Additively manufactured heat exchanger

Abstract

The invention relates to a heat exchanger (1), in particular for cooling a gas, with an additively manufactured heat exchanger block (2), wherein multiple first flow channels (9) for guiding a first fluid are formed in the heat exchanger block (2), which 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), wherein a second chamber (7) is formed on the heat exchanger block (2) at a second transverse end (6), wherein multiple second flow channels (15) for guiding a second fluid are formed in the heat exchanger block (2), which are fluidically separated from the first flow channels (9), which penetrate the heat exchanger block (2) in the block transverse direction (Y) and which fluidically connect the first chamber (4) to the second chamber (7). There is an advantageous distribution of thermal and / or mechanical stresses if multiple second flow channels (15) are arranged next to one another in the block longitudinal direction (X) in the heat exchanger block (2) and form a longitudinal row of channels (17) and if multiple longitudinal rows of channels (17) are arranged next to one another in the block vertical direction (Z) in the heat exchanger block (2).

Description

[0001] Additively manufactured heat exchanger

[0002] The present invention relates to an additively manufactured heat exchanger for media-separated heat transfer between a first fluid and a second fluid, in particular for cooling a gas.

[0003] Additive manufacturing, particularly three-dimensional printing, allows for geometries that are impossible or only possible with extremely high costs using conventional manufacturing methods such as casting and machining. Additive manufacturing can be carried out with plastics and metals.

[0004] A heat exchanger has a heat exchanger block in which media-separated heat transfer takes place between two different fluids. In conventional designs, the heat exchanger block consists of several separate components that are assembled in a suitable manner. For example, a conventional heat exchanger block comprises a distribution pipe or a distribution box and a header pipe or a header box, which are fluidically connected to one another via a plurality of connecting pipes. Flow-through spaces are formed between adjacent connecting pipes, in which fins can usually be arranged. A first fluid, which is to be heated or cooled, is passed through these spaces. A second fluid, which is to supply or dissipate heat, is passed through the connecting pipes. The second fluid is fed to the connecting pipes via the distribution pipe or the distribution box.The second fluid is discharged from the connecting pipes via the manifold or collection box. During operation of the heat exchanger, thermal and / or mechanical stress peaks arise, particularly at the transitions between the connecting pipes and the distribution pipe or manifold, which the heat exchanger block must tolerate. As a result, the heat exchanger block is inevitably oversized in many places. Furthermore, the heat transfer performance of a heat exchanger correlates with the surface area available for heat transfer. For example, the number of connecting pipes that can be implemented is limited by their manufacturability, space requirements, and the connection technology used, usually a soldering process.

[0005] The present invention addresses the problem of providing an improved or at least a different embodiment for a heat exchanger, which is characterized in particular by efficient heat transfer, wherein a reduction of thermal and / or mechanical stress peaks within the heat exchanger block is also sought.

[0006] 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.

[0007] The invention is based on the general idea of ​​additively manufacturing the heat exchanger block in such a way that a plurality of first flow channels for guiding a first fluid are formed in the heat exchanger block, which first flow channels penetrate the heat exchanger block in one direction, for example in the block longitudinal direction or in the block transverse direction, so that the first fluid can flow through the heat exchanger block in the first flow channels in the direction defined by these channels. Furthermore, a first chamber is formed on the heat exchanger block at a first transverse end, which extends, for example, in the block height direction. The heat exchanger has a first connection for supplying or discharging a second fluid. In addition, a second chamber is formed on the heat exchanger block at a second transverse end, which faces away from the first transverse end in the block transverse direction.The heat exchanger has a second connection for discharging or supplying the second fluid. In addition, a plurality of second flow channels for conducting the second fluid are formed in the heat exchanger block. These second flow channels are fluidically separated from the first flow channels, penetrate the heat exchanger block in the transverse direction of the block, and fluidically connect the first chamber to the second chamber. The additive manufacturing of the heat exchanger block makes it possible to arrange several second flow channels next to one another or one behind the other in the longitudinal direction of the block in order to form a longitudinal channel row. In the heat exchanger block, several such longitudinal channel rows are then arranged next to one another in the block height direction. For example, at least three, preferably at least five, in particular at least ten, connecting channels can be arranged next to one another in the longitudinal direction of the block in the respective longitudinal channel row.Compared to a conventionally manufactured heat exchanger block, in which a maximum of two connecting tubes are arranged side by side in the longitudinal direction of the block, the design proposed here results in a drastic increase in the surface area available for heat transfer while requiring the same amount of space. Furthermore, with additive construction, more material is available in the heat exchanger block for heat transfer, as the second flow channels and the first flow channels are routed through the material of the heat exchanger block. In contrast, with conventional construction, the material of the heat exchanger block is formed exclusively by the tube walls of the connecting tubes and by the walls of the fins that may be arranged between the connecting tubes. This means that more material is available for heat transfer in the additively manufactured heat exchanger block.

