EP2899481A1 - Réfrigérateur - Google Patents

Réfrigérateur Download PDF

Info

Publication number
EP2899481A1
EP2899481A1 EP13838191.8A EP13838191A EP2899481A1 EP 2899481 A1 EP2899481 A1 EP 2899481A1 EP 13838191 A EP13838191 A EP 13838191A EP 2899481 A1 EP2899481 A1 EP 2899481A1
Authority
EP
European Patent Office
Prior art keywords
cooling device
compartment
cold air
refrigerator
cold storage
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Withdrawn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
EP13838191.8A
Other languages
German (de)
English (en)
Other versions
EP2899481A4 (fr
Inventor
Yoshimasa Horio
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.)
Panasonic Intellectual Property Management Co Ltd
Original Assignee
Panasonic Intellectual Property Management Co Ltd
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 Panasonic Intellectual Property Management Co Ltd filed Critical Panasonic Intellectual Property Management Co Ltd
Publication of EP2899481A1 publication Critical patent/EP2899481A1/fr
Publication of EP2899481A4 publication Critical patent/EP2899481A4/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/04—Preventing the formation of frost or condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • F25D21/08—Removing frost by electric heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present invention relates to a refrigerator which uses cold air generated by a cooling device and circulated by a fan for cooling.
  • the following configurations have been proposed as methods for preventing decrease in the cooling efficiency caused by frost adhering to a cooling device.
  • cold air returning from the inside of a highly humid cold storage compartment to a cooling device reaches the cooling device from below along a guide plate disposed below the cooling device so as to equalize frosting on the cooling device and thereby prevent capability deterioration (for example, see PTL 1).
  • cold air returning from the inside of a refrigerator flows through the interior of a heat insulating partitioning wall disposed below a cooling device to pass through a distance substantially equivalent to the lateral length of the cooling device from the lower side of the cooling device, and thereby offer an advantage of equalization of frosting on the cooling device (for example, see PTL 2).
  • a flow path, a shield, and a guiding member are provided to direct the flow of cold air toward the center of a cooling device as much as possible in returning from the inside of a refrigerator to the cooling device (for example, see PTL 3). This configuration diffuses return cold air for equalization of frosting on the cooling device, and also prevents clogging of the cooling device caused by uneven frosting, so as to avoid decrease in cooling efficiency.
  • FIG. 7 is a perspective view illustrating a configuration of the surroundings of a cooling device of a refrigerator described in PTL 1, particularly illustrating guide plate 28 for cold storage compartment return cold air 27.
  • Cold air generated by cooling device 7 circulates inside the refrigerator, and flows from the inside of the refrigerator into cooling device 7 as return cold air after circulation.
  • Cold storage compartment return cold air 27 from the cold storage compartment enters return duct 29 disposed on the right side as illustrated in FIG. 7 .
  • Guide plate 28 positioned between defrosting heater 32 and drain pan 34 extends from an outlet of return duct 29 toward the left side below cooling device 7, forming a duct-shaped space between guide plate 28 and drain pan 34. Openings 28a are further formed in the surface of guide plate 28.
  • Cold storage compartment return cold air 27 is dispersed by openings 28a, and flows toward an area below cooling device 7. Then, cold storage compartment return cold air 27 is mixed with freezing compartment return cold air 30 flowing from a freezing compartment into a space between guide plate 28 and the lower end of cooling device 7, and the mixture of air 27 and 30 is uniformly sucked into a lower portion of cooling device 7.
  • guide plate 28 is formed between defrosting heater 32 and drain pan 34 as an extension of return duct 29.
  • This configuration produces the mixture of cold storage compartment return cold air 27 from the highly humid cold storage compartment and freezing compartment return cold air 30 from the freezing compartment, and thereby equalizes frosting on cooling device 7. Accordingly, this configuration maintains cooling performance for a long period by preventing unevenness of clogging between fins of cooling device 7 caused by frosting, and also shortens defrosting time of defrosting heater 32. As a result, power consumption decreases.
  • guide plate 28 is disposed in the up-down direction of cooling device 7. In this case, the inside length of the refrigerator in the depth direction does not become shorter, and advantages such as avoidance of decrease in the inner volume of the refrigerator can be offered.
  • FIGS. 8A and 8B are a front cross-sectional view of the surroundings of a cooling device of a refrigerator described in PTL 2, and a side cross-sectional view illustrating flow of cold air during operation of a cold storage compartment, respectively.
  • Cooling device 7 is provided behind a freezing compartment (not shown).
  • a cold storage compartment is provided on the upper side of the freezing compartment, and a vegetable compartment is provided on the lower side of the freezing compartment.
  • Cold air having cooled the cold storage compartment and circulated the inside of the refrigerator is supplied to the vegetable compartment via return duct 29 extending from the cold storage compartment (cold storage compartment-vegetable compartment communication duct).
  • Vegetable compartment return cold air from the vegetable compartment is directed into cooler compartment 23 via vegetable compartment return duct 31 provided within heat insulating partitioning wall 13.
  • return cold air from the cold storage compartment positioned on the upper side of the freezing compartment is directed to temporarily enter the vegetable compartment without direct flow into the cooler compartment, and subsequently enter cooler compartment 23 as vegetable compartment return cold air. Thereafter, the vegetable compartment return cold air is directed into cooler compartment 23 after passing through a vegetable compartment return delivery port which makes the lateral length of the vegetable compartment return cold air substantially equivalent to the lateral length of cooling device 7.
  • This configuration avoids decrease in the effective inner volume inside the refrigerator, and also offers an effect of equalization of frosting on cooling device 7. Accordingly, this configuration produces an advantage of excellent energy saving based on improvement of heat exchange efficiency of cooling device 7.
