DE10312780A1 - heat exchangers - Google Patents

Abstract

The invention relates to a heat exchanger, in particular an evaporator, in particular for a motor vehicle with a multi-flow and at least two-row flowable in flow channels evaporator block arranged outside of the flow channels, of air überströmbaren ribs and at least one collecting box, which communicates with the flow channels, longitudinally and has narrow sides and openings for the inlet and outlet of the refrigerant.

Description

The The invention relates to a heat exchanger, preferably an evaporator, especially for a Motor vehicle according to the preamble of claim 1.

Heat exchanger, such as evaporators, in particular for air conditioning systems of motor vehicles are known in various constructions, for. B. as an evaporator than Round tube evaporator, as a disk evaporator or as a flat tube evaporator. The round tubes, discs or flat tubes form flow channels for a refrigerant, z. B. R 134a, which evaporates in the flow through the evaporator becomes. On the outside the flow channels, d. H. between the panes or flat tubes are heat exchange surfaces in Form arranged for example by corrugated fins, which are covered by air. The air leads the refrigerant the heat required for evaporation. In a motor vehicle air conditioner is located on the refrigerant side before the evaporator, an expansion valve, which the refrigerant pressure reduced to the evaporation pressure. The expansion valve is over one Pressure and a suction line connected to the evaporator.

By the DE 198 14 050 a disc evaporator has been known in which the expansion valve via a suction and a pressure line and a clutch plate is connected directly to the evaporator and arranged on the narrow side thereof. Such a lateral arrangement is favorable for the Käl temittelführung in the evaporator, however, this solution requires the side of the evaporator considerable space that is not always available in the vehicle or in the air conditioning.

A similar solution, however, for a flat-tube evaporator was through the DE 198 26 881 known. This flat-tube evaporator has two rows of flat tubes that communicate with manifolds divided into longitudinal chambers. Suction and pressure line are laterally, ie connected to the narrow sides of the headers. The flat-tube evaporator is flowed through in 6 floods, ie it has two deflections in width on both the leeward and windward side (the side facing the air flow) and additionally a deflection in the depth, ie from leeward to windward. This results in a uniform temperature distribution on the air outlet side. However, this flat-tube evaporator has the already mentioned disadvantages of a lateral connection.

It was therefore by the applicant in DE-A 100 56 074 a so-called Longitudinal connection proposed, d. H. Suction pipe and pressure pipe are on the long side of a collecting box connected to a flat tube evaporator. This solution has the Advantage that claimed no space at the side of the evaporator is, and the expansion valve can directly in the air flow direction be arranged in front of the evaporator, optionally also directly over a Connection flange to be connected to the collection box. This too Flat-tube evaporator can be flowed through in 6 floods, d. H. he has each one three passes or passages on the lee and on the windward side. There is a double deflection at depth, d. H. on the one hand, a diversion from windward to lee and on the other hand from lee to windward.

On Problem with such evaporators is the uniform temperature distribution on the air outlet side - this is especially due to overheating of the refrigerant vapor at the end of the flow path due to the evaporator. Basically, the refrigerant retains from entering the evaporator the biggest part of the flow path the evaporation temperature at, d. H. an approximately constant temperature. For procedural reasons must the refrigerant but when exiting the evaporator, a predetermined overheating have that over the expansion valve is controlled. However, this overheating can already in the penultimate round (the penultimate passage) occur. A such overheating, d. H. one over the evaporation temperature lying temperature of the refrigerant Affects unfavorable to a uniform temperature distribution off, especially with smaller evaporators, which only have a 4-flow flow or block interconnection. In such a case, the overheating zone would on the air outlet area "penetrate" and the temperature distribution particularly unfavorable influence.

It Object of the present invention, a heat exchanger, in particular a Evaporator, the type mentioned above with respect to its connection options to improve and re his block interconnection to make more flexible, especially in With regard to an expansion valve position in front of the evaporator.

This The object is solved by the features of claim 1.