[0008] While in conventional manufacturing of the heat exchanger block the connecting pipes penetrate a side wall delimiting 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 / distribution box or the collecting pipe / distribution box, forming a flow obstacle there, such a protrusion is not required in additive manufacturing, resulting in a significant reduction in the flow resistance of the heat exchanger for the second fluid.

[0009] Such a heat exchanger can be used, for example, at a hydrogen filling station to cool the hydrogen when filling a vehicle tank.

[0010] According to an advantageous embodiment, the heat exchanger block has a longitudinal center plane running transversely to the block longitudinal direction and extending centrally through the heat exchanger block with respect to the block longitudinal direction. Furthermore, the flow resistance of the connecting channels can be configured such that, in the respective longitudinal channel row, the magnitude of the flow resistance of the respective second flow channel correlates with the distance of the respective second flow channel from the block longitudinal center plane, so that the second flow channels that are at a greater distance from the block longitudinal center plane have a greater flow resistance than second flow channels that are at a smaller distance from the block longitudinal center plane.This measure ensures that during operation of the heat exchanger the volume flow of the second fluid is unevenly distributed between the second flow channels within the respective longitudinal row of channels, such that a larger volume flow flows through the second flow channels in the region of the block's longitudinal center plane than in second flow channels that are spaced from the block's longitudinal center plane, with the volume flow decreasing further with increasing distance from the block's longitudinal center plane. This makes it possible to reduce stress peaks. This design utilizes the knowledge that thermal and / or mechanical stresses at the transition between the second flow channels and the first and / or second chamber, in particular the distribution chamber and / or the collection chamber, correlate with the distance from the block's longitudinal center plane. These stresses increase with increasing distance from the block's longitudinal center plane.By reducing the flow rate, the stresses in the longitudinal direction of the block can be homogenized.

[0011] In the present context, a "configuration" is synonymous with a "design", so that the phrase "configured so that" is synonymous with the phrase "designed so that".

[0012] Particularly expedient in this case is an embodiment in which the second flow channels are configured with regard to their flow-through cross-sectional area such that, in the respective longitudinal row of channels, the size of the flow-through cross-sectional area of ​​the respective second flow channel correlates with the distance of the respective second flow channel from the block longitudinal center plane, in such a way that the second flow channels which are at a greater distance from the block longitudinal center plane have a smaller flow-through cross-sectional area than second flow channels which are at a smaller distance from the block longitudinal center plane. The flow resistance of the respective second flow channel correlates with the flow-through cross-sectional area of ​​the respective second flow channel. The larger the flow-through cross-sectional area, the lower the flow resistance.The flow resistance can thus be influenced particularly easily via the flow-through cross-sectional area. Alternatively, the flow resistance of the secondary flow channels can also be influenced using other measures. For example, during additive manufacturing, flow obstructions such as baffles, flow guide surfaces, ribs, and studs can be incorporated into secondary flow channels that are intended to have a higher flow resistance.

