Classifications

• • C—CHEMISTRY; METALLURGY
  • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
  • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
  • C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
  • C09K5/02—Materials undergoing a change of physical state when used
  • C09K5/06—Materials undergoing a change of physical state when used the change of state being from liquid to solid or vice versa
  • C09K5/063—Materials absorbing or liberating heat during crystallisation; Heat storage materials
• • 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
  • F25D11/006—Self-contained movable devices, e.g. domestic refrigerators with cold storage accumulators
• • 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
  • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
  • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
  • F28D20/023—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat the latent heat storage material being enclosed in granular particles or dispersed in a porous, fibrous or cellular structure
• • 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
  • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
  • F28D2020/0004—Particular heat storage apparatus
  • F28D2020/0013—Particular heat storage apparatus the heat storage material being enclosed in elements attached to or integral with heat exchange conduits
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
  • Y02E60/14—Thermal energy storage

Definitions

• the present invention relates to a refrigeration appliance, in particular a domestic refrigeration appliance, with a storage chamber for refrigerated goods, arranged in thermal contact with the storage chamber, for holding the storage chamber in a predetermined temperature range intermittently operating evaporator and a heat storage associated with the evaporator, which contains a storage medium, the in each case changes its state of aggregation in operating and resting phases of the evaporator.
• a refrigerator of this type is known from DE 10 2004 035 017 A1.
• the temperatures of a condenser and an evaporator are similar to those of the environment of the refrigeration device or a storage chamber cooled by the evaporator.
• energy must therefore be expended each time to detect a temperature difference between the condenser and the environment or evaporator and evaporator
• the object of the invention is to provide a refrigerator with heat storage, which allows energy-efficient operation even with low heat capacity of the heat storage.
• a refrigeration device is in particular a household refrigeration appliance understood, ie a refrigeration appliance for household management in households or possibly in the
• Gastronomy area is used, and in particular serves to store food and / or drinks in household quantities at certain temperatures, such as For example, a refrigerator, a freezer, a fridge freezer, a freezer or a wine storage cabinet.
• phase transition temperature of the storage medium closer to the predetermined in a refrigeration device of the type defined
• the contact of the heat accumulator to the evaporator causes it, as long as the storage medium of the heat accumulator is not frozen, can not cool far below the melting temperature of the storage medium. In particular, it can not reach the limit temperature as long as the storage medium is not completely frozen.
• a high vapor pressure of the refrigerant is ensured in the evaporator.
• a consequent large amount of the refrigerant is circulated, and since the friction and other losses of the compressor are substantially proportional to the volumetric flow rate, the compressor operates with high efficiency. Only when the storage medium is completely frozen, the evaporator can continue to cool, with the result that proportional to the reduction of the
• the difference between the phase transition temperature of the storage medium and the attainable limit temperature should preferably be at least 10 ° C, i. in the case of the evaporator of a normal or fresh refrigerated compartment, which can reach a temperature of -20 ° C in continuous operation, the melting temperature of the
• Storage medium should not be below -10 ° C.
• a melting temperature of the storage medium of below -2 ° C is preferred, so that any necessary defrosting of the evaporator is not delayed by the fact that at the same time the heat storage medium must be melted.
• an aqueous solution is generally suitable, in particular, a solution of ethylene glycol or urea.
• the capacity of a storage chamber of the refrigerator not appreciably affecting amount of storage medium is sufficient.
• the amount of the storage medium is adjusted to the cooling capacity of the evaporator, that at most 20 minutes evaporator operation sufficient to freeze the storage medium. Too little amount of storage medium needed to freeze the
