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EP3869130A1 - Réfrigérateur pourvu d'évaporateur à lamelles - Google Patents

Réfrigérateur pourvu d'évaporateur à lamelles Download PDF

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Publication number
EP3869130A1
EP3869130A1 EP21152458.2A EP21152458A EP3869130A1 EP 3869130 A1 EP3869130 A1 EP 3869130A1 EP 21152458 A EP21152458 A EP 21152458A EP 3869130 A1 EP3869130 A1 EP 3869130A1
Authority
EP
European Patent Office
Prior art keywords
evaporator
storage chamber
chamber
refrigeration device
spatial direction
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP21152458.2A
Other languages
German (de)
English (en)
Inventor
Niels Liengaard
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 EP3869130A1 publication Critical patent/EP3869130A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F25D17/067—Evaporator fan units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
    • F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
    • F25D2317/0683—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans the fans not of the axial type

Definitions

  • the present invention relates to a refrigeration device, in particular a household refrigeration device, with an evaporator chamber and a first evaporator module arranged in the evaporator chamber.
  • a refrigeration device also referred to as a no-frost device
  • a storage chamber is cooled in that air is exchanged between the evaporator chamber and the storage chamber.
  • the evaporator chamber generally extends either between a rear wall of a body of the refrigeration device and a vertical partition wall to the storage chamber, and the lamellar evaporator therein is oriented on edge, or it extends between a ceiling of the body and a partition sloping in the depth direction of the body, and the lamellar evaporator is inclined parallel to the partition wall.
  • a refrigeration device with two storage chambers arranged one above the other is known, each of which is assigned its own evaporator. While the upper evaporator chamber extends vertically along a rear wall of the storage chamber as described above and communicates with the storage chamber via vertically spaced inlet and outlet openings, and an axial fan at the outlet opening drives the exchange of air, the lower, much higher storage chamber is a vertically elongated, horizontal one assigned through flow evaporator. In order to flow through this over its entire height, a likewise vertically elongated fan rotating about a vertical axis is proposed. Since this fan must suck in from the radial direction as well as discharge in the radial direction, and no precautions can be seen that could prevent air from being conveyed back from the outlet to the inlet inside the fan, the efficiency of the fan is low.
  • this need is satisfied in that, in a refrigeration device with at least one temperature zone comprising a storage chamber and an evaporator chamber assigned to the storage chamber, the evaporator chamber extending in a first spatial direction along the storage chamber and via inlet and outlet openings spaced in the first spatial direction with the storage chamber communicates and a fan is arranged at an outlet opening to suck air out of the evaporator chamber and expel it into the storage chamber, the fan is at least one radial fan whose axis of rotation is oriented in the first spatial direction.
  • the space requirement of the fan in the first spatial direction can be reduced considerably, and the dimensions of the evaporator in the first spatial direction can be selected to be correspondingly larger.
  • a partition between the storage compartment and the evaporator chamber is in the first spatial direction and one in addition extends orthogonal second spatial direction, and the dimension of the partition wall in the first spatial direction is greater than in the second.
  • the inlet opening and the outlet opening are preferably as slots elongated in a second direction at ends of the partition extending between the storage compartment and the evaporator chamber which are spaced apart in the first direction educated.
  • the axis of rotation of the radial fan is preferably oriented so that it crosses the evaporator; in this way the air can reach the radial fan in a straight line from the evaporator via an inlet extending around the axis.
  • the diameter of the radial fan can be greater than the distance between the inside of the bypass blocker facing the evaporator.
  • the diameter of the radial fan is preferably not greater than the distance between the outer sides of the bypass blockers facing away from one another.
  • the first preferably corresponds to the width of a body of the refrigeration device in which the storage compartment and the evaporator chamber are accommodated.
  • the second spatial direction can in particular be the height.
  • the arrangement defined above is particularly suitable for a storage chamber of low height.
  • the invention allows economical cooling of storage compartments with edge length ratios that were previously not common in refrigeration equipment because they could not be economically cooled with conventional evaporators - especially from the point of view of space utilization and energy efficiency - for example with a height that corresponds to a maximum of half the height or width.
