • the device includes the water collection device, such as a drip tray at the bottom of the heat exchanger, preferably for each of the two pressure zones, and a pump or other device for water removal.
  • the water collection device such as a drip tray at the bottom of the heat exchanger, preferably for each of the two pressure zones, and a pump or other device for water removal. This allows easy handling and early removal of the condensed water, so that ice formation in the heat exchanger or other problems with condensed liquid can be avoided.
  • FIG. 7c shows a schematic view of a heat exchanger with a primary input P.IN 710, a primary output P.OUT 720, a secondary input S.IN 730 and a secondary output S.OUT 740.
  • the inputs and outputs 710 to 740 are assigned in such a way that in the heat exchanger of FIG. B. the exhaust fluid flows from left to right and the fluid on the secondary side, ie z. B. the supply air fluid flows from right to left.
  • a first collection area 711 is coupled to the primary inlet, in which the primary fluid is distributed to the first number of channels 101a, 101b, 101c.
  • the primary collection area 711 typically extends around the outside of the heat exchanger and is also shown in FIG. 7a.
  • the second collection area 731 is designed in such a way that it guides the second fluid into the channels 102c, 102b and 102a, so that the first and second fluids flow through the heat exchanger wall structure in the area between the collection area in countercurrent.
  • the direction in the collection areas can be different, so if z. B. the primary side and the secondary side are charged differently than in other directions, and in different other positions of the heat exchanger, the inputs / outputs are attached.
  • the collection areas 711, 721, 731, 741 are fluidically separated from one another, apart from being connected by the respective channels.
  • the collection area 711 and the collection area 721 are connected only through the respective channels, and the collection areas 731 and 741 are also connected only through the respective channels.
  • the collection area 711 is completely fluidically separated from the collection area 741 by the wall structure, which also applies to the collection area 721 and the collection area 731, so that no short circuits occur here.
  • Another aspect of the present invention is that due to the fact that vertical and horizontal channels (in the transverse direction, ie transverse to the direction of flow) alternate regularly, the number of channels along the direction of flow can easily be changed. In the extreme case, after a period of e.g. B. 90 °, so when a change from horizontal channels to vertical channels has taken place, the number of horizontal and / or vertical channels changed, so increased by one or more channels. For example, by a smaller subdivision of the wall structures, as z. B. is shown with reference to Fig. 8a and Fig. 9a, a gradual reduction of the channels can be achieved. This gradual reduction of channels in favor of a larger number of channels is advantageous in order to implement a collection area that can be "connected" well.
  • a heat exchanger can be connected particularly well when there is only a single first channel and a single second channel at the interface, ie at the end of the heat exchanger.
  • the first channel would then comprise the upper half and the second channel would comprise the lower half.
  • the number of partial areas "to be rotated" and thus the number of channels would be increased after 90° or only after 180°, e.g. B. in any ratio that does not have to be an integer ratio.
  • This increases the number of channels per unit volume in order to go from very large channels that can be easily connected to very small channels that provide a good heat transfer coefficient. This can be achieved without special measures that would fall outside the pattern according to the invention.
  • the collection areas at the connections are also just sections of the canal which are basically designed in the same way as channel sections inside the structure, but have a larger volume in favor of their smaller number.
  • FIG. 8a shows, by way of example, the situation that exists when, instead of the situation in FIG. 2a, starting from the situation in FIG. 1e, the number of vertical channels is to be increased.
  • the dividing sections are increased in the horizontal direction. This results in narrower vertical channels, as can be seen in FIG. 8b compared to FIG. 2b, but in favor of a larger number of vertical channels. This is achieved simply by doubling or, generally speaking, enlarging the diamond-shaped partition structures shown in FIG. 2a in the horizontal direction.
  • FIG. 9a shows the procedure which is as shown in FIG. 9a.
  • Fig. 9a is compared with Fig. 2a, the diamond structure is enlarged in horizontal and vertical directions, so that more horizontal channels are achieved than is shown in Fig. 1e, for example.
  • FIG. 9a shows the situation which is reached when starting from the situation in FIG. 8b one “continues”. 9a thus shows the situation that, even with an interface with vertical channels, the distance is reduced due to the enlargement of the corresponding “axes of rotation” for the spiral-shaped or helical individual elements in order to obtain a smaller-scale structure.
  • 7a also shows a situation where, as shown for example at 760, the number of channels per angle element a is increased from five channels in the outer area of the heat exchanger to four channels in the inner area of the heat exchanger. This conversion can be carried out either at a horizontal or at a vertical "intersection", i.e. generally at a corresponding point of the heat exchanger where the channels run horizontally or vertically.
  • a situation is shown, for example, in which there is a transition from an angle element ⁇ , which has three channels, to two channels. It can be seen that any transition, from e.g. B. nine channels to eleven channels, etc., so can be made in any ratio, the number of channels in the direction of flow can be increased or verklei nert, depending on how the heat exchanger is traversed.
  • FIGS. 3a to 5d A preferred implementation of the wall structure of the heat exchanger is described below with reference to FIGS. 3a to 5d.
  • the wall structure of the heat exchanger can be produced with individual areas that have a spiral or helical shape along the direction of flow or “develop” in a certain shape along the direction of flow, it should be pointed out that a preferred form of manufacture of the heat exchanger by means of rapid prototyping or by means of 3D printing.
  • the individual partial areas can also be produced individually and then connected to one another, for example by gluing, soldering or some other way of connecting individual parts or groups of parts.
  • the manufacturing method is therefore not limited to 3D printing, although 3D printing is preferred.
  • FIG. 3a shows the section of the heat exchanger from FIGS. 1a to 2d, which is represented by the elements 301, 302, 303, 304.
  • the development of these elements along the direction of flow is given in a three-dimensional representation in FIG. 3a, which shows which cross-sections in the respective figures correspond to a corresponding position along the direction of flow of the heat exchanger of FIG. 3a.
  • a period T corresponds to the development of FIG. 1a to FIG. B. with a greater or lesser number of horizontal and / or vertical channels, as shown in Figures 8a to 9b.
  • the implementation of the present invention can be scaled arbitrarily in terms of size, depending on the embodiment, since the actual length in millimeters, for example, of a period can be set arbitrarily.
  • the length of a period less than 10 cm and preferably less than 2 cm is preferred in order to obtain a small-scale structure, which is also characterized in particular by the fact that the wall structure is relatively thin in order to ensure good heat transfer from the first fluid to the second fluid to reach.
  • the thermal conductivity of the wall structure alone is not as critical as, for example, in a plate heat exchanger, because the channels are constantly splitting and rejoining and the position of the channels is constantly changing.
  • FIG. 3b shows a top view of the four individual areas 301, 302, 303, 304, the corresponding rotations and angle information in FIGS. 1a to 2d corresponding to the corresponding angles of rotation between 0° and 360° in the top view of FIG. 3b.
  • FIG. 4a shows half of the representation of FIG. 3b and
  • FIG. 4b shows a perspective representation of the top view of FIG. 4a and again half of FIG. 3a.
  • FIG. 5a to 5d show the formation of an individual structure of the four structures in FIG. 3a and the two structures in FIG. 4b.
  • a circular shape is assumed, as shown in the plan view in FIG. 5a.
  • the circular shape developed as a spiral is shown in perspective in Fig. 5b.
  • the individual elements are rectangular, starting from Fig. 5a the circular shape is "cut” into a rectangular shape which, when it is “rolled out” as a screw in analogy to Fig. 5b, has the perspective shape as shown in Fig. 5d.
  • FIG. 3a shows four such spirals or helical structures as shown in FIG. 5d, which is why FIG. 1a is a cross-sectional view, for example of a heat exchanger, which reproduces from many such structures of FIG. 5d built up on one another or fastened to one another.
