EP4332476A1 - Appareil frigorifique et ensemble échangeur thermique pour un appareil frigorifique - Google Patents

Appareil frigorifique et ensemble échangeur thermique pour un appareil frigorifique Download PDF

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Publication number
EP4332476A1
EP4332476A1 EP23185319.3A EP23185319A EP4332476A1 EP 4332476 A1 EP4332476 A1 EP 4332476A1 EP 23185319 A EP23185319 A EP 23185319A EP 4332476 A1 EP4332476 A1 EP 4332476A1
Authority
EP
European Patent Office
Prior art keywords
opening
blow
machine room
air duct
fan
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
EP23185319.3A
Other languages
German (de)
English (en)
Inventor
Robert Stahl
Michael Vogel
Alexander Ruppert
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 EP4332476A1 publication Critical patent/EP4332476A1/fr
Pending 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
    • F25D23/00—General constructional features
    • F25D23/003—General constructional features for cooling refrigerating machinery
    • 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
    • F25B39/04—Condensers
    • 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
    • F25D2323/00—General constructional features not provided for in other groups of this subclass
    • F25D2323/002—Details for cooling refrigerating machinery
    • F25D2323/0021—Details for cooling refrigerating machinery using air guides
    • 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
    • F25D2323/00—General constructional features not provided for in other groups of this subclass
    • F25D2323/002—Details for cooling refrigerating machinery
    • F25D2323/0027—Details for cooling refrigerating machinery characterised by the out-flowing air
    • F25D2323/00271—Details for cooling refrigerating machinery characterised by the out-flowing air from the back bottom
    • 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
    • F25D2323/00—General constructional features not provided for in other groups of this subclass
    • F25D2323/002—Details for cooling refrigerating machinery
    • F25D2323/0028—Details for cooling refrigerating machinery characterised by the fans
    • F25D2323/00282—Details for cooling refrigerating machinery characterised by the fans the fans not of the axial type

Definitions

  • the present invention relates to a refrigeration appliance, in particular a household refrigeration appliance such as a refrigerator, a freezer or a freezer or a fridge-freezer combination, and a heat exchanger assembly for a refrigeration appliance.
  • a refrigeration appliance in particular a household refrigeration appliance such as a refrigerator, a freezer or a freezer or a fridge-freezer combination, and a heat exchanger assembly for a refrigeration appliance.
  • a storage compartment for holding refrigerated goods is dimensioned as large as possible in relation to the space required by the device that cannot be used as a storage space. It is therefore advantageous if the components of a refrigerant circuit can be accommodated in a machine room to save as much space as possible. It is also desirable that the refrigerant circuit works as energy-efficiently as possible.
  • US 2019/0011172 A1 describes a built-in refrigerator in which a condenser and a refrigerant compressor of a refrigerant circuit are arranged in a machine room.
  • An axial fan is arranged in the engine room between the condenser and the compressor, with a pressure side of the fan facing the compressor and a suction side of the fan facing the condenser. The fan draws in ambient air through the condenser and directs the air heated at the condenser through a duct to the compressor in order to cool it.
  • the EP 2 743 618 A1 discloses a built-in refrigeration device in which a condenser is arranged on a rear wall of the refrigeration device. There is also a radial fan in a machine room of the refrigerator. The radial fan sucks in air from the machine room and blows it into an air duct, which directs the air along the rear wall over the condenser.
  • a heat exchanger assembly for a refrigeration appliance in particular for a household refrigeration appliance, comprises a compact condenser for releasing heat to the environment, a fan for promoting an air flow over the condenser and an air duct which extends between the fan and the compact condenser , wherein the fan is positioned in the air duct in the area of a suction opening of the air duct and the compact condenser is positioned in the air duct in the area of an exhaust opening of the air duct on a pressure side of the fan.