  • FIG. 9 is a cross-sectional configuration view illustrating the interior of a cooler compartment of a refrigerator described in PTL 3.
  • Cooling device 7 is disposed behind freezing compartment 14, and a cold storage compartment is disposed above freezing compartment 14.
  • Cold storage compartment return cold air having cooled the cold storage compartment is introduced into cooler compartment 23 via a return duct disposed on the cooling device side.
  • Flow path 47 is provided between a front face of cooling device 7 and cooling device cover 20 which separates freezing compartment 14 from cooler compartment 23, to disperse cold storage compartment return cold air having a high humidity, and thereby equalize frost adhering to cooling device 7.
  • This configuration disperses frost adhering to cooling device 7. Accordingly, this configuration reduces decrease in cooling efficiency of cooling device 7 caused by clogging with frosting, and lowers the height of a frost layer adhering to cooling device 7. As a result, the efficiency during defrosting also improves.
  • an energy saving effect is produced by equalizing the frosting condition of frost adhering to the cooling device and thereby preventing decrease in the cooling efficiency during frosting.
  • the addition of guide plate 28 increases the cost and decreases the inside volume.
  • guide plate 28 disposed in the vicinity of cooling device 7 has an extremely low temperature, and frost easily remains inside the duct constituted by guide plate 28. Accordingly, there arises a problem that the cooling performance deteriorates due to blocking of the flow path by the remaining frost, in view of the long-term use of the refrigerator for approximately 10 years.
  • guide plate 28 disposed in the vicinity of a lower surface of defrosting heater 32 is influenced by a temperature effect produced by heat generation from defrosting heater 32 during defrosting.
  • the temperature of the surface of defrosting heater 32 increases to approximately 300°C by the heat generated from defrosting heater 32 during defrosting.
  • the temperature of the surface of guide plate 28 provided in the vicinity of defrosting heater 32 increases to approximately 100°C or higher. Accordingly, there arises a problem that a component covering the surface, such as aluminum foil or other metal, is needed to avoid thermal deformation. Thus, the material cost or the man-hour cost increases.
  • the return flow path toward cooling device 7 is configured to extend inside heat insulating partitioning wall 13. Accordingly, the thickness of heat insulating partitioning wall 13 increases due to the necessity of constituting the flow path, and thus problems such as decrease in the inner volume of the refrigerator and a rise of the component cost occur.
  • a refrigerator which improves cooling efficiency and defrosting efficiency during frosting based on equalization of frosting so as to achieve high energy saving performance, and also decreases ineffectual spaces while reducing cost and increasing the storage volume.
  • a refrigerator includes: a freezing compartment sectioned by a heat insulating wall; a cold storage compartment disposed above the freezing compartment; a cooler compartment disposed behind the freezing compartment; and a cooling device disposed in the cooler compartment, and including vertically stacked refrigerant pipes equipped with fins.
  • the refrigerator further includes a cooling device cover that covers a front face of the cooling device, and a cold storage compartment return duct disposed on a side of the cooling device as a duct through which cold air from the cold storage compartment returns toward the cooler compartment.
  • the lateral length of a lower part of the refrigerant pipes of the cooling device is shorter than the lateral length of an upper part of the refrigerant pipes.
  • the refrigerator of the present invention having this configuration, flow path pressure losses decrease by enlargement of a space of a portion to which inside cold air returns. Accordingly, cooling efficiency improves, and simultaneously dispersion of a frosting portion is achievable.
  • This configuration prevents performance deterioration caused by frost, and improves defrosting efficiency based on dispersion of frost, even under high-humidity conditions where frosting easily occurs. Accordingly, the refrigerator provided herein can enhance energy saving, and also can secure a sufficient inner volume.
  • FIG. 1 is a perspective view of a refrigerator according to the first exemplary embodiment of the present invention
  • FIG. 2 is a vertical cross-sectional view of the refrigerator according to the first exemplary embodiment of the present invention
  • FIG. 3 is a side cross-sectional view of the surroundings of a cooling device of the refrigerator according to the first exemplary embodiment of the present invention
  • FIG. 4 is a front cross-sectional view of the surroundings of the cooling device of the refrigerator according to the first exemplary embodiment of the present invention.
  • FIG. 5A is a front view of the cooling device of the refrigerator according to the first exemplary embodiment of the present invention
  • FIG. 5B is a side view of the cooling device of the refrigerator according to the first exemplary embodiment of the present invention.
  • FIG. 6 is a perspective view of the cooling device of the refrigerator according to the first exemplary embodiment of the present invention.
  • refrigerator main body 101 is a heat insulating body which includes outer box 124 made of metal (such as iron plate) and opening to the front, inner box 125 made of rigid resin (such as ABS (acrylonitrile butadiene styrene) resin), and rigid urethane foam 126 foamily filling a space between inner box 125 and outer box 124.
  • Cold storage compartment 102 is provided in the upper part of refrigerator body 101.
  • upper freezing compartment 103 Provided below cold storage compartment 102 are upper freezing compartment 103, and ice-making compartment 104 disposed in parallel with upper freezing compartment 103.
  • Lower freezing compartment 105 is provided between vegetable compartment 106 disposed in the lower part of refrigerator body 101, and upper freezing compartment 103 and ice-making compartment 104 disposed in parallel with each other. Front surfaces of upper freezing compartment 103, ice-making compartment 104, lower freezing compartment 105, and vegetable compartment 106 are openably closed by not-shown drawer type doors 103a, 104a, 105a, and 106a, respectively. A front surface of cold storage compartment 102 is openably closed by double-door 102a.
  • the temperature of the inside of cold storage compartment 102 is generally set within a range from 1°C to 5°C with a lower limit of a temperature set immediately above freezing for cold storage.
