EP2863157A1 - Heat exchanger - Google Patents

Abstract

The invention relates to a heat exchanger (1, 21, 41, 81) with a first flow channel (15, 39, 55, 100) through which a first fluid can flow, and with a second flow channel (14, 38, 54, 99). , which is traversed by a second fluid, wherein the first flow channel (15, 39, 55, 100), a first portion (12, 36, 52, 97), a second portion (13, 37, 53, 98) and a deflection region wherein the first subsection is in fluid communication with the second subsection via the deflection region (7, 27, 47, 87) and the first subsection (12, 36, 52, 97), the second subsection (13, 37, 53, 98 ) and the deflection region (7, 27, 47, 87) are flowed around by the second fluid, wherein the first portion (12, 36, 52, 97) and / or the second portion (13, 37, 53, 98) of the first Flow channel (15, 39, 55, 100) in each case by a plurality of tubes (8, 9, 28, 29, 48, 49, 88, 89) is formed.

Description

Technical area

The invention relates to a heat exchanger with a first flow channel, which is traversed by a first fluid, and with a second flow channel, which is traversed by a second fluid, wherein the first flow channel has a first section, a second section and a deflection, wherein the first subsection is in fluid communication with the second subsection over the deflection region and the first subsection, the second subsection and the deflection region can be flowed around by the second fluid.

State of the art

In many applications, so-called U-flow heat exchangers are used. These heat exchangers are characterized in that the fluid flowing through the heat exchanger flows in at an end region of the heat exchanger and is deflected by approximately 180 degrees at an end region opposite this end region. The fluid finally flows out of the heat exchanger at the end region where it has flowed.

Heat exchangers with such a configuration are preferably used when the installation space no longer permits conventionally flow-through heat exchangers or speak of other boundary conditions for use.

An advantage of such a heat exchanger is that on the same length about twice the cooling distance is available. The disadvantage, however, is that only a smaller cross section per cooling section is available, which has a negative effect on the resulting pressure drop.

Various embodiments of such heat exchangers are known in the prior art. So revealed the DE 10 2004 019 554 B4 an exhaust gas recirculation system for an internal combustion engine. The exhaust gas recirculation system in this case has a heat transfer unit, which comprises a heat exchanger, which has a deflection of a fluid to be cooled by about 180 degrees. The heat exchanger has for this purpose a flow channel, which is U-shaped. As a result, both the fluid inlet of the flow channel and the fluid outlet are arranged at a common end region of the heat exchanger. The flow channel is in the region of the outflow, in the region of the return flow and in the region of the deflection of a second fluid flows around, whereby a heat transfer between the fluid within the flow channel and the fluid flow around the flow channel is achieved.

A disadvantage of the solutions in the prior art is in particular that the deflection of the heat exchanger either not at all or only by the air surrounding the heat exchanger is cooled. Furthermore, in heat exchangers, which provide a flow around the flow channel including the deflection, often the maximum heat transfer is too low.

Presentation of the invention, object, solution, advantages

It is therefore the object of the present invention to provide a heat exchanger which has a temperature-controllable deflection region and is optimized with regard to its performance in comparison with the prior art.

The object of the present invention is achieved by a heat exchanger with the features of claim 1.

An embodiment of the invention relates to a heat exchanger having a first flow channel through which a first fluid can flow and with a second flow channel through which a second fluid can flow, the first flow channel having a first subsection, a second subsection and a deflection region, wherein the first portion is in fluid communication with the second portion over the deflection region and the first portion, the second portion and the deflection of the second fluid are flowed around, wherein the first portion and / or the second portion of the first flow channel in each case by a plurality of Tubes is formed.

A deflected along its flow direction heat exchanger is particularly advantageous because overall the overall length of the heat exchanger can be made shorter than a straight-flow heat exchanger. A deflecting region surrounded by a second fluid is advantageous because it provides an additional heat transfer capability within the heat exchanger, whereby the efficiency or the performance of the heat exchanger can be increased. The first section and / or the second section of the first flow channel is advantageously formed from tubes.

