EP4379296A1 - Appareil frigorifique - Google Patents

Appareil frigorifique Download PDF

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Publication number
EP4379296A1
EP4379296A1 EP23207870.9A EP23207870A EP4379296A1 EP 4379296 A1 EP4379296 A1 EP 4379296A1 EP 23207870 A EP23207870 A EP 23207870A EP 4379296 A1 EP4379296 A1 EP 4379296A1
Authority
EP
European Patent Office
Prior art keywords
fan
machine room
opening
condenser
refrigeration appliance
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
EP23207870.9A
Other languages
German (de)
English (en)
Inventor
Robert Stahl
Frank Cifrodelli
Achim Paulduro
Alexander Ruppert
Ming Zhang
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 EP4379296A1 publication Critical patent/EP4379296A1/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
    • 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 fridge-freezer combination.
  • a storage compartment for storing refrigerated goods is as large as possible in relation to the space required by the appliance that is not used by the customer as storage space. It is therefore advantageous if the components of a refrigerant circuit can be accommodated in the most space-saving way possible.
  • a refrigerant compressor and a condenser for condensing the refrigerant compressed by the compressor are therefore often housed in a machine room separate from the storage compartment.
  • a fan is usually positioned in the machine room in such cases to direct an air flow over the condenser and thus improve heat dissipation.
  • the fan promotes as high a volume flow as possible on the one hand, but has as low an energy consumption as possible on the other.
  • the US 2009 / 0 169 387 A1 describes a household refrigeration appliance in which a compressor, a condenser and an axial fan are arranged in the machine room.
  • a partition wall divides the machine room into a first area in which the condenser is positioned and a second area in which the compressor is positioned.
  • the axial fan is arranged in a recess in the partition wall.
  • the KR 100198334 B1 further describes a household refrigeration appliance with a free-standing axial fan arranged in the machine room for transporting air via a condenser.
  • a refrigeration appliance in which a condenser is positioned in the machine room, whereby a radial fan arranged in a fan housing sucks air from the machine room via a deflection duct and expels it directly into the environment through an opening in the fan housing.
  • 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 storing refrigerated goods, a machine room separate from the storage compartment and a refrigerant circuit thermally coupled to the storage compartment, which is designed to extract heat from the storage compartment and release it to the environment, wherein the refrigerant circuit has a condenser assembly arranged in the machine room with a condenser for releasing the heat to the environment and a fan.
  • the fan is designed as a radial fan with a free-running impeller and is arranged in such a way as to guide air over the condenser and expel it into the machine room.
  • An impeller of the fan has a large number of blades, for example backward-curved blades, the blade tips of which are freely exposed in the machine room.
  • the fan sucks air from the environment into the machine room on a suction side, e.g. through an intake opening in a wall of the machine room, and expels the sucked-in air into the machine room on a pressure side, from where it is discharged into the environment, e.g. through an exhaust opening formed in a wall of the machine room.
  • the free-running impeller means that the fan has a simple design. In particular, no air duct is required to guide the air emitted by the fan, but rather the tips of the fan's blades are freely exposed in the machine room. This creates a turbulent air flow in the machine room, which is beneficial for heat transfer to components on the pressure side of the fan, e.g. for heat dissipation from a refrigerant compressor. In addition, the free-running impeller allows high flow rates with relatively low energy consumption.
  • the condenser can be arranged on a suction side of the fan, so that air can be sucked in via the condenser and expelled into the machine room by means of the fan.
  • the air sucked in by the fan is thus passed over the condenser, where it absorbs heat from the condenser.
  • the fan thus expels warm air on the pressure side and, due to the free-running impeller on the pressure side, generates a turbulent, warm air flow. This can be advantageously used for heating purposes, e.g. to evaporate condensate in the machine room.
  • an evaporation tray for collecting condensate from the storage compartment is arranged on a pressure side of the fan in the machine room.
  • the turbulent flow generated by the fan advantageously increases the evaporation rate of the condensate collected in the evaporation tray. condensate. This effect is further increased if the condenser is located on the suction side of the fan.
