WO2013000773A2 - Appareil de froid à bac d'évaporation et dispositif auxiliaire favorisant l'évaporation - Google Patents

Appareil de froid à bac d'évaporation et dispositif auxiliaire favorisant l'évaporation Download PDF

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Publication number
WO2013000773A2
WO2013000773A2 PCT/EP2012/061758 EP2012061758W WO2013000773A2 WO 2013000773 A2 WO2013000773 A2 WO 2013000773A2 EP 2012061758 W EP2012061758 W EP 2012061758W WO 2013000773 A2 WO2013000773 A2 WO 2013000773A2
Authority
WO
WIPO (PCT)
Prior art keywords
control unit
compressor
temperature
storage chamber
auxiliary device
Prior art date
Application number
PCT/EP2012/061758
Other languages
German (de)
English (en)
Other versions
WO2013000773A3 (fr
Inventor
Adolf Feinauer
Hans Ihle
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
Publication of WO2013000773A2 publication Critical patent/WO2013000773A2/fr
Publication of WO2013000773A3 publication Critical patent/WO2013000773A3/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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/14—Collecting or removing condensed and defrost water; Drip trays
    • 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
    • F25D2321/00—Details or arrangements for defrosting; Preventing frosting; Removing condensed or defrost water, not provided for in other groups of this subclass
    • F25D2321/14—Collecting condense or defrost water; Removing condense or defrost water
    • F25D2321/141—Removal by evaporation
    • F25D2321/1411—Removal by evaporation using compressor heat
    • 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
    • F25D2321/00—Details or arrangements for defrosting; Preventing frosting; Removing condensed or defrost water, not provided for in other groups of this subclass
    • F25D2321/14—Collecting condense or defrost water; Removing condense or defrost water
    • F25D2321/141—Removal by evaporation
    • F25D2321/1413—Removal by evaporation using heat from electric elements or using an electric field for enhancing removal
    • 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
    • F25D2321/00—Details or arrangements for defrosting; Preventing frosting; Removing condensed or defrost water, not provided for in other groups of this subclass
    • F25D2321/14—Collecting condense or defrost water; Removing condense or defrost water
    • F25D2321/147—Collecting condense or defrost water; Removing condense or defrost water characterised by capillary, wick, adsorbent, or evaporation elements
    • 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
    • F25D2500/04—Calculation of parameters
    • 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
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/02—Sensors detecting door opening
    • 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
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/10—Sensors measuring the temperature of the evaporator
    • 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
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/14—Sensors measuring the temperature outside the refrigerator or freezer