• the average duration of an operating phase of an evaporator should be longer than the time required to freeze the storage medium in order to fully exploit its potential for action. On the other hand, it should not be much longer, in particular maximally twice as long as the time required for freezing the storage medium to the proportion of time in which the temperature of the evaporator well below the
• Freezing temperature of the storage medium is located and the energy efficiency of the evaporator is correspondingly limited to keep the total operating time of the refrigerator low.
• Temperature sensor can be used, which is located close enough to the evaporator or the heat storage, to a complete freezing of the
• Storage medium to detect the following temperature decrease, or it can
• Timer be provided, the operating phases of the compressor in each case to a limited in advance, sufficient for complete freezing of the storage medium sufficient time.
• the storage medium is expedient for the storage medium to be finely distributed in the heat store. This can e.g. can be achieved by the storage medium is bound in a plastic matrix of the heat accumulator.
• the heat accumulator may comprise a carrier material in which the storage medium is droplet-wise bound in cells.
• a particularly high stability of the storage medium and good handling of the carrier material can be achieved if the storage medium is contained in capsules which are embedded in the carrier material. If the material of the capsules at a
• the carrier material is soft, it is for example possible to form the carrier material together with the capsules contained therein thermoplastic to produce the heat storage.
• the heat storage when the evaporator is arranged in the storage chamber is particularly effective.
• the invention is also e.g. applicable to a coldwall evaporator located outside the storage chamber, between this and one
• Insulation material layer of the refrigeration device is arranged, but the gain in efficiency at a arranged in the storage chamber evaporator is greater.
• the heat accumulator is preferably arranged in physical contact with the evaporator.
• the evaporator is plate-shaped, a close thermal contact between the evaporator and the heat storage can be achieved if one side of the evaporator is at least predominantly covered by the heat storage.
• the heat storage is preferably located on a side facing away from the wall of the evaporator, so that refrigerated goods in the storage chamber is substantially cooled by the heat storage therethrough. If the evaporator is a roll-bond or tube-on-sheet evaporator, the
• FIG. 1 shows a schematic cross section through an inventive refrigeration device; FIG. an enlarged detail of Figure 1 according to a first embodiment. the same detail according to a second embodiment; typical temperature curves of conventional evaporators and an evaporator according to the present invention during an operation phase and subsequently; and a typical temperature profile of an evaporator according to the present invention during a defrosting phase.
• Fig. 1 shows a household refrigerator according to the present invention in a schematic section along a vertical sectional plane.
• a body 1 and a door 2 abutting thereon surround a storage chamber 3.
• the body 1 and the door 2 each comprise, in a manner known per se, a solid outer shell, an inner shell and a heat insulating layer of foam, which fills a space between the shells.
• a plate-shaped evaporator 5 is mounted at a small distance to a rear wall 4 of the body 1.
• the evaporator 5 may be a rollbond evaporator or a tube-on-sheet evaporator. Both types of evaporators include
• circuit board 6 having a planar first major surface of the
• Evaporator forms, and a refrigerant pipe 8 in the form of a recessed in a second board 7 channel or a side soldered to the board 6 pipe protrudes on the opposite second main surface of the evaporator 5.
• the first, planar main surface is here facing the part of the storage chamber 3 which can be used for refrigerated goods, while the main surface of the rear wall 4 carrying the refrigerant line 8 faces to form a narrow gap 9.
• the free arrangement within the storage chamber 3 allows the evaporator 5 to exchange heat with the storage chamber 3 via its two main surfaces. The dimensions of the evaporator 5 can therefore be kept low compared to a coldwall evaporator.
• the major part of the storage chamber 3 facing planar main surface is completely or almost completely covered by a heat storage 10.
• the heat storage 10 is a foil or a thin plate with a thickness of a few millimeters of a plastic substrate in which a storage medium is bound.
• an aqueous solution of e.g. Ethylene glycol or urea may be homogeneously distributed in the matrix of the plastic material, or may fill in small droplets of the plastic material in droplet form.
• a compressor 15 and a condenser, which supply the evaporator 5 with liquid refrigerant, are housed in a machine room niche at the bottom of the rear wall 4.
• a temperature sensor 16, which turns on the compressor 15 when exceeding a user-set threshold temperature, is arranged in a conventional manner away from the evaporator 5 to the storage chamber 3. Due to the distance from the heat storage 10 leaves the temperature sensor 16 in an operating phase of the
