Additive manufacturing heat exchanger

Abstract

The invention relates to a heat exchanger (1), in particular for cooling gases, comprising an additive-produced heat exchanger block (2), a plurality of first flow channels (9) for conducting a first fluid being formed in the heat exchanger block (2), said first flow channels running through the heat exchanger block (2), a first chamber (4) is formed on the heat exchanger block (2) at a first transverse end (3), a second chamber (7) is formed on the heat exchanger block (2) at a second transverse end (6), and a plurality of second flow channels (15) for conducting a second fluid are formed in the heat exchanger block (2), said second flow channels being fluidically separated from the first flow channels (9), the second flow channel runs through the heat exchanger block (2) in the block transverse direction (Y) and fluidically connects the first chamber (4) to the second chamber (7). According to the invention, an advantageous distribution of thermal and / or mechanical stresses is produced if a plurality of second flow channels (15) are arranged next to one another in the block longitudinal direction (X) in the heat exchanger block (2) and channel columns (17) are formed, and if a plurality of channel columns (17) are arranged next to one another in the block height direction (Z) in the heat exchanger block (2).

Description

Technical Field

[0001] The invention relates to an additively manufactured heat exchanger for transferring heat between a first fluid and a second fluid in a medium-separated manner, in particular for cooling gases. Background Art

[0002] In additive manufacturing, in particular in three-dimensional printing processes, geometries can be realized that are not achievable with conventional manufacturing methods such as injection molding and metal-cutting processes or can only be realized with great effort. Additive manufacturing can be performed with plastics and with metals.

[0003] The heat exchanger has a heat exchanger block in which heat is transferred between two different fluids in a medium-separated manner. In a conventional construction, the heat exchanger block consists of a plurality of independent components, which are assembled together in a suitable manner. For example, a conventional heat exchanger block comprises a distributor pipe or a distributor box and a collecting pipe or a collecting box, which are fluidically connected to each other via a plurality of connecting pipes. An intermediate space through which flow can be formed is provided between adjacent connecting pipes, in which a thin film can usually be arranged. A first fluid to be heated or cooled is guided through these intermediate spaces. A second fluid to be supplied or conducted away with heat is guided through the connecting pipes. The second fluid is supplied to the connecting pipes via the distributor pipe or the distributor box. The second fluid is conducted away from the connecting pipes via the collecting pipe or the collecting box. During the operation of the heat exchanger, in particular at the transition between the connecting pipe and the distributor pipe or the collecting pipe, thermal stress peaks and / or mechanical stress peaks that the heat exchanger block must withstand are generated. As a result, the heat exchanger block must be oversized in many places. In addition, the heat transfer capacity of the heat exchanger is associated with the surface used for heat transfer. In this case, for example, the number of achievable connection pieces is limited by their manufacturability, the space required and the respective connection technology used (usually soldering methods). Summary of the invention

[0004] The invention addresses the problem of providing an improved or at least a different embodiment for a heat exchanger which is distinguished in particular by an efficient heat transfer, wherein the aim is also to reduce thermal and / or mechanical stress peaks in the heat exchanger block.

[0005] This problem is solved according to the invention by the subject matter of the independent claim. Advantageous embodiments are the subject matter of the dependent claims.

[0006] The present invention is based on the following idea: a heat exchanger block is additively manufactured in such a way that a plurality of first flow channels for guiding a first fluid are constructed in the heat exchanger block, the first flow channels penetrate the heat exchanger block in one direction, for example, in the longitudinal direction of the block or in the transverse direction of the block, so that the first fluid can flow through the heat exchanger block in the first flow channels in the direction defined by these channels. In addition, a first chamber is constructed on the heat exchanger block at a first transverse end, the first chamber extending, for example, in the block height direction. The heat exchanger has a first attachment end for supplying or draining a second fluid. In addition, a second chamber is constructed on the heat exchanger block at a second transverse end, the second transverse end facing away from the first transverse end in the block transverse direction, the second chamber extending in the block height direction. The heat exchanger has a second attachment end for supplying or draining a second fluid. In addition, a plurality of second flow channels for guiding a second fluid are constructed in the heat exchanger block, the second flow channels are fluidically separated from the first flow channels, the second flow channels penetrate the heat exchanger block in the block transverse direction and the second flow channels fluidically connect the first chamber with the second chamber. Here, by additively manufacturing a heat exchanger block, a plurality of second flow channels can be arranged side by side or successively in the longitudinal direction of the block in the heat exchanger block to form a channel column. Then, in the heat exchanger block, a plurality of channel columns are arranged side by side in the block height direction. For example, in a corresponding channel column, at least three, preferably at least five, and in particular at least ten connecting channels can be arranged side by side in the longitudinal direction of the block. Compared with a conventionally manufactured heat exchanger block (in which a maximum of two connecting pipes are arranged side by side in the longitudinal direction of the block), the construction method proposed here produces an extreme increase in the surface available for heat transfer under the same structural space requirement. In addition, in the case of the additive construction method, more material in the heat exchanger block is available for heat transfer because the second flow channels and the first flow channels are guided through the material of the heat exchanger block. In contrast, in the case of the conventional construction method, the material of the heat exchanger block is formed only by the tube walls of the connecting pipes and the walls of the thin sheets that may be arranged between the connecting pipes. Therefore, in the additively manufactured heat exchanger block, more material is available for heat transfer.

[0007] In the conventional production of heat exchanger blocks, the connecting pipes penetrate the side walls that bound the distributor pipe or the distributor box or the collecting pipe or the collecting box and thereby protrude into the interior of the distributor pipe / distributor box or the collecting pipe / collecting box and form a flow obstruction there. In additive manufacturing, however, this type of protrusion is not required, thereby significantly reducing the flow resistance of the heat exchanger to the second fluid.

[0008] Heat exchangers of this type may be used, for example, at hydrogen filling stations in order to cool the hydrogen when filling vehicle tanks.

[0009] According to an advantageous embodiment, the heat exchanger block has a block longitudinal center plane extending transversely to the block longitudinal direction, which extends through the heat exchanger block centrally relative to the block longitudinal direction. In addition, the connecting channels can be configured with respect to their flow resistance in such a way that in the respective channel columns, the magnitude of the flow resistance of the respective second flow channels is associated with the distance of the respective second flow channels from the block longitudinal center plane, so that the flow resistance of the second flow channels having a greater distance from the block longitudinal center plane is greater than the flow resistance of the second flow channels having a smaller distance from the block longitudinal center plane. This measure makes it possible that during operation of the heat exchanger, the volume flow of the second fluid is distributed in different ways to the second flow channels in the respective channel columns in such a way that the volume flow flowing through the second flow channels in the region of the block longitudinal center plane is greater than the volume flow in the second flow channels spaced apart from the block longitudinal center plane, wherein the volume flow further decreases with increasing distance from the block longitudinal center plane. Stress peaks can thereby be reduced. This design makes use of the knowledge that the thermal and / or mechanical stresses at the transition between the second flow channel and the first and / or second chamber, in particular the distributor chamber and / or the collecting chamber, are linked to the distance from the longitudinal center plane of the block. These stresses increase with increasing distance from the longitudinal center plane of the block. By reducing the flow rate, the stresses in the longitudinal direction of the block can be homogenized.

[0010] In the present context, "configured" is synonymous with "configured", so the expression "configured so as to be" is synonymous with the expression "configured so as to be".

