EP4244549A1 - Échangeur thermique et circuit de refroidissement - Google Patents

Échangeur thermique et circuit de refroidissement

Info

Publication number
EP4244549A1
EP4244549A1 EP21810302.6A EP21810302A EP4244549A1 EP 4244549 A1 EP4244549 A1 EP 4244549A1 EP 21810302 A EP21810302 A EP 21810302A EP 4244549 A1 EP4244549 A1 EP 4244549A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
channel
distributor
nozzle
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
EP21810302.6A
Other languages
German (de)
English (en)
Inventor
Andreas Wagner
Thomas Rieger
Philipp JEHS
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.)
CTS Clima Temperatur Systeme GmbH
Original Assignee
CTS Clima Temperatur Systeme GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by CTS Clima Temperatur Systeme GmbH filed Critical CTS Clima Temperatur Systeme GmbH
Publication of EP4244549A1 publication Critical patent/EP4244549A1/fr
Pending legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F25B39/028—Evaporators having distributing means
    • 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
    • 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
    • F28D1/0535—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 the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with 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

Definitions

  • the invention relates to a heat exchanger for generating temperatures below a temperature of approximately 223 K.
  • a temperature of approximately 223 K is to be understood as a temperature in the range from 220 K to 230 K, preferably 220 K to 225 K.
  • the invention is therefore based on the object of creating a heat exchanger in which problems caused by sublimating refrigerants are avoided as far as possible.
  • this object is achieved by a heat exchanger which has a refrigerant distributor arranged on the inlet side of the heat exchanger, at least one nozzle element running from the refrigerant distributor and limiting a mass flow of the refrigerant, at least one heat exchanger channel which is connected to the at least one nozzle element and which in turn runs in a heat exchanger body, and a refrigerant collector arranged on the output side of the heat exchanger and adjoining the at least one heat exchanger channel on its side opposite the nozzle element.
  • the advantage of the solution according to the invention can be seen in the fact that the mass flow limitation required for the formation of a solid phase of the refrigerant takes place through the nozzle element immediately before entry into the heat exchanger channel, so that there is the possibility of the formation of the solid phase of the refrigerant as possible before entry into the heat exchanger channel and then in the heat exchanger channel, due to the expansion following the nozzle element, essentially only allowing a formation of solid and gaseous phases to take place, with the solid phase and the gaseous phase of the refrigerant in the course of the heat exchanger channel through sublimation of heat record, tape.
  • the formation of a solid phase and thus the problem of blockages due to the formation of the solid phase of the refrigerant can essentially be avoided both in the refrigerant distributor and in the nozzle element.
  • the nozzle element limiting the mass flow of the refrigerant has a cross-sectional area which, in relation to a subsequent heat exchanger channel supplied with refrigerant, is at most 0.05 mm 2 or less, preferably at most 0.01 mm 2 or less , and more preferably at most 0.005 mm 2 or less.
  • the maximum cross-sectional areas should be made even smaller by a factor corresponding to the number of nozzle elements.
  • the maximum cross-sectional areas must be increased by a factor corresponding to the number of heat exchanger channels.
  • the design of the heat exchanger channels it is preferably provided that they have a cross-sectional area of less than 8 mm 2 , preferably 4 mm 2 and even better 1.5 mm 2 in order to obtain optimum heat transfer, particularly with the sublimating refrigerant.
  • any sublimating refrigerant is conceivable as the refrigerant.
  • carbon dioxide is provided as a refrigerant within the scope of this invention, to which additives, for example hydrocarbons, can also be added if necessary.
  • thermoelectric body is designed to enclose the at least one heat exchanger channel on the peripheral side.
  • the heat exchanger body is designed as a tubular body.
  • a heat exchanger channel can run in the heat exchanger body.
  • Another possibility provides for a multiplicity of heat exchanger channels to run in the heat exchanger body.
  • the at least one heat exchanger channel has at least one flow deflection area.
  • a flow deflection area serves to prevent the solid phase of the refrigerant from settling in the heat exchanger channel by changing or varying the flow conditions, for example by generating turbulence.
  • the flow deflection area brings about a flow deflection at an angle of at least 30° with respect to a rectilinear direction of flow propagation.
  • the flow deflection region effects a flow deflection at an angle of at least 40° with respect to a straight flow propagation.
  • the at least one heat exchanger channel has flow deflection areas that connect channel sections running at an angle to one another.
  • the at least one heat exchanger channel has at least one curved flow deflection area, since this makes it possible to change the flow conditions to a sufficiently large extent.
  • the at least one curved flow deflection area has a radius of curvature that is at most 40 times the mean diameter of the heat exchanger channel.
  • An advantageous embodiment provides that the respective heat exchanger channel extends between a first end area associated with it and formed by the heat exchanger body and connected to the refrigerant distributor and a second end area connected to the refrigerant collector.
  • An advantageous solution provides that the first end area of the heat exchanger is arranged such that it engages in the coolant distributor.
  • the receptacle can be arranged, in particular formed, on the refrigerant distributor.
  • a particularly advantageous solution provides for the receptacle to be arranged on a wall of the refrigerant distributor and, in particular, to be formed into the wall by machining it.
  • an expedient solution provides that the receptacle accommodates an end wall area of the heat exchanger body.
  • the end wall area of the heat exchanger body rests against a base of the receptacle.
  • the receptacle encompasses the heat exchanger body in the area of its outer contour at least in a peripheral segment, in particular completely.
  • nozzle element in particular the nozzle channel, extends from a region of the receptacle adjoining the heat exchanger channel to the interior of the refrigerant distributor.
  • the first end region of the heat exchanger body extends into an interior space of the coolant distributor and is in particular arranged in it.