  • the condenser assembly divides the machine room into a first partial volume and a second partial volume, wherein the machine room has an intake opening that connects the first partial volume to the environment and an exhaust opening that connects the second partial volume to the environment, wherein the intake side of the fan is connected to the first partial volume and a pressure side of the fan is connected to the second partial volume in order to suck air into the first partial volume via the intake opening and expel it into the second partial volume, so that the second partial volume forms a pressure chamber from which the air can be discharged into the environment through the exhaust opening.
  • the condenser assembly for example the condenser itself, thus forms a physical separation between the first and the second partial volume.
  • the condenser assembly uses the entire available installation space in one direction, e.g. in a depth direction, which represents an efficient use of space. Furthermore, this limits a partial volume that forms a pressure chamber, i.e. a space in which a higher pressure prevails during operation of the fan compared to the partial volume connected to the suction side of the fan and in which a turbulent air flow flows. This allows the exhaust opening to be positioned more flexibly, whereby an advantageous effect can be achieved in terms of a uniform outflow through the exhaust opening and with regard to the pressure losses that occur there.
  • the machine room is delimited in relation to a vertical direction by a floor and a ceiling, in relation to a transverse direction by opposing side walls that extend between the floor and the ceiling, and in relation to a depth direction by an inner wall and a rear wall, wherein the blow-out opening is formed in the rear wall, for example as an elongated opening extending along the transverse direction.
  • the provision of the blow-out opening on the rear wall of the machine room offers the advantage that both in the case of built-in devices that are positioned in a built-in niche and in the case of free-standing devices, there is usually a gap between the rear wall and a boundary of the niche, through which the air can flow out.
  • the blow-out opening is formed in an end region of the rear wall facing the ceiling with respect to the vertical direction. This facilitates blowing out the air along the vertical direction and thus generally in a direction opposite to the direction of gravity. Since warm air is blown out through the blow-out opening, the blown-out air in this case flows out along the vertical direction due to natural convection.
  • the condenser assembly may divide the machine room in such a way that the first and second sub-volumes are located next to each other in relation to the transverse direction.
  • the condenser may, for example, extend along the depth direction between the inner wall and the rear wall and in relation to the vertical direction between the floor and the ceiling.
  • the intake opening is formed in the rear wall at a distance from the exhaust opening in the transverse direction. If the first and second partial volumes are located next to each other in relation to the transverse direction, as described above, this can advantageously result in a space-saving arrangement of the intake and exhaust openings. In the case of built-in devices in particular, the gap between the rear wall and the edge of the installation niche can be used advantageously for the air supply and exhaust in and out of the machine room.
  • the intake opening is formed in the rear wall at a distance from the exhaust opening in the vertical direction, and a seal is attached to an outer surface of the rear wall, which seal extends in the transverse direction and is arranged between the intake opening and the exhaust opening in relation to the vertical direction.
  • the seal can in particular be designed as a band-shaped seal.
  • the seal also extends along the outer surfaces of the side walls of the machine room along the depth direction.
  • the seal can be made of an elastic material, such as a foam material or rubber, for example. The seal represents a physical separation between the intake and exhaust openings and thus prevents a flow short circuit.
  • the seal can rest against the boundary of the installation niche, so that air is sucked into the intake opening from below and is discharged from above through the exhaust opening, whereby the seal seals the intake opening and the exhaust opening against each other in a fluid-tight manner.
  • the fan is positioned in the second partial volume.
  • the free-running impeller of the fan is not provided with an air guide housing, which is why the arrangement in the second partial volume has the advantage that the air does not have to be guided further into the machine room.
  • a refrigerant pipe that connects the compressor to the condenser can be provided to form a meander pipe in a space between the evaporation tray and the ceiling of the machine room.
  • This refrigerant pipe has a high temperature and can release heat both by radiation and by contact with air. Due to the meander shape with increased pipe length, the heat release is significant and the condenser will be operated at a lower temperature of the incoming gas. The heat release can be sufficient to dispense with routing the refrigerant pipe in the evaporation tray. This brings significant cost savings, since the heat release is achieved without the expense of a corrosion-protected refrigerant pipe.
  • the arrangement of the meander pipe in the space above the evaporation tray uses the heat release of the meander pipe for better evaporation of the water in the evaporation tray and can reduce or avoid condensation on the surrounding surfaces.
