Refrigeration device

Abstract

A heat exchanger assembly (100) for a refrigeration appliance (200), in particular for a domestic refrigeration appliance, comprises a compact condenser (32) for discharging heat to the environment, a fan (4) for conveying an airflow over the condenser (32) and an air duct (5) extending between the fan (4) and the compact condenser (32), wherein the fan (4) is positioned in the air duct (5) in the region of an intake opening (51) of the air duct (5) and the compact condenser (32) is positioned in the air duct (5) in the region of an exhaust opening (52) of the air duct (5) on a pressure side (PS) of the fan (4).

Description

TECHNICAL FIELD

[0001] The present invention relates to a refrigeration appliance, in particular a household refrigeration appliance such as a refrigerator, a freezer or a freezer chest or a fridge-freezer combination, and a heat exchanger assembly for a refrigeration appliance. STATE OF THE ART

[0002] In household refrigeration appliances such as refrigerators, fridge-freezer combinations, or similar, it is generally desirable that a storage compartment for refrigerated goods be as large as possible relative to the space required by the appliance that is not used for storage. It is therefore advantageous if the components of a refrigerant circuit can be housed in a machine room in the most space-efficient way possible. Furthermore, it is desirable that the refrigerant circuit operate as energy-efficiently as possible.

[0003] 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 machine 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 ambient air through the condenser and directs the air heated by the condenser through a duct to the compressor to cool it.

[0004] US 7 950 248 B2 describes a refrigerator-freezer combination with a condenser arranged horizontally under the floor of a freezer compartment, wherein an axial fan is arranged in a machine room, which sucks in air via the condenser and expels it in the direction of a compressor into the machine room.

[0005] EP 2 743 618 A1 discloses a built-in refrigeration appliance in which a condenser is arranged on a rear wall of the refrigeration appliance. Furthermore, a radial fan is arranged in a machine room of the refrigeration appliance. The radial fan draws air from the machine room and blows it into an air duct, which guides the air along the rear wall over the condenser.

[0006] CH 713 485 A2 describes a refrigeration device in which a condenser is positioned in the machine room and air is sucked in from the machine room via a deflection duct by means of a radial fan. SUMMARY OF THE INVENTION

[0007] It is one of the objects of the present invention to provide improved solutions for heat dissipation at a condenser of a refrigeration device.

[0008] This object is achieved according to the invention by a heat exchanger assembly having the features of claim 1 and by a refrigeration device having the features of claim 6.

[0009] According to a first aspect of the invention, a heat exchanger assembly for a refrigeration appliance, in particular for a household refrigeration appliance, comprises a compact condenser for dissipating heat to the environment, a fan for conveying an air flow over the condenser and an air duct extending between the fan and the compact condenser, wherein the fan is positioned in the air duct in the region of an intake opening of the air duct and the compact condenser is positioned in the air duct in the region of an exhaust opening of the air duct on a pressure side of the fan.

[0010] According to a second aspect of the invention, a refrigeration appliance, in particular a household refrigeration appliance such as a refrigerator, a freezer or a freezer chest or a fridge-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, wherein the refrigerant circuit has a heat exchanger assembly according to the first aspect of the invention, which is arranged in the machine room.

[0011] One idea underlying the invention is to arrange a compact condenser, e.g., a so-called MCHE condenser, on the pressure side of a fan in an air duct. "MCHE" is an abbreviation for "Multi-Channel Heat Exchanger." The air duct defines an interior or flow space and has a first opening, or intake opening, and a second opening, or exhaust opening. The fan is arranged in the region of the intake opening in the interior of the air duct such that a suction side of the fan faces the intake opening and a pressure side of the fan faces the exhaust opening. The compact condenser is arranged in the region of the intake opening in the interior of the air duct such that the fan draws air through the intake opening, blows it through convection channels of the compact condenser, and expels it through the exhaust opening.

[0012] 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 kind of bluff body. In particular, it was found that the inventive arrangement of the compact condenser on the pressure side of the fan creates a pressure chamber between the fan and the compact condenser in the air duct. In this pressure chamber, the flow velocities are distributed homogeneously across the cross-sectional area of ​​the air duct occupied by the compact condenser. This means that there are only slight differences in the flow velocities across the cross-sectional area. Thus, the compact condenser is essentially flowed through evenly over its entire surface, which improves heat dissipation at 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 designed smaller and thus more space-efficiently. Another advantage is that the homogeneous velocity distribution reduces pressure losses.

