WO2010091951A2 - Appareil frigorifique avec une distribution plus régulière de la température - Google Patents

Appareil frigorifique avec une distribution plus régulière de la température Download PDF

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Publication number
WO2010091951A2
WO2010091951A2 PCT/EP2010/050899 EP2010050899W WO2010091951A2 WO 2010091951 A2 WO2010091951 A2 WO 2010091951A2 EP 2010050899 W EP2010050899 W EP 2010050899W WO 2010091951 A2 WO2010091951 A2 WO 2010091951A2
Authority
WO
WIPO (PCT)
Prior art keywords
appliance according
refrigerating appliance
evaporator
injection
segments
Prior art date
Application number
PCT/EP2010/050899
Other languages
German (de)
English (en)
Other versions
WO2010091951A3 (fr
Inventor
Bernd Schlögel
Walter Woldenberg
Original Assignee
BSH Bosch und Siemens Hausgeräte GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BSH Bosch und Siemens Hausgeräte GmbH filed Critical BSH Bosch und Siemens Hausgeräte GmbH
Priority to EP10701855A priority Critical patent/EP2396610A2/fr
Publication of WO2010091951A2 publication Critical patent/WO2010091951A2/fr
Publication of WO2010091951A3 publication Critical patent/WO2010091951A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • 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
    • 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
    • F25D25/00—Charging, supporting, and discharging the articles to be cooled
    • F25D25/02—Charging, supporting, and discharging the articles to be cooled by shelves
    • F25D25/028—Cooled supporting means

