EP0000217A1 - Kühlschrank - Google Patents

Kühlschrank Download PDF

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Publication number
EP0000217A1
EP0000217A1 EP78200036A EP78200036A EP0000217A1 EP 0000217 A1 EP0000217 A1 EP 0000217A1 EP 78200036 A EP78200036 A EP 78200036A EP 78200036 A EP78200036 A EP 78200036A EP 0000217 A1 EP0000217 A1 EP 0000217A1
Authority
EP
European Patent Office
Prior art keywords
refrigerator
control
refrigerant
evaporator
gas
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.)
Granted
Application number
EP78200036A
Other languages
English (en)
French (fr)
Other versions
EP0000217B1 (de
Inventor
George Albert Apolonia Asselman
Adrianus Johannes Van Mensvoort
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.)
Whirlpool International BV
Original Assignee
Philips Gloeilampenfabrieken NV
Koninklijke Philips Electronics NV
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
Priority claimed from NL7706880A external-priority patent/NL7706880A/xx
Priority claimed from NL7714306A external-priority patent/NL7714306A/xx
Application filed by Philips Gloeilampenfabrieken NV, Koninklijke Philips Electronics NV filed Critical Philips Gloeilampenfabrieken NV
Publication of EP0000217A1 publication Critical patent/EP0000217A1/de
Application granted granted Critical
Publication of EP0000217B1 publication Critical patent/EP0000217B1/de
Expired legal-status Critical Current

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Classifications

    • 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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/06—Control arrangements therefor
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/025—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures using primary and secondary refrigeration systems
    • 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
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular
    • 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
    • F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
    • F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems
    • 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
    • F25D2400/30—Quick freezing