Tubes are particularly advantageous because they are inexpensive to produce and are available in a variety of different shapes on the market. By a plurality of tubes, which are each surrounded by a fluid at their outer surfaces, the total heat transfer surface can be increased, whereby an improved heat transfer between the fluid within the tubes and the fluid outside the tubes can be achieved.

Furthermore, it is advantageous if the heat exchanger has a housing which is formed in one or more parts with at least a first housing part and a second housing part.

By a multi-part design better mountability can be achieved. In addition, the housing may be better adapted to the shape of the heat exchanger. In particular, undercuts can be realized by a multi-part housing, which can not be realized, for example, by one-piece deep-drawn housing.

The housing is advantageously made of an aluminum material and produced in a die-casting process. In this case, either all housing parts or only individual housing parts can be generated in this way. Alternatively, the housing or individual housing parts may be made of a steel material, in particular stainless steel, or a plastic. Made of plastic housing or housing parts are preferably made in an injection molding process.

Moreover, it is preferable if the housing at least partially forms the second flow channel. Advantageously, the housing surrounds the first flow channel such that a cavity is formed between the outer walls of the first flow channel and the inner walls of the housing, which forms the second flow channel. By flowing through this second flow channel, the first flow channel is flowed around, whereby a heat transfer between the fluid in the first flow channel and the fluid in the second flow channel can be generated.

In addition, it is expedient if the first housing part surrounds the first and second part section and the second housing part surrounds the deflection area.

By such a separation, a particularly advantageous and cost-effective adaptation of the housing to the heat exchanger can be achieved. In particular, the subsections can advantageously be encompassed by a simple cuboid structure, while the deflection region can be encompassed, for example, by a further housing part which, for example, in the form of a housing part deep-drawn lid can be formed and can be produced in a separate manufacturing process.

It is also preferable if the tubesheet with a lid forms a collecting box, wherein the internal volume of the collecting box forms the deflection region. In this way, a fluid-tight deflection region can be produced by known production methods.

Furthermore, it is advantageous if a flow path of the second flow channel is formed between an outer wall delimiting the deflection region and an inner wall of the housing and / or a wall of the first flow channel, which can be flowed through by the second fluid.

This flow path is particularly advantageous, since it can flow around the deflection region with the second fluid, which is preferably cooling. As a result, the overall heat transfer area between the first fluid and the second fluid is increased, whereby the performance of the heat exchanger is improved.

It is also preferable if along the flow path turbulence inserts and / or cross-sectional narrowing means are arranged on the outer wall of the deflection region and / or on the inner wall of the housing.

By turbulence inserts, such as guide ribs, wave profiles, elevations and depressions on the surface or by other means for influencing the cross section, the fluid flow in the flow path can be advantageously influenced. In particular, the effective cross-flow area can be influenced, which has a direct influence on the occurring pressure loss within the heat exchanger. Via flow guide means of this type, the course of flow within the flow path can also be influenced.

Moreover, it is advantageous if the housing has a first fluid connection and a second fluid connection, via which the second fluid can be supplied into the housing and can be discharged from the housing.

In a preferred embodiment of the invention, it may be provided that the first section and the second section and / or the deflection of the first flow channel into the housing, which at least partially forms the second flow channel, can be integrated such that the second flow channel fluid-tight with respect to the First flow channel and / or the deflection region and the environment is sealed.

A fluid-tight seal of the flow channels with respect to the respective other flow channel and the environment is particularly advantageous in order to ensure the functionality of the heat exchanger. In a not completely fluid-tight design, a mixing of the fluids could occur, which can lead to damage of the heat exchanger and / or the upstream and downstream components.

It is also advantageous if all tubes are accommodated at least at a common end region in a tube plate. The tubes are advantageously accommodated at a common end region in a tube plate. This increases the stability of the heat exchanger. Furthermore, by providing a tube plate at a common end region, a particularly simple connection to a fluid supply line and a fluid discharge can be achieved.

Furthermore, it is expedient if the fluid supply and the fluid discharge of the first flow channel are arranged at a common end region of the heat exchanger. This allows a particularly compact design of the heat exchanger.