[0013] Advantageous embodiments and further developments arise from the subclaims which refer back to the independent claims in conjunction with the description.

[0014] According to some embodiments, the outlet opening of the air duct can be designed to be longitudinal, in particular rectangular, and the flow cross-section of the air duct widens from the intake opening to the outlet opening. An elongated design of the outlet opening and the condenser positioned therein offers the advantage that, for a given cross-sectional area of ​​the outlet opening, a relatively narrow opening is realized, so that an end region of the air duct, in which the outlet opening and the compact condenser are located, can be positioned in a space-saving manner in the machine room of a refrigeration appliance.

[0015] According to some embodiments, the intake opening of the air duct can be circular. This allows a large cross-sectional area of ​​the intake opening to be realized in a space-saving manner. Since the fan preferably has blades rotating around a rotational axis, the air duct can have a circular cross-section in the region of the intake opening.

[0016] According to some embodiments, the fan can be designed as a radial fan. Radial fans offer the advantage that they are stable against pressure fluctuations and can efficiently convey high mass flows, even against a certain counterpressure on the pressure side. This allows a pressure chamber to be built up even more efficiently in relation to the flow direction upstream of the compact condenser, which further promotes uniform flow through the condenser. Another advantage of using a radial fan is that it is designed to draw in air along a first axis and expel it along a second axis that extends transversely to the first axis. This allows the space available in the machine room of a refrigeration device to be used flexibly.

[0017] According to some embodiments, the compact condenser may comprise a plurality of parallel plates, each of which contains a plurality of channels for conducting refrigerant, and a plurality of fins arranged between the plates and in thermally conductive contact with the plates. The fins and plates extend parallel to a central axis of the discharge opening. The plates and fins together define convection channels of the compact condenser, through which the air conveyed by the fan can flow. Since the fins and plates extend parallel to a central axis of the discharge opening, the pressure loss during the air flow is further reduced.

[0018] According to some embodiments, it can be provided that the machine compartment has a floor, a ceiling wall opposite the floor, and side walls extending between the floor and the ceiling wall, wherein the floor, the ceiling wall, and the side walls define a rear opening, and the exhaust opening of the air duct is arranged in the region of the rear opening. The ceiling wall and the floor can extend, in particular, transversely to a rear wall of the refrigeration appliance that defines the storage compartment, e.g., in relation to a depth direction. At a rear of the refrigeration appliance defined by the rear wall, the machine compartment can advantageously be open, i.e., defined only by the floor, the side walls, and the ceiling. The rear opening can optionally be partially covered by a cover, which leaves the region of the exhaust opening of the air duct open.The outlet opening of the air duct is located at the rear. For example, the outlet opening of the air duct can be located in the rear opening of the machine room to blow air out along the rear wall of the refrigeration unit.

[0019] According to some embodiments, it can be provided that 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 appliance. For example, the central axis of the blow-out opening can be aligned parallel to the rear wall of the refrigeration appliance or generally form an angle with it in a range between 0 degrees and 30 degrees, in particular between 0 degrees and 15 degrees. Accordingly, the central axis of the blow-out opening can form an angle with the ceiling wall of the machine room in a range between 90 degrees and 60 degrees, in particular in a range between 90 degrees and 75 degrees. The air can thus be blown out along the rear wall of the refrigeration appliance. This reduces the pressure loss of the outflowing air, since there are typically hardly any flow obstructions along the rear wall.For example, the rear wall at an installation location of the refrigeration appliance typically faces a wall, e.g. a building wall or a wall of a built-in niche, so that a gap is formed between the rear wall and the wall in which the air can flow.

[0020] Furthermore, the air flow along the rear wall prevents the formation of condensate on the rear wall, as the air is heated at the compact condenser.

[0021] According to some embodiments, the compact condenser can have a plurality of parallel plates, each of which has a plurality of channels for conducting refrigerant, and a plurality of fins arranged between the plates and in thermally conductive contact with the plates. The fins and plates extend parallel to a central axis of the discharge opening, and the plates and fins extend transversely to the ceiling wall. The plates and fins thus extend parallel or substantially parallel to the direction of gravity when the refrigeration appliance is installed on a base, e.g., a floor or the floor of an installation niche, with the floor of the machine room facing the base. This promotes natural convection at the compact condenser, thereby further improving heat dissipation at the compact condenser.