  • the wall structure With regard to the dimensioning of the wall structure, it is designed to have a thickness of between 0.01 mm and 1 mm between one channel of the first number of channels and an adjacent channel of the second number of channels, or by a proportion of 5 to 40 percent of the volume of the heat exchanger and preferably a proportion of 15 to 20% of the volume of the heat exchanger.
  • the heat exchanger is designed to have at least 2 periods. It is also preferred to use many periods, in the range of 10,000 to 10,000,000 per liter of volume of the heat exchanger. Particularly preferred dimensions are in the range from 100,000 to 300,000 cycles per liter of volume.
  • the numbers of channels can be set in high ranges, such as in the range of more than one million, or in ranges between 100,000 and 2 million.
  • the number of periods can be set in the above range, or in the range from 5 to 8 if a particularly low flow resistance is desired.
  • the heat exchanger described above has been described as an air-to-air heat exchanger or gas-to-gas heat exchanger, this heat exchanger can also be operated as a liquid-to-gas or liquid-to-liquid heat exchanger.
  • the structures through which the respective liquid flows are dimensioned differently depending on the viscosity of the liquid, but this can easily be adapted depending on the application situation due to the size-independent shaping of the wall structure according to the invention.
  • the heat exchanger according to the invention can also be used in any application where a highly efficient heat exchanger is required, such as in the application described as a recuperator in the form of a gas refrigerator or as a heat exchanger in an air heat recovery device or in any other application where z .
  • B. Plate heat exchangers or other heat exchangers can be used in counterflow or in parallel flow.
  • FIGS. 10 to 12b The preferred implementation of a gas refrigerator is shown below with reference to FIGS. 10 to 12b.
  • the gas refrigerator shows a gas refrigerator with a gas inlet 2 for gas to be cooled, ie “warm” gas, and a gas outlet 5 for cooled, ie “cold” gas.
  • the gas is normal air, such as room air in an office, a data center, a factory, etc.
  • the gas refrigerator can be operated as an open cycle by introducing air via the gas inlet 2 at a point in is sucked in from a room and air that has been cooled is discharged into the room at another location in the room.
  • the present invention can also be implemented as a closed system, in which the gas outlet 5 is connected to a primary side of a heat exchanger and the gas inlet 2 is also connected to the primary side of the heat exchanger, but there to the "warm" end, and the secondary side of this Heat exchanger is connected to a heat source.
  • the gas refrigerator also includes a recuperator 10 with a first recuperator input 11, a first recuperator output 12, a second recuperator input
  • the route from the first recuperator input 11 to the first recuperator input 12 represents the primary side of the recuperator, and the route from the second recuperator input 13 to the second recuperator output
  • a compressor 40 with a compressor inlet 41 and a compressor outlet 42 is provided.
  • the compressor inlet 41 is coupled to the first recuperator outlet 12 via an intake region 30 which is delimited by the intake wall 31 .
  • a heat exchanger 60 which is occasionally used as another Heat exchanger is referred to to distinguish it from the recuperator heat exchanger, provided with a heat exchanger inlet 61 and a heat exchanger outlet 62.
  • the first heat exchanger inlet 61 and the first heat exchanger outlet 62 form the primary side of the heat exchanger 60.
  • the second heat exchanger inlet 63 and the second heat exchanger outlet 64 form the secondary side of the heat exchanger 60.
  • the secondary side is connected to a heat sink 80, which can be arranged, for example, on a roof if the gas refrigerator is used for cooling, or which can be underfloor heating if the gas refrigerator is used for heating, a pump 90 also being provided in the secondary side, which is preferably arranged between the heat sink 80 and the second heat exchanger inlet 63.
  • the first heat exchanger inlet 61 is connected to the compressor outlet 42, and the first heat exchanger outlet 62 is connected to the second recuperator inlet 13, ie the secondary side of the recuperator.
  • a turbine 70 is provided, which has a turbine inlet 71 and a turbine outlet 72 .
  • the turbine inlet 71 is preferably connected to the second outlet 14 of the recuperator 10, ie to the outlet of the secondary side of the recuperator, and the gas outlet 5 is either identical to the turbine outlet 72 or coupled to it.
  • the compressor inlet 41 is connected to the suction area 30, which is delimited and bounded by a suction wall 31 from the recuperator.
  • the intake area 30 extends away from the compressor 40, and the recuperator 10 is configured to extend at least partially around the intake area.
  • the intake area 30 is delimited by the intake wall 31, this intake wall 31 also representing the limitation of the recuperator.
  • the suction wall 31 is provided with openings in order to let gas that is at the second outlet 12 of the recuperator 10 into the suction area 30 .
  • the openings provided in the intake wall thus represent the first recuperator outlet 31.
  • the intake wall is also designed to create a fluidic separation between the intake area 30 and both the second recuperator inlet 13 and the second recuperator outlet 14 (and also with respect to the first recuperator inlet 11, which can only be reached by gas via the intended path in the recuperator).
  • the recuperator 10 in FIG. 10 or in FIGS. 11a to 12b is designed as a heat exchanger according to the invention, specifically similar to the implementation described in FIGS. 7a and 7b.
  • the plurality of first channels 101a, 101b, 101c of Fig. 1a for the first fluid are the channels 15 of Fig. 10, 11a, 11b or 12a
  • the plurality of second channels 102a, 102b, 102c of Fig. 1a for the second fluid are the channels are the channels 16 of Fig. 10, 11a, 11b or 12a.
  • the recuperator 10 is designed without the first collection area 711, as can be seen in Fig. 12b, in which this outer collection area is not formed, because air is sucked in from the outside through perforations provided for the first collection area in 12b would therefore be the space surrounding the first recuperator inlet 11, from which the air to be cooled is sucked.
  • the suction area in the middle of the recuperator 10 corresponds to the third collection area 721 of FIG. 7b.
  • the second collection area 731 in FIG. 7b corresponds to the collection area 18 in e.g. 10 or 12a.
  • the fourth collection area 741 of Figure 7b corresponds to the collection area 17 in Figure 10 or Figure 12a.
  • first recuperator input 11 corresponds to the first input P.EIN 710.
  • the first recuperator output (12) corresponds to the output P.AUS 720.
  • the second recuperator input (13) corresponds to the input S.EIN 713 and the second recuperator output (14) corresponds to the Output S.OUT 740 of Figure 7a or 7b.
  • the recuperator 10 is constructed as set forth in connection with Figures 7a and 7b , ie the channels alternately extend horizontally around the entire perimeter, then extend the full height, then again extend around the full perimeter according to the implementation as set out in Figures 1a-9.
  • recuperator 10 is preferably designed in such a way that the collection areas are obtained by gradual or sudden enlargement of the channels at the expense of the number of channels, as has been explained with reference to FIGS a large structure such as B. the trachea into smaller structures in which the alveoli are placed at the end.
  • a somewhat fractal implementation which is similar to itself, achieves a transparent and logical implementation that is also characterized by low flow resistance and high efficiency due to an optimally even distribution of the heat transfer effect over the entire volume of the heat exchanger.
  • the recuperator 10 extends completely around the intake area 30, as shown, for example, in FIG. 11a. At certain however, according to exemplary embodiments, it is sufficient for the recuperator to extend around the intake area by only part of the entire angular range of 360°. Thus, an arrangement of the recuperator that extends only 90° around the intake area 30 can be favorable if the gas refrigerator is to be fitted in a corner of a room, for example. Depending on the implementation, other larger or smaller extensions around the intake area are also conceivable for the recuperator. However, an implementation in which the recuperator extends completely, i.e. 360 around the intake area, is particularly efficient.
  • the recuperator has a circular cross section in plan view.
  • Other cross-sections such as triangular, quadrangular, pentagonal or other polygonal cross-sections in plan view are also conceivable, since these recuperators with such cross-sections in plan view can easily be designed with corresponding gas ducts in order to achieve a highly efficient recuperation effect, preferably from all sides to reach from.