[0011] Here, the following embodiment is particularly suitable: the second flow channel is configured in terms of its flow-through cross-sectional area so that in the corresponding channel column, the size of the flow-through cross-sectional area of ​​the corresponding second flow channel is associated with the distance between the corresponding second flow channel and the longitudinal center plane of the block, more precisely, so that the flow-through cross-sectional area of ​​the second flow channel with a larger distance from the longitudinal center plane of the block is smaller than the flow-through cross-sectional area of ​​the second flow channel with a smaller distance from the longitudinal center plane of the block. The flow resistance of the corresponding second flow channel is associated with the flow-through cross-sectional area of ​​the corresponding second flow channel. The larger the flow-through cross-sectional area, the smaller the flow resistance. Therefore, the flow resistance can be particularly easily influenced by the flow-through cross-sectional area. Alternatively, the flow resistance of the second flow channel can also be influenced by other measures. For example, in the framework of additive manufacturing, flow obstacles such as obstructions, flow guide surfaces, ribs and cams can be added to the second flow channel that should have a higher flow resistance.

[0012] The heat exchanger block has a middle transverse region, which is spaced apart from the first transverse end and from the second transverse end, and which transitions into the first chamber via a first transition region on the first transverse end and into the second chamber via a second transition region on the second transverse end. Preferably, the configuration of the second flow channel described above in terms of its flow-through cross-sectional area is applicable at least in the middle transverse region, because there, over the length of the second flow channel measured in the transverse direction of the block, the greatest influence on the flow resistance occurs. Suitably, the configuration of the second flow channel described above in terms of its flow-through cross-sectional area is also applicable in the first transition region, which connects the first chamber to the middle transverse region. Optionally, the configuration of the second flow channel described above in terms of its flow-through cross-sectional area can also be applied in the second transition region, which connects the middle transverse region to the second chamber.

[0013] According to an advantageous embodiment, the first chamber can form or have a distributor chamber, which supplies the second fluid to the second flow channel, wherein the first attachment end forms a supply attachment end for supplying the second fluid to the distributor chamber. The heat exchanger block can have a block longitudinal center plane extending transversely to the block longitudinal direction, and the block longitudinal center plane extends centrally through the heat exchanger block relative to the block longitudinal direction. In addition, the second flow channel can have an inlet opening on the distributor chamber, which has a round inlet cross section through which flow can flow. These round inlet cross sections have a longitudinal diameter measured in the longitudinal direction of the block and a height diameter measured in the height direction of the block. Now, the second flow channel can be configured in terms of its inlet cross section so that in the corresponding channel column, the size of the longitudinal diameter of the inlet cross section of the inlet opening of the corresponding second flow channel is associated with the distance between the corresponding second flow channel and the block longitudinal center plane, more precisely, so that the longitudinal diameter of the inlet cross section of the second flow channel with a larger distance from the block longitudinal center plane is greater than the longitudinal diameter of the inlet cross section of the second flow channel with a smaller distance from the block longitudinal center plane. In other words, the inlet cross section of the inlet opening becomes increasingly larger with increasing distance from the longitudinal center plane of the block. This measure helps to reduce thermal and / or mechanical stress peaks.

[0014] In this case, a configuration is advantageous in which, in all inlet openings, the longitudinal diameter of the inlet cross section is at least the same size as the height diameter. In particular, the inlet cross section can be circular or oval.

[0015] According to an advantageous embodiment, the height diameter of the inlet cross section of the corresponding second flow channel can be of the same size in all second fluid channels of the corresponding channel column. Thus, the inlet cross section of the inlet opening of the second flow channel spaced apart from the block longitudinal center plane is flat or elongated. In addition, the inlet cross section of the inlet opening of the flow channel arranged in the region of the block longitudinal center plane can be circular, while the inlet cross section of the inlet opening of the second flow channel spaced apart from the block longitudinal center plane is elliptical, wherein the elliptical cross section becomes increasingly flat or elongated as the spacing of the second flow channel from the block longitudinal center plane increases.

[0016] According to another embodiment, it can be provided that the second chamber can form or have a collecting chamber which receives the second fluid from the second flow channel, wherein the second attachment end then forms a discharge attachment end for discharging the second fluid from the collecting chamber.

[0017] Preferably, the above statements for the transition between the distributor chamber and the second flow channel also apply to the transition from the second flow channel to the collecting chamber. Therefore, preferably, the second flow channel has an outlet opening on the collecting chamber, which outlet opening has a circular outlet cross section, wherein the outlet cross section has a longitudinal diameter measured in the longitudinal direction of the block and a height diameter measured in the height direction of the block. Preferably, the second flow channel is now configured in terms of its outlet cross section so that in the corresponding channel column, the size of the longitudinal diameter of the outlet cross section of the corresponding second flow channel is associated with the spacing of the corresponding second flow channel from the longitudinal center plane of the block, so that the longitudinal diameter of the outlet cross section of the second flow channel with a larger spacing from the longitudinal center plane of the block is larger than the longitudinal diameter of the outlet cross section of the second flow channel with a smaller spacing from the longitudinal center plane of the block. Preferably, it can also be provided that in all second fluid channels in the corresponding channel column, the height diameter of the outlet cross section of the corresponding second flow channel is the same size. Preferably, it is also applicable here that the longitudinal diameter is the same size as the height diameter or is larger than the height diameter. Thus, the outlet cross section in the region of the block longitudinal center plane can be particularly circular, while the outlet cross section spaced apart from the block longitudinal center plane can be elliptical, wherein the elliptical cross section becomes increasingly flatter or more elongated with increasing distance from the block longitudinal center plane.

[0018] According to an advantageous embodiment, the heat exchanger block can have an intermediate transverse region which is spaced apart from the first transverse end and from the second transverse end. The second flow channel has a flow-through cross-sectional area and can be configured such that its flow-through cross-sectional area decreases from the first opening which flows into the first chamber to the intermediate transverse region and / or increases from the intermediate transverse region to the second opening which flows into the second chamber. In other words, the second flow channel has a variable flow-through cross-sectional area in the direction of the block height. As a result, thermal and / or mechanical stress peaks at the transition between the connecting channel and the first chamber and / or the second chamber can be reduced.

[0019] According to an advantageous embodiment, the heat exchanger block can have an intermediate transverse region which is spaced apart from the first transverse end and from the second transverse end. In addition, the heat exchanger block has a first transition region at the first transverse end and a second transition region at the second transverse end, the first transition region connecting the first chamber to the intermediate transverse region and the second transition region connecting the second chamber to the intermediate transverse region. In addition, the heat exchanger block has a block longitudinal center plane extending transversely to the longitudinal direction of the block. Now, the second flow channel can be configured in such a way that the second flow channel extends parallel to the transverse direction of the block in the intermediate transverse region. In addition, the second flow channel can be configured in such a way that the second flow channel spaced apart from the longitudinal center plane of the block extends obliquely relative to the transverse direction of the block in the first transition region and / or in the second transition region, wherein the inclination increases from the intermediate transverse region to the first chamber and / or to the second chamber. Thus, for the second flow channel, a fan-shaped run is generated in the corresponding transition region. It has been shown that by this type of construction, thermal stress peaks and / or mechanical stress peaks in the corresponding transition region can be reduced.

[0020] According to an advantageous embodiment, the heat exchanger block has a middle transverse region which is spaced apart from the first transverse end and from the second transverse end, wherein the heat exchanger block has a first transition region at the first transverse end and a second transition region at the second transverse end, the first transition region connecting the first chamber to the middle transverse region and the second transition region connecting the second chamber to the middle transverse region. In addition, the heat exchanger block has a block longitudinal center plane extending transversely to the block longitudinal direction. Advantageously, the second flow channels can now be configured in such a way that at least those second flow channels spaced apart from the block longitudinal center plane or facing away from the block longitudinal center plane have a geometrically varying opening cross section in the first transition region and / or in the second transition region along the block transverse direction. The second flow channels facing away from the block longitudinal center plane are those second flow channels which have the greatest spacing from the block longitudinal center plane within the corresponding channel longitudinal row. By means of the geometrically varying opening cross section, thermal and / or mechanical stress peaks in the corresponding transition region can be reduced.