Definitions

  • the invention relates to a refrigerator having a freezing compartment and a refrigerating compartment, which refrigerator is provided with a primary refrigerating system which contains a refrigerant with a primary 3 vapor- ator disposed in the freezing compartment, and a secondary refrigerating system which also contains a refrigerant with a secondary evaporator disposed in the refrigerating compartment and a secondary condensor which is in bear -exchanging contact with the primary evaporator, which secondary condensor has a condensation wall on whose surface the refrigerant condenses during operation.
  • a refrigerator of the said type is known from German Patent Specification 1,601,010.
  • the refrigerator in accordance with the invention is therefore characterized in that the secondary condensor is provided with means for varying the available condensation wall area so as to control the temperature of the secondary evaporator.
  • the wall area of the secondary condensor available for condensation is varied, the amount of refrigerant which condensates, and thus the temperature of the secondary evaporator, will vary. It is now in particular possible to adapt the available condensation wall area in such a way that, when the temperature in the freezing compartment changes, for example for rapidly freezing food, the temperature in the refrigerating compartment remains constant. Moreover, it is possible to defrost the secondary evaporator by adjusting the available condensation wall area of the secondary condensor to a minimum.
  • a preferred embodiment of the refrigerator in accordance with the invention is characterized in that the secondary condensor is provided with a reservoir containing a control gas, which control gas during operation constitutes an interface with refrigerant vapour at the location of the condensation wall, the interface being movable along the condensation wall. Owing to the movable interface the wall surface available for condensation can be adjusted to a size which corresponds to a desired temperature in the refrigerating compartment.
  • a further preferred embodiment of the refrigerator in accordance with the invention is characterized in that the reservoir containing the control gas contains a reversible control-gas getter, which can be heated for varying the amount of free control gas. Depending on its temperature this control-gas getter may absorb control gas or release control gas, so that the amount of free control gas can be reduced or increased respectively.
  • the displacement of the interface by which this is attended causes an increase or decrease of the available condensation wall area.
  • a further preferred embodiment of the refrigerator in accordance with the invention is characterized in that the reversible control gas getter can be heated by means of an electric heating element which is included in an electrical control circuit, which control circuit includes a temperature-sensitive element which is mounted in the refrigerating compartment, which temperature-sensitive element controls the heating element so as to maintain a specific temperature level in the refrigerating compartment.
  • the reversible control-gas getter and the electric heating element are accommodated in a holder of a thermal insulating material, which holder is provided with at least one wall which is permeable to a control gas.
  • the refrigerant is a freon
  • the control gas is nitrogen
  • the reversible control-gas getter is constituted by a molecular filter material, such as a zeolite.
  • a different embodiment of the refrigerator in accordance with the invention is characterized in that the reservoir has a fixed partition, which devides the reservoir into two sections, which is permeable to control gas and not to refrigerant vapour.
  • the advantage of this embodiment is that the temperature of the secondary evaporator can be controlled without the use of auxiliary energy.
  • Still another embodiment of the refrigerator in accordance with the invention is characterized in that the reservoir containing the control gas comprises a movable bounding wall for moving the interface. Owing to the movable bounding wall the interface between control gas and refrigerant vapour can be adjusted via the control gas to a posi tion which corresponds to specific size of the available condensation wall area, which in its turn corresponds to a desired temperature in the refrigerating compartment.
  • a further suitable embodiment of the refrigerator in accordance with the invention is characterized in that the movable bounding wall, with its side which is remote from the reservoir containing the control gas, forms part of the bounding surface of a further reservoir, which contains a pressure-transfer medium whose pressure is controllable.
  • the pressure-transfer medium can be heated by means of an electric heating element which is included in an electrical control circuit, which control circuit comprises a temperature-sensitive element which is disposed in the refrigerating compartment, which temperature-sensitive element controls the heating element so as to maintain a specific temperature level in the refrigerating compartment.
  • a further suitable embodiment of the refrigerator in accordance with the invention is characterized in that the secondary condensor takes the form of a tapered tube whose cross-section increases towards the secondary evaporator. Owing to a lerger cross-section at the inlet side of the condenser tube the rate of evaporation upon entrance in the secondary condensor is low. This facilitates reflux of condensed refrigerant to the secondary evaporator. Moreover, a part of the condenser tube has a smaller volume, so that in the case of control actions via this section the control speed is high.
  • a construction which employs the force of gravity for reflux of the refrigerant which has condensed in the secondary condensor to the secondary evaporator, may present problems.
  • This problem can be solved in accordance with the invention by connecting the secondary condensor to the secondary evaporator via a capillary structure. Feedback os condensed refrigerant to the secondary evaporator is now effected by capillary action independently of the force of gravity.
  • Stilan other embodiment of the refrigerator in accordance with the invention is characterized in that the secondary evaporator is locally provided with pockets which serve as reservoir for liquid refrigerant.
  • This embodiment has the advantage that it results in a uniformly distributed evaporation of the liquid over the entire evaporator surface. As a result of this cooling times for the refrigerating compartment are short, for example, after a defrosting period.
