EP3460365A1 - Appareil frigorifique avec chambre de stockage et chambre d'évaporateur - Google Patents

Appareil frigorifique avec chambre de stockage et chambre d'évaporateur Download PDF

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Publication number
EP3460365A1
EP3460365A1 EP18194700.3A EP18194700A EP3460365A1 EP 3460365 A1 EP3460365 A1 EP 3460365A1 EP 18194700 A EP18194700 A EP 18194700A EP 3460365 A1 EP3460365 A1 EP 3460365A1
Authority
EP
European Patent Office
Prior art keywords
evaporator
chamber
axis
refrigerating appliance
appliance according
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.)
Withdrawn
Application number
EP18194700.3A
Other languages
German (de)
English (en)
Inventor
Berthold Pflomm
Niels Liengaard
Ulrich Kriegsmann
Christian Hein
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.)
BSH Hausgeraete GmbH
Original Assignee
BSH Hausgeraete 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 BSH Hausgeraete GmbH filed Critical BSH Hausgeraete GmbH
Publication of EP3460365A1 publication Critical patent/EP3460365A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F25D17/067—Evaporator fan units
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/14—Collecting or removing condensed and defrost water; Drip trays
    • 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
    • F28D1/0233—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 air flow channels
    • F28D1/024—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 air flow channels with an air driving element
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • 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
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple 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
    • 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
    • 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
    • F28F1/34—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 obliquely
    • F28F1/36—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 obliquely the means being helically wound fins or wire spirals
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/08—Fluid driving means, e.g. pumps, fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • the present invention relates to a refrigerator with a storage chamber and a remote from the storage chamber evaporator chamber.
  • a fan is usually mounted on a passage between the storage chamber and the evaporator chamber to drive the exchange of air between the chambers.
  • the evaporator is usually a roughly parallelepipedal vane evaporator with lamellae which are parallel to one another and guide the flow of air through the lamella evaporator from one narrow side of the cuboid to the other.
  • the dimensions of the passage are generally much smaller than the length of the upstream and downstream narrow sides. This has the consequence that some parts of the evaporator are aerodynamically favorable in relation to the passage and are accordingly flowed through more than other parts. The strong flow in the aerodynamically favored parts causes the air to cool down less there than in the less favored parts. The existence of different tempered air streams, which mix after passage through the evaporator, affects the efficiency of the evaporator.
  • the object of the invention is to provide a refrigerator in which a uniform flow of the evaporator can be achieved over its entire cross section in a compact evaporator chamber.
  • the object is achieved by, in a refrigerator with at least one storage chamber, an evaporator chamber and at a passage between the storage chamber and Evaporator arranged, a rotation axis having fans and an evaporator arranged in the evaporator chamber arcuate refrigerant lines of the evaporator extend around the axis of rotation.
  • Such orientation of the refrigerant piping allows the air in the evaporator chamber to flow radially from the passageway or toward it while crossing the refrigerant piping under steady state conditions over the length of their bends, so that air flow and cooling of the air in each part of the cross section of the evaporator are approximately equal.
  • the arches may be arcs on at least part of their length, at the center of which is the axis of rotation.
  • the evaporator may have lamellae in a manner known per se in order to increase the surface available for the heat exchange. These fins should protrude from the refrigerant lines in the radial direction to guide the air in the radial direction away from or towards the passage.
  • the fins may comprise at least one plate extending helically around one of the refrigerant lines.
  • a plate may have a contiuous edge on its edge facing away from the refrigerant line edge; then the edge facing the refrigerant line is typically folded accordion-like, so that it can be fastened to the refrigerant line over its entire length.
  • the plate may be slotted on its edge remote from the refrigerant line to form a plurality of tongues between the slots which, when the plate is attached to the refrigerant line, protrude radially from the refrigerant line in different directions.
  • two refrigerant pipes spaced along the rotation axis are connected via the fins.
  • a stiffer, dimensionally stable evaporator block can be formed.
  • refrigerant pipes extending transversely to the direction of flow are not only in the direction of flow, but also in different positions transversely thereto arranged. Accordingly, there are also in the evaporator according to the invention transversely in the flow direction, ie radially to the axis of rotation, spaced refrigerant pipes. These can, without impeding the flow, in a common multi-chamber tube, in particular a microchannel multi-chamber tube run
  • the refrigerant pipes should extend around the axis of rotation over a minimum angle of 90 °.