[0013] The heat exchanger block has a central transverse region which is spaced from the first transverse end and the second transverse end and which merges into the first chamber via a first transition region at the first transverse end and into the second chamber via a second transition region at the second transverse end. The above-explained configuration of the second flow channels with regard to their flow-through cross-sectional area preferably applies at least in the central transverse region, since this is where the greatest influence on the flow resistance occurs via the length of the second flow channels measured in the transverse direction of the block. Expediently, the above-explained configuration of the second flow channels with regard to their flow-through cross-sectional area also applies in the first transition region, which connects the first chamber with the central transverse region.Optionally, the configuration of the second flow channels explained above with regard to their flow-through cross-sectional area can also apply to the second transition region which connects the central transverse region with the second chamber.

[0014] According to an advantageous embodiment, the first chamber can form or have a distribution chamber that supplies the second fluid to the second flow channels, wherein the first connection forms a supply connection for supplying the second fluid to the distribution chamber. The heat exchanger block can have a longitudinal center plane that runs transversely to the block longitudinal direction and extends centrally through the heat exchanger block with respect to the block longitudinal direction. Furthermore, the second flow channels on the distribution chamber can each have an inlet opening with a round inlet cross-section through which flow can pass. These round inlet cross-sections have a longitudinal diameter measured in the block longitudinal direction and a height diameter measured in the block height direction.The second flow channels can now be configured with regard to their inlet cross-section such that, in the respective longitudinal channel row, the size of the longitudinal diameter of the inlet cross-section of the inlet opening of the respective second flow channel correlates with the distance of the respective second flow channel from the block's longitudinal center plane, specifically such that the second flow channels that are at a greater distance from the block's longitudinal center plane have an inlet cross-section with a larger longitudinal diameter than second flow channels that are at a smaller distance from the block's longitudinal center plane. In other words, the inlet cross-sections of the inlet openings become increasingly larger in terms of their longitudinal diameter with increasing distance from the block's longitudinal center plane. This measure contributes to reducing thermal and / or mechanical stress peaks.

[0015] A configuration in which the longitudinal diameter of the inlet cross-sections is at least as large as the vertical diameter at all inlet openings is advantageous. In particular, the inlet cross-sections can be circular or elliptical.

[0016] According to an advantageous embodiment, the vertical diameter of the inlet cross-section of the inlet opening of the respective second flow channel can be the same for all second flow channels of the respective channel longitudinal row. Consequently, the inlet cross-sections of the inlet openings of second flow channels that are spaced from the block's longitudinal center plane are flat or elongated. Furthermore, the inlet cross-sections of the inlet openings of the second flow channels arranged in the region of the block's longitudinal center plane can be circular, while the inlet cross-sections of the inlet openings of the second flow channels spaced from the block's longitudinal center plane are elliptical, wherein the elliptical cross-sections become increasingly flatter or more elongated with increasing distance of the second flow channels from the block's longitudinal center plane.

[0017] According to another embodiment, it can be provided that the second chamber forms or has a collecting chamber which receives the second fluid coming from the second flow channels, wherein the second connection then forms a discharge connection for discharging the second fluid from the collecting chamber.

[0018] Preferably, what was stated above regarding the transition between the distribution chamber and the second flow channels also applies to the transition from the second flow channels to the collection chamber. Accordingly, the second flow channels at the collection chamber each expediently have an outlet opening with a circular outlet cross-section through which flow can occur, wherein the outlet cross-sections have a longitudinal diameter measured in the longitudinal direction of the block and a vertical diameter measured in the vertical direction of the block.The second flow channels are now expediently configured with regard to their outlet cross-section such that, in the respective longitudinal row of channels, the size of the longitudinal diameter of the outlet cross-section of the respective second flow channel correlates with the distance of the respective second flow channel from the block longitudinal center plane, so that the second flow channels that are at a greater distance from the block longitudinal center plane have an outlet cross-section with a larger longitudinal diameter than second flow channels that are at a smaller distance from the block longitudinal center plane. Preferably, it can also be provided here that the vertical diameter of the outlet cross-section of the respective second flow channel is the same for all second flow channels in the respective longitudinal row of channels. Here, too, it can expediently apply that the longitudinal diameter is the same as the vertical diameter or is greater than the vertical diameter.Thus, the exit cross-sections in the area of ​​the block longitudinal center plane can be circular in particular, while at a distance from the block longitudinal center plane they can be elliptical, with the elliptical cross-sections becoming increasingly flatter or more elongated with increasing distance from the block longitudinal center plane.