[0021] According to an advantageous development, at least those second flow channels which are spaced apart from the block longitudinal center plane or face away from the block longitudinal center plane can have an opening cross section which is geometrically constant in the block transverse direction in the middle transverse region. In other words, the opening cross section of the second flow channels is constant in the block transverse direction in the middle transverse region, while the opening cross section changes in the two transition regions.

[0022] In principle, the following embodiment is preferred: in this embodiment, the second flow channels of the respective channel columns extend independently from the first chamber to the second chamber and have independent inlet openings or outlet openings there. In contrast, in another embodiment, it can be provided that the second flow channels of the respective channel columns extend independently of one another at least in a middle transverse region of the heat exchanger block spaced apart from the first transverse end and from the second transverse end, while the second flow channels merge into a common channel in a first transition region of the heat exchanger block to the first chamber and / or in a second transition region of the heat exchanger block to the second chamber.

[0023] According to another advantageous development, at least the second flow channel spaced apart from the block longitudinal center plane or facing away from the block longitudinal center plane can have an elliptical opening cross section in the first opening that flows into the first chamber, the elliptical opening cross section is elongated in the block longitudinal direction, and the elliptical opening cross section changes into a circular opening cross section in the first transition region along the block transverse direction until the middle transverse region. Additionally or alternatively, at least the second flow channel spaced apart from the block longitudinal center plane or facing away from the block longitudinal center plane can have an elliptical opening cross section in the second opening that flows into the second chamber, the elliptical opening cross section is elongated in the block longitudinal direction, and the elliptical opening cross section changes into a circular opening cross section in the second transition region along the block transverse direction until the middle transverse region. Thus, in particular, the elliptical first opening can be transformed into a circular opening cross section in the first transition region, the circular opening cross section in particular remains constantly circular in the middle transverse region, and the circular opening cross section can be transformed into an elliptical second opening again in the second transition region. The use of a circular cross section, in particular an elliptical and a circular cross section, in the second flow channel reduces thermal and / or mechanical stresses.

[0024] According to another advantageous embodiment, it can be provided that the first chamber forms or has a distributor chamber, which supplies the second fluid to the second flow channel, wherein the first attachment end forms a supply attachment end for supplying the second fluid to the distributor chamber. In this case, the distributor chamber can have a profile that extends transversely to the block height direction and is concavely curved toward the inside of the distributor chamber on the distributor side facing the connecting channel. Additionally or alternatively, in one embodiment, the second chamber forms or has a collection chamber, which receives the second fluid from the second flow channel, and the second attachment end forms a lead-out attachment end for leading the second fluid from the collection chamber, in which embodiment, it can be optionally provided that the collection chamber has a profile that extends transversely to the block height direction and is concavely curved toward the inside of the collection chamber on the collection side facing the connecting channel. By means of the curved or bent profile on the distributor side of the distributor chamber or on the collection side of the collection chamber, thermal stress peaks and / or mechanical stress peaks can be reduced.

[0025] Alternatively, the second flow channel whose geometric cross section changes in the block transverse direction can be configured in such a way that the cross-sectional area through which flow can flow is constant or remains constant in the block transverse direction.

[0026] In an advantageous embodiment, it can be provided that in a plurality or all of the first and / or second flow channels, the ribs or projections protrude into the cross section through which flow can flow, so that the ribs or projections can be flowed against and / or around by the second fluid. This makes it possible to increase the surface available for heat transfer in the corresponding connecting channel.

[0027] According to an advantageous embodiment, the ribs can be configured helically so that they extend helically along the corresponding second flow channel in the block transverse direction or along the corresponding first flow channel in the block longitudinal direction or in the block transverse direction. The helical ribs increase the surface available for heat transfer and are distinguished by a relatively low flow resistance.

[0028] According to an advantageous embodiment, the first and / or second chamber can have a recess on the inner side exposed to the second fluid, for increasing the surface of the inner side. In particular, if the heat exchanger is used in a refrigeration circuit and forms an evaporator therein, these recesses can significantly improve the evaporation of the refrigerant. This type of recess is also referred to as a re-entry cavity.

[0029] According to an advantageous embodiment, a plurality of or all second flow channels can have a recess on their inner side exposed to the second fluid, at least in the transition region of the heat exchanger block adjoining the first or second tank, in order to increase the surface of the inner side. This measure also improves the heat transfer and supports the evaporation of the second fluid when used as an evaporator.

[0030] The following embodiment is particularly advantageous: in this embodiment, the recess has a narrowing at the transition to the inside, so that the cross section of the corresponding recess extending transversely to the normal direction of the inside is larger in the corresponding recess than in the narrowing. The narrowing thus forms an undercut. With conventional manufacturing methods, this type of recess or undercut cannot be manufactured or can only be manufactured with great difficulty. It has been shown that a recess with such a narrowing significantly supports the boiling characteristics of the second fluid and improves the efficiency of the heat exchanger used as an evaporator.

[0031] According to an advantageous embodiment, the heat exchanger can be designed as a cooler for cooling a first fluid by means of a second fluid, wherein the first fluid is a liquid coolant and the second fluid is a liquid or a gas.

[0032] Alternatively, the heat exchanger can also be designed as an evaporator for cooling a first fluid by means of a second fluid, wherein the first fluid is a two-phase refrigerant and the second fluid is a liquid or a gas. The refrigerant is two-phase because it is to be evaporated in the evaporator so that it is predominantly liquid at the supply attachment and predominantly gaseous at the discharge attachment.

[0033] As described above, according to a preferred embodiment, it can be provided that the first chamber forms a distributor chamber and has a first attachment end, which subsequently forms a supply attachment end. Then, the second chamber forms a collection chamber and has a second attachment end, which forms a lead-out attachment end. The distributor chamber and the collection chamber are fluidically connected to each other via a second flow channel. Therefore, the second fluid flows through the heat exchanger block once in the transverse direction of the block, that is, from the distributor chamber to the collection chamber through the second flow channel. On the contrary, in another embodiment, it can be provided that the first chamber forms or has a distributor chamber and a collection chamber, wherein the first attachment end is then constructed on the distributor chamber and forms a supply attachment end, and the second attachment end is constructed on the collection chamber and forms a lead-out attachment end. In this case, the second chamber forms a steering chamber. The steering chamber is fluidically connected to the distributor chamber and to the collection chamber via the second flow channel. Thus, in this configuration, the second fluid flows through the heat exchanger block twice, namely from the distributor chamber through the first set of second flow channels to the diverting chamber and from the diverting chamber through the second set of second flow channels to the collecting chamber.

[0034] Particularly advantageous is an embodiment in which the heat exchanger is designed as a cross-flow heat exchanger, i.e. in which the first flow channel and the second flow channel are guided through the heat exchanger block according to a cross-flow concept, i.e. cross or cross therein in a media-separated manner. Thus, the first flow channel passes through the heat exchanger block in the longitudinal direction of the block and fluidically connects the inflow side of the heat exchanger block exposed to the first fluid with the outflow side of the heat exchanger block exposed to the first fluid.

[0035] According to an advantageous embodiment, in a heat exchanger block, a plurality of first flow channels can be arranged side by side in the transverse direction of the block and can form channel rows. Then, in the heat exchanger block, a plurality of channel rows are arranged side by side in the block height direction. The heat exchanger block has an intermediate height region, which is spaced apart from lateral block ends facing away from each other in the block height direction. Now, the channel rows can be guided through the heat exchanger block at least in the intermediate height region of the heat exchanger block, respectively, between two adjacent channel longitudinal rows. Thus, an extremely compact construction is produced, which has a very large surface for contact with the first fluid and with the second fluid. In a conventional construction, the heat exchanger block has only one flow-through intermediate space between two adjacent connecting pipes, in which a thin sheet can be arranged for surface enlargement, while in the additively manufactured heat exchanger block, a plurality of, preferably more than ten, in particular more than twenty, first flow channels can be arranged side by side in the transverse direction of the block to form corresponding channel rows.

