DE102011079762A1 - HEAT EXCHANGER FOR A REFRIGERATOR, METHOD FOR MANUFACTURING A HEAT EXCHANGER AND REFRIGERATOR - Google Patents

Abstract

The invention relates to a heat exchanger (36) for a refrigeration appliance (10), in particular for a household refrigerating appliance, which has a refrigerant line (34). The refrigerant line (34) has a flow cross-sectional area (56) through which a refrigerant (32) flows in use. Furthermore, the refrigerant line (34) has a constriction for reducing the flow cross-sectional area (56). The invention also relates to a method for producing the heat exchanger (36) and a refrigeration device (10) which is equipped with such a heat exchanger (36).

Description

The invention relates to a heat exchanger for a refrigeration device, in particular for a household refrigerating appliance, which has a refrigerant line. Furthermore, the invention relates to a method for producing such a heat exchanger and a refrigerator, which is equipped with such a heat exchanger.

A refrigeration appliance is understood in particular to be a household refrigerating appliance, that is to say a refrigeration appliance which is used for household purposes or possibly also in the gastronomy sector and serves, in particular, for storing food and / or drinks in household quantities at specific temperatures, such as, for example, a refrigerator , a freezer, a fridge-freezer, a drink box or a wine storage cabinet.

As a heat exchanger without forced ventilation today usually Blechwandverflüssiger or Drahtrohrverflüssiger be used, as for example in the WO 2007/124705 A1 or EP 1 460 357 B1 are described. In both cases, for cost reasons, regardless of the compressor capacity and the mass flow, a steel pipe with mostly 4.76 mm outer diameter and 3.3 mm inner diameter, ie with 8.54 mm ² flow cross-sectional area, use.

In a wire tube condenser, wires are welded onto a pipe of the refrigerant pipe, so that a sufficient wall thickness of the pipe is advantageous. In a plate wall condenser, the refrigerant line is placed on a metal sheet. Both the metal sheet and the wires that are in contact with the refrigerant line improve the heat dissipation to the environment.

Alternatively, the refrigerant line can be mounted as a so-called skin condenser directly to a housing wall of the refrigerator.

As the efficiency of refrigeration equipment progresses, the mass flow flowing within the refrigerant piping is continually reduced. As a result, the heat transfer on the inside of the refrigerant piping is degraded by the reduction of the flow rates.

The object of the invention is to propose an improved heat exchanger for a refrigerator.

This object is achieved with a heat exchanger with the combination of features of claim 1.

A method for producing such a heat exchanger and a refrigeration device, which is equipped with such a heat exchanger, are the subject of the dependent claims.

Advantageous embodiments of the invention are the subject of the dependent claims.

A heat exchanger for a refrigeration device, in particular for a household refrigerating appliance, has a refrigerant line. The refrigerant line has a flow cross-sectional area through which refrigerant flows in use. A restriction is provided for reducing the flow cross-sectional area.

In the known condensers, a refrigerant line with a large flow cross-sectional area is used. At high efficiency of the refrigerator flows through the flow cross-sectional area only a small amount of refrigerant with a low flow velocity. As a result, only a small part of a wall of the refrigerant line is wetted with a relatively thick refrigerant film. This results in a deteriorated heat transfer from refrigerant to wall and thus has a negative effect on the efficiency of the heat exchanger and refrigerator.

However, if the heat exchanger is narrowed, the small amount of refrigerant is passed through a reduced flow cross-sectional area, thereby increasing the flow rate. The refrigerant film becomes thinner, resulting in better heat transfer from the refrigerant to the wall of the refrigerant pipe.

An additional advantage of a reduced flow cross-sectional area is that the storage volume in the refrigerant line, i. the amount of refrigerant in the refrigerant piping is reduced. In particular, in refrigerators with automatic start-stop, in which the compressor is switched off regularly, there is a temperature difference of the refrigerant, which is located inside the condenser, to the refrigerant, which is located inside the evaporator. Due to this temperature difference and the resulting pressure difference, refrigerant passes from the condenser into the evaporator. Since the refrigerant from the condenser is warmer than the refrigerant in the evaporator, this crossing causes heating of the actually to be cooled inside the refrigerator.

The reduced flow cross-sectional area also reduces the amount of refrigerant which could pass from the condenser into the evaporator. This results in a further increase in efficiency of the refrigerator.

To create the constriction, there are different possibilities, which may alternatively or cumulatively exist in any combination.

Particularly preferably, a reduction device is arranged in the interior of the refrigerant line. If, for example, a core is inserted into the interior of the refrigerant line, the flow cross-sectional area through which the refrigerant can flow is reduced. The refrigerant is thus forced to preferentially wet a larger portion of the wall of the refrigerant line.

Therefore, it is also advantageous if the reduction device is arranged to be flushed with the refrigerant.

Advantageously, the reduction device has a flexible element with the same cross-sectional shape as that of the refrigerant line. So it is advantageous particularly easy to introduce the reduction device later in the refrigerant pipe.

Alternatively or in addition to the reduction device, however, a constriction can also be created by using a tube with a smaller diameter.

For example, instead of the usual 4.75 mm diameter refrigerant piping, a 4.0 mm diameter refrigerant piping may be used. A small flow cross-sectional area, which is in particular smaller than 8.54 mm ^2, is preferred. The flow cross-sectional area is preferably 20%, particularly preferably 40% smaller than 8.54 mm ² .

Another way to create a constriction is in a design of the cross-sectional shape of the refrigerant line.

In a preferred embodiment, the refrigerant line has a flattening. If the refrigerant line, for example, by subsequent pressing with a pressing tool, preferably provided with an elliptical flow cross-sectional area, in spite of an originally large flow cross-sectional area favorable for the heat transfer efficiency flow profile can be created.

The restriction may be local at one or more locations, or may extend over at least a portion of the length of the refrigerant conduit or over its entire length.

Preferably, enlarging means for enlarging a heat releasing surface between the refrigerant piping and a heat transfer means for transferring heat from the refrigerant piping to an environment is further provided. Thus, preferably, a major portion of the heat transfer device is in thermal contact with the refrigerant line, and also the heat transfer efficiency from wall to ambient is improved.

The enlarging device is advantageously arranged on the outside of the refrigerant line. Thus, the enlarging device can preferably be attached to the refrigerant line even after completion of the heat exchanger.

For example, the enlarging device may comprise a heat storage mass. This is particularly preferably formed from bitumen. The heat storage mass is able to absorb a large amount of heat from the refrigerant line and thus dissipate quickly from the walls of the refrigerant line. It then advantageously stores the heat and can deliver it over a longer period to the environment.

Further advantageously, the enlarging device comprises a heat conducting device. This heat conducting device is in a particularly preferred embodiment, a metal strip and in particular an aluminum strip. Heat is preferably dissipated from the refrigerant line and discharged to the heat transfer device via the heat conducting device.

In a particularly preferred embodiment, the enlarging device is at least partially arranged to encase the refrigerant line. If, for example, the heat storage mass and / or the heat conduction device surrounds the refrigerant line, advantageously a larger proportion of the refrigerant conduction wall is in contact both with the environment and with the heat transfer device and heat can be removed from the refrigerant line so quickly.

Particularly preferably, the enlarging device is designed to fasten the refrigerant line to a housing wall of the refrigeration device. This can be achieved, for example, by using the aforementioned aluminum strip or bitumen as the adhesive material.

• a) Bereitstellen einer Kältemittelleitung mit einer Strömungsquerschnittsfläche;
• b) Verkleinern der Strömungsquerschnittsfläche.

A method of manufacturing a heat exchanger includes the following steps:

• a) providing a refrigerant line having a flow cross-sectional area;
• b) Reduction of the flow cross-sectional area.

• b1) Abflachen der Kältemittelleitung; und/oder
• b2) Einschieben eines Verkleinerungselements in ein Inneres der Kältemittelleitung. Vorteilhaft ist der Schritt c) Befestigen der Kältemittelleitung an einer Wärmeübertragungseinrichtung oder an einer Gehäusewand des Kältegerätes vorgesehen.

Advantageously, step b) has at least one of the following steps:

• b1) flattening the refrigerant line; and or
• b2) inserting a reduction element into an interior of the refrigerant line. The step c) attaching the refrigerant line to a heat transfer device or to a housing wall of the refrigeration device is advantageously provided.

In a particularly preferred embodiment, the refrigerant line is encased in a step d) with a heat conducting device and / or a heat storage mass.

All steps b1), b2) and d) can advantageously be carried out subsequently after producing the heat exchanger. For example, the refrigerant line may be flattened by using a press tool having cutouts for the wires of a wire tube condenser. Thus, only the pipe of the refrigerant pipe is flattened and deformed elliptically, while the wires preferably remain unaffected by the pressing tool.

The insertion of a reduction device can also advantageously be carried out after the heat exchanger has been produced, in particular if a flexible element is used which has the same cross-sectional shape as the refrigerant line.

A sheathing of the refrigerant line by coating with bitumen, for example, as a heat storage mass or by adhering, for example, an aluminum strip as a heat conduction device can preferably be carried out subsequently.

• – Verflüssiger,
• – Drossel,
• – Verdampfer, und
• – Verdichter.

A refrigeration appliance, in particular a household refrigerating appliance, has a housing with at least one interior space and a refrigerant circuit designed to cool the at least one interior space. The refrigerant circuit has at least one of the following elements:

• - liquefier,
• - Thrush,
• - evaporator, and
• - Compressor.

In a particularly preferred embodiment, the condenser and / or the evaporator are designed as heat exchangers having the properties described above. Further advantageously, the refrigeration device can be produced by the method described above.

Preferred embodiments of the invention are explained below with reference to the accompanying drawings. It shows:

1 a refrigerator as a fridge freezer with a refrigerant circuit;

2 a heat exchanger in the embodiment of a Blechwandverflüssigers;

3 a heat exchanger in the embodiment of a wire tube liquefier;

4 a cross section through a circular refrigerant pipe with a large flow cross-sectional area;

5 a cross-section through a circular refrigerant pipe with a small flow cross-sectional area;

6 a cross section through a refrigerant pipe with elliptical flow cross-sectional area;

7 the arrangement of a pressing tool for generating the elliptical flow cross-sectional area 6 ;

8th a cross section through a refrigerant pipe with a reduction device inserted therein;

9 a cross section through a fastened with aluminum tape refrigerant pipe; and

10 a cross section through a refrigerant pipe with applied bitumen layer.

1 shows a refrigerator 10 in the embodiment of a refrigerator / freezer combination with a refrigerated compartment 12 and a freezer 14 ,

The refrigeration device 10 has a heat-insulated housing 16 with housing walls 17 on, in common with heat-insulated doors 18 inside rooms 20 of the refrigerator compartment 12 and the freezer compartment 14 limit.

For cooling the interiors 20 is a refrigerant circuit 22 on the refrigeration device 10 arranged. This refrigerant circuit 22 has a condenser 24 , a throttle 26 , one in the refrigerator compartment 12 and in the freezer 14 , interconnected, evaporator 28 and a compressor 30 on. A refrigerant 32 is via a refrigerant pipe 34 in the refrigerant circuit 22 guided.

The evaporators 28 and the liquefier 24 each serve as a heat exchanger 36 about which the refrigerant 32 Heat to an environment 38 outside the refrigerator 10 releases or via which the refrigerant 32 Heat from the interior 20 of the refrigeration device 10 receives.

2 and 3 show embodiments of the condenser 24 out 1 , In 2 is an embodiment as Blechwandverflüssiger 40 and in 3 in the embodiment as a wire tube condenser 42 shown.

In the case of Blechwandverflüssigers 40 is the refrigerant line 34 in a tin wall 44 embedded, leaving heat from walls 46 the refrigerant line 34 on the sheet metal wall 44 can be transferred. This then gives the heat to the environment 38 from. Thus, the sheet metal wall forms 44 a heat transfer device 48 ,

In 3 are between snakes 50 the refrigerant line 34 wires 52 on the walls 46 welded, the heat from the walls 46 to the environment 38 transfer. Thus, in this embodiment, the wires form 52 the heat transfer device 48 ,

Due to the planar design of the sheet metal wall 44 arises in the contact area with the refrigerant line 34 a linear heat delivery surface 54 between sheet metal wall 44 and refrigerant piping 34 , In the case of the wire tube liquefier 42 are the wires 52 punctually on the walls 46 the refrigerant line 34 welded, so here punctiform heat delivery surfaces 54 between the refrigerant line 34 and the wires 52 arise.

4 shows a cross-sectional view through the refrigerant line 34 of the wire tube liquefier 42 out 3 , The refrigerant line 34 here has a circular flow cross-sectional area 56 on. Parallel running above and below the refrigerant line 34 are the wires 52 On Wall 46 welded, so that as far as possible a point-shaped heat transfer surface 54 arises. The same arrangement is also in 5 shown, but here has the refrigerant line 34 a smaller flow cross-sectional area than the refrigerant line 34 in 4 ,

Flows little refrigerant 32 in the refrigerant line 34 , then, as in 4 to see only a lower area 58 the Wall 46 wetted. Accordingly, only in this area 58 Heat from the refrigerant 32 On Wall 46 be delivered. In addition, that is due to the refrigerant 32 educated movie 59 thick and the resistance to heat transfer from refrigerant 32 effort 46 large.

Indicates the refrigerant line 34 now a smaller flow cross-sectional area 56 on, like in 5 can also see a small amount of refrigerant 32 the entire wall 46 wet and the movie 59 gets thinner. The heat transfer efficiency is thereby increased.

6 shows a further embodiment of the refrigerant line 34 , Here is the flow cross-sectional area 56 the refrigerant line 34 no longer circular, but elliptical. This means she has a flattening 60 in the areas of refrigerant piping 34 on that with the wires 52 are in contact.

7 shows how an elliptical flow cross-sectional area 56 starting from the embodiments in 4 and 5 can be achieved. This is a pressing tool 64 provided, the recesses 66 having. The pressing tool 64 is then so at the wire tube liquefier 42 out 4 arranged that press stamp 68 flat on the wall 46 rest, and join the wires 52 in the recesses 66 are located. Then in the direction of the arrow shown the press punches 68 moved towards each other, causing the refrigerant pipe 32 is compressed and the flattening 60 arises. Because of the wires 52 in the recesses 66 are arranged, they are through the pressing tool 64 not changed in shape.

The flattening 60 simultaneously forms a magnification device 69 that the heat delivery area 54 flat and planar forms and thus compared to the substantially point-shaped heat transfer surface 54 of the 4 and 5 enlarged, and a reduction device 70 because the flow cross-sectional area 56 in comparison to the embodiment in FIG 4 is reduced.

8th shows a further embodiment of the refrigerant line 34 , The refrigerant line 34 also in the embodiment in 8th a circular flow cross-sectional area 56 on and has about the same diameter as the refrigerant pipe 34 out 4 , Around the flow cross-sectional area 56 to downsize, here is the reduction device 70 in the form of a reduction element 71 internally 72 the refrigerant line 34 arranged. The reduction device 70 has the same cross-sectional shape as the refrigerant line 34 , ie it is also circular in shape. Around the reduction device 70 slightly into the refrigerant line 34 to introduce, is the reduction device 70 as a flexible element 74 educated. It is loose in the refrigerant line 34 pushed in, leaving them in the Refrigerant line 34 flowing refrigerant 32 on the entire circumference 76 is washed around.

9 and 10 show embodiments of the heat exchanger 36 in the embodiment as a skin liquefier 77 , In both embodiments, a refrigerant line 34 with a circular flow cross-sectional area 56 on the housing wall 17 arranged.

In 9 is about an outside 78 the refrigerant line 34 a heat conducting device 80 in the form of an aluminum band 82 guided. The aluminum band 82 is on its bottom 84 provided with an adhesive material, not shown, so that it is the refrigerant line 34 on the housing wall 17 attached. In addition to the heat delivery surface 54 in the contact area between the housing wall 17 and the wall 46 the refrigerant line 34 is now also possible via a contact between the aluminum band 82 with the wall 46 Heat both to the environment 38 as well as on the housing wall 17 be transmitted.

10 shows the refrigerant line 34 instead of the aluminum band 82 out 9 with a heat storage mass 86 , here bitumen 88 , is sheathed. The bitumen 88 takes heat away from the wall 46 and save them. If no refrigerant 32 more through the refrigerant line 34 flows, for example when the compressor 30 does not work, gives the bitumen 88 the stored heat to the environment 38 from.

Both the aluminum band 82 as well as the bitumen 88 act as a magnification device 62 to increase the heat delivery area 54 ,

The embodiments shown improve the heat transfer and reduce the start-stop losses in refrigerators 10 with a small mass flow, ie with compressor 30 with a small displacement, in particular with compressors 30 that are small and whose speed is variable.

As a heat exchanger 36 without forced ventilation, static condenser 24 called today, usually Blechwandverflüssiger 40 or wire tube liquefier 42 used. In both cases, for cost reasons, regardless of the compressor capacity and mass flow, a steel tube of 4.76 mm outside diameter and 3.3 mm inside diameter is usually used. With the wire tube liquefier 42 become the wires 52 on the pipe of the refrigerant pipe 34 welded, which is why a sufficient wall thickness of the tube is beneficial. There are special forms of the wire tube liquefier 42 that do without welding.

Through the wires 52 and the sheet metal wall 44 is the heat output from the outside of the refrigerant pipe 34 to the environment 38 improved.

The aim is to be an efficient heat exchanger 36 especially to propose for small mass flows. As the efficiency of refrigeration equipment progresses 10 For regular operation less and less power is required, and the mass flow is further reduced. The geometry of the pipes of the condenser 24 however, have not yet been adjusted for cost reasons. With sufficiently large mass flows and associated sufficiently high flow velocities, the internal heat transfer of refrigerant 32 effort 46 so large that it is in the area of external heat transfer from wall 46 on heat transfer device 48 or environment 38 only little influence on the transfer capacity of the condenser 24 Has. However, a too low mass flow, as occurs at low compressor performance, deteriorates the heat transfer on the inside by reducing the flow rates, so there is potential for optimization.

Especially for devices with start-stop operation, especially in refrigerators, the associated losses play a crucial role. At the start of the compressor 30 is at the condenser outlet after some time liquid refrigerant 32 to disposal. This delay, which results in a loss of efficiency, is dependent on the compressor power or the mass flow and the volume of the condenser 24 , A small internal volume results in less start-up losses.

When switching off the compressor 30 without a stop valve, this occurs in the condenser 24 still existing liquid refrigerant 32 in the evaporator 28 over and takes the heat with in the evaporator 28 , These shutdown losses also decrease with smaller internal volume of the condenser 24 ,

Investigations have shown that for small refrigerators a condenser 24 with 4 mm tube despite smaller outer surface leads to better efficiency of the device, with the more favorable flow in a tube of smaller cross-section, as in 5 shown has a significant share.

Another possibility is a subsequent flat pressing of the finished Drahtrohrverflüssigers 42 , A high machine outlay due to the high force required, associated tooling costs due to the difficulty of the flat pressing of individual samples, the mechanical loading of the welding points and thus the tightness problem stand for a mass flow adaptable final geometry, a short processing time and the fact that it is at the refrigerant line used 34 is an available purchased part.

In a second option, a flexible core, for example made of a refrigerant-resistant plastic, is subsequently added to the refrigerant line 34 threaded. Despite the fact that an additional part is necessary and a complicated threading slightly increases the production costs, here a simple prototype construction is possible, no tools are needed and the embodiment is quickly implemented.

In a third possibility, both on a plate wall plasticizer 40 can also be applied to a free-hanging skin condenser, the pipes are made with aluminum tape 82 or similar to ToS bonded with butyl and / or have an additional bitumen layer. Here, the diameter of the pipe of the refrigerant pipe 34 be arbitrary and it is a simple prototype construction possible, in contrast, there is a high production cost through the tools used and the life of the adhesive bond.

By the embodiments shown is an energy savings by lowering the condenser pressure and thus a colder condenser 24 through better internal heat transfer at the condenser 24 possible. All of these are cost-effective, easily implementable measures, in particular the insertion of a flexible core is cost-effective. Because here no design change is necessary and there are no tooling costs.

In a large pipe of the refrigerant pipe 34 A large amount of refrigerant is necessary to avoid unfavorable flow patterns. Smaller tubes, on the other hand, offer low flow rates for small quantities of refrigerant. Alternatively, a flattened tube may be used or a flexible core inserted into the large tube to produce favorable flow shapes.

LIST OF REFERENCE NUMBERS

10

 The refrigerator

12

 refrigerated compartment

14

 freezer

16

 casing

17

 housing wall

18

 door

20

 inner space

22

 Refrigerant circulation

24

 condenser

26

 throttle

28

 Evaporator

30

 compressor

32

 refrigerant

34

 Refrigerant line

36

 heat exchangers

38

 Surroundings

40

 Blechwandverflüssiger

42

 wire tube

44

 sheet metal wall

46

 wall

48

 Heat transfer device

50

 snakes

52

 wires

54

 Heat transfer surface

56

 Flow area

58

 lower area

59

 Movie

60

 flattening

64

 press tool

66

 recess

68

 press die

69

 enlarger

70

 reduction means

71

 reduction element

72

 Interior

74

 flexible element

76

 scope

77

 Skinverflüssiger

78

 outside

80

 heat conducting

82

 Aluminum tape

84

 bottom

86

 Heat storage mass

88

 bitumen

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• WO 2007/124705 A1 [0003]
• EP 1460357 B1 [0003]

Claims (15)

Heat exchanger ( 36 ) for a refrigeration appliance ( 10 ), in particular for a household refrigerating appliance, with a refrigerant line ( 34 ), which in use of a refrigerant ( 32 ) flow cross-sectional area ( 56 ), and a constriction for reducing the flow cross-sectional area ( 56 ) having. Heat exchanger ( 36 ) according to claim 1, characterized in that inside the refrigerant line ( 34 ) a reduction device ( 70 ) for reducing the flow cross-sectional area ( 56 ) is arranged. Heat exchanger ( 36 ) according to one of claims 1 or 2, characterized in that the reduction device ( 70 ) to be flushed with the refrigerant ( 32 ) is arranged. Heat exchanger ( 36 ) according to one of the preceding claims, characterized in that the reduction device ( 70 ) a flexible element ( 74 ) with the same cross-sectional shape as the refrigerant line ( 34 ) having. Heat exchanger ( 36 ) according to one of the preceding claims, characterized in that on the refrigerant line ( 34 ) a tube with a small flow cross-sectional area ( 56 ), in particular smaller than 8,54 mm ² , is arranged. Heat exchanger ( 36 ) according to claim 5, characterized in that the flow cross-sectional area ( 56 ) Is 20% smaller than 8,54 mm ² , in particular 40% smaller than 8,54 mm ² . Heat exchanger ( 36 ) according to one of the preceding claims, characterized in that the refrigerant line ( 34 ) a flattening ( 60 ) having. Heat exchanger ( 36 ) according to one of the preceding claims, characterized in that the refrigerant line ( 34 ) has an elliptical cross-sectional shape. Heat exchanger ( 36 ) according to one of the preceding claims, characterized by a magnification device ( 69 ) for enlarging a heat release surface ( 54 ) between refrigerant line ( 34 ) and a heat transfer device ( 48 ) for transferring heat from the refrigerant line ( 34 ) to an environment ( 38 ). Heat exchanger ( 36 ) according to claim 6, characterized in that the magnification device ( 69 ) a heat storage mass ( 86 ), in particular formed from bitumen ( 88 ), and / or that the magnification device ( 69 ) a heat conducting device ( 80 ), in particular a metal strip, more particularly an aluminum strip ( 82 ). Method for producing a heat exchanger ( 36 ) with the steps a) providing a refrigerant line ( 34 ) with a flow cross-sectional area ( 56 ); b) Reduction of the flow cross-sectional area ( 56 ). A method according to claim 11, characterized in that step b) comprises at least one of the following steps: b1) flattening the refrigerant line ( 34 ); and / or b2) inserting a reduction element ( 71 ) into an interior ( 72 ) of the refrigerant line ( 34 ); Method according to one of claims 11 or 12, characterized by the step c) fixing the refrigerant line ( 34 ) at a heat transfer device ( 48 ) or on a housing wall ( 17 ) of the refrigeration device ( 10 ). Method according to one of claims 11 to 13, characterized by the step d) sheathing the refrigerant line ( 34 ) with a heat conducting device ( 80 ) and / or a heat storage mass ( 86 ). Refrigeration appliance ( 10 ), in particular household refrigerating appliance, comprising a housing ( 16 ) with at least one interior ( 20 ), and one for cooling the at least one interior space ( 20 ) formed refrigerant circuit ( 22 ), wherein the refrigerant circuit ( 22 ) comprises at least one of the following elements: - liquefier ( 24 ), - Throttle ( 26 ), - Evaporator ( 28 ), and - compressors ( 30 ), characterized in that the liquefier ( 24 ) and / or the evaporator ( 28 ) as a heat exchanger ( 36 ) according to one of claims 1 to 10 and / or can be produced by a method according to one of claims 11 to 14.

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