It is also preferable if the first fluid is a gas and the second fluid is a coolant. In this way, a cooling of the in the first flow channel flowing fluid can be achieved advantageously. By cooling in the first subsection, in the second subsection and in the deflection region, a greater cooling of the first fluid or of the gas can be achieved.

Moreover, it is preferable if the second fluid has a lower temperature level than the first fluid. The second fluid serves to cool the first fluid. The second fluid can advantageously be incorporated into a cooling circuit in order to always ensure the lowest possible temperature level for the second fluid. Depending on the design of the heat exchanger, the second fluid in an alternative embodiment, but also have a higher temperature level than the first fluid. This is especially true when the heat exchanger is used to heat the first fluid.

It is also advantageous if the first fluid in the deflection region can be deflected by 180 degrees along its direction of flow. A deflection of about 180 degrees is particularly advantageous since in this way the fluid connections can be provided at a common end region of the heat exchanger. In alternative embodiments, it is also possible to provide deflections which have a different angle or, for example, two deflections of 90 degrees each.

Depending on whether only the first and second subsection or the deflection region are arranged in the housing, the maximum amount of heat that can be transferred may be larger or smaller. Particularly advantageous is an arrangement in which both the subsections and the deflection region of a second fluid, which is preferably a cooling fluid, flows around.

Advantageous developments of the present invention are described in the subclaims and in the following description of the figures.

Brief description of the drawings

Fig.1

eine perspektivische Ansicht eines in einem Gehäuse aufgenommenen in seiner Durchströmungsrichtung um 180 Grad umgelenkten Wärmeübertragers,

Fig. 2

eine perspektivische Ansicht des Wärmeübertragers gemäß Fig. 1,

Fig. 3

eine alternative perspektivische Ansicht eines in einem Gehäuse aufgenommenen Wärmeübertragers,

Fig. 4

eine perspektivische Ansicht eines alternativ ausgestalteten Wärmeübertragers gemäß Fig. 3,

Fig. 5

eine weitere alternative Ansicht eines in einem Gehäuse aufgenommenen Wärmeübertragers, der in seiner Durchströmungsrichtung um 180 Grad umgelenkt ist,

Fig. 6

eine perspektivische Ansicht des Wärmeübertragers gemäß Fig. 5,

Fig. 7

eine Schnittansicht durch einen in seiner Durchströmungsrichtung um 180 Grad umgelenkten Wärmeübertrager, wie er im Stand der Technik bekannt ist, und

Fig. 8

eine Schnittansicht eines erfindungsgemäßen Wärmeübertragers mit einer zusätzlichen Strömungsstrecke, welche den Umlenkbereich umgibt.

In the following the invention will be explained in detail by means of embodiments with reference to the drawings. In the drawings show:

Fig.1

a perspective view of a housed in a housing in its flow direction 180 degrees deflected heat exchanger,

Fig. 2

a perspective view of the heat exchanger according to Fig. 1 .

Fig. 3

an alternative perspective view of a received in a housing heat exchanger,

Fig. 4

a perspective view of an alternative heat exchanger according to Fig. 3 .

Fig. 5

a further alternative view of a received in a housing heat exchanger, which is deflected in its flow direction by 180 degrees,

Fig. 6

a perspective view of the heat exchanger according to Fig. 5 .

Fig. 7

a sectional view through a deflected in its flow direction by 180 degrees heat exchanger, as is known in the art, and

Fig. 8

a sectional view of a heat exchanger according to the invention with an additional flow path which surrounds the deflection region.

Preferred embodiment of the invention

The Fig. 1 shows a perspective view of a heat exchanger 1. The heat exchanger 1 is surrounded by a housing 2. The housing 2 has on its outer side a plurality of ribs 5, which increase the structural rigidity of the housing 2. The ribs 5 are for this purpose distributed on the housing 2 load. Furthermore, the housing 2 has a holding element 4, with which the heat exchanger 1 can be attached to a surrounding structure. In addition, the housing 2 has a fluid connection 3, through which a fluid can be conveyed into the housing 2. At the lower end region of the heat exchanger 1, a tube plate 6 is indicated, which belongs to the heat exchanger 1 inserted in the housing 2.