  • the angle over which the refrigerant lines extend around the axis of rotation does not exceed 180 °. Should it be necessary to surround the axis of rotation at an angle greater than 180 ° with an evaporator, this can be formed by a plurality of evaporator blocks.
  • the storage chamber and the evaporator chamber are generally housed in a common housing.
  • the storage chamber can here adjoin a door of the housing, while the evaporator chamber is adjacent to a door opposite the rear wall of the housing.
  • the passage is then typically in a partition wall parallel to the rear wall between the evaporator and storage chamber.
  • Air ducts needed in addition to the passage to form a closed air circuit between the storage and evaporator chambers may extend on sidewalls of the housing from a front end facing the door to the evaporator chamber to extend in the storage chamber substantially in the depth direction Storage chamber evenly flushing air flow to produce and ensure sufficient cooling in the storage compartment, especially near the door.
  • such a construction allows uniform cooling of an extraction box located between the side walls and their air ducts, whether by passing the air between the front ends of the air ducts and the passage at the rear of the storage chamber through the drawer itself or between side walls of the drawer and the side walls of the housing each having a gap is provided in which the air between said front ends of the air ducts and the passage can circulate.
  • an inner liner may be inserted into the housing, the passage being formed in a rear panel of the inner liner extending between the chambers, and the inner panel further comprising side walls extending between the air channels and the storage compartment ,
  • Fig. 1 shows a perspective view of an evaporator 1, which can be used in a refrigerator according to the present invention.
  • the evaporator 1 comprises a plurality of arcuate refrigerant lines 2, of which in each case several run side by side in a piece of multi-chamber tube, in particular a microchannel tube 3 made of aluminum.
  • the axis of curvature 4 is the same for all curved refrigerant lines 2 and microchannel tubes 3 and is perpendicular to the broad sides of the microchannel tubes 3.
  • the microchannel tubes 3 are offset in the direction of the axis of curvature 4 against each other and connected to each other in one piece via bows 5, the each centered on a radially extending to the axis of curvature 4 axis 6.
  • microchannel tubes 3 At two free ends of the microchannel tubes 3 elongate distributor 7 are soldered in the radial direction, which connect in parallel in the microchannel pipes 3 adjacent refrigerant pipes 2 and supply with refrigerant.
  • the tubes 3 are also interconnected by lamellae 8, which extend in the direction of the axis of curvature 4 and radially thereto and which each have two opposing, extending in the radial direction edges 9, which are soldered to the broad sides of the microchannel tubes 3 ,
  • the fins 8 are typically made of aluminum, like the tubes 3; they can be provided at least at their edges 9 with a solder layer which melts lower than the aluminum, so that the soldering can be done by the finished molded microchannel tubes 3 together with the placed between them lamellae 8 in an oven to the melting temperature of Lots are heated.
  • Fig. 2 shows possible cross sections of the microchannel tubes 3.
  • numerous refrigerant lines 2 of the same, compact cross section can extend side by side along the microchannel tube 3.
  • Fig. 3 shows a partial section through the housing of a refrigerator according to the invention along a vertically and in the width direction of the housing through the evaporator chamber 11 extending, in Fig. 4 Level III-III.
  • the housing comprises an inner container 12 which houses the evaporator chamber 11 and a storage chamber 13 (see FIG. Fig. 4 ), and a surrounding the inner container 12 insulating layer 14.
  • the evaporator 1 can be seen in the evaporator chamber 11 in plan view. Behind the evaporator 1 extends parallel to the cutting plane, a rear wall plate 15 between the evaporator chamber 11 and the storage chamber 13. From the rear wall plate 15 jump two L-shaped ribs 16 through the cutting plane of the Fig. 3 through to a rear wall 17 (s. Fig.
  • the ribs 16 have horizontal legs 18 which extend up to side walls 19 of the housing or the inner container 12. Above the legs 18 and the rear wall plate 15 extends to the side walls 19, below the legs 18 between the rear wall plate 15 and the side walls 19 each have a passage 20 is kept free.
  • Vertical legs 26 of the ribs 16 may be connected to each other by a rib which extends from an upper edge of the rear wall plate 15 and extends to the rear wall 17 of the housing to close the evaporator chamber 11 upwards.
  • the evaporator chamber 11 is closed at the top by a rear edge region of adegutabstellers 27 which divides the storage chamber 13 into an upper and a lower compartment 28, 29.
  • a circular passage 21 is formed centrally.
  • an axial fan 22 is mounted in the passage 21, an axial fan 22 is mounted.
  • the running direction of the axial fan 22 is chosen here so that it sucks air through the passages 20 and blows out via the passage 21 into the storage chamber 14. The sucked air thus flows from the passages 20 coming from both sides of the evaporator 1, is of its (in Fig. 3 indicated by dashed lines) fins 8 upwards in the direction of the axial fan 22 and the passage 21 and deflected by the axial fan 22 through the passage 21 back into the lower compartment 29 of the storage chamber thirteenth
  • the axis of curvature 4 of the microchannel tubes 2 coincides with an axis of rotation 23 of the fan 22.
