EP0758732A2 - Réfrigérateur - Google Patents

Réfrigérateur Download PDF

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Publication number
EP0758732A2
EP0758732A2 EP96112307A EP96112307A EP0758732A2 EP 0758732 A2 EP0758732 A2 EP 0758732A2 EP 96112307 A EP96112307 A EP 96112307A EP 96112307 A EP96112307 A EP 96112307A EP 0758732 A2 EP0758732 A2 EP 0758732A2
Authority
EP
European Patent Office
Prior art keywords
evaporator
cooling
plate
normal
refrigerant
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
EP96112307A
Other languages
German (de)
English (en)
Other versions
EP0758732B1 (fr
EP0758732A3 (fr
Inventor
Eugen Schmid
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.)
Liebherr Hausgeraete Ochsenhausen GmbH
Liebherr Hausgeraete GmbH
Original Assignee
Liebherr Hausgeraete Ochsenhausen GmbH
Liebherr Hausgeraete 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
Priority claimed from DE29603716U external-priority patent/DE29603716U1/de
Application filed by Liebherr Hausgeraete Ochsenhausen GmbH, Liebherr Hausgeraete GmbH filed Critical Liebherr Hausgeraete Ochsenhausen GmbH
Publication of EP0758732A2 publication Critical patent/EP0758732A2/fr
Publication of EP0758732A3 publication Critical patent/EP0758732A3/fr
Application granted granted Critical
Publication of EP0758732B1 publication Critical patent/EP0758732B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F25B39/024—Evaporators with plate-like or laminated elements with elements constructed in the shape of a hollow panel
    • 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
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/04—Treating air flowing to refrigeration compartments
    • F25D2317/041—Treating air flowing to refrigeration compartments by purification
    • F25D2317/0411—Treating air flowing to refrigeration compartments by purification by dehumidification
    • 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
    • F25D2400/08—Refrigerator tables
    • 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
    • F25D2500/00—Problems to be solved
    • F25D2500/02—Geometry problems