  • the pipe meander in the space area between the evaporative tray and the ceiling of the machine room is above a water surface in the evaporative tray and is independent of an optional refrigerant pipe section which connects the compressor to the condenser and is arranged inside the evaporative tray and can be in contact with water in the evaporative tray.
  • the condenser assembly may comprise a housing with a first opening in which the condenser is arranged and with a second opening which is connected to a suction connection of the fan.
  • the fan wheel may be arranged at the second opening.
  • the housing forms a flow channel in which the condenser is located and through which the fan sucks in air. This will advantageously increase the air flow actually passed over the condenser.
  • the housing may comprise a frame which defines the first opening and is optionally rectangular or substantially rectangular, and a funnel-shaped portion which extends from the frame and defines the second opening at an end facing away from the frame.
  • the condenser assembly may have a carrier which is attached to the housing and on which the fan is mounted.
  • the carrier may, for example, be detachably attached to the housing. This makes it easier to install the fan.
  • the carrier has a base portion which is arranged opposite the second opening of the housing and on which the fan is mounted, and at least one connecting strut which extends transversely to the base portion and is fastened to the frame of the housing.
  • the housing has a seal which extends along an outer circumference of the housing and rests against at least two opposite walls delimiting the machine room in order to hermetically seal a first side defined by the first opening of the housing against a side defined by the second opening of the housing.
  • the seal can, for example, rest against at least the ceiling and the floor of the machine room, optionally also against the rear wall and/or the inner wall. This advantageously prevents a flow short circuit between the pressure side and the suction side.
  • Fig.1 shows an example of a refrigeration device 100 in the form of a refrigerator.
  • the refrigeration device 100 can be a household refrigeration device, such as a refrigerator, a freezer or a freezer chest, or a fridge-freezer combination.
  • the refrigeration appliance 100 can be a built-in refrigeration appliance which is positioned in a built-in niche N.
  • the refrigeration appliance 100 has a storage compartment 1, a machine room 2 and a refrigerant circuit 3.
  • the storage compartment 1 serves to accommodate refrigerated goods, such as food, drinks, medicines or the like, and is delimited by a base wall 10, a ceiling wall 11 opposite this in a vertical direction V2, side walls 12 opposite each other in a transverse direction C2, which extend between the base wall 10 and the ceiling wall 11, and with respect to a depth direction T2 by a rear wall 13.
  • the installation niche N can be defined by a rear wall W, side walls S and a base B.
  • the rear wall 13 of the refrigeration appliance 100 can face the rear wall W of the installation niche N in the exemplary positioning of the refrigeration appliance 100 in the installation niche, leaving a gap G between the rear walls 13, W.
  • the machine room 2 forms a separate room from the storage compartment 1.
  • the machine room 2 can be defined with respect to the vertical direction V2 by a floor 20 and a ceiling 21, with respect to the transverse direction C2 by opposite side walls 22, 23 ( Figs. 2 to 4 ) extending between the floor 20 and the ceiling 21, and be limited in relation to the depth direction T2 by an inner wall 24 and a rear wall 25.
  • the floor wall 10 of the storage compartment 1 can optionally form the inner wall 24 and the ceiling 21 of the machine room 2 and thereby spatially separate the machine room 2 and the storage compartment 1 from one another.
  • the engine room 2 is connected by a suction opening 26 and a discharge opening 28, which, as in Fig.1 shown schematically, eg can be formed in the rear wall 25, connected to the environment.
  • the blow-out opening 28 can be designed, for example, as an elongated opening extending in the transverse direction C2. Irrespective of this, the blow-out opening 28 can optionally be designed in relation to the vertical direction V2 in an end region of the rear wall 25 facing the ceiling 21, as shown in Fig.2 is also shown.
  • the intake opening 26 can be formed, for example, in relation to the transverse direction C2 in an edge region of the rear wall 25 of the machine room 2, as shown in Fig.2
  • the suction opening 26 can be designed as a rectangular or substantially rectangular opening, which optionally extends over at least 50 percent of an extension of the rear wall 25 in the vertical direction V2.
  • the suction opening 26 and the exhaust opening 28 can be arranged at a distance from each other with respect to the transverse direction C2.
  • the suction opening 26 and the exhaust opening 28 can be designed at a distance from each other with respect to the vertical direction V2, as shown in Fig.2 is also shown.
  • a seal 5 can optionally be attached to an outer surface 25a of the rear wall 25 facing away from the machine room 2.
