EP2825832A2

EP2825832A2 - Heat exchanger

Info

Publication number: EP2825832A2
Application number: EP13710830.4A
Authority: EP
Inventors: Klaus Irmler; Peter Geskes
Original assignee: Behr GmbH and Co KG
Current assignee: Mahle Behr GmbH and Co KG
Priority date: 2012-03-16
Filing date: 2013-03-14
Publication date: 2015-01-21
Anticipated expiration: 2033-03-14
Also published as: WO2013135808A3; EP2825832B1; US20150060028A1; WO2013135808A2; DE102012204151A1

Abstract

The invention relates to a heat exchanger, such as in particular an exhaust-gas evaporator, having a housing with a fluid inlet and with a fluid outlet for a first medium, such as in particular exhaust gas, and having tubes which are arranged in the housing transversely with respect to the flow direction of the first fluid and through which a second medium can flow and which, by way of their ends at the inlet side and at the outlet side, are arranged and connected in a fluid-tight manner in a tube plate, wherein, to the respective tube plate, there is connected in each case one structure by means of which groups of tubes are connected to one another in such a way that an outlet of at least one tube is fluidically connected to an inlet of at least one other tube.

Description

Heat exchanger

description

Technical area

The invention relates to a heat exchanger, in particular an 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 outlet side are arranged in a tube sheet with their ends and connected fluid-tight.

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

Commercial vehicles or passenger cars, it is therefore appropriate to a Part of the energy content of the hot exhaust gas for driving the

Recover motor vehicle again.

Various methods are currently being tested for this energy recovery. So there are approaches, the energy content electrically means

Recover thermocouples. However, this is currently limited to low power, 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 on an expander or in a turbine so that mechanical energy is generated.

The evaporation of the medium takes place by means of a heating via the hot exhaust gas. To achieve the highest possible efficiencies, 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, instead of the Exhaust gas cooler is used or in addition to this, heat can be removed from the exhaust gas to evaporate 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 so-called disk evaporator according to WO 201 1/051163 A2 become known in which ribs are soldered between disk pairs and in which a number of such pairs of disks are connected in parallel. In this case, a fluid flows through the pairs of discs and another fluid flows around this usual way. In the discs then the fluid flowing through evaporates when the exhaust gas flows around the discs evaporators, which consist of discs and ribs, have a high

Power density, which makes it possible to provide also for vehicles very compact high performance evaporator. The disadvantage, however, is that such evaporators are relatively expensive to manufacture. Presentation of the invention, object, solution, advantages

It is the object of the invention to provide a heat exchanger, which compared to the prior art simple and yet

is inexpensive to manufacture 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, in particular exhaust gas, arranged in the housing transversely to the flow direction of the first fluid Tubes which can be traversed by a second medium and the inlet side and outlet side are arranged in a tube bottom with their ends and fluid-tightly connected, wherein each structure is connected to the respective tubesheet, by means of soft groups of tubes so

connected to each other, 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.

It is particularly advantageous if the structure consists of a deflecting plate and a cover plate, wherein the deflecting plate has openings which connect the outlets of one tube with the inlets of the other tubes, and wherein the cover plate covers the deflecting plate in a fluid-tight manner. 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 useful if the baffle with the respective

Tube bottom is formed in one piece, 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 when the tubes are arranged in rows, wherein the baffle deflects fluid between tubes of different rows, This means that the baffle fluid from a first tube or a group of first tubes in a second tube or in a group of deflects second tubes, wherein the first tubes and the second tubes are preferably arranged in a different series 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 baffle fluid from one segment to another

Segment deflects,

Furthermore, it is expedient if at least in one segment

Plural 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 characterized by the following

Description of the figures and described by the subclaims.

Brief description of the drawings Hereinafter, the invention will be based on at least one

Embodiment explained in more detail with reference to the drawings. Show it:

Fig. 1 shows a first embodiment of an inventive

Heat exchanger in three-dimensional view,

2 is a view of the heat exchanger from the side,

3 is a partial view of a collecting area,

4 is a partial view of a collecting area,

5 is a partial view of a collecting area, FIG. 6 is a view of the heat transfer core,

7 is a view of a front deflection of the

Heat exchanger, Fig. 8 is a view of a rear deflection of the

heat exchanger,

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

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

Fig. 1 1 another embodiment in a view of a front deflection, and Fig. 12 shows another embodiment in a view of a front deflection region.

