EP1793186B1 - Réfrigérateur - Google Patents

Réfrigérateur Download PDF

Info

Publication number
EP1793186B1
EP1793186B1 EP07001116.8A EP07001116A EP1793186B1 EP 1793186 B1 EP1793186 B1 EP 1793186B1 EP 07001116 A EP07001116 A EP 07001116A EP 1793186 B1 EP1793186 B1 EP 1793186B1
Authority
EP
European Patent Office
Prior art keywords
tube
heater
evaporator
refrigerator
glass
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.)
Expired - Lifetime
Application number
EP07001116.8A
Other languages
German (de)
English (en)
Other versions
EP1793186A3 (fr
EP1793186A2 (fr
Inventor
Masahiro Nakayama
Yuji Kishinaka
Kiyonori Yamamoto
Akira Yokoe
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 Corp
Original Assignee
Panasonic Corp
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 Corp filed Critical Panasonic Corp
Publication of EP1793186A2 publication Critical patent/EP1793186A2/fr
Publication of EP1793186A3 publication Critical patent/EP1793186A3/fr
Application granted granted Critical
Publication of EP1793186B1 publication Critical patent/EP1793186B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
    • H05B3/00—Ohmic-resistance heating
    • H05B3/40—Heating elements having the shape of rods or tubes
    • H05B3/42—Heating elements having the shape of rods or tubes non-flexible
    • H05B3/44—Heating elements having the shape of rods or tubes non-flexible heating conductor arranged within rods or tubes of insulating material
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05B—ELECTRIC HEATING; ELECTRIC LIGHT SOURCES NOT OTHERWISE PROVIDED FOR; CIRCUIT ARRANGEMENTS FOR ELECTRIC LIGHT SOURCES, IN GENERAL
    • H05B3/00—Ohmic-resistance heating
    • H05B3/40—Heating elements having the shape of rods or tubes
    • H05B3/42—Heating elements having the shape of rods or tubes non-flexible
    • H05B3/48—Heating elements having the shape of rods or tubes non-flexible heating conductor embedded in insulating material
    • H05B3/50—Heating elements having the shape of rods or tubes non-flexible heating conductor embedded in insulating material heating conductor arranged in metal tubes, the radiating surface having heat-conducting fins
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/12—Inflammable refrigerants
    • 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
    • F25D21/14—Collecting or removing condensed and defrost water; Drip trays
    • 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
    • F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
    • F25D2400/04—Refrigerators with a horizontal mullion
    • 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
    • F25D2400/00—General features of, or devices for refrigerators, cold rooms, ice-boxes, or for cooling or freezing apparatus not covered by any other subclass
    • F25D2400/24—Protection against refrigerant explosions