  • the entire gas refrigerating machine is housed in a housing, as shown for example at 100 in FIG. 11a.
  • the gas inlet 2 is located in an upper area of the housing 100 of FIG. 11a, the housing or the upper housing wall being designed identically to the recuperator wall.
  • the gas inlet 2 thus simultaneously represents the first recuperator inlet, which is represented by the perforations 11 in the housing wall.
  • the recuperator occupy a significant portion of the height of the overall housing 100, such as between 30 and 60% of the height of the housing.
  • all components of the gas refrigerator ie both the compressor 40 and the recuperator 10 as well as the heat exchanger 60 and the turbine 70 are located within the housing 100, as is shown in an exemplary, particularly compact implementation in FIG. 11a. Only the connections 63, 64 for the secondary side of the heat exchanger 60 and the air inlet 2 and the air outlet 5 are accessible from the outside Connection 101, which is also accessible to the outside. All other elements and inputs and outputs etc. are not accessible to the outside in the compact implementation.
  • the gas refrigeration The machine in the particularly compact structure shown in Fig. 11a therefore has only one air inlet 2, one air outlet 5, one connection 63, 64 for the secondary side of the heat exchanger 60 and one power/signal connection 101 for the electronics assembly 102.
  • the electronic module 102 is preferably used to supply a drive motor for the compressor 40 with energy or to supply control data to an element of the gas refrigerating machine or to acquire sensor data from an element of the gas refrigerating machine and is arranged in an area of the gas refrigerating machine which is designed or suitable to cool the electronics assembly.
  • the gas refrigerator can be used for cooling. Then the gas inlet is connected to a space to be cooled either directly or to an area to be cooled via a heat exchanger, and the heat exchanger 60 or the secondary side 63, 64 of the heat exchanger is connected to a heat sink 80, such as a fan on the roof of a building or a fan outside an area to be cooled.
  • a heat sink 80 such as a fan on the roof of a building or a fan outside an area to be cooled.
  • the secondary side 63, 64 of the heat exchanger is connected, for example, to underfloor heating (FBH) or to any heating circuit that can also have heating options other than underfloor heating.
  • the gas inlet 2 is in this case connected to a hot gas source if a direct system is used, or to a heat exchanger which is connected to a heat source on its primary side and the secondary side of which is gas inlet 2 and gas outlet 5.
  • the secondary inlet of this heat exchanger not shown in FIG. 10 is the gas inlet 2 and the secondary outlet is the gas outlet 5 of this heat exchanger not shown in FIG.
  • the compressor 40 is positioned upstream of the turbine 70 in the direction of operation of the gas refrigerator.
  • This has the advantage that warm air can be sucked in from top to bottom in an area to be cooled and cold air is discharged downwards into an area to be cooled.
  • the physical property is taken into account that cold air tends to collect on the floor or in the lower area of a room and warm air at the top of the room.
  • the compressor includes a compressor wheel
  • the turbine also includes a turbine wheel. Both wheels are preferably arranged on one and the same axle 43 .
  • a rotor 44 of a drive motor is arranged on the axle 43 in order to supply the additional drive force which is still required over and above the drive force achieved by the turbine.
  • the rotor 44 cooperates with the stator of a drive motor, which is not shown in FIG. 11a.
  • the rotor 44 is preferably located between the compressor wheel and the turbine wheel.
  • the recuperator is preferably arranged in an outer area of a volume of the gas refrigerator, so that the intake area 30, which is connected to the compressor inlet 41, can be arranged in the inner area of the recuperator. Air is then sucked in from all sides, as shown in FIG. 11a, in which the air inlet 2 is shown both on the left and on the right in the diagram in its schematic cross-sectional view.
  • the recuperator 10 thus comprises a volume shape having a central region with a central opening forming the suction region 30, the suction wall extending from a first end to a second end, the second end being covered with a cover 32. Therefore, no air or gas flows from above into the intake area, but only from the side through the primary area of the recuperator.
  • the widening from the first end at the compressor inlet 41 to the second end with the cover plate 32 is a continuous widening with an approximately parabola-like or hyperbola-like shape, which is there to ensure optimal flow patterns within the intake area, to ensure a laminar flow as far as possible, which forms the lowest flow resistance, must be ensured in the intake area from top to bottom.
  • the somewhat greater flow resistance due to longer gas ducts in the recuperator closer to the compressor inlet 41 is compensated by somewhat shorter gas ducts further away from the compressor inlet 41, so that the flow resistance conditions are almost the same for the entire area from bottom to top along the intake area, see above that the flow through the recuperator is equally efficient over its entire volume.
  • the recuperator 10 is rotationally symmetrical, and an axis of symmetry of the recuperator 10 coincides with an axis of the compressor or an axis of the turbine or an axis of the suction area and/or with an axis of the housing.
  • the recuperator is designed as a counterflow heat exchanger, which is indicated as one aspect in the schematic illustration in FIG. 12a.
  • Fig. 12a which represents, for example, the "left half" or "right half” of the recuperator of Fig. 11a
  • first gas ducts 15 from the first recuperator inlet 11 to the first recuperator outlet 12.
  • second gas ducts 16 the extending between a first collection space 17 on the left in Fig. 12a and between a second collection space 18 on the right in Fig. 12a.
  • the second gas channels 16 are in thermal interaction with the first gas channels 15.
  • the implementation i.e.
  • the flow direction in the gas channels 16 is in the same direction as the flow in the gas channels 15. Then the left one is Connection bottom left in Fig. 12a is the second recuperator inlet 13 and the right connection is the recuperator outlet 14. If the recuperator is to be operated in counterflow, which is preferred, with the direction of flow in the flow channels 15 and 16 being opposite to one another, the inlet is left in Fig. 12a is the second recuperator output 14 and the connection on the right in Fig. 12a is the second recuperator input 13.
  • the thermal interaction takes place via the material of the recuperator, which is arranged between the gas ducts 15 and 16, i.e. between a gas duct 15 and a corresponding gas duct 16, i.e. the heating of the warm gas drawn in at the expense of the cooling of the gas flowing in the secondary area of the recuperator gas that is brought to the turbine for relaxation.
  • the recuperator includes the collection space 17 in order to distribute gas supplied via the left connection 4 from bottom to top in the embodiment shown in FIG. 12a into the various gas channels.
  • gas that has flowed through the channels is collected on the other side through the second collection space 18 and drawn off via the second connection. If, on the other hand, the occupancy is different, ie in real counterflow, the collection space 18 divides the gas into the individual Gas channels 16 safe and the collection space 17 causes the collection of the gas discharged from the individual channels for the purpose of suction through the lower connection due to the turbine relaxation effect.
  • the housing in which the compact gas refrigerator is arranged is rotationally symmetrical or cylindrical and has a diameter of between 0.5 and 1.5 meters and a height of between 1.0 and 2.5 meters.
  • sizes with a diameter between 70 and 90 and especially 80 centimeters are preferred, and a height between 170 and 190 and preferably 180 cm is preferred in order to provide an already significant cooling for e.g. a computer room, which is preferably implemented as direct air cooling .
  • an expansion from the turbine outlet 72 to the gas outlet 5 is also provided, which also runs in a parabolic or hyperbolic shape, so that a favorable adjustment of the flow conditions from the high speed at the turbine outlet 72 to an adapted reduced speed is achieved at the air outlet 5, so that no excessive noise is generated by the cooling.
  • the housing has an elongated shape
  • the gas inlet is formed by a plurality of perforations in an upper region of the housing or a wall of the housing with respect to the operating direction of the gas refrigerator.
  • the gas outlet is formed by an opening in a lower area or in the base of the housing, the opening in the base of the area corresponding to at least 50% of a cross-sectional area of the housing in the upper area, ie in the air inlet. Opening the gas outlet as large as possible results in low air velocities at the gas outlet and thus a pleasant noise level and also a pleasant “draft” in the room with only a small amount of air movement.
