EP3973242A1 - Échangeur thermique et procédé de refroidissement - Google Patents

Échangeur thermique et procédé de refroidissement

Info

Publication number
EP3973242A1
EP3973242A1 EP20728693.1A EP20728693A EP3973242A1 EP 3973242 A1 EP3973242 A1 EP 3973242A1 EP 20728693 A EP20728693 A EP 20728693A EP 3973242 A1 EP3973242 A1 EP 3973242A1
Authority
EP
European Patent Office
Prior art keywords
section
refrigerant
heat exchanger
channel
cross
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
EP20728693.1A
Other languages
German (de)
English (en)
Inventor
Andreas Wagner
Yixia XU
Ullrich Hesse
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Technische Universitaet Dresden
Original Assignee
Technische Universitaet Dresden
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 Technische Universitaet Dresden filed Critical Technische Universitaet Dresden
Publication of EP3973242A1 publication Critical patent/EP3973242A1/fr
Pending legal-status Critical Current

Links

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
    • F28D7/16—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 in parallel spaced relation
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
    • F28F1/18—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion the element being built-up from finned sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/02—Centrifugal separation of gas, liquid or oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/13—Economisers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • 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
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • Various exemplary embodiments relate to a heat exchanger and a cooling method.
  • a fluorinated refrigerant e.g. R14, R23, etc.
  • a fluorinated refrigerant e.g. R14, R23, etc.
  • Such fluorinated refrigerants pose a problem for environmental protection, for example due to their increased global warming potential (GWP).
  • GWP global warming potential
  • Sublimation of carbon dioxide (CO2) is an environmentally friendly alternative for cooling at low temperatures (e.g. at temperatures below -20 ° C, below -35 ° C, below -50 ° C, etc.), because CO2 is a natural refrigerant with a low GWP (e.g.
  • the GWP of CO2 is negligible compared to fluorinated refrigerants in applications in one low temperature range), non-flammable and non-toxic.
  • suitable operating conditions e.g. pressure, temperature, etc.
  • the solid to be sublimated can also be Refrigerant (e.g. solid particles of refrigerant) lead to a blockage of the refrigeration system.
  • Various embodiments relate to a heat exchanger.
  • the use of the heat exchanger described herein in a refrigeration system enables the refrigeration system to also be used for a sublimation-based cooling process, and thus for cooling at a temperature level of below -50 ° C.
  • a heat exchanger can have at least one channel for guiding refrigerant, wherein the at least one channel has a first section and a second section, the first section in relation to a flow direction of the refrigerant in the at least one channel upstream relative to the second Section is arranged, wherein the second section has a cross-sectional area which is larger than a cross-sectional area of the first section, so that a sublimation of the refrigerant is made possible in the second section.
  • the first section can serve to distribute and expand the refrigerant (e.g. the liquid refrigerant, e.g. above the triple point).
  • the channel can be set up in such a way that no heat transfer (from the refrigerant) takes place (or can take place) in the first section.
  • the channel can be set up in such a way that the heat transfer (only) takes place in the second section.
  • the solid refrigerant is located in the second section (below the triple point) and the heat transfer can take place.
  • the channel can clearly be set up in such a way that the refrigerant is in the two sections at different pressures and states.
  • a cooling method for cooling a fluid by means of sublimation of a refrigerant can have the following: providing a refrigerant to a heat exchanger, the heat exchanger having at least one channel for guiding refrigerant; Guiding the refrigerant into the at least one channel, the at least one channel having a first section and a second section, the first section being arranged upstream relative to the second section with respect to a flow direction of the refrigerant in the at least one channel, the second section has a cross-sectional area which is greater than one Cross-sectional area of the first section, so that sublimation of the refrigerant is enabled in the second section; Providing a heat transfer between the refrigerant flowing into the second section and the fluid to be cooled, so that the refrigerant flowing into the second section can sublime and the fluid to be cooled can be cooled.
  • FIG. 1 shows a heat exchanger in a schematic
  • FIG. 2A, FIG. 2B, FIG. 2C, FIG. 2D, FIG. 2E and FIG. 2F each show a part of a channel of a heat exchanger in a schematic representation according to various embodiments;
  • FIG. 2G shows a container and a channel of a heat exchanger in a schematic illustration according to various embodiments
  • Figure 3 shows a refrigeration system having a heat exchanger
  • FIG. 4 shows a refrigeration system having a heat exchanger
  • Figure 5 shows a refrigeration system having a heat exchanger
  • FIG. 6 shows a refrigeration system having a heat exchanger in a schematic illustration according to various embodiments.
  • FIG. 7 a refrigeration system having a heat exchanger in
  • the terms “connected”, “connected” and “coupled” are used to describe both a direct and an indirect connection, a direct or indirect connection and a direct or indirect coupling.
  • identical or similar elements are provided with identical reference symbols, as far as this is appropriate.
  • the term "at least one” is used for the sake of brevity, which can mean: one, exactly one, several (e.g. exactly two, or more than two), many (e.g. exactly three or more than three ), etc.
  • the meaning “several” does not necessarily have to mean that there are several identical elements, but essentially functionally identical elements.
  • a channel is used to describe both a channel which is formed by a single tube (for example a single mini-channel) and a channel which is formed by a plurality of tubes (for example a plurality of mini-channels ) is formed.
  • a channel can be formed by a single tube, and a plurality of channels can be formed by a plurality of individual tubes which are arranged, for example, parallel to one another.
  • a channel can be formed by a plate, such as a flat metal plate (e.g. made of aluminum), in which a plurality of tubes (e.g. a plurality of mini-channels) are formed, for example by making a plurality of openings along a length of the plate.
  • a plurality of channels can have a plurality of plates, which can be arranged parallel to one another and in each of which a plurality of tubes (e.g. a plurality of mini-channels) are formed.
  • mini-channel is used to describe a channel which has a cross-section which ranges from hundreds of micrometers to a few millimeters.
  • the cross section of a mini-channel can have a size along a direction perpendicular to a direction of flow of a fluid in the channel (e.g.
  • a height, a width, a diameter, an edge length, etc. which is in a range from approximately 100 ⁇ m to approximately 20 mm, for example in a range from approximately 200 gm to approximately 15 mm, for example in a range from approximately 500 ⁇ m to approximately 10 mm, for example in a range from approximately 1 mm to approximately 5 mm, for example in a range from approximately 100 ⁇ m to approximately 1.5 mm.
  • These areas can relate, for example, to a section of the channel in which there is a heat transfer between a fluid flowing in the channel (for example a refrigerant flowing in the channel) and another fluid (for example to be cooled).
  • a mini-channel can be formed by a plurality of tubes, each of which has a cross section in one of the areas shown above.
  • upstream is used to describe the relative disposition of one or more elements with respect to a direction of flow of a fluid (e.g., a refrigerant).
  • a fluid e.g., a refrigerant
  • upstream relative to an element can describe a location which is located in front of the element (e.g. in front of an entry of the element) so that the fluid flows first through that location and then into the element.
  • a first element can be arranged upstream relative to a second element, so that the fluid first flows into the first element and then into the second element.
  • upstream does not necessarily mean that the first element and the second element are arranged directly next to one another, but other elements can also be arranged between the first element and the second element along the flow direction.
  • downstream is used to describe the relative arrangement of one or more elements with respect to a flow direction of a fluid (eg a refrigerant).
  • a fluid eg a refrigerant
  • downstream relative to an element can describe a point which is arranged after the element (eg after an exit of the element) so that the fluid first flows into the element and then through this point.
  • a first element can be arranged downstream relative to a second element, so that the fluid first flows into the second element and then into the first element.
  • downstream does not necessarily mean that the first element and the second element are arranged directly next to one another, but other elements can also be arranged between the first element and the second element along the flow direction.
  • a conventional heat exchanger e.g. a conventional evaporator
  • a conventional heat exchanger can also have several ribs which are arranged between the channels and which increase the area available for the heat transfer.
  • Such a heat transfer design e.g. with fins
  • the absorption of heat in a heat exchanger by sublimation presents various challenges compared to evaporating refrigerants.
  • the heat transfer is reduced and the accumulation of solid particles of refrigerant can lead to blockages and blockages in the heat exchanger.
  • a cooling system e.g. a refrigeration system
  • a refrigerant does not circulate back in the system after a heat transfer with a fluid to be cooled, but the refrigerant is lost into the environment. In other words, after evaporation or sublimation, the refrigerant is no longer available.
  • the refrigerant remains in a closed circuit after the heat transfer with the fluid to be cooled in the system, so that the refrigerant can be compressed again and made available to the heat exchanger for repetition of the process.
  • Cooling by means of sublimation a refrigerant is usually carried out in an open circuit, for example by spraying the refrigerant to be sublimated onto a surface to be cooled, so that large amounts of refrigerant should be used.
  • the sublimation in a closed circuit is hindered due to the blockage (e.g. damage) of the components of the refrigeration system (e.g. the compressor), which is caused by the solid refrigerant to be sublimated (e.g. solid particles of refrigerant).
  • One possibility could be to transport the solid refrigerant particles by means of a carrier fluid. In such a configuration, however, additional energy would be required to circulate the carrier fluid.
  • the refrigerant should be separated from the carrier fluid after sublimation in order to be able to be compressed again within the framework of the refrigeration cycle. Such a separation would require a high level of technical complexity and would cause pressure losses, which can have a negative effect on the refrigeration capacity and the efficiency of the process.
  • a heat exchanger with several channels could represent a suitable type of heat transfer for sublimation.
  • the increased heat transfer surface due to the high number of channels can compensate for the reduced heat transfer. If individual channels were blocked, additional channels would remain for the heat transfer, so that a refrigeration system in which the heat exchanger is used can continue to work.
  • a distributor on an evaporator consists of a type of container into which the channels (eg the mini-channels) protrude.
  • the refrigerant to be evaporated in the liquid and / or gaseous state of aggregation is distributed over the various channels.
  • a refrigerant to be sublimated e.g. CO 2
  • CO 2 which is solid and If it were to enter the container in gaseous form, its solid particles would clog the channel entrances.
  • Fig.l illustrates a heat exchanger 100 in a schematic representation according to various embodiments.
  • the heat exchanger 100 can have at least one channel 102 (e.g. at least one mini-channel) for conducting refrigerant.
  • the heat exchanger 100 can be set up in such a way that the refrigerant flows into the at least one channel 102 and can be in a heat transfer relationship with a fluid to be cooled (eg air, water, salt water, etc.), so that heat is removed from the fluid to be cooled into which refrigerant flowing into the at least one channel 102 can be received.
  • the at least one channel 102 can also have multiple tubes (e.g. multiple mini-channels, multiple mini-channel tubes, etc.) for guiding refrigerant, which can be arranged, for example, parallel to one another.
  • the heat exchanger 100 can also have a plurality of channels 102 for guiding refrigerant, which channels can for example be arranged parallel to one another.
  • the at least one channel 102 can have a first section 102-1 and a second section 102-2. With respect to a flow direction of the refrigerant in the at least one channel 102, the first section 102-1 can be arranged upstream relative to the second section 102-2. In other words, the at least one channel 102 can be set up such that the Refrigerant initially flows into the first section 102-1 and then into the second section 102-2. According to various embodiments, the second section 102-2 can be arranged directly next to the first section 102-1.
  • the second section 102-2 can have a cross-sectional area which is larger than a cross-sectional area of the first section 102-1, so that sublimation of the refrigerant in the second section 102-2 is made possible.
  • the heat exchanger 100 can be set up in such a way that the refrigerant is in a heat transfer relationship with a fluid to be cooled when the refrigerant flows into the second section 102-2, so that heat from the fluid to be cooled is transferred into the second section 102-2. 2 flowing refrigerants can be included.
  • the heat exchanger 100 can clearly be set up in such a way that the refrigerant can sublime in the second section 102-2 due to the heat transfer with the fluid to be cooled.
  • the refrigerant should be in an at least partially solid state (e.g. in a solid / gaseous state). Furthermore, the refrigerant should be at such a temperature level and / or pressure level that a direct phase change from a solid physical state to a gaseous physical state is made possible. In other words, the refrigerant should be at such a temperature level and / or pressure level which define a location in the phase diagram of the refrigerant in which sublimation of the refrigerant is possible.
  • a fluid e.g., refrigerant
  • a restriction e.g., into a throttle opening such as a portion of a tube with reduced cross-sectional area
  • the velocity of the fluid increases and, as a result, the pressure of the fluid is reduced.
  • the fluid can be at a high pressure level (for example at a pressure level in a range from approximately 10 bar to about 160 bar, for example from about 70 bar to about 140 bar, for example from about 40 bar to about 70 bar).
  • the fluid reaches a critical (sound) speed (a so-called stuffing limit, in English "choked flow"), so that the pressure in the throttle is at a lower pressure level (e.g.
  • a further expansion of the fluid follows downstream relative to the throttle and the pressure of the fluid continues to drop (for example to a pressure level in a range from approximately 0 bar to approximately 5 bar).
  • pressure ranges described herein are selected as examples, and they can apply, for example, to CO2 as a refrigerant to be sublimated. It goes without saying that the pressure ranges can be dependent on the refrigerant used to be sublimated, and can be adapted accordingly based on the refrigerant used.