The housing 2 is preferably formed from a plastic, which can be processed, for example, in a die-casting process. Alternatively, metallic materials can also be used.

The Fig. 2 shows a perspective view of the heat exchanger 1, as in the housing 2 of Fig. 1 is arranged.

The heat exchanger 1 has in its lower region a tube plate 6, in which a plurality of first tubes 8 and second tubes 9 is received. The tubes 8 and 9 are arranged in each case in two adjacent tube stacks with several tubes in depth. The tubes 8 are traversed along the flow direction 10 with a first fluid and the tubes 9 are flowed through along the flow direction 11 with the first fluid.

The directional deflection between the tubes 8 and tubes 9 takes place in the upper deflection region 7. The deflection region 7 is essentially also through a tube plate 16 is formed, in which the tubes 8, 9 are received and a box-like lid 17, which is inserted into this tubesheet, whereby an internal volume within the deflection region 7 is generated, in which the fluid from the tubes 8 into the tubes 9 flow can.

The first tubes 8 form a first section 12 of a first flow channel 15 and the second tubes 9 form a second section 13 of a first flow channel 15. Overall, the tubes 8 and 9 and the deflection 7 form the first flow channel 15.

The first flow channel 15 can be flowed around by a second fluid within the housing 2. Within the housing 2, a second flow channel 14 is formed for this purpose. In this way, a heat exchange between the first fluid can be generated both along the tubes 8 of the deflection region 7 and the tubes 9. Overall, thus, the heat transfer between the first fluid and the second fluid can be significantly increased, since in particular the deflection region 7 is fully involved in the heat transfer between the first fluid and the second fluid.

Furthermore, in Fig. 2 a Kühlmittelleitvorrichtung shown, which surrounds both the tubes 8 and the tubes 9. The task of the Kühlmittelleitvorrichtung is to influence the flow of fluid flowing within the housing. This should primarily be prevented that a short-circuit flow within the housing is formed and thus the fluid flows directly from the fluid inlet to the fluid outlet. This can happen, in particular, if the fluid inlet and the fluid outlet are arranged on a common housing side. Furthermore, the fluid can also be routed specifically between the tubes 8, 9 in such a way that the best possible flow around and thus an improved heat transfer occurs. Furthermore, an increase in the stability of the heat exchanger 1 can be achieved by the Kühlmittelleitvorrichtung.

Below the tube bottom 6 fluid connections may be provided in advantageous embodiments, which may be arranged for example on a collecting box. About this, the tubes 8, a fluid can be supplied and separated from the tubes 9, a fluid can be removed.

The Fig. 3 shows an alternative embodiment of a heat exchanger 21. The heat exchanger 21 is received within the housing 22. The housing 22 is preferably formed of a metallic material. Ideally, the housing 22 is formed of an aluminum.

The housing 22 has a plurality of holding elements 24, with which the housing 22 or the heat exchanger 21 can be attached to surrounding structures. At the lower end region of the housing 22, a tube plate 26 is indicated, which belongs to the heat exchanger 21 inserted in the housing 22.

The Fig. 4 shows a perspective view of the heat exchanger 21, as in the interior of the housing 22 of the Fig. 3 is arranged. The tube plate 26 has a plurality of tubes 28 received in the tubesheet 26 and tubes 29. The tubes 28 and 29 are in the tube plate 26 analogous to the arrangement of the tubes 8 and 9 of the Fig. 2 arranged in the tube sheet 6. In this case, the tubes 28 form a first section 36 of a first flow channel 39, and the tubes 29 form a second section 37 of the first flow channel 39. The tubes 28 and 29 are in the Fig. 4 further from a Kühlmittelleitvorrichtung similar to Fig. 2 whereby the fluid flow within the heat exchanger 21 can be improved overall and, in particular, short-circuit flows of the fluid between the fluid inlet and the fluid outlet of the housing can be avoided.

The tubes 28 are flowed through along the flow direction 30 with a first fluid and the tubes 29 are flowed through along the flow direction 31 with the first fluid. The deflection of the fluid takes place in the deflection region 27.