  • a storage compartment that is low in the sense of the present invention can also be recognized, for example, by the fact that it is filled by a single pull-out box, because even with a pull-out box, the height of all three dimensions is generally the smallest, otherwise one is faster Access to the contents of the box is not possible.
  • the evaporator preferably comprises a plurality of evaporator modules which are successive in width and which each have identically shaped refrigerant lines connected in series and fins attached to the refrigerant lines.
  • a small amount of liquid refrigerant is sufficient to completely fill one of the evaporator modules, and the fact that other evaporator modules further downstream in the refrigerant circuit may only contain steam does not affect the even distribution of the cooling effect over the cross section of the evaporator.
  • Each of these modules should extend the full height of the evaporator.
  • the refrigerant lines of various evaporator modules are preferably soldered to one another and / or plug-connected.
  • the modules can be manufactured inexpensively in large numbers; lamellar evaporators with different widths can be provided at low cost by connecting different numbers of modules as required.
  • connections between the refrigerant lines are preferably arranged along a single edge of the substantially cuboidal evaporator.
  • each lamella preferably has exactly two holes that form the refrigerant line each crosses once. This allows the refrigerant line to be bent into a hairpin shape, the lamellae to be pushed one after the other onto the pipe sections of the refrigerant line obtained thereby, and a heat-conducting contact to the lamellae to be established along the entire or substantially the entire circumference of the legs.
  • each tube section is connected to each lamella in a thermally conductive manner over at least two thirds of its circumference, preferably over its entire circumference.
  • each evaporator module are preferably rectangular and adjoin an adjacent block of the same evaporator module along at least one long edge and a block of another evaporator module along a short edge. In this way, one of the two pipe sections of a block can be placed in the flow shadow of the other.
  • the fins should not be oriented horizontally.
  • the fins of each evaporator module should be arranged in several blocks arranged one above the other.
  • the distance between the fins of an evaporator module located upstream with respect to the air flow or the refrigerant flow can be selected to be greater than the distance between the fins of an evaporator module located downstream with respect to this flow.
  • the heat absorption capacity of a lamella that is only cooled by refrigerant vapor is significantly smaller than that of one cooled by liquid refrigerant, so that if the modules connected in series have different levels of refrigerant are supplied, the fins of the evaporator module located foremost in the refrigerant flow can achieve the highest growth rate of the frost layer.
  • the distance between the fins should be uniform within an evaporator module.
  • the refrigeration device preferably has a plurality of storage chambers, each of which communicates with an evaporator chamber in order to be temperature-controlled by its evaporator.
  • each storage chamber can be regulated to its own temperature, preferably by means of its own temperature sensor, which, with a suitable design of the refrigerant circuit for individual storage chambers, can also be above the ambient temperature.
  • a specific humidity level for each storage chamber can be achieved by regulating a temperature difference between the evaporator and the storage chamber. Mixing of differently tempered or differently humid amounts of air from different storage chambers does not take place.
  • Fig. 1 shows two variants of lamellas 1, 1 'which are used to produce a lamellar evaporator.
  • the lamellas 1, 1 ' are thin metal sheets, typically made of aluminum, of a substantially rectangular shape.
  • Two holes 2 are spaced from each other in a direction parallel to a long edge 3 of the rectangles; the distance d between the holes 2 is typically between a third and half the length of the edge 3.
  • the length of a short edge 4 can be between d and 2 d.
  • the holes 2 of the lamella 1 are circular with a diameter which, with minimal play, corresponds to the diameter of a pipe section of a refrigerant line to be inserted in order to enable a thermally conductive contact between the pipe section and the lamella along essentially the entire circumference of the holes 2.
  • the circular circumference is interrupted by notches 5, which allow the tongues 6 delimited by the notches 5 to evade when the pipe section is inserted;
  • the pressure of the tongues 6 deflected during insertion ensures an efficient heat transfer between the pipe section and the lamella.
  • Fig. 2 shows a top view of partially finished evaporator modules 7a-d.
  • Each evaporator module comprises a hairpin-shaped bent refrigerant line 8 with a first bend 9 and two straight pipe sections 10a and 10b that are integrally connected via the bend 9.