  • the seal 5 can be made of an elastic material, such as a foam material or a rubber material.
  • the seal 5 also extends in the depth direction T2 along the side walls 22, 23 and 12 of the machine room 2 and the storage compartment 1, as shown in Fig.2 shown as an example.
  • the seal 5 can be arranged between the intake opening 26 and the exhaust opening 28 with respect to the vertical direction V2.
  • the seal 5 rests against the rear wall W and optionally against the side walls S, as shown in Fig.1 shown schematically. This seals the exhaust opening 28 and the intake opening 26 from each other.
  • the refrigerant circuit 3 has, as in Fig.1 purely schematically shown, a condenser assembly 30, an evaporator 33, a compressor 34 and a throttle (not shown), e.g. in the form of a capillary.
  • the condenser assembly 30 is in Fig.1 shown only schematically as a block and comprises a condenser 31 and a fan 32 ( Fig.5 ).
  • the evaporator 33 is thermally coupled to the storage compartment 1 and is designed to extract heat from it by evaporating coolant.
  • An outlet of the evaporator 33 is connected to a suction connection of the compressor 34, which is designed to compress the gaseous coolant.
  • An inlet of the condenser 31 is connected to a pressure connection of the compressor 34, wherein the coolant condenses in the condenser 31 while releasing heat.
  • the fan 32 sucks air from the environment through the intake opening 26 into the machine room 2, directs it via the condenser 32 and expels it into the machine room 2, from where the air reaches the environment via the exhaust opening 28.
  • An outlet of the condenser 31 is connected via the throttle to an inlet of the evaporator 33.
  • the refrigerant circuit 3 is thus thermally coupled to the storage compartment 1 and designed to extract heat from the storage compartment 1 and release it into the environment.
  • the condenser assembly 30 and the compressor 34 are arranged or accommodated in the machine room 2.
  • Fig.5 shows an example of a condenser assembly 30 with the condenser 31 and the fan 32 as well as an optional housing 300.
  • the condenser 31 can be a compact condenser, in particular in the form of an MCHE condenser. "MCHE" is an abbreviation for the English term "Micro Channel Heat Exchanger”.
  • the condenser 31 may have a plurality of parallel plates 31A, in each of which a plurality of channels (not shown) for the passage of coolant is formed, and a plurality of fins 31B, which are arranged between the plates 31A and are in thermally conductive contact with the plates 31B.
  • the plates 31A and the fins 31B together define convection channels through which air can flow through the condenser 31.
  • the compact condenser 31 can, for example, have a substantially rectangular shape.
  • the fan 32 is designed as a radial fan with a free-running impeller 320.
  • the impeller 320 is rotatable about a rotation axis A32, eg by means of an electric motor (not shown), and the fan 32 has a plurality of blades 321 which extend along a radial direction with respect to the rotation axis A32.
  • the blades 321 can be curved backwards. In this case, an exit angle at a blade tip 322 of the respective in relation to a direction of rotation DR of the impeller 320 is less than 90 degrees.
  • the impeller 320 Since the impeller 320 is free-running, the blade tips 322 of the blades 320 are not surrounded by an air guide housing in relation to the radial direction, air is freely discharged on a pressure side of the fan 32 or directly into the machine room 2.
  • the conveyed air flow has on the pressure side of the Fan 32 has a velocity component in the circumferential direction which is relatively high compared to the radial component of the flow velocity. This makes it easy to generate a turbulent flow on the pressure side of the fan in the machine room 2, as shown in Figs. 3 and 6 shown schematically by the arrows P1.
  • the rotation axis A32 of the fan 32 may extend transversely to the condenser 31.
  • the condenser 31 is arranged on the suction side of the fan 32, as shown in Fig.5 is also shown schematically.
  • the optional housing 300 may generally have a first opening 301 in which the condenser 31 is arranged and a second opening 302 which is connected to the suction port of the fan 32.
  • the fan 32 can be positioned, for example, at the second opening 302, in particular such that the axis of rotation A32 is coaxial with a central axis of the second opening 302.
  • the housing 300 may include a frame 303 defining the first opening 301 and a funnel-shaped portion 304 extending from the frame 303 and defining the second opening 302 at an end remote from the frame 303.
  • the frame 303 may be rectangular, for example, so that it surrounds the rectangular condenser 31.
  • the condenser assembly 30 can have a carrier 310 on which the fan 32 is mounted or which carries the fan 32.
  • the carrier 310 can in particular have a base section 311 and at least one connecting strut 312.
  • the base section 311 can have a flat extension and, for example, as in Fig.5 shown, be designed as a plate.
  • the fan 32 is mounted on the base section 311.
  • the carrier 310 shown has, purely by way of example, two connecting struts 312 which are attached to opposite ends of the base section 311 and each extend transversely to the base section 310.