Definitions

  • the present invention relates to defrosting for a refrigerator employing a combustible refrigerant.
  • Fig. 31 shows a vertical sectional view illustrating the essential part of a prior-art refrigerator.
  • refrigerator 1 has freezer compartment 2 and cold-storage compartment 3 therein, and to which, freezer door 4 and storage door 5 are fixed, respectively.
  • Freezer compartment 2 and cold-storage compartment 3 are separated by dividing wall 6.
  • the air in freezer compartment 2 is captured through inlets 7, and the air in cold-storage compartment 3 is captured through inlet 8.
  • Outlet 9 blows cold air into freezer compartment 2.
  • the cold air is circulated by fan 11.
  • Evaporator dividing wall 12 is disposed between freezer compartment 2 and evaporator 10.
  • Glass-tube heater 15 for defrosting has a structure in which a coiled nichrome-wire is covered with a glass tube.
  • Roof 16 protects heater 15 from being directly hit by a drip of melted frost that will give a sputter sound on evaporation.
  • Metallic bottom plate 17 is disposed, in insulation, between dripping pan 13 and heater 15.
  • Accumulator 18 is disposed at the exit of evaporator 10.
  • evaporator 10 When cooling the freezer compartment 2 and cold-storage compartment 3, evaporator 10 is cooled by a refrigerant flowing through evaporator 10. At the same time, fan 11 expels warmed air in freezer compartment 2 through inlet 7, similarly, expels warmed air in cold-storage compartment 3 through inlet 8, into cooling chamber 20. The warmed air is cooled at evaporator 10 by heat exchange, and then supplied through outlet 9 to freezer compartment 2. At the same time, a portion of the cooled air is fed from freezer compartment 2 through a communication opening (not shown) to cold-storage compartment 3.
  • the air that does heat-exchange at evaporator 10 has high moisture due to the air flown from outside into the refrigerator each time door 4 or door 5 is opened, and due to evaporation of moisture from stored foods in both compartments. Therefore, the moisture in the warmed air turns into frost on evaporator 10 where the temperature is lower than the air.
  • Accumulator 18 works to constantly feed refrigerant in cooling cycle operations. In addition, accumulator 18 protects a compressor from damage caused by direct return of liquid refrigerant, or minimizes a flowing noise of the refrigerant.
  • the water is collected into dripping pan 13; the dripping water partly goes directly down into pan 13, and partly hits roof 16 as a guard of heater 15 and then down into pan 13.
  • the water collected in pan 13 is drained through drainage hole 14 to the outside.
  • some of the heat rays radiated from heater 15 toward dripping pan 13 are reflected off bottom plate 17 and then scattered toward evaporator 10.
  • a combustible refrigerant has relatively large latent heat.
  • such a property of the refrigerant invites insufficient defrosting, thereby leaving frost in the pipe arrangement.
  • frost hampers heat transfer, resulting in poor refrigeration.
  • the document GB 2 277 663 discloses a defrosting heater 4 for a refrigerator has caps 8 and lead wires 5 at both ends, which are inserted into waterproof and heat-resisting tubes 16, respectively.
  • the tubes 16 are squeezed against the caps, so that the inner cylindrical surface of one end portion of each of the tubes 16 is in full contact with the outer cylindrical surfaces of the respective cap.
  • the other end portions of the tubes B are held with their openings E faced downwardly, and with the lead wires 5 bent like a U-shaped trap.
  • the document JP 11257831 discloses a refrigerator according to the preamble of claim 1.
  • the present invention addresses the problem above. It is therefore the object to provide a refrigerator equipped with a defrosting means capable of: not only preventing a combustible refrigerant from catching fire even if the defrosting operation is performed in an environment where leakage of the combustible refrigerant occurs at somewhere in the area having the defrosting means, but also improving a poor refrigeration due to residual frost.
  • a refrigerator according to claim 1 is provided in order to solve the above addressed problem.
  • the refrigerator of the present invention contains a refrigeration cycle and a defrosting means.
  • the refrigeration cycle has successive connections of the following elements: a compressor; a condenser; a pressure reduction mechanism; and an evaporator.
  • a combustible refrigerant is sealed in the refrigeration cycle.
  • the defrosting means is formed of a plurality of glass-tube heaters.
  • the structure above can suppress an input for each glass-tube heater when the evaporator and its surroundings are heated by the glass-tube heaters in the defrosting operation. This allows the surface temperature of the glass-tube heater to maintain below a temperature at which the combustible refrigerant can catch fire. As another plus, effective heating on the area having a large amount of frost can provide a uniform defrosting, thereby enhancing the efficiency of defrosting and eliminating residual frost.
  • Fig. 1 shows a schematic view illustrating the refrigeration cycle of a refrigerator in accordance with the first exemplary embodiment.
  • Fig. 2 is a vertical sectional view showing the essential part of the refrigerator of the first exemplary embodiment.
  • Fig. 3 is a schematic view illustrating the essential part of the refrigerator shown in Fig. 2 .
  • Fig. 4 is a sectional view of a glass-tube heater, with the essential part enlarged, of the refrigerator shown in Fig. 2 .
  • refrigeration cycle 301 has successive connections of the following elements: compressor 302, condenser 303, pressure reduction mechanism 305, and evaporator 306.
  • compressor 302 condenser 303
  • pressure reduction mechanism 305 pressure reduction mechanism 305
  • evaporator 306 evaporator 306.
  • a combustible refrigerant is sealed in refrigeration cycle 301.
  • defrosting means 307 is disposed close to evaporator 306.
  • the refrigerator of the first embodiment contains two glass-tube heaters 19a and 19b as an example of the defrosting means shown in Fig. 1 .
  • Each heater has a structure in which heater wire 24 made of metallic material, such as nickel chrome, is formed into a spiral shape and then inserted in a glass tube.
  • Heaters 19a and 19b are placed below evaporator 1 in a side-by-side arrangement; more specifically, heater 19a is disposed close to lowermost pipe 21 of evaporator 10.
  • glass-tube heaters 19a and 19b may often be referred to glass-tube heater 19 as a unit.
  • cooling chamber 20 As shown in Fig. 2 , evaporator 10, fan 11, roof 16, and glass-tube heater 19 are disposed.
  • a pair of supporting members 22, each one is disposed at each end of heater 19, fixes heater 19a together with heater 19b.
  • fan 11 stops to remove frost from evaporator 10, and a refrigerant stops flowing through evaporator 10. After that, the electric current is supplied through glass-tube heater 19 for generating heat to melt the frost on evaporator 10.
  • a defrost-completion detector (not shown) detects the completion of defrosting, the current-supply to heater 19 is stopped, so that defrosting operation completes.
  • heater 19a which is located near by lowermost pipe 21, encourages to evaporate the high amounts of the combustible refrigerant in the pipe at the lower section of evaporator 10.
  • the combustible refrigerant is changed into hot gas, moving up toward the pipes in the upper section of evaporator 10.
  • the pipes in the upper section of evaporator 10 are kept cool due to the frost on evaporator 10.
  • the hot gas of the refrigerant moved from the lower section is now cooled by the pipes and the fan and changed into liquid. For turning into liquid, the hot gas radiates the heat toward frost deposited on the upper section of evaporator 10. Defrosting is thus carried out.
  • the gaseous combustible refrigerant due to its high latent heat, radiates a large amount of heat required for changing into liquid, whereby the defrosting is accelerated. In this way, a thermo-siphon effect facilitates the defrosting of evaporator 10.
  • direct radiation of the heat generated from heater 19 melts the frost on evaporator 10 and peripheral components and walls. Besides, the ambient air warmed up by the heat moves around. All the actions above contribute to a thorough defrosting of evaporator 10.
  • second glass-tube heater 19b is disposed, next to first glass-tube heater 19a, below evaporator 10. That is, by virtue of the structure having plural heaters, the application of an electric current per heater can be smaller than that in the prior-art structure. This allows the surface temperature of a glass-tube heater to keep lower than the ignition temperature of the combustible refrigerant; in the case of employing isobutane as the refrigerant, the surface temperature of the heater can be kept below 460 °C. Generally, an amount of radiation is proportional with the surface area of a hot body. Compared to a structure with a single heater, a structure formed of a plurality of heaters 19 has larger surface area, accelerating heat-transfer to evaporator 10. Furthermore, the structure with plural heaters can effectively heat the lower section of the evaporator having high amounts of frost, ensuring a uniform defrosting. This enhances defrosting efficiencies, eliminating residual frost.
  • thermo-siphon effect of the combustible refrigerant in the pipes, and heat directly radiated from heaters 19a and 19b contribute to uniform defrosting the entire surfaces of evaporator 10, enhancing defrosting efficiencies, as well as eliminating residual frost.
  • disposing a plurality of glass-tube heaters (19a, 19b) can save the operating time per heater 19a (19b); accordingly, the radiating period of each heater is shortened. This ensures that the surface temperature of the heaters 19a and 19b is kept enough below the ignition temperature of the combustible refrigerant.
  • a pair of supporting members holds glass-tube heaters 19a and 19b so as to be an integrated structure, providing not only a simple structure but also easy assembling work.
  • the refrigerator of the first exemplary embodiment provides a structure having a plurality of glass-tube heaters for defrosting the evaporator.
  • the temperature of each glass-tube heater during the passage of an electric current can be kept lower than the ignition temperature of the combustible refrigerant. That is, defrosting can be carried out at temperatures below the ignition temperature of the refrigerant, without degradation in the efficiency of defrosting.
  • the refrigerator of the embodiment not only can prevent a combustible refrigerant from catching fire even if the defrosting operation is performed in an environment where leakage of the combustible refrigerant occurs at somewhere in the area having defrosting means, but also can improve a poor refrigeration due to residual frost.