  • the heat exchanger channel is closed at the first end area by an embossing of at least one wall area of the heat exchanger body, so that the heat exchanger channel does not open directly into the refrigerant distributor, but instead refrigerant is supplied from the refrigerant distributor via the nozzle element.
  • the respective heat exchanger channel is closed at the first end area by an embossing of at least one wall area of the heat exchanger body.
  • the embossing is expediently carried out in such a way that the at least one wall area of the heat exchanger body deformed by the embossing lies within an outer contour of the heat exchanger body in order to be able to easily establish a connection between the refrigerant distributor and the heat exchanger body in the area of the outer contour that is unchanged by such an embossing.
  • the embossing of the wall area of the heat exchanger body takes place as a one-sided embossing with partial preservation of an outer contour of the heat exchanger body opposite this wall area.
  • embossing is formed as a multi-sided embossing of a plurality of wall areas, in particular two wall areas lying opposite one another, of the heat exchanger body.
  • the nozzle element could be designed as a gap which limits the mass flow of the refrigerant.
  • nozzle element is designed as a nozzle channel.
  • the nozzle element could be arranged outside of the end area of the heat exchanger channel.
  • At least one nozzle element for supplying refrigerant to the respective heat exchanger channel is arranged on the first end area, so that the end area is also used to form the nozzle element.
  • the nozzle element is incorporated into the end area, for example this can take place before or after the embossing in the end area.
  • the nozzle element can be incorporated by laser processing.
  • nozzle element is arranged in the area of a wall area deformed by the embossing.
  • a further advantageous solution provides that the nozzle element is incorporated into an end wall area formed by the embossing.
  • the nozzle element is formed by a nozzle channel shaped body against which the at least one wall area is embossed, with the nozzle channel having the shape specified by the nozzle channel shaped body after the removal of the nozzle channel shaped body after embossing.
  • the object mentioned at the outset is achieved according to the invention in that a further advantageous solution provides for several heat exchanger channels to lie next to one another in the heat exchanger body, for example in a plane in which the heat exchanger body extends in the form of a plate.
  • a plate heat exchanger can thus be produced in a simple manner.
  • this is possible in that a plurality of heat exchanger bodies are arranged one above the other in a stacking direction with extension planes parallel to one another. Provision is preferably made here for the plurality of heat exchanger bodies to be connected to a refrigerant distributor which extends in the stacking direction.
  • a nozzle element for feeding refrigerant into the respective heat exchanger channel is arranged in a wall region of the refrigerant distributor, which is adjoined by at least one heat exchanger channel of the heat exchanger body.
  • the heat exchanger channels connect to the nozzle elements with their first end area and open into the refrigerant collector with their second end area.
  • the refrigerant collector extends in the stacking direction.
  • the object mentioned at the beginning is achieved in that in a further advantageous embodiment of a heat exchanger according to the invention it is provided that the heat exchanger channels run between an inner body enclosing a channel for heat-emitting medium and an outer body enclosing the inner body on its side opposite the heat-emitting medium and which is arranged in the area of a first end side of the inner body and the outer body of the refrigerant distributor and is arranged in the area of a second end side of the inner body and the outer body of the refrigerant collector opposite the first end side.
  • the nozzle elements e.g.
  • nozzle element carrier located between the inner body and the outer body, wherein the nozzle element carrier can be embodied, for example, as a distribution ring and with at least one nozzle element, in particular a nozzle duct, opening into one of the heat exchanger ducts.
  • a nozzle element that limits the mass flow of the refrigerant is arranged in the refrigerant distributor and supplies refrigerant to all of the heat exchanger channels.
  • the nozzle element has a sufficiently large cross section so that it can act to limit the mass flow for the total number of heat exchanger channels.
  • Such a nozzle element can be formed, for example, by an annular gap, with the annular gap preferably being formed by two concentric, for example conical, surfaces that can be adjusted relative to one another for setting the annular gap.
  • the heat-emitting medium supplies heat to the refrigerant in the respective heat-exchanger channel through the respective heat-exchanger body.
  • the at least one heat exchanger body is in direct contact with the heat-exchanging medium in order to ensure optimal heat conduction. Furthermore, to avoid evaporation processes in the refrigerant distributor, it is preferably provided that the heat exchanger in the area of the refrigerant distributor is provided with thermal insulation that encloses it in particular, so that the refrigerant is not cooled to such an extent that it is at least partially converted into a solid before it enters the nozzle element phase can pass.
  • the invention relates to a refrigerant circuit, comprising a refrigerant compressor, a heat exchanger extracting heat from the compressed refrigerant and a heat-absorbing heat exchanger fed with the compressed refrigerant, which heat exchanger is designed according to one of the preceding features.
  • the refrigerant supplied to the refrigerant distributor in the refrigerant circuit during operation thereof has a pressure above a triple point of the refrigerant and enters the refrigerant distributor with this pressure.
  • refrigerant is fed into the refrigerant distributor in a supercritical state of the latter.
  • refrigerant with a liquid phase and a gaseous phase is supplied to the refrigerant distributor.
  • a further embodiment of the solution according to the invention provides that when the refrigerant circuit is in operation, refrigerant in the liquid phase is supplied to the refrigerant distributor.
  • the refrigerant circuit according to the invention provides for the refrigerant in the heat exchanger channels to be present at a pressure below the pressure of the triple point of the refrigerant during operation of the refrigerant circuit.
  • Such a pressure has the consequence that part of the refrigerant changes into the solid phase and another part of the refrigerant into the gas phase and that the refrigerant present in the solid phase then also changes into the gas phase by sublimation.