[0019] According to an advantageous embodiment, the heat exchanger block can have a central transverse region that is spaced from the first transverse end and the second transverse end. The second flow channels have a flow-through cross-sectional area and can be configured such that their flow-through cross-sectional area decreases from a first opening opening at the first chamber to the central transverse region and / or increases from the central transverse region to a second opening opening at the second chamber. In other words, the second flow channels have a varying flow-through cross-sectional area along the block height direction. This makes it possible to reduce thermal and / or mechanical stress peaks at the transition between the connecting channels and the first chamber and / or the second chamber.

[0020] According to an advantageous embodiment, the heat exchanger block can have a central transverse region that is spaced apart from the first transverse end and the second transverse end. Furthermore, the heat exchanger block has a first transition region at the first transverse end that connects the first chamber to the central transverse region, and a second transition region at the second transverse end that connects the second chamber to the central transverse region. Furthermore, the heat exchanger block has a longitudinal center plane that runs transversely to the block longitudinal direction. The second flow channels can now be configured such that they run parallel to the block transverse direction in the central transverse region.Furthermore, the second flow channels can be configured such that second flow channels, which are spaced from the block's longitudinal center plane, extend at an angle to the block's transverse direction in the first transition region and / or in the second transition region, with the angle increasing from the central transverse region to the first chamber and / or to the second chamber. This results in a fan-like configuration for the second flow channels in the respective transition region. It has been shown that such a design can reduce thermal and / or mechanical stress peaks in the respective transition region.

[0021] According to an advantageous embodiment, the heat exchanger block has a central transverse region that is spaced from the first transverse end and the second transverse end, wherein the heat exchanger block has a first transition region at the first transverse end that connects the first chamber to the central transverse region, and a second transition region at the second transverse end that connects the second chamber to the central transverse region. The heat exchanger block also has a block longitudinal center plane running transversely to the block longitudinal direction. Advantageously, the second flow channels can now be configured such that at least those second flow channels that are spaced from 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's longitudinal center plane are those second flow channels that have the greatest distance from the block's longitudinal center plane within the respective channel row. The geometrically varying opening cross-section allows thermal and / or mechanical stress peaks in the respective transition area to be reduced.

[0022] According to an advantageous development, at least the second flow channels, which are spaced apart from or facing away from the block's longitudinal center plane, can have an opening cross-section in the central transverse region that is geometrically constant along the block's transverse direction. In other words, the opening cross-sections of the second flow channels are constant along the block's transverse direction in the central transverse region, while they vary in the two transition regions.

[0023] In principle, an embodiment is preferred in which the second flow channels of the respective longitudinal row of channels extend separately from the first chamber to the second chamber and each have separate inlet and outlet openings there. In another embodiment, however, it can be provided that the flow channels of the respective longitudinal row of channels run separately from one another at least in a central transverse region of the heat exchanger block, which is spaced from the first transverse end and the second transverse end, while they are combined into a common channel in a first transition region of the heat exchanger block, which leads to the first chamber, and / or in a second transition region of the heat exchanger block, which leads to the second chamber.