[0022] According to some embodiments, it can be provided that the outlet opening of the air duct is positioned in the region of the ceiling wall of the machine room. Accordingly, an end region of the air duct, in which the outlet opening and the compact condenser are arranged, is arranged in the region of a rear, upper region of the machine room, i.e. in a region where the ceiling wall and the rear wall merge into one another at the rear opening of the machine room. This region advantageously offers sufficient space for accommodating the compact condenser. In particular, due to the arrangement of the compact condenser on the pressure side of the fan, the compact condenser can be designed to be relatively small, thus achieving a further space advantage. Furthermore, the arrangement of the outlet opening in this region facilitates the outflow along the rear wall.Another advantage is the easy accessibility of this area through the rear opening. This allows the heat exchanger assembly to be easily installed in the machine room. At the same time, cleaning the compact condenser is made easier.

[0023] According to some embodiments, it can be provided that in a transition region between the ceiling wall of the machine room and a rear wall of the refrigeration device extending transversely to the ceiling wall and delimiting the storage compartment, a recess is formed in which the outlet 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, wherein the transition region forms a recess with respect to the outer surface of the rear wall. The air duct projects out of the machine room into this recess. Thus, the heat exchanger assembly as a whole can be positioned even closer to the ceiling wall, which saves further space in the machine room. Independently of this, the outflow along the rear wall is further facilitated.

[0024] According to some embodiments, the recess can form an opening on an outer surface of the rear wall, wherein the outer surface of the rear wall and a surface of the ceiling wall of the machine room are connected by a transition surface extending obliquely to the outer surface of the rear wall and the surface of the ceiling wall. The transition surface forms the connection between the substantially 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.

[0025] According to some embodiments, the recess can be formed in an insulation layer of the rear wall. The recess can thus be easily created by locally reducing the thickness of the insulation layer. In the area of ​​the transition from the machine 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. Thus, the recess does not significantly impair 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.

[0026] According to some embodiments, the exhaust opening can extend longitudinally in a direction transverse to the side walls of the machine room. For example, the exhaust opening can have a rectangular perimeter, with one long side of a rectangle extending from side wall to side wall. Thus, the width of the refrigeration device can be advantageously utilized for air discharge.

[0027] According to some embodiments, the exhaust opening can extend over at least 30 percent, in particular at least 50 percent, and especially preferably over at least 80 percent of the distance between the side walls of the engine room. In this way, a large portion of the available width of the rear wall can advantageously be used for flow guidance.

[0028] The features and advantages disclosed herein in connection with one aspect of the invention are also disclosed for the other aspect and vice versa. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] The invention is explained below with reference to the figures of the drawings. The figures show: Fig. 1 shows a simplified, schematic sectional view of a refrigeration device according to an embodiment of the invention; Fig. 2 shows a perspective view of a heat exchanger assembly according to an embodiment of the invention; Fig. 3 shows a simplified perspective illustration of a sectional view of a refrigeration device according to an embodiment of the invention; and Fig. 4 shows a further sectional view of the Fig. 3 shown refrigeration appliance, wherein a fan of the heat exchanger assembly of the refrigeration appliance is not shown; Fig. 5 a perspective partial view of a rear side of the Fig. 3 and 4shown refrigeration device; Fig. 6 shows a simplified sectional view of a refrigeration device according to a further embodiment of the invention, wherein a fan of the heat exchanger assembly of the refrigeration device is not shown; Fig. 7 shows a simplified sectional view of a refrigeration device according to a further embodiment of the invention; and Fig. 8 shows a simplified sectional view of a refrigeration device according to a further embodiment of the invention.

[0030] In the figures, the same reference symbols denote identical or functionally identical components, unless otherwise stated. DETAILED DESCRIPTION OF EMBODIMENTS

[0031] Fig. 1shows, by way of example, a refrigeration appliance 200 in the form of a refrigerator. The following description refers to this refrigeration appliance 200 by way of example, but the invention is not limited thereto. In general, the refrigeration appliance 200 can be a household refrigeration appliance, such as a refrigerator, a fridge-freezer combination, or a freezer. As shown in Fig. 1 As shown schematically, the refrigeration device 200 comprises a storage compartment 1, a machine room 2, a refrigerant circuit 3 and a heat exchanger assembly 100.