Preferred embodiment of the invention

Figures 1 and 2 show a heat exchanger 1, the in

Embodiment of Figure 1 is 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 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 preferably transversely to

Flow direction 7 of the first fluid are arranged, which are 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 inlet side and

outlet side are arranged in a tube sheet 8 with their ends 9 and connected fluid-tight.

The heat exchanger is to the inlet of the second fluid with a

Inlet port 10 and connected to the outlet with an outlet 1 1. Starting from the inlet, the fluid distributes to a first number of times

Pipes. 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 tubesheet 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 Abdeckpiatte 14, which are formed and arranged one above the other. The Abdeckpiatte 14 covers the baffle 13 fluid-tight. Preferably, the Abdeckpiatte 14 is welded to the baffle plate 3 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 with 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 soldered to the ground

or welded.

As the material for the tubes and tube sheets aluminum but most preferably stainless steel can be used. Also, the whole can

Heat exchanger made of aluminum or stainless steel.

The baffle 3 has openings or channel structures which are adapted to connect outlets of pipes with the admission 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. FIG. 4 shows that the

Deflection plate is formed with the tube bottom to a part 18. FIG. 5 shows that the deflecting plate with the cover plate is formed into 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. Correspondingly, the part 19 can also function as a milled component, which integrates deflecting piatia 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 Abdeckplatzte advantageously takes place via a 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 become uneven

Mass flow distribution in the pipes lead, 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.

FIG. 6 schematically shows a core 20 of the heat exchanger 1, in which a multiplicity of tubes 5 are 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 viewed in the exhaust gas flow direction 23 divided into individual segments 24, 25, 26, 27, 28 and 29.

Within a segment 24 to 29 are again a number of

Pipe rows 30, 31 are provided. In the example of Figure 6 two rows of tubes are provided per segment. Ideally, a segment consists of only a few Tube rows, for example, of two rows of tubes in the exhaust gas flow direction, so that the temperature gradient over a segment is possible 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 pipes a segment, or several segments are interconnected in parallel.

In the exemplary embodiment of FIG. 6, furthermore, up to 4 tubes per tube row 30, 31 are connected in parallel perpendicular to the exhaust gas flow direction.

As can be seen in FIG. 6, the second fluid flows in the region of

Pipe ends 32 and distributed on four tubes 5. The fluid flows through these tubes to the ends of these tubes on the opposite side and flows there in the area 33 from. The deflection region 35 directs the fluid into the inlet of the region 34, from where the fluid flows back to the region 36 through the respective tubes. 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. Connecting the corresponding flow through the second segment 28 takes place until the fluid flows over the passage 41 into the third segment 27.

Connecting the corresponding flow through the third segment 27 takes place until the fluid flows over the passage 42 in the fourth segment 26.

Connecting the corresponding flow through the fourth segment 26 takes place until the fluid flows over the passage 43 into the fifth segment 25.

Then the corresponding flow through the fifth segment takes place 25 until the fluid flows over the passage 44 in the sixth segment 24.

Connecting the corresponding flow through the sixth takes place

Segment 24 until the fluid at the outlet 4 from the sixth segment 24 flows out.

Figures 7 and 8 show once again the connection configuration of the tubes at the front and at the rear deflection region. 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 occurs on the

Front in accordance with Figure 7 in tubes 5, from which it exits at the rear side. Therefore, the tubes 5 in the front deflection region according to FIG. 7 are also marked with the complementary inlets or outlets as in FIG. Figure 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 Figure 9 shows a

Difference from the previous embodiment. In Figure 9, the deflection of the fluid in the front baffle of tubes one in tubes of the same row according to opening 60, while in the rear

Baffle a diversion of tubes of one row in tubes of another row according to opening or openings 59 takes place.

FIG. 10 shows a further exemplary embodiment in a further view, with six segments 70 to 75 each having two rows 76, 77 of tubes. As can be seen, the segments 71 and 72 are combined to form a common segment connected in parallel. The same applies to the 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 area. 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. 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, but these are shadowed 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 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.

