阅读说明：本技术 制冷器具 (Refrigeration device ) 是由 S·霍尔策 H·德罗特莱夫 M·姆尔齐格洛德 于 2020-01-23 设计创作，主要内容包括：本发明涉及一种制冷器具、尤其是家用制冷器具,其具有：液化器(4)、冷却第一存放格(23)的至少一个第一蒸发器(7)；节流部(6),该节流部将液化器(4)与第一蒸发器(7)的入口连接；用于从第一蒸发器(7)溢出的液态制冷剂的接收容器(8、30),该接收容器衔接于第一蒸发器(7)的出口并且布置在比第一蒸发器(7)的周围环境更热的周围环境中,其中,接收容器(8、30)配属有温度传感器(20),并且节流部(6)包括能控制的膨胀阀(14),所述膨胀阀根据由温度传感器(20)检测的温度来控制。(The invention relates to a refrigerator, in particular a domestic refrigerator, comprising: a liquefier (4), at least one first evaporator (7) cooling the first storage compartment (23); a throttle section (6) that connects the liquefier (4) to the inlet of the first evaporator (7); a receiving container (8, 30) for liquid refrigerant overflowing from the first evaporator (7), which receiving container is connected to an outlet of the first evaporator (7) and is arranged in a warmer surroundings than the surroundings of the first evaporator (7), wherein a temperature sensor (20) is assigned to the receiving container (8, 30), and the throttle section (6) comprises a controllable expansion valve (14) which is controlled as a function of the temperature detected by the temperature sensor (20).)

1. A refrigerator, in particular a domestic refrigerator, having a refrigerant circuit in which a liquefier (4), an accumulator (5), a throttle (6) and at least one first evaporator (7) cooling a first storage compartment (23) are connected in series in the stated order, characterized in that the accumulator (5) has a capacity which is dimensioned to provide space for at least half, preferably 90%, of the refrigerant in the liquid state.

2. The refrigerator according to claim 1, characterized in that the accumulator (5) is dimensioned to additionally also completely provide space for residual gas contained in the refrigerant circuit that is not drawn away when the refrigerant circuit is assembled.

3. The refrigeration appliance according to claim 1 or 2, wherein the capacity of the collector (5) is at least 50cm³And/or up to 200cm³。

4. The refrigeration appliance according to any of the preceding claims, wherein the collector (5) has an inlet and an outlet, wherein the outlet is lower than the inlet, preferably at least 2cm lower, more preferably at least 4cm lower.

5. The refrigeration appliance according to claim 4, wherein said inlet is shaped to feed a horizontally oriented flow of refrigerant into said accumulator (5).

6. The refrigeration appliance according to any of the preceding claims, wherein the collector (5) has at least partially a horizontal cross-sectional dimension of at least 8mm, preferably at least 15mm and/or has at least 0.5cm between the inlet and outlet (12, 13)²Preferably at least 2cm²The horizontal cross-sectional area of (a).

7. Refrigeration appliance according to any of the preceding claims, characterized in that a receiving container (8, 30) for liquid refrigerant overflowing from the first evaporator (7) is engaged at the outlet of the first evaporator (7) and arranged in a warmer ambient than the ambient of the first evaporator (7), that a temperature sensor (20) is assigned to the receiving container (8, 30), and that the throttle section (6) comprises a controllable expansion valve (14) which is controlled as a function of the temperature detected by the temperature sensor (20).

8. The refrigerator according to claim 7, wherein the receiving container (8) is separated from the first storage compartment (23) by a layer of insulating material (27).

9. The refrigeration appliance according to claim 7 or 8, characterized in that a capillary tube (15) is connected upstream of the controllable expansion valve (14), preferably dimensioned to have a smaller pressure drop than the controllable expansion valve (14).

10. The refrigeration appliance according to any of the preceding claims, wherein the receiving container (8) is a second evaporator (8).

11. The refrigerator according to claim 10, wherein the operating temperature of the second storage compartment (21) cooled by the second evaporator (8) is higher than the operating temperature of the first storage compartment (23).

12. The refrigeration appliance according to claim 10 or 11, characterized in that the temperature sensor (20) is a compartment temperature sensor of the second storage compartment (21).

13. The refrigeration appliance according to claim 10, 11 or 12, characterized in that the controllable expansion valve (14) is arranged in an intermediate wall (25) between the storage compartments (21, 23), preferably in a clearance (28) of a thermally insulating layer (27) contained in the intermediate wall (25), which clearance is open towards the first storage compartment (23).

14. A refrigerator appliance according to any of the preceding claims, wherein the capacity of the receiving container (8, 30) is dimensioned to provide space for at least half of the refrigerant in the liquid state.

15. The refrigeration appliance according to any of the preceding claims, characterized in that a control circuit (22) is configured to set a high mass flow in case the detected temperature is high and to set a low mass flow in case the detected temperature is low by means of the controllable expansion valve (14).

Technical Field

The invention relates to a refrigerator, in particular a domestic refrigerator, such as a freezer or freezer cabinet or a combination appliance, having a plurality of compartments which are maintained at different operating temperatures.

Background

In addition to energy efficiency, small or inconspicuous operating noises are an important quality feature of domestic refrigeration appliances. The main cause of operational noise is the refrigerant circulation in such appliances. Although the compressor and, if present, the ventilator of the refrigeration appliance are not noiseless, they can be controlled to run at the same speed so that the noise generated by them is only barely perceptible due to their uniformity.

For cost reasons, domestic refrigeration appliances usually use capillary tubes as throttle for decompressing the refrigerant. The capillary cannot be actively adjusted; as long as liquid refrigerant having a high density is present at the inlet of the capillary tube, the mass flow of the capillary tube is high. If the refrigerant exits through the capillary tube, the refrigerant vapor enters the capillary tube. This results in a reduction in the mass flow due to the low density of the vapor, so that the refrigerant condenses again before the capillary tube, and on the other hand, the vapor passes through the capillary tube at a higher velocity than the liquid refrigerant, and the velocity fluctuations that result therefrom lead to clearly perceptible fluctuations in the operating noise.

Thermostatic expansion valves that allow active control of mass flow are common in commercial refrigeration units. These valves are usually arranged downstream of the accumulator in order to control the mass flow of refrigerant on the basis of the measurement of the pressure sensor, so that liquid refrigerant is always present in the accumulator, which liquid refrigerant prevents gaseous refrigerant from reaching the expansion valve. By keeping the gaseous refrigerant away from the expansion valve, efficiency losses that occur when the spent energy cannot be used because on the one hand the vapor is compressed with the input of energy and on the other hand it is expanded in the expansion valve can be avoided. The expansion valve is significantly more expensive than the capillary tube conventionally used in domestic refrigeration appliances, and moreover the installation of the pressure sensor is laborious, since the pressure sensor must be in direct communication with the refrigerant to be measured and must be suitably sealed. Therefore, no consideration has been given so far to the transfer of this technology to domestic refrigeration appliances, which, although it has the advantages of being irrelevant and therefore unnoticeable in commercial refrigeration appliances, is particularly relevant for domestic refrigeration appliances: the expansion valve (since no vapor alternately flows through it as liquid refrigerant) operates with low noise.

Disclosure of Invention

The object of the invention is to provide a low-noise refrigerator. This is achieved with little control effort and correspondingly at little cost by: in the refrigerant circuit, a liquefier, an accumulator, a throttle and at least one first evaporator cooling a first storage compartment are connected in series in the order described, the accumulator having a capacity which is dimensioned to provide space for at least half, preferably 90%, of the refrigerant in the liquid state. This spacious accumulator gives the entire refrigerant circuit a large volume compared to a conventional refrigerant circuit of the same power, and requires a corresponding increase in the amount of filling of refrigerant. Thus, there is almost always enough liquid refrigerant stored in the accumulator when the refrigeration appliance is in operation to keep the refrigerant vapor away from the restriction.

Furthermore, the accumulator may also be sized to provide space for non-condensable residual gases that are not pumped away when the refrigerant circuit is assembled. Today's manufacturing methods allow to pump the refrigerant circuit to less than 30mg N at assembly₂To provide space for the gas quantity at a compressor output pressure of about 6bar, which requires 3-4cm³The volume of (a).

By dimensioning the accumulator sufficiently spacious, it is possible to neutralize a larger amount of residual gas than is currently usual when evacuating the refrigerant circuit. That is, the spacious accumulator allows shortening of suction air at the time of assembling the refrigerant circuit, thereby improving productivity.

The total capacity of the accumulator is preferably at least 50cm in a domestic refrigeration appliance of conventional size³. Should not exceed 200cm³So that it is not necessary to increase the refrigerant charge amount required for efficient operation.

To ensure a reliable separation of liquid and gaseous refrigerant in the accumulator, the outlet of the accumulator should be lower than the inlet, preferably at least 2cm lower, more preferably at least 4cm lower.

The configuration of the collector can be selected or adapted to the available installation space in a wide range of options, and its cross section can vary widely in the flow direction, and in particular can vary without steps. In contrast, for practical reasons, the line leading to or from the collector, respectively, usually has a constant cross section. Thus, in particular, such points in the refrigerant circuit can be considered as inlet and outlet: at this point, the cross section abruptly increases downstream of the supply line or exceeds the cross section of the line by more than a predetermined percentage, or at this point, the cross section abruptly decreases upstream of the discharge line or drops below the cross section of the line (by a predetermined percentage).

In order to resist the inflow of refrigerant vapor from mixing with liquid refrigerant present in the lower region of the accumulator, the inlet may be shaped to feed a horizontally oriented flow of refrigerant into the accumulator.

To avoid capillary effects against good separation of liquid and vapor, the collector preferably has a maximum horizontal cross-sectional dimension of at least 8mm or at least 0.5cm between the inlet and the outlet²The maximum horizontal cross-sectional area of. Larger values, e.g. at least 15mm or at least 2cm²Is preferred in order to enable a compact implementation of the collector.

The accumulator may contain internals to prevent the formation of vortices in the liquid refrigerant, such as intermediate walls or particle packings.

In order to be able to ensure that no refrigerant vapor can advance to the throttle under all practically relevant operating conditions, the throttle should be adjustable. The throttle can in particular comprise a controllable expansion valve, which is controlled by means of a temperature sensor.

The temperature sensor can be arranged on a receiving container for liquid refrigerant overflowing from the first evaporator, which receiving container is connected to the outlet of the first evaporator and is arranged in a warmer surroundings than the surroundings of the first evaporator.

The receiving vessel provides a buffer whose filling degree of the liquid refrigerant can be estimated based on the measured temperature. By controlling the mass flow through the expansion valve by means of this temperature, it can be ensured that sufficient liquid refrigerant is available at any time upstream of the throttle when the compressor is running, so that the vapor can be kept away from the expansion valve. At the same time, it is possible to completely fill the first evaporator with liquid refrigerant and thus to provide the high cooling power required, for example, for rapid cooling of freshly loaded refrigerated goods. By installing the receiving container in a warmer ambient than the first evaporator, it can be ensured that liquid refrigerant overflowing from the first evaporator into the receiving container does not accumulate there, but evaporates immediately.

In order to ensure different ambient temperatures of the first evaporator and the receiving container, the receiving container can be separated from the first storage compartment by a thermal insulation layer.

In order to be able to control the small mass flow through the expansion valve accurately, it can be advantageous to connect the expansion valve in series with the capillary tube, so that a part of the pressure difference between the liquefier and the first evaporator drops at the capillary tube and the remaining part drops at the expansion valve.

In order to avoid evaporation starting shortly before its downstream end in the capillary tube and thereby generating noise due to the alternation of vapor and liquid refrigerant at the output of the capillary tube, the capillary tube should be arranged upstream of the expansion valve and the pressure difference dropping there should be sufficiently small to prevent evaporation of the refrigerant before reaching the expansion valve.

Typically, the capillary tube should be dimensioned for this purpose with a smaller pressure drop than the controllable expansion valve.

The outlet of the liquefier should be connected to the throttle section without an intermediate connection of a further evaporator.

According to a particularly preferred embodiment, the receiving container is a second evaporator. The second evaporator may be of the same type of construction as the first evaporator, for example a pressure welded evaporator, ToS or finned evaporator.

Suitably, the second evaporator is for cooling the second storage compartment.

Since the second evaporator receives liquid refrigerant only when the first evaporator overflows, the operating temperature of the second storage compartment should be higher than that of the first storage compartment.

The evaporators can be arranged in direct thermal contact with the compartments cooled by them, i.e. the above-mentioned surroundings of the first evaporator and the receiving container or the second evaporator can be the compartments themselves.

The cell temperature sensor of the second storage cell may be used as the above-described temperature sensor that controls the expansion valve. Thus, costs associated with the installation of additional sensors can be avoided.

In order not to unnecessarily limit the available space for accommodating one or more evaporators, controllable expansion valves can be arranged in the separating wall between the compartments. In particular, the rear wall of the storage compartment therefore remains fully available for mounting one of the evaporators thereon.

The insulation layer may be part of the separation wall. Since the expansion valve cools during operation, the space of the insulating layer accommodating the expansion valve is open at least to the cooler storage compartment, i.e. generally to the first storage compartment.

In order to reliably prevent overflow of the receiving container or the second evaporator, its capacity should be dimensioned to provide space for at least half of the refrigerant in the liquid state. This space need not be sufficient for all refrigerant, since liquid refrigerant usually only reaches the receiver vessel after the first evaporator is full.

A control circuit is provided to set a high mass flow rate in case the detected temperature is high and a low mass flow rate in case the detected temperature is low through a controllable expansion valve.

Drawings

Further features and advantages of the invention result from the following description of an embodiment with reference to the drawings. The figures show:

fig. 1 is a block diagram of a refrigeration appliance according to a first configuration;

FIG. 2 is a cross-section of a collector according to a first embodiment;

FIG. 3 is a cross-section of a collector according to a second embodiment;

FIG. 4 is a schematic cross-section of the refrigeration appliance of FIG. 1;

fig. 5 is a block diagram of a refrigeration device according to a second embodiment of the invention; and

fig. 6 a schematic cross section of the refrigeration appliance in fig. 5.

Detailed Description

Fig. 1 illustrates the concept of the invention by means of a block diagram which essentially shows the components of the refrigerant circuit of a domestic refrigeration appliance. The refrigerant circuit comprises, in a manner known per se, a compressor 1, from whose pressure connection 2 a pressure line 3 extends via a liquefier 4 and an accumulator 5 or a dryer to a throttle 6. In the low-pressure part of the refrigerant circuit, which is connected to the throttle 6, the evaporator 7 and the evaporator 8 are connected in series, and a suction line 9, which leads from the evaporator 8, leads the refrigerant back to a suction connection 10 of the compressor 1.

At the collector 5, the pressure line 3 is locally expanded into a chamber 11 functioning as a steam separator, which has an inlet 12 at the upper end and an outlet 13 at the lower end. A mixture of liquid refrigerant and vapor enters accumulator 5 from liquefier 4 through inlet 12. Since the free cross-section of the accumulator 5 is larger than the free cross-section upstream and downstream of the pressure line 3, the flow velocity of the refrigerant in the accumulator decreases and the two phases of the refrigerant have the opportunity to separate from each other. In order to be able to be unimpeded by the capillary effect, the free cross-section of the collector 5 should at least partially reach at least 0.5cm²Should reach a value of at least 8 mm. A residence time of the refrigerant sufficient for the phase separation is achieved by the large volume of the chamber; this is preferably dimensioned to provide at least half of the total refrigerant present in the appliance in the liquid state, that is to say at a refrigerant fill of, for example, 50 or 100g and 0.95g/cm³In the case of density of (2), of the chamberThe capacity should be at least 50 or 100cm³. In order to prevent the liquid refrigerant present in the accumulator from generating a swirling motion and thus vapor bubbles reaching the outlet 13 when the refrigerant flows out via the outlet 13, a packing consisting of pellets, in particular of a dryer material which binds the remaining water in the refrigerant, can also be arranged in the region of the accumulator 5 close to the outlet.

Fig. 2 shows a schematic axial section of the collector 5 according to a first configuration. The collector 5 is here a rotationally symmetrical hollow body made of the same metal as the sections 37, 38 of the line 3, which are welded to the hollow body at the inlet 12 or the outlet 13. In the case shown here, after the dryer granulate 41 for binding the remaining water has been fixed in the lower housing part and by means of a screen 42, nonwoven or the like pushed over it, the hollow body itself is joined by the upper housing part 39 and the lower housing part 40. The volume occupied by the dryer pellets 41 occupies only a small fraction of the volume of the collector, in any case less than half. In the free space above the screen 42, the inflowing liquid and gaseous refrigerant can be separated without flow obstruction.

The sections 37, 38 may have different cross-sections; in particular, a smaller cross section is sufficient for the section 38 which conducts only liquid refrigerant than for the section 37 which also conducts vapor.

Fig. 3 shows a second configuration of the collector 5. As in the case of fig. 2, the dryer pellets 41 may be disposed in a lower portion of the inner space of the collector 5; alternatively, a separate dryer may be added to the refrigerant circuit for the dryer pellets. The upstream section 37 of the line 3 opens into the interior horizontally and offset with respect to the axis of rotational symmetry 43 of the collector 5, so that the liquid and gaseous refrigerant flows fed through this upstream section are offset in rotation about the axis 43 and the liquid fraction separates out on the wall of the collector. In the liquid phase in the lower part of the interior space, the rotation is damped by the screen or nonwoven 42 and, if necessary, the dryer granulate 41.

The collector 5 has a free volume of 50 to 200cm³. The density of the liquid refrigerant is about 2g/cm³And the filling amount is typically 100g, this volume is sufficient to contain at least half of the refrigerant injected in liquid form.

The throttle 6 comprises at least one controllable expansion valve 14. In the case shown in fig. 1, a capillary tube 15 is also provided between the collector 5 and the expansion valve 14. Capillary tube 15 is dimensioned to produce only a small part of the pressure drop between liquefier 4 and evaporator 7, while a larger part is produced at controllable expansion valve 14. The above-mentioned section 38 may be an integral part of the capillary 15; in other words, capillary tube 15 extends from outlet 13 of collector 5 consecutively to expansion valve 14. In particular, the nitrogen throughput of the capillary can be 500-800l/h with a pressure drop of 6 bar. The series connection with capillary tube 15 enables expansion valve 14 to accurately control a smaller mass flow at a given pressure differential than if the expansion valve were exposed to refrigerant pressure alone. Furthermore, because capillary tube 15 is disposed upstream of expansion valve 14, the pressure within capillary tube 15 is sufficiently high throughout its length to prevent evaporation of the refrigerant within capillary tube 15. Since the capillary tube is thus not cooled by internal evaporation, the residual heat of the liquid refrigerant can be efficiently transferred to the vapor returning to the compressor 1 in the suction tube, in the internal heat exchanger 16, in which the capillary tube 15 is in close contact with the suction tube 9.

The evaporator 8 is connected to the evaporator 7 in such a way that liquid refrigerant only enters the evaporator 8 when the evaporator 7 is full. For this purpose, for example, the evaporator 7 can be equipped with a refrigerant line 17 which rises continuously from an inlet 18 to an outlet 19 of the evaporator 7, so that the vapor generated in the evaporator 7 flows out in the direction of the outlet 19, but the liquid refrigerant can flow past the rising vapor in the direction of the inlet 18.

The temperature sensor 20 may be mounted on the evaporator 8; preferably, the temperature sensor is mounted in a storage compartment 21 cooled by the evaporator (see fig. 4), typically a normal refrigeration compartment of a refrigeration appliance, without direct contact with the evaporator 8, so as to detect the temperature of the storage compartment 21. The temperature is indicative of the amount of liquid refrigerant entering the evaporator 8, delayed and averaged over time.

The control circuit 22 is connected to the temperature sensor 20 and the expansion valve 14 for controlling the expansion valve on the basis of the measurement values of the temperature sensor 20. Furthermore, the control unit can also be connected to the compressor 1 in order to control the rotational speed of the compressor also as a function of these measured values and, if appropriate, as a function of the temperature measured in the storage compartment 23 (see fig. 4) cooled by the evaporator 7.

If the temperature detected by the temperature sensor 20 exceeds the rated value while the compressor 1 is operating, the expansion valve 14 is further opened. This happens gradually, that is to say as soon as the nominal value is exceeded, the control circuit 22 increases the opening degree of the expansion valve 14 continuously or at even small intervals, to ensure that the increase in opening degree does not lead to a temporary drying down of the collector 5 and to the admission of steam into the throttle 6. The likelihood of this occurrence is also reduced for the following reasons: the large volume of the accumulator 5 and the exceeding of the nominal value should take into account that the evaporator 8 contains a small amount of liquid refrigerant until there is no liquid refrigerant and accordingly must be stored in the accumulator 5 in large quantities. The supply of liquid refrigerant to the evaporator 7, which increases due to the increase in the opening degree, eventually overflows it, and the refrigerant entering the evaporator 8 causes the temperature detected by the temperature sensor 20 to decrease, reaching or falling below the nominal value, and the control circuit 22 does not further increase the opening degree of the expansion valve 14.

Conversely, as long as the temperature detected by the temperature sensor 20 is lower than the second rated value, which may be equal to or lower than the above-described rated value, while the compressor 1 is operating, the opening degree of the expansion valve 14 is gradually decreased. Thereby, the amount of liquid refrigerant reaching the evaporator 8 decreases, and the temperature of the storage compartment 21 detected by the temperature sensor 20 gradually increases. The cooling power available at the evaporator 7 does not change here, as long as refrigerant which is still completely in the liquid state reaches the evaporator 8. Only when this no longer occurs and the evaporator 7 is only not yet completely filled with liquid refrigerant, the cooling power of the evaporator is also reduced.

In order to adapt the cooling capacity to the respective requirements, it can be provided that the control circuit 22 also controls the rotational speed of the compressor 1 as a function of the cooling requirements of the storage compartment 23. If the measured temperature exceeds a target value in the storage compartment, the rotational speed of the compressor 1 is gradually increased. When the opening degree of the expansion valve 14 is not changed at the same time, this results in an increased evaporation in the evaporator 8 and a corresponding increase in the amount of liquid refrigerant in the accumulator 5. The increased evaporation causes the temperature in the holding compartment 23 to decrease, which is caused according to the principle set forth in the preceding paragraph, the opening degree of the expansion valve 14 is adjusted lower, less liquid refrigerant reaches the evaporator 8, and the additional cooling power remains substantially concentrated on the evaporator 7. Conversely, the rotational speed can be reduced below this setpoint value.

Fig. 4 shows a schematic cross section of the cabinet 24 of the refrigeration appliance of fig. 1. The cooler storage compartment 23 is arranged below the warmer storage compartment 21 and is separated from the warmer storage compartment by an intermediate wall 25. Like the rest of the cabinet 24, the intermediate wall 25 is also designed as a hollow body with an outer wall 26, the interior of which is filled with foam with an insulating material 27. The suction duct 9 extends downwards in the rear wall of the cabinet 24 at the two storage compartments 23, 21; over a portion of the length of this rear wall, capillary tube 15 extends inside the cabinet or is in contact with the outer wall of the cabinet to form an internal heat exchanger 16.

A void 28 is provided in the layer of insulating material 27 to accommodate the expansion valve 14. Since the expansion valve cools during operation, the recess 28 opens into the storage compartment 23 in order to be able to achieve a heat inflow from there to the expansion valve 14. This void may be closed by a less insulating cover 29, which may be removed to enable repair of the expansion valve 14 if necessary.

Fig. 5 shows a second configuration of the refrigeration device in a view similar to fig. 1. The components of the refrigerant circuit that are identical to those already described above are denoted by the same reference numerals and are not described repeatedly. The second evaporator 8 is replaced by a receiving container 30, which does not necessarily cool the storage compartment. Instead, the receiving container 30 is arranged in the evaporator chamber 31 of the frost-free refrigeration appliance upstream of the evaporator 7 with respect to the direction of circulation of the air flow circulating between the evaporator chamber 31 and the storage compartment 21 or 23, as is shown exemplarily in fig. 6.

Fig. 6 shows a section through the intermediate wall 32 of the frost-free refrigeration appliance. The evaporator chamber 31 is separated from the cold storage compartment 23 located therebelow by a thin separating wall 33 and from the warmer storage compartment 21 located thereabove by a wall filled with insulating material 27. A fan 34 is arranged in a manner known per se downstream of the evaporator 7, which is configured as a finned evaporator, in order to draw air from one of the compartments 21, 23, respectively, through an inlet 35. The position of the flap 36 determines which compartment air is drawn from. Regardless of the position of the flap 36, the air drawn in is always warmer upstream of the evaporator 7 than downstream thereof. Since the receiving container 30 is fitted upstream of the evaporator 7 in the evaporator chamber 31, the receiving container 30 is in a hotter environment than the evaporator and the refrigerant overflowing from the evaporator 7 into the receiving container 30 can still evaporate in the receiving container. By sufficiently dimensioning the common volume of the evaporator 7 and the receiving container 30 to receive all the refrigerant present in the refrigerant circuit in the liquid state, overflow of the receiving container 30 into the suction tube 9 can be precluded.

List of reference numerals

1 compressor

2 pressure interface

3 pressure line

4 liquefier

5 collector

6 throttling part

7 evaporator

8 evaporator

9 suction pipe

10 suction interface

11 chamber

12 inlet

13 outlet

14 expansion valve

15 capillary tube

16 heat exchanger

17 refrigerant pipe

18 inlet

19 outlet port

20 temperature sensor

21 storage grid

22 control circuit

23 storage grid

24 cabinet body

25 intermediate wall

26 outer wall

27 insulating material

28 left empty

29 cover

30 receiving container

31 evaporator chamber

32 intermediate wall

33 separating wall

34 Fan

35 inlet

36 valve

Section of 37-line 3

Section of 38-line 3

39 upper shell part

40 lower housing part

41 dryer pellets

42 mesh screen

43 axis.