EP2825832B1 - Heat exchanger - Google Patents

Description

Technical area

The invention relates to a heat exchanger according to the preamble of claim 1.

State of the art

In motor vehicles is a general trend to reduce fuel consumption. A not inconsiderable proportion of the energy content of the fuel is transmitted during combustion in the internal combustion engine in the hot exhaust, which often unused leaves the vehicle and thus a significant proportion of the energy content is not used.

To further reduce the fuel consumption of vehicles, such as in commercial vehicles or passenger cars, it is therefore expedient to recover part of the energy content of the hot exhaust gas for driving the motor vehicle again.

Various methods are currently being tested for this energy recovery. So there are approaches to recover the energy content electrically by means of thermocouples. However, this is currently still low Limited services, so that only about 1 kW in passenger cars is achieved.

This recovery can be thermal, i. the energy of the exhaust gas is used to heat the passenger compartment or to heat the engine and / or transmission.

In a variant that has been discussed for some time now, although thermal energy is also extracted from the exhaust gas, the energy is returned to the engine in mechanical form. The method is based on a steam power process in which a particular suitable medium in an evaporator is vaporized and superheated and expanded in an expander or turbine to generate mechanical energy.

The evaporation of the medium takes place by means of a heating via the hot exhaust gas. To achieve the highest possible efficiency, it is expedient if the medium can be brought to a higher pressure. In the case of water as the medium, about 40-50 bar can be achieved. When using organic refrigerants pressures up to about 30 bar are advantageous.

The medium to be evaporated is heated in a so-called evaporator in a first step to boiling temperature, then evaporated and then superheated. This can happen in a vehicle in two different locations. First, in an evaporator used in place of or in addition to the exhaust gas cooler, heat may be extracted from the exhaust gas to vaporize the fluid to be evaporated. Second, the main exhaust gas flow can also be used as a heat source in order to evaporate a fluid in a so-called main exhaust gas evaporator.

From the air conditioning technology for vehicles are so-called disk evaporator according to the WO 2011/051163 A2 have become known in which ribs are soldered between disc pairs and in which a number of such pairs of discs are connected in parallel. In this case, a fluid flows through the pairs of discs and another fluid flows around them usually. In the discs then the fluid flowing through evaporates when the exhaust gas flows around the discs.

Disc and ribbed evaporators have a high power density, which makes it possible to provide even very compact high performance evaporators for vehicles. The disadvantage, however, is that such evaporators are relatively expensive to manufacture.

The US 1 799 471 A discloses a heat exchanger according to the preamble of claim 1.

Presentation of the invention, object, solution, advantages

It is the object of the invention to provide a heat exchanger, which is simple and yet inexpensive to manufacture compared to the prior art and has a good power density.

This object is achieved with the features of claim 1.

A preferred embodiment discloses a heat exchanger, such as in particular exhaust gas evaporator, with a housing having a fluid inlet and a fluid outlet for a first medium, such as in particular exhaust gas, arranged in the housing transversely to the flow direction of the first fluid tubes, which are flowed through by a second medium and inlet side and arranged on the outlet side in a tubesheet with their ends and are fluid-tightly connected to the respective tubesheet, respectively a structure by means of which groups of tubes are interconnected such that an outlet of at least one tube is fluidly connected to an inlet of at least one other tube , It is particularly advantageous if the respective outlet from a group of tubes is connected to a respective inlet of a group of tubes.

According to the invention, the structure consists of a baffle and a cover plate, wherein the baffle plate has openings which connects the outlets of a tube with the inlets of the other tubes, and wherein the cover plate covers the baffle fluid-tight. Thus, the baffle plate is connected to the tubesheet and has openings within which inlets and outlets of a predeterminable number of tubes are in fluid communication.

It when the baffle plate is placed on the respective tube sheet and connected thereto, wherein the cover plate is placed on the respective baffle plate and connected thereto is particularly advantageous.

It is also expedient if the baffle plate is integrally formed with the respective tubesheet, wherein the cover plate is placed on the respective baffle plate and connected thereto.

It is also advantageous in another embodiment, when the baffle plate is integrally formed with the respective cover plate, wherein the baffle plate and the cover plate are placed on the respective tube sheet and connected thereto.

It is particularly advantageous if the tubes are arranged in rows, wherein the deflecting plate deflects fluid between tubes of different rows. This means that the baffle deflects fluid from a first tube or from a group of first tubes into a second tube or into a group of second tubes, wherein the first tubes and the second tubes are preferably arranged in a different row of tubes.