  • the reference numeral 1 refers to a refrigerator, which comprises a freezing compartment 2 and a refrigerating compartment 3.
  • the freezing compartment 2 is disposed above the refrigerating compartment 3.
  • the refrigerating compartment 2 is cooled by means of a primary refrigerating system which comprises a compressor 4, a primary condensor 5, a capillary tube 6 serving as a restriction, and a primary evaporator 7.
  • the primary refrigerating system contains a normal refrigerant, such as freon.
  • the temperature in the refrigerating compartment 2 is thermostatically controlled and the temperature level is adjustable in known manner, not indicated.
  • the refrigerating compartment 3 is cooled by means of a secondary refrigerating system, whose secondary evaporator 8 is located in the refrigerating compartment 3 and whose secondary condensor 9 is located in an insulated outer wall of the freezing compartment 2.
  • the secondary con-Gensor 9 has a condensation wall 10, which is brought into thermally conducting contact with the primary evaporator 7.
  • the secondary refrigerating system also contains a normal refrigerant, such as freon.
  • the secondary evaporator 8 and the secondary condensor 9 are constituted by a single pipe. heat transfer in the secondary refrigerating system is effected in that the liquid refrigerant evaporates in the evaporator 8 and subsequently codenses on the surface of the condensation wall 10. The condensed refrigerant flows back into the secondary evaporator 8 as a result of the force of gravity and in this way cools the refrigerating compartment
  • the temperature in the refrigerating compant- ment 3 is controlled by varying the available condensation wall area 10.
  • the end 11 of the secondary condensor 9 terminates in a reservoir 12, which is filled with a control gas 13.
  • This control gas 13 constitutes an interface 15 with the refrigerant vapour 14 at the location of the condensation wall 10. Below this interface 15 condensation of refrigerant vapour takes place during operation gerant which condenses and thus also the tamperature of the secondary evaporator 6.
  • the interface 15 can be moved along the condensation wall 10 by varying the amount of control gas 13.
  • a reversible control-gas getter 16 which can be heated, is contained in the reservoir 12. At increasing temperature the control gas getter releases more control gas and moves the interface 15 downwards, so that the available surface area of the condensation wall 10 is reduced. Conversely the control gas getter will absorb more control gas at decreasing temperature, so that the interface-15 is moved upwards and the available condensation wall area increases.
  • refrigerant for example, freon R12 (CF 2 CI 2 ) is used as control gas nitrogen, and as control gas getter the well-known molecular filter material, zeolite type 4A. This type of zeolite getters nitrogen, but substantially no freon R12.
  • freon R12 CF 2 CI 2
  • the control-gas getter 16 may be heated with the aid of a heating element 17, which is included in the electrical control circuit in accordance with Figure 2.
  • a heating element 17 which is included in the electrical control circuit in accordance with Figure 2.
  • This known control circuit is described in the brochure "Design of time-proportional temperature controls using the TDA 1023" (Philips Elcoma Division, Technical Information N° 025, 1 March 1977).
  • The-integrated circuit TDA 1023 in this control circuit is a time-proportional control circuit.
  • the temperature-sensitive element R NTC is located in the refrigerating compartment 3.
  • the temperature in the freezing compartment 2 is -18°C and the temperature in the refrigerating compartment 3 is +4°C. Food is to be frozen rapidly and the temperature level in the freezing compartment 2 is set to -30°C. As a result of this, the primary evaporator becomes colder and consequently more vapour will condense in the secondary condensor 9. As a result of this, the temperature in the refrigerating compartment 3 decreases. This is detected by the temperature-sensitive element R NTC in refrigerating compartment 3. Via the electrical control circuit the heating element 17 is now switched on. The con- trol gas getter 16 is heated and starts to release control gas 13. As a result of this, the interface 15 moves downwards along the condensation wall 10. The size of the available condensation wall area is reduced and less refrigerant vapour will condense. This compensates for the afore men- tioned effect that more vapour starts to condense because the primary evaporator 7 has become colder.
  • the temperature in the refrigerating compartment 3 is consewuently maintained at the level of approximately +4°C.
  • the temperature in the freezing compartment is reset to -18°C the process is reversed.
  • the invention enables the temperature in the refrigerating compartment 3 to be maintained constant automatically, irrespectively of the temperature in the freezing compartment 2. Moreover, it is possible to set the cemperature level in the refrigerator compartment 3 manually to a desired value via the variable resistor R , which is included in the electrical control circuit, which obviously is attended by a displacement of the interface 15.
  • Defrosting of the secnndary evaporator 8 is possible periodically via a timing circuit or counter circuit to be included in the electrical control circuit.
  • a timing circuit or counter circuit to be included in the electrical control circuit.
  • FIG. 3 A preferred form of the reservoir 12 containing the control gas is shown in Figure 3.
  • the reservoir has a filling opening 18 for the refrigerant and the control gas.
  • a holder 19 is located, which contains the control gas getter 16 and the heating element 17.
  • the walls 20 of the holder 19 are porous, so as to allow the control gas to pass through and they are thick-walled so : ing disposed at the outside. This enables the secondary refrigerating system to be filled during one of the last manufacturing stages.
  • FIG. 4 shows a different example of a control-gas reservoir.
  • the reservoir 12 is divided into two sections 27 and 28 by a partition 26. This partition is permeable to the control gas 13, but not to the refrigerant vapour 14. Thus, no refrigerant vapour can enter the section 28 of the reservoir.
  • Temperature control of the refrigerating compartment 3 is effected automatically. When the temperature in the refrigerating compartment 3 rises, more refrigerant will evaporate and the vapour pressure will increase. The control gas is further pressurised and the interface 15 moves upwards, so that the available condensation wall area increases and a new vapour pressure equilibrium is established. More vapour will condense and the temperature rise will be elimlir ated substantially.