[0036] As an alternative to the cross-flow construction, in another embodiment it can be provided that the heat exchanger is configured as a parallel flow heat exchanger, i.e. in the case of said parallel flow heat exchanger, the first flow channel and the second flow channel are guided through the heat exchanger block according to a parallel flow scheme, i.e. extend parallel to each other therein in a medium-separated manner. Thus, the first flow channel passes through the heat exchanger block in the block transverse direction. In this case, it can be provided in particular that in the heat exchanger block, the first flow channel and the second flow channel alternate in the block height direction and / or in the block longitudinal direction. This can improve the efficiency of the heat transfer.

[0037] According to an advantageous embodiment, it can be provided that the first chamber has or forms a first subchamber and a second subchamber, wherein the first subchamber is fluidically connected to the first flow channel and the second subchamber is fluidically connected to the second flow channel. It can also be provided that the second chamber has or forms a third subchamber and a fourth subchamber, wherein the third subchamber is fluidically connected to the first flow channel and the fourth subchamber is fluidically connected to the second flow channel. Preferably, each subchamber can have its own attachment end for supplying or discharging the first or second fluid. This allows a particularly compact design.

[0038] The following configuration is particularly advantageous: in this configuration, the first subchamber forms a collecting chamber for the first flow channel and has a discharge attachment end for the first fluid, in this configuration, the second subchamber forms a distributor chamber for the second flow channel and has a supply attachment end for the second fluid, in this configuration, the third subchamber forms a distributor chamber for the first flow channel and has a supply attachment end for the first fluid, in this configuration, the fourth subchamber forms a collecting chamber for the second flow channel and has a discharge attachment end for the second fluid. This configuration also supports a compact construction form.

[0039] Furthermore, in the configuration as a parallel flow heat exchanger, it can be provided that all first and second flow channels extend parallel to one another in the middle transverse region, while a plurality or all first and second flow channels cross or span in a medium-separated manner in the first transition region to the first and second subchambers and / or in the second transition region to the third and fourth subchambers. This also supports efficient heat transfer in a compact design.

[0040] If the heat exchanger is designed as a parallel flow heat exchanger, all the above-mentioned configurations and features relating to the second flow channel can also be implemented in a corresponding manner in the first flow channel. This applies in particular to the geometric configuration of the openings that merge into the corresponding chambers or subchambers and / or to the cross-sections that allow flow in the flow channel in the longitudinal direction of the block and in the case of adjacent flow channels, which vary in the longitudinal direction of the block. Thus, in particular, the first flow channel in the heat exchanger block can also be configured with a plurality of channel rows of first flow channels that are adjacent in the longitudinal direction of the block, wherein a plurality of such channel rows are adjacent in the direction of the block height.

[0041] Further important features and advantages of the invention emerge from the dependent claims, the drawings and the associated description of the figures based on the drawings.

[0042] It is obvious that the features mentioned above and to be explained below can be used not only in the respectively given combination but also in other combinations or independently without departing from the framework of the invention defined by the claims. The individually marked components mentioned above and still to be mentioned below of a superordinate unit (such as an apparatus, device or component) can form independent components or parts of the unit or can be integral regions or sections of the unit, even if this is shown in a different way in the drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Preferred exemplary embodiments of the invention are shown in the drawings and are explained in more detail in the following description, wherein identical reference numerals refer to identical or similar components or components having the same function.

[0044] The accompanying drawings schematically show:

[0045] Figure 1 shows a greatly simplified side view of a heat exchanger,

[0046] Figure 2 A cutaway isometric view showing the heat exchanger in the region of the distributor chamber,

[0047] Figure 3 A cutaway isometric view showing the heat exchanger in the region of the collecting chamber,

[0048] Figure 4 Show Figure 2 Zoomed in detail in IV,

[0049] FIG. 5 shows a greatly simplified cross section of a second flow channel at the inlet opening or outlet opening in the case of different flow channels A and B,

[0050] FIG. 6 shows a cross section as in FIG. 5 , but in another embodiment,

[0051] FIG. 7 shows different views of the second flow channel in the transition region in different viewing directions A, B, C,

[0052] Figure 8 an isometric view showing a plurality of second flow channels in the transition region,

[0053] Fig. 9 an isometric view showing a longitudinal section of a second flow channel or a first flow channel having ribs,

[0054] Fig.10 shows a greatly simplified sectional view in the region of the depression,

[0055] Fig.11 A greatly simplified cross-sectional view showing a heat exchanger in an embodiment with cross-flow,

[0056] Fig.12 A greatly simplified cross-sectional view showing a heat exchanger in an embodiment with parallel flow,

[0057] Fig.13 A greatly simplified sectional view of a heat exchanger in the region of the chamber is shown in another embodiment. DETAILED DESCRIPTION

[0058] according to Figure 1 , the additively manufactured heat exchanger 1 comprises an additively manufactured heat exchanger block 2 having a block longitudinal direction X, a block transverse direction Y and a block height direction Z extending perpendicularly to each other. Figure 1 In FIG. 1 , the block longitudinal direction X extends perpendicular to the drawing plane, while the block transverse direction Y extends vertically and the block height direction Z extends horizontally.

[0059] On the heat exchanger block 2, a first chamber 4 is configured at the first transverse end 3, the first chamber extending longitudinally in the block height direction Z and having a first attachment end 5. In the example shown here, the first chamber 4 forms a distributor chamber 4 and the first attachment end 5 forms a supply attachment end 5. In addition, on the heat exchanger block 2, a second chamber 7 is configured at the second transverse end 6, the second transverse end facing away from the first transverse end 3 in the block transverse direction Y, the second chamber extending longitudinally in the block height direction Z and having a second attachment end 8. In the example shown here, the second chamber 7 forms a collecting chamber 7 and the second attachment end 8 forms a discharge attachment end 8.

[0060] according to Figures 1 to 3In the heat exchanger block 2, a plurality of first flow channels 9 for guiding the first fluid are configured. The first flow channels penetrate the heat exchanger block 2 in the block longitudinal direction X, and the first flow channels fluidically connect an inlet side 10 of the heat exchanger block 2 exposed to the first fluid with an outlet side 12 exposed to the first fluid. The inlet side is located at the heat exchanger block 2. Figures 1 to 3 The outflow side is located at the first longitudinal end 11 facing the observer in the heat exchanger block 2. Figures 1 to 3 At the second longitudinal end 13 facing away from the observer. Figure 2 and 3 In FIG. 1 , the flow of the first fluid through the heat exchanger block 2 or the first flow channel 9 which occurs during the operation of the heat exchanger 1 is indicated by arrows and referenced by 14 .

[0061] according to Figure 2 and 3 In addition, a plurality of second flow channels 15 for conducting a second fluid are formed in the heat exchanger block 2, which are fluidically separated from the first flow channels 9. The second flow channels 15 penetrate the heat exchanger block 2 in the block transverse direction Y and fluidically connect the distributor chamber 4 to the collecting chamber 7. Figures 1 to 3 In FIG. 1 , the flow of the second fluid through the heat exchanger block 2 or the distributor chamber 4 , the connecting pipe 15 and the collecting chamber 7 which occurs during the operation of the heat exchanger 1 is indicated by arrows and is denoted by 16 .

[0062] according to Figure 2 and 3 In the heat exchanger block 2, a plurality of second flow channels 15 are arranged side by side in the block longitudinal direction X and form channel columns 17. In the example shown, each channel column 17 contains ten second flow channels 15. In the heat exchanger block 2, a plurality of channel columns 17 are arranged side by side in the block height direction Z. For example, Figure 2 and 3 In each of the figures nine such channel rows 17 can be seen. It is clear that in a heat exchanger block 2 a plurality of channel rows 17 can be arranged next to each other in the block height direction Z, for example more than fifty.