[0032] The storage compartment 1 is designed to accommodate refrigerated goods, such as food, beverages, medicines, or the like, and is defined by a floor 204, a ceiling wall 206 arranged opposite the floor 204, opposing side walls 205 extending between the floor 204 and the ceiling wall 206, and a rear wall 202 extending between the floor 204 and the ceiling wall 206 as well as 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 integrally as parts of an inner container 203. The inner container 203 can, for example, be formed as a plastic part, e.g., as a plastic injection-molded part, or as a metal part. As shown in Fig. 1Further shown, the inner container 203 can be surrounded, in particular overmolded, by an insulating layer 208 along the walls 202, 204, 205, 206. Opposite the rear wall 202, the storage compartment 1 has an opening 1A, which is bounded by the bottom 204, the side walls 205, and the ceiling 206.

[0033] The machine room 2 is defined as a separate room from the storage compartment 1 and can, as in Fig. 1 shown by way of example, adjoin the floor 204 of the storage compartment 1. For example, 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 extending between the floor 21 and the ceiling wall 22. The ceiling wall 22 of the machine room 2 can, for example, be formed by the floor 204 of the storage compartment 1, as in Fig. 1shown as an example. Optionally, a front cover 24 can be provided, which further delimits the machine room 2, wherein the front cover 24 extends between the floor 21 and the ceiling wall 22 as well as between the side walls 23. The front cover 24 can in particular have an inlet opening 24A, as in Fig. 1 shown schematically. The inlet opening 24A enables air exchange between the machine room 2 and the environment. The front cover 24 is arranged at an end of the machine room 2 opposite the rear wall 202. The inlet opening 24A can alternatively also be formed in one of the side walls 23 of the machine room 2. In the region of the rear wall 202, the machine room 2 can be open, with the side walls 23, the ceiling wall 22, and the floor 21 together defining a rear opening 25. Optionally, a part of the rear opening 25 can also be concealed by a cover (not shown).

[0034] The refrigerant circuit 3 comprises an evaporator 31, a condenser 32, a compressor 33, and 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, with 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, absorbing heat from the storage compartment 1. The compressor 33 draws in the evaporated refrigerant and conveys it at increased pressure to the condenser 32, where the refrigerant condenses, releasing heat to the environment. The refrigerant is released at the throttle point.The refrigerant circuit 3 is thus designed to remove heat from the storage compartment 1 and to release heat to the environment.

[0035] 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. In the Fig. 2 to 8 various heat exchanger assemblies 100 are shown in detail, with the Fig. 3 to 8 additionally show the arrangement of the respective heat exchanger assembly 100 in the engine room 2.

[0036] As in Fig. 1 As shown schematically, the fan 4 is rotatable about a rotation axis A4, e.g., by means of a motor (not shown), to promote an air flow. The fan 4 has a suction port or a suction side SS for sucking in air along the rotation axis A4 and a pressure port or a pressure side PS for expelling air. As shown in Fig. 1 As shown schematically, 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 Fig. 2 to 8 The fans 4 shown are also designed as radial fans.

[0037] The condenser 32 is designed as a compact condenser, e.g. as a so-called MCHE condenser. As in Fig. 2 As shown, the compact condenser 32 may comprise a plurality of parallel plates 35, each of which has a plurality of channels (not shown) for the passage of refrigerant, and a plurality of fins 34 arranged between the plates 35 and in thermally conductive contact with the plates 35. The plates 35 and the fins 34 together define convection channels 36 through which air can flow through the compact condenser 32. As shown in Fig. 2As shown by way of example, the compact condenser 32 can, for example, have a substantially rectangular shape. The plates 35 extend parallel to one long side of the rectangle, while the fins 34 extend transversely to the plates 35, in particular between the plates 35.

[0038] The air duct 5 defines an interior space 50 and has an intake opening 51 and an exhaust opening 52. As in Fig. 2 As shown by way of example, the intake opening 51 can be circular, for example. Regardless of the circumferential shape of the intake opening 51, the exhaust opening 52 can, for example, have a rectangular circumference. In particular, 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. In general, the exhaust opening 52 can be elongated.

[0039] As in Fig. 2Further shown by way of example, a central axis M51 of the intake opening 51 can extend transversely or perpendicularly to a central axis M52 of the exhaust opening 52. However, the invention is not limited to this. For example, the central axes M51, M52 of the intake opening 51 and the exhaust opening 52 can also be parallel to each other, as in Fig. 7 shown, or angled, e.g. at an angle between 5 degrees and 30 degrees to each other. As shown in Fig. 1 purely schematically and especially in the Fig. 4 and 6 As can be seen, a flow cross-section of the air duct 5 can widen from the intake opening 51 to the exhaust opening 52.