Definitions

  • the invention relates to a cooling device with a normal cooling room, preferably with a normal cooling room and a freezer compartment, the evaporator of which consists of two evaporator sections connected in series with the refrigerant pipe sections, of which the section into which the compressor provided with a control device introduces the refrigerant Freezer is assigned.
  • the coherent evaporator system and the insulation of the device are designed so that at normal ambient temperatures (+16 ° C to +32 ° C) the freezer at certain positions of the temperature in the
  • the normal cooling room regulating thermostat maintains at least -18 ° C, while the normal cooling room may have temperatures between 0 ° C and +5 ° C depending on the position of the thermostat. For example, at an ambient temperature of 25 ° C and a temperature of 5 ° C in the normal cold room, this means a temperature difference from the ambient temperature to the normal cold room of 20 K and to the 3-star freezer compartment of 43 K. Because of these values, the insulation strength is about 3- Star freezer compartment of the refrigerator is generally much thicker than around the normal cold room.
  • the usual control of a refrigerator with freezer compartment is carried out by a thermostat, the temperature sensor is located in the normal cold room and preferably on the evaporator plate.
  • the switch-on values of this thermostat are designed so that the evaporator section for the normal cold room defrosts in every switch-off phase of the compressor. To do this, the temperature on the surface of the evaporator of the normal cold room must rise at least above 0 ° C. Switch-on values of the thermostat at 3 ° C to 5 ° C are common. This means that in the case in which the switch-on value of the thermostat is, for example, 5 ° C, when the ambient temperature falls below 5 ° C, the thermostat no longer switches on, so that the temperature in the freezer compartment inevitably rises.
  • the goods in the freezer compartment can then warm up to thaw, so that the refrigerator is no longer fully functional. Even at ambient temperatures above 5 ° C to about 9 ° C, there are still considerable problems in maintaining the required minimum temperature in the freezer compartment, since the relative duty cycle of the compressor is too short to provide the cooling capacity required for the evaporator compartment.
  • the refrigerator compartment evaporator In order to ensure that the minimum temperature in the freezer compartment is maintained even if the ambient temperature drops below the normal temperature, i.e. below 16 ° C, it is known to adjust the relative duty cycle of the compressor to the minimum required cooling capacity of the freezer compartment. In cooling devices that are highly insulated for the purpose of saving energy the cooling requirement for the refrigerator compartment is very small. Since the refrigerator compartment evaporator is connected in series with the freezer compartment evaporator, the refrigerator compartment evaporator also receives a relatively high amount of coolant as a result of the relative duty cycle of the compressor, which is matched to the cooling requirements of the freezer compartment. In order not to cool the normal cold room too much, the cold room evaporator is therefore made very small.
  • the cold room evaporator In addition to its function as a heat exchanger, the cold room evaporator also forms the dehumidification plate on which the condensate condenses, so that the condensed water can drip off specifically from the cold room evaporator in collecting channels and can be discharged via these, for example for the purpose of evaporation to the compressor.
  • the dehumidification area formed by the small cold room evaporator can become too small, so that condensation can form on other parts of the cold room, preferably on the cooling part ceiling, which is due to the adjacent freezer compartment may be at a lower temperature than the dew point, and on the glass plates. If condensate forms at locations other than on the cold room evaporator plate, the condensed water cannot be drained off specifically, but it also drips onto the refrigerated goods in an undesirable manner.
  • the object of the invention is therefore to provide a cooling device of the type specified, in which one leads to dripping Condensation on parts of the cold room other than the cold room evaporator is prevented.
  • this object is achieved in a cooling device of the type specified at the outset in that the evaporator or evaporator section assigned to the normal cooling space consists of a plate made of a good heat-conducting material, the size of which is designed for the area required for dehumidification, and that the plate is connected with the the refrigerant pipe section is connected so that it is supplied with the cooling capacity required for the normal cooling space at essentially the same temperature distribution.
  • cooling capacity is supplied to the normal cooling space through a small cooled area
  • the cooling capacity per area is too large.
  • Such a small, cooled surface with high cooling capacity means that dehumidification takes place essentially only in the vicinity of the cooling surface, so that the moisture accumulates in the areas of the normal cooling space which are further away from the surface supplying the cooling capacity.
  • the supply of the cooling capacity through a small area also has the disadvantage that this area can become iced up, as a result of which the cooling capacity drops.
  • the cooling capacity per area of the evaporator plate is reduced, so that it supplies the required cooling capacity with a reduced surface temperature.