Definitions

  • the present invention relates to a refrigerator, in particular a household refrigerator.
  • the evaporator of such a refrigerating appliance usually has a refrigerant pipe guided in numerous loops, into which liquid refrigerant is injected at one end, while at the other end evaporated refrigerant is sucked off.
  • the cooling capacity is distributed unevenly on such an evaporator, on the one hand because the temperature of the refrigerant is lowest immediately after passing through the injection point and on the other hand because the maximum achievable at a given point of the refrigerant line cooling capacity is limited by the flow rate of liquid refrigerant, which, of course, becomes progressively smaller due to the evaporation progressing on the way from the point of injection to the suction connection.
  • the injection point is usually arranged at an upper and the suction connection at a lower end of the evaporator, so that the available cooling capacity in the upper region of the evaporator is higher and cooled air there due to its relatively high density can flow from alone into a lower area of the storage chamber.
  • the temperature at the warmest point in the storage chamber must be used as a reference for the control of the compressor operation.
  • the temperature at the warmest point in the storage chamber must be used as a reference for the control of the compressor operation.
  • DE 10 2007 016 849 A1 discloses a refrigeration device with three storage zones held at different temperatures, in which one storage zone is assigned an evaporator with two injection points and two refrigerant lines extending side by side over the surface of the evaporator from these injection points. One of these lines is connected in series with an evaporator of the second storage zone, the other with an evaporator of the third storage zone. An effect on the temperature distribution in the first storage zone does not duplicate the injection point at the evaporator.
  • Refrigeration appliances are also known in which a homogeneous temperature distribution in a storage chamber is achieved by means of a fan, which ensures increased air circulation in the storage chamber.
  • the fan affects the efficiency of such a refrigerator in several ways.
  • the operation of the fan directly leads to increased energy consumption of the device, on the other hand, the fan gives its waste heat mostly to the storage chamber whose air it circulates, with the result that the waste heat ultimately has to be eliminated via the evaporator of the chamber and in turn the energy demand for cooling increases.
  • Object of the present invention is therefore to provide a refrigeration device that achieves a homogeneous temperature distribution even in a large-sized storage chamber with purely passive, no drive energy consuming means.
  • the object is achieved in which in a refrigerator with a thermally insulated
  • the injection points are clearly spatially separated from each other, more specifically, that the two injection points are separated by a portion of the evaporator, which is cooled solely by supplied at one of the injection points refrigerant.
  • the spatial separation of the injection points results in two locally coldest points spaced apart in the storage chamber, whereby the distance between a locally coldest point and a locally or globally warmest Point of the chamber and, accordingly, also reduces the temperature gradient occurring at this distance.
  • the distance between the injection points is a multiple of the distance between adjacent line sections of the evaporator.
  • a uniform refrigerant line may extend from the at least two spaced-apart injection points to a common suction point of the evaporator.
  • this refrigerant line comprises two line sections, each starting from one of the injection points, which meet at a T-piece.
  • a suction line is connected to this tee at the same time, which leads to a refrigerant compressor.
  • the refrigerant piping may include an upstream pipe section extending from a first one of the injection sites to the second injection site, and a downstream pipe section extending from the second injection site to a suction pipe.
  • the refrigerant flows from the first and the second injection point mix on the downstream line section.
  • the cooling capacity of both line sections is at least approximately equal.
  • the line sections - in particular at a wire tube evaporator - be at least approximately the same length.
  • the sizing of the line cross sections for at least approximately the same residence times of the refrigerant in the two line sections can be taken care of.
  • the evaporator may be divided into a plurality of segments, each of the two pipe sections cooling at least one of the segments alone.
  • the segments are preferably formed as a wire tube evaporator, that is, they comprise an in-plane meandering piece of pipe and a plurality of wires, each of which is fastened to the pipe piece at a plurality of crossing points.
  • These segments are conveniently arranged in several horizontal planes one above the other in the storage chamber to divide them into several superposed compartments.
  • the injection points are preferably arranged on an uppermost and a lowermost of the segments.
  • the first injection point is located at an uppermost segment, while the suction line extends from a lowermost of the segments.
  • the second injection point is preferably arranged on a pipe piece connecting two segments.
  • FIG. 1 is a perspective view of an inner container of a refrigerator with an evaporator mounted therein according to the invention.
  • FIG. 2 is a perspective view of a wire tube type evaporator according to a first embodiment of the invention
  • Fig. 3 is a perspective view of the evaporator according to a second
  • FIG. 4 shows a plate evaporator analogous to FIG. 2; FIG. and
  • Fig. 5 is a similar to Fig. 3 plate evaporator.
  • Fig. 1 illustrates the problem of the invention with reference to the perspective view of an inner container 1 of a household freezer with evaporator mounted therein 2.
  • the evaporator 2 is divided into a plurality of superposed, held in grooves 3 on the side walls of the inner container 1 plate-shaped wire tube evaporator.
  • the spaces between the wires 6 with frost there is virtually no exchange of air between the compartments of the inner container 1 more. If these subjects also record closed-bottom drawers 7, convection in the inner container 1 is completely excluded.
  • the evaporator 2 of a first embodiment of the invention results in the structure shown in Fig. 2 in a perspective view obliquely from behind.
  • suction line 8 branch off two throttle tubes 9, 10, which, when the compressor is in operation, lead liquid refrigerant. They rise along a rear corner of the inner container 1, namely the throttle tube 9 of the highest point to an injection point 11 at 4-1 designated here evaporator segment, the throttle tube 10, however, to an injection point 12 of a pipe section, which is approximately halfway up the evaporator 2 segments 4-4, 4-5 connecting together.
  • the suction line 8 is connected to the lowest-lying evaporator segment 4-7.
  • the segments 4-1 to 4-4 are cooled exclusively by refrigerant supplied via the throttle pipe 9
  • the segments 4-5 to 4-7 are cooled by a mixture of the refrigerant from the throttle pipe 9 with fresh refrigerant from the throttle pipe 10.
  • the segment 4-5 reaches a lower temperature than the immediately above segment 4-4.
  • a temperature profile is thus obtained which drops from a locally high temperature at the bottom of the inner container 1 to a first local minimum at the level of the segment 4-5, in the vicinity of segment 4-4 again reaches a local maximum and has a second local minimum at segment 4-1.
  • the spatial distance between maximum and minimum temperature is thus significantly reduced, and heat flow through the chilled goods can contribute to a much greater extent to a compensation of the temperature differences, as is possible with a continuous over the entire height of the inner container 1 temperature gradient.
  • the flow rates of the throttle tubes 9 and 10 are set appropriately, thus, the difference between the highest and lowest temperature in the inner container 1 can be significantly reduced. If throttle tubes 9 and 10 are used of the same cross-section, the ratio of their throughputs over the length of the throttle tubes used can be adjusted. Since the area of the evaporator 2 below the injection point 12 is smaller than above and in the lower region usually still a balance of the cooling capacity of the refrigerant from the upper injection point 1 1 is available, the flow rate of the throttle tube 10 should be smaller than that of the throttle tube 9 be. In order to accommodate the tube length required for this purpose, 10 loops 13 are formed in the throttle tube.
  • suction and second injection point 12 are reversed.
  • the suction line 8 starts from a piece of pipe between the segments 4-4 and 4-5, and in the suction line 8 countercurrently guided throttle pipes 9, 10 emerge from this in the vicinity of the located between the segments 4-4 and 4-5 suction port 14 up and down to pass into injection ports 1 1, 12 of the uppermost and lowermost segment 4-1, 4-7.
  • locally coldest points of the inner container 1 are respectively at the level of the segments 4-1, 4-7, while the warmest region is at the level of the segments 4-4, 4-5. While in the embodiment of FIG.
  • FIGs. 4 and 5 show the application of the principle of the invention to a
  • evaporator On a one-piece evaporator plate an injection point 1 1 are arranged at an upper corner and a suction port 14 at a lower corner in a conventional manner. In about the middle of a connecting the terminals 11, 14 edge of the evaporator plate, a second injection point 12 is formed, which opens into the same refrigerant line as the upper injection point 11.
  • the refrigerant line extends across the board in meanders with mutually parallel line sections 15.
  • injection ports 11, 12 are disposed at upper and lower corners of the board, and a refrigerant piping passes over board sections 17-1, 17-2 to a suction port located centrally between the injection ports. Since the areas 17-1, 17-2 cooled in each case exclusively via one of the injection points 11, 12 are essentially the same area and the line sections running on them are of equal length, the cooling capacity of the sections 17-1, 17-2 is the same here as well, when both injection points 1 1, 12 are acted upon simultaneously with refrigerant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

