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
  • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
  • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
• • 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
  • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
• • 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
  • F25B2400/16—Receivers
• • 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
  • F25B2600/00—Control issues
  • F25B2600/25—Control of valves
  • F25B2600/2511—Evaporator distribution valves
• • 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

Definitions

• the invention relates to a refrigeration device with a heat-insulating housing, within which there are at least two heat-insulating separate refrigeration compartments, each with a different freezer temperature, which are each cooled by an evaporator with a corresponding cooling capacity, each of which has an upstream throttle device on the inflow side and which each have at least one control means
• refrigerant compressors with an upstream refrigerant accumulator on the suction side are subjected to forced, non-circulated refrigerant, which at least to a certain extent accumulates in a refrigerant guide section of the evaporator of higher refrigeration capacity in the standstill phase of the refrigerant compressor.
• Such an arrangement allows a separate temperature control of the compartments cooled by these evaporators, but this interconnection entails that during the downtime of the refrigerant compressor in the freezer compartment evaporator, due to the temperature and pressure difference to the refrigerator compartment evaporator, a certain amount of refrigerant shift to the freezer compartment evaporator occurs, which results in a cooling request from the cooling compartment, only a reduced amount of refrigerant for cooling tion of the refrigerator compartment evaporator is available and thus either delay times or even malfunctions can occur.
• the invention has for its object to design a refrigeration appliance according to the preamble of claim 1 with simple constructive measures such that on the one hand the disadvantages of the prior art are avoided and on the other hand a separate temperature control of the refrigeration compartments is possible.
• the refrigerant guide section is designed for at least approximately its complete filling with liquid refrigerant during the idle time of the compressor with regard to its refrigerant absorption volume.
• the freezer compartment evaporator Due to the design of the freezer compartment evaporator according to the invention, when the refrigeration compartment starts to cool when the refrigerant compressor starts up, pressure is exerted on the liquid refrigerant accumulated in this refrigerant guide section during the downtime of the refrigerant compressor, as a result of which it is transported from the freezer compartment evaporator to a refrigerant collector immediately after the compressor starts up from this is available for cooling the refrigerator compartment evaporator.
• the refrigerant absorption volume of the refrigerant guide section is dimensioned smaller than the amount of liquid refrigerant accumulating in the evaporator of higher refrigeration capacity during the idle time of the refrigerant compressor.
• the evaporator with a higher refrigeration capacity is particularly advantageous if, according to a next preferred embodiment of the object of the invention, it is provided that the evaporator with a higher refrigeration capacity is designed as a freezer compartment evaporator whose refrigerant guide section, which is the lowest in the functional position of the refrigeration device, is dimensioned to be smaller in terms of its refrigerant absorption volume than that amount of refrigerant accumulating there while the refrigerant compressor is standing.
• Complete filling of the refrigerant guide section can be achieved in the case of an evaporator made of a composite plate, for example by a corresponding reduction in the channel cross section.
• the evaporator of higher cooling capacity is designed as an evaporator system with a plurality of evaporator levels arranged one above the other at a distance.
• both plate-like evaporator planes and so-called wire-tube evaporators have proven successful, with the last type of evaporator, the refrigerant guide section which is at least completely filled with liquid refrigerant during the standing time of the compressor being designed through a meandering tubular section.
• the refrigerant collector is embedded in the heat insulation material of the heat-insulating housing.
• the refrigerant collector in the collecting area is one for collecting the Steamer gutter provided steamer with lower cooling capacity is provided.