  • the lateral edge regions 24 of the evaporator 1 are better for the coming of the passages 20 air flow and less change in the direction of flow than a central region 25 of the evaporator 1.
  • the axis of curvature 4 may be positioned above the axis of rotation 23.
  • the central region 25 of the evaporator 1 is closer to the fan axis 23 than the lateral edge regions 24, it is exposed to a stronger suction of the fan 22, so that the air flow rate per free cross-sectional area in the central region 25 at the edge regions 24 can be adjusted ,
  • the fins 8 are in Fig. 3 aligned exactly radially to the axis of rotation 23 and the axis of curvature 4, ie straight lines that extend the fins 8, crossing each other on the axes 4, 23. If axis of rotation 23 and axis of curvature 4 as described above do not coincide, the fins 8 are preferably radially to the axis of curvature 4 oriented.
  • a recess 30 in the bottom of the evaporator chamber is provided to collect condensate, which runs in a defrost of the evaporator 1 of this. Via a passage 31, which extends from the lowest point of the recess 30 through the insulating layer 14, the condensation reaches the outside of the evaporator chamber 11, preferably in an evaporation tray in an under the evaporator chamber 11 recessed in the housing engine room 32nd
  • Fig. 4 shows a section in the depth direction of the housing, along the fan axis 23, through the storage chamber 13 and the evaporator chamber 11.
  • the axial fan 22 is housed in a short pipe socket 33 which protrudes from the passage 21 into the storage chamber 13 inside.
  • a radial fan could be arranged at the passage 21 in the evaporator chamber 11, which sucks through the passage 20 and the sucked air in the radial direction, through the evaporator 1, thrown out.
  • hollow side cheeks 34 extend forward along the side walls 19 of the housing to near an open front side 35 of the housing, normally closed by a door during operation.
  • the side cheeks 34 may be injection molded as an interior trim integral with the back panel 15 or joined to the back panel 15 to form an interior trim assembly that is inserted into the interior vessel 12 from the front side 35 during assembly of the refrigeration apparatus.
  • the side cheeks 34 When retracted, the side cheeks 34, together with the adjacent side walls 19 of the housing, respectively define an air passage 36 which extends from an inlet 37 at the front end to the passages 20 of the rear wall panel 11.
  • the heat flow from the environment to the storage chamber 13 is generally particularly strong, since here usually only a magnetic seal the storage chamber 13 isolated from the environment. Air which has been heated at the magnetic seal can be sucked off via the air ducts 36 and cooled as it passes through the evaporator 1; Thus, a spread of the heat penetrating via the magnetic seal in the storage chamber 13 can be prevented and a temperature gradient between a warm area close to the door and a cold area of the storage chamber 13 near the rear can be limited.
  • the inlets 37 may each be as in Fig. 4 shown to be provided with a grid to prevent the ingress of foreign bodies in the air channels 31.
  • Fig. 5 shows a section through the housing of the refrigerator along a parallel to the plane III-III, in Fig. 4 level labeled VV.
  • VV the plane of the refrigerator
  • the air ducts 36 which extend on both side walls 19 of the housing and the side cheeks 34 which separate the air ducts 36 from the storage chamber 13.
  • the microchannel tubes 3 of the evaporator 1 should be as wide as possible in order to encompass the air flowing through the evaporator over as long a path as possible and to cool it;
  • the flexibility of the microchannel tubes 3 around the curvature axis 4 perpendicular to their broad sides is lower, the wider they are.
  • To prevent an excessive curvature of the microchannel tubes 3 leads to problems in the production of the evaporator 1 and at the same time a sufficient
  • both evaporators 1, 1 In order to ensure a uniform flow through both evaporators 1, 1 'over their entire passage cross-section, both should span the same angle ⁇ with respect to the axis of curvature 4. As in the case of Fig. 3 this angle ⁇ measures between 90 ° and 180 °.
  • the individual microchannel tubes 2 'of the outer evaporator 1' are longer than the tubes 2 of the inner evaporator 1, they therefore provide space for a larger number of fins 8 than the tubes 2.
  • the tubes 2, 2 'measured distance between the fins 8 in both evaporators 1, 1' is chosen equal, a high efficiency of heat exchange in the outer evaporator 1 'can be ensured while affecting the air flow in the inner evaporator is avoided by a too small distance between the near-axis ends of the fins 8.
  • evaporators 1, 1 ' are also connected in series with respect to the flow of the refrigerant;
  • a pipe section 38 extends radially between two distributors 7, 7 'of the evaporator 1, 1'.
  • An injection point is formed on the other manifold 7 of the inner evaporator 1, here by opening a capillary 39 into the manifold 7, so that refrigerant and air flow through the two evaporators 1, 1 'in opposite directions.
  • Refrigerant lines 2 "of an evaporator 1" are formed by a cylindrical tube which extends in an arc around the axis of curvature 4 and the axis of rotation 23 of the fan 22.
  • the refrigerant lines 2 are here connected in series via an arc 5" and extend with different radii about the axis 4. Further arcuate Refrigerant lines can be arranged offset from one another along the axis 4.
  • Each refrigerant line 2 is associated with a strip-shaped lamella 8", which is soldered at one of its longitudinal edges to the refrigerant line 2 "and projects radially all around from the refrigerant line 2".

