WO2016034461A1

WO2016034461A1 - Refrigerator having several storage compartments

Info

Publication number: WO2016034461A1
Application number: PCT/EP2015/069483
Authority: WO
Inventors: Andreas BABUCKE; Stefan Holzer; Matthias Mrzyglod
Original assignee: BSH Hausgeräte GmbH
Priority date: 2014-09-04
Filing date: 2015-08-26
Publication date: 2016-03-10
Also published as: DE102014217671A1

Abstract

The invention relates to a refrigerator, in particular a household refrigerator, comprising a compressor (1), a first evaporator (13) for cooling a first compartment (15), a second evaporator (14) for cooling a second compartment (16), said compartments being arranged in mutually parallel branches (9, 10) of a cooling line (4). A control unit (19) is connected to temperature sensors (20, 21) of the first and the second compartments (15, 16), in order to, when the switch-on temperature (T_on) of the first compartment is exceeded, start a cooling operating phase (t1-t3) of the first compartment (15) and an additional cooling operating phase (t0-t1) of the second compartment (16), and to end (S19) the cooling operating phase (t1-t3) of the first compartment (15) when a switch off condition of the first compartment (15) is met. A temperature (T1₁₆) of the second compartment (16), in which the control unit (19) ends (S9) the accessory cooling operating phase (t0-t1), is determined based on a target temperature (T_target) of the second compartment (16) and a temperature (T0) of the second compartment (16) prevailing at beginning of the cooling operating phase (t0-t1) of the second compartment (16).

Description

Refrigerating appliance with several storage compartments

The present invention relates to a refrigeration appliance, in particular a household refrigerating appliance, with a plurality of storage compartments provided for operation at different temperatures.

Domestic refrigerators with two held at different operating temperatures storage compartments such as a freezer and a normal refrigeration compartment and a refrigerator, in which a first evaporator for cooling the first storage compartment and a second evaporator for cooling the second storage compartment are arranged in mutually parallel branches of a refrigerant pipe to optionally with To be acted upon refrigerant are known per se. Usually, target temperatures for the compartments are adjustable on a control unit of such a refrigeration device, of which the control unit in each case derives a switch-on temperature and a switch-off temperature. If the switch-on temperature in one of the compartments is exceeded, the control unit operates the compressor until the temperature of the compartment has decreased to the switch-off temperature.

In the time that elapses until the switch-on temperature in one of the compartments is exceeded again, pressure differences which have been built up between upstream and downstream parts of the refrigerant line during the preceding compressor operation can equalize so that they start at the next compressor operating phase need to be restored under energy. Although such a pressure compensation can be slowed down by arranged in the refrigerant line valves; completely suppressing it is difficult, and if leaks occur in the course of use of the refrigerator, it is difficult to see from the outside, and the resulting increased energy consumption is usually unnoticed by the user of the refrigerator.

However, if in one of the compartments the switch-on temperature is exceeded while the compressor is already operating to cool the other compartment, then it is possible to switch between the compartments without interrupting the compressor operation so that there is no time for pressure equalization in this case remains. However, one of the compartments must remain temporarily uncooled here, while the cooling requirement of the other compartment must be maintained. is damaged, so that in this one compartment, the switch-on temperature can be significantly exceeded.

Object of the present invention is to provide a refrigeration device with several storage compartments, on the one hand achieves a high efficiency, on the other hand, but also outliers of the compartment temperature can be reliably avoided.

The object is achieved by providing in a refrigerator, in particular a domestic refrigerator, with a compressor, a first evaporator for cooling a first compartment, a second evaporator for cooling a second compartment, which are arranged in mutually parallel branches of a refrigerant line, and a control unit , which is connected to temperature sensors of the first and the second compartment to start a cooling operation phase of the first compartment when exceeding a switch-on temperature of the first compartment and terminate upon the occurrence of a Ausschaltkriterium the first compartment, the control unit is further configured to exceed the switch-on of first compartment also starts an accessory cooling operation phase of the second compartment, and a temperature of the second compartment, at which the accessory cooling operation phase is terminated, based on a target temperature of the second compartment and a prevailing at the beginning of the cooling operation phase of the second compartment n Define the temperature of the second compartment.

