WO2013000759A2 - 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
WO2013000759A2
WO2013000759A2 PCT/EP2012/061640 EP2012061640W WO2013000759A2 WO 2013000759 A2 WO2013000759 A2 WO 2013000759A2 EP 2012061640 W EP2012061640 W EP 2012061640W WO 2013000759 A2 WO2013000759 A2 WO 2013000759A2
Authority
WO
WIPO (PCT)
Prior art keywords
temperature
control unit
storage chamber
appliance according
compressor
Prior art date
Application number
PCT/EP2012/061640
Other languages
German (de)
English (en)
Other versions
WO2013000759A3 (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 WO2013000759A2 publication Critical patent/WO2013000759A2/fr
Publication of WO2013000759A3 publication Critical patent/WO2013000759A3/fr

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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
    • 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
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • F25D21/08—Removing frost by electric heating
    • 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
    • F25D2700/12—Sensors measuring the inside temperature
    • 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.
  • Domestic refrigeration appliance with at least one storage chamber, arranged in thermal contact with the storage chamber temperature sensor, an evaporation tray for Evaporation of discharged from the storage chamber condensation and a
  • Auxiliary device which can be switched by a control unit to increase the evaporation rate in the evaporation tray, the control unit is set up, a decision on the connection of the auxiliary device (10, 12) based on the time course of the temperature sensor (14, 17) detected temperature hold true.
  • control unit As an intermediate in the decision making, the control unit
  • the temperature detected by the sensor is linked by various relationships with the accumulating amount of condensate. For example, each opening of a door of the storage chamber leads to an inflow of warm, moist ambient air in the
  • Another related fact is that the cooling of an evaporator located at the storage chamber is delayed when moisture from the air flows through the air
  • cooling rate which is known to the evaporator with known moisture content of the air of the storage chamber, especially if it is dry and no condensation takes place, then by a deviation between this and a measured
  • Cooling Rate the extent of condensation can be estimated. For such an estimate, a short observation period is sufficient; in particular, in the case of a refrigeration device with an intermittently operated compressor, a judgment of the
  • the temperature sensor is mounted on the evaporator.
  • the count size may optionally be incremented in proportion to the calculated deviation by the amount accumulated in a given period of time or, in the case of an intermittently operated compressor, during an operating phase of the compressor
  • a delay in cooling by condensation may also be exploited by integrating, when an expected temperature is known as a function of time, the difference between a temperature measured by the temperature sensor and the expected temperature over time. Also this integral is proportional to the accumulating
  • the integral thus obtained or a variable proportional to it may serve as the above-mentioned count quantity.
  • control unit is set up, to take into account the temperature of the storage chamber and / or the ambient temperature when determining the connection, since the ambient temperature determines how much moisture may be present in a given amount of ambient air contained in the storage chamber, and the temperature of the storage chamber (in which both an actual temperature, for example the temperature detected by the temperature sensor and a setpoint temperature set by a user can be taken as a basis), allows conclusions to be drawn as to what percentage of the ingress of moisture will actually condense out.
  • control unit weighting the increment with a temperature dependent on the temperature of the storage chamber and / or the ambient temperature factor.
  • control unit may be connected to an ambient temperature sensor.
  • the control unit can be set up Estimate ambient temperature based on 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 can run continuously or almost 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 precipitated as frost which does not defrost between two phases of operation of the evaporator, then defrosting can be provided for defrosting the evaporator. Liquid condensate then essentially only accumulates when the defrost heater is in operation. Therefore, the control unit is in such a case
  • auxiliary device Preferably arranged to operate the auxiliary device together with the defrost heater to eliminate this condensation quickly.
  • auxiliary device in particular a heater and / or a fan come into consideration.
  • Figure 1 is a schematic section in the width direction by a household refrigerator according to the present invention.
  • Fig. 3 is a flowchart of a method for controlling the evaporation
  • FIGS. 1 and 2 shows an exemplary temperature profile in the storage chamber of the refrigerator of FIGS. 1 and 2;
  • FIG. 5 is a flowchart of a method of controlling the auxiliary device based on the temperature history shown in FIG. 4; FIG.
  • FIG. 6 is a flowchart of a second on the temperature profile of FIG .. 4
  • FIGS. 7 shows exemplary temperature profiles on the evaporator of the refrigerator of FIGS. 1 and 2;
  • FIG. 8 is a flow chart of a method of controlling the auxiliary device based on the temperature characteristics shown in FIG. 7; FIG.
  • FIG. 9 is a flowchart of a second method based on the temperature characteristics of FIG. 7; FIG. and
  • 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 ll or 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; It could also, for example, in the form of a film heater on an outer wall 1 1 of