  • the temperature of the inside of vegetable compartment 106 is often set within a range equivalent to or slightly higher than the range of the inside temperature of cold storage compartment 102, i.e., from 2°C to 7°C. The freshness of leafy vegetables is maintained for a longer period when the temperature of the inside of vegetable compartment 106 is set lower.
  • Both the temperature of the inside of upper freezing compartment 103 and the temperature of the inside of lower freezing compartment 105 are generally set within a range from -22°C to -18°C for frozen storage. However, these temperatures are set to lower temperatures in a range from -30°C to -25°C in some cases, for example, for improvement of frozen storage conditions.
  • each temperature range of cold storage compartment 102 and vegetable compartment 106 is called a cold storage temperature zone.
  • each temperature range of upper freezing compartment 103, lower freezing compartment 105, and ice-making compartment 104 is called a freezing temperature zone.
  • Upper freezing compartment 103 may be a room whose temperature range is switchable between the cold storage temperature zone and the freezing temperature zone as a switching compartment switchable by a damper mechanism or the like.
  • a top surface of refrigerator body 101 is recessed stepwise in the direction toward the rear of the refrigerator, forming machine compartment 119 within the stepwise recess portion.
  • the top surface of refrigerator body 101 is constituted by first top surface 108 and second top surface 109.
  • Machine compartment 119 includes compressor 117, a dryer (not shown) for removing moisture, and a capacitor (not shown).
  • Compressor 117, the dryer, the capacitor, a radiation pipe (not shown) for heat radiation, capillary tube 118, and cooling device 107 are sequentially connected in an annular shape.
  • Refrigerant is sealed into the connection of these components to constitute a freezing cycle.
  • Combustible refrigerant is often used for this refrigerant in view of protection of the environment in recent years.
  • the machine compartment may further include these function components.
  • Cold storage compartment 102 is separated from ice-making compartment 104 and upper freezing compartment 103 by first heat insulating partitioning portion 110. Ice-making compartment 104 is separated from upper freezing compartment 103 by second heat insulating partitioning portion 111. Ice-making compartment 104 and upper freezing compartment 103 are separated from lower freezing compartment 105 by third heat insulating partitioning portion 112.
  • Second heat insulating partitioning portion 111 and third heat insulating partitioning portion 112 are components assembled after foaming of refrigerator body 101. Accordingly, foamed polystyrene is generally used as a heat insulating material of these portions 111 and 112. Alternatively, a rigid urethane foam may be used for increasing heat insulation performance and rigidity. In addition, a vacuum heat insulating material having high heat insulation properties may be inserted to further reduce the thickness of the partitioning structure.
  • Second heat insulating partitioning portion 111 and third heat insulating partitioning portion 112 Reduction of the thicknesses of the shapes of second heat insulating partitioning portion 111 and third heat insulating partitioning portion 112 or elimination of these portions 111 and 112 while leaving sufficient moving areas of the door frames can secure a sufficient cooling flow path, and improve the cooling capability.
  • the interiors of second heat insulating partitioning portion 111 and third heat insulating partitioning portion 112 may be cut out to form a flow path. In this case, the cost decreases as a result of material reduction.
  • Lower freezing compartment 105 is separated from vegetable compartment 106 by fourth partitioning portion 113.
  • Cooler compartment 123 is provided in the rear part of refrigerator body 101.
  • Cooler compartment 123 includes cooling device 107 of a fin and tube type, as a typical example, for generating cold air.
  • Cooling device 107 disposed with the shorter side of cooling device 107 at the top, extends in the up-down direction throughout an area behind lower freezing compartment 105 including the rear regions of second partitioning portion 111 and third partitioning portion 112 corresponding to heat insulating partitioning walls.
  • Cooling device cover 120 for covering cooling device 107 is disposed on the front face of cooler compartment 123.
  • Cooling device cover 120 includes cold air return port 135 through which cold air having cooled lower freezing compartment 105 returns toward cooler compartment 123.
  • Cooling device 107 is made of aluminum or copper.
  • Cooling device cover 120 is constituted by front cover 137 on the lower freezing compartment 105 side, and rear cover 138 on the cooling device 107 side.
  • Metal heat transfer promoting member 140 is disposed on the cooling device 107 side of rear cover 138.
  • Heat transfer promoting member 140 according to this exemplary embodiment is made of aluminum foil having a thickness t of 8 ⁇ m for heat transfer promotion during defrosting in consideration of cost.
  • the dimension of heat transfer promoting member 140 in the up-down direction corresponds to the dimension from the lower end to the upper end of cooling device 107, and the dimension of heat transfer promoting member 140 in the left-right direction is a relatively large dimension in a range up to a length of approximately 15 mm larger than the length between fins of cooling device 107.
  • Heat transfer promoting member 140 attached to rear cover 138 promotes heat transfer during defrosting to improve the defrosting efficiency and offer defrosting time reduction effect.
  • Aluminum foil may be further disposed on inner box 125 behind cooling device 107 for providing further effect.
  • heat transfer promoting member 140 is formed by an aluminum plate having a larger thickness than the thickness of the aluminum foil, or material having higher heat conductivity (such as copper) than the heat conductivity of aluminum, the heat transfer promotion effect further increases.
  • Cold air supply fan 116 is disposed in the vicinity of cooling device 107 (such as in an upper space) for supplying cold air generated by cooling device 107 toward the respective storage compartments of cold storage compartment 102, ice-making compartment 104, upper freezing compartment 103, lower freezing compartment 105, and vegetable compartment 106 by forced convention cooling.
  • Glass-tube heater 132 is disposed below cooling device 107 as a defrosting heater for removing frost adhering to cooling device 107 and cold air supply fan 116 during cooling.
  • Heater cover 133 for covering glass-tube heater 132 is disposed above glass-tube heater 132.
  • Heater cover 133 has a dimension equivalent to or larger than the diameter of the glass-tube, and equivalent to or larger than the lateral length of the glass-tube so as to avoid generation of abnormal noise which is generated when drops of water falling from cooling device 107 during defrosting directly drop on the surface of the high-temperature glass-tube of glass-tube heater 132.