Since it is not necessary to wait for the accessory cooling operation phase until the switch-on temperature is exceeded in the second compartment, the time interval between the cooling operation phase of the first compartment and the accessory cooling operation phase can be arbitrarily set. Ideally, it is zero, ie the two phases immediately connect to each other without any intermittent service interruption of the compressor. Low-speed operation of the compressor also reduces fluctuations in injection noise from which a user of the device could feel disturbed. Since the beginning of the accessory cooling operation phase is not triggered by the exceeding of a switch-on temperature in the second compartment, the temperature in the second compartment may vary at the beginning of the accessory cooling operation phase. If the accessory cooling operating phase would always end when a fixed switch-off temperature of the second compartment, this would have an effect on the mean temperature of the second compartment. If, in a conventional manner, a regular (ie non-accessory) cooling operation phase of the second compartment is triggered by exceeding the switch-on temperature of the second compartment, then the temperatures at the beginning of the accessory cooling operation phases can only be below this switch-on temperature, and an end of the accessory Cooling phases at the switch-off temperature of the regular operating phases would lead to a lowering of the mean temperature of the second compartment and thus to increased energy consumption. By setting a temperature of the second compartment at which the accessory cooling operation phase is ended based on a target temperature of the second compartment and a temperature of the second compartment prevailing at the beginning of the second section's cooling operation phase, a reduction in the average compartment temperature can be counteracted.

A prerequisite for avoiding a decrease in the average compartment temperature of the second compartment by the accessory cooling operation phases is that an accessory cooling operation phase is started only when the temperature of the second compartment is above the target temperature of the second compartment.

An easy way to minimize the influence of the accessory cooling operating phases on the mean temperature of the second compartment is to choose the sum of start temperature and end temperature of each accessory cooling operation phase constant, i. the lower the start temperature of an accessory cooling operation phase, the higher its final temperature is selected.

As already mentioned above, in addition to the accessory cooling operating phases, the control unit should also support regular cooling operating phases of the second compartment, which are started when the second compartment switch-on temperature is exceeded and ended when the second compartment switch-off temperature is exceeded. In this case, the target temperature, based on which, as explained above, the final temperature of the accessory cooling operating phases is set, should be between the switch-on temperature and the switch-off temperature of the second compartment.

In the simplest case, half of the above-mentioned sum of start temperature and end temperature can be taken as the target temperature. If the second compartment is colder than the first compartment or for other reasons has a higher cooling requirement than the first compartment, then in a conventional refrigerator without accessory cooling operating phases, most compressor starts would be caused by the second compartment cooling requirements. By additionally cooling the second compartment each time cooling is needed in the first compartment, the frequency of compressor starts can be reduced more effectively than if the cooler compartment cooled along with the warmer accessory. However, this does not rule out that if cooling is required in each compartment, the other is additionally cooled along with it. If the accessory cooled second compartment is the colder, then it is convenient to perform the accessory cooling operation phase prior to the cooling operation phase of the first compartment (15). Since the temperature of a condenser, through which the heat extracted from the compartments is delivered to the environment, is lowest at the beginning of each compressor operating phase, a better efficiency can be achieved with this sequence than with the reverse one.

Conversely, if the accessory cooled compartment is warmer, it is preferable that the accessory cooling operation phase be connected to the regular cooling operation phase of the colder compartment.

In order to counteract a pressure equalization at standstill of the compressor, a valve for blocking a refrigerant flow from the first evaporator to the second evaporator is preferably arranged in a downstream part of the refrigerant line between outputs of the evaporator and an input of the compressor. In particular, this valve may be a non-return valve arranged between an outlet of the second evaporator and a confluence where the two branches of the refrigerant line meet.

In an upstream part of the refrigerant line, a directional control valve can counteract the pressure equalization that connects only one of the two branches to an outlet of the compressor. Preferably, a stop valve between the output of the compressor and inputs of the evaporator is additionally arranged. The control unit may be configured to control a time offset between a start of the compressor and an opening of the stop valve and / or between a switching off of the compressor and a closing of the stop valve.

Such a time offset may be that the control unit at the beginning of a cooling phase of the second evaporator, while the compressor is already running, keeps the stop valve closed for a while yet. Thus, it can be ensured that at the moment in which the stop valve opens, the pressure in the second evaporator is low enough to lead to the immediate evaporation of the incoming refrigerant, and a temporary heat input into the second evaporator by non-evaporating refrigerant can be prevented.