It when the tubes are arranged in rows, wherein the baffle deflects fluid between tubes of a series is particularly advantageous. This means that the baffle deflects fluid from a first tube or from a group of first tubes into a second tube or into a group of second tubes, wherein the first tubes and the second tubes are preferably arranged in a same row of tubes.

It is also advantageous if the rows of tubes are arranged in segments, wherein the deflecting plate deflects fluid from one segment to another segment.

Furthermore, it is expedient if at least in one segment a plurality of tubes are connected in parallel.

It is also advantageous if at least in one segment, a plurality of parallel-connected tubes are connected in series with each other.

Further advantageous embodiments are described by the following description of the figures and by the subclaims.

Brief description of the drawings

Fig. 1

ein erstes Ausführungsbeispiel eines erfindungsgemäßen Wärmeübertragers in dreidimensionaler Ansicht,

Fig. 2

eine Ansicht des Wärmeübertragers von der Seite,

Fig. 3

eine Teilansicht eines Sammelbereichs,

Fig. 4

eine Teilansicht eines Sammelbereichs,

Fig. 5

eine Teilansicht eines Sammelbereichs,

Fig. 6

eine Ansicht des Wärmeübertragerkerns,

Fig. 7

eine Ansicht eines vorderen Umlenkbereichs des Wärmeübertragers,

Fig. 8

eine Ansicht eines hinteren Umlenkbereichs des Wärmeübertragers,

Fig. 9

ein weiteres Ausführungsbeispiel in einer Ansicht eines vorderen Umlenkbereichs,

Fig. 10

ein weiteres Ausführungsbeispiel in einer Ansicht eines vorderen Umlenkbereichs,

Fig. 11

ein weiteres Ausführungsbeispiel in einer Ansicht eines vorderen Umlenkbereichs, und

Fig. 12

ein weiteres Ausführungsbeispiel in einer Ansicht eines vorderen Umlenkbereichs.

The invention will be explained in more detail on the basis of at least one embodiment with reference to the drawings. Show it:

Fig. 1

a first embodiment of a heat exchanger according to the invention in three-dimensional view,

Fig. 2

a view of the heat exchanger from the side,

Fig. 3

a partial view of a collection area,

Fig. 4

a partial view of a collection area,

Fig. 5

a partial view of a collection area,

Fig. 6

a view of the heat transfer core,

Fig. 7

a view of a front deflection region of the heat exchanger,

Fig. 8

a view of a rear deflection region of the heat exchanger,

Fig. 9

a further embodiment in a view of a front deflection region,

Fig. 10

a further embodiment in a view of a front deflection region,

Fig. 11

a further embodiment in a view of a front deflection, and

Fig. 12

a further embodiment in a view of a front deflection.

Preferred embodiment of the invention

The FIGS. 1 and 2 show a heat exchanger 1, which in the embodiment of FIG. 1 designed as an exhaust gas evaporator. In this case, the exhaust gas evaporator is flowed through by a first fluid, here preferably exhaust gas, and by a second fluid, here a fluid to be vaporized. The exhaust gas transfers heat to the fluid to be evaporated and evaporates it. The heat exchanger 1 in this case has a housing 2 with a fluid inlet 3 and a fluid outlet 4 for a first fluid. The exhaust gas flows through the housing from the inlet 3 to the outlet 4, wherein between inlet 3 and outlet 4, a series of tubes 5 are preferably arranged transversely to the flow direction 7 of the first fluid, which can be traversed by a second fluid. To improve the heat transfer between the first fluid and the second fluid, ribs 6 conveying the heat transfer are provided on the outside around the tubes 5 and / or between the tubes 5. These can be provided as corrugated ribs or as plane ribs or turbulence generators. The tubes 5 for the flow through the second fluid are preferably round tubes or flat tubes. These are preferably fluid-tightly received on both sides with their ends in tube sheets. The tubes 5 are preferably arranged on the inlet side and outlet side in a tube plate 8 with their ends 9 and connected fluid-tight.

The heat exchanger is connected to an inlet port 10 for the inlet of the second fluid and to an outlet port 11 to the outlet. From the inlet, the fluid distributes to a first number of tubes. These are preferably flowed through in parallel by the second fluid. Subsequently, the fluid is deflected at the opposite ends of these tubes in a further number of other tubes. These are again flowed through by the second fluid.