  • the nozzle element is dimensioned in such a way that there is essentially no expansion of the refrigerant to a pressure below the triple point of the same during operation of the refrigerant circuit, so that the refrigerant only has the opportunity in the heat exchanger channels to get into the solid To pass phase and then to sublimate.
  • the invention relates to a temperature testing system, in which a refrigerant circuit is provided according to one of the above features and in which the heat-absorbing heat exchanger interacts with a medium acting on a test object, which is arranged, for example, in a test chamber of the testing system, so that in the test chamber allow the desired low temperatures to be generated.
  • the refrigerant circuit supplies compressed refrigerant to a second heat exchanger, in which it evaporates at a pressure which is above the pressure of the triple point of the refrigerant.
  • Such a second heat exchanger offers the advantage that, due to its higher efficiency, the medium in the test chamber and thus also the test object can initially be cooled with it, and only then when temperatures below approximately 223° K are required, the first heat exchanger for use comes.
  • the temperature testing system according to the invention can thus be operated with improved efficiency.
  • the invention relates to a method for operating a refrigerant circuit and a temperature testing system.
  • Heat exchanger (30) comprising a refrigerant distributor arranged on the inlet side of the heat exchanger, at least one nozzle element (34, 146) running from the refrigerant distributor (32) and limiting a mass flow of the refrigerant, at least one nozzle element (34, 146) attached to the at least one nozzle element adjoining heat exchanger channel (36), which in turn runs in a heat exchanger body (40), and a refrigerant collector (38) arranged on the outlet side of the heat exchanger (30) and adjoining the at least one heat exchanger channel (36) on its side opposite the nozzle element (34, 146) .
  • Heat exchanger according to embodiment 1 or 2 wherein the heat exchanger body (40) is designed as a tubular body (50).
  • Heat exchanger according to one of the preceding embodiments, wherein a heat exchanger channel (36) runs in the heat exchanger body (40).
  • Heat exchanger according to one of embodiments 1 to 3, wherein a plurality of heat exchanger channels (36) runs in the heat exchanger body (40).
  • each flow deflection area (92) effects a flow deflection at an angle of at least 20° with respect to a rectilinear direction of flow propagation.
  • Heat exchanger according to embodiment 15 or 16 wherein the receptacle (35) accommodates an end wall area (64) of the heat exchanger body (40). 18. Heat exchanger according to one of embodiments 15 to 17, wherein the receptacle (35) encompasses the heat exchanger body (40) in the area of its outer contour (52) at least in the area of a peripheral segment.
  • Heat exchanger according to one of embodiments 15 to 18, wherein the nozzle element (34) extends from an area of the receptacle (35) adjoining the heat exchanger channel (36) to the interior (46) of the refrigerant distributor (32).
  • Heat exchanger according to one of embodiments 19 to 25, wherein at least one nozzle element (40, 146) for supplying refrigerant to the respective heat exchanger channel (36) is arranged on the first end region (42).
  • Heat exchanger according to one of the embodiments 21 to 27, wherein the nozzle element (34) is arranged in the area of a wall area (56, 64) deformed by the embossing.
  • Heat exchanger according to the preamble of embodiment 1 or according to one of the preceding embodiments, wherein a plurality of heat exchanger channels (36) lie next to the heat exchanger body (40') in a plane in which the heat exchanger body (40') extends in the form of a plate.
  • Heat exchanger according to embodiment 33 wherein in a wall area of the refrigerant distributor (32), to which at least one heat exchanger channel (36) of the heat exchanger body (40') adjoins, a nozzle element (34) for supplying refrigerant into the respective heat exchanger channel (36) is arranged.
  • Heat exchanger according to one of the preceding embodiments, wherein the heat exchanger channels (36) connect to the nozzle elements (34) with their first end areas (42) and open into the refrigerant collector (38') with their second end areas (44').
  • Heat exchanger according to embodiment 37 wherein the nozzle elements (34) are arranged in a nozzle element carrier (128) located between the inner body (122) and the outer body (124) and that in each case at least one nozzle element (34) is inserted into one of the heat exchanger channels (36) flows.
  • Heat exchanger according to embodiment 37 wherein a nozzle element (146) limiting the mass flow of the refrigerant is arranged in the refrigerant distributor (32′′′′) and supplies refrigerant to all heat exchanger channels (36).
  • Heat exchanger according to one of the preceding embodiments, wherein a heat-emitting medium supplies heat to the coolant in the respective heat-exchanger channel (36) through the respective heat-exchanger body (40).
  • Heat exchanger according to embodiment 40 wherein the at least one heat exchanger body (40) is in direct contact with the heat-exchanging medium.
  • Refrigerant circuit (10) comprising a refrigerant compressor (12), a heat exchanger (18) extracting heat from the compressed refrigerant, and a heat-absorbing heat exchanger (30) fed with the compressed refrigerant, which is designed according to one of the preceding embodiments.
  • Refrigerant circuit according to embodiment 43 wherein the refrigerant supplied to the refrigerant distributor (32) in the refrigerant circuit (10) has a pressure above a triple point of the refrigerant and enters the refrigerant distributor (32) with it.
  • Refrigerant circuit according to embodiment 43 or 44 wherein the pressure of the refrigerant in the heat exchanger channels (36) is below the triple point of the refrigerant and the refrigerant collector (38) is connected to a suction side (14) of the refrigerant compressor (12).
  • Refrigerant circuit according to embodiment 43 to 45 wherein in the refrigerant circuit (10), refrigerant is supplied into the refrigerant distributor (32) in a supercritical state thereof.
  • Refrigerant circuit according to one of the embodiments 43 to 46 wherein in the refrigerant circuit (10) a supply of refrigerant with a liquid and a gaseous phase takes place in the refrigerant distributor (32).