[0063] The heat exchanger block 2 has a block longitudinal center plane 18 which is located at Figure 2 and 3 Indicated by a dashed line in FIG. 1 , the longitudinal center plane of the block extends transversely to the longitudinal direction X of the block. Figure 4, the second flow channels 15 have a first opening 19 and a round inlet cross section 43 through which flow can flow, which first opening forms the inlet opening 19. These inlet cross sections 43 have a longitudinal diameter 20 measured in the block longitudinal direction X and a height diameter 21 measured in the block height direction Z. The second flow channels 15 are now configured with respect to their inlet cross sections 43 such that in the respective channel row 17 the size of the longitudinal diameter 20 is correlated with the distance of the respective second flow channel 15 from the block longitudinal center plane 18, more precisely such that the longitudinal diameter 20 of the inlet cross section 43 of the second flow channel 15 which is at a greater distance from the block longitudinal center plane 18 is greater than the longitudinal diameter of the inlet cross section of the second flow channel 15 which is at a smaller distance from the block longitudinal center plane 18. Purely by way of example, this transition from a larger longitudinal diameter 20 to a smaller longitudinal diameter 20 is shown in FIG. 5 . Figure 5A The inlet cross section 43 of the inlet opening 19 of the second flow channel 15 is shown, which is spaced relatively far apart from the block longitudinal center plane 18. In contrast, Figure 5B The inlet cross section 43 of the inlet opening 19 of the second flow channel 15 which is relatively close to the block longitudinal center plane 18 is shown. It can be seen that the longitudinal diameter 20 increases with increasing distance from the block longitudinal center plane 18. The corresponding transition is indicated by an arrow in FIG. 5 and is denoted by 22. In the example shown, it can also be provided that the inlet cross section 43 of the inlet opening 19 is of the same size, i.e. remains constant, in all second flow channels 15 of the corresponding channel column 17.

[0064] Optionally, the same may also apply in the region of the collecting chamber 7. Figure 4 and 5 illustrate this relationship. Figure 4 If the chamber shown in the figure is a collecting chamber 7, the inlet opening of the second flow channel 15 is not the inlet opening 19, but the second opening 23 or the outlet opening 23, whose outlet cross section 44 also has the longitudinal diameter 20 and the height diameter 21. Then, the second flow channel 15 is configured in its outlet cross section 44 in such a way that in the corresponding channel column 17, the size of the longitudinal diameter 20 is related to the distance of the corresponding second flow channel 15 from the block longitudinal center plane 18 in such a way that the longitudinal diameter 20 of the outlet cross section 44 of the second flow channel 15 with a larger distance from the block longitudinal center plane 18 is larger than the longitudinal diameter of the outlet cross section of the second flow channel 15 with a smaller distance from the block longitudinal center plane 18. Here, it is also possible to Figure 5A and Figure 5B It is provided that in all second flow channels 15 of a respective channel row 17 the height diameter 21 of the outlet cross section 44 is of the same size.

[0065] In the example of FIG. 5 , in the second flow channel 15 arranged close to the block longitudinal center plane 18 , the corresponding cross-sections 43 , 44 at the inlet opening 19 or at the outlet opening 23 are circular, whereas in the second flow channel 15 spaced apart from the block longitudinal center plane 18 , the corresponding cross-sections 43 , 44 at the inlet opening 19 or at the outlet opening 23 are elliptical.

[0066] In another embodiment explained in conjunction with FIG. 6 , the second flow channels 15 can be configured with respect to their flow resistance in such a way that in the respective channel row 17 the magnitude of the flow resistance of the respective second flow channel 15 is correlated with the distance of the respective second flow channel 15 from the block longitudinal center plane 18, more precisely in such a way that the flow resistance of the second flow channel 15 at a greater distance from the block longitudinal center plane 18 is greater than the flow resistance of the second flow channel 15 at a smaller distance from the block longitudinal center plane 18. It is conceivable that the flow resistance of the second flow channel 15 is increased by an obstacle, which is formed in the second flow channel 15 for this purpose. In this case, this embodiment can be combined with the embodiment described above, in which the longitudinal diameter 20 changes when the second flow channels 15 are adjacent in the block longitudinal direction X.

[0067] Combination Fig. 6A and 6B , another embodiment is further described in detail, in which the flow resistance of the corresponding second flow channel 15 is changed by means of the flow-through cross-sectional area 24 of the corresponding second flow channel 15. Fig. 6A and 6B In the example of , the second flow channels 15 each have a circular, flow-through cross-section 45. It can now be advantageously provided that in the respective channel row 17, the size of the flow-through cross-sectional area 24 of the respective second flow channel 15 is linked to the distance of the respective second flow channel 15 from the block longitudinal center plane 18, more precisely in such a way that the flow-through cross-sectional area 24 of the second flow channel 15 at a greater distance from the block longitudinal center plane 18 is smaller than the flow-through cross-sectional area of ​​the second flow channel 15 at a smaller distance from the block longitudinal center plane 18. Fig. 6A The cross-sectional area 24 through which the flow can pass is shown, which is at a relatively large distance from the block longitudinal center plane 18, while Figure 6B The cross-sectional area 24 through which flow can flow is shown for a second flow channel 15 at a relatively small distance from the block longitudinal center plane 18. It can be seen that the cross-sectional area 24 through which flow can flow decreases significantly with increasing distance from the block longitudinal center plane 18. The corresponding transition is indicated in FIG. 6 by arrows and is denoted by 25.

[0068] according to Figure 1, the heat exchanger block 2 has a middle transverse region 26 which is spaced apart from the first transverse end 3 and from the second transverse end 6. Furthermore, the heat exchanger block 2 has a first transition region 27 which connects the middle transverse region 26 to the distributor chamber 4. Furthermore, the heat exchanger block 2 has a second transition region 28 which connects the middle transverse region 26 to the collecting chamber 27.

[0069] According to the relationship described above, the cross-sectional area 24 through which the flow can flow of the respective second flow channel 15 decreases as the distance of the respective second flow channel 15 from the block longitudinal center plane 18 increases, which relationship applies at least to the middle transverse region 26 of the heat exchanger block 2. Preferably, this relationship also applies in the first transition region 27 and / or in the second transition region 28.

[0070] In principle, the second flow channel 15 can be configured such that its through-flow cross-sectional area 24 decreases from the inlet opening 19 opening at the distributor chamber 4 to the middle transverse region 26 and / or increases from the middle transverse region 26 to the outlet opening 23 opening at the collecting chamber 7. Preferably, it can be provided that in the second flow channel 15, the through-flow cross-sectional area 24 decreases from the inlet opening 19 in a first transition region 27 to the middle transverse region 26, is constant in the middle transverse region 26, and increases from the middle transverse region 26 to the outlet opening 23, i.e. in the second transition region 28. By reducing the cross section in the middle transverse region 26, in particular, the through-flow resistance of the second flow channel 15 can also be varied.

[0071] In contrast, in an alternative embodiment, provision can be made for the second flow channel 15 to have a constant flow-through cross-sectional area 24 from the inlet opening 19 to the outlet opening 23 , wherein the geometric flow-through cross section 45 or the opening cross section 45 can be constant or variable.

[0072] according to Figure 2 and 3 Optionally, the second flow channel 15 can also be configured such that the second flow channel 15 spaced apart from the block longitudinal center plane 18 or facing away from the block longitudinal center plane extends obliquely in the first transition region 27 or in the second transition region 28 relative to the block transverse direction Y. Figure 2 and 3, for each second flow channel 15 facing away from the block longitudinal center plane 18, i.e. at the greatest distance from the block longitudinal center plane 18 within the respective channel row 17, a longitudinal center axis 29 is drawn, by way of example and representatively for all other second flow channels 15, which the respective second flow channel 15 has in its inlet opening 19 or in its outlet opening 23. This longitudinal center axis 29 has an inclination angle 30 or a slope 30 with respect to the block transverse direction Y. Now, the embodiment shown here is particularly advantageous in which the slope 30 increases from the middle transverse region 26 in the first transition region 27 to the distributor chamber 4 and from the middle transverse region 26 to the collecting chamber 7 in the second transition region 28. As a result, the second flow channels 15 are distributed over a larger area in the block longitudinal direction X on the distributor chamber 4 and in the collecting chamber 7 than in the middle transverse region of the heat exchanger block 2.