  • Fig. 5 is a vertical sectional view showing the essential part of a refrigerator of the second exemplary embodiment.
  • the second embodiment differs from the first embodiment in the following points.
  • first glass-tube heater 25a is disposed at a position lower than evaporator 10; on the other hand, second glass-tube heater 25b is disposed at a position higher than evaporator 10 and close to accumulator 18.
  • the combustible refrigerant liquid in evaporator 10 flows down, by its own weight, to lowermost pipe 21 that collects higher amounts of the refrigerant than other pipes in evaporator 10.
  • heat generated from glass-tube heater 25a heats up the combustible refrigerant collected in the lowermost pipe and its vicinity.
  • the combustible refrigerant is changed into hot gas, moving up toward the pipes disposed in the upper section of evaporator 10.
  • the hot gas of the refrigerant carried from the lower section is now cooled and again changed into a liquid by the pipes and radiation fins of the evaporator.
  • the hot gas radiates the heat toward frost deposited on the upper section of evaporator 10.
  • the refrigerant liquid flows down to lowermost pipe 21. In this way, repeating the thermo-siphoned cycle thus carries out defrosting of the evaporator.
  • evaporator 10 Due to structural difference in evaporator 10, an amount of the combustible refrigerant may not leave accumulator 18 for lowermost pipe 21. Such a position where the refrigerant tends to stay-on will be a slow-defrosted area.
  • heater 25b disposed above evaporator 10 can heat up the stay-on position, thereby shortening the defrosting time. In this way, the structure can uniformly remove frost from the evaporator and its surroundings, thereby enhancing the efficiency of defrosting and therefore eliminating residual frost. Furthermore, defrosting completes in a shortened operation-time of the glass-tube heater, which contributes to a power saving.
  • the glass-tube heaters have an opposing location via the evaporator; one is disposed above, the other is disposed under the evaporator.
  • the arrangement of the heaters allows the evaporator to be uniformly heated up from the top and the bottom.
  • the structure having plural heaters allows an individual heater to have small heating value, thereby keeping the surface temperature of the heater below the ignition temperature of the combustible refrigerant.
  • the uniform defrosting enhances the efficiency of defrosting, contributing to energy conservation.
  • the accumulator which is located above the evaporator, can be properly defrosted without residual frost.
  • the refrigerator of the embodiment not only can prevent a combustible refrigerant from catching fire even if the defrosting operation is performed in an environment where leakage of the combustible refrigerant occurs at somewhere in the area having the defrosting means, but also can improve a poor refrigeration due to residual frost.
  • a slow-defrosting area may vary according to the structure of an evaporator.
  • the second glass-tube heater can be disposed close to the area where frost persists.
  • the glass-tube heaters can be placed in an opposite arrangement in a widthwise direction of the evaporator; one is in front of, and the other is at rear of the evaporator.
  • the arrangement can protect glass-tube heater 25a against direct dripping-down of melted frost from evaporator 10. Thereby, roof 16 can be removed from the structure.
  • Fig. 6 is a vertical sectional view showing the essential part of a refrigerator of the third exemplary embodiment.
  • the structure of the third embodiment differs from those of the aforementioned embodiments in the following point.
  • first glass-tube heater 26a is disposed below evaporator 10; on the other hand, second glass-tube heater 26b is disposed at an intermediate position in evaporator 10.
  • an electric current is fed through heater 26b, as well as heater 26a. Most of the heat from heater 26a by the passage of electric current directly heats up, as radiant heat, evaporator 10.
  • the hot surface of the glass-tube heater 26a warms up the ambient air to go upward, as an upward-moving stream, along evaporator 10.
  • the upward-moving hot air warms up frosted evaporator 10 from the bottom toward the upper sections.
  • heat radiated from heater 26b disposed within evaporator 10 heats up a low-temperature area in the mid toward the upper sections.
  • heater 26a Of radiant heat from heater 26a disposed below evaporator 10, upwardly radiated heat directly warms up evaporator 10; while downwardly radiated heat reaches the evaporator as reflection off dripping pan 13.
  • heater 26b since it is located inside evaporator 10, can directly heat up evaporator 10 in upward and downward (or frontward and backward) directions.
  • the arrangement of the heaters can provide the evaporator with a rapid and uniform defrosting, allowing the surface temperature of the glass-tube heaters to keep below the ignition temperature of the combustible refrigerant.
  • the refrigerator of the embodiment not only can prevent a combustible refrigerant from catching fire even if the defrosting operation is performed in an environment where leakage of the combustible refrigerant occurs at somewhere in the area having the defrosting means, but also can improve a poor refrigeration due to residual frost.
  • Fig. 7 is a vertical sectional view showing the essential part of a refrigerator of the fourth exemplary embodiment.
  • the structure of the fourth embodiment differs from those of the aforementioned embodiments in the following points.
  • first glass-tube heater 27a is disposed below evaporator 10; on the other hand, second glass-tube heater 27b is disposed either in front of or behind of evaporator 10.
  • Evaporator 10 has indent 28 at a part of the fins to place heater 27b.
  • heater 27a disposed below evaporator 10 has a capacity larger than that of heater 27b that is located higher than heater 27a.
  • the defrosting operation begins with the application of an electric current to heaters 27a and 27b.
  • Heater 27a which is disposed below evaporator 10, defrosts the evaporator upwardly from the bottom.
  • heater 27b disposed at the front (or the behind) of evaporator 10 warms up a low-temperature area - the area having a slow-rise in temperature despite of the thermo-siphon effect in evaporator 10 - and effectively removes the frost from the surface of evaporator 10.
  • heater 27a can properly defrost the bottom of evaporator 10 having a large amount of frost, thereby enhancing the defrost efficiency.
  • the quick and uniform defrosting can suppress the surface temperature of glass-tube heaters 27a and 27b below the ignition temperature of the combustible refrigerant.
  • the refrigerator of the embodiment not only can prevent a combustible refrigerant from catching fire even if the defrosting operation is performed in an environment where leakage of the combustible refrigerant occurs at somewhere in the area having the defrosting means, but also can improve a poor refrigeration due to residual frost.
  • Indent 28 is formed at a part of the fins of evaporator 10 so as to accept heater 27b that is placed either in the front of or behind the evaporator.
  • the arrangement can minimize waste space caused by installing heater 27b.
  • the arrangement - regardless of whether heater 27b is disposed at the front, or at the behind of the evaporator - is effective in protecting heater 27b from a drip of melted frost. Accordingly, the structure can do away with the need to additional installment of the roof, which can be a barrier to air course when fan 11 is in operation.
  • Fig. 8 is a vertical sectional view showing the essential part of a refrigerator of the fifth exemplary embodiment.
  • the structure of the fifth embodiment differs from those of the aforementioned embodiments in the following points.
  • temperature sensor 29 detects the surface temperature of glass-tube heater 19.
  • Controller 30 is responsible for ON/OFF controlling the application of voltage to heater 19.
  • Heater 19 has heating wire 31 therein.
  • R600a isobutane
  • controller 30 performs ON/OFF control of the application of voltage to heater 19, thereby keeping the surface temperature of heater 19 below the ignition temperature of the combustible refrigerant.
  • the defrosting is thus performed with reliable thermal control.
  • R600a isobutane
  • the surface temperature of heater 19 is kept below the ignition temperature, for example, 450 °C or lower while current is applied to the heater in defrosting.
  • the refrigerator of the embodiment can prevent a combustible refrigerant from catching fire even if the defrosting operation is performed in an environment where leakage of the combustible refrigerant occurs at somewhere in the area having the defrosting means.
  • the risk of catching fire can be avoided even in the cases that undesired high voltage is applied to the glass-tube heater for some reasons, or that unnecessary defrosting is carried out because the completion of defrosting is not properly detected for some reasons.
  • Fig. 9 is a vertical sectional view showing the essential part of a refrigerator of the sixth exemplary embodiment.
  • the structure of the sixth embodiment differs from those of the aforementioned embodiments in the following points.
  • temperature sensor 29 detects the surface temperature of glass-tube heater 19. Controller 32 increases or decreases the application of voltage to heater 19. Heater 19 has heating wire 31 therein.
  • R600a isobutane
  • controller 32 increases or decreases the application of voltage to heater 19, thereby keeping the surface temperature of heater 19 below the ignition temperature of the combustible refrigerant.
  • the defrosting is thus performed with reliable thermal control.
  • R600a isobutane
  • voltage to be applied to the heater is properly controlled so that the surface temperature of heater 19 is kept below the ignition temperature, for example, 450 °C or lower while current is applied to the heater in defrosting.
  • the refrigerator of the embodiment can prevent a combustible refrigerant from catching fire even if the defrosting operation is performed in an environment where the combustible refrigerant leaks at somewhere in the area having the defrosting means.
  • the risk of catching fire can be avoided even in the cases that undesired high voltage is applied to the glass-tube heater for some reasons, or that unnecessary defrosting is carried out because the completion of defrosting is not properly detected for some reasons.
  • the high/low control of the application of voltage can minimize variations in temperature of the heating wire, which can protect the heating wire from a break; accordingly, protecting the combustible refrigerant from electric spark caused by breaking of wire.