Conversely, the time offset may be that at the end of the cooling phase of an evaporator, with the stop valve closed, the control unit continues to operate the compressor for a while. After-running of the compressor after a cooling operation phase of the first evaporator helps to reduce the pressure difference between the two evaporators in a subsequent standstill phase of the compressor and thus to minimize any leakage of refrigerant through the shut-off valve from the first to the second evaporator. Following a cooling operating phase of the second evaporator, in this way, refrigerant can be displaced into a high-pressure region of the refrigerant circuit and the amount of liquid refrigerant in the second evaporator can be reduced, so that the risk that liquid refrigerant at the beginning of a subsequent cooling operation phase of the second evaporator this is displaced and evaporates useless in a suction line leading to the compressor, is reduced. In order to be able to store refrigerant in the high pressure region of the refrigerant circuit at the end of a cooling operation phase, with the stop valve already closed, a refrigerant collector may be provided on the refrigerant circuit between an outlet of the compressor and the stop valve. The refrigerant collector may be formed by a chamber inserted into the refrigerant pipe; but it can also be used as a collector usually also serving another purpose components of the refrigerant circuit by, for example, for refrigerant pipes in the upstream part of the refrigerant circuit tubes with large diameter or by having a dryer with a larger volume than required for the drying function. Such a dryer will generally only be partially filled with desiccant in order to be able to absorb liquid refrigerant in large quantities. Subject of the invention is also a method for operating a refrigeration device as described above, with the steps:

a) monitoring the temperature of the first compartment, and if the temperature of the first compartment exceeds a switch-on temperature,

b) starting a cooling operation phase of the first compartment and terminating the cooling operation phase upon occurrence of a switch-off condition of the first compartment,

c) starting an accessory cooling operation phase of the second compartment and terminating the accessory cooling operation phase when the temperature of the second compartment falls below a final temperature determined by the initial temperature of the second compartment prevailing at the beginning of the accessory cooling operation phase.

Depending on the configuration of the method or depending on which of several compartments of the refrigeration device the switch-on temperature has been exceeded, step b) before step c) or step c) before step b) can be performed. The switch-off condition of the first compartment may be that the temperature of the first compartment falls below a switch-off temperature that is in a fixed relationship to the switch-on temperature or to the target temperature of the first compartment. This is particularly useful if between the exceeding of the switch-on and the cooling operation phase of the first compartment no accessory cooling of the second compartment has taken place, i. if step b) has been carried out before step c).

If, on the other hand, the cooling operation phase of the first compartment does not take place until after the second compartment has been cooled, that is, step c) is carried out before step b), then the temperature of the first compartment normally has continued to increase during this accessory cooling. In this case, in order to keep the mean temperature of the first compartment unchanged, it is possible to select, as the switch-off condition, the undershooting of an end temperature which is determined by the temperature of the first compartment prevailing at the beginning of this cooling operation phase. Further features and advantages of the invention will become apparent from the following description of embodiments with reference to the accompanying figures. 1 shows a schematic representation of the refrigerant circuit of a refrigeration device according to the invention;

2 shows a flowchart of a method of operation of a control unit of the refrigeration device;

3 shows the development over time of the electrical power consumption of a compressor and the evaporation temperature of the refrigerant during operation of the refrigeration device from FIG. 1; and

Fig. 4 shows the evolution of the temperature of a compartment of the refrigerator in the course of

Time. The refrigerant circuit shown in Fig. 1 comprises in a conventional manner a compressor 1 with a compressed refrigerant outlet 2 and an inlet 3 for refrigerant suction. A condenser 5, a dryer 6, a stop valve 7 that can be switched between an open state and a blocking state, and a directional control valve 8 are arranged in series at a refrigerant line 4 starting from the outlet 2. Between the condenser 5 and the dryer 8, a frame heater 23 may be inserted into the refrigerant line 4. At the directional control valve 8, the refrigerant line 4 divides into two branches 9, 10.