  • a plurality of parallel lamellae 1 are each pushed onto the pipe sections 10a-b and grouped into blocks 11a-d.
  • the extent of all blocks 11a-d in the longitudinal direction of the pipe sections 9 is the same; the number of lamellas 1 in a block 11a-d and their distance from one another can vary.
  • Fig. 3 shows a finished evaporator module 7. Areas of the pipe sections 10a-b, which are in the stage of Fig. 2 have remained free of lamellas are formed into semicircular second arcs 12, so that the blocks 11a-d form a stack in which long edges 3 of the lamellas of one block each face long edges of the lamellas of an adjacent block.
  • the block 11a adjacent to the first sheet 9 forms the bottom block of the stack.
  • the pipe sections 10a-b meander through the blocks 11b, 11c stacked on them up to inlet and outlet connections 13, 14.
  • One of these connections, here connection 13, is widened in order to enable the connection 14 of a structurally identical second evaporator module to be plugged in .
  • Fig. 4 shows four evaporator modules, denoted by 7a-d, the refrigerant lines 8 of which are connected in series by plugging into one another and soldering the connections 13, 14.
  • the connectors 13, 14 plugged into one another lie on a straight line which runs parallel to a long edge of the approximately cuboidal evaporator 15 formed by the evaporator modules 7a-d.
  • the evaporator modules 7a-d can be exactly identical; in the case of Fig. 4
  • the evaporator module 7a differs from the other modules 7b-d in that the distance between the lamellae 1 is greater. If air flows through the evaporator 15 horizontally, in the direction of the arrows 16, during operation, the evaporator module 7a is the most upstream module in relation to the airflow, and moisture carried along in the airflow is preferably deposited on the fins of the module 7a especially when the connection 13 is used as an inlet connection and therefore the evaporator module 7a is better supplied with liquid refrigerant than the others.
  • the increased spacing of the lamellas makes it possible to select a long time interval between two defrosting processes.
  • rapid tire build-up of the evaporator module 7a can be counteracted if the connection 14 of the module 7d is used as an inlet connection for refrigerant; then the module 7d is best supplied with liquid refrigerant.
  • the formation of frost can vary depending on how often and how much liquid refrigerant reaches the blocks further downstream in relation to the refrigerant flow distribute to modules 7a-d. If only steam gets into the modules 7b-d, the formation of frost is so concentrated on the module 7d that it can make sense to provide an enlarged lamellar spacing in this. If the other modules also receive liquid refrigerant from time to time, frost formation takes place in these too, so that the frost is distributed over all modules and the fin spacing can be the same in all of them.
  • the connected connections 13, 14 represent the highest points of the refrigerant line in the evaporator 15, it is possible to completely fill the refrigerant line 8 of the module 7a or 7d which is furthest upstream in relation to the refrigerant flow with liquid refrigerant, even if the refrigerant lines 8 the following modules only contain steam. In this way, uniform cooling of the air flowing through is ensured over the entire cross section of the evaporator 15, even if the evaporator 15 is not completely filled.
  • Fig. 5 shows a section through the body 17 of a household refrigeration appliance with several storage chambers at different temperatures.
  • the sectional plane runs near a rear wall of the body 17 through evaporator chambers 18a-c extending on this rear wall, each of the evaporator chambers 18a-c each contains an evaporator 15a-c of the type described above and forms a closed air circuit with the associated storage chamber.
  • Storage chambers (not shown) each have the same height as the associated evaporator chambers 18a-c and are separated from one another by intermediate floors 19 of the body 17 which are heat-insulating and which prevent air exchange between the various air circuits.
  • the lowest storage chamber here is a freezer compartment, the height of which roughly corresponds to its width.
  • the height of the evaporator chamber 18a is somewhat smaller than that of the storage chamber, since part of the rear wall is occupied by a machine room 20 in the usual manner.
  • the evaporator chamber 18a communicates with the storage chamber via an outlet opening 22a provided with an axial fan 21 in an upper region of a partition wall 24a and an inlet opening 23a in the form of a gap at a lower edge of the partition wall 24a.
  • the evaporator 15a comprises several, here five, in the width direction of the body 17 arranged side by side evaporator modules 7 with here five blocks 11, which are flown through from bottom to top during operation.
  • next higher storage chamber and its evaporation chamber 18b are much flatter; if one wanted to provide a horizontal gap and an opening as in the evaporator chamber 18a, then there would be no space to accommodate evaporator modules 7 in sufficient number and size.