• Compressor 15 detected temperature no safe conclusion on the
• FIG. 2 shows an enlarged schematic section through the heat accumulator 10 and the supporting board 6, in which a plurality of randomly distributed, with the
• Storage medium filled cavities 1 1 different size in the carrier material 14 of the heat accumulator 10 can be seen.
• the cavities 1 1 are spherical, and the thickness of walls of the substrate 14, the adjacent cavities 1 1 separate, is of the same order of magnitude
• the substrate 14 could form a closed cell foam, i. the cavities 1 1 would no longer be spherical, as shown in the figure, but would have the shape of irregular, each separated by thin membranes of the carrier material and filled with the storage medium polyhedron.
• the storage medium 12 is encapsulated in thin-walled, diffusion-tight plastic hollow spheres 13, which in turn are embedded in the carrier material 14.
• the encapsulation allows convenient manufacture of the heat accumulator 10 by mixing the capsules under the support material and forming the mixture into sheets of the desired thickness.
• FIG. 4 shows a comparison of typical temperature profiles of the evaporator 5 of the type shown in FIG. 1 with a heat accumulator 10, an evaporator without a heat accumulator arranged free in a storage chamber and a coldwall evaporator.
• the vapor pressure in the evaporator has therefore by far the majority of the
• Evaporator connected compressor must compress a large volume to suck a given mass of the refrigerant from the evaporator, and to the
• the curve C shows the temperature profile for the evaporator 5 of the refrigeration device from FIG. 1.
• the speed of cooling corresponds approximately to curve B, since the heat capacity of the heat accumulator 10 in this temperature range is comparable to that of the inner shell and the insulation layer in the Coldwall evaporator.
• the freezing temperature of -5 ° C
• Storage medium 12 of the heat accumulator 10 reaches.
• the temperature now remains substantially constant until the storage medium 12 is completely frozen. As long as this is the case, the vapor pressure in the evaporator 5 is high, and the refrigerant can be circulated efficiently. Only after the complete freezing of the
• a second temperature sensor 17 on the evaporator To control evaporator temperature and to avoid long-term operation at low temperature, a second temperature sensor 17 on the evaporator. 5
• Storage chamber influenced is a control by a timer, which is set when switching on the compressor 15 in motion and this after a
• a value of 100 watts is used as the cooling capacity of the evaporator 5 in an operating phase and, for the sake of simplicity, assumes that it cools only the heat accumulator 10, but not the surrounding storage chamber 3, then the heat accumulator 10 is freeze until complete freezing
• Storage medium 12 in a period of about 15 minutes extracted heat 750 kJ. The freed when freezing an aqueous storage medium
• Latent heat is about 300 J / g. It is therefore sufficient for a quantity of approx. 250 g of the
• Storage medium 12 to obtain a 15 minute freezing phase. Assuming that these 250g of the storage medium 12 spread over an area of the evaporator 5 of, for example, 40 x 40 cm, then accounts for each cm 2 of the evaporator about 0.15 g of
• Storage medium 12 This shows that a layer thickness of the heat accumulator 10 of a few mm sufficient to realize the temperature profile of the curve C.
• Defrosting of the evaporator 5 is required at regular intervals.
• the next operating phase of the evaporator 5 is delayed, resulting in the temperature profile shown in Fig. 5.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• Combustion & Propulsion (AREA)
• General Engineering & Computer Science (AREA)
• Chemical Kinetics & Catalysis (AREA)
• Dispersion Chemistry (AREA)
• Organic Chemistry (AREA)
• Materials Engineering (AREA)
• Devices That Are Associated With Refrigeration Equipment (AREA)
• Air Conditioning Control Device (AREA)
• Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

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• 2011
  • 2011-05-19 WO PCT/EP2011/058117 patent/WO2012123036A1/de active Application Filing
  • 2011-05-19 EP EP11720119.4A patent/EP2686623A1/de not_active Withdrawn
  • 2011-05-19 CN CN201180069292.9A patent/CN103597300B/zh not_active Expired - Fee Related
  • 2011-05-20 DE DE102011076169A patent/DE102011076169A1/de not_active Withdrawn
• 2012
  • 2012-03-02 WO PCT/EP2012/053657 patent/WO2012123271A2/de active Application Filing
  • 2012-03-02 WO PCT/EP2012/053632 patent/WO2012123268A2/de active Application Filing
  • 2012-03-02 EP EP12706608.2A patent/EP2686624B1/de active Active
  • 2012-03-02 PL PL12706608T patent/PL2686624T3/pl unknown
  • 2012-03-02 CN CN201280013536.6A patent/CN103443565B/zh active Active
  • 2012-03-02 ES ES12706608.2T patent/ES2547812T3/es active Active

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