L'invention concerne un appareil frigorifique avec une chambre de stockage (1) isolée thermiquement et un évaporateur (4) qui refroidit la chambre de stockage (1) et qui comprend au moins deux points d'injection (11, 12). Les deux points d'injection (11, 12) sont séparés par une partie (4-1, 4-2,..., 4-4; 17-1) de l'évaporateur qui est uniquement refroidie par le fluide frigorifique amené à l'un des points d'injection (11).
PCT/EP2010/050899 2009-02-13 2010-01-27 Appareil frigorifique avec une distribution plus régulière de la température WO2010091951A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10701855A EP2396610A2 (fr) 2009-02-13 2010-01-27 Appareil frigorifique avec une distribution plus régulière de la température

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009000840.3 2009-02-13
DE102009000840A DE102009000840A1 (de) 2009-02-13 2009-02-13 Kältegerät mit vergleichmäßiger Temperaturverteilung

Publications (2)

Publication Number Publication Date
WO2010091951A2 true WO2010091951A2 (fr) 2010-08-19
WO2010091951A3 WO2010091951A3 (fr) 2011-03-31

Family

ID=41723091

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/050899 WO2010091951A2 (fr) 2009-02-13 2010-01-27 Appareil frigorifique avec une distribution plus régulière de la température

Country Status (3)

Country Link
EP (1) EP2396610A2 (fr)
DE (1) DE102009000840A1 (fr)
WO (1) WO2010091951A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105157335A (zh) * 2015-07-09 2015-12-16 中国海洋大学 一种自动收纳食物的冰箱抽屉

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19756860A1 (de) 1997-12-19 1999-06-24 Bosch Siemens Hausgeraete Kältegerät
WO2007074094A1 (fr) 2005-12-29 2007-07-05 Arcelik Anonim Sirketi Dispositif de refroidissement
DE102007016849A1 (de) 2007-04-10 2008-10-16 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit drei Temperaturzonen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19756860A1 (de) 1997-12-19 1999-06-24 Bosch Siemens Hausgeraete Kältegerät
WO2007074094A1 (fr) 2005-12-29 2007-07-05 Arcelik Anonim Sirketi Dispositif de refroidissement
DE102007016849A1 (de) 2007-04-10 2008-10-16 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit drei Temperaturzonen

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105157335A (zh) * 2015-07-09 2015-12-16 中国海洋大学 一种自动收纳食物的冰箱抽屉
CN105157335B (zh) * 2015-07-09 2017-12-05 中国海洋大学 一种自动收纳食物的冰箱抽屉

Also Published As

Publication number Publication date
DE102009000840A1 (de) 2010-08-19
WO2010091951A3 (fr) 2011-03-31
EP2396610A2 (fr) 2011-12-21

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