  • the evaporator plate assigned to the normal cooling space is designed once so large that it forms a sufficiently large dehumidification surface and, on the other hand, is kept at a temperature such that it supplies the required cooling capacity.
  • the pipe section carrying the refrigerant can be connected to the cold room evaporator plate only over part of its length and / or material which is less conductive than heat, such that the normal cooling room is supplied with the required cooling capacity by thermal decoupling despite the enlarged plate.
  • the pipe section connected to the evaporator plate of the normal cooling space or running in this plate and carrying the refrigerant has a length corresponding to the heat output to be transmitted.
  • the pipe section can be connected directly to the evaporator plate by means of clamp connections or connections of a conventional type, or else can be integrated into the plate, as is the case with roll or Z-bond evaporator boards.
  • the pipe section carrying the refrigerant is connected to the plate at least over part of its length or runs in this and that the plate is provided with cutouts or window-like openings.
  • the plate is expediently provided with rows of recesses, the pipe sections carrying the refrigerant running between the rows.
  • the pipe sections carrying the refrigerant, apart from the rows on the edge only run between every other row of recesses.
  • the cold is only introduced from one side into each section of the evaporator plate, which is provided with the rows of recesses, so that there is a particularly good, uniform temperature distribution over the plate.
  • Condensed moisture condenses on parts whose temperature is below the dew point temperature.
  • the temperature of the evaporator plate of the cold room rises to above 0 ° C, which is necessary for defrosting the evaporator plate and the pipe section laid on it or the cold room walls behind which the evaporator is foamed. It is therefore possible that, for example, temporarily during the switch-off times of the compressor, the cooling compartment ceiling has a temperature which is below that of the evaporator plate and below the dew point temperature. Nevertheless, during the times in which the temperature of the refrigerator compartment ceiling is temporarily below that of the evaporator plate, not so much moisture should deposit on the refrigerator compartment ceiling that dripping can occur.
  • the thermal coupling of the tube section assigned to the normal cooling space to the evaporator plate of the normal cooling space is selected such that its temperature is substantially below the dew point temperature.
  • the size of the evaporator plate and its thermal coupling to the pipe section carrying the refrigerant are expediently chosen so that condensate which temporarily forms on the cooling part ceiling evaporates again and is then deposited on the evaporator plate of the normal cooling space when its temperature drops again after restarting the compressor the dew point temperature and the temperature of the refrigerator compartment ceiling.
  • the evaporator plate assigned to the normal cooling chamber is so large that it forms a sufficiently large dehumidification surface, and is thermally coupled to the pipe section carrying the refrigerant, or is only carried out for such a long time when the heat-conducting connection to the evaporator plate is complete that the surface temperature of the evaporator plate is just below the dew point.
  • an evaporator plate that is significantly enlarged in terms of area and forms a heat exchanger can be arranged in the normal cooling room, or the cooling capacity can be supplied through a much larger wall area of the normal cooling room if the evaporator is foamed in behind the cooling room wall, without the cooling capacity becoming too large for the normal cooling room and the cold room temperature drops too far.
  • the wall area through which the cooling capacity is supplied to the normal cold room can be significantly increased.
  • the recesses themselves are closed by the wall of the normal cooling space, which is made of a plastic plate, so that the temperature gradually decreases from the edges of the recesses to their central regions during the switching-on phases of the compressor, so that the recessed regions still participate in the transmission of the cooling capacity .
  • the arrangement of the recesses in the evaporator plate enables the direct connection of the pipe section carrying the refrigerant to it or the integration of this section into it, so that the reproducibility of the transfer of the cooling power to the evaporator plate is more favorable than with a point-only coupling or a coupling only over short distances or insulating materials to the evaporator plate.
  • By arranging the recesses in the evaporator plate this can be stretched over a desired larger area of the normal cold room inner wall.
  • the type of thermal coupling of the pipe section to the evaporator plate or the length of the pipe section connected to the evaporator plate and the size of the evaporator plate can be calculated or also determined empirically for the different types of cooling devices.
  • the area of the evaporator plate of the normal cooling room should be chosen so large that it fulfills its function as a dehumidifying plate, the thermal coupling of the dehumidifying and evaporating plate to the pipe section carrying the refrigerant or its length being carried out and selected such that the cooling capacity does not become too high and nevertheless the dew point temperature is not reached during the switch-on phases of the compressor.