For diverting the fluid, a respective structure 12 is connected to the respective tube sheet 8, by means of which groups of tubes 5 are connected to each other such that an outlet 15 of at least one tube 5 is fluidly connected to an inlet 16 of at least one other tube 5.

The structure 12 consists of at least one baffle plate 13 and a cover plate 14 which are formed and arranged one above the other. The cover plate 14 covers the baffle 13 fluid-tight. Preferably, the cover plate 14 is welded to the baffle 13 or soldered or glued or even formed in one piece.

The baffle plate 13 has openings which connect the outlets 15 of one tube 5 to the inlets 16 of the other tubes 5.

The tubes 5 are inserted on at least one side in the tube sheet 8 in openings 17, where the tubes are soldered or welded to the ground.

As the material for the tubes and tube sheets aluminum but most preferably stainless steel can be used. Also, the entire heat exchanger made of aluminum or stainless steel.

The baffle 13 has openings or channel structures adapted to connect outlets of pipes to inlets of other pipes.

As an alternative to the separate formation of tube plate 8, baffle plate 13 and cover plate 14, it may also be advantageous if the baffle plate is formed with the tube sheet to a part or the baffle plate is formed with the cover plate as a part. In FIG. 4 It is shown that the baffle plate is formed with the tube sheet to a part 18. In FIG. 5 It is shown that the baffle plate is formed with the cover plate to a part 19.

In this case, the common part 18 and 19 respectively placed on the other part 14 and 8 and connected to this fluid-tight.

In this case, the tubesheet can also be designed such as milled, for example, that the so multifunctional modified tube sheet also takes on the task of fluid distribution and acts as a combination of bottom plate and baffle. Then only a cover plate is placed and connected to the ground. Accordingly, the part 19 can also act as a milled component, which integrated deflection plate and cover plate.

Furthermore, the tubesheet and / or the baffle plate and / or the cover plate may also be formed as a casting, which has a corresponding structure with recessed integrated openings for distribution of the medium.

The connection of the two or three elements tube plate, baffle and cover plate is advantageously carried out by welding, soldering or screwing, whereby a combination of the connection options can be used. For this purpose, the top plate can also have holes to distribute at certain points over the surface to connect by welding the plates together.

In particular, in order to achieve a good solder joint, the 3 plates can be fixed to each other by means of rivets or tack welds and pressed together, alternatively on welds, embossing or screwing.

The baffle contains openings as structures to collect the medium from at least one tube and redistribute it to at least one other tube. Preferably, from up to four or more tubes, the fluid to be vaporized is collected in the ports and then re-divided into up to four or more other tubes. With each collection and distribution of the fluid thermal instabilities leading to the uneven mass flow distribution in the tubes, and thus to different temperatures and or vapor levels, largely balanced. This can compensate for instability effects that lead to significant performance losses.

This is also a significant advantage of the 2 sandwich floors compared to the solution with pipe bends and only one sandwich floor. Thus, the mixing processes take place in both soils.

The FIG. 6 schematically shows a core 20 of the heat exchanger 1, in which a plurality of tubes 5 is arranged. These tubes 5 are arranged between the distributor plates 21, 22 formed as deflection regions and received there in tube plates and deflecting and cover plates.

The distributor plates 21, 22 are divided into individual segments 24, 25, 26, 27, 28 and 29 when viewed in the exhaust gas flow direction 23. Within a segment 24 to 29, a number of tube rows 30, 31 are again provided. In the example of FIG. 6 For each segment two rows of tubes are provided. Ideally, a segment consists of only a few Tube rows, for example, two rows of tubes in the exhaust gas flow direction, so that the temperature gradient over a segment is as small as possible and thus all tubes are subjected to almost the same exhaust gas temperature. Depending on the working medium but can also form up to 6 rows of tubes a segment, or several segments are interconnected in parallel.

In the embodiment of FIG. 6 continue to be connected in parallel to each tube row 30, 31 up to 4 tubes perpendicular to the exhaust gas flow direction.

As in FIG. 6 As can be seen, the second fluid flows in the region of the tube ends 32 and is distributed over four tubes 5. The fluid flows through these tubes to the ends of these tubes on the opposite side and flows out there into the region 33. The deflection region 35 directs the fluid into the inlets of the region 34, from where the fluid flows back through the respective tubes back to the region 36. Subsequently, the fluid is deflected by the deflection region 37 to the region 38 of the tube ends and distributed, so that the fluid now flows back through tubes that lie below the first passage.