  • the number of evaporator modules 7a-d is therefore reduced in evaporator 15b, so that space remains to the right and left of evaporator 15b to provide an inlet opening 23b and an outlet opening 22b - here covered by a radial fan 25 - as well as the number of blocks 11 is reduced to match the height of the evaporation chamber 18b.
  • the blocks 11 themselves can be identical to those of the evaporator 15a; However, it is also conceivable to vary the number of lamellae 1 per block 11 from one evaporator 15a-c to the other in order to adapt to the capacities required in each case for the individual storage chambers. However, the smaller the number of fins, the less favorable the ratio of power to space requirement of the evaporator due to the protruding arches 9, 12. It can therefore be expedient to further reduce the number of modules 7 when the power requirement is low, as shown in the example of the evaporator 15c, so that the evaporator chamber 18c only occupies part of the width of the rear wall and the remaining width of the storage chamber 26c extends up to can extend to the rear wall.
  • the inlet opening 23c can then be designed as a vertically elongated gap between the rear wall and an end of the partition wall 24c facing away from the radial fan 25.
  • Fig. 6 shows a section through a rear part of the body 17 at the level of the line VI-VI Fig. 5 .
  • the already mentioned rear wall of the body 17 is denoted by 27, side walls by 28.
  • the arches 9, 12 of the evaporator 15b protruding in the depth direction of the body are received in bypass blockers 29, typically molded parts made of expanded polystyrene, in order to be removed from the storage chamber via the inlet opening 23b 26b to force air sucked in between the fins of the evaporator 15b.
  • a suction opening 30 of the radial fan 25 lies opposite a downstream end of the evaporator 15b.
  • the radial fan 25 comprises in a manner known per se Fan wheel 35, which rotates within a housing 31 - shown here cut open in half - about an axis 34 which is concentric to the suction opening 30 and parallel to the lamellae 1.
  • the diameter of the suction opening 30 corresponds approximately to the edge length of a block 11 in the direction perpendicular to the lamellas or the distance between facing inner sides of the bypass blockers 29, the diameter of the housing 31 corresponds approximately to the thickness of the evaporator 15b including the bends 9, 12 or is slightly smaller than the distance between the respective outer sides of the bypass blockers 29 resting against the partition wall 24b and the rear wall 27 of the body.
  • the fan wheel 35 carries a ring of blades 36, the inner diameter of which corresponds approximately to that of the suction opening 30; The rotation of the fan wheel 35 accelerates the air between the blades 36 radially outwards and escapes from the housing 31 via a nozzle 37 branching off in a tangential direction.
  • the nozzle 37 crosses the partition wall 24b, its end protruding into the bearing chamber 26b forms the outlet opening 22b.
  • the diameter of the fan 25 and in particular its suction opening is significantly smaller than the height of the evaporator 15b, which can lead to an uneven distribution of the air flow velocity over the height, especially in the evaporator module 7d which is closest to the fan 25b.
  • This can in particular be tolerated to a certain extent if the evaporator module 7d is the module located furthest downstream in the refrigerant circuit and the other modules, which are better supplied with liquid refrigerant, contribute more to the cooling capacity.
  • two radial fans could also be arranged one above the other in order to achieve a more uniform distribution of the air flow at the downstream end of the evaporator 15b.
  • a pull-out basket or pull-out box 32 In order to be able to easily access the contents of the storage chamber 26b despite its small height, it is useful to provide a pull-out basket or pull-out box 32.
  • a rail guide or the shape of the pull-out box 32 can ensure that it does not block the openings 22b, 23b.
  • the inlet opening 23b is flanked by a web 33 of the partition wall 24b protruding into the storage chamber 26b, and the depth of the pull-out box 32 is adapted to that of the storage chamber 26b so that a door of the storage chamber 26b can only be closed when the pull-out drawer 32 as in shown next to the web 33 on the partition 24b, but leaves the space in front of the inlet opening 23b free.
  • the nozzle 37 protruding over the partition wall 24b prevents the door from closing when the pull-out box 32 blocks the outlet opening 22b restrict the width of the storage chamber 26b that can be used by refrigerated goods or the pull-out box 32 as little as possible.
  • Fig. 7 shows a modification of the body of Fig. 6 , in which the height of the freezer compartment is reduced, so that the space on the rear wall of the body is no longer sufficient to accommodate the evaporator 15a and the axial fan 21 there.
  • the axial fan is therefore replaced by radial fan 25 with a vertical axis. So that the evaporator 15a is sufficiently flowed through over its entire width, several, here two, fans 25 are distributed over the evaporator.