  • the cross-sectional area of the first section 102-1 can be smaller than the cross-sectional area of the second section 102-2, so that the first section 102-1 provides a throttle point at the entry of the at least one channel 102.
  • the first section 102-1 is a throttle point at the inlet of the at least one channel 102.
  • the cross-sectional area of the first section 102-1 can be dimensioned such that a refrigerant is at a high pressure level in front of the first section 102-1 (for example at a pressure level in a range from approximately 10 bar to approximately 160 bar, for example from approximately 70 bar to about 140 bar, for example from about 40 bar to about 70 bar);
  • the refrigerant reaches a critical (sonic) speed, so that the pressure of the refrigerant in the first section 102-1 increases a lower pressure level (for example at a pressure level in a range from about 10 bar to about 70 bar, for example from about 10 bar to about 40 bar, for example from about 40 bar to about 70 bar) falls; and after the first section 102-1 (in other words, downstream relative to the first section 102-1, when entering the second section 102-2) there is a further expansion of the refrigerant and the pressure of the refrigerant drops further, for example to a sublimation pressure level (eg at a pressure level in a range from about
  • the cross-sectional area of the first section 102-1 can be dimensioned such that the pressure of the refrigerant in the first section 102-1, clearly up to the outlet of the first section 102-1, is above the sublimation pressure of the refrigerant, so that the Refrigerant cannot sublime in the first section 102-1.
  • the cross-sectional area of the first section 102-1 can be dimensioned in such a way that the drop in pressure of the refrigerant flowing into the first section 102-1 is not sufficient to enable sublimation of the refrigerant in the first section 102-1.
  • the cross-sectional area of the first section 102-1 can thus be dimensioned in such a way that sublimation of the refrigerant in the first section 102-1 is prevented.
  • the heat exchanger can be set up (e.g. the first section can be dimensioned in such a way) that no heat transfer takes place between the refrigerant flowing into the first section and the fluid to be cooled.
  • the refrigerant instead exchanges heat with the fluid while it is flowing in the first section.
  • an evaporation of the liquid Occur in the refrigerant heat beforehand at a higher temperature.
  • an additional component would be used for the distribution of the solid refrigerant in the first section (otherwise blockage by solid refrigerant could occur before the first section).
  • the cross-sectional area of the first section 102-1 can be dimensioned such that the refrigerant in the first section 102-1 is at a pressure level that is greater than the pressure level of the triple point of the refrigerant.
  • the cross-sectional area of the first section 102-1 can be dimensioned such that the refrigerant in the first section 102-1 is or is in a non-solid (eg liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state can be located.
  • the cross-sectional area of the first section 102-1 can be dimensioned such that the refrigerant is at such a pressure level that the refrigerant in the first section 102-1 is in a non-solid (eg liquid, gaseous, liquid) / gaseous, supercritical, etc.) physical state.
  • the cross-sectional area of the first section 102-1 can be dimensioned such that the critical mass flow through the throttle point, which is dependent on the inlet pressure and / or on the inlet temperature (e.g. the pressure and / or the temperature at the inlet of the first section 102-1) (in other words by the first section 102-1) is reached and the critical outlet pressure (for example the pressure at the outlet of the first section 102-1) is above the triple point of the refrigerant.
  • a clogging of the throttle point for example a blockage of the first section 102-1, and thus of the at least one channel 102
  • the refrigerant is in the throttle point (in other words, in the first section 102-1) is in a non-solid aggregate state. Only after exiting the throttle point (in other words when entering the second section 102-2) does the refrigerant expand to the sublimation pressure level.
  • the cross-sectional area of the first section 102-1 and the cross-sectional area of the second section 102-2 can be dimensioned such that the pressure of a refrigerant flowing into the at least one channel 102 is downstream relative to the first section 102-1 (in other words in Entry into the second section 102-2) is lower (eg 5 bar lower, 10 bar lower, 20 bar lower, 30 bar lower, 50 bar lower, etc.) than the pressure in the first section 102-1.
  • the cross-sectional area of the first section 102-1 can be dimensioned such that the refrigerant is at a pressure level in a range from approximately 10 bar to approximately 70 bar (for example from approximately 10 bar to approximately 40 bar, from approximately 40 bar to approximately 70 bar bar, etc.) is located in the first section 102-1.
  • the cross-sectional area of the second section 102-2 can be dimensioned such that the refrigerant is at a pressure level in a range from approximately 0 bar to approximately 5 bar (e.g. at an atmospheric pressure level) in the second section 102-2.
  • the cross-sectional area of the first section 102-1 and the cross-sectional area of the second section 102-2 can be dimensioned such that a refrigerant flowing into the at least one channel 102 is at such a pressure level downstream relative to the first section 102-1 ( eg in the second section 102-2) is that the sublimation of the refrigerant is made possible.
  • the cross-sectional area of the first section 102-1 and the cross-sectional area of the second section 102-2 can be dimensioned such that the refrigerant is at a pressure level suitable for sublimation (e.g. at a sublimation pressure level, such as atmospheric pressure, if the refrigerant comprises CO2) when it flows into the second section 102-2.
  • the throttling of the refrigerant upon entry into the at least one channel 102 ensures that the sublimation region of the refrigerant can only be reached in the at least one channel 102 (e.g. in the second section 102-2).
  • the throttling of the refrigerant upon entry into the at least one channel 102 enables refrigerant to be provided to the at least one channel 102 in a non-sublimable (e.g. non-solid) aggregate state and that the refrigerant only enters the at least one channel 102 passes into a sublimable (eg at least partially solid) aggregate state.
  • the throttle point can be dimensioned such that the refrigerant from the liquid or liquid / gaseous aggregate state upstream relative to the first section 102-1 into an at least partially solid (e.g. solid / gaseous) aggregate state downstream relative to the first section 102-1 (in other words in the second section 102-2) is expanded.
  • the cross-sectional area of the first section 102-1 and the cross-sectional area of the second section 102-2 can be dimensioned in such a way that the pressure drops when the refrigerant flows from the first section 102-1 into the second section 102-2, so that the refrigerant changes from a non-solid (e.g.
  • the cross-sectional area of the first section 102-1 and the cross-sectional area of the second section 102-2 can be dimensioned in such a way that there is such a drop in pressure that the refrigerant is a sublimation region of the phase diagram of the refrigerant in the second section 102-2 reached .
  • the first section 102-1 can have a cross-sectional area in a range from approximately 0.0001 mm 2 to approximately 0.8 mm 2 , for example in a range from approximately 0.001 mm 2 to approximately 0.5 mm 2 , for example in a range of approximately 0.005 mm 2 to about 0.25 mm 2 .
  • the second section 102-2 can have a cross-sectional area in a range from approximately 0.01 mm 2 to approximately 400 mm 2 , for example in a range from approximately 0.1 mm 2 to approximately 100 mm 2 , for example in a range of approximately 0.5 mm 2 to about 50 mm 2 , for example in a range from about 1 mm 2 to about 20 mm 2 .
  • the heat exchanger 100 can thus serve as a sublimator, even if a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) refrigerant is provided to it.
  • a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) refrigerant is provided to it.
  • a conventional heat exchanger could be adapted by means of the design of the channel or channels described here in such a way that it could also be used for the sublimation of refrigerants (e.g. CO2).
  • the arrangement described herein thus represents a comparatively inexpensive option for a sublimator which could be used in a closed cooling circuit.
  • the heat exchanger 100 can thus be set up in such a way that it can receive a refrigerant in a non-solid state of aggregation, and the refrigerant within the heat exchanger 100 changes to an at least partially solid state of aggregation, so that sublimation of the refrigerant is made possible.
  • the refrigerant can have a natural refrigerant, such as carbon dioxide (CO2)
  • the refrigerant can also have a hydrocarbon-based refrigerant, such as HFC, HCFC, HFO, R170, R290, R600, etc.
  • the refrigerant can a mixture of a plurality of mutually different refrigerants exhibit. It goes without saying that the refrigerant can be selected based on the desired operation of the heat exchanger 100 (eg on the temperature range to be achieved).
  • the heat exchanger 100 can have at least one heat transfer element 104 which is arranged in contact (e.g. in direct physical contact) with the at least one channel 102.
  • the at least one heat transfer element 104 can be configured, for example, as an outer protrusion or a plurality of outer protrusions from the surfaces of the at least one channel 102 (such as, for example, a rib, a plurality of ribs, a lamella, a plurality of lamellae, etc.).
  • the heat exchanger 100 can also have a plurality of heat transfer elements 104, which can be arranged in contact with the at least one channel 102 or between two adjacent channels 102.
  • the at least one heat transfer element 104 can be configured to provide the area available for heat transfer between the fluid to be cooled and the refrigerant flowing into the at least one channel 102 (eg into the second section 102-2 of the at least one channel 102) so that the heat transfer rate and the overall efficiency of the heat exchanger 100 can be improved.
  • the heat exchanger 100 can be set up such that the fluid to be cooled can flow through the at least one heat transfer element 104 (for example in a direction at an angle to or perpendicular to the flow direction of the refrigerant in the at least one channel 102) and heat in a more efficient manner can dispense the refrigerant.
  • the heat exchanger 100 can have a first container 106 (eg a distributor container).
  • the first container 106 can be set up to supply the refrigerant to the at least one channel 102.
  • the first container 106 can be set up to distribute the refrigerant to the multiple tubes (eg to the multiple mini-channels) of the at least one channel 102 or to the channels 102 of the plurality of channels 102 (eg evenly).
  • the arrangement described herein enables simple supply or distribution of the refrigerant (eg to be sublimated) by means of the first container 106, because the refrigerant is in a non-solid (eg liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state or can be located when this flows into the first container 106.
  • the first container 106 can be set up such that a refrigerant flowing into the first container 106 is in a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state.
  • a refrigerant to be sublimated can also be supplied or distributed in a simple manner, and only when it enters the at least one channel 102 (e.g. when it enters the second section 102-2) does it change into an at least partially solid state of aggregation.
  • the first container 106 can be set up in such a way that the refrigerant is at a medium pressure level or a high pressure level (for example at a pressure level in a range from approximately 10 bar to approximately 160 bar, for example from approximately 70 bar to approximately 140 bar, for example from approximately 40 bar to approximately 70 bar, for example from approximately 10 bar to approximately 40 bar, etc.) in the first container 106.
  • the first container 106 can thus be set up in such a way that the refrigerant is completely liquid or liquid / gaseous or supercritical in the first container 106.
  • the first container 106 can be set up in such a way that the refrigerant is at a pressure level in the first container 106 which is (for example always) above the pressure level of the triple point of the refrigerant.
  • the throttling at a low pressure level (eg at a pressure level in a range from approximately 0 bar to approximately 5 bar) occurs in the second section 102-2 of the at least one channel 102.
  • the first container 106 can be configured as a separator (e.g. as a medium-pressure separator) for separating a liquid phase of the refrigerant from a gas phase of the refrigerant.
  • the first container 106 can be set up to supply the liquid refrigerant to the at least one channel 102 or to distribute the liquid refrigerant to the channels of the plurality of channels 102, and to output the gaseous refrigerant through an additional outlet (eg a gas outlet) .
  • an additional outlet eg a gas outlet
  • the first container 106 can be set up in such a way that it is thermally insulated from a fluid to be cooled.
  • the first container 106 can have a (e.g., thermal) coating or be or be coated by means of a coating which is set up to thermally isolate the first container 106 from a fluid to be cooled, which flows over or through the heat exchanger 100. The consequence of this is that subcooling of the refrigerant in the first container 106 can be prevented, so that the refrigerant in the first container 106 does not change into a sublimable (e.g. into an at least partially solid) physical state.
  • a sublimable e.g. into an at least partially solid
  • the heat exchanger 100 can have a second container 108 (for example a collecting container).
  • the second container 108 may be configured to receive the refrigerant discharged from the at least one channel 102.
  • the second container 108 can be set up to contain solid refrigerant components (e.g. solid particles of refrigerant) to accumulate.
  • solid refrigerant components e.g. solid particles of refrigerant
  • solid refrigerant constituents of the refrigerant can form.
  • These solid refrigerant components can sublime in the second section 102-2 due to the heat transfer with the fluid to be cooled. In the event that some of these solid refrigerant components do not sublime, these some refrigerant components can be problematic for a refrigeration system.
  • these solid refrigerant components can damage a compressor.
  • the second container 108 can thus be set up in such a way that solid refrigerant components discharged from the at least one channel 102 collect in the second container 108. An undesired circulation of these refrigerant components in a refrigeration system can thus be prevented.
  • the second container 108 can be set up as a solids separator (e.g. as a cyclone separator).
  • the second container 108 can be set up in such a way that it emits gaseous refrigerant from a first outlet and collects solid refrigerant (e.g. solid refrigerant components, such as solid particles of refrigerant).
  • the second container 108 may have a second outlet for discharging the accumulated solid refrigerant. If the heat exchanger 100 is used in a refrigeration system, the second container 108 can in this way make it possible that only gaseous refrigerant is provided for circulation in the refrigeration system.
  • FIG. 2A, FIG. 2B, FIG. 2C, FIG. 2D, FIG. 2E and FIG. 2F each illustrate a part of a channel 102 of a heat exchanger 100 in a schematic representation according to various embodiments.
  • the first section 102-1 and the second section 102-2 of the at least one channel 102 can be dimensioned and / or shaped as desired in such a way that the Effect can be achieved that the sublimation of the refrigerant is only made possible in the second section 102-2.
  • the first section 102-1 and / or the second section 102-2 can have any shape cross section, such as a circular cross section, an elliptical cross section, a square cross section, a rectangular cross section, a polygonal cross section, etc.
  • the cross section of the first section 102-1 can have the same shape as the cross section of the second section 102-2.