Deviating from the representation of FIG. 1, the directional control valve 8 can be integrated into the stop valve 7, in that the latter has three instead of two connections and two passage states, wherein in one of the passage states the directional control valve transfers the condenser 5 with the branch 9 and in the other with the branch 10 connects, and in the locked state to none of the branches 9, 10 is a connection. At the branches 9, 10 are each a capillary 1 1 or 12 and an evaporator 13 and 14 connected in series. Each of the two evaporators 13, 14 cools a compartment 15 or 16 of the refrigerator. The mean operating temperature of the compartment 15 is higher than that of the Tray 16, for example, tray 15 may be a normal refrigerated compartment and tray 16 may be a freezer compartment of the refrigerator.

The two branches 9, 10 meet again at a confluence 17. In the branch 10, a check valve 18 is arranged between an outlet of the evaporator 14 and the confluence 17, which allows a flow of refrigerant from the evaporator 14 to the compressor 1, but blocks in the opposite direction.

An electronic control unit 19 is connected to temperature sensors 20, 21 on the compartments 15, 16 to control the operation of the compressor 1 and the position of the stop valve 7 and the directional control valve 8 based on the temperatures measured there. Target temperatures Ttarget for both compartments 15, 16 may be set by a user at the control unit 19.

The capillary 1 1 of the normal cooling compartment 15 has, given a pressure drop of the refrigerant, two mass flow rates, a high value for liquid and a low for gaseous refrigerant. The mass flow rate of the compressor 1 is either, if it is a fixed speed compressor, specified by design or, in the case of a variable speed compressor, set by the control unit 19 to a value which is between the flow rates of the capillary 1 1. As a result, in a cooling operating phase of the evaporator 13, refrigerant vapor accumulates in front of the capillary 11 and condenses. When a drop of the condensate reaches and enters the capillary 11, its mass flow rate increases, and the liquid refrigerant is allowed to pass to the evaporator 13 before a larger amount can accumulate in front of the capillary 11. Thus, in the course of a cooling operating phase of the evaporator 13 liquid and vapor refrigerant of the capillary 1 1 alternate in rapid succession.

The capillary 12 has at the same pressure drop a much smaller mass flow rate than the capillary 1 1. The flow rate of the capillary 12 is even for liquid refrigerant even lower than the flow rate of the compressor 1, so that the rate at which refrigerant condenses in the liquefier , is higher than that, with which it can flow via the capillary 12. In order to provide space for the liquid refrigerant, which accumulates in a cooling operation phase of the evaporator 14 in front of the capillary 12, here the dryer 6 is formed as a refrigerant collector 22, ie the housing of the dryer 6 is only partially with Absorber material filled, the rest is empty to provide space for the liquid refrigerant.

The control unit 19 can operate according to different methods. In a first refinement of a working method, the control unit 19 continuously monitors in step S1 whether a switch- _on temperature T _{on, 15} or T _{on, 16 is} exceeded in one of the compartments 15, 16, which is added here by adding a difference value ΔΤ from the target temperature Ttarget , 15 and T _ta rget is derived i6 of the relevant compartment.

In the case of exceeding the switch-on temperature in the normal cooling compartment 15, ie when T ₁₅ > T _on 15, the method branches to step S2, in which the compressor 1 is turned on. The switch-on time corresponds to the time t0 in FIG. 3 and FIG. 4. The pressure in both evaporators decreases as a result of the operation of the compressor, and the evaporation temperature drops accordingly, as shown in FIG. 3 after t0. In step S3, it is checked whether the temperature T _{16 of} the freezing compartment 16 is above its target temperature T _ta rget, i6. If not, then the directional control valve 8 is driven to connect the capillary 1 1 with the condenser 5 and so the normal cooling compartment 15 to cool (S4) until in step S5 the switch-off T _off i _{6 is} reached. If, on the other hand, it is determined in S3 that T ₁₆ > Ttarget, i6, then in step S6 the current temperature T0i _{6 of} the freezer compartment 16 is measured; it represents the starting temperature of the now commencing accessory cooling operating phase of the evaporator 16. An associated end temperature T1 -I6 is calculated in S7:

T116 = 2 Ttarget, 16 ^~ 0l6-

The cooling operation S8 of the evaporator 14 is maintained until it is determined in step S9 that the freezing compartment 16 has reached the final temperature T1 ₆ . This corresponds to the time t1 in FIG. 3 and FIG. 4. Thus, when the freezer compartment 16 is cooled in advance due to the refrigeration requirement of the refrigerating compartment 15, its temperature fluctuates only by a narrow interval by T _ta rget, the average temperature of the freezer compartment 16 continues to coincide with its target temperature _Ta rget, i6, which would not be the case if, as illustrated in FIG. 4 by a dashed curve, the accessory cooling operating phase would not be terminated until reaching T _off, i ₆ . The step S9 could then be followed by a cooling operating phase of the evaporator 13, in the course of which the normal cooling compartment 15 is cooled down to T _{off, 15} . However, since the temperature T _{15 of} the normal cooling compartment 15 has risen further between tO and t1 and is now above T _{on, 15} , this would result in an increase in the average temperature of the normal cooling compartment to a value above T _ta rget _, i ₅ . This is prevented in the method of FIG. 2 by branching to step S13 or S15, which will be described in more detail later.

If an exceeding of the switch-on temperature in the freezer compartment 16 is detected in step S1, ie if T ₁₆ > T _{on, 16} , then the method branches to step S1 1, in which the compressor 1 is switched on and the directional control valve 8 is actuated, around the freezer compartment 16 to cool until it is determined in step S12 that the switch-off temperature T ₀ ff, i6 is reached.

In the following step S13, it is determined whether the temperature T15 of the normal refrigerating compartment 15 via the set temperature T _ta rget, is i5. If this is not the case, then the compressor is turned off (S14), and the process returns to the starting point S1. If the target temperature T _ta rget, i5 is exceeded, the process branches to step S15. Since this is always the case when S13 has been reached via S9, it is also possible to jump from S9 directly to S15. In step S15, the current temperature T0i _{5 of} the normal cooling compartment 15 is detected. In an analogous manner to step S7, based on this, a final temperature T1 _{15 is} calculated in S16:

T115 = 2 Ttarget, 15 ^- TO15. Subsequently, the directional control valve 8 is switched to pressurize the evaporator 13 with refrigerant. If an accessory cooling operation of the freezer compartment 16 has previously taken place, ie if step S15 has been reached via step S9, then due to the low mass flow rate of the capillary 12 during the accessory cooling operation, liquid refrigerant has built up in front of the capillary 12. This refrigerant flows rapidly after switching over the directional control valve 8 via the capillary, there is a rapid increase in pressure in the evaporator 13 and accordingly, as can be seen in FIG. 3, after the switchover time t1 to a rapid increase in the evaporation temperature in the evaporator 13. This decreases again as soon as the supply of dammed up liquid refrigerant is consumed by the capillary 1 1 and, from the time t2, liquid refrigerant and refrigerant vapor in the capillary 1 1 alternate. The reduced as of this time t2 average mass flow rate of the capillary 1 1 leads to a low pressure drop and a corresponding decrease in the evaporation temperature to a value a few degrees below 0 ° C.

In step S18, it is continuously monitored whether the normal cooling compartment 15 has reached its switch-off _temperature T _0ff , i5. If this is the case (at time t3 in FIG. 3), the control unit 19 turns off the compressor 1 (S19) and returns to step S1. While the control unit 19 is waiting for the switch- _on temperature T _{on to be} exceeded again in a compartment, the temperature of the evaporator 13 approaches that of the compartment 15 which it has cooled.

The time t4 in FIG. 3 corresponds to the occurrence of cooling demand in the freezer compartment 16, ie an increase of T ₁₆ via T _{on, 16} . In this case, in step S10, the evaporator 1 is turned on again and operated (S1 1) until the control unit 19 recognizes in step S12 at time t5 that the switch- _off temperature T _{off, 16 of} the freezing compartment 16 is reached. In the case shown in FIGS. 3 and 4, the compressor 1 is now switched off (S14), since the temperature sensor 20 of the normal cooling compartment 15 has not detected any renewed cooling requirement.