The tube plate 26 has, in addition to openings in which the tubes 28 and 29 are received and the openings 32 and 33. By means of these, the interior of the housing 22 or of the second flow channel 38 formed in the interior of the housing 22 can be subjected to a fluid or the fluid can be discharged from the interior of the housing 22. For this purpose, the tube plate has a circumferential shoulder, which is guided both around the openings 32, 33 and the tubes 28 and 29. This paragraph comes when placing the housing 22 on an inner wall of the housing for lying and thus serves to seal the housing 22 relative to the tube sheet 26th

In an alternative embodiment, a sealing means may further be provided on this shoulder. Outside this paragraph, the tube plate 26 has a plurality of openings, which can serve for screwing the tube plate 26 to the housing 22 and the connection of fluid connections to the tube plate 26 for supplying the tubes 28 with a first fluid or for the discharge of the first Fluids from the pipes 29.

The deflection region 27, which analogous to the Fig. 2 is formed by a tube plate 23 and a lid 25 inserted into this tubesheet, has on the upwardly directed outer wall turbulence inserts or flow guide elements 34. The turbulence inserts 34 are designed such that the gap which arises between the outer wall of the deflection region 27 and the inner wall of the housing 22 is influenced such that the fluid flow of the second fluid flowing within the housing 22 is optimized. In the region between the deflection region 27 and the inner wall of the housing 22, a flow path 35 is formed. By means of turbulence inserts 34, both the width of this flow path 35 along the deflection region 27 and the propagation of the second fluid within this flow path 35 can be influenced.

For this purpose, the housing 22 as well as the housing 2 of Fig. 1 designed such that at least between the deflection region 27 and the deflection region 7 and the interior of the housing 22 and 2, a sufficiently large gap remains, as Flow path 35 is formed and can be flowed through by the second fluid within the housing 22 and 2 respectively. In addition, the tubes 28 and 29 are also flowed around by the second fluid, whereby along the entire heat exchanger 1, 21, a heat transfer between the first fluid within the tubes 8, 9, 28, 29 of the heat exchanger 1, 21 and the second fluid in the housing 2, 22 of the heat exchanger 1, 21 can take place.

The Fig. 5 shows a further perspective view of a heat exchanger 41, which is arranged within a housing 42. The housing 42 is formed in two parts and has a substantially cuboidal region 42 and a housing part 45 connected thereto or placed on this area. Fluid connections 43 and 44 for feeding or discharging a second fluid into the housing 42 are provided on the cuboid housing part 42 intended. At the lower end of the housing 42, a tube plate 46 of the heat exchanger 41 is indicated.

The Fig. 6 shows a view of the heat exchanger 41, as in the housing 42 of the Fig. 5 is arranged. In the view of Fig. 6 the housing part 42 and the housing part 45 is not shown. The fluid ports 43 and 44 of the housing 42 are further shown.

The heat exchanger 41 has a plurality of first tubes 48 and a plurality of second tubes 49, which analogous to the Fig. 4 and 2 are arranged. The tubes 48 are traversed along the flow direction 50 and form a first section 52 of the first flow channel 55. The tubes 49 are traversed along the flow direction 51 and form a second section 53 of the first flow channel 55.

In an alternative embodiment, the flow direction, as shown in the Fig. 6 and the previous ones Fig. 2 and 4 is implied, and vice versa.

The deflection between the tubes 48 and the tubes 49 takes place along the deflection region 47, which is analogous to the preceding figures formed by a tube plate 56 and a cover 57 inserted therein. Both the tubes 48, 49 and the deflection region 47 can be flowed around by the second fluid, while they are flowed through by the first fluid. For this purpose, the housing 42, 45 forms a second flow channel 54. In this way, a complete heat transfer also takes place both on the tubes 48, 49 and on the deflection region 47.

The Fig. 7 shows a sectional view through a conventional deflected heat exchanger 61, as is known in the art. This has a plurality of tubes 68, which are flowed through along the flow direction 70 and a plurality of tubes 69, which are flowed through along the flow direction 71. The tubes 68, 69 are received in the tube plate 63 in their left-hand region and in the tubesheet 64 at their right-hand end region. The tube plates 63 and 64 are accommodated within the housing 62 in widened regions 65, 66. Advantageously, the tube sheets 64, 64 are welded or soldered to the housing 62.