  • the cross section of the first section 102-1 and the cross section of the second section 102-2 can, however, also have a different shape from one another.
  • the first section 102-1 can have a cross section which does not change along a flow direction of the refrigerant in the first section 102-1 (e.g. along a direction 101, for example a length of the first section 102-1).
  • the first section 102-1 can also have a cross section which changes along a flow direction of the refrigerant in the first section 102-1 (e.g. along a direction 101, such as a length of the first section 102-1).
  • a shape and / or a size of the cross section of the first section 102-1 can change.
  • the second section 102-2 can have a cross section which does not change along a flow direction of the refrigerant in the second section 102-2 (for example along a direction 101, for example a length of the second section 102-2).
  • the second section 102-2 can, however, also have a cross section which changes along a flow direction of the refrigerant in the second section 102-2 (for example along a direction 101, for example a length of the second section 102-2).
  • a shape and / or a size of the cross section of the second section 102-2 can change.
  • the first section 102-1 and the second section 102-2 can be set up in such a way that a sudden (in other words, abrupt) change in the cross-sectional area at the interface between the first section 102-1 and the second section 102-2 is provided as shown for example in Fig. 2A.
  • the second section 102-2 can, however, also have a cross-sectional area which, starting from the interface with the first section 102-1, gradually increases until a desired cross-sectional area is reached, as shown for example in FIG. 2B.
  • the second section 102-2 can have a tapered shape. In this embodiment there is thus a gradual change in the cross-sectional area.
  • the shape and the cross-sectional area of the first section 102-1 and of the second section 102-2 can thus be selected as desired, for example as a function of the refrigerant and / or other operating parameters of a refrigeration system in which the heat exchanger 100 should be used.
  • the cross section of the first section 102-1 can have a size along a direction perpendicular to the flow direction of the refrigerant in the at least one channel 102 (eg perpendicular to a direction 101, such as a height, a width, a diameter, an edge length , etc.), which is in a range from approximately 0.01 mm to approximately 0.5 mm, for example in a range from approximately 0.01 mm to approximately 0.2 mm, for example in a range from approximately 0.02 mm to approximately 0.1 mm, for example in a range from about 0.02 mm to about 0.05 mm.
  • a direction 101 such as a height, a width, a diameter, an edge length , etc.
  • the cross section of the first section 102-1 can have a size along a direction perpendicular to the direction of flow of the refrigerant in the at least one channel 102, which is smaller than 0.1 mm.
  • the cross section of the first section 102-1 can, for example, be dimensioned such that a refrigerant flowing into the first section 102-1 reaches a critical speed (for example a speed of sound).
  • the first section 102-1 can have a size along a direction parallel to the direction of flow of the refrigerant in the at least one channel 102 (for example along a direction 101, for example a length of the first section 102-1), which is dimensioned in this way that the refrigerant in the first section 102-1 remains in a non-solid aggregate state.
  • the length of the first section 102-1 can be dimensioned such that the drop in the pressure of the refrigerant flowing into the first section 102-1 is not sufficient to allow sublimation of the refrigerant in the first section 102-1 ( e.g. to achieve a pressure level below the triple point of the refrigerant).
  • the cross section of the second section 102-2 can have a size along a direction perpendicular to the direction of flow of the refrigerant in the at least one channel 102 (eg perpendicular to a direction 101, such as a height, a width, a diameter, an edge length , etc.), which is in a range from about 0.1 mm to about 20 mm, for example from about 0.5 mm to about 10 mm, for example from about 1 mm to about 5 mm.
  • the second section 102-2 can have a size along a direction parallel to the flow direction of the refrigerant in the at least one channel 102 (for example along a direction 101, for example a length of the second section 102-2), which is dimensioned in this way that a complete sublimation of the refrigerant in the second section 102-2 can be made possible.
  • a wire of the desired size (eg with the desired diameter) can be inserted into a conventional channel (eg into a conventional mini-channel); the initial section of the channel can then be upset; and the wire can finally be removed, as a result of which a channel 102 having a first portion 102-1 with a reduced cross-sectional area is provided.
  • the inserted wire can be coated so that after upsetting the coating can be burned out by means of heating. As a result, a free space is created between the channel 102 (for example between an inner surface of the channel 102) and the wire, so that the wire can be removed in a simpler manner.
  • several wires can be used (for example at the same time) in order to modify several channels (for example several mini-channels) or several pipes of a channel.
  • a channel can be compressed up to the closure of the entry of the channel, and then a hole (eg by means of drilling, by means of lasers, etc.) can be made in the channel, so that as a result a channel 102 having a first section 102-1 can be provided with a reduced cross-sectional area.
  • a hole e.g. several mini-channels
  • several tubes of a channel can be modified at the same time, so that a hole can be made in the respective channel or in the respective tube.
  • a constricting element 210 (eg a sleeve, a perforated disk, a perforated plate, a cap, etc.) can be used to reduce the cross-sectional area of the first section 102-1 or to provide a throttle point at the entry of the at least one channel 102 , as shown for example in Fig.2C to 2F.
  • the constricting element 210 can be any suitable element so that a throttle point is provided when the at least one channel 102 enters.
  • the constricting element 210 can have any suitable cross section (eg an inner cross section), such as a circular cross section, an elliptical cross section, a square cross section, a rectangular cross section, a polygonal cross section, etc.
  • the cross section (e.g. the inner cross section) of the constricting element 210 may have a size (e.g. an inner size) along a direction perpendicular to the flow direction of the refrigerant in the constricting element 210 (e.g. perpendicular to a direction 101, e.g. a height, a width , a diameter, an edge length, etc.) which is in a range from approximately 0.01 mm to approximately 0.5 mm, for example in a range from approximately 0.01 mm to approximately 0.2 mm, for example in a range from approximately 0.02 mm to approximately 0.1 mm, for example in a range from approximately 0.02 mm to approximately 0.05 mm.
  • a size e.g. an inner size along a direction perpendicular to the flow direction of the refrigerant in the constricting element 210 (e.g. perpendicular to a direction 101, e.g. a height, a width , a diameter, an edge length, etc
  • the cross section of the narrowing element 210 may have a size along a direction perpendicular to the flow direction of the refrigerant in the narrowing element 210, which is smaller than 0.1 mm.
  • the cross section of the constricting element 210 can, for example, be dimensioned such that a refrigerant flowing into the constricting element 210 reaches a critical speed (e.g. a speed of sound) in the constricting element 210 (and clearly in the first section 102-1).
  • the cross section (eg the inner cross section) of the constricting element 210 can be dimensioned such that sublimation of the refrigerant in the constricting element 210 (and clearly in the first section 102-1) is prevented.
  • the cross section of the constricting element 210 can be dimensioned in such a way that the refrigerant is at a pressure level in the constricting element 210 at which sublimation of the refrigerant is impossible.
  • the cross section of the constricting element 210 be dimensioned such that the refrigerant in the constricting element 210 is in a non-solid (eg liquid, gaseous, liquid / gaseous, supercritical) physical state.
  • the cross section of the narrowing element 210 can be dimensioned such that the refrigerant is at a pressure level in the narrowing element 210 which is greater than the pressure level of the triple point of the refrigerant.
  • the constricting element 210 can have a size along a direction parallel to the flow direction of the refrigerant in the constricting element 210 (eg along a direction 101, for example a length of the constricting element 210), which is dimensioned such that the refrigerant in the constricting element 210 remains in a non-solid aggregate state.
  • the length of the constricting element 210 can be dimensioned in such a way that the drop in the pressure of the refrigerant flowing into the constricting element 210 is not sufficient to allow sublimation of the refrigerant in the constricting element 210 or to achieve a pressure level below the To achieve triple pressure of the refrigerant.
  • the at least one channel 102 can have a narrowing element 210, which is arranged in the first section 102-1, so that the cross-sectional area of the first section 102-1 can be reduced, as shown in FIGS. 2C and 2D is.
  • the constricting element 210 can be placed in a channel, and the channel (eg the entry of the channel) can be compressed so that the constricting element 210 is fixed, and as a result a channel 102 having a first section 102-1 with a reduced cross-sectional area can be provided.
  • a constricting element can be arranged in each channel of a plurality of channels or in each tube (for example in each mini-channel) of a channel.
  • the constricting element 210 can be arranged completely within the at least one channel 102 (for example within the first section 102-1), as is illustrated, for example, in FIG. 2C.
  • the constricting element 210 can, however, also have a part which is arranged outside the at least one channel 102 (for example outside the first section 102-1), as is shown, for example, in FIG. 2D.
  • the constricting element 210 can be arranged (e.g. fastened, such as soldered, etc.) at the entry of the at least one channel 102, as is shown, for example, in FIGS.
  • the narrowing element 210 can have a length or a thickness in a range from approximately 1 ⁇ m to approximately 500 ⁇ m, for example in a range from approximately 50 ⁇ m to approximately 200 ⁇ m.
  • the constricting element 210 can be a thin plate (e.g. a sheet metal, a disk) in which one or more holes are made, as is shown for example in FIG. 2E.
  • the constricting element 210 can be a cap which is arranged at the entry of the at least one channel 102 and in which one or more holes are introduced, as is shown, for example, in FIG. 2F.
  • the narrowing element 210 can form an additional part of the at least one channel 102.
  • the narrowing element 210 can thus serve as a first section 102 - 1 of the at least one channel 102, and the at least one channel 102 can serve as a second section 102-2 of the at least one channel 102.
  • the constricting element 210 and the at least one channel 102 can be set up or dimensioned in such a way that a refrigerant in front of the constricting element 210 is at a high pressure level (for example at a pressure level in a range from approximately 10 bar to approximately 160 bar , for example in a range from about 70 bar to about 140 bar, for example in a range from about 40 bar to about 70 bar);
  • a critical (sonic) speed so that the pressure of the refrigerant in the constricting element 210 is at a lower pressure level (for example at a pressure level in a range from approximately 10 bar to approximately 70 bar, for example from about 10 bar to about 40 bar, for example from about 40 bar to about 70 bar); and after the constricting element 210 (for example when entering the at least one channel 102) there is a further expansion of the refrigerant and the pressure of the refrigerant drops further, for example at a sublimation pressure level
  • a heat exchanger 100 can have at least one channel 102 for conducting refrigerant, and at least one narrowing element 210 which is arranged upstream relative to the at least one channel 102, the at least one channel 102 having a cross-sectional area which is greater than a cross-sectional area (for example, an inner cross-sectional area) of the at least one narrowing element 210, so that sublimation of the refrigerant in the at least one channel 102 is made possible.
  • a cross-sectional area for example, an inner cross-sectional area
  • Fig. 2G illustrates a container 106 and a channel 102 of a heat exchanger 100 in a schematic illustration according to various embodiments.
  • first container 106 and the at least one channel 102 are shown in FIG. 2G. It goes without saying that the other elements of the heat exchanger 100 (e.g. the second container 106, the at least one heat transfer element 104, etc.) are also present.
  • the other elements of the heat exchanger 100 e.g. the second container 106, the at least one heat transfer element 104, etc.
  • the at least one channel 102 can be introduced into the first container 106 (for example by means of soldering).
  • the at least one channel 102 can protrude into the first container 106 in such a way that the first section 102-1 is sufficiently removed from the connection point (eg from the soldering point) between the at least one channel 102 and the first container 106, so that undesired modifications of the first section 102-1 (in other words, the throttle point) can be avoided.
  • the at least one channel 102 can be introduced into the first container 106 at a depth t E such that undesired modifications of the first section 102-1 can be avoided.
  • the constricting element 210 can comprise a material which is different from the solder used is not wetted.
  • Fig. 3 illustrates a refrigeration system 300 having a heat exchanger 100 in a schematic representation according to various embodiments.
  • the heat exchanger 100 can be inserted into a refrigeration system 300 (eg in a cooling system), so that the refrigeration system 300 is also used for a sublimation-based cooling process, and thus for cooling at a temperature level of below -50 ° C can be.
  • the refrigeration system 300 can be a conventional (e.g. Cold vapor-based) refrigeration system in which an evaporator has been replaced by the heat exchanger 100 described herein.
  • the refrigeration system 300 can have a compressor 312 (e.g. a reciprocating compressor, a screw compressor, a rotary compressor, a centrifugal compressor, a scroll compressor, etc.) which is arranged downstream relative to the heat exchanger 100.
  • the refrigeration system 300 can be set up in such a way that the refrigerant output by the heat exchanger 100, which is in a gaseous state after sublimation, is fed to the compressor 312.
  • the compressor 312 can be in (e.g. fluidic) communication with the heat exchanger 100, e.g.
  • the compressor 312 and the heat exchanger 100 can be connected to one another (e.g. by means of a line such as a suction line).
  • the compressor 312 can be set up to suck in the refrigerant from the outlet of the heat exchanger 100 (e.g. from the second container 108, such as from a gas outlet of the second container 108).
  • the compressor 312 can be configured to compress the refrigerant.
  • the compressor 312 can thus be set up, for example, that it receives the refrigerant at a low pressure (eg at a pressure level in a range from approximately 0 bar to approximately 5 bar), and the refrigerant at a high pressure (eg at a pressure level in a range from about 10 bar to about 160 bar, for example from about 70 bar to about 140 bar, for example from about 40 bar to about 70 bar).
  • the compressor 312 can furthermore be set up to circulate the refrigerant in the refrigeration system 300, so that the refrigerant can circulate in the refrigeration system 300.
  • the refrigeration system 300 can have a heat-emitting heat exchanger 314 (eg a condenser, a gas cooler, etc.), which is arranged downstream relative to the compressor 312.