  • the compressor 40 is preferably arranged in order to achieve an air movement in the intake area, in the operating direction of the gas refrigerator, from top to bottom.
  • the compressor 40 then leads to a deflection of the flow from bottom to top, with a duct 45 of the compressor being advantageously used here, which already inherently achieves a 90° deflection at the transition from the compressor wheel to the duct 45 .
  • the next 90 ° are then achieved by the gas that has been compressed, at the outlet of the control chamber from bottom to top via the heat exchanger inlet 61, which is also the Compressor output 42 is fed.
  • the gas then moves from the outside in, towards the heat exchanger outlet 62, which coincides with the inlet 13 of the recuperator.
  • the gas then moves over collection areas, as shown in FIG. 12a, first in the recuperator from bottom to top and then at the exit of the corresponding gas channels from top to bottom, finally entering the turbine inlet 71 at the second recuperator outlet 14 .
  • the turbine inlet 71 is again optimal in terms of flow, connected to the second recuperator outlet in the outer area, i.e. outside the heat exchanger, so that as few gas deflections as possible are achieved so that the gas can enter the turbine 70 without suffering significant losses can, relaxed in the turbine, drive the turbine accordingly and lose heat through the relaxation process.
  • the turbine outlet is located at the bottom of the housing.
  • This allows the gas chiller to be placed on a cooling inlet area in a "false" floor of a data center. Air ducts extend from this cooling inlet area into the area to be cooled, e.g. B. computer racks.
  • the gas chiller thus represents a compact measure to feed cold air into an existing infrastructure of false floors or air ducts running in the floor, which lead off from the (central) cooling inlet.
  • the arrangement of the turbine outlet at the bottom of the gas chiller is also advantageous in that condensed moisture falls away from the device due to gravity and can be easily collected and drained off without the engine having to be protected from the moisture at great expense.
  • FIG. 12b shows a schematic top view of a preferred recuperator 10 with collection spaces on the secondary side.
  • the plan view of Figure 11a or 11b is schematic.
  • the gas refrigerator is completely closed at the top by a closed cover.
  • Figure 12b 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 suction area 30.
  • the glass flow is from the outside inwards, as shown by the arrows 50, namely from the first recuperator inlet 11 to the first recuperator outlet 12. Then the gas in the intake area 31 flows down as it passes through the Arrow ends 51 in area 30 is shown.
  • the gas is then compressed and flows through the heat exchanger 60 to flow into the second recuperator inlet 13 . From there it flows from bottom to top as indicated by the arrowheads in collection space 18. The gas then flows back out through the recuperator into the collection space 17 and down there, as shown by the ends of the arrows 53 . The gas then passes from the collection chamber 17 via the second recuperator 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 input 13 to the second recuperator output 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.
  • the heat exchanger 60 has a disc-shaped volume and the heat exchanger inlet is on the outside of the disc-shaped volume and the heat exchanger outlet is on the inside of the disc-shaped volume. Furthermore, the heat exchanger inlet is preferably arranged at the bottom of the heat exchanger and the heat exchanger outlet is arranged at the top of the disc-shaped volume. In other exemplary embodiments, it is preferred to design the heat exchanger in a wedge-shaped cross section, with a cross section of the heat exchanger inlet 61 being larger than a cross section of the heat exchanger outlet 62 whose outer boundary of the ring cross-section in FIG. 11b is larger than the inner boundary, the heat exchanger also not having to be arranged horizontally as in FIG. 11a, for example, but can be arranged diagonally from bottom to top.
  • a liquid such as a Water/glycol mixture that carries the waste heat to the heat sink 80.
  • the medium cooled in the heat sink 80 which can be designed, for example, as a liquid/air heat exchanger with a fan on a roof, is fed back into the inlet 63 of the secondary side of the heat exchanger 60 by the pump 90, as is also shown in Fig. 11a is shown. Therefore, preferably spiral-shaped liquid lines are located in the heat exchanger 40 in the area through which the gas flows, in order to remove and dissipate heat from the gas as efficiently as possible.
  • the suction region extends a distance greater than 10 cm, and preferably greater than 60 cm, from the compressor inlet.
  • the gas ducts are arranged in such a way that they are distributed substantially evenly over the volume on all sides and can therefore guide as much air as possible into the intake area as efficiently as possible with little resistance.
  • the gas refrigeration machine is operated in such a way that the suction is achieved through the suction area 30 that projects specifically into the recuperator.
  • recuperator can also be implemented with other heat exchange technologies, e.g 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.
  • the heat exchanger does not necessarily have to be arranged in the housing between the recuperator and the turbine or between the recuperator and the compressor.
  • the heat exchanger could also be externally connected, although an internal arrangement is preferred for compact construction.
  • the compressor and turbine need not necessarily be implemented as radial impellers, although this is preferred, as favorable power matching can be achieved by stepless speed control of the compressor via the electronics assembly 102 of FIG. 11a.
  • the compressor as shown in FIG. 11a, can be designed as a turbocompressor with a radial impeller and with a duct or duct 45, 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 design that leads to good efficiency.
  • FIG. 11b shows a sectional view of a fully integrated gas refrigerator according to a further exemplary embodiment of the present invention with an alternative arrangement of the electronic assembly 102 with respect to FIG. 11a.
  • the electronics assembly is mounted in the cool area next to the turbine outlet, in FIG. 11b it is located in the so-called “machine room” between the base of the compressor wheel 40 and the base of the turbine wheel 70.
  • the arrangement of the assembly 102 on the upper limit 71a of the turbine inlet 71 is advantageous because this area is well cooled 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 electronic assembly 102 for the electrical supply of the gas refrigerator with energy and/or control signals preferably has an opening in the middle and is disk-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 further exemplified in FIG an area between a base of a compressor wheel of the compressor 40 and a base of a turbine wheel of the turbine.
  • the construction group can be formed in any way, as long as it is accommodated in the engine room and is in thermal interaction with the boundary 71a of the inlet 71 of the turbine 70, ie z. B. is mounted on the boundary 71a.
  • the supply line for energy 101a and data 101b for the motor pass through the lateral boundary To lead 14a of the recuperator output 14 and through the housing 100 at the appropriate point, as z. as shown in Figure 11b. '
  • Gas refrigerator with the following features: an input (2) for gas to be cooled; a recuperator (10) comprising a heat exchanger as described above and claimed below; a compressor (40) having a compressor input (41), wherein the compressor input (41) is coupled to a first recuperator output (12); a further heat exchanger (60); a turbine (70); and a gas outlet (5), wherein the compressor inlet (41) is connected to a suction area (30) which is delimited by a suction wall (31) and extends away from the compressor (40), and wherein the recuperator (10) extends extends at least partially around the intake area (30) and is delimited by the intake wall (31).
  • the recuperator (10) has a first recuperator inlet (11), the first recuperator outlet (12), a second recuperator inlet (13) and a second recuperator outlet (14), or the compressor has the compressor inlet ( 41) and a compressor outlet (42), or wherein the further heat exchanger (60) has a first heat exchanger inlet (61) and a first heat exchanger outlet (62) on a primary side, a second heat exchanger inlet (63) and a second heat exchanger outlet (64) on one Secondary side, wherein the first heat exchanger inlet (61) is coupled to the compressor outlet (42), and wherein the first heat exchanger outlet (62) is coupled to the second recuperator inlet (13), or wherein the turbine (70) has a turbine inlet (71) and having a turbine outlet (72), the turbine inlet (71) being connected to the second recuperator outlet (14), and the gas outlet (5) being connected to the Turbine output (72) is coupled.