  • Fig. 10 is a vertical sectional view showing the essential part of a refrigerator of the seventh exemplary embodiment.
  • refrigerator 101 contains outer case 102, inner case 103, and rigid polyurethane foam-made heat insulating material 104.
  • the space between outer case 103 and inner case 102 is filled out with insulating material 104.
  • Cold-storage compartment 105 and freezer compartment 106 are separated by partition wall 107.
  • Evaporator 108 is disposed at the rear of freezer compartment 106.
  • Polystylene foam 109 is disposed at the front of evaporator 108 so as to provide electrical insulation between freezer compartment 106 and the chamber accommodating evaporator 108 therein.
  • molded-resin decorative laminate 110 is disposed on the outside of polystylene foam 109.
  • Cold-air outlet 111 is integrally formed with decorative laminate 110.
  • Cold-air inlet 112 is formed between the bottom edge of laminate 110 and inner case 103.
  • Cold-air mixing fan motor 113 is fixed at a section of decorative laminate 110. Fan motor 113 spews out cold air, which has been cooled in evaporator 108, into freezer 106 and other chambers having different temperatures (not shown). Dripping pan 114 is disposed under evaporator 108. The upper opening of pan 114 is formed slightly larger than the bottom shape of evaporator 108. Glass-tube heater 115 is fixed between evaporator 108 and dripping pan 114. Evaporation pipe 116 and fin 117 are secured by press fitting, caulking, or the like.
  • Evaporation basin 119 is located under dripping pan 114 so as to collect water dripped in receiver 114.
  • Radiation pipe 120 which is disposed in basin 119, heats up the water collected in basin 119 and evaporates it.
  • the outer wall of heater 115 maintains at-all-times contact with an edge of fin 117.
  • Fin 117 is formed of vertically arranged continuous fin.
  • Ni-Cr wire is employed for the resistance wire for heater 115.
  • Cold air cooled in evaporator 108 is spewed out by fan motor 113 from cold-air outlet 111. After used for heat exchange in freezer compartment 106, the air goes through cold-air inlet 112 back to evaporator 108. Repeating the air circulation above cools freezer compartment 106 at a predetermined temperature. A portion of the cold air cooled in evaporator 108 is distributed, via a duct and damper (not shown), to cold-storage compartment 105 and other chambers having different temperature ranges, whereby each chamber is kept properly cool.
  • Evaporation basin 119 collects the water from melted-frost via dripping pan 114, and then radiation pipe 120 heats up the water to evaporate.
  • the refrigeration cycle has successive connections of the following elements: a compressor, a condenser, a pressure reduction mechanism, and an evaporator.
  • the refrigeration cycle contains a combustible refrigerant to circulate therethrough.
  • the structure in which heater 115 contacts with an end of fin 108 can defrost the evaporator by heat transferred from heater 115, as well as by radiant heat from the heater, thereby improving the defrost efficiency.
  • radiation effect resulted from heat-transfer to fin 108 keeps the surface temperature of glass-tube heater 115 cool, with the amount of heat radiated from heater 115 maintained. This allows the surface temperature of heater 115 to keep below an ignition temperature (e.g. isobutane has an ignition temperature of 460 °C) of a combustible refrigerant. Therefore, the structure has no danger of catching fire in the event that a combustible refrigerant leaks at somewhere in the refrigerator.
  • an ignition temperature e.g. isobutane
  • fin 117 disposed in evaporator 108 is formed of vertically arranged continuous fin; the structure enhances radiation effect resulted from heat-transfer to fin 117, increasing the efficiency of defrosting. Furthermore, the structure can lower the surface temperature of heater 115, with the amount of heat radiated from the heater maintained. Thereby, the surface temperature of the heater can be kept below the ignition temperature of a combustible refrigerant.
  • Ni-Cr wire is employed for the resistance wire for heater 115. Even in the use of the heating wire at low temperatures, the Ni-Cr resistance wire has no brittle fracture that would be observed in a Fe-Cr resistance wire at approx. 470 °C, thereby protecting the heating wire from a break.
  • Fig. 11 is a vertical sectional view showing the essential part of a refrigerator of the eighth exemplary embodiment.
  • the structure of the eighth embodiment differs from that of the seventh embodiment in the following points.
  • each of a plurality of fins 121 of the structure in the eighth embodiment has half-round indent 122 conforming to the outer wall of glass-tube heater 115, as shown in Fig. 11 .
  • Continuous fins 121 make contact, at indent 122, with the outer wall of heater 115.
  • each indent 122 makes contact with the outer wall of heater 115
  • the structure of the eighth embodiment in which each indent 122 makes contact with the outer wall of heater 115, can increase the contact area between the fin and the heater, accordingly, enhancing the efficiency of heat transfer.
  • the improved efficiency further accelerates defrosting.
  • the surface temperature of the heater can be kept sufficiently lower than the ignition temperature of a combustible refrigerant.
  • Fig. 12 is a view, partially in perspective, of a refrigerator of the ninth exemplary embodiment.
  • Fig. 13 is a front view, looking in the direction of arrow B of Fig. 12 .
  • Fig. 14 is a view, partially in perspective, of another evaporator and glass-tube heater of a refrigerator of the ninth exemplary embodiment.
  • Fig. 15 is a front view, looking in the direction of arrow C of Fig. 14 .
  • each fin 123 has L-shape bend 124 at the bottom end of the fin. Bend 124 makes contact with the outer wall of glass-tube heater 115. Fin 123 is arranged, as shown in Fig. 13 , so as to have interval 125 between the edge of bend 124 and adjacent fin.
  • the fin also can have a structure as that shown in Fig. 14 -each fin 126 has half-round indent 127 at an end so as to conform to the outer wall of glass-tube heater 115, and the end having indent 127 further has L-shape bend 128.
  • each fin 123 has an L-shape bend at an end having contact with the outer wall of heater 115.
  • the structure allows each fin 123 to couple to the outer wall of heater 115 through line contact, enhancing the efficiency of heat transfer.
  • interval 125 formed between an edge of bend 124 and adjacent fin can upwardly transfer the radiant heat from heater 115.
  • Figs. 14 and 15 show another structure in which an end of each fin 126 has half-round indent 127 so as to conform to the outer wall of heater 115, and the end is further bent into an L shape.
  • the structure allows each fin 126 to couple to the outer wall of heater 115 through area contact, further improving the efficiency of heat transfer.
  • the structure of the embodiment, as described above, can provide further improved defrost efficiency.
  • the surface temperature of heater 115 can be kept further lower, with the amount of heat radiated from the heater maintained. Thereby, the surface temperature of the heater can be retained below the ignition temperature of a combustible refrigerant.
  • Fig. 16 is a view, partially in perspective, of an evaporator and a glass-tube heater of a refrigerator of a tenth exemplary embodiment.
  • Fig. 17 is a front view, looking in the direction of arrow D of Fig. 16 .
  • both ends of glass-tube heater 115 are fixed by holder 129.
  • Holder 129 is formed of partially notched vertical flange 131 of side plate 130 that is disposed on the side surface of the evaporator. Fixing heater 115 to holder 129 provides contact between the outer wall of the heater and each edge of fin 117.
  • Holder 129 is formed of partially notched vertical flange 131 of side plate 130 that is disposed on the side surface of the evaporator. Therefore, holder 129 can securely hold heater 115 with no danger of falling down, when both ends of the heater are fixed to the holder. That is, such a structure has no need for preparing additional fixing member in assemble work, providing a low-cost product.
  • the consistent positional relation of the structure can establish a reliable connection between heater 115 and fin 117, providing a consistent heat transfer.
  • the defrosting effect is preferably increased.
  • the advantage can enhance the defrosting effect.
  • the surface temperature of heater 115 can be kept lower, with the amount of heat radiated from the heater maintained. Thereby, the surface temperature of the heater can be retained below the ignition temperature of a combustible refrigerant.
  • Fig. 18 is a view, partially in perspective, of an evaporator and a glass-tube heater of a refrigerator of the eleventh exemplary embodiment.
  • Fig. 19 is a front view, looking in the direction of arrow E of Fig. 18 .
  • shield plate 132 is inserted between evaporator 108 and glass-tube heater 115.
  • the top surface of shield plate 132 makes contact with each bottom end 133 of fin 117.
  • Both ends 134 of shield plate 132 are integrally fixed to side-end fin 135 by caulking or the like.
  • shield plate 132 When an electric current is applied to heater 115, heat from the heater is conveyed to shield plate 132. Through the connection between the top surface of shield plate 132 and each bottom end 133 of fin 117, the heat from heater 115 can be radiated to fin 117. That is, the surface temperature of heater 115 can be kept lower than the ignition temperature of a combustible refrigerant, with the amount of heat from the heater maintained. In addition, shield plate 132 receives a drip of melted frost from evaporator 108, thereby avoiding a splash of the water from the evaporator directly down to heater 15. This can eliminate the noise, such as a sputter, which is produced when drippings instantly evaporates on hot heater 115.
  • Fig. 20 is a view, partially in perspective, of an evaporator and a glass-tube heater of a refrigerator of a twelfth exemplary embodiment.
  • Fig. 21 is a front view, looking in the direction of arrow F of Fig. 20 .
  • each long fin 136 has L-shaped bend 138 at the bottom end. Bend 138 makes contact with the outer wall of glass-tube heater 115.
  • each short fin 137 is formed shorter than long fin 136 in length, therefore the bottom end of the short fin have no contact with the heater. Interval "a" between adjacent two long fins is determined longer than interval "b" between long fin 136 and short fin 137.
  • Each long fin 136 has an L-shape bend at an end having contact with the outer wall of heater 115.