[0073] 7 and 8 show the second flow channel 15 or the wall material of the heat exchanger block 2, which delimits the second flow channel 15, more precisely optionally in the first transition area 27 to the distributor chamber 4 or in the second transition area 28 to the collecting chamber 7. Fig. 7A An isometric view of the second flow channel 15 is shown. Figure 7B A side view of the second flow channel 15 in a viewing direction extending parallel to the block height direction Z is shown. Figure 7C A side view of the second flow channel 15 in a viewing direction extending parallel to the block longitudinal direction X is shown. Figure 8 An isometric view of a plurality of second flow channels 15 is shown, which are arranged next to each other in the block height direction Z. In this case, Figures 7 and 8 each show a second flow channel 15 which is at a relatively large distance from the block longitudinal center plane 18. In particular, this can be the second flow channel 15 which is the farthest away from the block longitudinal center plane 18 in each case.

[0074] Expediently, the second flow channels 15 can now be configured such that those second flow channels 15 which are spaced apart from the block longitudinal center plane 18 or face away from it have a geometrically varying opening cross section 45 in the first transition region 27 or in the second transition region 28 along the block transverse direction Y. Furthermore, the second flow channels 15 can be configured such that they have a geometrically constant opening cross section 45 in the middle transverse region 26 along the block transverse direction Y. In the example of FIGS. 7 and 8 , the second flow channels 15 have an elliptical opening cross section 45 in their inlet opening 19, which is elongated in the block longitudinal direction X, i.e., as Figure 5AAs shown, in the block longitudinal direction X, it has a larger longitudinal diameter 20. Then, this elliptical opening cross section 45 transforms into a circular opening cross section 45 in the first transition region 27 along the block transverse direction Y up to the middle transverse region 26. In FIGS. 7 and 8, this circular opening cross section 45 is respectively located at the lower end of the illustrated section of the second flow channel 15. Purely by way of example, in Figure 5B , 6A 6B shows a circular cross section 45. Optionally, the same also applies in the second transition region 28. In this case, the second flow channel 15 has an elliptical opening cross section 45 in its outlet opening 23 that opens into the collecting chamber 7, which is elongated in the block longitudinal direction X and which transforms into a circular opening cross section 45 in the second transition region 28 along the block transverse direction Y up to the middle transverse region 26.

[0075] according to Figure 2 and Figure 4 The distributor chamber 4 has a contour on the distributor side 31 facing the second flow channel 15, which extends transversely to the block height direction Z and is curved concavely toward the interior of the distributor chamber 4. The inlet opening 19 is located in the distributor side 31. Figure 3 and 4 , the collecting chamber 7 has a profile on the collecting side 32 facing the second flow channel 15, which extends transversely to the block height direction Z and is concavely curved toward the interior of the collecting chamber 7. The outlet opening 23 is located in the collecting side 32. Through this structural form, a flow-favorable transition from the distributor chamber 4 into the second flow channel 15 and from the second flow channel 15 into the collecting chamber 7 is achieved, which is characterized by a reduced flow resistance.

[0076] If in particular Figures 1 to 3 As can be seen in FIG. 1 , in the heat exchanger block 2, a plurality of first flow channels 9 are arranged side by side in the block transverse direction Y, so that the first flow channels form channel rows 33. For example, each channel row 33 can have more than twenty or more than fifty first flow channels 9. Now, in the heat exchanger block 2, a plurality of channel rows 33 are arranged side by side in the block height direction Z. According to Figure 1 , the heat exchanger block 1 has a mid-height region 34 which is spaced apart from lateral block ends 35, 36 which face away from one another in the block height direction Z. The channel rows 33 are guided through the heat exchanger block 2 at least in this mid-height region 34 between two adjacent channel rows 17. This results in a particularly compact arrangement of intersecting first flow channels 9 and second flow channels 15, which is advantageous for an intensive heat transfer.

[0077] In a plurality or all of the second flow channels 15 and / or in a plurality or all of the first flow channels 9, ribs or projections may protrude into the flow-through cross section 45, so that the ribs or projections can be flowed toward and / or around by the first fluid or the second fluid. Without limiting the generality, Fig. 9 The example is shown for two spirally configured ribs 37 which extend spirally along the respective second flow channel 15 , i.e. in the block transverse direction Y, or along the respective first flow channel 9 , i.e. in the block longitudinal direction X. It is clear that more than two ribs 37 of this type can also be present in the respective channel 9 , 15 .

[0078] exist Fig.10 In the figure, a depression 38 can be seen, which is formed in the inner side 39 exposed to the second fluid. In this case, the inner side 39 can belong to the collecting chamber 7 or the distributor chamber 4, or to the second flow channel 15, where the second flow channel is preferably in the first transition area 27 or in the second transition area 28. The depression 38 increases the surface of the respective inner side 39. For example, the depression 38 can have a constriction 40 at the transition to the inner side 39. Therefore, the cross-section 41 of the respective depression 38 is larger in the respective depression 38 than in the constriction 40. Here, the cross-section 41 is measured transversely to a normal direction 42 of the inner side 39, which is perpendicular to the inner side 39. In the figure, the cross-section 41 is measured transversely to a normal direction 42 of the inner side 39, which is perpendicular to the inner side 39. Fig.10 In FIG. 4 , the cross section 41 measured in the respective depression 38 is furthermore designated by 411 . The significantly smaller cross section 41 in the constriction 40 is furthermore designated by 412 .

[0079] exist Figures 1 to 10 In the embodiment, the heat exchanger 1 is configured as a cross-flow heat exchanger 1 so that a first flow channel 9 passes through the heat exchanger block 2 in the block longitudinal direction X and fluidically connects an inlet side 10 of the heat exchanger block 2 exposed to the first fluid with an outlet side 12 of the heat exchanger block 2 exposed to the first fluid.

[0080] In addition, Figures 1 to 10 In the example of , it is provided that the first chamber 4 forms a distributor chamber 4 and has a supply attachment end 5 , while the second chamber 7 forms a collecting chamber 7 and has a discharge attachment end 8 .

[0081] Now, Fig.11Another embodiment is shown purely by way of example and in a greatly simplified manner, in which the first chamber 4 has or forms a distributor chamber 46 and a collecting chamber 47. This can be achieved, for example, by means of a partition wall 48, which divides the first chamber 4 so that the distributor chamber 46 and the collecting chamber 47 are constructed therein. Then, the first attachment end 5 is constructed on the distributor chamber 46 and forms the supply attachment end 5, while the second attachment end 8 is constructed on the collecting chamber 47 and forms the outlet attachment end 8. In this case, the second chamber 7 forms a deflection chamber 49. For example, a partition 50 can be constructed in the second chamber 7 for this purpose, which partition guides or supports the flow deflection of the second fluid in the deflection chamber 49. A first group 51 of a plurality of second flow channels 15 connects the distributor chamber 46 with the deflection chamber 49. A second group 52 of a plurality of second flow channels 15 connects the deflection chamber 49 with the collecting chamber 47.

[0082] On the contrary, in a purely exemplary and greatly simplified manner Fig.12 In another alternative embodiment shown in , the heat exchanger 1 can be designed as a parallel flow heat exchanger 1 in which the first flow channels 9 pass through the heat exchanger block 2 in the block transverse direction Y. In this case, it can then be provided in particular that in the heat exchanger block 2, the first flow channels 9 and the second flow channels 15 alternate in the block height direction Z and / or in the block longitudinal direction X. Fig.12 It is shown how the first flow channels 9 and the second flow channels 15 alternate in the central transverse region 26 and intersect in a medium-dividing manner in the transition regions 27 , 28 .