  • Gas refrigeration machine which has a housing (100) in the wall of which the inlet (2) for the gas to be cooled is arranged, and in the wall of which the gas outlet (5) is arranged, the recuperator (10), the compressor (40), the turbine (70) or the further heat exchanger (60) being arranged in the housing (100).
  • Gas refrigerator according to example 5 in which the rotor (44) is arranged between the compressor wheel (40) and the turbine wheel (70), or in which the compressor wheel (40), a first axis section (43), a rotor (44) , a second axle section (43) and the turbine wheel (70) are formed in one piece, or in which a first bearing section is formed on the compressor wheel (40) and a second bearing section is formed on the turbine wheel (70), or in which the rotor (44) made of a non-ferromagnetic material such as B. aluminum, and a ferromagnetic yoke element around the rotor (44) is attached and magnets (are arranged on the yoke element.
  • a non-ferromagnetic material such as B. aluminum
  • Gas refrigerator according to one of the preceding examples in which the recuperator (10) is arranged in an outer area of a volume of the gas refrigerator and the compressor inlet (41) is arranged in an inner area of the volume of the gas refrigerator.
  • the recuperator (10) has a volume shape which has a central opening located in a central region, which forms the suction region (30), the suction wall (31) extending from a first end from the central opening forming the compressor inlet (41) to a second end closed by a cover (32).
  • suction region (30) has a continuously increasing opening area from a first end to a second end and the suction wall (31) is formed continuously or steplessly.
  • recuperator (10) is rotationally symmetrical, with an axis of symmetry of the recuperator (10) being aligned with an axis of the compressor (40) or an axis of the turbine (70) or an axis of the gas outlet (5th ) or the gas inlet (2) or with an axis of the intake area (30) essentially coincides.
  • Gas refrigerator in which a housing (100) has a side wall and a bottom wall or a cover wall, the inlet (2) for the gas to be cooled being arranged in the side wall and the gas outlet (5) in the bottom wall or the cover wall, or in which the gas outlet (5) is formed in a floor of the gas refrigerator in the operating direction and is shaped in such a way that the gas outlet can be placed on a cooling gas inlet in a floor of a room in which the gas refrigerator can be installed, or in which the gas outlet (5) is formed in a base of the gas refrigeration machine in the operating direction and a moisture-collecting device is also provided in order to collect condensate occurring in the gas outlet (5).
  • a housing (100) is rotationally symmetrical or cylindrical or has a diameter of between 0.5 m and 1.5 m or a height of between 1.0 m and 2.5 m.
  • Gas refrigerator in which a housing (100) has an elongated shape, the inlet (2) for the gas to be cooled having a plurality of perforations in an upper region of the housing (100) with respect to an operating direction of the gas refrigerator or a wall of the recuperator (10), and the gas outlet (5) has an opening in a lower region of the housing (100) with an opening area which is at least 50% of a cross-sectional area of the housing (100) in the upper region.
  • the further heat exchanger (60) has a wedge-shaped or disc-shaped volume and a heat exchanger inlet (61) is arranged on the outside of the wedge-shaped or disc-shaped volume and a heat exchanger outlet (62) on the inside of the wedge-shaped or disc-shaped Volume is arranged, or in which the heat exchanger inlet (61) is arranged at the bottom of the wedge-shaped or disc-shaped volume and the heat exchanger outlet (62) is arranged at the top of the wedge-shaped or disc-shaped volume.
  • the recuperator (10) has a volume which has a countercurrent heat exchanger structure in an outer area and adjoins the intake area (30) in an inner area, with a first recuperator inlet (11) is arranged on the outside of the outer area, a first recuperator outlet (12) being located on the inner region to direct gas into the intake region (30), a second recuperator inlet (13) also being located on the inner region and a second recuperator outlet (14) also on the outer Area is arranged, wherein the first recuperator inlet (11) and the second recuperator outlet (14) are fluidically separated in the recuperator (10) and the first recuperator outlet (12) and the second recuperator inlet (13) in the recuperator (10) are fluidically separated.
  • first recuperator outlet (12) has two interconnected gas ducts (16) between a second recuperator inlet (13) and a second recuperator outlet (14), the first gas ducts (15) and the second gas ducts (16) being in thermal interaction are arranged, wherein the recuperator (10) at the second recuperator input a first collection area (18) which connects the second gas channels (16) on one side and which extends along the inner area and forms the second recuperator input (12). , and a second collection area (17) which connects the second gas channels on another side and extends along an edge area of the outer area and forms the second recuperator outlet (14), the suction wall (31) delimiting the first collection area and the first Collection area (18) separates from the intake area (30).
  • Gas refrigeration machine in which a turbine inlet (71) is connected to a second recuperator outlet (14) via a connection area, the connection area extending around the further heat exchanger (60).
  • the further heat exchanger (60) is a gas-liquid heat exchanger and, in a volume through which gas flows, has a line structure through which liquid can flow, the liquid structure having a secondary inlet (63 ) and a secondary output (64) of the further heat exchanger (60) is coupled.
  • Gas refrigerator according to example 23 in which a housing (100) has a liquid outlet (64) from the further heat exchanger (60) and a liquid inlet (63) to the further heat exchanger (60).
  • Gas refrigeration machine in which the liquid inlet and the liquid outlet are connected to a heat sink (80), a pump (90) being arranged in a circuit with the heat sink (80).
  • the recuperator (10) has a volume which completely encloses the intake area (30), the intake area (30) and the volume of the recuperator (10) differing by a distance greater than 10 cm from the compressor inlet (41), the inlet (2) for gas to be cooled being formed by first ends of first gas channels (15), second ends of the first gas channels opening into the intake area (30), the first gas channels (15) are distributed over the volume in order to guide gas from several sides into the suction area (30).
  • Gas refrigerator according to one of the preceding examples, which is designed as an open system, the inlet (2) for gas to be cooled being arranged in an area to be cooled and the gas outlet (5) being arranged in the area to be cooled in order to warm gas to suck in from the area to be cooled and to discharge cold gas into the area to be cooled.
  • Gas refrigeration machine in which an electronics assembly (102) for supplying a drive motor for the compressor (40) with energy or for supplying control data to an element of the gas refrigeration machine or for acquiring sensor data from an element of the gas refrigeration machine in a Area of the gas refrigerator is arranged, which is designed to cool the electronics assembly, or in which an electronics assembly (102) for the electrical supply of the gas refrigeration machine with energy and/or control signals is arranged in an area between the turbine outlet (72) and the gas outlet (5) and a housing wall outside the gas outlet (5), or in which one Electronic assembly (102) for the electrical supply of the gas refrigerator with energy and/or control signals is arranged in an area between a base of a compressor wheel of the compressor (40) and a base of a turbine wheel of the turbine, or in which an electronic assembly (102) for the electrical supply of the Gas refrigeration machine with energy and/or control signals is arranged on a limiting element (71a) of a turbine inlet (71) of the turbine (70), the electronics assembly also being arranged outside
  • the device 1600 for treating gas comprises a compressor 40 with a compressor inlet 41 and a compressor outlet 42.
  • the device also comprises 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 two-th heat exchanger outlet 14 has.
  • 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 inlet 11 and the outlet 12, and on its secondary side, which is formed by the inlet 13 and the outlet 14 is used, the same type of gas is used, e.g. air.
  • 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.
  • 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 dissipate thermal energy from the heat exchanger 10 .
  • the device 1600 for treating gas is supplemented with an input interface 1000 or an output interface 200 or both interfaces.
  • the input interface 1000 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 1102a and a fresh air duct 1102b.
  • 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 1202a and an exhaust air duct 1202b.
  • the input interface includes an exhaust air input or duct 1102a on an input side and a fresh air input 1102b also on the input side.
  • the input interface 1000 includes a first input interface output 1104 and a second input interface output 106 on an output side of the input interface 1000.