[0040] The fan 4 and the condenser 32 are each arranged in the interior 50 of the air duct. As in Fig. 1 schematic and Fig. 2As shown in detail by way of example, the fan 4 is arranged in the area of ​​the intake opening 51, in particular directly adjacent to the intake opening 51, and the condenser 32 is arranged in the area of ​​the outlet opening 52, e.g. in the outlet opening 52. Optionally, the rotation axis A4 of the fan 4 can be coaxial to the central axis M51 of the intake opening 51, as in Fig. 2 shown as an example. The suction side SS of the fan 4 faces the intake opening 51 and the pressure side PS of the fan 4 faces the interior 50 of the air duct 5. Thus, the compact condenser 32 is 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 intake 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. As in Fig. 2 to 5As shown, the fins 34 and the plates 35 can extend parallel to the central axis M52 of the outlet opening 52. Due to the arrangement of the compact condenser 32 on the pressure side PS of the fan 4 in the interior space 50 of the air duct 5, a pressure chamber is formed between the fan 4 and the compact condenser 32, in which a relatively homogeneous velocity distribution prevails. This promotes a uniform flow through the compact condenser 32 with low pressure losses. In particular, this reduces the deviation of the mass flows flowing through the individual convection channels 36 of the compact condenser 32. If necessary, at least one deflector plate (not shown) can be provided in the interior space 50 of the air duct 5, which extends on the pressure side PS of the fan 4 at least partially curved around the axis of rotation A4 of the fan 4.

[0041] In the Fig. 2 to 5In the heat exchanger assembly 100 shown as an example, as already explained above, the central axis M51 of the intake opening 51 extends transversely or perpendicularly to the central axis M52 of the exhaust opening 52. In addition, the rotational axis A4 of the fan 4 extends transversely to the central axis M52 of the exhaust opening 52. As in Fig. 2 As shown further, 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 outlet opening 52.

[0042] The Fig. 3 and 4 show schematic sectional views of a refrigeration device 200, in whose machine room 2 the Fig. 2 illustrated heat exchanger assembly 100 is arranged. Fig. 5 shows a view of the rear of the refrigeration unit 200 from the Fig. 3 and 4 .

[0043] As in the Fig. 3 to 5As shown, the heat exchanger assembly 100 can be positioned in the region of the rear opening 25 of the machine room 2. In general, at least the outlet opening 52 of the air duct 5 can be arranged in the region of the rear opening 25. The outlet opening 52 preferably extends longitudinally in a direction transverse to the side walls 23 of the machine room 2, i.e. parallel or substantially parallel to the rear wall 202 or along the width of the rear wall 202 of the refrigeration device 200, as shown in particular in Fig. 5shown. Optionally, it can be provided that the exhaust opening 52 extends substantially over the entire distance d23 between the side walls 23 of the machine room. For example, the exhaust opening 52 can have a length w52 that 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. Independent of the length w52 in relation to the distance d23 of the side walls 23, the central axis M52 of the exhaust opening 52 can extend transversely to the ceiling wall 52. For example, the central axis M52 of the exhaust opening 52 can extend parallel to the rear wall 202, as shown in the Fig. 2 to 5 shown purely as an example. Thus, the air can be blown out along the rear wall 202 of the refrigeration device 200, as shown in Fig. 5symbolically 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 refrigeration appliance 200 is positioned such that the rear wall 202 is aligned along the direction of gravity G, the plates 35 and fins 34 are also substantially parallel to the direction of gravity G. This advantageously promotes natural convection at the compact condenser 32.

[0044] As in the Fig. 3 to 5 As further shown by way of example, the exhaust opening 52 can be arranged in the region of the ceiling 22 of the engine room 2. Accordingly, the intake opening 51 can be located closer to the floor 21 of the engine room 2 than the exhaust opening 52.

[0045] As in the Fig. 3 to 5As shown by way of example, it can be provided that 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. As shown in Fig. 5 As shown by way of example, the recess 207 can extend from one 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. As is particularly the case in Fig. 4As shown, 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 connects 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 of the rear wall 202. The transition surface 222a runs obliquely to the outer surface 202a and to the surface 22a. As in Fig. 4 Shown purely by way of example, the transition surface 222a can, for example, be convexly curved or at least have a curved region. The recess 207 can, for example, be formed in the insulation layer 208 or in the insulation material forming the insulation layer 208. As shown in Fig. 4As can be seen, this does not result in any significant weakening of the insulation layer 208, since, due to the arrangement in the transition region between the top wall 22 and the rear wall 202, only a corner region of the insulation layer 208 is removed. Thus, a substantially constant thickness d208 of the insulation layer 208 is maintained.