  • the liquefied refrigerant is fed to the evaporator via a capillary tube, which forms a throttle element. Since the liquefied refrigerant has a relatively high temperature, the line leading the liquefied refrigerant to the capillary tube is laid in the suction line, via which the compressor sucks the evaporated refrigerant out of the evaporator. This cools the liquefied refrigerant, since the refrigerant vapor present in the intake pipe is still at a relatively low temperature. Nevertheless, the refrigerant expanded in the capillary tube is still at a higher temperature in front of it, so that the residual heat of the refrigerant must also be dissipated, which worsens the energy balance.
  • This supply of heat to the cold room evaporator plate is useful not only in the evaporator plate according to the invention, which is coupled to the pipe section carrying the refrigerant only with reduced heat conduction, but also in conventional cooling devices with a 3-star compartment. Because with cooling devices it is known to arrange a heating device in the normal cooling room or behind the wall of the normal cooling room at ambient temperatures below normal, which supplies the normal cooling room with heat if, due to the too small temperature difference between the temperature of the normal cooling room and the ambient temperature, the target temperature in the freezer compartment, the relative duty cycle of the compressor is no longer achieved. The supply of heat to the cold room evaporator through a section of the conduit carrying the liquefied refrigerant can therefore make an additional heating device in the normal cold room superfluous.
  • the transition area of the evaporator between the freezer evaporator section and the normal cold room evaporator section, which is located in the area of the normal cold room, is critical because this transition area is at a lower temperature than the main surface of the freezer evaporator is located, so that this transition part tends to freeze in an undesirable manner.
  • a section of the liquefied refrigerant leading to the capillary tube is laid in the transition area between the two evaporator sections in or near the normal cooling space.
  • This liquefied refrigerant line section is expediently in heat-conducting connection with the transition area, so that it is ensured that this critical transition area also defrosts during the downtimes of the compressor.
  • the conventional type of cooling device shown schematically with reference to FIGS. 3 and 4 consists of a housing 1 with an outer shell and an inner shell, with the space between the shells for Thermal insulation is foamed with a polyurethane foam.
  • the U-shaped curved evaporator section 3 assigned to the freezer compartment 2 is arranged behind the shell of the freezer compartment and foamed.
  • the evaporator section 5 assigned to the normal cooling space 4 is also foamed in behind the inner normal cooling space shell.
  • Both evaporator sections 3, 5 are bent out of a common roll or Z-bond evaporator board and connected to one another by a narrow board strip 6 in which the lines are arranged, through which the two evaporator sections are connected in series with one another.
  • the condenser 7 is arranged behind the rear wall of the cooling device in a conventional manner and the compressor 8 is located in a niche of the cooling device housing.
  • a thermostat 9 is arranged on the cooling space evaporator section and controls the starting frequency of the compressor.
  • FIG. 1 shows a refrigerator in which an evaporator plate 10 which is reduced in size in accordance with the low cooling requirement of the normal cooling space is arranged in the normal cooling space, the lower edge of which is designated by the dashed line 11.
  • an evaporator plate 10 which is reduced in size in accordance with the low cooling requirement of the normal cooling space is arranged in the normal cooling space, the lower edge of which is designated by the dashed line 11.
  • the normal cooling space evaporator plate 10 is enlarged by the dashed-line evaporator plates 12, which are connected in one piece to the bottom edge of the evaporator plate 10 shown in dashed lines.
  • the evaporator plate 10, 12 is connected to the evaporator plate only at the points marked by crosses 13.
  • connection of the pipe coil 14 carrying the refrigerant to the dehumidification evaporator plate 10, 12 only point by point or in sections can be carried out in the usual way by spot welding, crimping, gluing or by clamp connections.
  • 12 channels are provided in a conventional manner for collecting and draining the dripping water.
  • FIG. 2 shows a schematic plan view of an evaporator plate 15 foamed in behind the rear wall of a normal cooling space.
  • This consists of a so-called roll or Z-bond evaporator board, in which the tube section 16 carrying the refrigerant is arranged approximately with a rectangular shape.
  • the circuit board is provided with four rows of rectangular recesses 17 lying next to one another.
  • the horizontal run Branches of the pipe sections 16 in such a way between the rows of the recesses 17 that the cooling power is supplied to each row only from one horizontal branch of the pipe section 16.
  • the influence of the vertical branches of the pipe section is neglected. This could also be reduced by this enclosing lateral, gap-shaped recesses.
  • each row of the recesses 17 receives its cooling capacities essentially only from a horizontal branch of the tube section, these run on a circuit board with four rows of recesses between the first and second and between the third and fourth rows, so that they a distance of a from the upper and lower edge and aa from each other.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP19960112307 1995-08-16 1996-07-30 Réfrigérateur Expired - Lifetime EP0758732B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE29513175U 1995-08-16
DE29513175 1995-08-16
DE29603716U DE29603716U1 (de) 1995-08-16 1996-02-29 Kühlgerät
DE29603716U 1996-02-29