Definitions

  • the present invention relates to a refrigeration appliance, in particular a household refrigeration appliance such as a refrigerator or freezer, with an evaporation tray for the evaporation of condensate discharged from a storage chamber of the device, and a
  • Auxiliary device which is switchable to promote the evaporation of the dew water in the evaporation tray, if necessary.
  • heat-insulating wall of the refrigerator is passed to an evaporation tray.
  • the evaporation tray is located beyond the heat-insulating wall to release moisture evaporating from it freely to the environment.
  • Object of the present invention is therefore to provide an inexpensive and reliable solution with which sufficient evaporation of condensation can be ensured and at the same time a good energy efficiency of the refrigerator is maintained.
  • a refrigeration device Under a refrigeration device is in particular a household refrigeration appliance understood, ie a refrigeration appliance for household management in households or possibly in the
  • Catering area is used, and in particular serves to store food and / or drinks in household quantities at certain temperatures, such as a refrigerator, a freezer, a fridge-freezer, a freezer or a wine storage cabinet.
  • control unit may be configured to further control the operation of the auxiliary device depending on the
  • Ambient temperature to control because the amount of moisture that enters the storage chamber together with a given volume of air from the environment, generally increases sharply with the temperature of the air.
  • control unit may be connected to a suitable temperature sensor.
  • the control unit can be set up to estimate the ambient temperature on the basis of the duration of an operating phase of the compressor.
  • the duration of an operating phase depends not only on the difference between the switch-on and switch-off temperature of the compressor, but also on the rate at which ambient heat penetrates into the storage chamber and delays its cooling during operation of the compressor. The higher the ambient temperature, the higher the rate, and accordingly, each operating phase lasts longer.
  • Refrigeration appliances are also known, in which the capacity of the compressor is variable and regulated to a value at which the compressor is continuous or near Run continuously while keeping the temperature of the storage chamber constant.
  • the capacity of the compressor to equalize the flow of heat from the storage compartment environment depends on the ambient temperature, specifically the difference between the ambient temperature and the temperature of the storage chamber, so that the performance to which the compressor is subjected at one such refrigeration device is regulated, also allows a conclusion on the ambient temperature.
  • Humidity sensor is equipped to detect the humidity in the storage chamber and to allow a controlled dehumidification of the air to a tuned to the refrigerated goods contained therein target value.
  • the amount of condensate arising in such a controlled dehumidification can be accurately estimated on the basis of the measured humidity values and can be used to control the auxiliary device.
  • Humidity sensor possible.
  • a temperature sensor for detecting the temperature of the evaporator may be arranged on an evaporator cooling the storage chamber in order to detect the change in the evaporator temperature during startup. Moisture condensing on the evaporator delays its cooling, so that by comparing the time course of cooling with a normal course without condensation, the amount of condensation can be estimated, which is reflected in this in an operating phase of the evaporator on this.
  • the control unit is in such a case
  • this device Preferably arranged to operate this device together with the defrost heater to quickly eliminate this condensation.
  • the consideration of the various above-mentioned, the amount of accumulating condensation water influencing variables can be done by the
  • Control unit is set, with each door open a count size by one increment based on at least one of door opening duration, ambient temperature, compressor run time, compressor capacity, humidity in the storage chamber and
  • Rate of change of the evaporator temperature selected size and to operate the auxiliary device when the count size reaches a limit.
  • auxiliary device in particular a heater and / or a fan come into consideration.
  • FIG. 1 is a schematic section in the width direction through a household refrigerator according to the present invention
  • Fig. 3 is a flowchart of a method for controlling the evaporation
  • FIG. 6 shows exemplary temperature profiles on the evaporator of the refrigerator of FIGS. 1 and 2;
  • FIG. 7 is a flowchart of a method of controlling the auxiliary device based on the temperature characteristics shown in FIG. 6; FIG. and
  • FIG. 8 is a flowchart of a second method based on the temperature curves of FIG. 6.
  • Figs. 1 and 2 show schematic sections through a household refrigerator, to which the present invention is applicable. The sectional planes of the two figures are shown in the other Fig. As dash-dotted lines l-l and II-II.
  • the household refrigerator here a refrigerator, has in the usual way
  • heat-insulating housing having a body 1 and a door 2 defining a storage chamber 3.
  • the storage chamber 3 is here cooled by a coldwall evaporator 4 arranged on its rear wall between an inner container of the body 1 and an insulating foam layer surrounding it, but it should be immediately obvious to the person skilled in the art that the features of the invention explained below also apply in connection with FIG any other types of evaporator are applicable.
  • the evaporator 4 is part of a refrigerator which further comprises a compressor 6 housed in a machine room 5 recessed from the cabinet 1 and a condenser not shown in the figures, which may for example be accommodated on the outside of the rear wall of the cabinet 1 or in the machine room 5 ,
  • a collecting channel 7 extends for condensed water, which is reflected at the area cooled by the evaporator 4 of the inner container and flows down there.
  • a pipeline 8 leads from the lowest point of the gutter 7 through the insulating
  • An electric heater 10 is here in the form of a inside of the Evaporation tray 9 extending heating loop shown; she could too
  • Evaporation tray 9 may be mounted, in which case outside the film heater around still an insulating layer may be provided to ensure that the heater emits its heat substantially in the evaporation tray 9 inside.
  • a fan 12 may be arranged in the engine room 5 so that it drives an air flow over the water level of the evaporation tray 9. Since the on and off times of the
  • Heater 10 and the fan 12 are linked and preferably the same, the description may be limited to the case that both are present.
  • Heating device 10 and fan 12 are controlled by an electronic
  • Control unit 13 which is shown here for simplicity in the engine room 5, but in practice largely arbitrarily on the refrigerator and in particular adjacent to a - not shown - control panel can be arranged.
  • the control unit 13 also controls the operation of the compressor 6 on the basis of a temperature sensor 14 arranged on the bearing chamber 3.
  • a simple on-off control of the compressor 6 can be provided within the scope of the invention, in which the control unit 13 turns on the compressor 6, when the temperature of the storage chamber, a switch-on threshold T a exceeds 3, and it turns off again as soon as the temperature of the storage chamber 3 is below a switch-off threshold T off.
  • it is also a continuous control of the power, in particular the speed of the compressor 6 or switching between numerous discrete non-vanishing power levels of the compressor 6 in dependence on the measured temperature into consideration.
  • a second temperature sensor 17 may be arranged directly on the evaporator 4 in order to control its temperature
  • step S31 the
  • Control unit 13 from that the switch 15 detects an opening of the door 2. If this is the case, an internal counter c of the control unit 13 is incremented in step S32 by an increment incr, which may be a constant in a simple embodiment, however, according to a preferred embodiment, directly or indirectly from the temperature T ext in the environment of the refrigerator and possibly still depends on other sizes. In order to estimate the outside temperature T ext , a