  • the refrigeration system 300 can be set up in such a way that the refrigerant compressed by the compressor 312 is fed to the heat-emitting heat exchanger 314.
  • the heat-emitting heat exchanger 314 can be in (eg fluidic) connection with the compressor 312, for example the heat-emitting heat exchanger 314 and the compressor 312 can be or will be connected to one another (eg by means of a line, such as a gas line).
  • a line such as a gas line
  • the heat-emitting heat exchanger 314 can be arranged upstream relative to the heat exchanger 100.
  • the refrigeration system 300 can thus be set up in such a way that the refrigerant output by the heat-emitting heat exchanger 314 is fed to the heat exchanger 100 (e.g. the first container 106).
  • the exothermic heat exchanger 314 can be in (e.g. fluidic) communication with the heat exchanger 100 (e.g. with the first container 106), e.g.
  • the heat-emitting heat exchanger 314 and the heat exchanger 100 can be connected to one another (for example by means of a line, such as a liquid line).
  • the heat-emitting heat exchanger 314 can be set up in such a way that the refrigerant flows into the heat-emitting heat exchanger 314 and this is in a heat transfer relationship with a secondary fluid (e.g. air, water, salt water, etc.), so that heat is extracted from the refrigerant and is absorbed in the secondary fluid as the refrigerant flows into the exothermic heat exchanger 314.
  • a secondary fluid e.g. air, water, salt water, etc.
  • the refrigerant output by the heat-emitting heat exchanger 314 can be in a high pressure state (eg the pressure of the refrigerant can be in a range from about 10 bar to about 160 bar, for example from about 70 bar to about 140 bar, for example from about 40 bar to about 70 bar).
  • the heat-emitting heat exchanger 314 can be set up in such a way that the refrigerant flows into the heat-emitting heat exchanger 314 and this is in a heat transfer relationship with a second refrigerant.
  • the heat-emitting heat exchanger 314 can be in a heat transfer relationship with another heat exchanger (e.g. with another cooling circuit), so that heat is extracted from the refrigerant flowing into the heat-emitting heat exchanger 314 and into the refrigerant flowing into the other heat exchanger (e.g. in the other cooling circuit) second refrigerant can be added.
  • the critical mass flow for example, increases with increasing inlet pressure (e.g. with increasing pressure of the refrigerant at the inlet of the first section 102-1).
  • An increased cooling capacity can be achieved by means of an increased mass flow.
  • the refrigeration system 300 can furthermore have a control system or a control system with a control loop.
  • the control system or the regulation system can be set up to control the component of the refrigeration system 300 or to regulate the operating conditions of the component of the refrigeration system 300.
  • Regulation of the pressure (eg the high pressure) of the refrigerant output by the heat-emitting heat exchanger 314, and thus regulation of the pressure of the refrigerant supplied to the heat exchanger 100, can result in the Mass flow in the first container 106 and / or in the first section 102-1 can be regulated.
  • An increase in the high pressure can increase the critical mass flow, as a result of which the overheating of the refrigerant is reduced or the cooling capacity is increased.
  • the high pressure can be regulated, for example, by regulating the temperature level of the heat-emitting heat exchanger 314.
  • control system or the regulation system can be set up to control or regulate the heat-emitting heat exchanger 314 in such a way that the pressure of the refrigerant emitted by the heat-emitting heat exchanger 314 is increased (or decreased), so that the mass flow of the refrigerant is increased (or decreased) in the first container 106.
  • control system or the regulation system can be set up to control or regulate the heat-emitting heat exchanger 314 in such a way that the pressure of the refrigerant emitted by the heat-emitting heat exchanger 314 is increased (or decreased) so that the mass flow increases (or decreases). is reduced) and / or the superheating of the refrigerant is reduced (or increased).
  • the refrigeration system 300 can optionally have a valve 316 (e.g. a throttle valve, a capillary tube, an expansion valve such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.), which is downstream relative to the heat-emitting heat exchanger 314 and upstream relative to the Heat exchanger 100 (for example between the heat-emitting heat exchanger 314 and the heat exchanger 100) can be arranged.
  • a valve 316 e.g. a throttle valve, a capillary tube, an expansion valve such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.
  • the overheating and / or the cooling capacity can be controlled or regulated by means of the valve 316.
  • two-phase (for example liquid / gaseous) refrigerant or supercritical refrigerant flows into the first container 106.
  • a liquid / gaseous state of entry into the first container 106 results in a worse distribution than a purely liquid or supercritical entry condition.
  • the refrigeration system 300 can be set up such that the refrigerant output by the heat-emitting heat exchanger 314 is supplied to the valve 316.
  • the valve 316 may be in (e.g. fluidic) communication with the exothermic heat exchanger 314, e.g.
  • the valve 316 and the heat-emitting heat exchanger 314 can be connected to one another (e.g. by means of a line such as a gas line, a liquid line, etc.).
  • the refrigeration system 300 can be set up in such a way that the refrigerant output by the valve 316 is supplied to the heat exchanger 100.
  • the valve 316 can be in (e.g. fluidic) communication with the heat exchanger 100, e.g.
  • the valve 316 and the heat exchanger 100 can be connected to one another (e.g. by means of a line, such as a gas line, a liquid line, etc.).
  • the valve 316 can be set up in such a way that the pressure of the refrigerant is reduced when it flows into the valve 316 so that the valve 316 can be used to regulate the pressure of the refrigerant supplied to the heat exchanger 100.
  • the valve 316 can thus clearly be used to regulate the pressure of the refrigerant in the first container 106 and in the first section 102-1.
  • the mass flow or the cooling capacity in the heat exchanger 100 can be adapted by means of the valve 316.
  • control system or the regulation system can be set up to control or regulate the valve 316 in such a way that the pressure of the refrigerant output by the valve 316 is increased (or decreased) so that the mass flow of the refrigerant in the Heat exchanger 100 (e.g. in the first container 106) increased (or decreased) becomes.
  • two expansion stages can be implemented. The first expansion stage is implemented by means of the valve 316 and the second expansion stage is located in the at least one channel 102 (for example after the throttling provided by the first section 102-1).
  • the refrigeration system 300 can furthermore have a shut-off valve (not shown), which can be arranged (e.g. directly) upstream relative to the heat exchanger 100.
  • the shut-off valve can be set up in such a way that, when it is closed, no refrigerant can flow into the shut-off valve, and that, when it is open, the refrigerant can flow into the shut-off valve.
  • the shut-off valve can be set up in such a way that it remains closed when a cooling process is started until a minimum suction pressure is reached by means of the compressor 312 (e.g. by means of a refrigerant suction of the compressor 312).
  • the shut-off valve can thus be set up in such a way that it only opens or is opened after the minimum permissible suction pressure has been reached.
  • the shut-off valve can be set up so that it is closed during operation when a maximum permissible suction pressure is exceeded.
  • the flow of the refrigerant into the heat exchanger 100 can therefore be enabled (or prevented) in a suitable manner if the pressure level in the refrigeration system 300 is suitable for the desired operation of the heat exchanger 100 (e.g. to achieve sublimation of the refrigerant in the second section 102-2 of the at least one channel 102 of the heat exchanger 100).
  • the shut-off valve can be designed to remain closed during a system standstill in order to maintain the operating pressure level.
  • the second container 108 of the heat exchanger 100 can be set up as a solids separator or become.
  • the refrigeration system 300 can have a solids separator (not shown), which can be arranged downstream relative to the heat exchanger 100.
  • the solids separator can be set up to receive the refrigerant output by the heat exchanger 100; provide the gaseous refrigerant to compressor 312; and to accumulate the solid refrigerant (eg, solid refrigerant components such as solid particles of refrigerant). In this way, the compressor 312 can be protected from damage by solid refrigerant.
  • the refrigeration system 300 can furthermore have a particle filter (not shown) which is set up to bind non-refrigerant particles.
  • the particle filter can be arranged in any suitable location in the refrigeration system 300 so that the non-refrigerant particles circulating in the refrigeration system 300 can be blocked. A blockage of the throttle point (e.g. of the at least one channel 102 and / or of the first section 102-1 of the at least one channel 102) due to the particles foreign to the refrigerant can thus be avoided.
  • the refrigeration system 300 can have an internal heat exchanger (not shown) for transferring heat to the suction gas at the outlet of the heat exchanger 100.
  • the heat can be withdrawn from the cooling process, for example after the heat-emitting heat exchanger 314. In this configuration, the efficiency of the process and the cooling capacity can be increased.
  • Fig. 4 illustrates a refrigeration system 300 having a heat exchanger 100 in a schematic representation according to various embodiments.
  • the first container 106 can be set up as a separator (for example as a medium-pressure separator).
  • the first container 106 can be an elevation above the uppermost channel 102 (eg above the at least one channel 102 or above the topmost channel 102 of the plurality of channels 102).
  • the first container 106 can extend above the uppermost channel 102.
  • the first container 106 can have a gas outlet, which can be arranged, for example, in the elevation, and the refrigeration system 300 can be set up such that the gaseous refrigerant discharged from the gas outlet of the first container 106 is fed to the compressor 312.
  • the refrigeration system 300 can be set up in such a way that the gaseous refrigerant output from the gas outlet of the first container 106 is fed to the compressor 312 together with the gaseous refrigerant output from the heat exchanger 100 (e.g. from the second container 108).
  • the refrigeration system 300 can optionally have an additional valve 418 (for example a throttle valve, a capillary tube, an expansion valve, such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.), which can be set up such that the pressure of the refrigerant is reduced when it flows into the additional valve 418, and which can be arranged downstream relative to the gas outlet of the first container 106 (for example between the gas outlet of the first container 106 and the compressor 312).
  • the additional valve 418 can be in (e.g. fluidic) communication with the gas outlet of the first container 106, for example the additional valve 418 and the gas outlet of the first container 106 can be connected to one another (e.g. by means of a line such as a gas line).
  • the additional valve 418 can thus be used to reduce the pressure of the refrigerant received from the gas outlet of the first container 106 so that it is at the same or a similar pressure level as that of the heat exchanger 100 (e.g. from the second container 108) issued gaseous refrigerants.
  • the additional valve 418 can be set up in such a way that it removes the refrigerant from the gas outlet of the first container 106 at a medium pressure level (for example at a pressure level in a range from approximately 10 bar to approximately 70 bar, for example in a range from approximately 10 bar to about 40 bar, for example in a range from about 40 bar to about 70 bar), and the pressure of the refrigerant is reduced to a low pressure level (e.g. to a pressure level in a range from about 0 bar to about 5 bar).
  • the resulting medium-pressure gas can thus be fed to the suction gas of the compressor 312 via the additional valve 418.
  • the compressor 312 can be set up in such a way that gaseous refrigerant at medium pressure level (for example at a pressure level in a range from approximately 10 bar to approximately 70 bar, for example in a range from approximately 10 bar to approximately 40 bar, for example in a range from approximately 40 bar to approximately 70 bar) can be supplied within the compression process (a so-called intermediate injection).
  • the compressor 312 can be set up in such a way that it receives refrigerant from the gas outlet of the first container 106 (e.g. directly) without the pressure of the refrigerant being reduced.
  • the compressor 312 can have a first inlet and a second inlet, the compressor 312 being configured to receive refrigerant from the second container 108 through the first input (in other words, to draw in) refrigerant from the gas outlet of the first container 106 through the second input to receive.
  • the refrigerant received from the gas outlet of the first container 106 can thus be supplied within the compression process, e.g. after the refrigerant received from the second tank 108 is compressed.
  • the second container 108 can be set up as a solids separator (for example as a cyclone separator).
  • the second Container 108 of the heat exchanger 100 have an expansion below the lowermost channel 102 (for example below the at least one channel 102 or below the lowermost channel 102 of the plurality of channels 102).
  • the second container 108 can extend below the lowermost channel 102.
  • the second container 108 can be set up in such a way that it emits gaseous refrigerant from a gas outlet and that solid refrigerant (eg solid refrigerant components, such as solid particles of refrigerant) accumulates.
  • the second container 108 can be configured to accumulate the solid refrigerant in the extension.
  • the refrigeration system 300 can be set up in such a way that the gaseous refrigerant output by the second container 108 is supplied to the compressor 312. Thus, the suction of solid refrigerant by the compressor 312 can be avoided.
  • the second container 108 can have a second outlet, through which solid refrigerant components (e.g. solid particles of refrigerant) can also be output and provided to the compressor 312.
  • the extension of the second container 108 and the compressor 312 can be in (e.g. fluidic) communication with one another.
  • the second container 108 can be set up in such a way that the solid refrigerant components provided to the compressor 312 are dimensioned in such a way that they can sublime on the way to the compressor 312 and thus do not cause any damage to the compressor 312. It can thus be made possible that refrigerating machine oil which is output by the compressor 312 and which has been circulated in the circuit in the second container 108 (e.g. in the extension of the second container 108) can be fed back to the compressor 312.
  • refrigerating machine oil which is output by the compressor 312 and which has been circulated in the circuit in the second container 108 (e.g. in the extension of the second container 108) can be fed back to the compressor 312.
  • the overheating can be at the bottom of the second container 108 (for example at the bottom of the solids separator). Overheating occurs there only if no solid refrigerant constituents leave the at least one channel 102 (or the channels 102 of the plurality of channels 102).
  • overheating can be determined even though the solid refrigerant leaves the at least one channel 102 because the refrigerant is not in thermal equilibrium.
  • Fig. 5 illustrates a refrigeration system 300 having a heat exchanger 100 in a schematic representation according to various embodiments.
  • the refrigeration system 300 can have a second compressor 520 (e.g. a reciprocating compressor, a screw compressor, a rotary compressor, a centrifugal compressor, a scroll compressor, etc.), so that a two-stage compression of the refrigerant can be implemented.