  • Temperature testing system according to embodiment 51, wherein the refrigerant circuit supplies compressed refrigerant to a second heat exchanger (230), in which this refrigerant evaporates at a pressure which is above the pressure of the triple point of the refrigerant.
  • a method for operating a refrigerant circuit (10) comprising a refrigerant compressor (12), a heat exchanger (18) extracting heat from the compressed refrigerant and a heat-absorbing heat exchanger (30) fed with the compressed refrigerant, which is designed according to one of the preceding embodiments, wherein in the refrigerant circuit (10) the refrigerant is supplied to the refrigerant distributor (32) at a pressure above a triple point of the refrigerant.
  • Method for operating a temperature testing system which has a refrigerant circuit (10') according to one of the embodiments 43 to 50, and a heat-absorbing first heat exchanger (30) according to one of the embodiments 1 to 42, which is connected to a medium (214), in particular in a test chamber (210) thereof, and in which the refrigerant circuit (10') is operated according to a method according to one of the embodiments 53 to 59.
  • FIG. 1 shows a schematic representation of a first embodiment of a refrigerant circuit according to the invention
  • FIG. 2 shows a first exemplary embodiment of a heat exchanger according to the invention
  • FIG. 3 shows a schematic representation of a first end region of a heat exchanger body designed as a tubular body, wherein
  • Fig. 3a is a plan view of the end portion
  • Figure 3b shows a longitudinal section through the end portion
  • Figure 4a is a front plan view
  • Fig. 4b is a longitudinal section and Fig. 4c shows the final shape of a closure of the tubular body achieved by stamping
  • FIG. 5 shows a schematic representation similar to FIG. 4 of the production of a nozzle channel by inserting a nozzle channel shaped body during embossing and removing the same after embossing
  • 5a shows the embossing with the nozzle channel shaped body in a plan view from the front
  • 5c shows the end shape of the nozzle channel after removal of the nozzle channel shaped body
  • 6a shows the embossing in a plan view from the front
  • FIG. 7 shows a closure of a heat exchanger channel by stamping the tubular body on two sides analogously to FIG. 4;
  • FIG. 8 shows the production of a nozzle channel by multi-sided stamping of the tubular body using a nozzle channel shaped body analogous to FIG. 5 and
  • FIG. 9 shows the introduction of a nozzle channel into an end wall area of the embossed end area analogous to FIG. 6;
  • FIG. 10 shows a longitudinal section through a second embodiment of a closure of heat exchanger channels in the first end area of a heat exchanger body
  • FIG. 11 shows a representation of a further exemplary embodiment of a closure of a plurality of heat exchanger channels of the tubular body in the first end region
  • 11a is a plan view of the end area
  • 11b shows a longitudinal section through the end area
  • FIG. 12 shows a representation of a closure of the multiple heat exchanger channels by embossing on one side analogously to FIG. 4;
  • FIG. 13 shows a schematic representation similar to FIG. 12 of a production of a nozzle channel by means of a nozzle channel shaped body and removal of the same after stamping analogous to FIG. 5;
  • FIG. 14 shows the introduction of a nozzle channel into the end wall area of the end area produced by embossing analogously to FIG. 6;
  • FIG. 15 shows a closure of the heat exchanger channels by stamping the tubular body on two sides analogously to FIG. 7;
  • FIG. 16 shows the production of a nozzle channel by stamping the tubular body on two sides using a nozzle channel shaped body analogous to FIG. 8 ;
  • FIG. 17 an introduction of a nozzle channel into an end wall area of the embossed end area analogously to FIG. 9;
  • FIG. 18 shows a partial side view of a further exemplary embodiment of a heat exchanger according to the invention.
  • Figure 19 is a section taken along line 19-19 of Figure 18;
  • FIG. 20 shows a section similar to FIG. 19 through a further exemplary embodiment of a heat exchanger according to the invention.
  • FIG. 21 shows a first exemplary embodiment of a heat exchanger channel with flow deflection elements
  • FIG. 22 shows a second exemplary embodiment of a heat exchanger channel with flow deflection elements
  • FIG. 23 shows a third exemplary embodiment of a heat exchanger channel with flow deflection elements
  • FIG. 24 shows a fourth exemplary embodiment of a heat exchanger channel with flow deflection elements
  • FIG. 25 shows a fifth exemplary embodiment of a heat exchanger channel with flow deflection elements
  • 26 shows a sixth exemplary embodiment of a heat exchanger channel with flow deflection elements
  • FIG. 27 shows a schematic representation of a partial section along line 27-27 in FIG. 28 through a further exemplary embodiment of a heat exchanger according to the invention, designed as a plate heat exchanger;
  • FIG. 28 shows a position of the plate heat exchanger according to FIG. 27;
  • 29 shows a representation of a distribution ring with nozzle channels for supplying refrigerant to the heat exchanger channels of a layer of the plate heat exchanger;
  • FIG. 30 shows an exemplary embodiment of a refrigerant distributor which is routed through all layers of the plate heat exchanger
  • FIG. 31 shows an exploded view of a further exemplary embodiment of a heat exchanger according to the invention, designed as a coaxial heat exchanger;
  • FIG. 32 shows a longitudinal section through a further exemplary embodiment of a heat exchanger according to the invention, also designed as a coaxial heat exchanger and
  • FIG 33 shows a schematic representation of an exemplary embodiment of a temperature testing system.
  • FIG. 1 of a refrigerant circuit designated as a whole by 10 comprises a refrigerant compressor 12, which compresses refrigerant supplied on a suction side 14 and discharges it on a high-pressure side 16, with the refrigerant compressed to high pressure being fed from the refrigerant circuit 10 to a heat exchanger 18 on the high-pressure side , which is capable of extracting heat from the refrigerant compressed to high pressure and dissipating it in the form of a heat flow 22 .