  • Ambient temperature sensor may be provided on the refrigeration device outside the insulation layer. However, it is preferable to save the cost of such a sensor and the
  • an air humidity sensor is provided in the storage chamber 3, its measured value can be used after the door 2 has been closed again in order to reduce the amount of fuel Quantify water vapor in storage chamber 3 quantitatively and set the increment accordingly.
  • step S33 it is checked whether the counter has exceeded a limit value c ma x which corresponds to a critical water level in the evaporation tray 9. If so, in step S34, the heater 10 and / or the fan 12
  • step S35 the counter c is reset in step S35, and the process returns to the output. While heater 10 and fan 12 are in operation, the detection of door openings continues with steps S31, S32, S33 and the concomitant re-increment of counter c. Each after a predetermined period of operation, which is empirically determined as sufficient to a the
  • Threshold c ma x corresponding amount of water to evaporate and so to reduce the water level in the evaporation tray 9 back to a safe level, heater 10 and fan 12 are turned off again.
  • the control unit 13 In the case of on-off control of the compressor 6 by the control unit 13, it may be provided that, when the compressor 6 is in operation, the count value c is reduced by a predetermined decrement at regular time intervals. In the case that the compressor 6 is continuously operated at variable power, the amount of decrement may be proportional or the time interval between two
  • Decrements are set inversely proportional to the compressor power.
  • FIG. 4 illustrates a first method for indirectly estimating the
  • step S41 it is waited until the temperature detected by the temperature sensor 14 temperature T of the storage chamber 3 rises above the turn-T a. Once this is the case, the compressor 6 is turned on and on in step S42
  • the timepiece can count on the count of
  • step S43 Clock periods of a clock of the control unit 13 based.
  • step S43 Once it is determined in step S43 that the temperature of the storage chamber 3 to the switch-off threshold T from has dropped, the compressor 6 is turned off again, the timer is stopped and since the step S42, elapsed time detected t, and the outdoor temperature T ext is the basis of a Look-up table estimated in which these as a function of the f (from User adjustable) on threshold T and the delay time t of the compressor 6 is recorded.
  • the table that describes the relationship between f T a turn-on threshold, compressor running time t and ambient temperature T ext has been previously determined empirically by the manufacturer of the refrigeration unit and stored in a read-only memory of the controller. 13
  • the compressor 6 is switchable between different non-vanishing power levels.
  • Procedure is repeated at regular intervals.
  • an upper limit T max and a lower limit T min are set for the temperature of the storage chamber 3, which should not be exceeded or fallen below for a long time if possible. If it is determined in step S51 when comparing the temperature T of the storage chamber 3 with the upper limit T max that the temperature T of the storage chamber 3 is above the upper limit T max , the power PV of the compressor 6 is increased by a predetermined increment in step S52 ⁇ increased.
  • the time interval between two repetitions of the method is chosen to be large enough to be able to observe an effect of the changed compressor power PV on the temperature T. If the compressor power PV after the boost is sufficient to lower the temperature T, and it is determined in step S51 that the temperature T has fallen below T max , then the process branches from step S51 to S53, where the temperature T is compared with the lower limit T min . If this is not exceeded, the compressor power PV remains unchanged, and in turn begins after the predetermined time interval, the process again.
  • step S54 if the temperature T is less than T min , in step S54 the
  • the compressor power PV continuously adapts to the cooling temperature of the storage chamber 3 that is variable according to the ambient temperature T ext .
  • the ambient temperature T ext can be used as a function of the actual temperature T of the storage chamber 3 or its user set limits T max , T min and the compressor power PV a table empirically determined for the respective model of the refrigerator can be estimated.
  • Evaporator 4 as a function of time t, in each case assumed that at a time tO, the control unit 13 turns on the compressor 6.
  • the temperature Tv of the evaporator 4 rises very slowly together with the temperature T of the storage chamber 3.
  • the temperature Tv starts to fall.
  • the speed of the temperature drop depends on the humidity in the storage chamber 3 and the rate at which this humidity on the evaporator 4 is reflected as condensation.
  • the fastest drop shown as curve A in Fig. 6, then arises when the air in the storage chamber 3 is dry and no condensation heat through
  • Storage chamber 3 has risen above the switch-on threshold T a . Once this is the case, the compressor 6 is turned on in step S72, and a timer is started to measure the elapsed time t from the switch-on time tO.
  • step S73 it is decided whether the door 2 has been open since the last time the compressor 6 was turned on. If not, then it can be assumed that the air in the storage chamber 3 is so dry that the frosting at the evaporator 4 will be negligible in the now commencing phase of operation, and the method advances to step S74 at the temperatures measured during this phase of operation of the evaporator as reference temperatures Tv ref (t) corresponding to the curve A of FIG. 6.
  • step S75 by means of the
  • Temperature sensor 17 the actual temperature Tv measured at the evaporator at the current time t and compared with the value obtained in an earlier operating phase Tv ref (t).
  • the difference between the two temperatures Tv (t) and Tv ref (t) is a measure of the rate at which condensate condenses on the evaporator 4.
  • a count c is incremented by this difference.
  • step S76 the count value c is compared with a threshold value c max , and as described with reference to Fig. 3, if the threshold value c ma x heater 10 and fan 12 are exceeded, the count value c is reset (S77) (S78).
  • the steps S75, S76 are repeated so long until it is determined in step S79 that the storage chamber to the switch-off temperature T out is cooled. Once this is the case, the process returns to the origin S71.
  • step S75 corresponds to a numerical integration of the difference between the two curves B, A of FIG. 6.
  • the value of the integral, c is proportional to the accumulated amount of condensation water.
  • Heating device 10 and fan 12 remain switched on after step S77, is empirically set so that it is sufficient to the c ma x corresponding amount of condensation water evaporate. This period obviously depends on the power of the heater 10 and the fan 12, but also on the waste heat capacity of the compressor 6 in operation.
  • step S85 it is decided whether the door 2 has been open since the last time the compressor 6 was turned on. If not, the measured values obtained in steps S83 and S84 are stored as reference values TV ref (t1), TV ref (t2) of the curve A (S86). If yes, then a typical rate of decrease of curve B can be determined from these two measurements. In step S87, the difference between this decrease rate and the decrease rate Tv ref (t2) -Tv ref (t1) of the curve A determined at an earlier operating phase of the compressor 6 is calculated at these two points in time.
  • step S88 it is checked whether the count value c has exceeded the threshold c ma x. If not, in the current operating phase of the compressor, the fan 12 and the heater 10 are not needed, and the process returns to step S81 to await the next compressor operation phase. If c ma x is exceeded, then
  • Heating device 10 and fan 12 is turned on (S89) and remain in operation as long as necessary to evaporate the c ma x corresponding amount of water. Accordingly, the count value is decremented by c ma x in step S90 before the process returns to step S81