  • a refrigeration device in particular a household refrigeration device such as a refrigerator, a freezer or a chest freezer or a refrigerator-freezer combination, comprises a storage compartment for receiving refrigerated goods, a machine room separate from the storage compartment and a refrigerant circuit for absorbing heat from the storage compartment and for dissipating heat to the environment, the refrigerant circuit having a heat exchanger assembly according to the first aspect of the invention, which is arranged in the engine room.
  • MCHE compact condenser
  • the air guide duct defines an interior or flow space and has a first opening or suction opening and a second opening or exhaust opening.
  • the fan is arranged in the area of the suction opening in the interior of the air duct in such a way that a suction side of the fan faces the suction opening and a pressure side of the fan faces the exhaust opening.
  • the compact condenser is arranged in the area of the suction opening in the interior of the air duct, so that the fan sucks in air through the suction opening and blows it through convection channels of the compact condenser and ejects it at the outlet opening.
  • the fan thus blows air into the air duct, in particular into a space between the compact condenser and the fan.
  • the compact condenser represents a flow resistance. Since the compact condenser is arranged on the pressure side of the fan, it acts as a bluff body, so to speak. In particular, it was found that the arrangement of the compact condenser according to the invention on the pressure side of the fan forms a pressure space between the fan and the compact condenser in the air duct. In this pressure chamber, there is a homogeneous distribution of flow velocities across the cross-sectional area of the air duct, which is occupied by the compact condenser. This means that there are only small differences in flow velocities across the cross-sectional area.
  • the flow through the compact condenser is essentially uniform over its entire surface, which improves heat dissipation from the compact condenser. This is beneficial for the energy efficiency of the refrigerant circuit. Furthermore, for a given thermal output, the compact condenser can be made smaller and therefore more space-saving. Another advantage is that pressure losses are reduced due to the homogeneous speed distribution.
  • the blow-out opening of the air duct is longitudinal, in particular rectangular, and a flow cross section of the air duct widens from the suction opening towards the blow-out opening.
  • An elongated design of the blow-out opening and the condenser positioned therein offers the advantage that, for a given cross-sectional area of the blow-out opening, a relatively narrow opening is realized, so that an end region of the air duct, in which the blow-out opening and the compact condenser are located, is space-saving in the machine room of a refrigeration appliance can be positioned.
  • the suction opening of the air duct is circular.
  • the air guide duct can have a circular cross section in the area of the suction opening.
  • the fan is designed as a radial fan.
  • Radial fans offer the advantage that they are stable against pressure fluctuations and can efficiently promote high mass flows, even against a certain back pressure on the pressure side. This means that a pressure chamber can be built up more efficiently in front of the compact condenser in relation to the flow direction, which further promotes the uniform flow through the condenser.
  • an advantage of using a radial fan is that it is designed to suck in air along a first axis and to expel air along a second axis that extends transversely to the first axis. This means that the space available in the machine room of a refrigeration device can be used flexibly.
  • the compact condenser has a plurality of parallel plates, in each of which a plurality of channels for the passage of refrigerant is formed, and a plurality of fins, which are arranged between the plates and in thermally conductive contact with the Plates stand, the slats and the plates extend parallel to a central axis of the exhaust opening.
  • the plates and fins together define convection channels of the compact condenser, through which the air conveyed by the fan passes can flow. Since the slats and the plates extend parallel to a central axis of the blow-out opening, the pressure loss in the air flow is further reduced.
  • the machine room has a floor, a ceiling wall opposite the floor and side walls extending between the floor and the ceiling wall, the floor, the ceiling wall and the side walls delimiting a rear opening and the blow-out opening of the air duct in the area of Rear opening is arranged.
  • the ceiling wall and the floor can extend in particular transversely to a rear wall of the refrigeration device, which delimits the storage compartment, for example in relation to a depth direction.
  • the machine room can advantageously be open, i.e. limited only by the floor, the side walls and the ceiling.
  • the rear opening can optionally be partially covered by a cover, which leaves the area of the blow-out opening of the air duct open.
  • the blow-out opening of the air duct is located in the rear area.
  • the blow-out opening of the air duct can be located in the rear opening of the machine room in order to blow out air along the rear wall of the refrigeration device.