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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)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
EP21152458.2A 2020-02-20 2021-01-20 Réfrigérateur pourvu d'évaporateur à lamelles Withdrawn EP3869130A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102020202172.4A DE102020202172A1 (de) 2020-02-20 2020-02-20 Kältegerät mit Lamellenverdampfer

Publications (1)

Publication Number Publication Date
EP3869130A1 true EP3869130A1 (fr) 2021-08-25

Family

ID=74191670

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21152458.2A Withdrawn EP3869130A1 (fr) 2020-02-20 2021-01-20 Réfrigérateur pourvu d'évaporateur à lamelles

Country Status (3)

Country Link
EP (1) EP3869130A1 (fr)
CN (1) CN113280557A (fr)
DE (1) DE102020202172A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2997857A (en) * 1958-09-04 1961-08-29 Gen Motors Corp Refrigerating apparatus
JPH03169482A (ja) * 1989-11-29 1991-07-23 Showa Alum Corp 熱交換器の製造方法
KR19980018857U (ko) 1996-09-30 1998-07-06 배순훈 수평으로 냉기가 순환되는 냉장실을 갖는 냉장고
JP2002168552A (ja) * 2000-11-30 2002-06-14 Sanyo Electric Co Ltd 冷蔵庫
WO2006120079A1 (fr) * 2005-05-10 2006-11-16 BSH Bosch und Siemens Hausgeräte GmbH Appareil frigorifique
DE102006015992A1 (de) * 2006-04-05 2007-10-11 BSH Bosch und Siemens Hausgeräte GmbH Gebläse für ein Kältegerät
DE102010038373A1 (de) * 2010-07-23 2012-01-26 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit Gebläse

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014222851A1 (de) * 2014-11-10 2016-05-12 BSH Hausgeräte GmbH No-Frost-Kältegerät
KR20190125651A (ko) * 2018-04-30 2019-11-07 주식회사 위니아대우 증발기 유닛 및 이를 갖는 냉장고

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2997857A (en) * 1958-09-04 1961-08-29 Gen Motors Corp Refrigerating apparatus
JPH03169482A (ja) * 1989-11-29 1991-07-23 Showa Alum Corp 熱交換器の製造方法
KR19980018857U (ko) 1996-09-30 1998-07-06 배순훈 수평으로 냉기가 순환되는 냉장실을 갖는 냉장고
JP2002168552A (ja) * 2000-11-30 2002-06-14 Sanyo Electric Co Ltd 冷蔵庫
WO2006120079A1 (fr) * 2005-05-10 2006-11-16 BSH Bosch und Siemens Hausgeräte GmbH Appareil frigorifique
DE102006015992A1 (de) * 2006-04-05 2007-10-11 BSH Bosch und Siemens Hausgeräte GmbH Gebläse für ein Kältegerät
DE102010038373A1 (de) * 2010-07-23 2012-01-26 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit Gebläse

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DE102020202172A1 (de) 2021-08-26
CN113280557A (zh) 2021-08-20

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