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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)
  • Removal Of Water From Condensation And Defrosting (AREA)

Abstract

L'invention concerne un appareil de froid, en particulier un appareil électroménager, comportant au moins une chambre de stockage (3) pouvant être fermée par une porte (2), un bac d'évaporation (9) pour l'évaporation d'eau de condensation évacuée de la chambre de stockage (3), et un dispositif auxiliaire (10, 12) qui peut être activé par une unité de commande (13) pour augmenter la vitesse d'évaporation dans le bac d'évaporation (9). L'unité de commande (13) est conçue pour détecter l'ouverture de la porte (2) et pour commander le fonctionnement du dispositif auxiliaire (10, 12) à l'aide du nombre et/ou de la durée des ouvertures de porte détectées et/ou en fonction de la température ambiante (Text), et/ou pour tenir compte de la variation dans le temps de la température (Tv) d'un évaporateur (4) lors de la commande du fonctionnement du dispositif auxiliaire (10, 12).
PCT/EP2012/061758 2011-06-29 2012-06-20 Appareil de froid à bac d'évaporation et dispositif auxiliaire favorisant l'évaporation WO2013000773A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110078321 DE102011078321A1 (de) 2011-06-29 2011-06-29 Kältegerät mit Verdunstungsschale und Hilfseinrichtung zur Verdunstungsförderung
DE102011078321.0 2011-06-29

Publications (2)

Publication Number Publication Date
WO2013000773A2 true WO2013000773A2 (fr) 2013-01-03
WO2013000773A3 WO2013000773A3 (fr) 2013-09-06

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PCT/EP2012/061758 WO2013000773A2 (fr) 2011-06-29 2012-06-20 Appareil de froid à bac d'évaporation et dispositif auxiliaire favorisant l'évaporation

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DE (1) DE102011078321A1 (fr)
WO (1) WO2013000773A2 (fr)

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Publication number Priority date Publication date Assignee Title
DE102011085155A1 (de) 2011-10-25 2013-04-25 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät mit Verdunstungsschale und Hilfseinrichtung zur Verdunstungsförderung

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Publication number Priority date Publication date Assignee Title
DE102004012498A1 (de) * 2004-03-15 2005-10-06 BSH Bosch und Siemens Hausgeräte GmbH Kältegerät
KR100709721B1 (ko) * 2005-12-06 2007-04-19 주식회사 퍼시픽콘트롤즈 기계식 냉장고용 전자식 제상타이머
PL2313718T3 (pl) * 2008-07-04 2018-02-28 Arçelik Anonim Sirketi Urządzenie chłodzące

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DE102011078321A1 (de) 2013-01-03
WO2013000773A3 (fr) 2013-09-06

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