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP18194700.3A 2017-09-25 2018-09-17 Appareil frigorifique avec chambre de stockage et chambre d'évaporateur Withdrawn EP3460365A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017216943.5A DE102017216943A1 (de) 2017-09-25 2017-09-25 Kältegerät mit Lagerkammer und Verdampferkammer

Publications (1)

Publication Number Publication Date
EP3460365A1 true EP3460365A1 (fr) 2019-03-27

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ID=63637677

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Application Number Title Priority Date Filing Date
EP18194700.3A Withdrawn EP3460365A1 (fr) 2017-09-25 2018-09-17 Appareil frigorifique avec chambre de stockage et chambre d'évaporateur

Country Status (3)

Country Link
EP (1) EP3460365A1 (fr)
CN (1) CN109556339B (fr)
DE (1) DE102017216943A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3736515A1 (fr) * 2019-05-07 2020-11-11 Carrier Corporation Armoire d'affichage réfrigérée comprenant des échangeurs de chaleur à microcanaux

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112984895B (zh) * 2019-12-17 2022-11-25 合肥华凌股份有限公司 圆形制冷设备

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2083547A1 (fr) * 1970-03-24 1971-12-17 Schmole Metallwerke Echangeur de chaleur pour liquides et gaz
JPS52131242A (en) * 1976-04-28 1977-11-04 Hitachi Ltd Heat exchanger
JPH0552682U (ja) * 1991-12-05 1993-07-13 ダイキン工業株式会社 冷凍冷蔵装置
JP2001304774A (ja) * 2000-04-18 2001-10-31 Daikin Ind Ltd 熱交換器及び該熱交換器を備えた空気調和機
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