According to the invention, the inlet opening for the evaporator is arranged laterally, ie on the narrow side and the outlet opening on the longitudinal side of the evaporator. Advantageously, initially a small space requirement in the lateral direction, since the expansion valve can be arranged in front of the evaporator. In addition, there are advantageous Verschaltungsmöglichkeiten, ie both a 6-flow flow for larger and a 4-flow flow for smaller evaporator. Also at overheating will not adversely affect the temperature distribution on the air outlet side, since the last two passages of the refrigerant flow are arranged on the air inlet side (windward side) and thus there is no danger that the overheating will "break through" on the leeward side. ,

advantageous Embodiments of the invention will become apparent from the dependent claims. Of the inventive connection of suction and pressure line on the longitudinal and narrow side of the evaporator is due to the different evaporator designs like disc evaporator or flat tube evaporator applicable. Particularly advantageous is the inventive solution, however for one double-row flat-tube evaporator having collecting tanks with longitudinal chambers. there can the entrance opening in the front side of the leeward longitudinal chamber and the outlet opening the long side the windward longitudinal chamber be arranged and connected to the pressure or suction line. As already mentioned, is Not only a 6-flooded, but also a 4-flooded flow through the Vaporizer possible which in particular for small evaporator is advantageous. 6- or 4-flooded means that the evaporator in six or four passages (group of flow channels with same flow direction) flows through is, with between the individual passages deflections in width or lie in the depth. Double row means that the evaporator on the one hand flowing through on the leeward side and on the other side on the windward side, wherein two rows are also formed by a continuous flat tube can be. Preferably, the evaporator is first flowed through on the leeward, so in three or two passages and then on the windward or air intake side, from where the exhaust of the refrigerant vapor he follows.

In a further advantageous embodiment of the invention is - in the air flow direction seen - before the evaporator arranged an expansion valve and a Pressure and a suction line connected to the inlet or outlet port is. The suction tube is advantageously largely straight, d. H. without strong bends and short and therefore causes only minimal pressure losses. This comes the cooling capacity benefit of the evaporator.

embodiments The invention are illustrated in the drawings and will be described in more detail below. Show it

1 a flat tube evaporator with lateral and longitudinal connection in perspective view,

2 Representation of a 6-flow refrigerant flow of the evaporator according to 1 .

3 Representation of a 4-flow throughflow of an evaporator with a lateral and a longitudinal connection,

4 Representation of a 5-flow throughflow of an evaporator with a lateral and a longitudinal connection,

5 Representation of a 5-flow throughflow of an evaporator with a lateral and a longitudinal connection,

6 Representation of a 5-flow throughflow of an evaporator with a lateral and a longitudinal connection,

7 Representation of a 7-flow throughflow of an evaporator with a lateral and a longitudinal connection and

8th schematic representation of a heat exchanger.

1 shows a flat tube evaporator 1 in perspective view with two refrigerant connection pipes 2 . 3 that from the evaporator 1 to an expansion valve 4 lead, which is shown only schematically and in broken lines. The evaporator 1 is from an evaporator block 5 of pipes and ribs and two collecting boxes placed on top of this block 6 . 7 built up. Both collection boxes 6 . 7 each have two longitudinal chambers 6a . 6b such as 7a . 7b on. The evaporator block 5 consists of a variety of flow channels, such as flat tubes 8th , between which ribs, not shown, such as corrugated fins, are arranged, which are overflowed by air in the direction of flow shown by arrows L. The evaporator block 5 is laterally by side parts 9 completed, which form the one side, such as the narrow sides. The other sides, for example, the long side is with 10 denotes and corresponds to the air inlet side. The parts of the evaporator block 5 as well as the collection boxes 6 . 7 are preferably made of aluminum or of an aluminum alloy and are preferably soldered together, with the ends of the flat tubes 8th sealed or sealed in openings in the collecting tanks 6 . 7 are included.

The evaporator 1 is from a refrigerant, for. B. R 134 a flows through, which is the rear, ie leeward longitudinal chamber 6a through the pressure line 2 is supplied. Also, the refrigerant can be supplied to the windward side of the heat exchanger. Previously, the refrigerant is in the expansion valve 4 reduced to the evaporator pressure, ie the refrigerant enters as Kältemitttelnassdampf in the longitudinal chamber 6a on. After flowing through the evaporator - which is explained in more detail below - the Käl means via the suction line 3 aspirated. The expansion valve 4 So is in the air flow direction L before the evaporator 1 or the evaporator block 5 , However, this expansion valve may be arranged otherwise in other embodiments of the invention. The suction tube 3 is short and relatively straight, that is formed without strong bends, so that in this intake manifold 3 minimal pressure losses occur. The evaporator end of the suction tube 3 is in an exit opening 3a the front longitudinal chamber 6b soldered. The input-side pressure tube 2 by contrast, with its evaporator-side end into an inlet opening in the end face of the longitudinal chamber 6a soldered and leads over two to three pipe bends to the expansion valve 4 , The connection of the suction pipe 3 on the long side of the longitudinal chamber 6b is referred to as a so-called longitudinal connection and the connection of the pressure tube 2 on the narrow or front side of the longitudinal chamber 6a is referred to as a lateral connection.