  • the output interface 200 preferably includes an inlet air outlet 1202a and an exhaust air outlet 1202b on an outlet 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 1600 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 1104 is connected to the first heat exchanger input 11, and the second input interface output 106 is connected to the Compressor input 41 connected.
  • the connections set out above are direct connections of a gas channel to another gas channel, so that the gas flows directly from the input interface output 1104, for example, into the first heat exchanger input 11 on the primary side of the heat exchanger 10.
  • the input interface 1000 is designed to couple the input side of the input interface 1000 to the output side of the input interface 1000 .
  • 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. 14 or FIG 16a or in FIG. 17a, a switch such as shown in FIG. 17c and in FIG. 16a can be used to perform a corresponding switching from one coupling to the other. This achieves, for example, a cooling mode or summer mode, as shown in FIG. 14, 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. 13 also shows an implementation in which the input interface or the output interface can be controlled depending on a control signal 1302, 1304, the device having a controller 300 which is designed to receive a control input and to To deliver control signal 1302, 1304, 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 1000 or the output interface 200) by the control signal 1302, 1304 in a summer mode for cooling a gas for a supply gas duct 1202a of the gas discharge, and to switch the input interface 1000 or to set the output interface 200 by the control signal 1302, 1304 in a winter mode for heating a gas for the Ceiaska channel 1202a.
  • the controller may use a control table 1301 of Fig. 16b or a control table 1303 of FIG. 17b in a memory and use accordingly.
  • the input interface 1000 is designed as a fixed connection between the fresh air duct 1102b 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 1102b.
  • the exhaust air duct 1102a is also directly connected to the first heat exchanger inlet 11 or to the second inlet/interface outlet 1104 .
  • a corresponding direct connection also exists between the output interface input 206 and the supply air duct 1202a on the one hand and the second heat exchanger input 12 or the output interface input 204 and the exhaust air output 1202b, as shown in FIG.
  • FIG. 14 shows a coupling of the device 1600 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. 18a or 18b, comprises a splitter 502, which optionally has a fan to draw air from the room and pump it into the input interface 1000, an optional handler 504 and a combiner 506, preferably including a fan, for pumping the room supply air in the room supply air duct 510 into the room and drawing the corresponding supply air from the supply air port 1202a.
  • the 14 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. 14, 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 air, which is now under high pressure and has a temperature of about 28°C is cooled down in the Turbine 70 relaxes, to a temperature of, for example, 5°C, resulting in relaxation to the original pressure ratio being obtained.
  • the 5°C cold air is then fed into the supply air duct 1202a 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 discharged to the outside via the exhaust air duct 1202b, 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 in, which is, for example, a room in a building, such as a conference room, a room, a hall or something similar, or which can also be a “functional room”, such as a computer center.
  • FIG. 15 shows an alternative implementation of the device 1600 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 1102a, 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 .
  • This very cold air is discharged to the environment via an exhaust air outlet, which in the exemplary embodiment shown in FIG. 15 already has a very cold temperature of -30.degree.
  • the ambient air is fed into the primary-side inlet 11 of the heat exchanger 10 via the fresh air duct 1102b 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 ultimately achieve a temperature of 25°C in the room supply air duct 510, for example.
  • Fig. 14 for cooling and in Fig. 15 for heating are extreme examples.
  • the example in FIG. 14 shows that even at extremely hot outside temperatures of 50° C., a cooling effect is easily achieved and exhaust air can be generated which is 87° C. hot and can therefore be fed into the environment as a heat sink without further ado can.
  • 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 1102a and the reintroduction flow 512, with the exhaust air present in the exhaust air duct 1102a 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 1102a represents the re-injection stream 512, which is typically not altered 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 are disinfecting the refeed stream or filtering the refeed stream for dust or biological particles such as bacteria or viruses. However, the handler 504 may be bypassed or omitted as shown in phantom in Figure 18a.
  • the combiner 506 the supply air in the supply air duct 1202a, which is due to fresh air that has changed in terms of its temperature, is combined with the reintroduction stream directly or with the processed reintroduction stream and is fed to the room 400 via the room inlet air duct 510.
  • the combiner 506 preferably comprises a fan, e.g. B. 506 of Fig. 8c, which can be used to draw in supply air via the supply air duct 1202a, so, referring to Fig. 20c, to pull 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 1102a in order to transport it through the heat exchanger 10 as exhaust air into the environment, for example during summer operation.
  • 18b 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. 18b is similar to the device of Fig. 18a.
  • 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.
  • connection 1202a 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. 18a, the processor 504 has to process less gas flow in FIG. 18a than in FIG. 18b 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.
  • fan L 21 can also be placed at the outlet of the heat exchanger before connection A4.
  • the placement in Fig. 17a 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 also particularly advantageous because normallyteurzumate-generating tasks in addition to air conditioning by the device for treating gas, such as dehumidification of the supply air especially for the cooling operation z. B. can be easily carried out in summer.
  • 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 the heating operation in winter, as shown in Fig. 15, easily be obtained simply by the fact that at the outlet 12 of the heat exchanger 10, ie before the combiner, where the gas is relatively hot, such as. B. has 45 °, an open water surface is placed, which is surrounded by z. B. a Wegerkonstruc tion 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 inventive device for treating gas in contrast to existing ventilation and air conditioning devices, in which heat recovery from the room exhaust air flow takes place using a heat pump that uses a liquid such as water as the working medium, the inventive device for treating gas completely without a liquid is sufficient as the working medium, but only gas is used 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.
  • FIG. 16a shows an implementation of the input interface 1000 or the output interface 200 as a two-way switch, as is shown schematically in FIG. 17c, 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 1104 in Fig. 16a shown, is connected and the fresh air is connected to port A3, as shown by the current "switch position" of the switch 1700.
  • the changeover switch 1700 is rotated by 90°, the fresh air duct is connected to the port A1 and the exhaust air duct is connected to the port A3.
  • Fig. 16b shows a corresponding control table that expresses that in summer operation, for example, which is shown in Fig. 14, the exhaust air is connected to port A1, the fresh air is connected to port A3, and the supply air is connected to the on connection A2, and the exhaust air is connected to connection A4.
  • the device according to the invention for treating gas according to FIG. 15 is configured in winter mode, the exhaust air is connected to port A3, the fresh air is connected to port A1, the supply air is connected to port A4, and the exhaust air is connected to port A2.
  • FIG. 17a 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. 16a.
  • the input interface includes a first switch 1000a for port A3 and a second switch 1000b 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 1000a has a fresh air connection 308 and an exhaust air connection 320.
  • the second switch 1000b 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 1302b for the first control signal C1 and via a second control signal 1302a 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 1304a for the second changeover switch, ie for the control signal C2, and via a further control signal 1304b for the control connection C4.
  • Fig. 17b 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. 14 or to achieve heating in the room according to FIG.
  • FIG. 20c shows another preferred implementation of an apparatus for treating gas, again comprising the turbine 70, the compressor 40 and the heat exchanger 10.
  • FIG. 20c 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 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 via the connection A1 via a primary-side collection space 19a, which extends outside around the other collection space 17, is supplied with gas.
  • 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, which can be contained, for example, in the combiner 506 of FIG. 18a.
  • a fan not shown in Figure 20c, may be mounted "above" port A1, which could then be present in splitter 502, and which brings the gas from the primary inlet to the primary outlet 12 or intake area 30 and from there into connection A4 and from there, depending on the output interface wiring, further into the room or into the environment.
  • FIG. 20b 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.
  • Figure 20b 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 first recuperator output 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 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 rooms 17, 18 are den in the embodiment shown Associated with lines 16 that connect the second recuperator input 13 to the second recuperator output 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. 20a also shows a schematic representation of a heat exchanger which, in contrast to Fig. 20c or Fig. 20b, is not designed to be rotationally symmetrical, but for a heat exchanger designed, for example, in a cylindrical or cuboid shape, into which gas is fed via the first recuperator inlet 11 into a primary-side first collection space 19a flows, via the channels 15 to the first recuperator outlet 12 and in particular to a second primary-side collection space 19b and from there the recuperator 10 via the second heat exchanger outlet 12 leaves.