  • the compressed refrigerant which has been cooled by removing the heat flow 22, is fed to a control valve 24, which thus makes it possible to feed the refrigerant, which is still under pressure, to a heat exchanger, designated as a whole by 30, in which, after expansion of the refrigerant, heat is absorbed, in Fig. 1 identified as fluid stream 28.
  • the heat exchanger has a refrigerant distributor 32 connected to the control valve 24, to which the pressurized refrigerant is supplied and from which the refrigerant is supplied via nozzle channels 34 to the heat exchanger channels 36, in which the refrigerant expands while absorbing heat from the fluid flow 28 takes place, which runs in particular transversely or perpendicularly to the plane of the drawing.
  • the refrigerant After flowing through the heat exchanger channels 36 , the refrigerant enters a refrigerant collector 38 which collects the refrigerant from all the heat exchanger channels 36 and from which the refrigerant is then supplied to the suction side 14 of the refrigerant compressor 12 .
  • the heat exchanger channels 36 are formed by heat exchanger bodies 40 running parallel to one another, which extend from the refrigerant distributor 32 to the refrigerant collector 38, with the heat exchanger bodies 40 having a first end region 42 for connection to the refrigerant distributor 32 and a second end region 44 for connection to the refrigerant collector.
  • a preferred design solution provides for the first end area 42 of the heat exchanger bodies 40 to protrude into an interior space 46 of the refrigerant distributor 32 and also for the first end area 42 to be provided with the nozzle duct 34, which thus leads out of the interior space 46 of the refrigerant distributor 32 refrigerant absorbs and delivers it to the heat exchanger channel 36, in which the refrigerant then expands and cools the heat exchanger body 40, so that it can absorb heat from the heat flow 28 flowing around the respective heat exchanger body.
  • the nozzle channels 34 are formed in the end regions 42 in such a way that they limit a mass flow of the refrigerant flowing from the interior 46 to the respective heat exchanger channel 36 .
  • the design of the nozzle channels 34 with regard to their cross-sectional area is such that the refrigerant flows in them at the critical speed, ie in this case the speed of sound, and thus essentially an isenthalpic expansion of the refrigerant takes place in the nozzle channels 34 .
  • the refrigerant is supplied in the refrigerant circuit 10 to the refrigerant distributor 32 at a pressure level which is above the triple point, for example in the range between 10 bar and 160 bar, preferably in the range from 70 bar to about 140 bar and in particular in the range from 10 bar to about 70 bar.
  • the pressure in the nozzle channel 34 is then reduced, but at the transition from the nozzle channel 34 to the heat exchanger channel 36 it is preferably still above the triple point of the refrigerant, in this case above the triple point of CO2, so that there is essentially a sublimation in the nozzle channel 34 is prevented.
  • the pressure in the nozzle channel 34 and in particular also up to the outlet of the nozzle channel 34 is preferably in the range of greater than 6 bar, for example in the range from approximately 6 bar to approximately 40 bar.
  • the pressure is below the pressure of the refrigerant at the triple point, so that a solid phase of the refrigerant forms and sublimation of the refrigerant, i.e. in this case CO2 for example, occurs, so that the refrigerant on its way passes completely into the gaseous state through the heat exchanger channel 36 in the respective heat exchanger body 40 and can absorb heat from the fluid flow 28 in the process.
  • a solid phase of the refrigerant forms and sublimation of the refrigerant, i.e. in this case CO2 for example
  • Gaseous refrigerant is preferably present at the second connection 44 of the heat exchanger body 40, which passes from the heat exchanger channel 36, in particular with its cross section, into an interior space 48 of the refrigerant collector and is collected by the latter and fed via the refrigerant circuit 10 to the suction side 14 of the refrigerant compressor 12.
  • the nozzle channels 34 have, for example, a diameter of less than 0.1 mm and a length in the range of 0.05 mm to 5 mm.
  • the heat exchanger body 40 is designed, for example, as a tubular body 50, which extends from the first end region 42 to the second end region 44 and has, for example, a substantially circular outer contour 52, with a tube wall 54 forming the outer contour 52 encloses the heat exchanger channel 36 on the peripheral side, as shown in FIGS. 3a and 3b.
  • first end region 42 When forming the first end region 42, it is necessary, as shown in FIGS. 4a to 4c, to close the heat exchanger channel 36.
  • This is done, for example, by embossing the tubular body 50 on one side, with a first tubular wall area 56, which forms, for example, one half of the tubular body 50, being deformed in such a way that it comes to rest against an opposite, undeformed tubular wall area 58, so that the embossing of the tubular body 50 the embossed tube wall area 56 lies tightly against the undeformed tube wall area 58 along a contact surface 62 and thus closes the heat exchanger channel 36 in the area of the connection section 42, this taking place in particular with the formation of an end wall area 64 closing the heat exchanger channel 36, as shown in FIGS. 4a to 4c .
  • a nozzle channel shaped body 72 in the region of contact surface 62 when stamping tube wall region 56 into tube wall region 58 before laying tube wall region 56 against tube wall region 58, which has the dimensions of the 5a to 5b, so that the tube wall area 56 rests against the tube wall area 58 along the contact surface 62, but not in the area of the nozzle channel shaped body 72.
  • the nozzle channel 34 remains in the end section 42, as shown in FIG.
  • nozzle channel shaped body As an alternative to providing the nozzle channel shaped body, there is also the possibility, as shown in Fig. 6a to c, of introducing the nozzle channel 34 into the end wall area 64 after closing the heat exchanger channel 36 in the area of the first connection section 42 by machining, for example laser machining, so that the nozzle channel 34 passes through the end wall area 64 and thus the pipe wall area 56 bears against the pipe wall area 58 over the entire surface along the contact surface 62 formed during the embossing.