  • the structure allows each long fin 136 to couple to the outer wall of heater 115 through line contact, thereby enhancing the efficiency of heat transfer from heater 115 to long fin 136.
  • Long fin 136 and short fin 137 of the evaporator are arranged so that the interval between adjacent fins in the upper section is larger than that in the lower section, i.e., interval "a" is longer than interval "b".
  • the arrangement protects the lower section of the evaporator from being heavily covered with frost. In other words, frost uniformly covers the evaporator, thereby realizing a less frequent defrosting operation. This fact can suppress power consumption required for defrosting, contributing to energy saving.
  • Fig. 22 is a view, partially in perspective, of an evaporator and a glass-tube heater of a refrigerator of a thirteenth exemplary embodiment.
  • Fig. 23 is a front view, looking in the direction of arrow G of Fig. 22 .
  • Fig. 24 is a partially enlarged sectional view of a glass-tube heater of the refrigerator shown in Fig. 22 .
  • glass-tube heater 139 has a tube-in-tube structure formed of inner tube 140 and outer tube 141.
  • Outer tube 141 accommodates inner tube 140 therein, keeping a predetermined interval from the outer wall of inner tube 140.
  • Inner tube 140 contains resistance wire heater 143 therein. Both ends of both tubes are integrally fixed by cap 142 so as to be set in position.
  • outer tube 141 of heater 139 is always maintained in contact with each bottom end of fin 117.
  • Fig. 25 is a view illustrating the refrigeration cycle of a refrigerator of a fourteenth exemplary embodiment.
  • Fig. 26 is a partially sectional view of a glass-tube heater of the refrigerator of the fourteenth exemplary embodiment.
  • refrigeration cycle 201 has successive connections of the following elements: compressor 202; condenser 203; pressure drier 204; capillary tube 205 as a reduction mechanism; and evaporator 206.
  • a combustible refrigerant is sealed in the refrigeration cycle.
  • Glass-tube heater 207 as defrosting means is disposed below evaporator 206 to defrost the evaporator at regular intervals.
  • sealing member 208 has inner-tube holder 209 and outer-tube holder 210, which are integrally formed of rubber.
  • Inner-tube holder 209 and outer-tube holder 210 support the ends of inner tube 211 and outer tube 212 of the tube-in-tube structure, respectively.
  • Heating wire 213, which is made of iron-chrome, nickel-chrome, or the like material, is accommodated in inner tube 211, with a predetermined interval from the inner wall of tube 211 maintained.
  • Heating wire 213 is caulked with lead-out wire 215 at joint 214, and lead-out wire 215 goes out from the lower side or the bottom of sealing member 208.
  • Fig. 27 is a partially sectional view of another glass-tube heater of the refrigerator of the fourteenth exemplary embodiment.
  • sealing member 216 has inner-tube holder 217 and outer-tube holder 218, which are integrally formed of rubber.
  • Inner-tube holder 217 supports inner tube 219 in such a way that overlap 221 overlaps over inner tube 219 by length "c"
  • outer-tube holder 218 supports outer tube 220 in such a way that overlap 222 overlaps over outer tube 220 by length "d”.
  • End surface 224 (i.e., plane “I” in Fig. 27 ) of overlap 222 is outwardly located than end surface 223 (i.e., plane "H") of overlap 221.
  • glass-tube heater 207 In the defrosting process, an electric current is applied to heating wire 213 of glass-tube heater 207 to periodically remove frost from evaporator 206. Heat from the glass-tube heater is transmitted, through inner tube 211 and outer tube 212, to evaporator 206 to remove frost therefrom.
  • Glass-tube heater 207 has a tube-in-tube structure. In the heat transfer process, the space between inner tube 211 and outer tube 212 serves as an insulator, so that the surface temperature of the outer tube becomes lower than that of the inner tube. That is, the surface temperature of outer tube 212 can be kept lower than the ignition temperature (e.g. 460 °C for isobutane) of a combustible refrigerant, with the amount of heat from the heater maintained.
  • the ignition temperature e.g. 460 °C for isobutane
  • sealing member 208 at the end of the glass tube ensures the positioning of the glass tube in the tube-in-tube structure, thereby properly maintaining the interval between the inner tube and the outer tube; accordingly, it minimizes variations in the surface temperatures of the glass tubes.
  • Sealing member 216 of Fig. 27 contains inner-tube holder 217 and outer-tube holder 218 as an integral structure, providing a cost-decreased product and reliable assembling work due to minimized variations in dimensions.
  • inner-tube holder 217 and outer-tube holder 218 contain overlap 221 and overlap 222, respectively, at the end of each outer wall of the glass tubes. The structure can properly suppress airflow from the outside into the glass tube.
  • end surface 224 i.e., plane "I” in Fig. 27
  • end surface 223 i.e., plane "H" of overlap 221.
  • the positional relationship allows the radiant heat from inner tube 219 to be easily transferred, enhancing the efficiency of defrosting.
  • the structure invites an easy attachment of outer tube 220 to sealing member 216, enhancing the efficiency of assembling work.
  • the structure of the fourteenth embodiment employs a rubber-made sealing member, it is not limited thereto; the similar effect will be expected as long as the material has heat-resisting property.
  • Fig. 28 is a partially sectional view of a glass-tube heater of a refrigerator of the fifteenth exemplary embodiment.
  • sealing member 225 has inner-tube holder 226 and outer-tube holder 227, which are integrally formed of rubber.
  • Inner-tube holder 226 supports inner tube 228 in such a way that overlap 230 overlaps over inner tube 228 by length "e"
  • outer-tube holder 227 supports outer tube 229 in such a way that lap 231 laps over outer tube 229 by length "e”.
  • End surface 233 of overlap 231 contains a plane (i.e., plane "J") common with end surface 232 of overlap 230.
  • Inner tube 228 and outer tube 229 measure the same in length, each end of which is located on a common plane, i.e., plane "K" in Fig. 28 .
  • the glass-tube heater contains inner tube 228 and outer tube 229.
  • Sealing member 225 holds the two tubes so that the end surface 233 of the outer-tube holder's lap contains a plane common with the end surface 232 of the inner-tube holder's lap.
  • the structure effectively suppresses airflow from outside into the glass tube, thereby minimizing the risk of catching fire if the combustible refrigerant leaks in the refrigerator.
  • inner tube 228 and outer tube 229 are identical in length. This therefore simplifies manufacturing processes, that is, provides an easy manufacturing of glass tubes.
  • Fig. 29 is a partially sectional view of a glass-tube heater of a refrigerator of the sixteenth exemplary embodiment.
  • sealing member 234 is formed of a plurality of supporting members: inner-tube supporting member 235, outer-tube supporting member 236 separately formed from member 235.
  • Inner-tube holder 237 of inner-tube supporting member 235 holds an end of the outer wall of inner tube 239.
  • outer-tube holder 238 of outer-tube supporting member 236 holds an end of the outer wall of outer tube 240.
  • Outer-tube supporting member 236 fits snugly against a part of the exterior of inner-tube supporting member 235.
  • Inner-tube supporting member 235 is formed of material having high heat resistance
  • outer-tube supporting member 236 is formed of material having heat resistance lower than that of member 235.
  • Sealing member 234 is formed of inner-tube supporting member 235 and outer-tube supporting member 236, each of which has a separate structure. This allows sealing member 234 to employ different material between the two members 235 and 236, increasing design flexibility of sealing member 234.
  • Inner-tube supporting member 235 is formed of material having high heat resistance
  • outer-tube supporting member 236 is formed of material having heat resistance lower than that of member 235.
  • Employing a high-temperature-resistant material increases reliability of the sealing member.
  • employing materials that differ in heat resistance can decrease the use of a heat-resistant material, which invites high production cost. As a result, a low-cost sealing member can be obtained.
  • Fig. 30 is a partially sectional view of a glass-tube heater of a refrigerator of the seventeenth exemplary embodiment.
  • sealing member 241 has inner-tube holder 242 and outer-tube holder 243, which are integrally formed of rubber.
  • Inner-tube holder 242 supports inner tube 244 in such a way that overlap 246 overlaps over inner tube 244 by length "f", similarly, outer-tube holder 243 supports outer tube 245 in such a way that lap 247 overlaps over outer tube 245 by length "g".
  • End surface 249 (i.e., plane “M” in Fig. 30 ) of overlap 247 of outer-tube holder 243 is inwardly located than end surface 248 (i.e., plane "L") of overlap 246 of inner-tube holder 242.
  • the glass-tube heater is so arranged that end surface 249 of the overlap of outer-tube holder 243 is inwardly located than end surface 248 of the overlap of inner-tube holder 242.
  • the arrangement allows outer-tube holder 242 to have sufficient lapping length of "g", accordingly, offering good sealing between the glass tubes.
  • the structure therefore effectively suppresses airflow from outside into the glass tube, thereby minimizing the risk of catching fire if the combustible refrigerant leaks in the refrigerator.
  • lapping length "f" of overlap 246 of inner-tube holder 242 can be relatively decreased, accordingly, holder 242 considerably escapes from being affected by radiant heat from heating wire 213.
  • the fact can protect the inner-tube holder from undesired rise in temperature caused by the radiant heat when an electric current is applied to the glass tube. Therefore, there is no need to employ an extra high-temperature-resistant material for sealing member 241, whereby the production cost can be decreased.
  • the refrigerator of the present invention has a plurality of glass-tube heaters as a means for defrosting the evaporator that is disposed in a combustible refrigerant-sealed refrigeration cycle.
  • a current-carrying period or an application of voltage to the glass-tube heater is controlled so that the temperature of the heater is kept below the ignition temperature of a combustible refrigerant. This not only protects the combustible refrigerant from the risk of catching fire, but also avoids poor refrigeration caused by residual frost.
  • a glass-tube heater makes contact with fins of the evaporator to decrease the surface temperature of the glass-tube heater.
  • the glass-tube heater has a tube-in-tube structure, and a sealing member is disposed on an end of the glass tube.