[0083] In addition, according to Fig.12 In the configuration of the parallel flow heat exchanger 1, it can be provided that the first chamber 4 has or forms a first sub-chamber 53 and a second sub-chamber 54, wherein the first sub-chamber 53 is fluidically connected to the first flow channel 9, and the second sub-chamber 54 is fluidically connected to the second flow channel 15. In addition, the second chamber 7 can have or form a third sub-chamber 55 and a fourth sub-chamber 56, wherein the third sub-chamber 55 is fluidically connected to the first flow channel 9, and the fourth sub-chamber 56 is fluidically connected to the second flow channel 15.

[0084] Optionally, then according to Fig.12In addition, it can be provided that the first sub-chamber 53 forms a collecting chamber 53 for the first flow channel 9, the second sub-chamber 54 forms a distributor chamber 54 for the second flow channel 15, the third sub-chamber 55 forms a distributor chamber 55 for the first flow channel 9, and the fourth sub-chamber 56 forms a collecting chamber 7 for the second flow channel 15. The first attachment end 5 is used as a supply attachment end 5 for the second fluid and is constructed on the second sub-chamber. The second attachment end 8 is used as a lead-out attachment end 8 for the second fluid and is constructed on the fourth sub-chamber 56. The third attachment end 57 is used as a supply attachment end 57 for the first fluid and is constructed on the third sub-chamber 55. The fourth attachment end 58 is used as a lead-out attachment end 58 for the first fluid and is constructed on the first sub-chamber 53.

[0085] If the heat exchanger 1 is configured as a parallel flow heat exchanger 1, then in the above description Figures 1 to 10 All the configurations and features described with respect to the second flow channels 15 can also be implemented in a corresponding manner in the first flow channels 9. This applies in particular to the geometric configuration of the openings that merge into the respective chambers 4, 7 or subchambers 53, 54, 55, 56 and / or to the cross-sections through which the flow can flow vary in the block longitudinal direction Y and in the case of adjacent flow channels 9, 15 in the block longitudinal direction X. In particular, the first flow channels 9 can therefore also be configured in the heat exchanger block 2 with a plurality of channel rows of first flow channels 9 that are adjacent in the block longitudinal direction X, wherein a plurality of such channel rows are adjacent in the block height direction Z.

[0086] In principle, according to Figures 1 to 12 , the following embodiment is preferred: in this embodiment, the second flow channels 15 of the corresponding channel column 17 extend independently from the first chamber 4 to the second chamber 7 and have an independent inlet opening 19 or an independent outlet opening 23 there. Fig.13 In another embodiment, which is shown purely by way of example and in a greatly simplified manner, it can be provided that the second flow channels 15 of the corresponding channel rows 17 extend independently of one another at least in the middle transverse region 26 of the heat exchanger block 2, while the second flow channels merge into a common channel 59 in the first transition region 27 of the heat exchanger block 2 and / or in the second transition region 28 of the heat exchanger block 2.

Claims

1. An additively manufactured heat exchanger (1) for transferring heat between a first fluid and a second fluid in a medium-separated manner, the heat exchanger being used in particular for cooling a gas, - the heat exchanger has an additively manufactured heat exchanger block (2) having a block longitudinal direction (X), a block transverse direction (Y) and a block height direction (Z) extending perpendicularly to one another, -in, A plurality of first flow channels (9) for guiding a first fluid are formed in the heat exchanger block (2), wherein the first flow channels penetrate the heat exchanger block (2). wherein a first chamber (4) is formed on the heat exchanger block (2) at a first transverse end (3), the first chamber extending in the block height direction (Z), wherein a second chamber (7) is formed on the heat exchanger block (2) at a second transverse end (6), the second transverse end facing away from the first transverse end (3) in the transverse direction (Y) of the block, the second chamber extending in the height direction (Z) of the block, wherein a plurality of second flow channels (15) for conducting a second fluid are formed in the heat exchanger block (2), the second flow channels being fluidically separated from the first flow channels (9), the second flow channels penetrating the heat exchanger block (2) in the block transverse direction (Y) and the second flow channels fluidically connecting the first chamber (4) with the second chamber (7), wherein the heat exchanger (1) has a first attachment end (5) for supplying or discharging the second fluid and a second attachment end (8) for supplying or discharging the second fluid, wherein, in the heat exchanger block (2), a plurality of second flow channels (15) are arranged side by side in the longitudinal direction (X) of the block and form a channel column (17), - wherein in the heat exchanger block (2), a plurality of channel rows (17) are arranged side by side in the block height direction (Z).

2. The heat exchanger (1) according to claim 1, It is characterized in that - the heat exchanger block (2) has a block longitudinal center plane (18) extending transversely to the block longitudinal direction (X), - The second flow channels (15) are configured in such a way with respect to their flow resistance that in the corresponding channel longitudinal row (17), the magnitude of the flow resistance of the corresponding second flow channel (15) is associated with the distance between the corresponding second flow channel (15) and the longitudinal center plane (18) of the block, so that the flow resistance of the second flow channel (15) at a greater distance from the longitudinal center plane (18) of the block is greater than the flow resistance of the second flow channel (15) at a smaller distance from the longitudinal center plane (18) of the block.

3. The heat exchanger (1) according to claim 1 or 2, It is characterized in that - the heat exchanger block (2) has a block longitudinal center plane (18) extending transversely to the block longitudinal direction (X), - The second flow channel (15) is configured in such a way with respect to its flow-through cross-sectional area (24) that in the corresponding channel longitudinal row (17), the size of the flow-through cross-sectional area (24) of the corresponding second flow channel (15) is associated with the distance between the corresponding second flow channel (15) and the longitudinal center plane (18) of the block, so that the flow-through cross-sectional area (24) of the second flow channel (15) at a greater distance from the longitudinal center plane (18) of the block is smaller than the flow-through cross-sectional area of ​​the second flow channel (15) at a smaller distance from the longitudinal center plane (18) of the block.

4. The heat exchanger (1) according to claim 3, It is characterized in that the heat exchanger block (2) has a middle transverse region (26) which is spaced apart from the first transverse end (3) and from the second transverse end (6), - The second flow channel (15) is configured in such a way with respect to its flow-through cross-sectional area (24) that at least in the middle transverse region (26) in the corresponding channel longitudinal row (17), the size of the flow-through cross-sectional area (24) of the corresponding second flow channel (15) is associated with the distance between the corresponding second flow channel (15) and the longitudinal center plane (18) of the block, so that the flow-through cross-sectional area (24) of the second flow channel (15) at a greater distance from the longitudinal center plane (18) of the block is smaller than the flow-through cross-sectional area of ​​the second flow channel (15) at a smaller distance from the longitudinal center plane (18) of the block.

5. The heat exchanger (1) according to any one of claims 1 to 4, It is characterized in that the heat exchanger block (2) has a middle transverse region (26) which is spaced apart from the first transverse end (3) and from the second transverse end (6), - the second flow channel (15) has a flow-through cross-sectional area (24), which decreases from a first opening (19) opening into the first chamber (4) to the intermediate transverse region (26) and / or increases from the intermediate transverse region (26) to a second opening (23) opening into the second chamber (7).