• Such an arrangement of the refrigerant collector makes thermal insulation to avoid condensation for the latter, since the condensation water that occurs in the event of condensation of the refrigerant collector is introduced directly into the existing condensate collecting channel.
• Fig. 1 is a refrigerator and freezer combination, the cooling compartment and the freezer compartment is cooled separately from evaporators arranged in parallel, of which the freezer evaporator at its bottom portion is at least almost completely filled with liquid refrigerant in the standstill phase of the refrigerant compressor, in a spatial view from the side and
• FIG. 2 shows a detail of an enlarged section of a channel section of the freezer compartment evaporator filled with liquid refrigerant.
• Fig. 1 shows a simplified schematic representation of a refrigerator and freezer combination 10 with a heat-insulating housing 11, the interior of which is divided by a heat-insulating, horizontally arranged intermediate wall 12 into two sections, of which the higher section is designed as a cooling compartment 13.
• a circuit board-like evaporator is provided with a refrigerant channel 15, which has a refrigerant injection point 16 at its inflow end.
• a freezer compartment 17 is provided within the heat-insulating housing 11, which is formed by an evaporator 18, for example, designed as a wire tube evaporator with three vertical distances in the present case.
• evaporator planes 19, 20 and 21, which are arranged one another by appropriate shaping of a single pipeline, are cooled.
• the near-bottom evaporator level 21 like the two other evaporator levels 19 and 20, has a refrigerant guide section 22 formed from a continuous, meandering-shaped pipeline, which, due to its dimensions, namely its inside diameter and its length, has a cold absorption volume which is at least complete Filling of the refrigerant guide section 22 with liquid refrigerant 23 (see FIG.
• a connecting line 24 adjoins the refrigerant guide section 22, which has an installation position which favors its complete filling, which opens into a branch point 25, to which the end of the cooling compartment evaporator 14 on the outside is also guided.
• the branch point 25 is connected via a connecting line 26 to a refrigerant collector 27 designed as a steam dome, which is embedded in the thermal insulation of the intermediate floor 12 to avoid condensation in the cooling operation of the refrigerator compartment evaporator.
• the refrigerant collector 27 is connected via a suction line 28 to a refrigerant compressor 29 which is connected on the pressure side to a condenser 30, the output side of which is connected, for example, to an electrically controllable 3/2 way solenoid valve 31.
• the 3/2-way solenoid valve 31 is used to control the refrigerant 23, which is forcibly rolled by the refrigerant compressor 29, to the evaporators
• the solenoid valve 31 in a control position I deflecting the liquid refrigerant 24 via a throttle 32 to the freezer compartment evaporator 18, where it is guided to its cooling via its levels 19 to 21.
• the refrigerant compressor 29 When the refrigerant compressor 29 is in operation, the refrigerant 23 flows from the drain-side end of the evaporator level 21 via the connecting line 24 to the branch point 25 and from there to
• the solenoid valve 31 has a control position II in which the forcibly circulated liquid refrigerant 23 is supplied to the evaporator 14 via a throttle 33 connected upstream of the evaporator 14, from which it is supplied at its outflow end via the branch point 25 and the refrigerant collector 27 via the suction line 28, the refrigerant compressor 29 is in turn supplied.

Priority Applications (1)

Applications Claiming Priority (3)

Publications (2)

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Family Applications (1)

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• 1999
  • 1999-11-30 DE DE19957719A patent/DE19957719A1/de not_active Withdrawn
• 2000
  • 2000-10-26 EP EP00975926A patent/EP1240466B1/fr not_active Expired - Lifetime
  • 2000-10-26 AT AT00975926T patent/ATE298413T1/de not_active IP Right Cessation
  • 2000-10-26 WO PCT/EP2000/010556 patent/WO2001040721A1/fr active Search and Examination
  • 2000-10-26 CN CNB00816410XA patent/CN100398948C/zh not_active Expired - Fee Related
  • 2000-10-26 BR BR0015829-1A patent/BR0015829A/pt active Search and Examination
  • 2000-10-26 TR TR2002/01200T patent/TR200201200T2/xx unknown
  • 2000-10-26 ES ES00975926T patent/ES2243321T3/es not_active Expired - Lifetime
  • 2000-10-26 DE DE50010611T patent/DE50010611D1/de not_active Expired - Fee Related
• 2002
  • 2002-05-30 US US10/158,033 patent/US6655170B2/en not_active Expired - Fee Related

Non-Patent Citations (1)

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