  • 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.
  • the door 2 switch 15 On a side wall of the body 1 an operable by the door 2 switch 15 is mounted, which can serve in a conventional manner for switching on and off a lamp 16 of the storage chamber 3 when opening or closing the door 2.
  • the switch 15 may be connected to the control unit 13 in order to allow detection of the opening and closing of the door 2 by the control unit 13 in the context of a control method which will be described below.
  • 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 opening of the door 2 is detected. This detection can by means of of the switch 15 or by one of the methods described later with reference to FIGS. 4 to 6.
  • Control unit 13 by an increment incr (T ext , 7) increases, the value of which is proportional to an estimated amount of passing through the door opening in the storage chamber 3
  • Moisture level is set. This amount can be estimated on the basis of parameters such as the temperature T ext in the vicinity of the refrigerator or the duration of the door 2 open. It is easy to understand that the amount of ambient air that enters the storage chamber 3 when opening the door 2, the greater, the longer the door 2 is open, and that, accordingly, the amount of water introduced with the ambient air increases. However, as soon as the air in the storage chamber 3 is completely replaced, the registered amount of moisture increases only slowly. Therefore, it can be assumed in a simple embodiment of the method that with each door opening the air is completely replaced; then only the number of door openings, but not their duration in the increment needs to be considered. A more accurate estimate of the moisture input is achieved if a correspondingly reduced increment is taken as the basis for a short door open which is insufficient for complete air exchange.
  • Ambient temperature sensor may be provided on the refrigeration device outside the insulating layer; an alternative, less expensive feasible option, if the compressor 6 is operated intermittently, to measure the duration of an operating phase of the compressor 6 and the ambient temperature based on a previously determined empirically
  • Storage chamber 3 results, then the ambient temperature T ext in an analogous manner estimated from a known relationship between temperature T, compressor power and ambient temperature.
  • 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.
  • the detection of door openings continues with steps S31, S32, S33 and the concomitant re-increment of counter c.
  • a predetermined operating time which is determined empirically as sufficient to evaporate an amount of water corresponding to the limit c ma x and so to reduce the water level in the evaporation tray 9 back to a safe level, heating device 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 operated continuously at variable power, the amount of decrement can be set proportional or the time interval between two decrements inversely proportional to the compressor power.
  • Fig. 4 shows typical courses of the temperature sensor 14 over time
  • Switch-T a which causes the control unit 13, the compressor 6 turn on; at the designated time points with t from the temperature T reaches a switch-off threshold of T, in which the control unit 13 turns off the compressor 6. As long as the door remains closed, the time between these times changes
  • Temperature T is no longer significantly different from the temperature, which is without a
  • FIG. 5 shows a flowchart of a first method which employs the monitoring of the temperature T in the storage chamber 3 to carry out the step S31. The process is repeated at regular intervals, regardless of whether the compressor 6 is turned on or not.
  • step S51 the temperature T, which
  • step S52 the process branches in step S52 to step S53, where it is checked whether the measured value T, is higher than the measured value ⁇ , .- ⁇ obtained in the previous iteration. If not, the iteration is finished. Otherwise, the method reaches step S55.
  • step S55 it is concluded that the door has been opened.
  • step S56 wait until either the compressor 6 changes its operating state or, if at the time of detection of the door opening the compressor 6 was turned on, the Temperature T begins to fall again or, if the compressor 6 was off, the temperature T starts to rise again.
  • control unit 13 normal values for the time derivative of the temperature T with switched on and off compressor 6 are known. These values can be programmed by the manufacturer, or they can be based on measurements of the temperature profile that the control unit 13 itself performs on the refrigeration device. Again, in step S61, first the current temperature T, at the time of the ith
  • the time derivative dT, / dT is calculated in step S62 on the basis of a temperature value Tu measured in the respectively preceding iteration.
  • Step S63 checks whether the derivative thus calculated is more positive than normal, i. as the rate of change of temperature that would be expected with the door closed, taking into account the compressor operating condition. If this is not the case, then the iteration ends; if it is the case, it is concluded in S64 that the door has been opened. Again, to avoid multiple counts, in S65 the temperature T is still measured at regular intervals and its derivative calculated, but for
  • the starting point of the process is only returned when the thus obtained
  • Derivative values are normalized again, i. the disturbance caused by the door opening has subsided in the normal course of temperature.
  • FIG. 7 shows two curves of the temperature Tv of the evaporator 4 as a function of the time t, it being assumed in each case that the control unit 13 switches on the compressor 6 at a time tO.