Within the deflection region 67, which is formed analogously to the preceding figures by a lid inserted into the tubesheet 64, the fluid flow of the first fluid is deflected from the tubes 68 to the tubes 69. This is illustrated with the flow direction 73 within the deflection region 67.

The lid is advantageously inserted within the tube bottom 64 with a sealing element 72. Between the tube sheet 64 and the lid, a positive connection can be generated, alternatively, a cohesive, for example by gluing, soldering, welding.

The in Fig. 7 shown heat exchanger 61 is only flowed through by a first fluid along the tubes 68, 69 and the deflection region 67. The housing 62 can be traversed by a second fluid.

The deflection region 67 is shown in the illustration of Fig. 7 does not flow around a cooling second fluid, so that the heat transfer takes place in the heat exchanger 61 only along the tubes 68 and 69. As a result, the overall heat transfer path is reduced compared to the preceding figures, whereby the total amount of heat transferable is reduced. The deflection region 67 can only be exposed to the surrounding medium, such as the air, whereby both an additional cooling of the first fluid and an unwanted heating of the first fluid can take place.

The Fig. 8 shows a sectional view through a heat exchanger 81. In the Fig. 8 a heat exchanger 81 is shown, as already in the Fig. 5 or 6 is shown. The heat exchanger 81 has a plurality of first tubes 88 and a plurality of second tubes 89, which are flowed through according to the flow direction 90 and 91, respectively. The first tubes 88 form a first section 97 and the second tubes 89 form a second section 98. The two subsections 97, 98 together with a deflection region 87 form a first flow channel 100.

The tubes 88, 89 are received in tube ends 83 and 84 at the ends. The tubes 88 and 89 are surrounded by the housing 82. Between the tubes 88, 89 and the housing 82, a second flow channel 99 is formed, which can be traversed by a second fluid. In the left-hand extended region 86, the tube plate 83 is inserted in the housing 82 in a fluid-tight manner. At the right-hand widened area 95, the housing 82 is connected in a fluid-tight manner to the housing part 85 such that the deflection area 87 and the tube bottom 93 are received within the housing part 85.

Between the housing part 85 and an inner wall of the housing part 85 and an outer wall of the deflection 87, thereby creating the flow path 94, which also, as the space between the tubes 88 and 89 of the second fluid, which flows within the housing 82, can be flowed through along the second flow channel 99.

The flow path 94, as already in Fig. 4 indicated by means which reduce the cross-section, or are designed by turbulence inserts such that an optimal heat exchange between the first fluid in the deflection region 87 and the second fluid in the flow path 94 takes place. In particular, the provision of means for reducing the cross section of the flow path 94 and / or turbulence inserts can influence the resulting pressure loss in the flow path 94.

The deflection region 87 is formed, as in the preceding figures, by a cover 101, which is inserted into the tubesheet 84 and sealed with a sealing agent 93, such that the fluid flow of the first fluid within the deflection region 87 of the fluid flow of the second fluid in the Flow path 94 and within the housing 82 is separated. The deflection within the deflection region 87 takes place along the flow direction 96.

The housings 2, 22, 42, 45, 82 and 85 can be formed both from a plastic and from a metallic material. The corresponding material has to be adapted to the application condition. If the respective housing 2, 33, 43, 45, 82 and 85 flows through a second fluid, the connection between the respective tube plates 6, 16, 23, 26, 46, 56, 83, 84 and the housing 2, 22nd , 42, 82 and the additional housing part 45, 85 be designed so fluid-tight that no leaks to the environment or in the circulation of the first fluid arise.

By an additional flow around the deflection region 7, 27, 47, 87 with a cooling fluid, an increase in the cooling capacity of the heat exchanger 1, 21, 41, 81 overall can be achieved. In this case, particular care should be taken that the resulting pressure loss within the heat exchanger 1, 21, 41, 81 by the measure as possible does not increase or increases only to a small extent. All features of Fig. 1 to 6 and 8th can be combined individually. The embodiments 1 to 6 and 8 have no limiting character. In particular, with regard to the dimensions, the geometries and the arrangement of the individual components to each other and the choice of materials are the Fig. 1 to 6 and 8th by way of example and serve to clarify the inventive idea.