  • the second compressor 520 may, for example, be arranged downstream relative to the first compressor 312.
  • the heat-emitting heat exchanger 314 can be at the ambient temperature level, which leads to high pressure ratios and compression end temperatures.
  • the second compressor 520 can thus be used to achieve such high pressure ratios.
  • the additional valve 418 can be dispensed with, and the gaseous refrigerant output from the first container 106 (eg from the gas outlet of the first container 106) can be supplied to the second compressor 520 (eg directly).
  • the two-stage compression makes it possible that the pressure of the gaseous refrigerant discharged from the first container 106 (for example from the gas outlet of the first container 106) should not be reduced to a low pressure level. This has the consequence that a higher Efficiency of the process (e.g. the compression process) can be achieved.
  • the refrigeration system 300 can be set up in such a way that the gaseous refrigerant output by the first container 106 (e.g. from the gas outlet of the first container 106) is fed to the second compressor 520 together with the compressed refrigerant output by the compressor 312.
  • the gas outlet of the first container 106 and the second compressor 520 can be in communication with one another, e.g.
  • the gas outlet of the first container 106 and the second compressor 520 can be connected to one another (e.g. by means of a line such as a gas line).
  • the second compressor 520 can be set up to suck in the refrigerant from the first container 106 (e.g. from the gas outlet of the first container 106).
  • control system or the regulating system can be set up to control or regulate the second compressor 520 (e.g. a speed of the second compressor 520).
  • the control system or the regulation system can be set up to control or regulate the second compressor 520 (for example the speed of the second compressor 520) in such a way that the pressure of the refrigerant in the first container 106 increases (or decreases) can be.
  • the overheating of the refrigerant can also be regulated.
  • Fig. 6 illustrates a refrigeration system 300 having a heat exchanger 100 in a schematic representation according to various embodiments.
  • the refrigeration system 300 can have a separator 622 (for example a medium-pressure separator) which is upstream relative to the heat exchanger 100 can be arranged.
  • the separator 622 can be configured to separate gaseous refrigerant from the liquid refrigerant.
  • the refrigeration system 300 can be set up in such a way that the liquid refrigerant output by the separator 622 is fed to the heat exchanger 100.
  • the separator 622 can have a gas outlet and a liquid outlet, and the liquid outlet can be connected to the heat exchanger 100 (e.g. to the first container 106).
  • the heat exchanger 100 e.g. to the first container 106.
  • only liquid or supercritical refrigerant can be supplied to the first container 106.
  • the refrigerant can be supplied or distributed in a more efficient manner.
  • the refrigeration system 300 can be set up in such a way that the gaseous refrigerant output by the separator 622 is fed to the compressor 312.
  • the refrigeration system 300 can have another valve 624 (for example a throttle valve, a capillary tube, an expansion valve, such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.), which can be set up such that the pressure of the Refrigerant is reduced when this flows into the other valve 624, and which can be arranged downstream relative to the gas outlet of the separator 622 and upstream relative to the compressor 312.
  • the other valve 624 can be in (e.g. fluidic) communication with the gas outlet of the separator 622, e.g.
  • the other valve 624 and the gas outlet of the separator 622 can be connected to one another (e.g. by means of a line such as a gas line).
  • the other valve 624 can thus be used to control the pressure of the gas output of the separator 622 To reduce refrigerant so that it is at the same or a similar pressure level as the gaseous refrigerant output by the heat exchanger 100 (for example from the second container 108).
  • the other valve 624 can be set up in such a way that it removes the refrigerant from the gas outlet of the separator 622 at a medium pressure level (for example at a pressure level in a range from approximately 10 bar to approximately 70 bar, for example in a range from approximately 10 bar to approximately 40 bar, for example in a range from approximately 40 bar to approximately 70 bar), and the pressure of the refrigerant is reduced to a low pressure level (eg to a pressure level in a range from approximately 0 bar to approximately 5 bar).
  • the resulting medium-pressure gas can thus be fed to the suction gas of the compressor 312 via the other valve 624.
  • thermo sensors and / or pressure sensors can be provided in order to detect the temperature and / or the pressure of the refrigerant in different areas of the cooling circuit.
  • the detected temperature and / or the detected pressure can be used as feedback parameters in order to control or regulate the operating parameters of the elements of the refrigeration system 300 (e.g. the operating parameters of the valve 316, the other valve 624, the compressor 312, etc.).
  • control system or the regulating system can be set up to control or regulate the valve 316 and / or the other valve 624 based on the detected temperature and / or on the detected pressure.
  • control system or the regulation system may be set up to apply the compressor 312 (eg a speed of the compressor 312) or the second compressor 520 (eg a speed of the second compressor 520) based on the detected temperature and / or on the detected pressure control or regulate.
  • the valve 316 for the subcritical operation can be controlled or regulated according to a predetermined subcooling. When the input pressure resulting therefrom reaches a maximum predetermined subcritical high pressure, the valve 316 should be controlled or regulated according to the predetermined maximum predetermined subcritical high pressure.
  • the other valve 624 can regulate the pressure (e.g. the medium pressure) in the separator 622.
  • An increase in pressure e.g. the mean pressure
  • the control system or the regulating system can be configured to control or regulate the other valve 624 in such a way that the pressure of the refrigerant output by the other valve 624 is increased (or decreased) so that the pressure of the refrigerant in the Separator 622 is increased (or decreased).
  • control system or the regulating system can be set up to control or regulate the other valve 624 such that the pressure of the refrigerant output by the other valve 624 is increased (or decreased) so that the mass flow of the refrigerant in the Separator 622 is increased (or decreased).
  • the maximum pressure (e.g. the maximum mean pressure) is limited by a setpoint high pressure upstream of the valve 316.
  • the minimum pressure (e.g. the minimum mean pressure) is limited by the dependent minimum critical pressure, which should be above the triple pressure of the refrigerant.
  • the other valve 624 can also be controlled or regulated according to the cooling capacity or according to overheating. In transcritical operation, for example, the pressure (e.g. the mean pressure) can be kept at the subcritical pressure level by means of the other valve 624.
  • the overheating can be regulated by changing the volume flow of the compressor 312. For example, an increase in the volume flow of the compressor 312 lowers the sublimation pressure and increases the overheating.
  • the cooling capacity is only slightly increased by the proportion of the additional Overheating increased. Limitations result from the maximum sublimation pressure and the minimum permissible suction pressure.
  • the control system or the regulation system can be set up to control or regulate the compressor 312 (eg the speed of the compressor 312) in such a way that the pressure of the refrigerant (eg in the heat exchanger 100) increases (or decreases) ) can be.
  • the overheating of the refrigerant can thus also be regulated by means of the control or regulation of the compressor 312 (for example the speed of the compressor 312).
  • control system or the regulating system can be set up to control or regulate the other valve 624 in such a way that the pressure (e.g. the mean pressure) in the separator 622 is set to supercritical pressure below or equal to the high pressure (e.g. at a pressure level in a range from approximately 10 bar to approximately 160 bar, for example in a range from approximately 70 bar to approximately 140 bar, for example in a range from approximately 40 bar to approximately 70 bar), so that supercritical refrigerant the heat exchanger 100 (e.g. the throttle point provided by the first section 102-1) and is expanded in the second section 102-2 of the at least one channel 102 of the heat exchanger 100.
  • Such an expansion of the medium pressure range by the supercritical pressure range can enlarge the range of the power control by increasing the critical mass flow in the throttle point (e.g. in the first section 102-1).
  • the refrigeration system 300 can have an internal heat exchanger.
  • the inner heat exchanger can be arranged downstream relative to the liquid outlet of the separator 622, so that subcooling of the liquid refrigerant is made possible. This has the consequence that there is less or no bubble formation due to external heat input in the first container 106, and thus leads to a more stable supply or to a more stable distribution of the refrigerant.
  • Fig. 7 illustrates a refrigeration system 300 having a heat exchanger 100 in a schematic representation, according to various embodiments.
  • the refrigeration system 300 can have the second compressor 520 and the separator 622, which can be set up as shown above.
  • the other valve 624 can be dispensed with and the gaseous refrigerant discharged from the separator 622 (e.g. from the gas outlet of the separator 622) can be supplied to the second compressor 520.
  • the two-stage compression enables the pressure of the gaseous refrigerant discharged from the separator 622 (e.g., from the gas outlet of the separator 622) not to be reduced to a low pressure level.
  • the refrigeration system 300 can be set up in such a way that the gaseous refrigerant output by the separator 622 (e.g. from the gas outlet of the separator 622) is fed to the second compressor 520, for example together with the compressed refrigerant output by the compressor 312.
  • control system or the regulating system can be set up to control or regulate the second compressor 520 (for example a speed of the second compressor 520).
  • the control system or the regulating system can be set up to control or regulate the second compressor 520 (eg the speed of the second compressor 520) in such a way that the pressure of the refrigerant in the separator 622 is increased (or decreased) can.
  • the overheating of the refrigerant can also be regulated.
  • the refrigeration system 300 can, however, also have the other valve 624 in order to provide a further possibility for regulating the pressure in the separator 622.
  • the refrigeration system 300 may have another heat exchanger (not shown) which may be arranged downstream relative to the compressor 312, e.g. between the gas outlet of the separator 622 and the outlet of the compressor 312.
  • the other heat exchanger can be arranged upstream relative to the second compressor 520.
  • the refrigeration system 300 can be set up in such a way that the compressed refrigerant output by the compressor 312 can be cooled by means of the other heat exchanger. Such cooling enables a larger mass flow of refrigerant to flow into the second compressor 520 and that the efficiency of the compression process can be increased.
  • a cooling method for cooling a fluid by means of sublimation of a refrigerant can include providing a refrigerant to a heat exchanger 100.
  • the heat exchanger 100 can be set up as illustrated above and can have at least one channel 102 for conducting refrigerant.
  • the refrigerant provided to the heat exchanger 100 can be in a non-solid (e.g. in a liquid, gaseous, liquid / gaseous, supercritical) physical state.
  • the cooling method can include guiding the refrigerant into the at least one channel 102 of the heat exchanger 100.
  • the at least one channel 102 can have a first section 102-1 and a second section 102-2, wherein the first section 102-1 is upstream relative to the second section 102-2 with respect to a flow direction of the refrigerant in the at least one channel 102 is arranged, wherein the second portion 102-2 has a cross-sectional area which is greater than a cross-sectional area of the first Section 102-1 so that a sublimation of the refrigerant is made possible in the second section 102-2.
  • the cooling method can include guiding the refrigerant into the first section 102-1 of the at least one channel 102 of the heat exchanger 100, wherein the cross-sectional area of the first section 102-1 can be dimensioned such that sublimation of the refrigerant in the first section 102-1 is prevented.
  • the cross-sectional area of the first section 102-1 can be dimensioned such that the refrigerant in the first section 102-1 is in a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state.
  • a non-solid e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.
  • the cooling method can include guiding the refrigerant into the second section 102 - 2 of the at least one channel 102 of the heat exchanger 100.
  • the cross-sectional area of the second section 102-2 can be dimensioned such that the refrigerant is expanded in an at least partially solid (e.g. solid / gaseous) physical state in the second section 102-2.
  • the cooling method may include providing a heat transfer between the refrigerant flowing into the second section 102-2 and the fluid to be cooled, so that the refrigerant flowing into the second section 102-2 can sublime and the fluid to be cooled can be cooled.
  • the heat exchanger 100 described herein, the cooling system 300 described herein and the cooling method described herein can be used in applications which require deep cooling (for example at a temperature level below -50 ° C.).
  • One possible application is the simulation of climatic conditions, for example for testing equipment and / or components at extremely low temperatures.
  • Another possible application is in medical methods that require such a low temperature.
  • Example 1 is a heat exchanger which can have at least one channel for guiding refrigerant, the at least one channel having a first section and a second section; wherein the first section is arranged with respect to a flow direction of the refrigerant in the at least one channel upstream relative to the second section; wherein the second section has a cross-sectional area which is larger than a cross-sectional area of the first section, so that sublimation of the refrigerant is made possible in the second section.
  • the heat exchanger according to example 1 can optionally also have the at least one channel having multiple tubes (e.g. multiple mini-channels, multiple mini-channel tubes, etc.).
  • the heat exchanger according to example 1 or 2 can optionally also have the heat exchanger set up such that a refrigerant flowing into the at least one channel can be in a heat transfer relationship with a fluid to be cooled.
  • the heat exchanger according to one of examples 1 to 3 can optionally also have the heat exchanger set up such that a refrigerant flowing into the second section can be in a heat transfer relationship with a fluid to be cooled.
  • the heat exchanger according to one of examples 1 to 4 can optionally furthermore have the second section being arranged directly next to the first section.
  • the heat exchanger according to one of examples 1 to 5 can optionally also have the first section being set up in such a way that it provides a throttle point at the inlet of the at least one channel.
  • the heat exchanger according to one of examples 1 to 6 can optionally also have the cross-sectional area of the first section being dimensioned in such a way that there is a drop in the pressure of a refrigerant flowing into the first section.
  • the cross-sectional area of the first section can be dimensioned such that a refrigerant is at a high pressure level in front of the first section (e.g. at a pressure level in a range from approximately 10 bar to approximately 160 bar, for example in a range from approximately 70 bar to approximately 140 bar, for example in a range from about 40 bar to about 70 bar);