[0046] As particularly in the Fig. 4 and 5 As can be seen, an end region of the air duct 5, in which the outlet opening 52 of the air duct 5 is positioned, protrudes into the recess 207. Thus, the outlet opening 52 of the air duct 5 is located in the recess 207. Thus, the heat exchanger assembly 100 as a whole, but in particular the compact condenser 32, can be moved even closer to the ceiling wall 22 of the machine room 2, and the heat exchanger assembly 100 can be accommodated in the machine room 2 in a space-saving manner.

[0047] In Fig. 6is a sectional view of another refrigeration device 200 with a heat exchanger assembly 100, which according to Fig. 2 In contrast to the Fig. 3 to 5 In the refrigeration device 200 shown, the heat exchanger assembly 100 is in the Fig. 6 shown refrigeration device 200 is arranged such that the central axis M51 of the intake opening 51 and the central axis M52 of the exhaust opening 52 each extend at an angle to the ceiling wall 22. As a result, the air in the recess 207 can be blown out of the exhaust opening 52 at a reduced angle, optionally substantially tangential to the transition surface 222a. Alternatively, it is also conceivable that the central axes M51, M52 of the intake opening 51 and the exhaust opening 52 extend at an angle to each other, e.g., at an angle between 5 degrees and 30 degrees, wherein the central axis M52 of the exhaust opening 52 is as shown in Fig. 6shown and the central axis M51 of the suction opening 51 extends parallel to the ceiling wall 22.

[0048] In Fig. 7 is a sectional view of another refrigeration device 200 with a heat exchanger assembly 100. The Fig. 7 The heat exchanger assembly 100 shown differs from that shown in Fig. 2 The heat exchanger assembly 100 shown in FIG. 1 is characterized in that the central axes M51, M52 of the intake opening 51 and the exhaust opening 52 extend parallel to each other. With respect to a direction perpendicular to the central axes M51, M52, the intake opening 51 and the exhaust opening 52 are located adjacent to each other, i.e., the central axes M51, M52 of the intake opening 51 and the exhaust opening 52 are spaced apart from each other. The rotational axis A4 of the fan 4 is coaxial with the central axis M51 of the intake opening 51. As shown in FIG. Fig. 7As can be seen, the central axis M51 of the intake opening 51 and thus also the rotation axis A4 of the fan 4 extends transversely to the ceiling wall 22. As in Fig. 7 As shown schematically, 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 intake opening 51 and the fan 4 are located, in the region of the ceiling wall 22 of the machine room 2. The intake opening 51 faces the floor 21 of the machine room 2.

[0049] In Fig. 8 is a sectional view of another refrigeration device 200 with a heat exchanger assembly 100. The Fig. 8 The heat exchanger assembly 100 shown differs from that shown in Fig. 2shown heat exchanger assembly 100 in that the central axis M51 of the intake opening 51 runs transversely to the longitudinal extent of the exhaust opening 52, e.g. to the long side of the rectangular circumference of the exhaust opening 52, but parallel to the longitudinal extent of the exhaust opening 52. In Fig. 8 It is shown by way of example that the central axis M51 of the intake opening 51 and thus also the rotational axis A4 of the fan 4 extend transversely to the side walls 23 of the machine room 2.

[0050] Although the present invention has been explained above using exemplary embodiments, it is not limited thereto but can be modified in a variety of ways. In particular, combinations of the above embodiments are also conceivable. REFERENCE SYMBOL

[0051] 1Storage compartment 1AOpening 2Machine room 3Refrigerant circuit 4Fan 5Air duct 21Floor of the machine room 22Ceiling wall of the machine room 22aSurface of the ceiling wall of the machine room 23Side walls of the machine room 24Front cover 24AInlet opening 25Rear opening 31Evaporator 32Compact condenser 33Compressor 34Fins 35Plates 36Convection ducts 50Interior 51Intake opening 52Discharge opening 100Heat exchanger assembly 200Refrigeration unit 202Rear wall of the storage compartment 202aOuter surface of the rear wall 203Inner container 204Floor of the storage compartment 205Side walls of the storage compartment 206Ceiling wall of the storage compartment 207Recess 208Insulation layer A4Rotation axis of the fan d208Layer thickness of the insulation layer M51Central axis of the intake opening M52Central axis of the exhaust opening w52Length of the exhaust opening d23Distance of the side walls of the machine room