  • Drain pan 134 disposed below glass-tube heater 132 is a portion integrally formed with an upper surface of fourth partitioning portion 113 as a freezing compartment lower surface which receives defrosted water falling as melted frost after adhesion to cooling device 107.
  • Protrusion 136 is provided on drain pan 134 formed integrally with the upper surface of fourth partitioning portion 113. Protrusion 136 protrudes from the freezing compartment lower surface toward the inside of the refrigerator to catch and fix the lower part of cooling device cover 120. Protrusion 136 is disposed between a lower end of cold air return port 135 and glass-tube heater 132. In this arrangement, red heat into the refrigerator becomes invisible. Moreover, protrusion 136 lies behind the lower end of the cold air return port of cooling device cover 120 as viewed from the inside of the refrigerator, so that the appearance is good and the external appearance is improved.
  • refrigerant used in a freezing cycle is isobutane as combustible refrigerant having a small global warming potential in view of protection of the global environment.
  • Isobutane as hydrocarbon has a specific gravity approximately twice larger than that of air at the normal temperature and under the atmospheric pressure (2.04 under 300K). Accordingly, the refrigerant filling amount decreases in comparison with the conventional freezing cycle, and cost reduction is achievable. Moreover, in case of leakage of combustible refrigerant, the leakage amount becomes smaller, and safety further increases.
  • isobutane is used as the refrigerant, and the maximum temperature of the glass-tube surface as an outer case of glass-tube heater 132 during defrosting is regulated for the purpose of explosion proof.
  • a double-layered glass-tube heater having a double-layered glass-tube is adopted for reducing the temperature of the glass-tube surface of glass-tube heater 132.
  • a component having high radiation capability such as aluminum fin
  • the glass-tube may be constituted by a single-layer pipe for reduction of the external dimensions of glass-tube heater 132.
  • a pipe heater in tight contact with cooling device 107 may be used as means for increasing efficiency during defrosting together with glass-tube heater 132.
  • cooling device 107 is efficiently defrosted by utilizing direct heat transfer from the pipe heater.
  • frost adhering to drain pan 134 and cold air supply fan 116 around cooling device 107 is melted by glass-tube heater 132.
  • This configuration decreases the defrosting time, thereby enhancing energy saving and reducing an inside temperature rise produced during the defrosting time.
  • Cooling of the refrigerator starts with actuation of compressor 117 when the inside temperature of lower freezing compartment 105 increases to a start temperature of a freezing compartment sensor (not shown) or higher as a result of entrance of heat from the outside air or opening and closing of the doors.
  • High-temperature and high-pressure refrigerant delivered from compressor 117 is cooled and liquefied particularly within the radiation pipe (not shown) disposed in outer box 124 by heat exchange with the air outside outer box 124 and rigid urethane foam 126 within the refrigerator in the course for finally reaching the dryer (not shown) disposed in machine compartment 119.
  • the pressure of the liquefied refrigerant is reduced by capillary tube 118, and the resultant refrigerant is introduced into cooling device 107 for heat exchange with inside cold air around cooling device 107.
  • the cold air after heat exchange is supplied into the refrigerator by cold air supply fan 116 disposed in the vicinity of the cold air to cool the inside of the refrigerator. Thereafter, the refrigerant is heated and gasified, and returns to compressor 117.
  • the inside of the refrigerator is cooled to such a level that the temperature of the freezing compartment sensor (not shown) becomes a stop temperature or lower, the operation of compressor 117 stops.
  • Cold air supply fan 116 may be directly disposed on inner box 125, or may be disposed on second partitioning portion 111 assembled after foaming for manufacturing by component block machining for the purpose of reducing the manufacturing cost.
  • a diffuser (not shown) constituted by front cover 137 is disposed in front of cold air supply fan 116 so that air with a high static pressure from cold air supply fan 116 can be delivered into the refrigerator without losses.
  • refrigerators of a type which increases the volume by enlarging the inside case dimensions of lower freezing compartment 105 have been available on the market in view of the inside volume and with the tendency of more frequent use of frozen foods.
  • cold air generated by cooling device 107 is initially supplied by cold air supply fan 116 in the vicinity of the cooling device toward cold storage compartment 102, upper freezing compartment 103, and lower freezing compartment 105.
  • Cold air supplied via cooling device cover 120 circulates in upper freezing compartment 103 and lower freezing compartment 105, and returns through cold air return port 135 formed in the lower part of cooling device cover 120 toward cooler compartment 123.
  • cold air supplied toward cold storage compartment 102 is controlled in accordance with opening and closing of the damper (not shown) so as to equalize the temperature of cold air with the inside temperature. After passing through the damper, the cold air is supplied to cold storage compartment 102, and circulates in cold storage compartment 102. Then, the cold air after circulation flows through cold storage compartment return duct 129 extending through the side of the cooling device, and returns to cooler compartment 123.
  • Vegetable compartment 106 receives a part of cold air supplied to cold storage compartment 102.
  • the separated part of cold air flows through a vegetable compartment delivery duct (not shown) extending through the side of cooling device 107, and enters vegetable compartment 106.
  • the cold air circulates in vegetable compartment 106 for cooling, and returns to cooler compartment 123.
  • a part of cold air supplied for cooling cold storage compartment 102 is separated as a part for cooling vegetable compartment 106.
  • vegetable compartment 106 may be individually cooled by using an exclusively used damper for vegetable compartment cooling.
  • a cooler compartment is disposed behind a freezing compartment, so that a duct is required to return cold air from a cold storage compartment disposed on the upper side toward the cooler compartment.
  • the duct is an ineffectual space, and therefore is generally disposed on the cooler compartment side for preventing decrease in the inner volume.