  • a central axis of the blow-out opening is aligned transversely to the ceiling wall of the machine room, so that air can be blown out along a rear wall of the refrigeration device.
  • the central axis of the blow-out opening can be aligned parallel to the rear wall of the refrigeration appliance or can generally form an angle with it in a range between 0 degrees and 30 degrees, in particular between 0 degrees and 15 degrees.
  • the central axis of the blow-out opening with the ceiling wall of the machine room can enclose an angle in a range between 90 degrees and 60 degrees, in particular in a range between 90 degrees and 75 degrees. This allows the air to be blown out along the rear wall of the refrigerator.
  • the rear wall typically faces a wall, for example a building wall or a wall of an installation niche, so that a gap is formed between the rear wall and the wall in which the air can flow.
  • the air flow along the rear wall prevents the formation of condensate on the rear wall as the air heats up at the compact condenser.
  • the compact condenser has a plurality of parallel plates, in each of which a plurality of channels for the passage of refrigerant is formed, and a plurality of fins, which are arranged between the plates and in thermally conductive contact with the Plates stand, the slats and the plates extend parallel to a central axis of the exhaust opening, and the plates and slats extend transversely to the ceiling wall.
  • the plates and slats thus extend parallel or essentially parallel to the direction of gravity when the refrigeration device is placed on a base, e.g. a floor or the floor of a built-in niche, so that the floor of the machine room faces the base. This promotes natural convection on the compact condenser, which further improves heat dissipation on the compact condenser.
  • the blow-out opening of the air duct is positioned in the area of the ceiling wall of the machine room. Accordingly, an end region of the air duct, in which the blow-out opening and the compact condenser are arranged, is arranged in the region of a rear, upper region of the machine room, i.e. in an area in which the ceiling wall and the rear wall merge into one another at the rear opening of the machine room.
  • This area advantageously offers sufficient space to accommodate the compact condenser.
  • the compact condenser can be made relatively small, so that a further space advantage is achieved.
  • the arrangement of the blow-out opening in this area facilitates the outflow along the rear wall. Another advantage is that this area is easily accessible through the rear opening. This means that the heat exchanger assembly can be easily installed in the machine room. At the same time, cleaning the compact condenser is made easier.
  • a recess is formed in which the blow-out opening of the air duct is located.
  • the transition region connects essentially flat surface sections of an outer surface of the rear wall and a surface of the ceiling wall of the machine room, with the transition region forming a recess in relation to the outer surface of the rear wall.
  • the air duct protrudes from the engine room into this recess. This means that the heat exchanger assembly as a whole can be positioned even closer to the ceiling wall, which saves further space in the machine room. Regardless of this, the flow along the rear wall is further facilitated.
  • the recess forms an opening on an outer surface of the rear wall, the outer surface of the rear wall and a surface of the ceiling wall of the machine room being connected by a transition surface running obliquely to the outer surface of the rear wall and to the surface of the ceiling wall.
  • the transition surface forms the connection between the essentially flat surface sections of the outer surface of the rear wall and the surface of the ceiling wall of the machine room.
  • the transition surface can, for example, be curved, in particular convexly curved, or flat.
  • the recess is formed in an insulating layer of the rear wall.
  • the recess can therefore be easily produced by locally reducing the thickness of the insulation layer. In the area of the transition from the engine room ceiling to the rear wall, which extend transversely to each other, there is already an excess of insulation material due to the corner formed there. The recess therefore does not significantly affect the insulating effect of the insulation layer. At the same time, insulation material is saved and the functional integration of the refrigeration device is improved.
  • the blow-out opening extends longitudinally in a direction transverse to the side walls of the machine room.
  • the blow-out opening can have a circumference in the form of a rectangle, with a long side of a rectangle extending in the direction from side wall to side wall. This means that the width of the refrigeration device can be used advantageously for blowing out the air.