  • the vapour pressure also depends on the temperature of the primary evaporator 7.
  • the temperature of the primary evaporator 7 decreases, so that more refrigerant vapour condenses in the secondary condensor 9 and the temperature in the refrigerating compartment 3 decreases.
  • the lower temperature of the primary evaporator 7 also results in a reduced vapour pressure in the secondary condensor 9. so that more control gas 13 is withdrawn from the section 28 pf the reservoir 12 and the interface 15 moves downwards along the condensation wall 10.
  • the available condensation wall area is reduced and the temperature drop is substantially compensated for.
  • the section 28 of the reservoir 12 also contains a reversible control gas getter, which can be heated by a heating element which is included in an electrical control circuit, which circuit includes a temperature-sensitive element accommodated in the refrigerating compartment 3 for controlling the heating element, changing the temperature level in the refrigerating compartment is possible.
  • Figure 5 shows still an other construction for noving the interface 15.
  • the secondary condensor 9 terminates in a reservoir 21, in which'a movable bounding wall, such a diaphragm or bellows 22 are located.
  • k displacement of the bellows 22 results in the displacement of the interface 15 and thus a change in size of the available condensation wall area 10.
  • the displacement of the bellows 22 should be related to the difference between the desired and prevailing temperature in the refrigerating compartment. This can be achieved in different manners.
  • this is effected by mounting a pressure-transfer medium 24 and a heating element 25 in a space 23 above the bellows 22.
  • the heating element 25 may then again be included in an electrical control circuit as shown in Figure 2.
  • pressure-transfer medium it is for example possible to use a medium, which in the same as the refrigerant.
  • the bellows 22 can be controlled with the aid of various control systems such as on-off control system (for example,.a bimetallic strip), an analog or a digital control system (for example, a servo system).
  • on-off control system for example,.a bimetallic strip
  • an analog or a digital control system for example, a servo system
  • FIG. 6 shows a variant of the secondary condensor of Figure 1.
  • the secondary condensor 9 takes the form of a tapered tube whose cross-section in- wases towards the secondary evaporator 8.
  • the vapour speed upon entrance in the condensor tube is low.
  • the condensed refrigerant can readily flow back to the secondary evaporator 8.
  • Another advantage of the tapered condensor tube 9 is that the upper portion of the tube has a smaller volume, so ' that for control actions over this portion the control speed is high.
  • Figure 7 is a cross-sectional view of the secondary condensor tube 9 and the primary evaporator tube 7 which is in heat exchanging contact therewith.
  • the primary evaporator tube 7 is disposed on both sides of the secondary condensor tube 9.
  • the condensor tube 9 and the evaporator tube 7 have a slightly flattened shape, so that in comparison with for example round tubes, the volume of the control gas is low and the surface area of the condensation wall 10 is large.
  • the amount of getter material can then also be small. This moreover reduces the electric power required for the temperature control of the control-gas getter.
  • FIG 8 in which corresponding parts bear the same reference numerals as in Figure 1, but augmented by the number 100, schematically shows a refrigerator in which the refrigerating compartment 103 is disposed above the freezing compartment 102.
  • the secondary condensor 109 is located in an insulated outer wall of the refrigerating compartment 103, where it is in heat-exchanging contact with the primary evaporator 107.
  • the refrigerant, which has condensed in the secondary condensor 109 also flows back to the secondary evaporator 108 by the force of gravity.
  • the entire secondary refrigerating system is located .at the same level as the refrigerating compartment 103, which demands a substantial mounting height of the refrigerating compartment.
  • This substantial mounting height can be reduced by construction as shown in Figure 9.
  • the secondary condensor 109a and the part of the primary evaporator .107a, which is in heat exchanging contact therewith, are curved.
  • the length of the secondary condensor 109a and thus the size of the condensation wall area is now equal to that in Figure 8, whilst the mounting height of the refrigerating compartment and thus the overall height of the refrigerator is smaller.
  • FIG. 10 An other construction, where the refrigerating compartment also disposed above the freezing compartment, is shown in Figure 10.
  • the parts corresponding to Figure 1 now bear the same reference numerals, augmented by the number 200.
  • the secondary condensor 209 is located in an insulated wall of the freezing compartment 202 and the secondary evaporator 209 in the refrigerating compartment 203.
  • the secon- d ary evaporator 208 is thus located above the secondary condensor 209.
  • a capillary structure 209 is located in the secondary condensor 209 and in the secondary evaporator 208, for example a layer of metal gauze or capillary grooves in the inner wall.
  • FIG 11 shows a favourable construction of a secondary evaporator 8 of the refrigerator of Figure 1.
  • the secondary evaporator 8 is locally provided with pockets 8a, which serves as reservoirs for liquid refrigerant.
  • pockets 8a which serves as reservoirs for liquid refrigerant.
  • a refrigerator with a primary refrigerating system consisting of a compressor, a condensor and an evaporator is alternatively possible to provide the refrigerator with a primary refrigerating system based on absorption.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP78200036A 1977-06-22 1978-06-12 Kühlschrank Expired EP0000217B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
NL7706880 1977-06-22
NL7706880A NL7706880A (en) 1977-06-22 1977-06-22 Refrigerator with freezing compartment - has two cooling circuits with condenser mounted in outer wall of freezing compartment to be in heat exchange with evaporator
NL7714306 1977-12-23
NL7714306A NL7714306A (en) 1977-12-23 1977-12-23 Refrigerator with freezing compartment - has two cooling circuits with condenser mounted in outer wall of freezing compartment to be in heat exchange with evaporator