Thus, the first segment flows through in alternating flows and the fluid finally exits the region 39 from the segment and is diverted at the transition 40 from the first segment 29 into the second segment 28.

Subsequently, the corresponding flow through the second segment 28 takes place until the fluid flows over the passage 41 into the third segment 27. Subsequently, the corresponding flow through the third segment 27 takes place until the fluid flows over the passage 42 into the fourth segment 26. Subsequently, the corresponding flow through the fourth segment 26 takes place until the fluid flows over the transition 43 into the fifth segment 25. Subsequently, the corresponding flow through the fifth segment 25 until the fluid flows over the passage 44 into the sixth segment 24. Subsequently, the corresponding flow through the sixth segment 24 takes place until the fluid at the outlet 4 flows out of the sixth segment 24.

The FIGS. 7 and 8th show once again the connection configuration of the tubes at the front and at the rear deflection area. It can be seen that in each case four tubes are connected in parallel and a diversion of fluid from four tubes into four other tubes takes place. The fluid enters the front according to FIG. 7 in tubes 5, from which it emerges at the rear side. Therefore, the tubes 5 are in the front deflection according to FIG. 7 also with the complementary entries or withdrawals as in FIG. 8 characterized.

The FIG. 9 shows a corresponding view of six segments 50 to 55, each having two rows of tubes. In each case, three tubes are combined to form a passage 56 and connected in parallel. At passage 56, the fluid flows in and flows through the tubes to the rear deflection region. There, the fluid is deflected from one row of tubes to the adjacent row of tubes. Subsequently, the fluid flows through the next three tubes and is deflected in the front deflection in the same row of tubes in three more tubes. Thereafter, the fluid flows through the tubes to the rear deflection region. There, the fluid is redirected from one row of tubes to the adjacent row of tubes. Subsequently, the fluid flows through the next three tubes and is deflected in the front deflection in the same row of tubes in three more tubes. This takes place until the fluid in the region 57 flows out of the tubes and is transferred through the passage 58 into the next segment. The passage may preferably be integrated in the baffle or carried out by an external transfer via pipe.

The flow through the heat exchanger of FIG. 9 shows a difference from the previous embodiment. In FIG. 9 the deflection of the fluid in the front baffle of tubes takes place in tubes of the same row according to opening 60, while in the rear baffle a diversion of tubes of one row into tubes of another row according to opening or openings 59 takes place.

The FIG. 10 shows a further embodiment in a further view, wherein six segments 70 to 75 each have two rows 76,77 of tubes. As can be seen, the segments 71 and 72 are combined to form a common parallel-connected segment. The same applies to segments 73 and 74.

Furthermore, in each case three tubes are combined to form a passage 78 and connected in parallel. At passage 78, the fluid flows in and flows through the tubes to the rear deflection region. There, the fluid is deflected from one row of tubes to the adjacent row of tubes through openings 79 in the baffle plate. Subsequently, the fluid flows through the next three tubes and is deflected in the front deflection region in the same row of tubes in three more tubes through the opening 80 of the front baffle plate. Thereafter, the fluid flows through the tubes to the rear deflection region. There, the fluid is redirected from one row of tubes to the adjacent row of tubes. Subsequently, the fluid flows through the next three tubes and is deflected in the front deflection in the same row of tubes in three more tubes. This takes place until the fluid in the region 81 flows out of the tubes and is transferred through the passage 82 into the next segment 71, 72. The passage 82 may preferably be integrated in the baffle or carried out by an external transfer via pipe.

In the segments 71, 72, the flow through takes place as in the segment 70, although these are connected in parallel and the fluid enters the regions 83 and 84 in parallel. Subsequently, the tubes of the segments 71 and 72 are flowed through like the tubes of the segment 70, before the fluid is again discharged from the segment at the regions 85 and 86 and transferred into the parallel segments 73 and 74 by means of the transition 87. In the segments 73 and 74, the flow through as in the segments 71 and 72. Subsequently, the fluid from the segments 73 and 74 is collected and introduced into the final segment 75, where it flows through the segment 75 as in the input-side segment 70 before it is discharged from the heat exchanger.