2 shows the refrigerant side and air side flow through the flat tube evaporator 1 according to 1 , The same reference numerals as in FIG 1 used. This illustration of the evaporator 1 leaves in the rear longitudinal chamber 6a a first row 11 of pipe openings or pipe ends and in the front longitudinal chamber 6b a second row 12 recognize from pipe openings. Corresponding tube openings are in the two lower longitudinal chambers 7a . 7b intended. In these openings 11 . 12 open the flat tubes 8th , which either as two rows of flat tubes 8th or are formed as a series of continuous flat tubes with two flow directions. Preferably, the flat tubes 8th designed as multi-chamber tubes with a plurality of parallel flow channels. The flat tube evaporator 1 is traversed by the refrigerant in accordance with the dar made arrows from A to D 6-flow, ie there are in the back row 11 three passages A, B, C, each with two deflections between A and B and B and C in the width and three passages from D over E to F in the front row 12 , wherein the passage C is connected via a deflection in the depth C / D against the flow direction L of the air with the passage D. The deflections in the width are by two transverse partitions 13 . 14 in the rear longitudinal chamber 6a and in the front longitudinal chamber 6b as well as other partitions 15 . 16 in the lower longitudinal chambers 7a . 7b causes. The entry of the refrigerant takes place - as before for 1 executed - over the inlet opening 2a on the narrow side 9 of the evaporator 1 during the discharge of the refrigerant through the opening 3a on the long side 10 the evaporator takes place. As known in the art, the longitudinal chambers are 6a . 6b such as 7a . 7b through longitudinal partitions 6c . 7c separated from each other, the partition 7c in the area of the deflection C / D in depth bypass openings 7d having.

This refrigerant guide, also called block interconnection, leads to a uniform temperature distribution on the air outlet side 17 , As the entry of the refrigerant in the leeward pipe line 11 takes place, the refrigerant is still in the passages A, B, C in the wet steam region, ie the refrigerant points in the leeward pipe line 11 continuously an approximately constant temperature, namely the evaporation temperature. Only in the last passages E or F in the windward tube row 12 occurs overheating of the refrigerant and thus a rise in temperature. This increase in temperature of the refrigerant causes an asymmetry in the temperature distribution, but this is approximately compensated insofar as they are on the air inlet side 10 occurs and not on the air outlet side 17 by strikes.

3 shows a further embodiment of the invention, namely a flat tube evaporator 18 with a lateral refrigerant inlet 19 and a longitudinal connection 20 for the outlet or the suction of the refrigerant. The lateral inlet is arranged on a leeward side or on a leeward collecting tank of the evaporator, the outlet is arranged on the windward side of the evaporator or on a windward collecting box. In the embodiment of the invention, it is advantageous that the collection box areas 21a ' and 21b ' with the connections 19 . 20 are arranged adjacent to one side of the evaporator.

This evaporator 18 is basically the same as the previously described evaporator 1 constructed, but it is smaller in the longitudinal extent and is flowed through (only) 4-flow, ie in four passages I, II, III, IV, wherein after the passage II, a deflection in the depth II / III takes place against the air flow direction L.

The evaporator 18 has an upper header 21 with two longitudinal chambers 21a . 21b and two transverse partitions 22 . 23 on. These separate the collection chambers into four areas 21a ' . 21a '' . 21b ' and 21b ' ,

The partitions 22 and 23 are in the chambers 21a and 21b at the same height, viewed in the width of the evaporator perpendicular to the air flow direction, arranged. Due to the central arrangement of the partitions it follows that the floods I to IV are the same size. However, it may also be expedient that the partitions are not arranged at the same height and / or not centrally and thus the floods are different, ie have different numbers of flat tubes or flow paths.

A lower collection box 24 has two longitudinal chambers 24a . 24b on - without transverse partitions. Because of this education the collecting boxes 21 . 24 with partitions 22 . 23 as well as lateral connection 19 and longitudinal connection 20 results in the illustrated 4-flow flow. Again, the refrigerant is in the passages I, II on the leeward side of the evaporator 18 as wet steam with (constant) evaporation temperature, so that there is a uniform temperature distribution on the air outlet side. As mentioned, the refrigerant should be at the outlet 20 present as superheated steam at a predetermined superheat temperature; Therefore, in the last passage IV refrigerant with overheating temperature flows, possibly already in the penultimate passage III - but both are on the air inlet side. A blow through of the overheating on the air outlet side is not to get. This results in a uniform temperature distribution on the air outlet side - even for a small, four-flow evaporator.