  • the blow-out opening extends over at least 30 percent, in particular at least 50 percent, in particular preferably over at least 80 percent of a distance between the side walls of the machine room. In this way, a large part of the available width of the rear wall can advantageously be used for flow guidance.
  • Fig. 1 shows an example of a refrigeration device 200 in the form of a refrigerator.
  • the refrigeration device 200 can be a household refrigeration device, such as a refrigerator, a refrigerator-freezer combination or a freezer.
  • the refrigeration device 200 has a storage compartment 1, a machine room 2, a refrigerant circuit 3 and a heat exchanger assembly 100.
  • the storage compartment 1 is designed to hold refrigerated goods, such as food, drinks, medication or the like, and is characterized by a floor 204, a ceiling wall 206 arranged opposite the floor 204, and opposite side walls 205, which are located between the floor 204 and the ceiling wall 206 extend and delimit a rear wall 202, which extends between the floor 204 and the top wall 206 and between the side walls 205.
  • the floor 204, the ceiling 206, the side walls 205 and the rear wall 202 can, for example, be formed in one piece as parts of an inner container 203.
  • the inner container 203 can be designed, for example, as a plastic part, for example as a plastic injection-molded part, or as a metal part. As in Fig.
  • the inner container 203 can be surrounded, in particular encapsulated, by an insulating layer 208 along the walls 202, 204, 205, 206.
  • the storage compartment 1 has an opening 1A, which is delimited by the floor 204, the side walls 205 and the ceiling 206.
  • the machine room 2 is defined as a separate room from the storage compartment 1 and can, as in Fig. 1 shown as an example, adjoin the bottom 204 of the storage compartment 1.
  • the machine room 2 can be delimited by a floor 21 and a ceiling wall 22 opposite it, as well as by opposing side walls 23 which extend between the floor 21 and the ceiling wall 22.
  • the ceiling wall 22 of the machine room 2 can be formed, for example, by the floor 204 of the storage compartment 1, as in Fig. 1 shown as an example.
  • a front cover 24 can be provided, which further delimits the machine room 2, with the front cover 24 extending between the floor 21 and the ceiling wall 22 and between the side walls 23.
  • the front cover 24 may in particular have an inlet opening 24A, as in Fig. 1 shown schematically.
  • the inlet opening 24A allows air to be exchanged between the engine room 2 and the surroundings.
  • the front cover 24 is arranged at an end of the machine room 2 located opposite the rear wall 202.
  • the inlet opening 24A can alternatively also be formed in one of the side walls 23 of the engine room 2.
  • the machine room 2 can be open, with the side walls 23, the top wall 22 and the floor 21 together defining a rear opening 25.
  • part of the rear opening 25 can also be covered by a cover (not shown).
  • the refrigerant circuit 3 includes an evaporator 31, a condenser 32 and a compressor 33 as well as a throttle (not shown).
  • the compressor 33 is designed to circulate refrigerant, with a suction port of the compressor 33 being connected to an outlet of the evaporator 31 and a pressure port of the compressor 33 being connected to an inlet of the condenser 32.
  • An outlet of the condenser 32 is connected to an inlet of the evaporator 31, the throttle point being located between the outlet of the condenser 32 and an inlet of the evaporator 31.
  • the evaporator 31 is thermally coupled to the storage compartment 1 and liquid refrigerant evaporates in the evaporator 31 while absorbing heat from the storage compartment 1.
  • the compressor 33 sucks in the evaporated refrigerant and conveys it at increased pressure to the condenser 32, where the refrigerant is released Heat condenses into the surroundings.
  • the refrigerant is expanded at the throttle point.
  • the refrigerant circuit 3 is thus designed to dissipate heat from the storage compartment 1 and to release heat to the environment.
  • the condenser 32 is part of a heat exchanger assembly 100 arranged in the machine room 2, which additionally has a fan 4 and an air duct 5.
  • Fig. 1 shows schematically the basic structure of the heat exchanger assembly 100.
  • Figs. 2 to 8 Various heat exchanger assemblies 100 are shown in detail, with the Figs. 3 to 8 additionally show the arrangement of the respective heat exchanger assembly 100 in the engine room 2.