The FIG. 11 shows a further embodiment in a further view, wherein six segments 90 to 95 each have two rows 96,97 of tubes. As can be seen, the segments 90 and 91 are combined into a common parallel-connected segment. The same applies to the segments 92, 93 and 94, which are combined into a common segment.

In the segments 90 and 91 or in the segments 92 to 94, only one tube 98 is flowed through in parallel to a tube 99 of the other segment. Within the segment, the tubes 98 are only flowed through serially. This is done up to the middle of the segment. There, the fluid flows out of the tubes 101, 102 of the two segments. There is a mixing zone 100, so that the fluid from the first segment 90 can mix with the fluid of the second segment 91 before it re-distributes to the tubes 103, 104 of the segments.

At passage 98, the fluid flows in and flows through a tube to the rear deflection region. There, the fluid is deflected from one row of tubes to the adjacent row of tubes through an opening 105 in the baffle plate. Subsequently, the fluid flows through the next tube and is deflected in the front deflection region in the same row of tubes in another tube through the opening 106 of the front baffle plate. Thereafter, the fluid flows through the tubes to the rear deflection region. There, the fluid is redirected from one row of tubes to the adjacent row of tubes. Subsequently, the fluid flows through the next tube and is deflected in the front deflection in the same row of tubes in another tube. This takes place until the fluid flows out in the mixing zone 100. In the second area after the mixing zone, the corresponding flow through the pipes takes place. Subsequently, the fluid is transferred through the passage 107 into the next segment 92, 93, 94. The passage 107 may preferably be integrated in the baffle plate or by an external passage via pipe.

In the segments 92, 93, 94, the flow takes place as in the segment 90, 91, although these are all connected in parallel. Subsequently, the tubes of the segments 92 to 94 are flowed through, before the fluid is again discharged from the segment and transferred to the segment 95 by means of the transfer 108. In the segment 95, the flow takes place as in the segment 70 of FIG. 10 in which three tubes are connected in parallel. Subsequently, the fluid is discharged from the heat exchanger.

The FIG. 12 shows a further embodiment in a further view, wherein six segments 110 to 115 each have two rows 116, 117 of tubes. As can be seen, the segments 110 to 112 and 113 to 115 are combined to form a common parallel-connected segment.

In the segments 110 to 112 or in the segments 113 to 115, in each case only one tube 116 is parallel to a tube 117, 118 of the other Segments flows through. Within the segment, the tubes 116, 117 or 118 are only flowed through serially. This is done up to the middle of the segment. There, the fluid flows out of the tubes 119, 120, 121 of the three segments. There is a mixing zone 122, so that the fluid from the first segment 110 can mix with the fluid of the second and third segments 111, 112 before returning to the tubes 123, 124 and 125 of the segments 110, 111, 112 is distributed.

At passage 116, the fluid flows in and flows through a tube to the rear deflection region. There, the fluid is deflected from one row of tubes to the adjacent row of tubes through an opening in the baffle plate. Subsequently, the fluid flows through the next tube and is deflected in the front deflection in the same row of tubes in another tube through the opening of the front baffle plate. Thereafter, the fluid flows through the tubes to the rear deflection region. There, the fluid is redirected from one row of tubes to the adjacent row of tubes. Subsequently, the fluid flows through the next tube and is deflected in the front deflection in the same row of tubes in another tube. This takes place until the fluid flows out in the mixing zone 122. In the second area after the mixing zone, the corresponding flow through the pipes takes place. Subsequently, the fluid is transferred through the passage 126 into the next segment 113, 114, 115. The passage 126 may preferably be integrated in the deflection plate or be made by an external passage via pipe.

In the segments 113, 114 and 115, the flow through as in the segments 110, 111 and 112. Subsequently, the fluid is discharged from the heat exchanger.

The design of the baffle is provided rectangular in the figures. It can also be round, so that it can be installed in a round, cylindrical recess in a housing or in a silencer.

To increase performance can be threaded on the tubes gas side ribs, see the ribs 6 of FIG. 2 , The gas-side ribs form the so-called secondary surface of the heat transfer and the tubes represent the primary surface of the heat transfer. The ribs 6 can be soldered to the tubes 3 or a thermally conductive connection is achieved without the addition of solder during the soldering process of the entire evaporator. This can be achieved by a very tightly tolerated pipe run, which leads to a very small gap between the rib and pipe. Thus, in the high-temperature brazing process by diffusion processes, a thermally conductive connection between the ribs and the tubes is made, even if no solder should be present.