4 shows a further embodiment of the invention, namely a flat tube evaporator 118 with a lateral refrigerant inlet 119 and a longitudinal connection 120 for the outlet or the suction of the refrigerant. This evaporator 118 is basically the same as the previously described evaporator 1 constructed, but it is greater in the longitudinal extent and flows through 5-flow, ie in five passages I, II, III, IV, V, wherein after the passage III, a deflection in the depth III / IV against the air flow direction L takes place. However, the deflection in depth can also take place in the air flow direction. This also applies generally to the other embodiments.

The evaporator 118 has an upper header 121 with two longitudinal chambers 121 . 121b and two transverse partitions 122 . 123 on. A lower collection box 124 has two longitudinal chambers 124a . 124b on with a transverse partition 150 , The partitions 122 . 150 on the leeward side are arranged offset with respect to the longitudinal extent of the evaporator to ensure the dreiflutige training. On the windward side is the partition 123 arranged centrally of the evaporator. As a result, two equally distributed floods are generated on the windward side.

Because of this education the collecting boxes 121 . 124 with partitions 122 . 123 . 150 as well as lateral connection 119 and longitudinal connection 120 results in the illustrated 5-flow flow. Again, depending on the operating conditions of the evaporator advantageously the refrigerant in the passages I, II and III on the leeward side of the evaporator 118 be present as wet steam with (constant) evaporation temperature, so that could result in a uniform temperature distribution on the air outlet side.

As mentioned, the refrigerant should be at the outlet 120 present as superheated steam at a predetermined superheat temperature; Therefore, in the last passage V refrigerant with superheat temperature flows, possibly already in the penultimate passage IV - but both are on the air inlet side. This results in a uniform temperature distribution on the air outlet side, even for a 5-flow evaporator.

Of the Evaporator is on the lee side and the windward side in different Divide areas as in different tides. These areas are on the leeward side and the windward side as shown not equal large. this leads to to that the Blockverschaltung is progressive, that is, that the first row of tubes, in the the refrigerant flows or is injected, divides into three areas or floods (I, II, III) while the second row of tubes from which the refrigerant is sucked off, itself only divided into two areas or floods (IV, V). This has the Advantage that that Gas can expand accordingly with increasing evaporation and the space required is provided.

at another embodiment The invention may be the block interconnection in a 5-flow evaporator also be degressive, that means that the first Pipe row in which the refrigerant flows or is injected, divides into two areas or floods (I, II) while the second row of tubes from which the refrigerant is sucked in three areas or floods (III, IV, V) divides.

In the embodiment of the 4 the inlet for the refrigerant is arranged on a lower longitudinal chamber and the outlet on an upper connection. Advantageously, however, the connections are arranged on the same side of the evaporator, viewed in the longitudinal direction. However, in another embodiment, the ports may also be arranged on opposite sides of the evaporator in the longitudinal direction.

5 shows a further embodiment of the invention, namely a flat tube evaporator 218 with a lateral refrigerant inlet 219 and a longitudinal connection 220 for the outlet or the suction of the refrigerant. This evaporator 218 is in principle the same as the previously described bene evaporator 118 constructed and flows through 5-flood, d: h. in five passages I, II, III, IV, V, wherein after the passage II, a deflection takes place in the depth II / III against the air flow direction L. However, the deflection in depth can also take place in the air flow direction. This also applies generally to the other embodiments. The evaporator 218 has an upper header 221 with two longitudinal chambers 221a . 221b and a transverse partition 222 on. A lower collection box 224 has two longitudinal chambers 224a . 224b on with two transverse partitions 150 . 151 , Because of this education the collecting boxes 221 . 224 with partitions 222 . 251 . 250 as well as lateral connection 219 and longitudinal connection 220 results in the illustrated 5-flow flow.

The partitions 222 . 251 on the windward side are offset with respect to the longitudinal extent of the evaporator to ensure the dreiflutige training. On the lee side is the partition 250 arranged centrally of the evaporator. As a result, two equally distributed floods are generated on the leeward side.