  • the fan 4 is rotatable about an axis of rotation A4, for example by means of a motor (not shown), in order to promote an air flow.
  • the fan 4 has a suction connection or a suction side SS for sucking in air along the axis of rotation A4 and a pressure connection or a pressure side PS for ejecting air.
  • the fan 4 can be designed as a radial fan, which is designed to expel air in a direction transverse to the axis of rotation A4.
  • the fans 4 shown are also implemented as radial fans.
  • the condenser 32 is implemented as a compact condenser, for example as a so-called MCHE condenser.
  • the compact condenser 32 can have a plurality of parallel plates 35, in each of which a plurality of channels (not shown) are formed for the passage of refrigerant, and a plurality of fins 34, which are arranged between the plates 35 and in thermal conductive contact with the plates 35.
  • the plates 35 and the slats 34 together delimit convection channels 36 through which air can flow through the compact condenser 32.
  • the compact condenser 32 may, for example, have a substantially rectangular shape.
  • the plates 35 extend parallel to a long side of the rectangle, the slats 34 extend transversely to the plates 35, in particular between the plates 35.
  • the air guide duct 5 defines an interior 50 and has a suction opening 51 and a blow-out opening 52.
  • the suction opening 51 can be circular, for example.
  • the exhaust opening 52 can, for example, have a circumference in the form of a rectangle.
  • the long side of the rectangle can be significantly longer than the short side of the rectangle, for example the length ratio of the long side to the short side can be greater than or equal to 5:1.
  • the blow-out opening 52 can be longitudinal.
  • a central axis M51 of the suction opening 51 can extend transversely or perpendicular to a central axis M52 of the exhaust opening 52.
  • the invention is not limited to this.
  • the central axes M51, M52 of the suction opening 51 and the exhaust opening 52 can also be parallel to one another, as in Fig. 7 shown, or angled, for example at an angle between 5 degrees and 30 degrees to each other.
  • a flow cross section of the air guide duct 5 can widen from the intake opening 51 to the exhaust opening 52.
  • the fan 4 and the condenser 32 are each arranged in the interior 50 of the air duct.
  • the fan 4 is arranged in the area of the intake opening 51, in particular immediately adjacent to the intake opening 51, and the condenser 32 is arranged in the area of the outlet opening 52, for example in the outlet opening 52.
  • the axis of rotation A4 of the fan 4 can be coaxial with the central axis M51 of the suction opening 51, as in Fig. 2 shown as an example.
  • the suction side SS of the fan 4 faces the suction opening 51 and the pressure side PS of the fan 4 faces the interior 50 of the air duct 5.
  • the compact condenser 32 is therefore positioned on the pressure side PS of the fan 4.
  • the fan 4 can thus suck in air from the machine room 2 through the suction opening 51, transport it through the interior 50 to the compact condenser 32 and through its convection channels 36 and expel it through the exhaust opening 52.
  • the slats 34 and the plates 35 can extend parallel to the central axis M52 of the exhaust opening 52.
  • At least one deflector plate (not shown) can be provided in the interior 50 of the air duct 5, which extends at least partially curved around the axis of rotation A4 of the fan 4 on the pressure side PS of the fan 4.
  • the central axis M51 of the suction opening 51 extends transversely or perpendicular to the central axis M52 of the exhaust opening 52.
  • the axis of rotation A4 of the fan 4 extends transversely to the central axis M52 of the exhaust opening 52.
  • the fan 4 can also be positioned with respect to the central axis M51 of the inlet opening 51 so that it is arranged overlapping the exhaust opening 52.
  • Figs. 3 and 4 show schematic sectional views of a refrigeration device 200, in the machine room 2 of which the in Fig. 2 heat exchanger assembly 100 shown is arranged.
  • Fig. 5 shows a view of the back of the refrigerator 200 from the Figs. 3 and 4 .
  • the heat exchanger assembly 100 can be positioned overall in the area of the rear opening 25 of the machine room 2.