  • cold storage compartment return cold air 127 having a high humidity enters from the side of cooling device 107, so that equalization of frosting is difficult. Accordingly, a problem of uneven frosting on cooling device 107 is arising.
  • cooling device 107 is of a typical fin and tube type similarly to cooling device 107 generally adopted, as cooling device 107 where refrigerant pipes 145 equipped with fins 146 are vertically stacked.
  • Cooling device 107 includes 30 refrigerant pipes 145 disposed in 10 steps substantially in the up-down direction, and in 3 lines in the front-rear direction.
  • the lateral length of refrigerant pipes 145 of cooling device 107 in the lower part is smaller than the lateral length of refrigerant pipes 145 in the upper part.
  • the lateral length of refrigerant pipes 145 in this context refers to a dimension of refrigerant pipes 145 in the left-right direction as viewed from the front of the refrigerator, i.e., a length of refrigerant pipes 145.
  • frost adhering to cooling device 107 gathers on a flow inlet through which return cold air enters cooling device 107 from the inside of the refrigerator.
  • frost easily adheres to a portion through which cold storage compartment return cold air 127 enters cooling device 107 from cold storage compartment 102 having a high humidity via cold storage compartment return duct 129.
  • the lateral length of the lower portion of refrigerant pipes 145 is smaller than the lateral length of the upper portion of refrigerant pipes 145, flow path blocking caused by adhesion and growth of frost is prevented.
  • the lateral length of refrigerant pipes 145 in the inlet portion from cold storage compartment return duct 129 into cooling device 107 is shortened, and thus flow path losses (ventilation resistance) produced by enlargement of the space of the inlet portion decreases. Accordingly, circulation air amount increases by the decrease in ventilation resistance of return cold air, and the heat exchange amount rose at cooling device 107 increases the evaporating temperature. As a result, the operation efficiency of the freezing cycle improves and thus energy saving is achievable.
  • a wider range of cold storage compartment return cold air 127 can exchange heat with cooling device 107.
  • K is a coefficient of overall heat transfer
  • A is a heat transfer area
  • ⁇ T is a temperature difference between the cooling device and passing air.
  • frost grows, heat exchange efficiency between cooling device 107 and circulating cold air lowers to a level insufficient for cooling the inside of the refrigerator, causing slow cooling or no cooling in the final stage. Accordingly, periodical defrosting of the refrigerator is needed to remove frost adhering to cooling device 107.
  • defrosting is automatically executed in a similar manner after an elapse of a certain period from the start of operation of the refrigerator.
  • defrosting operations of compressor 117 and cold air supply fan 116 are stopped, and glass-tube heater 132 corresponding to a defrosting heater is energized.
  • the temperature of cooling device 107 increases in accordance with melting of frost which adheres to refrigerant staying inside cooling device 107 or adheres to cooling device 107 while generally undergoing a sensible heat change from -30°C to 0°C, a latent heat change at 0°C, and a sensible heat change from 0°C to a higher temperature.
  • a defrosting sensor (not shown) is provided on cooling device 107 to stop energization of glass-tube heater 132 when the temperature of cooling device 107 reaches a predetermined temperature. According to this exemplary embodiment, energization of glass-tube heater 132 is stopped when the defrosting sensor detects 10°C.
  • energization of glass-tube heater 132 makes the temperature of the glass-tube surface high, whereby radiation heat thus produced melts frost adhering to cooling device 107, drain pan 134, and cold air supply fan 116 around cooling device 107 in the surroundings of the cooling device, so as to refresh cooling device 107.
  • the temperature of the defrosting sensor (not shown) does not sufficiently increase during defrosting due to the effect of the outside air even after sufficient removal of frost on cooling device 107, and the defrosting time tends to increase.
  • control for ending defrosting after an elapse of a certain period or longer may be combined depending on the condition of the sensible heat change from 0°C to a higher temperature. This control prevents temperature increase caused by unnecessary heater input or radiation heat into the refrigerator, and temperature increase caused by cooling stop during defrosting, the temperature increases occurring when the defrosting time becomes longer due to insufficient temperature increase of cooling device 107 under the condition of the low-temperature outside air even after sufficient defrosting.
  • cooling capability of cooling device 107 gradually lowers by the effect of frost accumulating between respective executions of defrosting.
  • fins 146 are thinned out in an area above refrigerant pipes 145 having the reduced lateral length and disposed at the inlet portion for cold air entering from cold storage compartment return duct 129 into cooling device 107, i.e., a portion to which frost easily adheres.
  • This configuration not only lowers the ventilation resistance of return cold air to increase the circulation air amount, but also reduces closure of the flow path caused by frost during frosting to prevent performance deterioration during frosting and improve the frosting resistance performance.
  • thinning of fins 146 in the flow direction of cold air further lowers the ventilation resistance and increases the circulation air amount, and also reduces closure of the flow path caused by frosting and offers an advantage of further preventing performance deterioration during frosting.
  • Fins 146 of cooling device 107 are separate fins on vertically stacked refrigerant pipes 145.
  • a step for attaching the fins is needed during the manufacturing step of cooling device 107.
  • fins formed into one piece body in the up-down direction may be adopted. This configuration reduces the number of fins attached to the cooling device, and improves productivity by reduction of man-hour. Accordingly, cost reduction is achievable.
  • Refrigerant pipes 145 of cooling device 107 are of a type called bear pipes having unprocessed inner sides. Accordingly, grooved pipes may be used, for example, so as to increase heat conductivity inside the pipes.
  • the grooved pipes are pipes in which straight grooves or spiral grooves are formed, for example. When the grooved pipes are used, the performance of the cooling device improves, whereby energy saving is further enhanced.
  • refrigerant pipes 145 of cooling device 107 are made of an aluminum material.
  • Refrigerant pipes 145 are often made of aluminum in view of cost reduction demanded as a result of a recent rise of material cost.