Publications (2)

Publication Number Publication Date
EP0000217A1 true EP0000217A1 (de) 1979-01-10
EP0000217B1 EP0000217B1 (de) 1981-09-16

Family

ID=26645329

Family Applications (1)

Application Number Title Priority Date Filing Date
EP78200036A Expired EP0000217B1 (de) 1977-06-22 1978-06-12 Kühlschrank

Country Status (9)

Country Link
US (1) US4258554A (de)
EP (1) EP0000217B1 (de)
JP (1) JPS5410467A (de)
AR (1) AR217693A1 (de)
AU (1) AU519150B2 (de)
CA (1) CA1088333A (de)
DE (1) DE2861071D1 (de)
ES (1) ES470936A1 (de)
IT (1) IT1096563B (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2122734A (en) * 1982-06-29 1984-01-18 Philips Nv Refrigeration circuit of the motor-driven compressor type
EP0136458A1 (de) * 1983-08-08 1985-04-10 Firma Heinrich Bucher Behälter zum Kühlen eines Kühlgutes
FR2682746A1 (fr) * 1991-10-17 1993-04-23 Electroniques Mecaniques Et Echangeur de chaleur destine aux dissipateurs thermiques a effet caloduc et comportant une structure a plusieurs etages d'echanges thermiques.
EP2165135A1 (de) * 2007-05-25 2010-03-24 Lg Electronics Inc. Kühlsystem

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Publication number Priority date Publication date Assignee Title
FR2486638B1 (fr) * 1980-07-11 1986-03-28 Thomson Brandt Ensemble frigorifique a compartiments a temperatures differentes
SE0303227D0 (sv) * 2003-12-01 2003-12-01 Dometic Sweden Ab Defrosting
JP4387974B2 (ja) * 2005-04-25 2009-12-24 パナソニック株式会社 冷凍サイクル装置
US20120047917A1 (en) * 2010-08-27 2012-03-01 Alexander Rafalovich MODULAR REFRIGERATOR and ICEMAKER
CN104613804B (zh) * 2014-12-15 2017-03-01 青岛海尔股份有限公司 弯折管件及具有该弯折管件的半导体制冷冰箱
CN104567175B (zh) * 2014-12-15 2016-11-23 青岛海尔股份有限公司 半导体制冷冰箱
CN107289705B (zh) * 2016-03-30 2024-02-09 苏州圣荣元电子科技有限公司 一种低温冰箱