Publications (3)

Publication Number Publication Date
EP0758732A2 true EP0758732A2 (fr) 1997-02-19
EP0758732A3 EP0758732A3 (fr) 2000-07-12
EP0758732B1 EP0758732B1 (fr) 2002-12-04

Family

ID=26058140

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19960112307 Expired - Lifetime EP0758732B1 (fr) 1995-08-16 1996-07-30 Réfrigérateur

Country Status (2)

Country Link
EP (1) EP0758732B1 (fr)
ES (1) ES2099057T3 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0902244A2 (fr) 1997-09-15 1999-03-17 Liebherr-Hausgeräte Gmbh Appareil frigorifique avec un espace de réfrigération et un compartiment de congélation
EP0928934A3 (fr) * 1998-01-09 2000-03-22 Whirlpool Corporation Réfrigérateur ménager
DE20001253U1 (de) * 2000-01-25 2001-06-07 Liebherr-Hausgeräte GmbH, 88416 Ochsenhausen Kühlgerät mit einem Kühl-, einem Kaltlager- und einem Gefrierfach
EP1340950A1 (fr) * 2001-11-16 2003-09-03 Lg Electronics Inc. Réfrigérateur avec refroidissement direct
DE202023102953U1 (de) 2023-05-30 2023-06-21 BINDER GmbH Rollbond-Verdampfer-Platte
EP4471355A1 (fr) 2023-05-30 2024-12-04 Binder GmbH Plaque d'évaporateur à liaison par rouleau

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2390808A (en) * 1943-07-21 1945-12-11 Gen Electric Refrigerator
US2640329A (en) * 1949-09-24 1953-06-02 Ingvardsen Johan Freder Ingvar Cold plate with means to prevent condensation
FR2193186A1 (fr) * 1972-07-20 1974-02-15 Soissonnais Manufacture
FR2203687B1 (fr) * 1972-10-20 1975-06-13 Bonnet Ets
DD108809A1 (fr) * 1973-04-12 1974-10-05
DE3306869A1 (de) * 1983-02-26 1984-08-30 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Kuehlgeraet mit einem waermeuebertrager

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0902244A2 (fr) 1997-09-15 1999-03-17 Liebherr-Hausgeräte Gmbh Appareil frigorifique avec un espace de réfrigération et un compartiment de congélation
EP0928934A3 (fr) * 1998-01-09 2000-03-22 Whirlpool Corporation Réfrigérateur ménager
DE20001253U1 (de) * 2000-01-25 2001-06-07 Liebherr-Hausgeräte GmbH, 88416 Ochsenhausen Kühlgerät mit einem Kühl-, einem Kaltlager- und einem Gefrierfach
WO2001055655A1 (fr) 2000-01-25 2001-08-02 Liebherr-Hausgeräte GmbH Refrigerateur comportant un compartiment refrigere, un compartiment d'entreposage frigorifique et un compartiment de congelation
RU2233410C2 (ru) * 2000-01-25 2004-07-27 Либхерр-Хаузгерэте Гмбх Холодильный бытовой прибор
US7127904B2 (en) 2000-01-25 2006-10-31 Liebherr-Hausgeräte GmbH Refrigerating appliance comprising a refrigerating compartment, a cold storage compartment and a freezer compartment
EP1340950A1 (fr) * 2001-11-16 2003-09-03 Lg Electronics Inc. Réfrigérateur avec refroidissement direct
DE202023102953U1 (de) 2023-05-30 2023-06-21 BINDER GmbH Rollbond-Verdampfer-Platte
EP4471355A1 (fr) 2023-05-30 2024-12-04 Binder GmbH Plaque d'évaporateur à liaison par rouleau
DE102023114063A1 (de) 2023-05-30 2024-12-05 Binder Gmbh Rollbond-Verdampfer-Platte
US20240401850A1 (en) * 2023-05-30 2024-12-05 Binder Gmbh Roll Bond Evaporator Plate
DE102023114063B4 (de) * 2023-05-30 2025-10-16 Binder Gmbh Kältemittelkreis mit einer Rollbond-Verdampfer-Platte

Also Published As

Publication number Publication date
ES2099057T1 (es) 1997-05-16
EP0758732B1 (fr) 2002-12-04
EP0758732A3 (fr) 2000-07-12
ES2099057T3 (es) 2003-07-01

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