  • the carrier 310 is attached to the housing 300, eg detachably.
  • the connecting struts 312 can be connected to the housing 300, eg to the frame 303.
  • the frame 303 may have a groove 306 on an outer surface into which an end region 313 of the connecting strut 312 engages.
  • the base portion 311 is arranged opposite the second opening 302 of the housing 300
  • the condenser assembly 30 is accommodated in the machine room 2. If the condenser 31, as described above, is arranged on a suction side of the fan 32, air is sucked into the machine room 2 through the intake opening 26 by means of the fan 32, passed over the condenser 31 and expelled directly into the machine room 2 on the pressure side of the fan 32.
  • the condenser assembly 31, the condenser assembly 100 divides the machine room 2 into a first partial volume 2A and a second partial volume 2B, e.g. in relation to the transverse direction C1, as shown in the Figs. 3 and 4 shown.
  • the condenser 31 or the frame 303 of the housing 300 extends along the depth direction T1 between the inner wall 24 and the rear wall 25 and in relation to the vertical direction V2 between the floor 20 and the ceiling 21 of the machine room 2.
  • a seal 305 can be provided on the outer circumference of the housing 300, e.g. between the ceiling 21 and the frame 303 and between the floor 20 and the frame 303, wherein the seal 305 rests on the frame 303 and on the ceiling 21 or the floor 20.
  • the intake opening 24 connects the first partial volume 2A, which in the example of Figs. 3 and 4 through the first side wall 22, the floor 20, the condenser assembly 30 and the ceiling 21 as well as through the rear wall 25, in particular through its section located above the optional seal 5 ( Fig.2 ) and the inner wall 24, with the environment.
  • the blow-out opening 26 connects the second partial volume 2B, which in the example of the Figs. 3 and 4 by the second side wall 22, the floor 20, the condenser assembly 30 and the ceiling 21 as well as by the rear wall 25 and the inner wall 24, with the environment.
  • the fan 32 can be arranged in the second partial volume 2B.
  • the suction side of the fan 32 is connected to the first partial volume 2A through the housing 300 or its first and second openings 301, 302.
  • the pressure side of the fan 32 is located in the second partial volume 2B.
  • the compressor 34 of the refrigerant circuit 3 can also be positioned in the second partial volume 2B. This improves the heat dissipation from the compressor 34, since the air coming from the fan 32, as in Fig.4 shown schematically, flows turbulently or rotating in the machine room 2 and thereby high heat transfer performance for cooling the compressor 34 is achieved.
  • an evaporation tray 4 which in the example of the Figs. 3 and 4 is attached to the compressor 34 and serves to collect condensate from the storage compartment 1, also be arranged in the second partial volume 2B.
  • the evaporation tray 4 is preferably arranged on a pressure side of the fan 32.
  • the visible space between the evaporation tray 4 and the ceiling 2 of the machine room can be used for arranging a meander pipe in a refrigerant pipe that connects the compressor 34 to the condenser 31.
  • this refrigerant pipe causes the compressed gas to cool down and generates additional condensation power.
  • the refrigerant pipe causes the water in the evaporation tray to evaporate better.
  • the fan 32 thus sucks air into the first partial volume 2A via the intake opening 26.
  • the air flows over or through the condenser 31, where it absorbs heat, and passes through the openings 301, 302 of the housing 300 to the impeller 320 of the fan 32.
  • the rotating impeller 320 conveys air radially outwards by means of the blades 321, so that the air is expelled from the blade tips 322 directly into the second partial volume 2B.
  • the second partial volume 2B forms a pressure chamber in which there is a turbulent or rotating, warm air flow. This flow promotes high evaporation rates in the optional evaporation tray 4. From the second partial volume 2B, the air flows out into the environment through the exhaust opening 28.
  • the air flows along the rear wall 13 in the vertical direction V2 upwards, as shown in Fig.1 and similarly in the Figs. 2 and 4 symbolically represented by the arrows P2.
  • the warm air advantageously prevents the formation of condensate on the rear wall 13 of the refrigeration device. Since the air is expelled undirected by the fan 32 directly into the machine room 2, where it travels a certain flow path and only then reaches the blow-out opening 28, a relatively even distribution of the flow speeds is advantageously achieved. in relation to the transverse direction C2. This advantageously reduces the pressure losses of the flow and also promotes an even heat distribution on the rear wall 13.
  • these advantages are not only achieved in the Fig.1 shown installation situation of a refrigeration appliance 100 realized as a built-in appliance, but also, for example, when a free-standing refrigeration appliance 100 is positioned with its rear wall 13 close to a wall.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP23207870.9A 2022-11-30 2023-11-06 Appareil frigorifique Pending EP4379296A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102022212849.4A DE102022212849A1 (de) 2022-11-30 2022-11-30 Kältegerät