Again, can advantageously the refrigerant in the passages I and II on the leeward side of the evaporator 218 be present as wet steam with (constant) evaporation temperature, so that could result in a uniform temperature distribution on the air outlet side. As mentioned, the refrigerant should be at the outlet 220 present as superheated steam at a predetermined superheat temperature; Therefore, in the last passage V refrigerant with superheat temperature flows, possibly already in the penultimate passage IV - but both are on the air inlet side. This results in a uniform temperature distribution on the air outlet side, even for a 5-flow evaporator.

Of the Evaporator is on the lee side and the windward side in different Divide areas as in different tides. These areas are on the leeward side and the windward side as shown not equal large. this leads to to that the Block interconnection is degressive, that is, that the first row of tubes in the the refrigerant flows or is injected, divides into two areas or floods (I, II) while the second row of tubes from which the refrigerant is sucked off, itself divided into three areas or floods (III, IV, V).

In the embodiment of the 5 the inlet for the refrigerant is arranged on the leeward side at a lower longitudinal core and the outlet at an upper connection is windward. Advantageously, however, the connections are arranged on the same side of the evaporator, viewed in the longitudinal direction. However, in another embodiment, the ports may also be arranged on opposite sides of the evaporator in the longitudinal direction.

6 shows a further embodiment of the invention, namely a flat tube evaporator 318 with a lateral refrigerant inlet 319 and a longitudinal connection 320 for the outlet or the suction of the refrigerant. This evaporator 318 is basically the same as the previously described evaporator 118 constructed and flows through 5-flow, ie in five passages I, II, III, IV, V, wherein after the passage I a deflection in the depth I / II in the air flow direction L takes place and after the passage III a deflection in depth III / IV takes place against the direction of air flow.

The evaporator 318 has an upper header 321 with two longitudinal chambers 321a . 321b and three transverse partitions 360 . 361 . 362 on. A lower collection box 324 has two longitudinal chambers 324a . 324b on with a transverse partition 350 , Because of this education the collecting boxes 321 . 324 with partitions 350 . 360 . 361 . 362 as well as lateral connection 319 and longitudinal connection 320 This results in the illustrated 5-flow throughflow. Again, can advantageously the refrigerant in the passages II and III on the leeward side of the evaporator 218 be present as wet steam with (constant) evaporation temperature, so that could result in a uniform temperature distribution on the air outlet side. As mentioned, the refrigerant should be at the outlet 320 present as superheated steam at a predetermined superheat temperature; Therefore, in the last passage V refrigerant with superheat temperature flows, possibly already in the penultimate passage IV - but both are on the air inlet side. This results in a uniform temperature distribution on the air outlet side, even for a 5-flow evaporator.

The arrangement of the partitions 361 and 362 allows an exit 320 in the middle tide of the evaporator on the windward side. However, this requires the two deflections in the depth (A → B, C → D).

7 shows a further embodiment of the invention, namely a flat tube evaporator 418 with a lateral refrigerant inlet 419 and a longitudinal connection 420 for the outlet or the suction of the refrigerant. This evaporator 418 is basically the same as the previously described evaporator 1 However, it is larger in the longitudinal extent and flows through 7-flows, ie in seven passages I, II, III, IV, V, VI, VII, wherein after the passage IV a deflection in the depth IV / V against the air flow direction L takes place. However, the deflection in depth can also take place in the air flow direction. This also applies generally to the other embodiments. The evaporator 418 has an upper header 421 with two longitudinal chambers 421a . 421b and two transverse partitions 422 . 423 on. A lower collection box 424 has two longitudinal chambers 424a . 424b on with three transverse partitions 450 . 451 . 452 , Because of this training the Sam melkästen 421 . 424 with partitions 422 . 423 . 450 . 451 . 452 as well as lateral connection 419 and longitudinal connection 420 results in the illustrated 7-flow flow. Again, can advantageously the refrigerant in the passages I, II, III and IV on the leeward side of the evaporator 418 be present as wet steam with (constant) evaporation temperature, so that could result in a uniform temperature distribution on the air outlet side. As mentioned, the refrigerant should be at the outlet 420 present as superheated steam at a predetermined superheat temperature; Therefore, in the last passage VII refrigerant with superheat temperature flows, possibly already in the penultimate passage VI - but both are on the air inlet side. This results in a uniform temperature distribution on the air outlet side, even for a 7-flute evaporator.

at further embodiments can also Evaporators can be created with three or more than seven floods. In a three-flow evaporator injection over the entire Lee- or windward side done, in which case on the windward or Lee side is a two-way interconnection.

at an eight-flow embodiment can be an interconnection similar a six-flow interconnection can be realized, in which case per Windward and leeward four floods are realized.