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DE723857C (de) * 1939-05-20 1942-08-12 Dornier Werke Gmbh Heizeinrichtung, insbesondere fuer Luftfahrzeuge
US2314190A (en) * 1941-02-21 1943-03-16 Gen Electric Refrigerating apparatus
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US2581044A (en) * 1949-09-17 1952-01-01 Jack A Ratcliff Refrigerating system
US3402761A (en) * 1967-02-17 1968-09-24 Navy Usa Controllable heat pipe apparatus
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NL6917311A (de) * 1968-12-05 1970-06-09
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NL6919338A (de) * 1969-12-24 1971-06-28
NL7403517A (de) * 1973-03-16 1974-09-18

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DE723857C (de) * 1939-05-20 1942-08-12 Dornier Werke Gmbh Heizeinrichtung, insbesondere fuer Luftfahrzeuge
US2314190A (en) * 1941-02-21 1943-03-16 Gen Electric Refrigerating apparatus
US2350348A (en) * 1942-12-21 1944-06-06 Gen Motors Corp Heat transfer device
US2421773A (en) * 1943-12-29 1947-06-10 Westinghouse Electric Corp Heat exchange apparatus in refrigeration systems
US2433187A (en) * 1945-05-25 1947-12-23 Westinghouse Electric Corp Controlled refrigerating apparatus with secondary refrigerating circuit
US2492648A (en) * 1945-11-10 1949-12-27 Westinghouse Electric Corp Two temperature refrigeration apparatus
US2581044A (en) * 1949-09-17 1952-01-01 Jack A Ratcliff Refrigerating system
US3402761A (en) * 1967-02-17 1968-09-24 Navy Usa Controllable heat pipe apparatus
DE1601010A1 (de) * 1967-08-19 1970-05-14 Bosch Hausgeraete Gmbh Kuehlgeraet,insbesondere Zweitemperaturen-Kuehlschrank
NL6917311A (de) * 1968-12-05 1970-06-09
US3525386A (en) * 1969-01-22 1970-08-25 Atomic Energy Commission Thermal control chamber
NL6919338A (de) * 1969-12-24 1971-06-28
NL7403517A (de) * 1973-03-16 1974-09-18

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Title
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2122734A (en) * 1982-06-29 1984-01-18 Philips Nv Refrigeration circuit of the motor-driven compressor type
EP0136458A1 (de) * 1983-08-08 1985-04-10 Firma Heinrich Bucher Behälter zum Kühlen eines Kühlgutes
FR2682746A1 (fr) * 1991-10-17 1993-04-23 Electroniques Mecaniques Et Echangeur de chaleur destine aux dissipateurs thermiques a effet caloduc et comportant une structure a plusieurs etages d'echanges thermiques.
EP2165135A1 (de) * 2007-05-25 2010-03-24 Lg Electronics Inc. Kühlsystem
EP2165135A4 (de) * 2007-05-25 2015-03-25 Lg Electronics Inc Kühlsystem

Also Published As

Publication number Publication date
IT1096563B (it) 1985-08-26
DE2861071D1 (en) 1981-12-03
ES470936A1 (es) 1979-02-01
JPS5410467A (en) 1979-01-26
IT7824625A0 (it) 1978-06-16
AU3723378A (en) 1980-01-03
AU519150B2 (en) 1981-11-12
JPS6337303B2 (de) 1988-07-25
EP0000217B1 (de) 1981-09-16
US4258554A (en) 1981-03-31
AR217693A1 (es) 1980-04-15
CA1088333A (en) 1980-10-28

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