Publications (1)

Publication Number Publication Date
EP4379296A1 true EP4379296A1 (fr) 2024-06-05

Family

ID=88598823

Family Applications (1)

Application Number Title Priority Date Filing Date
EP23207870.9A Pending EP4379296A1 (fr) 2022-11-30 2023-11-06 Appareil frigorifique

Country Status (3)

Country Link
EP (1) EP4379296A1 (fr)
CN (1) CN118111155A (fr)
DE (1) DE102022212849A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2080879A (en) * 1980-07-28 1982-02-10 Gebhardt Gmbh Wilhelm Flow guides for centrifugal fans
KR100198334B1 (ko) 1996-09-25 1999-06-15 전주범 냉장고 기계실 착탈장치
JP2003322456A (ja) * 2002-04-26 2003-11-14 Hitachi Home & Life Solutions Inc 冷蔵庫
US20090169387A1 (en) 2007-12-28 2009-07-02 Lg Electronics, Inc. Fan assembly
US20130067948A1 (en) 2011-09-15 2013-03-21 Hyun Kim Cooling apparatus for a machine room of a refrigerator using a nacelle-shaped duct
KR101650379B1 (ko) * 2009-05-18 2016-08-23 엘지전자 주식회사 냉장고
CH713485A2 (de) 2018-07-16 2018-09-28 V Zug Ag Kühlgerät mit aktiv gekühltem Maschinenraum.

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3403529A (en) 1966-11-07 1968-10-01 Philco Ford Corp Refrigeration condensate handling means
DE19907077A1 (de) 1999-02-19 2000-08-24 Bsh Bosch Siemens Hausgeraete Kältegerät für den Einbau in eine Möbelnische
JP2005140410A (ja) 2003-11-06 2005-06-02 Matsushita Electric Ind Co Ltd 冷蔵庫
EP1559975A3 (fr) 2004-01-28 2006-04-19 Lg Electronics Inc. Réfrigérateur avec ventilateur à courant transversal

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2080879A (en) * 1980-07-28 1982-02-10 Gebhardt Gmbh Wilhelm Flow guides for centrifugal fans
KR100198334B1 (ko) 1996-09-25 1999-06-15 전주범 냉장고 기계실 착탈장치
JP2003322456A (ja) * 2002-04-26 2003-11-14 Hitachi Home & Life Solutions Inc 冷蔵庫
US20090169387A1 (en) 2007-12-28 2009-07-02 Lg Electronics, Inc. Fan assembly
KR101650379B1 (ko) * 2009-05-18 2016-08-23 엘지전자 주식회사 냉장고
US20130067948A1 (en) 2011-09-15 2013-03-21 Hyun Kim Cooling apparatus for a machine room of a refrigerator using a nacelle-shaped duct
CH713485A2 (de) 2018-07-16 2018-09-28 V Zug Ag Kühlgerät mit aktiv gekühltem Maschinenraum.

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Publication number Publication date
DE102022212849A1 (de) 2024-06-06
CN118111155A (zh) 2024-05-31

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