A further development of the operating method explained above can, if at the time tO cooling demand of the normal cooling compartment 15 is detected, the compressor 1 are switched on immediately, but the stop valve 7 remains closed for a while, so that, even if in the previous stoppage phase of the compressor 1 refrigerant agent vapor has passed through the check valve 18 from the evaporator 13 into the evaporator 14, the pressure in both evaporators 13, 14 is again lowered far enough to ensure that refrigerant at the moment of opening the stop valve 7 in the evaporator 14th of the freezer compartment 16 is evaporated from the outset at a temperature which is not higher than the current temperature of the evaporator 14.

If the mass flow rate of the capillary 12 is of a similar order of magnitude as that of the capillary 1 1 and is too high to prevent damming up of liquid refrigerant in front of the capillary. Re 12, it may be appropriate according to a further modification, when switching from the accessory cooling operation of the evaporator 14 to the regular cooling operation of the evaporator 13 at time t1 to close the stop valve 7 for a short time, in order to reduce refrigerant in the collector 22nd accumulate, which then, when the stop valve 7 is opened again, gushing into the evaporator 13. Thus, shortly after the start of the cooling operation of the evaporator 13, a pressure can be produced in the latter, which makes it possible to evaporate the refrigerant at a temperature which is appropriate for a normal refrigeration compartment at approximately 0 ° C.

Correspondingly, according to a further development, if at the time t5 the regular cooling operation phase of the freezer evaporator 14 ends, the stop valve 7 is first closed and the compressor 1 is then operated for a while thereafter. In this way, the amount of liquid refrigerant left in the evaporator 14 after the cooling operation phase is reduced, and the resulting evaporative cooling cools the freezer compartment. The refrigerant evaporated in this way can no longer be displaced in liquid form from downstream refrigerant during a subsequent cooling operating phase of the evaporator 14 and is available in a subsequent cooling operating phase of the evaporator 13 to fill it in such a short time that an adequate evaporation temperature is reached. Even at the time t3, after the regular cooling operation phase of the evaporator 13, it can be provided that initially the stop valve 7 is closed and turned off only after a certain waiting time of the compressor 1. As a result, the evaporation pressure in the normal refrigeration evaporator 13 would drop to close to that of the freezer evaporator 14, which would result from the time t3 lower temperatures of the evaporator 13 as shown in the lower diagram of FIG. The resulting reduced pressure difference between the two sides of the check valve 18 reduces any leakage of refrigerant vapor through the check valve 18 and thus an undesirable heat input into the freezer evaporator 14th REFERENCE NUMBERS

1 compressor

2 output

3 entrance

4 refrigerant line

5 liquefier

6 dryers

7 stop valve

8 way valve

9 branch

10 branch

1 1 capillary

12 capillaries

13 evaporators

14 evaporator

15 subject

16 compartment

17 confluence

18 check valve

19 control unit

20 temperature sensor

21 temperature sensor

22 Refrigerant collector

23 frame heating

30

Claims

Refrigerating appliance, in particular household refrigerating appliance, with a compressor (1), a first evaporator (1 3) for cooling a first compartment (1 5), a second evaporator (14) for cooling a second compartment (1 6), in parallel branches (9, 1 0) of a refrigerant line (4) are arranged, and with a control unit (1 9), which is connected to temperature sensors (20, 21) of the first and the second compartment (1 5, 1 6) to a cooling operation phase (t1 -t3) of the first compartment (1 5) when exceeding a switch- _on temperature (T _{on, 15} ) of the first compartment (1 5) to start and terminate upon the occurrence of a switch-off condition of the first compartment (1 5), characterized in that the control unit (1 9) is further arranged to start on exceeding the switch- _on temperature (T _{on, 15} ) of the first compartment (1 5) also an accessory cooling operation phase (t0-t1) of the second compartment (1 6) and a temperature (T1 ₁₆ ) of the second compartment (1 6), in which the accessory cooling operation phase (t0-t1) is terminated, based on a target temperature ( _Ta rget, i6) of the second compartment (1 6) and a prevailing at the beginning of the accessory cooling operating phase (t0-t1) of the second compartment (1 6) temperature (T0i ₆ ) of the second compartment (1 6).

Refrigerating appliance according to claim 1 or 2, characterized in that the control unit (1 9) is adapted to start the accessory cooling operation phase (t0-t1) only when the temperature (T0i ₆ ) of the second compartment (1 6) above the target temperature (Ttarget, i6) of the second compartment (1 6).