  • at least the blow-out opening 52 of the air duct 5 can be arranged in the area of the rear opening 25.
  • the blow-out opening 52 preferably extends longitudinally in a direction transverse to the side walls 23 of the machine room 2, i.e. parallel or essentially parallel to the rear wall 202 or along the width of the rear wall 202 of the refrigeration appliance 200, as in particular in Fig. 5 shown.
  • the blow-out opening 52 extends essentially over the entire distance d23 between the side walls 23 of the machine room.
  • the blow-out opening 52 can have a length w52 which extends over at least 30 percent, in particular at least 50 percent, in particular preferably over at least 80 percent of a distance d23 of the side walls 23. Regardless of the length w52 in relation to the distance d23 of the side walls 23, the central axis M52 of the blow-out opening 52 can extend transversely to the ceiling wall 52.
  • the central axis M52 of the exhaust opening 52 can extend parallel to the rear wall 202, as shown in FIGS Figs. 2 to 5 is shown purely as an example.
  • the air can be blown out along the rear wall 202 of the refrigerator 200, as shown in FIG Fig. 5 is symbolically represented by the arrows P1.
  • the plates 35 and fins 34 of the condenser 32 preferably also extend transversely to the ceiling wall 22. If the refrigerator 200 is set up so that the rear wall 202 is aligned along the direction of gravity G, the plates 35 and slats 34 also essentially parallel to the direction of gravity G. This advantageously promotes natural convection on the compact condenser 32.
  • the blow-out opening 52 can be arranged in the area of the ceiling 22 of the machine room 2. Accordingly, the suction opening 51 can be located closer to the floor 21 of the machine room 2 than the exhaust opening 52.
  • a recess 207 is formed in a transition area between the ceiling wall 22 of the machine room 2 and the rear wall 202 of the refrigeration device 200.
  • the recess 207 can extend from a side wall 23 to the opposite side wall 23 of the machine room 2.
  • the recess 207 forms an opening or depression on an outer surface 202a of the rear wall 202, which is oriented away from the storage compartment 1, as in Fig. 5 is clearly visible.
  • Fig. 5 Like in particular Fig.
  • the transition area between the ceiling wall 22 of the machine room 2 and the rear wall 202 is formed by a transition or connecting surface 222a, which has a substantially flat surface section of a surface 22a of the ceiling wall 22 facing the machine room 2 with a substantially flat surface section of the outer surface 202a the rear wall 202 connects.
  • the transition surface 222a runs obliquely to the outer surface 202a and to the surface 22a.
  • the transition surface 222a can, for example, be convexly curved or at least have a curved region.
  • the recess 207 can be formed, for example, in the insulation layer 208 or in the insulation material forming the insulation layer 208. As in Fig.
  • the blow-out opening 52 of the air duct 5 is therefore located in the recess 207.
  • FIG. 6 is a sectional view of another refrigerator 200 with a heat exchanger assembly 100 shown, which according to Fig. 2 is trained.
  • Refrigeration device 200 shown is the heat exchanger assembly 100 in the in Fig. 6 shown refrigeration device 200 arranged so that the central axis M51 of the suction opening 51 and the central axis M52 of the exhaust opening 52 each extend inclined to the ceiling wall 22.
  • the air in the recess 207 can be blown out of the blow-out opening 52 at a reduced angle, optionally essentially tangentially to the transition surface 222a.
  • the central axes M51, M52 of the suction opening 51 and the blow-out opening 52 are angled, for example at an angle between 5 degrees and 30 degrees, to each other, with the central axis M52 of the blow-out opening 52 as in Fig. 6 shown runs and the central axis M51 of the suction opening 51 extends parallel to the ceiling wall 22.
  • FIG. 7 is a sectional view of another refrigerator 200 with a heat exchanger assembly 100 shown.