  • copper may be used as material of refrigerant pipes 145.
  • This alternative configuration improves heat conductivity, thereby increasing heat exchange efficiency between the inside and outside of refrigerant pipes 145. Accordingly, energy saving is further enhanced.
  • Cold storage compartment return duct opening upper end 143 is disposed above cooling device lower end 144 of cooling device 107 at an opening of cold storage compartment return duct 129 formed on the side of cooling device 107 for entrance into cooling device 107.
  • This configuration enlarges the opening of cold storage compartment return duct 129, thereby reducing flow path losses at the entrance into cooling device 107. Accordingly, cooling performance mainly for cold storage compartment 102 improves as a result of increase in the circulation air amount, and energy saving is enhanced as a result of increase in the heat exchange efficiency.
  • positioning of cold storage compartment return duct opening upper end 143 above cooling device lower end 144 allows easy introduction of cold storage compartment return cold air 127 into cooling device 107.
  • a part of the side of cooling device 107 is utilized as a flow path. This configuration reduces ineffectual spaces, and secures a sufficient inside volume.
  • Cooling device cover 120 includes freezing compartment cold air return port 135 disposed in the lower part of cooling device cover 120. Since freezing compartment cold air return port upper end 139 is disposed above cooling device lower end 144, return cold air having circulated inside the refrigerator has a large heat exchange area for heat exchange with cooling device 107. Accordingly, the heat exchange amount provided by cooling device 107 increases, whereby the capability of cooling device 107 improves.
  • Improvement of the heat exchange amount of cooling device 107 and increase in the circulation air amount can decrease the time for cooling the inside of the refrigerator.
  • the amount of frosting on the cooling device decreases by reduction of the cooling operation time. Accordingly, the defrosting cycle of the cooling device increases, and both the number of times of input of glass-tube heater 132, and input required for cooling the inside of the refrigerator after temperature increase inside the refrigerator caused by defrosting decrease. As a result, energy saving is further enhanced.
  • the heat exchange area of cooling device 107 increases based on improvement of the flow path, the area of cooling device 107 to which frost adheres enlarges accordingly. In this case, deterioration of the cooling capability during frosting is avoidable. As a result, the period from the start of operation of the refrigerator to the time requiring defrosting can be prolonged. In this case, both the number of times of input of glass-tube heater 132, and input required for cooling the inside of the refrigerator after increase in the inside temperature as a result of defrosting can decrease, and thus further energy saving is achievable.
  • Air direction guiding members 122 are provided at cold air return port 135. Air direction guiding members 122 are formed at intervals of 5 mm, aiming at prevention of insertion of fingers, and securing strengths of a metal mold and cooling device cover 120. Air direction guiding members 122 are similarly angled upward from the inside of the refrigerator toward the cooling device.
  • the upward inclination of air direction guiding members 122 not only lowers the ventilation resistance of a blow-in flow path for return cold air, but also equalizes flow. Accordingly, the cooling efficiency improves, and energy saving is further enhanced.
  • the center of glass-tube heater 132 is disposed above fourth partitioning portion 113 constituting a freezing compartment bottom base surface.
  • This configuration makes the shape of drain pan 134 formed integrally with the freezing compartment bottom base surface substantially horizontal, thereby reducing the ineffectual space occupied by glass-tube heater 132. Accordingly, the inner volume increases.
  • the depth of drain pan 134 is small as in this configuration, the metal mold cost required in molding constituent components lowers. Accordingly, cost reduction is achievable.
  • fourth partitioning portion 113 constituting the freezing compartment base surface is a separate part. Forming only fourth partitioning portion 113 in a sub step, and inserting and assembling fourth partitioning portion 113 into the inner box in a post process as adopted in this exemplary embodiment is a method capable of achieving sharing of work processes and increasing production efficiency. Rather than adopting this constitution, a configuration which forms fourth partitioning portion 113 from the inner box may be employed. In this case, such a method may be used which extends an ABS sheet corresponding to the material of inner box 125 by a forming machine, and forms an integrally molded component including inner box 125 and the partitioning portion. This method is often used when inner box 125 has a small depth.
  • this method is also applicable to production of a refrigerator having a large depth for the purpose of thickness equalization achievable by extension of a sheet.
  • this method is employed, material cost, job labor, management cost, transportation cost, and others for producing the partitioning portions decrease, wherefore considerable cost reduction is achievable.
  • production efficiency improves, whereby the overall product cost lowers.
  • a refrigerator includes: a freezing compartment sectioned by a heat insulating wall; a cold storage compartment disposed above the freezing compartment; a cooler compartment disposed behind the freezing compartment; and a cooling device disposed in the cooler compartment, and including vertically stacked refrigerant pipes equipped with fins.
  • the refrigerator further includes a cooling device cover that covers a front face of the cooling device, and a cold storage compartment return duct disposed on a side of the cooling device, and configured to guide cold air from the cold storage compartment to the cooler compartment.
  • the lateral length of a lower part of the refrigerant pipes of the cooling device is shorter than the lateral length of an upper part of the refrigerant pipes.
  • flow path pressure losses decreases by enlargement of a space of an inlet portion through which return cold air enters the cooling device from the inside of the refrigerator. Accordingly, the circulation air amount increases by reduction of the ventilation resistance of the return cold air, and the heat exchange amount rose at cooling device increases the evaporating temperature. As a result, the operation efficiency of the freezing cycle improves and thus energy saving is achievable.