  • machining for example laser machining
  • a nozzle channel 34 in one of the end wall areas 64a, 64b after stamping the tube wall areas 56a and 56b together to form the end wall areas 64a and 64b, for example by machining, in particular laser machining then penetrates the respective end wall area 64a or 64b.
  • the embossing of the pipe wall areas 56 and 58 takes place within the outer contour 52, so that the heat exchanger body 40 in the area of the first end area 42 does not extend beyond the outer contour 52 of the tube body 50 extends out, but the deformed tube wall areas 56 are all within the outer contour 52.
  • the refrigerant distributor 32 is provided with thermal insulation 86, which prevents unwanted cooling of the refrigerant already in the interior 46 of the refrigerant distributor 32, so that this occurs even at a pressure that is higher than the pressure at the triple point a solid phase of the refrigerant before it enters the nozzle channels 34 is prevented as far as possible.
  • the heat exchanger body 40' is designed such that it has a tubular body 50' in which a plurality of heat exchanger channels 36 are arranged, with each heat exchanger channel 36 being surrounded by tube walls 54'.
  • the tube wall area 56 belonging to the respective heat exchanger channel 36 is embossed in the direction of an undeformed tube wall area 58, forming the contact surface 62 such that there is also a tight seal in the area of the contact surface 62 .
  • An end wall area 64 is thus formed for each heat exchanger channel 36, which closes this heat exchanger channel 36 in a similar way to that described in detail in connection with FIG. 4, to which reference is made in this regard.
  • a nozzle channel 34 can be formed on the respective end region 42', in particular by inserting a nozzle channel shaped body 72 between the tube wall regions 56 and 58 to be stamped in order to stamp the tube wall region 56, so that when the tube wall region is molded on 56 to the tube wall area 58 the Contact surface 62 in the area of the molded nozzle channel body 72 does not close tightly, but after the molded nozzle channel body 72 has been pulled out, as shown in FIG.
  • the respective nozzle channel 34 can also be provided in a manner similar to that described in connection with the tubular body 50 .
  • the nozzle channel shaped body 72 is to be inserted between the pipe wall areas 56a and 56b to be pressed and to be removed after the stamping has taken place, so that the nozzle channel 34 corresponding to the nozzle channel gauge 72 is placed between the stamped ones Tube wall portions 56a and 56b remains.
  • a nozzle channel 34 for example by laser machining, into the end wall regions 64a and 64b that form when the tube wall regions 56a and 56b are stamped together, for example in one of them or optionally in both , as shown in Fig. 17b.
  • the tubular wall regions 56a and 56b are also embossed in such a way that their final shape does not protrude beyond the outer contour 52' of the tubular body 50', so that the tubular body 50' can, analogously to the solution according to FIG. 10, be placed in openings 82 of the wall 84 of the refrigerant distributor 32 can be introduced and connected to the wall 84 outside of the first end region 42 in order to be able to produce the heat exchanger 30 as simply as possible.
  • a heat exchanger 30 according to the invention shown in Figs.
  • the refrigerant distributor 32 comprises an elongate, for example tube-like body with a wall 33 which, preferably, accommodates a receptacle 35 for the end region 42 of the heat exchanger body 40 designed as a tubular body 50 is adapted in a form-fitting manner to the first end region 42, which is designed in particular as a blunt end of the tubular body 50, so that the end region 42 rests with its end wall region 54 on a base 37 of the receptacle 35 and a side wall 39 of the receptacle 35 has an outer contour 52 of the tubular body 50 , In particular the circular outer contour of the tubular body 50 includes.
  • the end region 42 After the end region 42 has been inserted into the receptacle 35, it can be tightly connected to the wall 33 of the distributor 32 in a simple manner, for example by joining.
  • a nozzle channel 34 which is designed according to the dimensions corresponding to the above exemplary embodiments and functions according to the operating conditions mentioned, is preferably incorporated in an area of the base 37 that covers the front side of the heat exchanger channel 36 and, starting from this, which extends into the interior space 46 of the refrigerant distributor 32 extends, the incorporation of the nozzle channel 34 being carried out, for example, by mechanical drilling or laser machining.
  • the receptacle 35 in the wall 33 of the refrigerant distributor 32 is incorporated by mechanical processing, for example drilling or milling, and in particular is dimensionally precisely matched to the outer contour 52 of the tubular body.
  • two receptacles 35 can be incorporated into a side wall 33s of the refrigerant distributor 32, for example with an oval cross-sectional shape, with a tubular body 50 being inserted in the same way in each of these receptacles 35. as described in connection with the previous embodiment.
  • the respective nozzle channel 34 which extends into the interior 46 , is also worked out in the respective bottom 37 of the respective receptacle.
  • the dimensions of the nozzle channel 34 and the pressures in the refrigerant distributor 32 and in the respective nozzle channel 34 are therefore identical to those of the preceding exemplary embodiments.
  • the heat exchanger channels 36 have flow deflection areas 92, as shown in FIG the solid refrigerant takes place.
  • the flow deflection areas 92 could be arranged in such a way that they are each arranged between channel sections 94 running in a straight line.
  • the flow deflection areas 92 are preferably designed in such a way that they cause a flow deflection, for example in relation to a straight flow propagation direction 96, of for example at least 20°, preferably at least 40°, in order to achieve sufficiently large turbulence of the sublimating refrigerant.
  • the respective flow deflection area 92 could be designed as a kinked course of the heat exchanger channel 36 .
  • Another advantageous solution provides between the straight channel sections 94 flow deflection areas 92 ', which do not represent a kinking course of the heat exchanger channel 36, but a curved course with a radius of curvature R, which is a multiple of a central channel cross section. preferably less than 40 times the mean channel cross-section.