  • Heat exchanger assembly 100 shown differs from that in Fig. 2 heat exchanger assembly 100 shown in that the central axes M51, M52 of the suction opening 51 and the exhaust opening 52 extend parallel to one another. With respect to a direction perpendicular to the central axes M51, M52, the suction opening 51 and the exhaust opening 52 are located next to each other, that is, the central axes M51, M52 of the suction opening 51 and the exhaust opening 52 are spaced apart from one another.
  • the axis of rotation A4 of the fan 4 is coaxial with the central axis M51 of the intake opening 51.
  • Fig. 7 Heat exchanger assembly 100 shown differs from that in Fig. 2 heat exchanger assembly 100 shown in that the central axes M51, M52 of the suction opening 51 and the exhaust opening 52 extend parallel to one another. With respect to a direction perpendicular to the central axes M51, M52
  • the central axis M51 of the suction opening 51 and thus also the axis of rotation A4 of the fan 4 extends transversely to the ceiling wall 22.
  • a very space-saving arrangement of the heat exchanger assembly 100 can be achieved by positioning an end region of the air duct 5, in which the suction opening 51 and the fan 4 are located, in the area of the ceiling wall 22 of the machine room 2.
  • the suction opening 51 faces the floor 21 of the machine room 2.
  • FIG. 8 is a sectional view of another refrigerator 200 with a heat exchanger assembly 100 shown.
  • Heat exchanger assembly 100 shown differs from that in Fig. 2 shown heat exchanger assembly 100 in that the central axis M51 of the suction opening 51 runs transversely to the longitudinal extent of the blow-out opening 52, for example to the long side of the rectangular circumference of the blow-out opening 52, but parallel to the longitudinal extent of the blow-out opening 52.
  • Fig. 8 is shown by way of example that the central axis M51 of the suction opening 51 and therefore also the axis of rotation A4 of the fan 4 extend transversely to the side walls 23 of the machine room 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)
  • Other Air-Conditioning Systems (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP23185319.3A 2022-08-29 2023-07-13 Appareil frigorifique et ensemble échangeur thermique pour un appareil frigorifique Pending EP4332476A1 (fr)

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1893941U (de) * 1962-03-28 1964-06-04 Siemens Elektrogeraete Gmbh Kompressorkuehlschrank.
JP2009068754A (ja) * 2007-09-12 2009-04-02 Hitachi Appliances Inc 冷蔵庫
US7950248B2 (en) 2007-09-14 2011-05-31 Samsung Electronics Co., Ltd. Refrigerator having component and storage compartments
EP2743618A1 (fr) 2012-12-17 2014-06-18 Electrolux Home Products Corporation N.V. Réfrigérateur pour aliments
WO2016177803A1 (fr) * 2015-05-07 2016-11-10 Arcelik Anonim Sirketi Dispositif de refroidissement comprenant un condenseur refroidi par un ventilateur
CH713485A2 (de) 2018-07-16 2018-09-28 V Zug Ag Kühlgerät mit aktiv gekühltem Maschinenraum.
US20190011172A1 (en) 2017-03-06 2019-01-10 Whirlpool Corporation Appliance machine compartment airflow system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1893941U (de) * 1962-03-28 1964-06-04 Siemens Elektrogeraete Gmbh Kompressorkuehlschrank.
JP2009068754A (ja) * 2007-09-12 2009-04-02 Hitachi Appliances Inc 冷蔵庫
US7950248B2 (en) 2007-09-14 2011-05-31 Samsung Electronics Co., Ltd. Refrigerator having component and storage compartments
EP2743618A1 (fr) 2012-12-17 2014-06-18 Electrolux Home Products Corporation N.V. Réfrigérateur pour aliments
WO2016177803A1 (fr) * 2015-05-07 2016-11-10 Arcelik Anonim Sirketi Dispositif de refroidissement comprenant un condenseur refroidi par un ventilateur
US20190011172A1 (en) 2017-03-06 2019-01-10 Whirlpool Corporation Appliance machine compartment airflow system
CH713485A2 (de) 2018-07-16 2018-09-28 V Zug Ag Kühlgerät mit aktiv gekühltem Maschinenraum.

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