Refrigerating appliance according to claim 1 or 2, characterized in that the sum of the starting temperature (T0i ₆ ) and the end temperature (T1 ₁₆ ) of the accessory cooling operating phase (t0-t1) is a constant (2 * _Ta rget, i6).

Refrigerating appliance according to claim 1, 2 or 3, characterized in that the control unit (1 9) is arranged, a cooling operation phase of the second compartment (1 6) even when exceeding a switch-on (T _{on, 16} ) of the second compartment (1 6) start and this cooling operation phase when it falls below a switch-off temperature (T ₀ ff, i ₆ ) of the second compartment (1 6) to end, the target temperature ( _Ta rget, i6) between the switch-on temperature (T _{on, 16} ) and the switch-off temperature (T _{off, 16} ).

5. Refrigerating appliance according to claim 4, as far as dependent on claim 3, characterized in that the constant (2 ^* T _ta rget, i6) equal to the sum of switch-on temperature (T _{on, 16} ) and switch-off (T _{off, 16} ) of the second compartment (16).

6. Refrigerating appliance according to one of the preceding claims, characterized in that the control unit (19) is set up, the cooling operation phase (t1 -t3) of the first compartment (15) and the accessory cooling operation phase (t0-t1) of the second compartment (16) in a same operating phase (t0-t3) of the compressor (1) to perform.

7. Refrigerating appliance according to one of the preceding claims, characterized in that the second compartment (16) is colder than the first compartment (15).

8. Refrigerating appliance according to claim 7, characterized in that the control unit (19) is adapted to perform the accessory cooling operation phase (t0-t1) before the cooling operation phase (t1 -t3) of the first compartment (15). 9. Refrigerating appliance according to one of claims 1 to 6, characterized in that the second compartment (15) is warmer than the first compartment (16) and the control unit (19) is arranged, the accessory cooling operation phase after the cooling operation phase of the first compartment (16 ). 10. Refrigerating appliance according to one of the preceding claims, characterized in that in a downstream part of the refrigerant line (4) between outputs of the evaporator (13, 14) and an input (3) of the compressor (1) a valve (18) for locking a Refrigerant flow from the first evaporator (13) to the second evaporator (14) is arranged.

1 1. Refrigeration appliance according to claim 10, characterized in that in an upstream part of the refrigerant line (4) between an output (2) of the Compressor (1) and inputs of the evaporator (13, 14) a stop valve (7) is arranged.

Refrigerating appliance according to claim 1 1, characterized in that the control unit is set up, a time offset between a start of the compressor (1) and an opening of the stop valve (7) and / or between a switching off of the compressor (1) and a closing of the stop valve ( 7) to control.

Chiller according to claim 12, characterized in that a refrigerant collector (22) in the refrigerant line (4) upstream of the stop valve (7) is arranged.

Method for operating a refrigerating device, in particular a household refrigerating appliance, with a compressor (1), a first evaporator (13) for cooling a first compartment (15), and a second evaporator (14) for cooling a second compartment (16) a refrigerant line (4) are interconnected, comprising the steps of:

a) monitoring (S1) the temperature of the first compartment (15), and,

if the temperature of the first compartment ( ₁₅ ) exceeds a switch-on temperature (T _{on, 15} ) (S2),

b) starting (S4, S17) a cooling operation phase (t1 -t3) of the first compartment (15) and terminating the cooling operation phase (S5, S18) upon occurrence of a turn-off condition of the first compartment (15),

c) starting (S8) an accessory cooling operation phase (t0-t1) of the second compartment (16) and terminating (S9) the accessory cooling operation phase (t0-t1) when the temperature of the second compartment (16) is one based on the at the beginning of the accessory Cooling phase (t0-t1) prevailing initial temperature (T0i ₆ ) of the second compartment (16) set final temperature (T1 ₁₆ ).

A method according to claim 14, characterized in that the switch-off condition, the falling below a final temperature (T1 ₁₅ ), at the entrance of the cooling operation phase (t1 -t3) of the first compartment (15) is terminated, the falling below a final temperature (T1 ₁₅ ), the is determined based on the prevailing at the beginning (t1) of this cooling operation phase (t1 -t3) temperature (T0i ₅ ) of the first compartment (15).