  • the change in curvature causes, for example, a direction deflection of the order of 90° with respect to the rectilinear propagation of the flow 96.
  • the flow deflection areas 92' can also be arranged, as for example in Fig. 23, so that two consecutive flow deflection areas 92' with their curvature cause a deflection in the same direction and then again in the opposite direction, whereby in each case between two flow deflection areas deflecting in the same direction 92' straight channel sections 94 lie.
  • the flow deflection areas 92" are curved in such a way that they each cause a flow deflection by an angle of the order of approximately 180°, with successive flow deflection areas 92" being connected to one another by straight channel sections 94 .
  • the flow deflection regions 92' which have a radius of curvature, are arranged directly one after the other, so that there are no longer any channel sections 94 running in a straight line between them.
  • the flow deflection sections 92' lead to flow deflections in the order of approximately 20° to 90°.
  • the flow deflection areas 92" also follow one another directly, with these flow deflection areas 92" each causing a flow deflection with the radius of curvature R., which, however, is in the order of approximately 180°, so that in particular the Course of the heat exchanger channel 36 can also be referred to as meandering.
  • a heat exchanger 30" in a further exemplary embodiment of a heat exchanger 30" according to the invention, shown in FIGS. 27, 28 and 29, this is designed as a plate heat exchanger 100, which has layers 104 lying one above the other in a stacking direction 102, in which on the one hand the heat exchanger channels 36 run and on the other hand separated from This medium to be cooled, in this case preferably a fluid, such as a liquid, a gas or a phase-changing fluid, such as brine, is guided.
  • a fluid such as a liquid, a gas or a phase-changing fluid, such as brine
  • each layer 104 comprises two layered metal sheets 104a, 104b lying one on top of the other, which enclose the heat exchanger channels 36 between them and together form the heat exchanger bodies 40" in the layers 104, with the heat-emitting medium flowing through the layers 104 between the heat exchanger bodies 40".
  • the refrigerant distributor 32" runs parallel to the stacking direction 102 and/or the refrigerant collector 38" runs parallel to the stacking direction 102 and penetrates the various layers 104.
  • Such a layer 104 for forming the heat exchanger channels 36 is shown in FIG. 28, the channels 36 in the respective layer 104 being separated from one another by channel separations 106 provided in this layer 104, for example formed by the layer plates 104a, 104b.
  • At least one nozzle duct 34 leads to the respective heat exchanger duct 36, in which case all of the nozzle ducts 34 are formed in the wall 84" of the refrigerant distributor 32" and not in the heat exchanger ducts 36.
  • the wall 84" is formed in the respective layer by a distributor body 108, in which the individual nozzle channels 34 are incorporated, whereby this distributor body 108 can also be aligned relative to the respective layer 104 of the plate heat exchanger by means of an orientation element, for example a nose 112 .
  • an orientation element for example a nose 112 .
  • the distributor bodies 108 are each part of the coolant distributor 32" and form the wall 84" in the respective position as shown in FIG.
  • the distributor bodies 108 can be formed in one piece, with the nozzle channels 34 being incorporated into the wall 84'' by laser machining.
  • the distributor body 108 is divided in two, with the separating plane T between the distributor body elements 108a and 108b running through the nozzle channels 34 and these being produced in that the distributor body elements 108a and 108b are embossed with one another and for embossing in the separating plane T at the points of the to be produced
  • Nozzle channels 34 are arranged nozzle moldings 72, so that when the distribution body elements 108, 108b are stamped in the area of the parting plane T, the nozzle channels 34 are formed, as described in connection with the production of a nozzle channel 34 with FIGS. 5, 8, 13 and 16, whereupon content is referred to.
  • the refrigerant distributor 32 by a tubular body 114, which passes through all layers 104 and in each of the layers 104 in which the heat exchanger channels 36 are arranged, with heat exchanger channels to these 36 leading nozzle channels 34 are provided.
  • the heat exchanger channels 36 run between an inner body 122 and an outer body 124 enclosing the inner body 122, or they are incorporated into one of the same, with the inner body 122 enclosing a space 126 , In which a heat-emitting medium is arranged, in particular flows through it.
  • the inner body 122 and the outer body 124 thus together form the heat exchanger body 40'''.
  • a distribution body 128 is provided, which is provided with the nozzle channels 34 and extends between the inner body 122 and the outer body 124 and thus an interior space 46"' located between the inner body 122 and the outer body 124 of the also in this area by the inner body 122 and the outer body 124 formed coolant distributor 32"' delimited, wherein opposite the distributor body 128 the interior 46"" is closed by an annular body 132.
  • the refrigerant is supplied to the interior 46'' via a connection 134 from the refrigerant circuit.
  • the heat exchanger channels 36 in this exemplary embodiment also preferably run in a meandering manner, similar to the course in FIG. 25, so that reference can be made to the explanations relating to FIG. 25 in this regard.
  • the outer body 124 is provided with a connection 136 for the expanded refrigerant to be discharged, with the interior 48 of the refrigerant collector 38" forming between the inner body 122 and the outer body 124 following the second end regions 44" of the heat exchanger channels 36.
  • the heat exchanger channels 36 are also located between the inner body 122 and the outer body 124, and the heat-emitting fluid also flows through the inner space 126.
  • the refrigerant distributor 32"" is formed by a conical inner body 142 and a conical outer body 144 running at a distance from this, which form an annular gap or conical gap 146 between them, the flow cross section of which also limits the mass flow to via a connection 148 incoming pressurized refrigerant acts and thus has the same effect as the plurality of nozzle channels 34 in the distribution ring 128 of the previous embodiment.