  • the refrigerant reaches a critical (sonic) speed, so that the pressure of the refrigerant in the first section is at a lower pressure level (for example at a pressure level in a range from approximately 10 bar to approximately 70 bar, for example in a range from about 10 bar to about 40 bar, for example in a range from about 40 bar to about 70 bar); and after the first section (eg when entering the second section) there is a further expansion of the refrigerant and the pressure of the The refrigerant continues to drop (for example at a pressure level in a range from approximately 0 bar to approximately 5 bar, for example at a sublimation pressure
  • Examples 1 to 7 optionally further have that the
  • Cross-sectional area of the first section is dimensioned such that sublimation of the refrigerant is prevented in the first section.
  • Examples 1 to 8 optionally further have that the
  • the cross-sectional area of the first section is dimensioned such that the refrigerant is or can be in a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) aggregate state in the first section.
  • a non-solid e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.
  • Examples 1 to 9 optionally further have that the
  • Cross-sectional area of the first section is dimensioned such that the refrigerant is at a pressure level in the first section (e.g. up to the outlet of the first section) which is greater than the pressure level of the
  • Examples 1 to 10 optionally further have that the
  • the cross-sectional area of the first section is dimensioned such that the critical mass flow, which is dependent on the pressure when the first section enters, is achieved through the first section.
  • Examples 1 to 11 optionally further have that the
  • the cross-sectional area of the first section and the cross-sectional area of the second section are dimensioned such that a refrigerant flowing into the at least one channel is at such a pressure level (eg Atmospheric pressure level) is located downstream relative to the first section (for example in the second section) that the sublimation of the refrigerant is made possible.
  • a pressure level eg Atmospheric pressure level
  • Examples 1 to 12 optionally further have that the
  • the cross-sectional area of the first section and the cross-sectional area of the second section are dimensioned such that the refrigerant is expanded into an at least partially solid (e.g. solid / gaseous) physical state in the second section.
  • Examples 1 to 13 optionally further include that the first section has a cross-sectional area in a range from approximately 0.0001 mm 2 to approximately 0.8 mm 2 , for example in a range from approximately 0.001 mm 2 to approximately 0.5 mm 2 , for example in a range of approximately 0.005 mm 2 to about 0.25 mm 2 .
  • Examples 1 to 14 optionally further include that the second section has a cross-sectional area in a range from approximately 0.01 mm 2 to approximately 400 mm 2 , for example in a range from approximately 0.1 mm 2 to approximately 100 mm 2 , for example in a range of approximately 0.5 mm 2 to approximately 50 mm 2 , for example in a range from approximately 1 mm 2 to approximately 20 mm 2 .
  • Examples 1 to 15 optionally further have that the
  • the cross-sectional area of the first section and the cross-sectional area of the second section are dimensioned such that the refrigerant is at a pressure level in a range from approximately 0 bar to approximately 5 bar in the second section.
  • the heat exchanger according to one of examples 1 to 16 can optionally furthermore have that the refrigerant contains carbon dioxide.
  • the heat exchanger according to one of examples 1 to 17 can optionally furthermore have that the refrigerant comprises a hydrocarbon-based refrigerant.
  • the refrigerant can have HFC and / or HCFC and / or HFO and / or R170 and / or R290 and / or R600 etc.
  • the heat exchanger according to one of examples 1 to 18 can optionally furthermore have that the refrigerant has a mixture of a plurality of mutually different refrigerants.
  • the heat exchanger according to one of examples 1 to 19 can optionally also have a first container (e.g. a distributor container) which is set up to supply the refrigerant to the at least one channel.
  • a first container e.g. a distributor container
  • the first container can be set up to distribute the refrigerant to the multiple tubes (e.g. to the multiple mini-channels) of the at least one channel (e.g. evenly).
  • the heat exchanger according to example 20 can optionally also have the first container set up in such a way that a refrigerant flowing into the first container is at a pressure level which is above the pressure level of the triple point of the refrigerant.
  • the heat exchanger according to example 20 or 21 can optionally further have that the first container is set up in such a way that the refrigerant is at a medium pressure level or high pressure level (eg at a Pressure level in a range from approximately 10 bar to approximately 160 bar, for example in a range from approximately 70 bar to approximately 140 bar, for example in a range from approximately 40 bar to approximately 70 bar, for example in a range from approximately 10 bar to approximately 40 bar, etc.) is located in the first container.
  • a medium pressure level or high pressure level eg at a Pressure level in a range from approximately 10 bar to approximately 160 bar, for example in a range from approximately 70 bar to approximately 140 bar, for example in a range from approximately 40 bar to approximately 70 bar, for example in a range from approximately 10 bar to approximately 40 bar, etc.
  • the heat exchanger according to one of examples 20 to 22 can optionally also have the first container set up such that a refrigerant flowing into the first container is converted into a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state.
  • a refrigerant flowing into the first container is converted into a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state.
  • the heat exchanger according to one of examples 20 to 23 can optionally also have the first container set up as a separator (e.g. as a medium-pressure separator).
  • a separator e.g. as a medium-pressure separator
  • the first container can be set up to supply the liquid refrigerant to the at least one channel and to output the gaseous refrigerant from a gas outlet.
  • the heat exchanger according to one of examples 1 to 24 can optionally also have a second container (e.g. a collecting container) which is set up to receive the refrigerant discharged from the at least one channel.
  • a second container e.g. a collecting container
  • the heat exchanger according to example 25 can optionally also have the second container set up as a solids separator (e.g. as a cyclone separator).
  • a solids separator e.g. as a cyclone separator
  • the second container can be set up in such a way that it emits gaseous refrigerant from a first outlet and collects solid refrigerant (for example solid refrigerant components, such as solid particles of refrigerant).
  • solid refrigerant for example solid refrigerant components, such as solid particles of refrigerant.
  • Examples 1 to 26 optionally further comprise that the first
  • Section has a circular or an elliptical cross section.
  • Examples 1 to 26 optionally further comprise that the first
  • Section has a square or a rectangular or a polygonal cross section.
  • Examples 1 to 28 optionally further have that the
  • At least one channel in which at least one channel (eg a height, a width, a diameter, an edge length, etc.) in a range from approximately 0.01 mm to approximately 0.5 mm, for example in a range of approximately 0.01 mm to approximately 0.2 mm, for example in a range from approximately 0.02 mm to approximately 0.1 mm, for example in a range from approximately 0.02 mm to approximately 0.05 mm.
  • the size of the cross section of the first section can be smaller than 0.1 mm.
  • Examples 1 to 29 optionally further include that the second section has a circular or elliptical cross section.
  • Examples 1 to 29 optionally further include that the second section has a square or a rectangular or a polygonal cross section.
  • the heat exchanger according to one of examples 1 to 31 can optionally furthermore have that the cross section of the second section has a size along a Direction perpendicular to the flow direction of the refrigerant in the at least one channel (eg a height, a width, a diameter, an edge length, etc.) in a range from approximately 0.1 mm to approximately 20 mm, for example from approximately 0.5 mm to approximately 10 mm, from about 1 mm to about 5 mm.
  • the heat exchanger according to one of examples 1 to 32 can optionally further include that the cross-sectional area of the first section is provided (in other words, reduced) by upsetting the at least one channel.
  • the heat exchanger according to one of examples 1 to 33 can optionally further include that the at least one channel has a narrowing element (eg a sleeve, a perforated disk, a perforated plate, a cap, etc.) which is arranged in the first section so that the cross-sectional area of the first section is reduced.
  • a narrowing element eg a sleeve, a perforated disk, a perforated plate, a cap, etc.
  • the heat exchanger according to one of examples 1 to 33 can optionally further include that a narrowing element is arranged (e.g. fastened, such as soldered, etc.) at the inlet of the at least one channel.
  • a narrowing element is arranged (e.g. fastened, such as soldered, etc.) at the inlet of the at least one channel.
  • the narrowing element can serve as the first section of the at least one channel and the at least one channel can serve as the second section of the at least one channel.
  • Example 36 is a heat exchanger having at least one channel for guiding refrigerant, and at least one constricting element which is arranged upstream relative to the at least one channel, wherein the at least one channel has a cross-sectional area which is greater than a cross-sectional area (e.g. an inner cross-sectional area ) of the at least one narrowing element, so that a Sublimation of the refrigerant in which at least one channel is made possible.
  • a cross-sectional area e.g. an inner cross-sectional area
  • the heat exchanger according to example 36 can optionally further include that the at least one constricting element is arranged (e.g. fastened, such as soldered, etc.) at the inlet of the at least one channel.
  • the at least one constricting element is arranged (e.g. fastened, such as soldered, etc.) at the inlet of the at least one channel.
  • Example 38 is a refrigeration system having a heat exchanger according to one of Examples 1 to 37.
  • the refrigeration system can optionally have a control system or a control system with a control loop.
  • the control system or the regulation system can be set up to control the component of the refrigeration system or to regulate the operating conditions of the component of the refrigeration system.
  • the refrigeration system can optionally have a compressor which is arranged downstream relative to the heat exchanger.
  • the refrigeration system can optionally have a heat-emitting heat exchanger.
  • the heat-emitting heat exchanger can be arranged downstream relative to the compressor.
  • the heat-emitting heat exchanger can be arranged upstream relative to the heat exchanger (e.g. relative to the first container of the heat exchanger).
  • the refrigeration system according to example 38 can optionally also have the control system or the regulation system being set up to control or regulate the compressor (e.g. the speed of the compressor) in such a way that the pressure of the refrigerant (e.g. in the heat exchanger ) can be increased (or decreased).
  • control system or the regulation system being set up to control or regulate the compressor (e.g. the speed of the compressor) in such a way that the pressure of the refrigerant (e.g. in the heat exchanger ) can be increased (or decreased).
  • the refrigeration system according to example 38 or 39 can optionally further comprise that the control system or the Control system is set up to control or regulate the heat-emitting heat exchanger in such a way that the pressure of the refrigerant output by the heat-emitting heat exchanger is increased (or decreased) so that the mass flow of the refrigerant in the first container is increased (or decreased) .
  • the refrigeration system according to one of examples 38 to 40 can optionally also have the control system or the regulating system being set up to control or regulate the heat-emitting heat exchanger in such a way that the pressure of the refrigerant output by the heat-emitting heat exchanger increases ( or decreased), so that the overheating of the refrigerant is decreased (or increased).
  • the refrigeration system according to one of examples 38 to 41 can optionally have a valve (e.g. a throttle valve, a capillary tube, an expansion valve, such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.).
  • a valve e.g. a throttle valve, a capillary tube, an expansion valve, such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.
  • the valve can be set up in such a way that the pressure of the refrigerant is reduced when it flows into the valve.
  • valve can be arranged downstream relative to the heat-emitting heat exchanger and upstream relative to the heat exchanger (e.g. between the heat-emitting heat exchanger and the heat exchanger).
  • the refrigeration system according to example 42 can optionally further have that the control system or the regulating system is set up to control or regulate the valve in such a way that the pressure of the refrigerant output by the valve is increased (or decreased), that the mass flow of the refrigerant in the heat exchanger (for example in the first container) is increased (or decreased).
  • the refrigeration system according to one of examples 38 to 43 can optionally also have the first container of the heat exchanger as a separator (eg as a Medium-pressure separator) is set up, and that the refrigeration system is set up so that the gaseous refrigerant discharged from the first container is fed to the compressor.
  • a separator eg as a Medium-pressure separator
  • the refrigeration system according to example 44 can optionally also have an additional valve (e.g. a throttle valve, a capillary tube, an expansion valve, such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.).
  • the additional valve can be set up in such a way that the pressure of the refrigerant is reduced when it flows into the additional valve.
  • the additional valve can be arranged downstream relative to a gas outlet of the first container (e.g. between the gas outlet of the first container and the compressor).
  • the refrigeration system according to one of examples 38 to 45 can optionally further include that the second container of the heat exchanger is set up as a solids separator. For example, overheating of the refrigerant at the bottom of the second container can be detected.
  • the refrigeration system according to one of examples 38 to 46 can optionally also have a second compressor (e.g. a reciprocating compressor, a screw compressor, a rotary compressor, a centrifugal compressor, a scroll compressor, etc.).
  • the second compressor can for example be arranged downstream relative to the compressor.
  • the refrigeration system can be set up in such a way that the gaseous refrigerant output by the first container (for example from the gas outlet of the first container) is fed to the second compressor together with the compressed refrigerant output by the compressor.
  • the refrigeration system according to example 47 can optionally further include that the control system or the regulation system is set up to control or regulate the second compressor (eg a speed of the additional compressor) in such a way that the pressure of the refrigerant in the first container is increased (or decreased).
  • the refrigeration system according to one of examples 38 to 48 can optionally also have a separator (e.g. a medium-pressure separator).
  • the separator can be set up to separate gaseous refrigerant from the liquid refrigerant.
  • the separator can be arranged upstream relative to the heat exchanger.
  • the refrigeration system can be set up in such a way that the gaseous refrigerant output by the separator is fed to the compressor and / or the second compressor.