The in the 1 to 7 Heat exchangers shown are preferably evaporators for use in air conditioning systems of a motor vehicle. These evaporators can be used in an air conditioner that provide the entire vehicle (front air conditioning) or as an evaporator for a rear air conditioning, see for example. 8th ,

In particular for one Rear air conditioning, but also for other air conditioners, it can be done according to one Another idea of the invention, regardless of the Anschlusspositon be advantageous if the evaporator is smaller in size is trained. Particularly advantageous is an education in the Dimensions length Length width B · Depth T in the range 60 mm <= L <= 180 mm; 60 mm <= B <= 180 mm; 20 mm <= T <= 80 mm.

A preferred embodiment is designed such that the Dimensions of the tube / fin block between the collection boxes almost has square dimensions, such as about 130 mm · approx. 120 mm. Near-square is understood to mean a geometry that has a relationship the side lengths from 0.7 to 1.3, preferably from 0.8 to 1.2, and more preferably from 0.9 to 1.1.

It may be advantageous that an even or odd number of tubes or flow channels is provided. It may also be expedient if, for example, the number of tubes per flood is equal or unequal. For example, in a 5- or 6-flow evaporator with a total of 11 pipes on the leeward or windward side, it may be expedient if there are two floods on the windward and / or leeward side 4 Tubes cover and a tide 3 Includes pipes, see 8th , There are two floods A, B equipped with four pipes and a flood with three pipes. Preferably, the flood is with more or less pipes, here with three pipes between or next to the floods with the same number of tubes, here with four pipes.

Claims (15)

Heat exchanger, such as evaporator, in particular for a motor vehicle with a multi-flow and single-row or at least two rows in flow channels through-flowable evaporator block arranged outside the flow channels, from air flowed over ribs and at least one collecting box, which communicates with the flow channels, longitudinal and narrow sides and Having openings for the inlet and outlet of the refrigerant, characterized in that an opening, preferably the opening for the inlet of the refrigerant on the narrow side and the other opening, preferably the opening for the exit of the refrigerant are arranged on the longitudinal side. heat exchangers according to claim 1, characterized in that the flow channels as slices a disc evaporator are formed. heat exchangers according to claim 1, characterized in that the flow channels as flat tubes a flat tube evaporator are formed. heat exchangers according to claim 3, characterized by a series of flat tubes, each of which can be flowed through in 2-flooded with a deflection in the depth. heat exchangers according to claim 3, characterized by two rows of flat tubes, each flow through 1-flood are. heat exchangers according to one of the claims 1 to 5, characterized in that the ribs as corrugated ribs are formed. Heat exchanger according to claim 3, 4, 5 or 6, characterized in that the collecting box ( 6 ) two longitudinal chambers ( 6a . 6b ), which with the flat tubes ( 8th ) communicate. Heat exchanger according to claim 7, characterized ge indicates that the inlet opening ( 2a ) at the leeward longitudinal chamber ( 6a ) and the exit opening ( 3a ) at the windward longitudinal chamber ( 6b ) are arranged. heat exchangers according to one of the claims 1 to 8, characterized by a 6-flow throughflow (A, B, C, D, E, F), each with two deflections in width on the lee side and the windward side as well as a deflection in the depth of the lee to the windward side. heat exchangers according to one of the claims 1 to 8, characterized by a 4-flow throughflow (I, II, III, IV), each with a deflection in the width on the lee side and the windward side and a diversion in depth from the leeward Windward side. heat exchangers according to one of the claims 1 to 8, characterized by a 5-flow throughflow (I, II, III, IV, V) with at least one deflection in the width the lee side and the windward side and at least one diversion in the Depth from the leeward side to the windward side. heat exchangers according to one of the claims 1 to 8, characterized by a 3-flow throughflow (I, II, III) with at least one deflection in width on the Leeward or the windward side and at least one diversion in the Depth from the leeward side to the windward side. heat exchangers according to one of the claims 1 to 8, characterized by a 7-flow or multi-flow with at least one diversion in width on the leeward side and the windward side and at least one diversion in depth from the leeward to the windward side. Heat exchanger according to one of the preceding claims, characterized in that in the air flow direction (L) in front of the evaporator ( 1 ) an expansion valve ( 4 ) is arranged, which via a pressure line ( 2 ) with the inlet opening ( 2a ) and via a suction line ( 3 ) with the outlet opening ( 3a ) connected is. heat exchangers according to claim 14, characterized in that the suction line in Essentially straight is formed.