  • the interior space 46"" of the coolant distributor 32"" simultaneously serves as a flow-restricting element for the inflowing coolant.
  • a distribution body similar to the distribution body 128 with nozzle channels 34 can also be provided between the conical inner body 142 and the conical outer body 144 .
  • the interior space 48 of the refrigerant collector 38 ′′ for discharging the refrigerant expanded in the heat exchanger channels 36 is also formed between the inner body 122 and the outer body 124 following the second end region 44 of the heat exchanger channels 36 .
  • a variant of a refrigerant circuit 10' according to the invention is, as shown in Fig. 33, part of a temperature testing system designated as a whole by 200, in particular for carrying out temperature tests, which has, for example, a thermally insulated test chamber 210 in which a test object 212 is arranged, which cold , in particular low temperatures below a temperature of about 223 K is to be exposed.
  • a gaseous medium 214 is arranged in the test chamber 210 , which medium surrounds the test object 12 and is circulated, for example, by means of a blower unit 216 .
  • the gaseous medium 214 is cooled in order to reach the low temperatures by the first heat exchanger 30, which is circulated in particular in the refrigerant circuit 10 'and compressed by the compressor 12 refrigerant in the same way and with the same operating conditions, as explained in connection with Fig. 1, is operated and in particular the heat exchanger is designed and operated according to one of the preceding exemplary embodiments.
  • the heat exchanger 18 is divided into two, namely comprising a heat exchanger 18a, in which the refrigerant compressed by the compressor 12 is first cooled by ambient air in order to release the heat flow 22a, and subsequently comprising the heat exchanger 18b, which is not through a whole Refrigeration system 220 explained in more detail is cooled in order to absorb the heat flow 220b and to liquefy the refrigerant.
  • a supply line to a second heat exchanger 230 branches off from the refrigeration circuit downstream of heat exchanger 18b, in which a control valve 232 is arranged, which controls an inflow of the refrigerant to the second heat exchanger 230, with a return flow from the heat exchanger 230 to the suction connection 14 of the refrigerant compressor has a non-return valve 234 .
  • the second heat exchanger 230 is operated at a higher pressure level, so that when the heat flow 228 is absorbed from the medium 214 in the test chamber 210, there is no sublimation of the refrigerant, but conventional evaporation thereof.
  • a controller 250 controls the inflow of refrigerant from refrigerant circuit 10 via control valve 24 and control valve 232 so that, depending on the required temperature of medium 214, either second heat exchanger 230, for example at temperatures above 220 K, or first heat exchanger 30, for example at temperatures below 220 K, is used.
  • test chamber 10 is also assigned a heater 214 which allows the test chamber 210 and thus the test object 212 to also be heated if necessary in order to implement temperature cycles for testing the test object 212 .
  • the controller 250 preferably also controls the heating 240 in such a way that there is the possibility of exposing the medium 214 and also the object 212 to predetermined temperature cycles.
  • another solution provides for the heat exchangers 30 and 230 to interact with a test medium that is liquid, for example a brine, or gaseous or a phase-changing medium, in that this medium flows through the heat exchangers 30, 230 and the heater 214 and to it the test object 212 is guided.
  • a test medium that is liquid, for example a brine, or gaseous or a phase-changing medium, in that this medium flows through the heat exchangers 30, 230 and the heater 214 and to it the test object 212 is guided.

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  • 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)

Abstract

Echangeur thermique, comprenant un répartiteur d'agent de refroidissement disposé côté entrée de l'échangeur thermique, au moins un élément buse s'étendant à partir du répartiteur d'agent de refroidissement et limitant un flux massique de l'agent de refroidissement, au moins un canal d'échangeur thermique qui est raccordé à l'au moins un élément buse et qui, du côté de ce dernier, s'étend dans un corps d'échange thermique, et un collecteur d'agent de refroidissement disposé côté sortie de l'échangeur thermique et se raccordant à l'au moins un canal d'échangeur thermique de son côté opposé à l'élément buse.
EP21810302.6A 2020-11-13 2021-11-08 Échangeur thermique et circuit de refroidissement Pending EP4244549A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020130061.1A DE102020130061A1 (de) 2020-11-13 2020-11-13 Wärmeübertrager und Kältemittelkreislauf
PCT/EP2021/080954 WO2022101140A1 (fr) 2020-11-13 2021-11-08 Échangeur thermique et circuit de refroidissement

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EP4311989A1 (fr) * 2022-07-26 2024-01-31 CTS Clima Temperatur Systeme GmbH Circuit de fluide frigorigène

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DE1044125B (de) * 1956-02-15 1958-11-20 Gea Luftkuehler Ges M B H Durch einen zwanglaeufig bewegten Luftstrom gekuehlter Oberflaechenkondensator
US6185957B1 (en) 1999-09-07 2001-02-13 Modine Manufacturing Company Combined evaporator/accumulator/suctionline heat exchanger
US20080105420A1 (en) * 2005-02-02 2008-05-08 Carrier Corporation Parallel Flow Heat Exchanger With Crimped Channel Entrance
CN103759474B (zh) * 2014-01-28 2018-01-02 丹佛斯微通道换热器（嘉兴）有限公司 板式换热器
CN108088300B (zh) * 2018-02-23 2021-06-11 江苏宝得换热设备股份有限公司 一种块状流体分配器及其制造方法
US10976084B2 (en) * 2018-09-05 2021-04-13 Audi Ag Evaporator in a refrigerant circuit a
US11713931B2 (en) 2019-05-02 2023-08-01 Carrier Corporation Multichannel evaporator distributor
DE102019113327A1 (de) * 2019-05-20 2020-11-26 Technische Universität Dresden Wärmeübertrager und Kühlungsverfahren

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