6. The heat exchanger (1) according to any one of claims 1 to 5, It is characterized in that the heat exchanger block (2) has a middle transverse region (26) which is spaced apart from the first transverse end (3) and from the second transverse end (6), the heat exchanger block (2) has a first transition region (27) at the first transverse end (3) and a second transition region (28) at the second transverse end (6), the first transition region connecting the first chamber (4) to the intermediate transverse region (26), the second transition region connecting the second chamber (7) to the intermediate transverse region (26), - the heat exchanger block (2) has a block longitudinal center plane (18) extending transversely to the block longitudinal direction (X), - the second flow channel (15) extends in the intermediate transverse region (26) parallel to the block transverse direction (Y), - a second flow channel (15) which is spaced apart from the block longitudinal center plane (18) or which faces away from the block longitudinal center plane and which extends in the first transition region (27) and / or in the second transition region (28) at an inclination relative to the block transverse direction (Y), wherein the inclination (30) increases from the intermediate transverse region (26) to the distributor chamber (4) and / or to the collecting chamber (7).

7. The heat exchanger (1) according to any one of claims 1 to 6, It is characterized in that the heat exchanger block (2) has a middle transverse region (26) which is spaced apart from the first transverse end (3) and from the second transverse end (6), the heat exchanger block (2) has a first transition region (27) at the first transverse end (3) and a second transition region (28) at the second transverse end (6), the first transition region connecting the first chamber (4) to the intermediate transverse region (26), the second transition region connecting the second chamber (7) to the intermediate transverse region (26), - the heat exchanger block (2) has a block longitudinal center plane (18) extending transversely to the block longitudinal direction (X), - at least a second flow channel (15) spaced apart from the block longitudinal center plane (18) or facing away from the block longitudinal center plane has a changing opening cross section (45) in the first transition region (27) and / or in the second transition region (28) along the block transverse direction (Y).

8. The heat exchanger (1) according to claim 7, It is characterized in that At least a second flow channel (15) spaced apart from the block longitudinal center plane (18) or facing away from the block longitudinal center plane has in the middle transverse region (26) a constant opening cross section (45) along the block transverse direction (Y).

9. The heat exchanger (1) according to claim 7 or 8, It is characterized in that - at least a second flow channel (15) spaced apart from or facing away from the block longitudinal center plane (18) has an elliptical opening cross section (45) in a first opening (19) opening into the first chamber (4), the elliptical opening cross section being elongated in the block longitudinal direction (X) and transforming into a circular opening cross section (45) along the block transverse direction (Y) in the first transition region (27) up to the intermediate transverse region (26), and / or - A second flow channel (15) which is at least spaced apart from or facing away from the longitudinal center plane (18) of the block has an elliptical opening cross section (45) in a second opening (23) opening into the second chamber (7), the elliptical opening cross section being elongated in the longitudinal direction (X) of the block and transforming into a circular opening cross section (45) along the transverse direction (Y) of the block in the second transition region (28) up to the intermediate transverse region (26).

10. The heat exchanger (1) according to any one of claims 1 to 9, It is characterized in that the first chamber (4) forms or has a distributor chamber (4) which supplies the second fluid to the second flow channel (15), the first attachment end (5) is configured on the distributor chamber (4) and forms a supply attachment end (5) for supplying the second fluid to the distributor chamber (4), The distributor chamber (4) has, on a distributor side (31) facing the second flow channel (15), a contour which extends transversely to the block height direction (Z) and is curved concavely toward the interior of the distributor chamber (4).

11. The heat exchanger (1) according to any one of claims 1 to 10, It is characterized in that the second chamber (7) forms or has a collecting chamber (7) which receives the second fluid from the second flow channel (15), the second attachment end (8) is configured on the collecting chamber (7) and forms a discharge attachment end (8) for discharging the second fluid from the collecting chamber (7), The collecting chamber (7) has, on a collecting side (32) facing the connecting channel (15), a contour which extends transversely to the block height direction (Z) and is curved concavely toward the interior of the collecting chamber (7).

12. The heat exchanger (1) according to any one of claims 1 to 11, It is characterized in that In a plurality or all of the second flow channels (15), the ribs (37) or projections protrude into the through-flow cross section (45), so that the second fluid can flow toward and / or around the ribs (37) or projections.

13. The heat exchanger (1) according to any one of claims 1 to 12, It is characterized in that In a plurality or all of the first flow channels (9), the ribs (37) or projections protrude into the through-flow cross section (45), so that the first fluid can flow toward and / or around the ribs (37) or projections.

14. The heat exchanger (1) according to claim 12 or 13, It is characterized in that The rib (37) is helically shaped so that it extends helically along the respective second flow channel (15) or along the respective first flow channel (9).

15. Heat exchanger (1) according to any one of the preceding claims, It is characterized in that The first chamber or the second chamber (4, 7) has a recess (38) on its inner side (39) exposed to the second fluid, for increasing the surface of the inner side (39).

16. Heat exchanger (1) according to any one of the preceding claims, It is characterized in that - a plurality of or all second flow channels (15) have, at least in a transition region (27, 28) of the heat exchanger block (2) adjacent to the first chamber or the second chamber (4, 7), a recess (38) on their inner side (39) exposed to the second fluid, for increasing the surface of the inner side (39).

17. The heat exchanger (1) according to claim 15 or 16, It is characterized in that The recess (38) has a narrowing (40) at the transition to the inner side (39), so that a cross section (41) of the corresponding recess (38) extending transversely to a normal direction (42) of the inner side (39) is larger in the corresponding recess (38) than in the narrowing (40).

18. The heat exchanger (1) according to any one of claims 1 to 9 and 12 to 17, It is characterized in that - the first chamber (4) has or forms a distributor chamber (46) and a collecting chamber (47), - the first attachment end (5) is configured on the dispenser chamber (46) and forms a supply attachment end (5), the second attachment end (8) is configured on the collecting chamber (47) and forms a discharge attachment end (8), - said second chamber (7) forms a deflection chamber (49).

19. The heat exchanger (1) according to any one of claims 1 to 18, It is characterized in that - the heat exchanger (1) is configured as a cross-flow heat exchanger (1), The first flow channel (9) passes through the heat exchanger block (2) in the block longitudinal direction (X) of the heat exchanger block (2) and fluidically connects an inflow side (10) of the heat exchanger block (2) exposed to the first fluid with an outflow side (12) of the heat exchanger block (2) exposed to the first fluid.

20. The heat exchanger (1) according to claim 19, It is characterized in that - in the heat exchanger block (2), a plurality of first flow channels (9) are arranged side by side in the transverse direction (Y) of the block and form channel rows (33), - in the heat exchanger block (2), a plurality of channel rows (33) are arranged side by side in the block height direction (Z), the heat exchanger block (2) has a mid-height region (34) which is spaced apart from lateral block ends (35, 36) which face away from one another in the block height direction (Z), The channel transverse rows (33) are guided through the heat exchanger block (2) at least in the middle height region (34) of the heat exchanger block (2) between two adjacent channel longitudinal rows (17).

21. The heat exchanger (1) according to any one of claims 1 to 17, It is characterized in that - the heat exchanger (1) is configured as a parallel flow heat exchanger (1), - the first flow channel (9) passes through the heat exchanger block (2) in the block transverse direction (Y), In the heat exchanger block (2), first flow channels (9) and second flow channels (15) alternate in the block height direction (Z) and / or in the block longitudinal direction (X).

22. The heat exchanger (1) according to claim 21, It is characterized in that - the first chamber (4) has or forms a first sub-chamber (53) and a second sub-chamber (54), the first subchamber (53) is fluidically connected to the first flow channel (9), and the second subchamber (54) is fluidically connected to the second flow channel (15), - the second chamber (7) has or forms a third sub-chamber (55) and a fourth sub-chamber (56), The third subchamber (55) is fluidically connected to the first flow channel (9), and the fourth subchamber (56) is fluidically connected to the second flow channel (15).

23. The heat exchanger according to claim 22, It is characterized in that - the first subchamber (53) forms a collecting chamber for the first flow channel (9), the second subchamber (54) forms a distributor chamber for the second flow channel (15), - the third subchamber (55) forms a distributor chamber for the first flow channel (9), The fourth subchamber (56) forms a collecting chamber for the second flow channel (15).

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