Claims (5)

  1. Réfrigérateur comprenant :
    un cycle de réfrigération à réfrigérant combustible isolé ayant des connexions successives des éléments suivants : un compresseur (202), un condenseur (203), un mécanisme de réduction de pression (204), et un évaporateur (206) ;
    un réchauffeur à tube de verre (207), et
    un élément de scellement (208) disposé au niveau d'une extrémité du réchauffeur à tube de verre (207),
    caractérisé par
    le réchauffeur à tube de verre (207) ayant une structure à double tube est disposé dans une section inférieure de l'évaporateur (206) ou en-dessous de l'évaporateur,
    dans lequel les tubes de verre multi-structurés comportent un tube intérieur (211) et un tube extérieur (212), l'élément de scellement (208) contient d'un seul tenant un porte-tube intérieur (209) et un porte-tube extérieur (210), le porte-tube intérieur (209) supporte le tube intérieur (211) et le porte-tube extérieur (210) supporte le tube extérieur (212), et le porte-tube intérieur (209) et le porte-tube extérieur (210) ont une section de chevauchement (221 ; 222) au niveau d'une extrémité d'une paroi extérieure du tube intérieur (209) et d'une extrémité d'une paroi extérieure ou intérieure du tube extérieur (212), respectivement.
  2. Réfrigérateur de la revendication 1, dans lequel une face de pointe (224) de la section de recouvrement (222) du porte-tube extérieur (210) est située à l'extérieur d'une face de pointe (223) de la section de recouvrement (221) du porte-tube intérieur (209).
  3. Réfrigérateur de la revendication 1, dans lequel une face de pointe (233) de la section de recouvrement (231) du porte-tube extérieur (227) est disposée pour partager un plan commun avec une face de pointe (232) de la section de recouvrement (230) du porte-tube intérieur (226).
  4. Réfrigérateur de la revendication 1, dans lequel une face de pointe (249) de la section de recouvrement (247) du porte-tube extérieur (243) est située à l'intérieur d'une face de pointe (248) de la section de recouvrement (246) du porte-tube intérieur (242).
  5. Réfrigérateur de la revendication 1, dans lequel les tubes de verre du réchauffeur ayant la structure à double tube sont de longueur identique.
EP07001116.8A 2001-03-13 2002-03-13 Réfrigérateur Expired - Lifetime EP1793186B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001069976A JP2002267331A (ja) 2001-03-13 2001-03-13 冷蔵庫
EP02705107A EP1369650B1 (fr) 2001-03-13 2002-03-13 Refrigerateur