Claims (12)

Heat exchanger (1, 21, 41, 81) with a first flow channel (15, 39, 55, 100), which is traversed by a first fluid, and with a second flow channel (14, 38, 54, 99), of a through which the second flow passage (15, 39, 55, 100) has a first subsection (12, 36, 52, 97), a second subsection (13, 37, 53, 98) and a deflection region, wherein the first subsection with the second subsection about the deflection region (7, 27, 47, 87) is in fluid communication and the first subsection (12, 36, 52, 97), the second subsection (13, 37, 53, 98) and the deflection region (7, 27, 47, 87) are flowed around by the second fluid, characterized in that the first portion (12, 36, 52, 97) and / or the second portion (13, 37, 53, 98) of the first flow channel (15, 39, 55, 100) are each formed by a plurality of tubes (8, 9, 28, 29, 48, 49, 88, 89). Heat exchanger according to claim 1, characterized in that the heat exchanger has a housing (42, 45, 82, 85) which is formed in one or more parts with at least a first housing part (42, 82) and a second housing part (45, 85). Heat exchanger according to claim 2, characterized in that the housing (42, 45, 82, 85) at least partially forms the second flow channel. Heat exchanger according to claim 2, characterized in that the first housing part (42, 82) surrounds the first and second part section and the second housing part (45, 85) surrounds the deflection region (47, 87). Heat exchanger according to one of claims 2 to 4, characterized in that the tube plate (16, 23, 56, 84) with a cover (17, 25, 57, 101) forms a collection box, wherein the inner volume of the header box forms the deflection region (7, 27, 47, 87). Heat exchanger (21, 81) according to any one of claims 2 to 5, characterized in that between the deflection region (27, 87) delimiting outer wall (25, 101) and an inner wall of the housing (22, 82, 85) and / or a Wall of the first flow channel (39,100) is a flow path of the second flow channel (35, 94) is formed, which is traversed by the second fluid. Heat exchanger (21) according to claim 6, characterized in that arranged along the flow path (35) turbulence inserts (34) and / or cross-sectional narrowing means (34) on the outer wall of the deflection region (27) and / or on the inner wall of the housing (22) are. Heat exchanger (21, 41, 81) according to one of claims 2 to 7, characterized in that the housing (22, 42, 45, 82, 85) has a first fluid connection (32, 33, 43, 44) and a second fluid connection ( 32, 33, 43, 44), via which the second fluid in the housing (22, 42, 45, 82, 85) can be supplied and from the housing (22, 42, 45, 82, 85) can be discharged. Heat exchanger (1, 21, 41, 81) according to one of the preceding claims 2 to 7, characterized in that the first section (12, 36, 52, 97) and the second section (13, 37, 53, 98) (15 , 39, 55, 100) and / or the deflection region (7, 27, 47, 87) of the first flow channel in the housing (2, 22, 42, 45, 82, 85), which the second flow channel (14, 38, 54, 99) at least partially forms, can be integrated or integrated such that the second flow channel (14, 38, 54, 99) is fluid-tight with respect to the first flow channel (15, 39, 55, 100) and / or the deflection region (7, 27 , 47, 87) and the environment is sealed. Heat exchanger (1, 21, 41, 81) according to one of the preceding claims, characterized in that all tubes (8, 9, 28, 29, 48, 49, 88, 89) at least at a common end portion in a tube plate (6, 16, 23, 26, 46, 56, 83, 84) are received. Heat exchanger (1, 21, 41, 81) according to any one of the preceding claims, characterized in that the fluid supply and the fluid discharge of the first flow channel (15, 39, 55, 100) at a common end region of the heat exchanger (1, 21, 41, 81) are arranged. Heat exchanger (1, 21, 41, 81) according to any one of the preceding claims, characterized in that the first fluid is a gas and the second fluid is a coolant.

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