  • the secondary side includes a second recuperator inlet 12 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 outlet 14 leaves the recuperator 10 or heat exchanger.
  • first collection space 19a on the primary side and the second collection space 19b on the primary side are 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. 20a also serves to show at least part of a rotationally symmetrical heat exchanger, as shown in FIG. 20b 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. 20b shows the case that the first recuperator outlet 12 is below with respect to the plane of the drawing, as represented by the downwardly directed flow 51 in Fig. 20b, and as is also represented schematically in Fig. 20c, if at least in With regard to the heat exchanger 10 Fig. 20c shows the actual installation 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 therefore guide as much air as possible from the primary-side inlet 11 with little resistance into the intake area as efficiently as possible.
  • 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.
  • recuperator 10 may be implemented with other heat exchange technologies, such as a heat exchanger that does not operate in counterflow and where the gas channels are not parallel to each other or perpendicular to the 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, as favorable power matching can be achieved by stepless speed control of the compressor via an electronics assembly 102 of Figure 19b.
  • the compressor can be designed as a turbo compressor with a radial impeller and with a duct or duct which has a 180° deflection of the gas flow achieved.
  • other gas conduction measures can also be achieved via a different shape of the guide space, for example, or via a different shape of the radial impeller, in order to still achieve a particularly efficient design that leads to good efficiency.
  • FIG. 19a shows a perspective view of a preferred compressor-turbine combination
  • FIG. 19b shows a side view of the preferred compressor-turbine combination from FIG. 19a.
  • 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 bearing area hangers are attached to the wall of the intake area 30 of FIG.
  • the combination is dimensioned such that the diameter of the compressor wheel 40a is larger than the diameter of the rotor 44, and that the diameter of the rotor 44 (preferably without yoke 44a and magnets 44b) is equal to or 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.
  • 19b 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 spaced 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. 19b, the assembly may be formed in any way so long as it is housed in the machine room and thermally interacts with the boundary 71a of the inlet 71 of the turbine 70, e.g. B. is mounted on the boundary 71a. In this case, it is also preferred to route the supply line for energy 101a and data 101b for the motor through the lateral boundary 14a of the recuperator outlet 14 and through the housing 100 at the appropriate point.
  • 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; and a turbine (70) having 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). is. 2.
  • Example 1 which also has an input interface for coupling the compressor input (41) and the first heat exchanger input (11) with a gas supply - supply (1102a, 1102b), or an output interface (200) for coupling the Turbine outlet (72) and the first heat exchanger outlet (12) with a gas outlet (1202a, 1202b).
  • the input interface (1000) has an exhaust air input (1102a) and a fresh air input (1102b) on an input side and a first input interface output (1104) and a second input interface output (106 ), wherein the input interface (1000) is designed to couple the input side of the input interface to the output side of the input interface, or in which the output interface (200) has a first output interface input ( 204); Output interface (200) to couple to the output side of the output interface.
  • an input interface (1000) is designed to connect the compressor input (41) to a fresh gas channel (1102b) of the gas supply, and to the first To connect the heat exchanger inlet (11) to an exhaust gas duct (1102a) of the gas supply, or wherein an outlet interface (200) is formed in order to connect the turbine outlet (72) to an inlet gas duct (1202a) of the gas outlet, and to connect the first heat exchanger outlet ( 12) to be connected to an exhaust gas duct (1202b) of the gas discharge.
  • an input interface (1000) is designed to connect the compressor input (41) to an exhaust gas duct (1102a) of the gas supply, and to connect the first to connect the heat exchanger inlet (11) to a fresh gas duct (1102b) of the gas supply, or wherein an outlet interface (200) is designed to connect the turbine outlet (72) to an exhaust gas duct of the gas discharge, and to connect the first heat exchanger outlet to a feed gas duct ( 1202a) of the gas outlet.
  • the input interface (1000) or the output interface t200) dependent on a control signal (1302, 1304) are controllable, and wherein the device has a controller (300) that is formed is to receive a control input and to provide the control signal (1302, 1304) in response to the control input, wherein the controller (300) is adapted to the control signal (1302, 1304) by a manual input or a sensor-controlled input receive.
  • controller (300) is designed to switch the input interface (1000) or the output interface (200) by the control signal (1302, 1304) into a summer mode for cooling a gas for one To set the gas exhaust duct (1202a) and to set the input interface (1000) or the output interface (200) by the control signal (1302, 1304) in a winter mode for heating a gas for the gas exhaust duct (1202a).
  • the input interface (1000) has a two-way switch which has an exhaust gas input and a fresh gas input for the gas supply, and which has a first input interface output which is connected to the first Heat exchanger input is connected, and a second input interface output, which is connected to the compressor input (41), has, wherein the two-way switch is designed to connect the exhaust gas input either to the first input interface output or the second input interface output and to connect the fresh gas inlet to either the second inlet interface outlet or the first inlet interface outlet.
  • the output interface (200) has a two-way switch which has a gas outlet and a gas outlet for gas discharge, wherein the two-way switch is designed to to connect the exhaust gas outlet to the turbine outlet (72) and the exhaust gas outlet to the first heat exchanger outlet (12), or to connect the exhaust gas outlet (1202b) to the turbine outlet (72) and the exhaust gas outlet to the first heat exchanger outlet.
  • the input interface (1000) has a first changeover switch (1000b) or a second changeover switch (1000a), wherein the first switch has an output (A1) which is connected to the first heat exchanger input, and wherein the first switch (1000b) has a first input which is connected to an exhaust gas duct of the gas supply and a second input which is connected to a fresh gas channel of the gas supply, wherein the first switch (1000b) can be controlled by a control signal (1302b) in order to connect either the first input or the second input to the output, or wherein the second switch (1000a) has an output ( A3), which is connected to the compressor inlet, and wherein the first changeover switch (1000b) has a first inlet, which is connected to an exhaust gas duct of the gas supply, and a second inlet, which is connected to a fresh gas duct of the gas supply, wherein the first switch (1000b) is controllable by a control signal (1302a) to connect
  • the output interface (200) has a first switch (200a) or a second switch (200b), the first switch (200a) having an input (A2 ) which is connected to the turbine outlet, and wherein the first changeover switch (200a) has a first outlet which is connected to an inlet gas duct of the gas outlet, and a second outlet which is connected to an exhaust gas duct of the gas outlet, the first changeover switch (200a) can be controlled by a control signal (1304a) in order to connect either the first outlet or the second outlet to the inlet, or wherein the second changeover switch (200b) has an inlet (A4) which is connected to the second heat exchanger outlet, and wherein the second changeover switch (200b) has a first output, which is connected to a supply gas channel of the gas discharge, and a second output, which is connected to an exhaust gas channel of the gas discharge, the first e switch (200a) can be controlled by a control signal (1304b) in order to
  • the supply gas is supply air
  • the exhaust gas is exhaust air
  • the fresh gas is fresh air
  • the exhaust gas is exhaust air
  • a droplet catching 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
  • a humidifying device is arranged at the first heat exchanger outlet (12)
  • the liquid to be evaporated brings into contact with the gas flow at the first heat exchanger outlet (12)
  • the at the at the a fan (21) is arranged at the first heat exchanger inlet (11) in order to press gas into the first heat exchanger inlet (11), or in which a fan is arranged at the first heat exchanger outlet (12) in order to suck gas out of the first heat exchanger outlet (12).
  • RLT device air conditioning device
  • the air conditioning device having an exhaust air connection (1102a), an air supply connection (1202a), an exhaust air connection and a fresh air connection
  • the Device for treating gas with the air conditioning device via an input interface (1000) or an output interface (200) can be coupled.