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP02705107.7 Division 2002-03-13
EP02705107A Division EP1369650B1 (fr) 2001-03-13 2002-03-13 Refrigerateur

Publications (3)

Publication Number Publication Date
EP1793186A2 EP1793186A2 (fr) 2007-06-06
EP1793186A3 EP1793186A3 (fr) 2012-06-13
EP1793186B1 true EP1793186B1 (fr) 2015-09-09

Family

ID=18927930

Family Applications (2)

Application Number Title Priority Date Filing Date
EP02705107A Expired - Lifetime EP1369650B1 (fr) 2001-03-13 2002-03-13 Refrigerateur
EP07001116.8A Expired - Lifetime EP1793186B1 (fr) 2001-03-13 2002-03-13 Réfrigérateur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP02705107A Expired - Lifetime EP1369650B1 (fr) 2001-03-13 2002-03-13 Refrigerateur

Country Status (8)

Country Link
EP (2) EP1369650B1 (fr)
JP (1) JP2002267331A (fr)
KR (1) KR100600185B1 (fr)
CN (3) CN100513949C (fr)
DE (1) DE60232715D1 (fr)
HK (1) HK1075696A1 (fr)
TW (1) TW539838B (fr)
WO (1) WO2002073106A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020093114A1 (fr) * 2018-11-07 2020-05-14 Da Gragnano Bruno Système et procédé automatique pour l'économie d'énergie selon des conditions ambiantes et d'autres paramètres techniques, à utiliser dans des systèmes à résistances pour le chauffage de vitres de présentoirs commerciaux réfrigérés ou congelés