  • the refrigeration system according to example 49 can optionally also have another valve (e.g. a throttle valve, a capillary tube, an expansion valve, such as a thermostatic expansion valve, an electronic expansion valve, a manual expansion valve, etc.).
  • the other valve can be set up in such a way that the pressure of the refrigerant is reduced when it flows into the other valve.
  • the other valve can be arranged downstream relative to a gas outlet of the separator.
  • the refrigeration system according to example 50 can optionally further include that the control system or the regulating system is set up to control or regulate the other valve in such a way that the pressure of the refrigerant output by the other valve increases (or decreases) so that the pressure of the refrigerant in the separator is increased (or decreased).
  • the refrigeration system according to example 50 or 51 can optionally further include that the control system or the regulating system is set up to control or regulate the other valve in such a way that the pressure of the other Valve dispensed refrigerant is increased (or decreased), so that the mass flow of the refrigerant in the separator is increased (or decreased).
  • the refrigeration system according to one of examples 50 to 52 can optionally further have that the control system or the regulating system is set up to control or regulate the other valve in such a way that the pressure (eg the mean pressure) in the separator is set to supercritical Pressure below or equal to the high pressure (for example to a pressure level in a range from about 10 bar to about 160 bar, for example from about 70 bar to about 140 bar, for example from about 40 bar to about 70 bar) is increased.
  • the control system or the regulating system is set up to control or regulate the other valve in such a way that the pressure (eg the mean pressure) in the separator is set to supercritical Pressure below or equal to the high pressure (for example to a pressure level in a range from about 10 bar to about 160 bar, for example from about 70 bar to about 140 bar, for example from about 40 bar to about 70 bar) is increased.
  • the refrigeration system according to example 47 or 48 and according to one of examples 49 to 53 can optionally further include that the control system or the regulation system is set up to control or close the second compressor (eg the speed of the second compressor) in this way regulate that the pressure of the refrigerant in the separator is increased (or decreased).
  • the control system or the regulation system is set up to control or close the second compressor (eg the speed of the second compressor) in this way regulate that the pressure of the refrigerant in the separator is increased (or decreased).
  • Example 55 is a cooling method for cooling a fluid by means of sublimation of a refrigerant, which comprises the following: providing a refrigerant to a heat exchanger, the heat exchanger having at least one channel for guiding refrigerant; Guiding the refrigerant into the at least one channel, the at least one channel having a first section and a second section, the first section being arranged upstream relative to the second section with respect to a flow direction of the refrigerant in the at least one channel, the the second section has a cross-sectional area which is larger than a cross-sectional area of the first section so that sublimation of the refrigerant is made possible in the second section; Providing a heat transfer between the refrigerant flowing into the second section and the fluid to be cooled, so that the sublimate refrigerant flowing into the second section and the fluid to be cooled can be cooled.
  • the cooling method according to example 55 can optionally further include that the refrigerant provided to the heat exchanger is in a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state.
  • a non-solid e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.
  • the cooling method according to example 55 or 56 can optionally further include guiding the refrigerant into a first section of the at least one channel of the heat exchanger, the cross-sectional area of the first section being dimensioned such that sublimation of the refrigerant in the first section is prevented .
  • the cooling method according to one of examples 55 to 57 can optionally further include guiding the refrigerant into a second section of the at least one channel of the heat exchanger.
  • the cooling method according to one of examples 55 to 58 can optionally further include that the at least one channel has multiple tubes (e.g. multiple mini-channels, multiple mini-channel tubes).
  • the cooling method according to one of examples 55 to 59 can optionally further include that the heat exchanger is set up such that a refrigerant flowing into the at least one channel can be in a heat transfer relationship with a fluid to be cooled.
  • the cooling method according to one of examples 55 to 60 can optionally further include that the heat exchanger is set up such that a refrigerant flowing into the second section can be in a heat transfer relationship with a fluid to be cooled.
  • the cooling method according to one of examples 55 to 61 can optionally further comprise that the second section is arranged directly next to the first section.
  • the cooling method according to one of examples 55 to 62 can optionally further include that the first section is set up in such a way that it provides a throttle point at the inlet of the at least one channel.
  • the cooling method according to one of examples 55 to 63 can optionally further include that the cross-sectional area of the first section is dimensioned such that the pressure of a refrigerant flowing into the first section drops.
  • the cross-sectional area of the first section can be dimensioned such that a refrigerant is at a high pressure level in front of the first section (e.g. at a pressure level in a range from approximately 10 bar to approximately 160 bar, for example in a range from approximately 70 bar to approximately 140 bar, for example in a range from about 40 bar to about 70 bar);
  • the refrigerant reaches a critical (sonic) speed, so that the pressure of the refrigerant in the first section is at a lower pressure level (for example at a pressure level in a range from approximately 10 bar to approximately 70 bar, for example in a range from about 10 bar to about 40 bar, for example in a range from about 40 bar to about 70 bar); and after the first section (e.g.
  • the pressure of the refrigerant falls further (e.g. at a pressure level in a range from approximately 0 bar to approximately 5 bar, e.g. at a sublimation pressure level) .
  • the cooling method according to one of examples 55 to 64 can optionally further comprise that the Cross-sectional area of the first section is dimensioned such that sublimation of the refrigerant is prevented in the first section.
  • the cooling method according to one of examples 55 to 65 can optionally further include that the cross-sectional area of the first section is dimensioned such that the refrigerant in the first section is in a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical) , etc.) physical state is or can be.
  • a non-solid e.g. liquid, gaseous, liquid / gaseous, supercritical
  • the cooling method according to one of examples 55 to 66 can optionally further include that the cross-sectional area of the first section is dimensioned such that the refrigerant is at a pressure level in the first section (eg up to the exit of the first section) which is greater than the pressure level of the triple point of the refrigerant.
  • the cooling method according to one of examples 55 to 67 can optionally further include that the cross-sectional area of the first section is dimensioned such that the critical mass flow, which is dependent on the pressure at the entry of the first section, is achieved through the first section.
  • the cooling method according to one of examples 55 to 68 can optionally further include that the cross-sectional area of the first section and the cross-sectional area of the second section are dimensioned such that a refrigerant flowing into the at least one channel is at such a pressure level (e.g. Atmospheric pressure level) is located downstream relative to the first section (for example in the second section) that the sublimation of the refrigerant is made possible.
  • a pressure level e.g. Atmospheric pressure level
  • the cooling method according to one of examples 55 to 69 can optionally further comprise that the The cross-sectional area of the first section and the cross-sectional area of the second section are dimensioned such that the refrigerant is expanded into an at least partially solid (eg solid / gaseous) physical state in the second section.
  • the cooling method according to one of examples 55 to 70 can optionally further comprise that the first section has a cross-sectional area in a range from approximately 0.0001 mm 2 to approximately 0.8 mm 2 , for example in a range from approximately 0.001 mm 2 to approximately 0.5 mm 2 , for example in a range from approximately 0.005 mm 2 to approximately 0.25 mm 2 .
  • the cooling method according to one of examples 55 to 71 can optionally further include that the second section has a cross-sectional area in a range from approximately 0.01 mm 2 to approximately 400 mm 2 , for example in a range from approximately 0.1 mm 2 to approximately 100 mm 2 , for example in a range from approximately 0.5 mm 2 to approximately 50 mm 2 , for example in a range from approximately 1 mm 2 to approximately 20 mm 2 .
  • the cooling method according to one of examples 55 to 72 can optionally further include that the cross-sectional area of the first section and the cross-sectional area of the second section are dimensioned such that the refrigerant is at a pressure level in a range from approximately 0 bar to approximately 5 bar is located in the second section.
  • the cooling method according to any one of examples 55 to 73 can optionally further include that the refrigerant comprises carbon dioxide.
  • cooling method according to any one of examples 55 to 74 can optionally further comprise that the
  • Refrigerant comprises a hydrocarbon-based refrigerant.
  • the refrigerant can have HFC and / or HCFC and / or HFO and / or R170 and / or R290 and / or R600 etc.
  • the cooling method according to one of examples 55 to 75 can optionally further include that the refrigerant comprises a mixture of a plurality of mutually different refrigerants.
  • the cooling method according to one of examples 55 to 76 can optionally further comprise a first container (e.g. a distributor container) which is set up to supply the refrigerant to the at least one channel.
  • a first container e.g. a distributor container
  • the first container can be set up to deliver the refrigerant to the multiple tubes (e.g. to the multiple tubes).
  • Mini-channels of the at least one channel (e.g. evenly) if the at least one channel has several pipes.
  • the cooling method according to example 77 can optionally further include that the first container is set up in such a way that a refrigerant flowing into the first container is at a pressure level which is above the pressure level of the triple point of the refrigerant.
  • the cooling method according to example 77 or 78 can optionally further include that the first container is set up in such a way that the refrigerant is at a medium pressure level or high pressure level (e.g. at a pressure level in a range from approximately 10 bar to approximately
  • the cooling method according to one of examples 77 to 79 can optionally further include that the first container is set up such that a refrigerant flowing into the first container is converted into a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state.
  • a refrigerant flowing into the first container is converted into a non-solid (e.g. liquid, gaseous, liquid / gaseous, supercritical, etc.) physical state.
  • the cooling method according to one of examples 77 to 80 can optionally further include that the first container is set up as a separator (e.g. as a medium-pressure separator).
  • a separator e.g. as a medium-pressure separator
  • the first container can be set up to supply the liquid refrigerant to the at least one channel and to output the gaseous refrigerant from a gas outlet.
  • the cooling method according to one of examples 55 to 81 can optionally further comprise a second container (e.g. a collecting container) which is configured to receive the refrigerant discharged from the at least one channel.
  • a second container e.g. a collecting container
  • the cooling method according to example 82 can optionally further include that the second container is set up as a solids separator (e.g. as a cyclone separator).
  • the second container is set up as a solids separator (e.g. as a cyclone separator).
  • the second container can be set up in such a way that it emits gaseous refrigerant from a first outlet and collects solid refrigerant (e.g. solid refrigerant components, such as solid particles of refrigerant).
  • solid refrigerant e.g. solid refrigerant components, such as solid particles of refrigerant.
  • the cooling method according to one of examples 55 to 83 can optionally further comprise that the first section has a circular or an elliptical cross section.
  • the cooling method according to one of examples 55 to 83 can optionally further include that the first section has a square or a rectangular or a polygonal cross section.
  • the cooling method according to one of examples 55 to 85 can optionally further include that the cross section of the first section has a size along a direction perpendicular to the flow direction of the refrigerant in the at least one channel (e.g. a height, a width, a diameter, an edge length, etc.) in a range from approximately 0.01 mm to approximately 0.5 mm, for example in a range from approximately 0.01 mm to approximately 0.2 mm, for example in a range from approximately 0.02 mm to approximately 0.1 mm, for example in a range of about 0.02 mm to about 0.05 mm.
  • the cross section of the first section has a size along a direction perpendicular to the flow direction of the refrigerant in the at least one channel (e.g. a height, a width, a diameter, an edge length, etc.) in a range from approximately 0.01 mm to approximately 0.5 mm, for example in a range from approximately 0.01 mm to approximately 0.2 mm, for example in a range from
  • the size of the cross section of the first section can be smaller than 0.1 mm.
  • the cooling method according to any one of examples 55 to 86 can optionally further include that the second portion has a circular or elliptical cross section.
  • the cooling method according to one of examples 55 to 86 can optionally further comprise that the second section has a square or a rectangular or a polygonal cross section.
  • the cooling method according to one of examples 55 to 88 can optionally further comprise that the cross section of the second section has a size along a direction perpendicular to the flow direction of the refrigerant in the at least one channel (e.g. a height, a width, a diameter, an edge length, etc.) in a range from approximately 0.1 mm to approximately 20 mm, for example from approximately 0.5 mm to approximately 10 mm, from approximately 1 mm to approximately 5 mm.
  • Examples 55 to 89 optionally further comprise that the
  • Cross-sectional area of the first section is provided (in other words, reduced) by upsetting the at least one channel.
  • Example 91 the cooling method according to any one of
  • Examples 55 to 90 optionally further include that the at least one channel has a narrowing element (eg a sleeve, a perforated disk, a perforated plate, a cap, etc.) which is arranged in the first section, so that the cross-sectional area of the first section is reduced.
  • a narrowing element eg a sleeve, a perforated disk, a perforated plate, a cap, etc.
  • Examples 55 to 90 optionally further comprise that a constricting element is arranged (e.g. fastened, such as soldered, etc.) at the entry of the at least one channel.
  • a constricting element is arranged (e.g. fastened, such as soldered, etc.) at the entry of the at least one channel.
  • the narrowing element can serve as the first section of the at least one channel and the at least one channel can serve as the second section of the at least one channel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