  • the lateral length of the lower portion of the refrigerant pipes of the cooling device is shortened, and thus closure caused by frost is difficult to occur even under the conditions of the summer seasons where high humidity and frequent opening and closing of doors allow easy adhesion of frost to the refrigerant pipes and the fins. Accordingly, equalization of the frosting portions of the cooling device is achievable through dispersion of the frosting portions.
  • a short-lateral length portion of the refrigerant pipes may correspond to an inlet portion through which cold air from the cold storage compartment return duct enters the cooling device.
  • Frosting occurs by initial heat exchange with the refrigerant pipe disposed at the entrance of the inlet portion of the cooling device through which return cold air enters, and by subsequent dehumidification.
  • frost particularly adheres to the portion through which cold storage compartment return cold air enters from the cold storage compartment having a high humidity through the cold storage compartment return duct.
  • the refrigerant pipe is shortened at the position through which cold storage compartment return cold air enters, flow path blocking caused by adhesion and growth of frost is avoidable.
  • the fins of the refrigerant pipes may be thinned out above the short-lateral length portion of the refrigerant pipes.
  • the cooling device includes the vertically stacked refrigerant pipes equipped with the fins.
  • the downstream part of the return cold air does not exchange heat when the flow path is closed by frost on the upstream side.
  • cooling efficiency losses are produced.
  • the fins are thinned out to increase the circulation air amount by reduction of the ventilation resistance of return cold air, and also to avoid performance deterioration during frosting by reduction of closure of the flow path caused by frost during frosting. Accordingly, frosting resistance performance of the cooling device improves.
  • an upper end of an opening of the cold storage compartment return duct may be disposed above a lower end of the cooling device.
  • This configuration enlarges the opening of the cold storage compartment return duct, thereby further reducing flow path losses at the entrance into cooling device. Accordingly, cooling performance mainly for the cold storage compartment improves as a result of increase in the circulation air amount, and energy saving is enhanced as a result of increase in the heat exchange efficiency.
  • positioning of the upper end of the cold storage compartment return duct opening above the lower end of the cooling device allows easy introduction of cold storage compartment return cold air into the cooling device.
  • a part of the side of the cooling device is utilized as a flow path. Accordingly, this configuration reduces ineffectual spaces, and secures a sufficient inside volume.
  • a freezing compartment cold air return port through which cold air from the freezing compartment returns to the cooler compartment may be provided in a lower part of the cooling device cover, and an upper end of the freezing compartment cold air return port may be disposed above a lower end of the cooling device.
  • This configuration enlarges the area of return cold air for heat exchange with the cooling device.
  • the circulation air amount increases by reduction of the ventilation resistance of return cold air, and the heat exchange amount raised thereby at the cooling device increases the evaporating temperature.
  • the operation efficiency of the freezing cycle improves and thus energy saving is achievable.
  • increase in the heat exchange amount by the cooling device and the increase in the circulation air amount can decrease the time for cooling the inside of the refrigerator.
  • the amount of frosting on the cooling device decreases with reduction of the cooling operation time. Accordingly, the defrosting cycle of the cooling device can be prolonged, and both the number of times of input of the defrosting heater, and input required for cooling the inside of the refrigerator after increase in the inside temperature as a result of defrosting can decrease. As a result, further energy saving is achievable.
  • the frosting area of the cooling device increases. Accordingly, deterioration of the cooling capability during frosting is avoidable. As a result, the period from the start of operation of the refrigerator to the time for requiring defrosting can be prolonged. In this case, both the number of times of input of the defrosting heater, and input required for cooling the inside of the refrigerator after increase in the inside temperature as a result of defrosting can decrease, and thus further energy saving is achievable.
  • the fins of the refrigerant pipes may be thinned out on the left and right sides of the flow direction of cold air from the cold storage compartment return duct toward the cooling device.
  • Thinning the fins in the flow direction of cold air can further decrease the ventilation resistance of return cold air and increases the circulation air amount.
  • flow path blocking by frost during frosting is reduced particularly for return cold air from the cold storage compartment and the vegetable compartment and thus having a high humidity, and further prevention of performance deterioration during frosting is achievable. Accordingly, the frosting resistance performance further improves. Improvement of the frosting resistance performance requires equalization of frosting on the cooling device. Assuming that the amount of moisture contained in circulating cold air is uniform per unit time, flow path blocking by frosting can be delayed by equalization of frosting on the cooling device.
  • the thickness of frost becomes substantially uniform, and thus defrosting efficiency for melting frost during defrosting improves. Accordingly, the defrosting time decreases.
  • a defrosting glass-tube heater may be provided below the cooling device, and a center height of the glass-tube heater may be positioned above a base bottom surface of the freezing compartment.
  • This configuration makes the shape of a drain pan formed integrally with the base surface of the freezing compartment bottom substantially horizontal, thereby reducing the ineffectual space occupied by the defrosting heater. Accordingly, the inner volume increases. In addition, reduction of the depth of the drain pan decreases the metal mold cost required in molding constituent components.
  • a refrigerator according to the present invention is applicable to a household refrigerator aimed at improvement of energy saving and freezing freshness keeping performance, and enlargement of the inside volume.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Cold Air Circulating Systems And Constructional Details In Refrigerators (AREA)
  • Defrosting Systems (AREA)
EP13838191.8A 2012-09-19 2013-09-19 Réfrigérateur Withdrawn EP2899481A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012205272A JP6089222B2 (ja) 2012-09-19 2012-09-19 冷蔵庫
PCT/JP2013/005525 WO2014045576A1 (fr) 2012-09-19 2013-09-19 Réfrigérateur