FIG. 1 shows a further exemplary 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 grouped into a common segment connected in parallel. The same applies to the segments 92, 93 and 94, which are combined to form a common segment. In the segments 90 and 91 and in the segments 92 to 94, only one tube 98 in each case becomes parallel to a tube 99 of the other segment

flows through. Within the segment, the tubes 98 are only flowed through serially. This is done until 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 again distributed to the tubes 103, 04 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 in the

Baffle be integrated or done by an external transfer 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 Figure 10, in which three tubes are connected in parallel. Subsequently, the fluid is discharged from the heat exchanger.

FIG. 12 shows a further exemplary embodiment in a further view, wherein six segments 1 10 to 15 each have two rows 16, 17 of tubes. As can be seen, the segments 1 10 to 1 12 and 1 13 to 1 15 are combined to form a common parallel-connected segment. In the segments 1 10 to 1 12 and in the segments 1 13 to 15 only one pipe 1 16 is parallel to a pipe 1 17, 1 18 of the other Segments flows through. Within the segment, the tubes 1 16, 1 17 or 1 18 are only flowed through serially. This takes place up to the middle of the segment, where the fluid flows out of the tubes 1 19, 120, 121 of the three segments. There is a mixing zone 122, so that the fluid from the first segment 1 10 can mix with the fluid of the second or third segment 1 11, 1 12 before it again on the tubes 123, 124 and 125 of the segments 1 10th , 1 1 1, 1 12 is distributed.

At passage 1 16, 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 region 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 26 in the next segment 1 13, 1 14, 1 15. The passage 126 may preferably be integrated in the deflection plate or be made by an external passage via pipe.

In the segments 1 13, 1 14 and 1 15, the flow takes place as in the segments 1 10, 1 1 1 and 1 2. Subsequently, the fluid from the

Heat exchanger omitted. 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, gas-side ribs can be threaded onto the tubes, 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 it 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

be achieved. 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 off the ribs from the tubes when cooled, the rib may have small slots 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. Especially It is useful to memorize such structures in the ribs that the

Flow directed specifically 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 carried out as a twist raw r, but then preferably without outer ribs. In particular, pipes are also very deep

pronounced grooves formed similar to a bellows with larger pipe diameters to increase the heat transfer on the gas side and at the same time can accommodate the thermal expansion difference between the tubes. Basically you can

different performance classes are achieved

when an evaporator in the exhaust gas flow direction consists of individual modules.

Claims

claims

1 . Heat exchanger, in particular exhaust gas evaporator, with a

Housing with a fluid inlet and a fluid outlet for a first medium, in particular exhaust gas, arranged in the housing transversely to the flow direction of the first fluid tubes, which are traversed by a second medium and arranged on the inlet side and outlet side in a tube plate with their ends and fluid-tight are each connected to the respective tubesheet, 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.

2. Heat exchanger according to claim 1, characterized in that the structure consists of a baffle plate 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.

3. Heat exchanger according to claim 1 or 2, characterized in that the baffle plate is placed on the respective tube sheet and connected thereto, wherein the cover plate to the respective

Baffle is placed and connected to this.

4. Heat exchanger according to claim 1 or 2, characterized in that the deflection plate with the respective tube sheet in one piece is formed, wherein the cover plate is placed on the respective baffle plate and connected thereto.

5. Heat exchanger according to claim 1 or 2, characterized in that the baffle plate is formed integrally with the respective cover plate, wherein the baffle plate and the cover plate is placed on the respective tube sheet and connected thereto.

6. Heat exchanger according to one of the preceding claims, characterized in that the tubes are arranged in rows, wherein the baffle deflects fluid between tubes of different rows.

7. Heat exchanger according to one of the preceding claims, characterized in that the tubes are arranged in rows, wherein the baffle deflects fluid between tubes of a same series.

8. Heat exchanger according to one of the preceding claims, characterized in that the rows of tubes in segments

are arranged, wherein the baffle deflects fluid from one segment to another segment.

9. Heat exchanger according to one of the preceding claims, characterized in that at least in a segment, a plurality of tubes are connected in parallel.

10. Heat exchanger according to one of the preceding claims, characterized in that _» at least in one segment, a plurality of parallel-connected tubes are connected in series with each other.