  • the compressor (40) has a compressor wheel (40a) and the turbine (70) has a turbine wheel (70a), the compressor wheel and the turbine wheel (70a) being arranged on a common axis , wherein a rotor (44) of a drive motor is arranged on the axis and 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 diameter than a turbine wheel ( 70a) of the turbine (40).
  • the rotor (44) is arranged between the compressor wheel (40a) and the turbine wheel (70a), or in which the compressor wheel (40a), a first axle 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 with of the rotor (44) 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.
  • a non-ferromagnetic material such as. B. aluminum
  • the heat exchanger (10) has a volume shape having a located in a central area central opening forming a suction area (30), wherein a suction wall (31) of a first end of the central opening, to a second end which is closed by a cover (32).
  • the heat exchanger (10) has a volume which has a counterflow 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 outside on the outer area
  • the first heat exchanger outlet (12) being arranged on the inner area in order to direct gas into the suction area (30)
  • the second heat exchanger inlet (13) also being arranged on the inner area
  • the second heat exchanger outlet (14) is also arranged on the outer area
  • 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 ) are fluidically separated in the heat exchanger (10).
  • 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 second interconnected gas ducts (16) between the second heat exchanger inlet (13) and the second heat exchanger outlet (14), the first gas ducts (15) and the second gas ducts (16) being arranged in thermal interaction, the heat exchanger (10) having a first collection area (18) at the second heat exchanger inlet, the the second gas ducts (16) on one side and which extends along the inner region and forms the second heat exchanger inlet (12), and has a second collection region (17) which connects the second gas ducts on another side and extends along an edge region of the extends the outer area and forms the second heat exchanger outlet (14), with an intake wall (31) delimiting the first collection area and separating the first collection area (18) from an intake area (30).
  • an electronic assembly (102) for supplying a drive motor for the compressor (40) with energy or for supplying control data to an element of the device or for acquiring sensor data from an element of the device in a Area of the device is arranged, which is designed to cool the electronics assembly, or in which an electronics assembly (102) for the electrical supply of the device with energy and / o the control signals in an area between the turbine outlet (72) and the gas outlet (5) and a housing wall of the housing (100) is arranged outside the gas outlet (5), or in which an electronic assembly (102) for supplying the device with power 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 is arranged, or in which an elec 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), the electronics
  • 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 examples 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 outlet. 25.
  • Air conditioning device which has 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 (1102a) 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 (1202a) in order to feed air into the room supply air connection (510), the gas supply of the device being configured to supply the exhaust air flow from the exhaust air duct ( 1102a), and wherein the gas discharge is designed to deliver the supply air flow for the supply air duct (1202a), or a divider (502) for dividing air from the room exhaust air connection (508) into an exhaust air flow for an exhaust air duct (1102a) and a feed stream (512); a combiner (506) for combining the feed flow (512) with a supply air flow from a supply air duct (1202a) to obtain a combined air flow; and
  • Air conditioning device in which the processor (504) is designed to process the feed stream in terms of oxygen, moisture or disinfection.
  • Air conditioning device in which the divider (502) or the combiner (506) can be controlled in order to determine a ratio between an air quantity 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.
  • Air conditioning device according to one of Examples 25 to 27, in which the combiner (506) has a fan (506a) to suck in the supply air flow in the supply air duct (1202a), or in which the divider (502) has a fan to to pump the flow of exhaust air into the exhaust duct (1102a), 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 to move into the compressor inlet (41). 29.
  • 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), the heat exchanger being designed as a gas-gas heat exchanger; and a turbine (70) having a turbine inlet (71) and a turbine outlet (72), with the following steps: 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).
  • a method for producing a device for treating gas with a com pressor (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).
  • 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 or as 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 hardware apparatus (or using a hardware Apparatus), such as a microprocessor, a programmable computer, or an electronic circuit. In some embodiments, some or more of the essential process steps can be performed by such an apparatus.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Central Air Conditioning (AREA)

Abstract

La présente invention concerne un échangeur de chaleur présentant les caractéristiques suivantes : un premier nombre de canaux (101a, 101b, 101c) pour un premier fluide, qui s'étendent dans une première direction d'écoulement du premier fluide et dans une première direction transversale, la première direction transversale variant dans la première direction d'écoulement ; un deuxième nombre de canaux (102a, 102b, 102c) pour un second fluide, qui s'étendent dans une seconde direction d'écoulement du second fluide et dans une seconde direction transversale, la seconde direction transversale variant dans la seconde direction d'écoulement ; une structure de paroi (200a-200e, 202a-202d), qui est conçue de telle sorte que le premier nombre de canaux et le second nombre de canaux interagissent thermiquement et de telle sorte que la première direction transversale ou la seconde direction transversale dans une première position de l'échangeur de chaleur par rapport à la première ou à la seconde direction d'écoulement est différente d'une première ou d'une seconde direction transversale dans une seconde position de l'échangeur de chaleur par rapport à la première ou à la seconde direction d'écoulement.
PCT/EP2022/054002 2021-02-17 2022-02-17 Échangeur de chaleur, procédé d'actionnement d'un échangeur de chaleur, procédé de production d'un échangeur de chaleur, machine frigorifique à gaz comprenant un échangeur de chaleur en tant que récupérateur, dispositif de traitement de gaz, et dispositif de ventilation et de climatisation WO2022175411A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP22708876.2A EP4294639A1 (fr) 2021-02-17 2022-02-17 Échangeur de chaleur, procédé d'actionnement d'un échangeur de chaleur, procédé de production d'un échangeur de chaleur, machine frigorifique à gaz comprenant un échangeur de chaleur en tant que récupérateur, dispositif de traitement de gaz, et dispositif de ventilation et de climatisation
AU2022223205A AU2022223205A1 (en) 2021-02-17 2022-02-17 Heat exchanger, method for operating a heat exchanger, method for producing a heat exchanger, gas refrigeration machine comprising a heat exchanger as a recuperator, device for treating gas, and ventilation and air conditioning device
JP2023549542A JP2024506406A (ja) 2021-02-17 2022-02-17 熱交換器、熱交換器の動作方法、熱交換器の製造方法、復熱器として熱交換器を有するガス冷凍機、ガス処理装置および空気調和装置
US18/446,638 US20230384038A1 (en) 2021-02-17 2023-08-09 Heat Exchanger, Method for Operating a Heat Exchanger, Method for Manufacturing a Heat Exchanger, Gas Refrigerating Machine Having a Heat Exchanger as Recuperator, Apparatus for Treating Gas and Air-Conditioning Device

Applications Claiming Priority (2)

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DE102021201532.8A DE102021201532A1 (de) 2021-02-17 2021-02-17 Wärmetauscher, verfahren zum betreiben eines wärmetauschers, verfahren zum herstellen eines wärmetauschers, gaskältemaschine mit einem wärmetauscher als rekuperator, vorrichtung zum behandeln von gas und raumlufttechnisches gerät
DE102021201532.8 2021-02-17

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US18/446,638 Continuation US20230384038A1 (en) 2021-02-17 2023-08-09 Heat Exchanger, Method for Operating a Heat Exchanger, Method for Manufacturing a Heat Exchanger, Gas Refrigerating Machine Having a Heat Exchanger as Recuperator, Apparatus for Treating Gas and Air-Conditioning Device

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EP (1) EP4294639A1 (fr)
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DE (1) DE102021201532A1 (fr)
WO (1) WO2022175411A1 (fr)

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AU2022223205A1 (en) 2023-08-31
JP2024506406A (ja) 2024-02-13
EP4294639A1 (fr) 2023-12-27
DE102021201532A1 (de) 2022-08-18
US20230384038A1 (en) 2023-11-30

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