  • 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. 7, is given when the air in the storage chamber 3 is dry and no condensation heat through
  • step S81 the control unit 13 waits until the temperature T of the
  • step S82 the compressor 6 is turned on, and a timer is set in motion to measure the elapsed time t from the switch-on time tO.
  • step S83 the actual temperature Tv at the evaporator at the current time t is measured by means of the temperature sensor 17 and compared with a value Tv ref (t), which would be expected according to curve A at this time t, when the air in the
  • step S84 the count value c is compared with a threshold value c ma x, and as described with reference to Fig. 3, when the threshold value c max heater 10 and fan 12 are exceeded (S85), the count value c is reset (S86).
  • the steps S83, S84 are repeated so long until it is determined in step S87 that the storage chamber to the switch-off temperature T out is cooled. Once this is the case, the process returns to the origin S81.
  • the repeated summation in step S83 corresponds to a numerical integration of the difference between the two curves B, A of FIG. 7.
  • the value of the integral, c can be assumed to be proportional to the accumulated amount of condensation water.
  • the period of time during which the heater 10 and fan 12 remain on after step S85 is empirically determined to be sufficient to correspond to the c ma x
  • Amount of condensation water to 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. 9 shows a flow chart of a second on the evaluation of
  • Evaporator temperature Tv (t1) instead (S93).
  • a second measurement (S94) takes place at time t2.
  • a typical rate of decrease of the curve B can be determined.
  • step S95 the difference between this decrease rate and a decrease rate Tv ref (t2) -Tv ref (t1) of the curve A stored beforehand empirically and stored in the control unit is calculated at these two points in time.
  • This difference is again representative of the condensation rate at the evaporator 4 and thus for the total amount of moisture contained in the air of the storage chamber 3 and will be reflected in the course of the current operating phase of the compressor 6 at the evaporator 4. Accordingly, the count c is incremented by this difference in S95.
  • the value of c is thus representative of the amount of condensation water at the end of the
  • step S96 it is checked whether the count value c has exceeded the threshold c max . 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 S91 to await the next compressor operation phase. If c max is exceeded, heater 10 and fan 12 are turned on (S97) and remain in operation as long as necessary to evaporate the amount of water corresponding to c ma x.
  • the count value is decremented by c ma x in step S98 before the process returns to step S91.
  • step S101 A further embodiment of a method for controlling heating device 10 and fan 12 is shown in FIG. 10 on the basis of the temperature T detected by temperature sensor 14 of storage chamber 3.
  • step S101 first, the current temperature T, the storage chamber 3 is measured.
  • step S102 it is checked whether this temperature is higher than the normal temperature corresponding to the solid curve in FIG. 4. If not, the iteration ends, otherwise, in step S103 the extent of deviation d, between actual temperature T, and
  • Step S104 compares this deviation d, with a value d ma x stored from a previous iteration. If the deviation d, is greater, d ma x is overwritten with d, in S105, and the iteration ends.
  • the maximum of the deviation from the normal temperature occurring after a door opening is exceeded, and the stored value d max denotes the maximum of this temperature deviation.
  • This maximum may be understood as a measure of the amount of ambient air entering the storage chamber 3 at the door opening, and the amount of moisture contained in this ambient air is estimated by measuring dmax in step S106 with a function of, for example, a suitably arranged sensor Ambient temperature T ext is multiplied.
  • the control unit may, for example, a known relationship between ambient temperature, target temperature of the storage chamber 3 and - with intermittently operating compressor 6 - the duration (t from -t e in) an operating phase of the compressor , or the average power of the compressor 6 draw.
  • a count c representative of the water level in the evaporation tray is incremented around the product thus obtained, and d ma x is reset to zero to prepare for detection of a later door opening.

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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 prendre une décision (S31- S33, S83-S84; S93-S96; S102-S107) concernant l'activation du dispositif auxiliaire (10, 12) en fonction de la variation dans le temps de la température détectée par le capteur de température(14, 17).
PCT/EP2012/061640 2011-06-29 2012-06-19 Appareil de froid à bac d'évaporation et dispositif auxiliaire favorisant l'évaporation WO2013000759A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110078323 DE102011078323A1 (de) 2011-06-29 2011-06-29 Kältegerät mit Verdunstungsschale und Hilfseinrichtung zur Verdunstungsförderung
DE102011078323.7 2011-06-29

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WO2013000759A2 true WO2013000759A2 (fr) 2013-01-03
WO2013000759A3 WO2013000759A3 (fr) 2013-07-18

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WO (1) WO2013000759A2 (fr)

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PL2313718T3 (pl) * 2008-07-04 2018-02-28 Arçelik Anonim Sirketi Urządzenie chłodzące

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WO2019142323A1 (fr) * 2018-01-19 2019-07-25 三菱電機株式会社 Présentoir
JPWO2019142323A1 (ja) * 2018-01-19 2020-09-03 三菱電機株式会社 ショーケース

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