Claims

1. Heat exchanger assembly (100) for a refrigeration appliance (200), in particular for a household refrigeration appliance, comprising: a compact condenser (32) for dissipating heat to the environment; a fan (4) for conveying an air flow over the condenser (32); and an air duct (5) extending between the fan (4) and the compact condenser (32); characterized in that the fan (4) is positioned in the air duct (5) in the region of an intake opening (51) of the air duct (5) and the compact condenser (32) is positioned in the air duct (5) in the region of an exhaust opening (52) of the air duct (5) on a pressure side (PS) of the fan (4).

2. Heat exchanger assembly (100) according to claim 1, wherein the blow-out opening (52) of the air guide duct (5) is longitudinally shaped, in particular rectangular, and a flow cross-section of the air guide duct (5) widens from the intake opening (51) to the blow-out opening (52).

3. Heat exchanger assembly (100) according to claim 1 or 2, wherein the intake opening (51) of the air duct (5) is circular.

4. Heat exchanger assembly (100) according to one of the preceding claims, wherein the fan (4) is designed as a radial fan.

5. Heat exchanger assembly (100) according to one of the preceding claims, wherein the compact condenser (32) has a plurality of parallel plates (35), in each of which a plurality of channels for the passage of refrigerant is formed, and a plurality of fins (34) which are arranged between the plates (35) and are in thermally conductive contact with the plates (35), wherein the fins (34) and the plates (35) extend parallel to a central axis (M52) of the blow-out opening (52).

6. Refrigeration appliance (200), in particular a household refrigeration appliance, comprising: a storage compartment (1) for accommodating refrigerated goods; a machine room (2) separate from the storage compartment (1); and a refrigerant circuit (3) for absorbing heat from the storage compartment (1) and dissipating heat to the environment, wherein the refrigerant circuit (3) comprises a heat exchanger assembly (100) according to one of the preceding claims, which is arranged in the machine room (2).

7. Refrigeration appliance (200) according to claim 6, wherein the machine room (2) has a floor (21), a ceiling wall (22) opposite the floor (21) and side walls (23) extending between the floor (21) and the ceiling wall (22), wherein the floor (21), the ceiling wall (22) and the side walls (23) define a rear opening (25) and the blow-out opening (52) of the air duct (5) is arranged in the region of the rear opening (25).

8. Refrigeration device (200) according to claim 7, wherein a central axis (M52) of the blow-out opening (52) is aligned transversely to the ceiling wall (22) of the machine room (52), so that air can be blown out along a rear wall (202) of the refrigeration device (200).

9. Refrigeration device (200) according to claim 8, wherein the compact condenser (32) is designed according to claim 5, and the plates (35) and fins (34) extend transversely to the ceiling wall (22).

10. Refrigeration appliance (200) according to one of claims 7 to 9, wherein the outlet opening (52) of the air duct (5) is positioned in the region of the ceiling wall (22) of the machine room (2).

11. Refrigeration device (200) according to claim 10, wherein in a transition region between the ceiling wall (22) of the machine room (2) and a rear wall (202) of the refrigeration device (200) extending transversely to the ceiling wall (22) and delimiting the storage compartment (1), a recess (207) is formed, in which the blow-out opening (52) of the air duct (5) is located.

12. Refrigeration appliance (200) according to claim 11, wherein the recess (207) forms an opening on an outer surface (202a) of the rear wall (202), and wherein the outer surface (202a) of the rear wall (202) and a surface (22a) of the ceiling wall (22) of the machine room (2) are connected by a transition surface (222a) running obliquely to the outer surface (202a) of the rear wall (202) and to the surface (22a) of the ceiling wall (22).

13. Refrigeration device (200) according to claim 11 or 12, wherein the recess (207) is formed in an insulation layer (208) of the rear wall (202).

14. Refrigeration appliance (200) according to one of claims 7 to 13, wherein the blow-out opening (52) extends longitudinally in a direction transverse to the side walls (23) of the machine room (2).

15. Refrigeration appliance (200) according to claim 14, wherein the blow-out opening (52) 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) of the machine room (2).