Selon différents modes de réalisation, un échangeur de chaleur (100) peut présenter au moins un canal (102) pour acheminer un agent de refroidissement, l'au moins un canal (102) présentant une première section (102-1) et une seconde section (102-2), la première section (102-1) se trouvant en amont de la seconde section (102-2) lorsque l'on considère le sens de circulation de l'agent de refroidissement dans l'au moins un canal (102), la seconde section (102-2) présentant une surface de section transversale qui est supérieure à celle de la première section (102-1) de telle sorte qu'une sublimation de l'agent de refroidissement est possible dans la seconde section (102.2).
EP20728693.1A 2019-05-20 2020-05-20 Échangeur thermique et procédé de refroidissement Pending EP3973242A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019113327.0A DE102019113327A1 (de) 2019-05-20 2019-05-20 Wärmeübertrager und Kühlungsverfahren
PCT/EP2020/064085 WO2020234358A1 (fr) 2019-05-20 2020-05-20 Échangeur thermique et procédé de refroidissement

Publications (1)

Publication Number Publication Date
EP3973242A1 true EP3973242A1 (fr) 2022-03-30

Family

ID=70861453

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20728693.1A Pending EP3973242A1 (fr) 2019-05-20 2020-05-20 Échangeur thermique et procédé de refroidissement

Country Status (6)

Country Link
US (1) US11994346B2 (fr)
EP (1) EP3973242A1 (fr)
JP (1) JP2022533701A (fr)
CN (1) CN114144628A (fr)
DE (1) DE102019113327A1 (fr)
WO (1) WO2020234358A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021024403A1 (fr) * 2019-08-07 2021-02-11 三菱電機株式会社 Unité de refroidissement
DE102020130061A1 (de) * 2020-11-13 2022-05-19 CTS Clima Temperatur Systeme GmbH Wärmeübertrager und Kältemittelkreislauf

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH482993A (de) * 1967-05-27 1969-12-15 Benteler Werke Ag Klimaanlage mit mindestens einem Heiz- bzw. Kühlkörper
DE10237037A1 (de) * 2002-08-08 2004-02-19 Behr Gmbh & Co. Kondensator, insbesonder für eine Kraftfahrzeug-Klimaanlage
JP2004308972A (ja) * 2003-04-03 2004-11-04 Mayekawa Mfg Co Ltd Ｃｏ２冷凍機
CN100541108C (zh) * 2003-08-01 2009-09-16 昭和电工株式会社 集管箱和具有该集管箱的热交换器
AU2005326710A1 (en) * 2005-02-02 2006-08-10 Carrier Corporation Parallel flow heat exchanger with crimped channel entrance
EP1939548A1 (fr) * 2005-10-17 2008-07-02 Mayekawa Mfg. Co., Ltd. Refrigerateur a co2
CN101275790A (zh) * 2008-04-16 2008-10-01 张信荣 利用二氧化碳作为循环工质的低温制冷方法及其热泵系统
JP4715971B2 (ja) * 2009-11-04 2011-07-06 ダイキン工業株式会社 熱交換器及びそれを備えた室内機
IT1397911B1 (it) * 2010-01-28 2013-02-04 Alfa Laval Corp Ab Sistema di distribuzione del fluido refrigerante in un dispositivo di scambio termico
CN201903225U (zh) * 2010-12-10 2011-07-20 北大工学院绍兴技术研究院 适用二氧化碳固气两相流的蒸发器
JP5934569B2 (ja) * 2012-04-27 2016-06-15 日立Ｇｅニュークリア・エナジー株式会社 保護部材付熱交換器
US9297595B2 (en) * 2013-08-22 2016-03-29 King Fahd University Of Petroleum And Minerals Heat exchanger flow balancing system
JP6405914B2 (ja) * 2014-11-11 2018-10-17 株式会社デンソー 熱交換装置及び熱交換装置の製造方法
DE102015111183B4 (de) 2015-07-10 2023-05-04 Technische Universität Dresden Kreislaufverfahren zur Kältebereitstellung mit Kohlendioxid als Kältemittel und Kälteanlage zur Durchführung des Verfahrens
DE102015118105B4 (de) * 2015-10-23 2019-05-09 Technische Universität Dresden Verfahren und Vorrichtung zum Betreiben eines Kältekreislaufes mit einem Sublimator für Kohlendioxid als Kältemittel

Also Published As

Publication number Publication date
DE102019113327A1 (de) 2020-11-26
WO2020234358A1 (fr) 2020-11-26
US20220221227A1 (en) 2022-07-14
JP2022533701A (ja) 2022-07-25
US11994346B2 (en) 2024-05-28
CN114144628A (zh) 2022-03-04

Similar Documents

Publication Publication Date Title
DE60113363T2 (de) Kälteanlage mit Phasentrennung
DE60011196T2 (de) Kombinierter Wärmetauscher mit Verdampfer, Akkumulator und Saugleitung
DE102006012441B4 (de) Ejektorpumpenkreisvorrichtung
DE102006036549B4 (de) Ejektorpumpenkreis
DE102010044532B4 (de) Ejektor
DE102006014867B4 (de) Ejektorpumpenkühlkreis
DE69827110T2 (de) Klimaanlage
DE102007002720A1 (de) Wärmetauscher und Kühlkreisvorrichtung mit diesem
DE102005012611A1 (de) Ejektorpumpe
DE10294713T5 (de) Akkumulator für interne Wärmeaustauscher
DE69421222T2 (de) Kühlgerät
EP3973242A1 (fr) Échangeur thermique et procédé de refroidissement
DE112014000558T5 (de) Kapazitätsmodulierung einer Ausdehnungsvorrichtung einer Heizungs-, Lüftungs- und Klimaanlage
DE69510405T2 (de) Kältemittel-Verteilvorrichtung
DE102007015530A1 (de) Wärmeaustauscher
DE60108677T2 (de) Druckverminderer und Kältekreislauf zur Verwendung derselben
DE69733284T2 (de) Kondensatoraufbaustruktur
DE102007034710B4 (de) Zweistufiger Absorptionskühler
DE3229779C2 (fr)
EP0190319B1 (fr) Machine frigorifique ou pompe a chaleur et pompe a jet pour celle-ci
DE102012110701A1 (de) Wärmeübertrager für einen Kältemittelkreislauf
DE102020130063A1 (de) Temperieranlage und Verfahren zum Betreiben einer Temperieranlage
DE112013002133T5 (de) Wärmetauscher und Verfahren zur Wärmeübertragung
DE2754132C2 (de) Kühlvorrichtung
DE102008005076A1 (de) Kältemittelkreis und Verfahren zum Betreiben eines Kältemittelkreises

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20210915

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS