EP1770345B1 - Heat exchange network and heat exchanger using same - Google Patents

Description

The invention relates to a heat exchanger network of the type specified in the preamble of claim 1 and a heat exchanger equipped therewith.

With heat exchanger networks of this type produced heat exchangers are z. B. needed in compressed air systems to that produced by a compressor and under a pressure of z. B. 25 bar standing compressed air to remove the moisture to make them critical applications such. B. in the food and paper industry or in the medical field to make suitable. The air drying takes place in that the heated air coming from the compressor is passed after passage through an aftercooler through a device containing an air / air and a refrigerant / air heat exchanger.

While the air / air heat exchanger is usually made in the manner of a plate heat exchanger of conventional construction, the refrigerant / air heat exchanger z. Example, from a combined pipe / plate heat exchanger with a network, which has formed from plates and these spaced-apart strips air passages and intermediate refrigerant passages. These consist z. B. arranged between each two plates, round or square cross-sections having tubes, the straight sections and these serpentine or meandering have connecting deflecting sections ( EP 0 521 298 A2 ). A disadvantage of this construction is that between the individual pipe sections unused spaces arise and the curved deflection sections are usually outside of the space occupied by the actual network and are not involved in the heat exchange.

In addition, has already been proposed (also EP 0 521 298 A2 ) to replace the flow-through of the refrigerant passages through the network produced by conventional plate-type pipe and deflection sections by these are limited by conventional, arranged between the plates partitions in the form of strips. The disadvantage here, however, that either comparatively thick bars must be provided in order to create the soldering surfaces sufficiently large for solder joints, whereby for given overall dimensions of the network reduced flow cross sections are obtained, or although narrow strips can be used, which allow favorable flow cross sections, but comparatively small, for the required strength of the heat exchanger not always sufficient soldering surfaces must be taken into account.

The last-mentioned problems can largely be avoided in that the dividing walls are formed by the webs and / or flanges of profiles arranged between the plates with I- and / or U-shaped cross sections ( EP 1 304 536 A2 ). If the flow channels are produced according to a first variant by means of a plurality of I-profiles, which are connected to the plates by soldering, then these profiles od before the soldering at least two points by laser welding. Like, are connected to the plates, to exclude relative position changes between the plates and the profiles during the dipping and tilting processes required during the soldering process. If, however, the flow channels are formed according to a second variant as U-shaped grooves in solid, plane-parallel plates, these and the deflection zones must be produced by milling, in particular track milling. Both variants cause comparatively high production costs, which are not always sustainable.

Devices according to the preamble of claim 1 were already in the documents WO 03/071213 A and JP 2004 150760 A disclosed.

In contrast, the invention, the technical problem underlying the heat exchanger network of the type described above in such a way that it can be produced using cost-effective manufacturing process with the required strength, is problematic in soldering technology and yet allows for given overall dimensions comparatively large flow cross sections for the refrigerant.

To solve this problem serve the characterizing features of claim 1.

By the use according to the invention of lamellae, which each form a plurality of flow channels, the number of welding operations to be carried out before the soldering operation can be considerably reduced. In addition, the slats can be produced by extrusion or milling and thereby cost-effectively with any strength. Finally, the dividing walls and / or the limited of these flow channels in principle any cross-sectional shape can be given, which is favorable in view of the desired performance in individual cases and stability of the heat exchange network.

Further advantageous features of the invention will become apparent from the dependent claims,

• Fig. 1 eine schematische Vorderansicht eines kombinierten Kältemittel/Luft- und Luft/Luft-Wärmeaustauscherblocks für Kältetrockner an Druckluftanlagen;
• Fig. 2 und 3 Schnitte längs der Linien II-II und III-III der Fig. 1;
• Fig. 4 eine vergrößerte Draufsicht auf eine erfindungsgemäße Lamelle zur Herstellung von Kältemittel-Durchgängen in einem für den Kältemittel/Luft-Wärmeaustausch bestimmten Netz des Blocks nach Fig. 1;
• Fig. 5 bis 7 Schnitte längs der Linien V-V bis VII-VII der Fig. 4;
• Fig. 8 eine vergrößerte Vorderansicht auf einen Ausschnitt eines Kältemittel-Durchgangs in einem für den Kältemittel/Luft-Wärmeaustausch bestimmten Netz des Blocks nach Fig. 1 bei Anwendung der Lamellen nach Fig. 4 bis 7;
• Fig. 9 eine Draufsicht auf den Kältemittel-Durchgang nach Fig. 8 bei Weglassung einer oberen Platte;
• Fig. 10 eine vergrößerte Vorderansicht des für den Kältemittel/Luft-Wärmeaustausch bestimmten Netzes des Blocks nach Fig. 1, hergestellt mit Lamellen nach Fig. 4 bis 7;
• Fig. 11 einen Schnitt längs der Linie XI-XI der Fig. 10;
• Fig. 12 und 13 den Fig. 10 und 11 entsprechende Ansichten eines zweiten, nicht beanspruchten Ausführungsbeispiels des Netzes;
• Fig. 14 bis 17 den Fig. 4 bis 7 entsprechende Ansichten einer zweiten Ausführungsform der erfindungsgemäl3e.n Lamelle;
• Fig. 18 bis 21 den Fig. 4 bis 7 entsprechende Ansichten einer dritten Ausführungsform der erfindungsgemäßen Lamelle; und
• Fig. 22 eine der Fig. 8 entsprechende Vorderansicht eines Kältemittel-Durchgangs bei Anwendung der Lamellen nach Fig. 14 bis 21.

The invention will be explained in more detail below in conjunction with the accompanying drawings with reference to embodiments. Show it:

• Fig. 1 a schematic front view of a combined refrigerant / air and air / air heat exchanger block for refrigeration dryer in compressed air systems;
• FIGS. 2 and 3 Sections along the lines II-II and III-III of Fig. 1 ;
• Fig. 4 an enlarged plan view of a blade according to the invention for the production of refrigerant passages in a for the refrigerant / air heat exchange certain network of the block Fig. 1 ;
• Fig. 5 to 7 Sections along the lines VV to VII-VII of Fig. 4 ;
• Fig. 8 an enlarged front view of a section of a refrigerant passage in a designated for the refrigerant / air heat exchange network of the block after Fig. 1 when using the slats after Fig. 4 to 7 ;
• Fig. 9 a plan view of the refrigerant passage after Fig. 8 omitting an upper plate;
• Fig. 10 an enlarged front view of the determined for the refrigerant / air heat exchange network of the block after Fig. 1 , made with slats after Fig. 4 to 7 ;
• Fig. 11 a section along the line XI-XI the Fig. 10 ;
• FIGS. 12 and 13 the 10 and 11 corresponding views of a second, not claimed embodiment of the network;
• FIGS. 14 to 17 the Fig. 4 to 7 corresponding views of a second embodiment of the inventive slat;
• Fig. 18 to 21 the Fig. 4 to 7 corresponding views of a third embodiment of the blade according to the invention; and
• Fig. 22 one of the Fig. 8 Corresponding front view of a refrigerant passage when using the slats after Fig. 14 to 21 ,

A heat exchanger device for refrigeration dryer in compressed air systems contains after Fig. 1 to 3 in the right section a refrigerant / air heat exchanger and in the left section an air / air heat exchanger. There are only one refrigerant / air heat exchanger network 1 and an adjacent air / air heat exchange network 2, both of which are arranged side by side in an assumed longitudinal direction and combined to form an integral structural unit and form a single, continuous block 3. Alternatively, it would of course also be possible to produce and operate both networks 1 and 2 as separate units.

The two nets 1 and 2 are mainly formed by plane-parallel, rectangular or square plates or dividers 4, which are extending over the entire width and length of the block 3. According to Fig. 1 and 3 is a part of the plates 4 on the one hand by perpendicular to the longitudinal direction strips 5, the in Fig. 3 left ends of the block 3 are arranged, and on the other hand by longitudinally extending, arranged on the side edges of the plates 4 strips 6, 7 held in pairs at a distance. This creates between these plates 4 passes 8. Am in Fig. 3 left end, the upper strips 6 are slightly shorter, so that between their left ends and the strips 5 respectively gaps 9 arise, can enter laterally through the air in the direction of a dashed arrow 10. At the in Fig. 3 on the other hand, the air can escape laterally parallel to the longitudinal direction of the passages 8 and in the direction of an arrow 11 drawn on the right. In the passages 8, moreover, it is usual to insert usual slats 12, which are in Fig. 1 are only partially shown and their passages accordingly Fig. 3 along lines 14 are deflected by 90 °.

The other part of the plates 4 is according to Fig. 1 and 2 in which the net 2 forming portion by parallel to the longitudinal direction, arranged on the side edges of the plates 4 strips 15 and 16 and transverse thereto, the left and right end of the network 2 forming end strips 17 and 18 are kept in pairs at a distance. This results in between each two plates 4 each a further passage 19. On the sides of in Fig. 2 Right end strips 18 are in Fig. 2 Upper strips 15 slightly shorter, so that between them and the end strips 18 each gaps 20 arise, by the air laterally in the direction of an arrow 21 shown. Fig. 2 ) can be supplied. By contrast, on the in Fig. 2 left side the strips 16 a little shorter, so that between them and the end strips 17 gaps 22 arise through which the air supplied at 20 can be removed again (arrow 23). The deflections are carried out analogously to Fig. 3 preferably with correspondingly formed, provided in the passages 19 fins ( Fig. 1 ).

In the network 1, the same plates 4 delimiting the passages 19 serve to form serpentine passages 24 (FIG. Fig. 1 ), which have straight and the deflection serving sections, as explained in more detail below. The passages 24 each extend from the end strips 18 to a end strip or plate 25, the Fig. 1 and 2 is arranged at the right end of the block 3. In this case, preferably plates 4 alternate with the passages 8 and plates 4 with the passages 19, 24 in superimposed planes, wherein at least one passage 8, 19, 24 is present in each plane. According to Fig. 2 the passage 24 is supplied at a direction indicated by an arrow 26 a refrigerant inlet, which can flow out at an indicated by an arrow 27 output again and flows through a refrigerant circuit, not shown.

The marked by the arrows 10, 11, 21, 23, 26 and 27 inputs and outputs od with known, not shown inlet nipples, collection boxes od. Like. Connected.

The operation of the described heat exchanger device is essentially as follows:

Coming from a compressed air system, on z. B. about 35 to 55 ° C heated compressed air is supplied in the direction of arrow 10 so that it flows through the passages 8. In this case, the air is first in the network 2 by the counter-current in the direction of arrow 21 supplied, coming from a water trap, not shown cold air to a temperature of z. B. 20 ° C cooled. On its way through the passages 8, the compressed air is then gradually in the network. 1 Cooled to its dew point, since it interacts here with the refrigerant, which in the direction of arrow 26 (FIG. Fig. 2 ) flows into the passages 24. The compressed air is then at the by the arrow 11 ( Fig. 3 ) marked output and taken to a water separator, not shown, from where it is introduced at the arrow 21 in the network 2 and this is taken at the indicated by the arrow 23 output, which serves as a tap for the compressed air. In this case, the arrangement is chosen so that the air at the tapping point is heated again approximately at room temperature.

Heat exchangers of the type described and their mode of action are generally known to the person skilled in the art ( EP 0 521 298 A2 . EP 1 304 536 A2 ) and therefore need not be explained in detail.

The inventive design of a refrigerant passage 24 of the network 1 will be described below with reference to Fig. 4 to 9 for convenience of description, the terms "right", "left", "from", "rear", "top" and "bottom" are selected according to the particular situation resulting from the specific illustration in FIG Fig. 4 to 9 results. Thereafter, the passage 24 through a plurality of parallel juxtaposed slats 31 (FIG. Fig. 4 to 7 ) educated. Each blade 31 has according to 6 and 7 a meandering cross-section and a plurality, in the exemplary embodiment, five partition walls 32. Like also in 6 and 7 is shown, the partitions 32 are vertically, parallel to each other and arranged at equal distances from each other and alternately top and bottom by horizontal, upper and lower webs 33, 34 connected to each other, as is typical for meanders. Because of the presence of five partitions 32, two upper and two lower webs 33, 34 are provided, so that each two adjacent partitions 32 and a connecting web 33 or 34 define a flow channel 35 and a total of four such flow channels 35 per blade 31 are present. In this case, the arrangement is preferably made such that each flow channel 35 has the same flow cross-section. At the lateral ends of the blade 31 is bounded by one of the partitions 32.

The lamellae 31 are preferably produced by extrusion of aluminum or an aluminum alloy and subsequent cutting to the desired length in the individual case. Therefore, their partitions 32 are initially of equal length and each with a front and rear end and a front or rear end face 32 a, 32 b ( Fig. 5 ) Mistake. After cutting to length, however, the dividing walls 32 are provided with a recess 36 at one or the other end 32a, 32b. As in Fig. 5 is indicated by dashed lines, for this purpose z. B. od the last, at the end 32a, 32b adjacent portion of the partition 32 by milling od. Like. Removes, whereupon for grinding the ridges od a cleaning operation with a steel brush. Like. Can connect. In particular Fig. 4 shows, the recesses 36 are mounted alternately at successive dividing walls 32 at one or the other end 32a, 32b, so come in the embodiment at the front end of the blade 31 three and at the rear end of the blade 31 two such recesses 36 come to rest.

8 and 8 show a prepared by the application of the blades 31 and arranged in a plane refrigerant passage 24. In addition, in 10 and 11 in each case the complete, the network 1 containing portion of the heat exchanger device shown enlarged. For the preparation of the passage 24 after 8 and 9 a first louver 31a is arranged parallel to and at a distance corresponding to the width of a flow channel 35 from the end strip 18. In this case, the position of the blade 31a is selected so that an outer, leftmost partition wall 32a arranged parallel to the bar 18 and its recess 36 on the in Fig. 9 not shown, the rear end of the blade 31a is provided. This is z. B. the in 6 and 7 shown blade 31 is used, but after rotation about an in Fig. 4 axis perpendicular to the plane of the drawing by 180 °. To the partition 32a, which like the other partitions 32 in Fig. 9 indicated by dashed lines, close as Fig. 8 shows, according to the meandering shape, three central partitions 32b, 32c and 32d and a further outer partition wall 32e, which in FIG 8 and 9 comes to the far right. Because of the basis of the Fig. 4 to 7 described arrangement of the recesses 36 are doing the two recesses 36 of the partitions 32b, 32d from and three in Fig. 9 invisible recesses 36 of the partitions 32a, 32c and 32e to lie behind. This is best off Fig. 11 recognizable.

The lamella 31a is closed in 8 and 9 a second blade 31b. This is identical to the blade 31 a formed, but compared to this in the 4 and 6 apparent location, so that in her three recesses 36 from and two more, in Fig. 9 invisible recesses 36 are behind. In addition, a leftmost partition wall 32f of the sipe 31b having a width corresponding to the width of a flow channel 35 is disposed away from and parallel to the partition wall 32e of the sipe 31a. That too is best Fig. 11 seen.

The alternately upwardly and downwardly open flow channels 35 (FIG. 6 and 7 ) according to Fig. 8 closed at the top or bottom by one of the plates 4, which are connected to the outer sides of the webs 33, 34 expediently by soldering. In contrast, the front and rear ends of the flow channels 35 are closed by individual profiles 37 having a width substantially equal to twice the distance of two partitions 32, with the front and rear ends of the fins 31 a and 31 b and the partitions 32 and with the Plates 4 are preferably connected gas-tight by welding (MIG or TIG) and for weight and cost reduction z. B. from Fig. 9 apparent, have trapezoidal cross-sections. Similarly, the front and rear and upper and lower portions of flow channels 38, 38 a, 38 b sealed between the blade 31 a and the end strip 18, between the blades 31 a and 31 b (eg. Fig. 8 ) and on the other side of the net 1 between the last lamella 31 and the end strip 25 (FIG. 10 and 11 ) are formed, wherein the two flow channels 38 and 38b accordingly Fig. 11 z. B. remain open at the front, there to the refrigerant in the direction of arrows 26, 27 and to be able to discharge.

The application of individual profiles 37 is always preferred over the application of continuous plates, despite the associated workload, when it is necessary to compensate for tolerances and leakage currents of the refrigerant or consequent short circuits between the individual flow channels 35 in Fig. 11 safe from left to right. In an alternative not claimed, but instead of the profiles 37, plates 39 (FIG. FIGS. 12 and 13 ) are used, which extend virtually over the entire width and height of the network 1 and seal all existing flow channels 24 at the same time.

The described recesses 36 form after the completion of the refrigerant passages 24 (FIG. Fig. 11 and 13 ) each one alternately from or behind lying deflection zone, which is bounded by the respective plates 4, profiles 37 (or plate 39) and partitions 32. This allows the chiller according to Fig. 11 and 13 z. B. in the direction of arrow 26 in the associated flow channel 38, at its rear end by the associated recess 36 in the partition wall 32a in the adjacent, formed between the partitions 32a, 32b flow channel 35 and this flow from behind to from to then to flow through the front recess 36 in the partition wall 32b in the flow channel 35 formed between this and the partition wall 32c, etc., until it finally out of the in Fig. 11 and 13 flows out the rightmost flow channel 38b in the direction of arrow 27 again. The refrigerant therefore flows along a serpentine, in Fig. 11 and 13 partially marked by arrows flow path through the passage 24th

Above and below the in Fig. 8 represented passage 24 may further, corresponding passages 24 are present and separated by air passages from each other, in particular Fig. 1 to 3 and 10 . 12 make clear. In this case, the profiles 37 and plates 39 suitably extend over the entire height of the heat exchange network.

The number of flow channels 35 and 38, from which the refrigerant passages 24 may be selected depending on the requirements of the case. Instead of the four flow channels 35 after 6 and 7 can also be more or less flow channels 35 per blade 31 may be present. In an even number of partitions 32 per blade 31, these can be laid in particular with the same orientation, since in this case the recesses 36 of the first partition wall 32 is always z. B. from and the recesses 36 of the last partition wall 32 always z. B. come to lie behind. Combinations with different numbers of dividing walls 32 and flow channels 35 are also possible, whereby adjacent fins 31 can also be arranged directly next to each other, in which case the flow channels 38 located between them would be missing. In this case, slats 31 with a smaller number of partitions 32 have the advantage that they are only slightly curved during extrusion because of the more uniform flow of material and therefore can be straightened during the successful before soldering setting the heat exchanger network 1. In contrast, would have provided with a much larger number of partitions 32 slats 31 before setting the network 1 by means of additional devices such. B. rollers od. Like. Be straightened.

The assembly of the heat exchanger block 3 after Fig. 1 takes place in a customary in heat exchangers by z. B. first, the plates 4 and fins 31 connected by soldering and then the profiles 37 (or plates 39) are fixed by welding to the plates 4 and fins 31. This results in the advantage that the blades 31 must be connected before soldering to secure the position only at two points, each with an associated plate 4 by welding, while using individual profiles as partitions (in the embodiment, five individual profiles per blade) each 10th Welding operations were required.

FIGS. 14 to 17 show a second embodiment of the blade 31 according to the invention, in contrast to the blade 31 after 6 and 7 not only has an even number of partitions 32, but also terminates on one side with a foot or land 34a instead of a dividing wall 32. This web 34a protrudes from one associated, end-side partition wall 32 to the outside, such as FIGS. 16 and 17 clearly show. This makes it possible to use two or more such blades 31 analogously Fig. 8 to arrange so immediately adjacent to each other, that in each case an end-side partition wall 32 of a blade 31 abuts an end-side web 34 a of the other blade 31. The web 34a specifies the distance of two adjacent blades 31. As a result, the advantage is achieved that when setting the network 2 does not need to pay attention to whether the blades 31 have the correct distances from each other, as in Fig. 8 for the adjacent to the flow channel 38a lamella 31 applies. In a corresponding manner, the web 34a z. In Fig. 11 are applied with impact to the rightmost terminal block 25 to the flow channel 38 b ( Fig. 11 ) to build.

So that it is also possible, the slats 31 with impact on the in Fig. 11 In the leftmost end strip 18 to create, is preferably according to a third embodiment of the invention additionally a blade 31 according to Fig. 18 to 21 provided, which ends on both sides with a respective foot or web 34b, 34c, which projects from an associated, end-side partition 32 to the outside, in particular FIGS. 20 and 21 demonstrate. A web (eg 34b) is expediently arranged at the top and the other web (eg 34c) at the bottom. As a result, when setting a passage 24 ( Fig. 11 ) z. B. with a blade 31 after Fig. 20 are begun, the web 34 b is placed against the respective end strip 18, as in Fig. 22 for a louver 31c to form the flow channel 38. At this lamella then closes in Fig. 22 slat denoted by reference numeral 31d Fig. 16 on, so that a leftmost partition wall 32g abuts from this to the web 34c. At this lamella 31 then further fins 31 can after Fig. 16 connect until the end bar 25 ( Fig. 11 ), at which the web 34a is abutted, whereby the flow channel 38b (FIG. Fig. 11 ) is formed. In this way, the entire network 2 can be set without a distance between two slats 31 erroneously too large or too small fails.

The invention is not limited to the described embodiments, which could be modified in many ways. This applies z. B. for the specific cross sections of the fins 31, the corresponding Fig. 8 may be provided on the outer sides of the webs 33, 34 with lateral spacers 40 in order to obtain larger solder surfaces, without thereby substantially reduce the flow cross-sections. In addition, the webs 33 and 34 and / or the spacers 40 could be slightly convex curved to obtain a desired to improve the soldering crown. Next, although the lamellae 31 and profiles 37 (or plates 39) z. As aluminum and the plates 4 made of clad aluminum, but it is clear that, depending on requirements, other commonly used for the production of Wärmeaustauschern networks materials can be used. In this case, the production of the lamellae 31 as described by extrusion, but also in other ways, in particular by the fact that a plate by milling od. Like. Is provided with the flow channels 35. Furthermore, it is in principle immaterial whether the networks 1 and 2 form an integral component by means of the continuous plates 4, manufactured separately and then assembled into an integral component or find application as separate components that are used independently or by appropriate lines with each other get connected. The nets 1, 2 can also be arranged one above the other instead of side by side. In addition, it is of course possible to apply the inventive heat exchange nets 1 for purposes other than those described and wherever refrigerant passages are needed. Finally, it is understood that the various features may be provided in combinations other than those described and illustrated.

Claims (15)

1. Heat exchanger network with at least two plates (4) and with a refrigerant passage (24) arranged between these and having a plurality of parallel flow ducts (35), the flow ducts (35) being formed in at least one fin (31) which has a meander-shaped cross section and which has partitions (32) arranged perpendicularly to the plates (4) and each having two ends (32a, 32b) and laterally delimiting the flow ducts (35), and webs (33, 34) connected to the partitions (32) and delimiting the flow ducts (35) alternately at the top and bottom, there being provided alternately at the one or the other ends (32a, 32b) of the partitions (32) recesses (36) which form deflection zones and by means of which the flow ducts (35) are connected to one another in a serpentine-like manner, characterized in that those ends of in each case two adjacent flow ducts (35) which are open at front and rear ends of the fin (4) and also a deflection zone assigned in each case to these are sealed off in each case by means of a profile (37) connected to an outside of the fin (31) and to the plates (4) by welding.
2. Heat exchanger network according to Claim 1, characterized in that the refrigerant passage (24) is composed of a plurality of fins (31) lying next to one another and having in each case a plurality of partitions (32).
3. Heat exchanger network according to Claim 2, characterized in that it has at least one fin (31) which terminates on at least one side with a web (34a) which projects outwards from an end-face partition (32).
4. Heat exchanger network according to Claim 2 or 3, characterized in that it has at least one fin (31) which terminates on each of the two sides with a web (33b, 34c) which projects outwards from an end-face partition (32).
5. Heat exchanger network according to Claim 4, characterized in that one web (for example, 33b) is connected at the top and another web (for example, 34c) is connected at the bottom to an associated partition (32).
6. Heat exchanger network according to one of Claims 1 to 5, characterized in that the fins (31) consist of extruded parts.
7. Heat exchanger network according to one of Claims 1 to 6, characterized in that the fins (31) consist of aluminium or of an aluminium alloy.
8. Heat exchanger network according to one of Claims 2 to 7, characterized in that the fins (31) lie next to one another with partitions (32) which face one another and which have a spacing from one another corresponding to the width of a flow duct (38a).
9. Heat exchanger network according to one of Claims 1 to 8, characterized in that the fins (31) and plates (4) are connected to one another by soldering.
10. Heat exchanger network according to one of Claims 1 to 9, characterized in that the recesses (36) are obtained by milling.
11. Heat exchanger network according to one of Claims 1 to 10, characterized in that it has a plurality of refrigerant passages (24) arranged one above the other and, between each of two refrigerant passages (24) lying directly one above the other, an air passage (8).
12. Heat exchanger network according to one of Claims 1 to 11, characterized in that it is designed as part of a combined refrigerant/air heat exchanger block (1).
13. Heat exchanger network according to Claim 12, characterized in that the plates (4) have in each case two portions, in each case the one portions forming a refrigerant/air heat exchanger network (1) and the other portions forming an air/air heat exchanger network (2).
14. Refrigerant/air heat exchanger, characterized in that it contains a heat exchanger network (1) according to at least one of Claims 1 to 13.
15. Heat exchanger according to Claim 14, characterized in that it is designed as a combined refrigerant/air and air/air heat exchanger.

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