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004197964A (ja) * 2002-12-16 2004-07-15 Matsushita Refrig Co Ltd 除霜用ヒータ
JP3580307B2 (ja) * 2003-02-20 2004-10-20 松下電器産業株式会社 除霜ヒーター
JP3552715B1 (ja) * 2003-10-23 2004-08-11 松下電器産業株式会社 除霜ヒーター
JP2005134030A (ja) * 2003-10-30 2005-05-26 Matsushita Electric Ind Co Ltd 冷蔵庫
JP3944498B2 (ja) * 2004-08-25 2007-07-11 日立アプライアンス株式会社 冷蔵庫
JP2006343089A (ja) * 2005-05-12 2006-12-21 Matsushita Electric Ind Co Ltd 除霜装置付き冷却器と除霜装置付き冷却器を備えた冷蔵庫
WO2010092624A1 (fr) * 2009-02-12 2010-08-19 パナソニック株式会社 Réfrigérateur
JP5025689B2 (ja) * 2009-06-26 2012-09-12 三菱電機株式会社 冷蔵庫
DE102010003833A1 (de) * 2010-04-09 2011-10-13 BSH Bosch und Siemens Hausgeräte GmbH Abtauheizung für ein Kältegerät
JP5868034B2 (ja) * 2011-06-07 2016-02-24 株式会社東芝 冷蔵庫
JP6026966B2 (ja) * 2013-06-28 2016-11-16 アクア株式会社 冷蔵庫
JP5752199B2 (ja) * 2013-09-13 2015-07-22 株式会社Uacj 冷凍冷蔵庫の熱交換装置
CN103851851B (zh) * 2013-11-07 2016-09-07 海信（山东）冰箱有限公司 一种带有加湿功能的风冷冰箱及其控制方法
KR101728388B1 (ko) * 2014-12-15 2017-04-19 엘지전자 주식회사 제상장치를 구비한 냉장고
CN106247742B (zh) * 2016-08-12 2018-09-18 长虹美菱股份有限公司 一种冰箱冷冻风扇化霜装置及其控制方法
KR102204008B1 (ko) * 2016-11-30 2021-01-18 엘지전자 주식회사 냉장고

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4091637A (en) * 1976-10-13 1978-05-30 Mcquay-Perfex, Inc. Electric defrost heater for fin and tube refrigeration heat exchanger
JPS5828908B2 (ja) * 1978-11-24 1983-06-18 株式会社東芝 冷蔵庫
JPS589911B2 (ja) * 1978-11-29 1983-02-23 株式会社日立製作所 冷凍機用蒸発器
JPS597383U (ja) * 1982-07-05 1984-01-18 三菱電機株式会社 冷蔵庫
JPS5916971U (ja) * 1982-07-22 1984-02-01 三菱電機株式会社 冷蔵庫
JPH0625813Y2 (ja) * 1989-06-14 1994-07-06 サンデン株式会社 冷却器の除霜ヒータ取付構造
JPH0427372U (fr) * 1990-06-26 1992-03-04
JPH06313664A (ja) 1993-04-28 1994-11-08 Mitsubishi Electric Corp 冷蔵庫の除霜用ヒータ
JPH11257831A (ja) * 1998-03-13 1999-09-24 Toshiba Corp 冷蔵庫
JP3404299B2 (ja) * 1998-10-20 2003-05-06 松下冷機株式会社 冷蔵庫
JP4310825B2 (ja) * 1998-10-20 2009-08-12 パナソニック株式会社 冷蔵庫
JP3507724B2 (ja) * 1999-03-18 2004-03-15 松下冷機株式会社 冷蔵庫

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020093114A1 (fr) * 2018-11-07 2020-05-14 Da Gragnano Bruno Système et procédé automatique pour l'économie d'énergie selon des conditions ambiantes et d'autres paramètres techniques, à utiliser dans des systèmes à résistances pour le chauffage de vitres de présentoirs commerciaux réfrigérés ou congelés

Also Published As

Publication number Publication date
WO2002073106A1 (fr) 2002-09-19
JP2002267331A (ja) 2002-09-18
EP1793186A3 (fr) 2012-06-13
CN1945177A (zh) 2007-04-11
KR100600185B1 (ko) 2006-07-12
DE60232715D1 (de) 2009-08-06
CN100439831C (zh) 2008-12-03
TW539838B (en) 2003-07-01
EP1793186A2 (fr) 2007-06-06
EP1369650B1 (fr) 2009-06-24
HK1075696A1 (en) 2005-12-23
CN1940419A (zh) 2007-04-04
EP1369650A1 (fr) 2003-12-10
CN100513949C (zh) 2009-07-15
CN1620585A (zh) 2005-05-25
EP1369650A4 (fr) 2006-04-26
KR20030094279A (ko) 2003-12-11
CN1327177C (zh) 2007-07-18

Similar Documents

Publication Publication Date Title
EP1793186B1 (fr) Réfrigérateur
CA2413540C (fr) Degivreur pour evaporateur de refrigerateur
WO2000070281A1 (fr) Refrigerateur et element chauffant degivreur
JP2010133590A (ja) 冷凍冷蔵庫
EP2034262B1 (fr) Dispositif de stockage refrigere
JP2009127925A (ja) 除霜ヒータ付き冷却器および物品貯蔵装置
US3394559A (en) Refrigerator including defrost means
JP3404395B2 (ja) 冷蔵庫
JP3482406B2 (ja) 冷凍冷蔵庫
EP3435010B1 (fr) Réfrigérateur comprenant un évaporateur
JP2000121237A (ja) 冷蔵庫
JP2010032152A (ja) 除霜装置付き冷却器と除霜装置付き冷却器の製造方法およびその冷却器を備えた物品貯蔵装置
JP2010014332A (ja) 冷蔵庫
KR100288263B1 (ko) 냉장고의제상장치
JP2002206849A (ja) 冷蔵庫
JP2003075053A (ja) ガラス管ヒータおよびガラス管ヒータを備えた冷蔵庫
JP2003202177A (ja) ガラス管ヒータおよびガラス管ヒータを備えた冷蔵庫
KR940002912Y1 (ko) 냉장고
CN113531975A (zh) 冰箱
KR20050016027A (ko) 냉장고
JP2006010152A (ja) 冷蔵庫
JP2004190960A (ja) 冷蔵庫
JP2006010151A (ja) 冷蔵庫
JP2010091233A (ja) 冷蔵庫
KR19990018697U (ko) 압축기의 열을 이용한 쇼케이스 제상장치

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: 20070124

AC Divisional application: reference to earlier application

Ref document number: 1369650

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: PANASONIC CORPORATION

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

RIC1 Information provided on ipc code assigned before grant

Ipc: H05B 3/50 20060101ALI20120509BHEP

Ipc: F25D 21/08 20060101AFI20120509BHEP

Ipc: H05B 3/44 20060101ALI20120509BHEP

AKX Designation fees paid

Designated state(s): DE FR GB IT SE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 60247465

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F25D0021080000

Ipc: F25D0021140000

RIC1 Information provided on ipc code assigned before grant

Ipc: F25D 21/14 20060101AFI20150130BHEP

Ipc: H05B 3/50 20060101ALI20150130BHEP

Ipc: H05B 3/44 20060101ALI20150130BHEP

Ipc: F25D 21/08 20060101ALI20150130BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150327

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AC Divisional application: reference to earlier application

Ref document number: 1369650

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 60247465

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150909

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 60247465

Country of ref document: DE

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20160330

Year of fee payment: 15

26N No opposition filed

Effective date: 20160610

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20160313

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20161130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160331

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160313

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 60247465

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20171003