A better connection of the ribs with the pipes, whether with or without solder, can be achieved by a combination of austenitic pipes and ferritic ribs. Ferrites have a lower expansion at high temperatures than austenite, so that the tubes are pressed against the ribs at soldering temperature. In order to avoid tearing of the ribs from the tubes during cooling, the rib may have small slits around the tubes.

The ribs have pipe passages with so-called collar, through which the distance between the ribs is ensured. Alternatively, the rib spacing can also be ensured by exhibiting spacers in the rib. The rib density can be between 30 Ri / dm and 80 Ri / dm. The ribs can be punched and have cut and erect gills or even embossed structures, such as winglets, dimples or bulges, to increase performance. In particular It is expedient to impress such structures in the ribs, which directs the flow targeted to the pipes and thus a higher heat transfer can be achieved on the primary surface.

The rib thickness is 0.1 mm to 0.5 mm or preferably between 0.25 and 0.4 mm, which is advantageous for stainless steel as a ribbed material.

Furthermore, slots can be introduced in the composite of the plates above and / or below, so that a different thermal expansion due to different temperatures from the gas inlet to the gas outlet is made possible and does not lead to damage.

The pipe diameter of the pipes is preferably in the range of 3 to 20 mm, ideally in the range of 5 to 15 mm and preferably in the range of 6 to 10 mm.

Turbulence generating structures can be incorporated into the tubes, e.g. Swirl generator to promote heat transfer especially in the area where the fluid overheats.

The tube can also be designed as a spiral tube, but then preferably without outer ribs. In particular, pipes with very deep grooves are used, which are similar to a bellows with larger pipe diameters formed in order to increase the heat transfer on the gas side and at the same time can absorb the thermal expansion difference between the tubes. Basically, different performance classes can be achieved
when an evaporator in the exhaust gas flow direction consists of individual modules.

Claims (9)

1. A heat exchanger (1), such as in particular an exhaust gas evaporator, having a housing (2) with a fluid inlet (3) and a fluid outlet (4) for a first medium, such as in particular exhaust gas, and having tubes (5) which are arranged in the housing (2) transversely with respect to the flow direction of the first fluid and through which a second medium can flow and the ends of which are arranged and connected in a fluid-tight manner in a tube sheet (8) at the inlet side and at the outlet side, wherein the respective tube sheet (8) has connected to it in each case a structure (12) by means of which groups of tubes (5) are connected to one another in such a way that an outlet of at least one tube (5) is fluidically connected to an inlet of at least one other tube (5), characterised in that the structure (12) consists of a deflection plate (13) and a cover plate (14), wherein the deflection plate (13) has openings which connect the outlets of one set of tubes (5) to the inlets of the other set of tubes (5), and wherein the cover plate (14) covers the deflection plate (13) in a fluid-tight manner.
2. The heat exchanger (1) as claimed in claim 1, characterised in that the deflection plate (13) is placed on the respective tube sheet (8) and connected thereto, wherein the cover plate (14) is placed on the respective deflection plate (13) and connected thereto.
3. The heat exchanger (1) as claimed in claim 1, characterised in that the deflection plate (13) is of one-piece design with the respective tube sheet (8), wherein the cover plate (14) is placed on the respective deflection plate (13) and connected thereto.
4. The heat exchanger (1) as claimed in claim 1, characterised in that the deflection plate (13) is of one-piece design with the respective cover plate (14), wherein the deflection plate (13) and the cover plate (14) are placed on the respective tube sheet (8) and connected thereto.
5. The heat exchanger (1) as claimed in one of the preceding claims, characterised in that the tubes (5) are arranged in rows, wherein the deflection plate (13) deflects fluid between tubes (5) in different rows.
6. The heat exchanger (1) as claimed in one of the preceding claims, characterised in that the tubes (5) are arranged in rows, wherein the deflection plate (13) deflects fluid between tubes (5) in the same row.
7. The heat exchanger (1) as claimed in one of the preceding claims, characterised in that the rows of tubes (5) are arranged in segments, wherein the deflection plate (13) deflects fluid from one segment into another segment.
8. The heat exchanger (1) as claimed in one of the preceding claims, characterised in that a plurality of tubes (5) is connected in parallel, at least in one segment.
9. The heat exchanger (1) as claimed in one of the preceding claims, characterised in that a plurality of tubes (5) connected in parallel is connected in series with one another, at least in one segment.

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