Publications (2)

Publication Number Publication Date
EP2899481A1 true EP2899481A1 (fr) 2015-07-29
EP2899481A4 EP2899481A4 (fr) 2016-06-01

Family

ID=50340912

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13838191.8A Withdrawn EP2899481A4 (fr) 2012-09-19 2013-09-19 Réfrigérateur

Country Status (4)

Country Link
EP (1) EP2899481A4 (fr)
JP (1) JP6089222B2 (fr)
CN (1) CN104641190B (fr)
WO (1) WO2014045576A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018205523A1 (de) 2017-04-27 2018-10-31 BSH Hausgeräte GmbH Kühlvorrichtung mit einem Verdampfer

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6405525B2 (ja) * 2014-05-22 2018-10-17 パナソニックＩｐマネジメント株式会社 冷蔵庫
US10184713B2 (en) 2016-01-06 2019-01-22 Electrolux Home Products, Inc. Evaporator shields
CN105737454A (zh) * 2016-04-18 2016-07-06 合肥太通制冷科技有限公司 一种端部中心线平行冷冻翅片蒸发器
CN105758068A (zh) * 2016-04-19 2016-07-13 合肥太通制冷科技有限公司 一种六层垒密降噪除霜翅片蒸发器
CN105674630A (zh) * 2016-04-19 2016-06-15 合肥太通制冷科技有限公司 一种新型无侧板密翅卡位翅片蒸发器
CN106766397A (zh) * 2017-02-13 2017-05-31 合肥美的电冰箱有限公司 翅片式蒸发器和制冷设备
CN110285630B (zh) * 2019-02-26 2020-03-06 青岛海尔电冰箱有限公司 冰箱
CN116928955A (zh) * 2022-03-31 2023-10-24 青岛海尔电冰箱有限公司 用于冰箱的内胆以及具有其的冰箱

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA2119983C (fr) * 1993-03-25 1999-05-11 Mitsuaki Oshima Systeme de communication
JPH07270028A (ja) 1994-03-31 1995-10-20 Toshiba Corp 冷蔵庫
JPH11183011A (ja) 1997-12-18 1999-07-06 Hitachi Ltd 冷蔵庫
JP2000205737A (ja) * 1999-01-19 2000-07-28 Mitsubishi Electric Corp 冷蔵庫
JP2002318055A (ja) * 2001-04-20 2002-10-31 Fujitsu General Ltd 冷蔵庫
KR100431348B1 (ko) * 2002-03-20 2004-05-12 삼성전자주식회사 냉장고
KR20060016738A (ko) * 2003-06-23 2006-02-22 에어 오퍼레이션 테크놀로지스 가부시키가이샤 냉각 장치
CN100513950C (zh) * 2005-05-12 2009-07-15 松下电器产业株式会社 带除霜装置的冷却器和具有带除霜装置的冷却器的冰箱
JP2011038714A (ja) * 2009-08-12 2011-02-24 Hitachi Appliances Inc 冷蔵庫
EP2450649B1 (fr) * 2009-08-26 2016-01-06 Panasonic Intellectual Property Management Co., Ltd. Réfrigérateur
JP5402779B2 (ja) * 2010-03-30 2014-01-29 パナソニック株式会社 冷蔵庫
JP5447438B2 (ja) * 2011-05-24 2014-03-19 三菱電機株式会社 冷蔵庫
JP5267614B2 (ja) * 2011-05-24 2013-08-21 三菱電機株式会社 冷蔵庫

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018205523A1 (de) 2017-04-27 2018-10-31 BSH Hausgeräte GmbH Kühlvorrichtung mit einem Verdampfer

Also Published As

Publication number Publication date
EP2899481A4 (fr) 2016-06-01
JP2014059115A (ja) 2014-04-03
CN104641190B (zh) 2016-12-14
CN104641190A (zh) 2015-05-20
WO2014045576A1 (fr) 2014-03-27
JP6089222B2 (ja) 2017-03-08

Similar Documents

Publication Publication Date Title
EP2899481A1 (fr) Réfrigérateur
KR101260277B1 (ko) 냉장고
EP2762808B1 (fr) Réfrigérateur
KR101306536B1 (ko) 냉장고
JP5507511B2 (ja) 冷蔵庫
JP2013061089A (ja) 冷蔵庫
EP2789940A1 (fr) Réfrigérateur
TWI716636B (zh) 冰箱
JP5436522B2 (ja) 冷凍冷蔵庫
JP6405526B2 (ja) 冷蔵庫
JP5838238B2 (ja) 冷蔵庫
US20220011035A1 (en) Refrigerator
CN112013605B (zh) 冰箱
KR20110016834A (ko) 냉장고
KR102508224B1 (ko) 냉장고
JP6244543B2 (ja) 冷蔵庫
WO2015178025A1 (fr) Réfrigérateur
JP2002130909A (ja) 冷蔵庫
JP2015017737A (ja) 冷蔵庫
US11333422B2 (en) Augmented door bin cooling using a dedicated air duct in a dual-evaporator refrigerator configuration
JP6282255B2 (ja) 冷蔵庫
JP6709348B2 (ja) 冷蔵庫
JP6709346B2 (ja) 冷蔵庫
JP6489767B2 (ja) 冷蔵庫
JP2006078050A (ja) 冷蔵庫

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20150420

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
RA4 Supplementary search report drawn up and despatched (corrected)

Effective date: 20160503

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 1/32 20060101ALI20160426BHEP

Ipc: F25D 21/04 20060101AFI20160426BHEP

Ipc: F25B 39/02 20060101ALI20160426BHEP

Ipc: F28D 1/047 20060101ALI20160426BHEP

Ipc: F28D 21/00 20060101ALI20160426BHEP

Ipc: F25D 17/08 20060101ALI20160426BHEP

Ipc: F25D 21/08 20060101ALI20160426BHEP

17Q First examination report despatched

Effective date: 20170831

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20180814