[0024] According to another development, at least the second flow channels, which are spaced apart from or facing away from the block's longitudinal center plane, can have, in a first opening leading into the first chamber, an elliptical opening cross-section which is elongated in the block's longitudinal direction and which transitions into a circular opening cross-section along the block's transverse direction within the first transition region up to the central transverse region. Additionally or alternatively, at least the second flow channels, which are spaced apart from or facing away from the block's longitudinal center plane, can have, in a second opening leading into the second chamber, an elliptical opening cross-section which is elongated in the block's longitudinal direction and which transitions into a circular opening cross-section along the block's transverse direction within the second transition region up to the central transverse region.In particular, the elliptical first openings in the first transition region can thus transition into circular opening cross-sections, which remain consistently circular within the central transverse region and can transition again into elliptical second openings in the second transition region. The use of round cross-sections in the second flow channels, in particular elliptical and circular cross-sections, reduces thermal and / or mechanical stresses.

[0025] According to another advantageous embodiment, it can again be provided that the first chamber forms or has a distribution chamber that supplies the second fluid to the second flow channels, wherein the first connection forms a supply connection for supplying the second fluid to the distribution chamber. In this case, the distribution chamber can have, on a distributor side facing the connecting channels, a profile that runs transversely to the block height direction and is concavely curved toward the interior of the distribution chamber.Additionally or alternatively, in an embodiment in which the second chamber forms or has a collection chamber that receives the second fluid coming from the second flow channels, and in which the second connection forms a discharge connection for discharging the second fluid from the collection chamber, it can optionally be provided that the collection chamber has, on a collection side facing the connecting channels, a profile that runs transversely to the block height direction and is concavely curved toward the interior of the collection chamber. The curved or bent profile on the distributor side of the distributor chamber or on the collector side of the collection chamber can reduce thermal and / or mechanical stress peaks.

[0026] The second flow channels, in which the geometric cross-section varies along the block transverse direction, can optionally be configured so that their flow-through cross-sectional area is or remains constant along the block transverse direction.

[0027] In an advantageous embodiment, it can be provided that ribs or knobs protrude into the flow-through cross-section in several or all of the first and / or second flow channels, so that the second fluid can flow against and / or around the ribs or knobs. This can increase the surface area available for heat transfer in the respective connecting channels.

[0028] According to an advantageous embodiment, the fins can be helically configured, so that they extend helically along the respective second flow channel in the block transverse direction or along the respective first flow channel in the block longitudinal direction or in the block transverse direction. The helical fins increase the surface area available for heat transfer and are characterized by comparatively low flow resistance.

[0029] According to an advantageous embodiment, the first and / or second chamber can have recesses on an inner side exposed to the second fluid to increase the surface area of ​​the inner side. Particularly in a heat exchanger used in a refrigeration circuit and forming an evaporator therein, these recesses can significantly improve the evaporation of the refrigerant. Such recesses are also referred to as re-entry cavities.

[0030] According to an advantageous embodiment, several or all of the second flow channels can have recesses on their inner side exposed to the second fluid, at least in a transition region of the heat exchanger block adjoining the first or second box, to increase the surface area of ​​the inner side. This measure also improves heat transfer and, when used as an evaporator, supports the evaporation of the second fluid.

[0031] A particularly advantageous embodiment is one in which the recesses have a constriction at the transition to the inner side, so that a cross-section of the respective recess running perpendicular to the normal direction of the inner side is larger within the respective recess than within the constriction. The constriction thus forms an undercut. Such recesses or undercuts are extremely difficult or impossible to produce using conventional manufacturing methods. It has been shown that recesses with such a constriction significantly support the boiling behavior of the second fluid and improve the efficiency of the heat exchanger used as an evaporator.

[0032] According to an advantageous embodiment, the heat exchanger can be designed as a cooler for cooling the first fluid using the second fluid, wherein the first fluid is a liquid coolant, while the second fluid is a liquid or a gas. Alternatively, the heat exchanger can be designed as an evaporator for cooling the first fluid using the second fluid, wherein the first fluid is a two-phase refrigerant, while 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 largely liquid at the supply port, while it is largely gaseous at the discharge port.

[0033] As already explained above, according to a preferred embodiment it can be provided that the first chamber forms a distribution chamber and has the first connection, which then forms a supply connection. The second chamber then forms a collection chamber and has the second connection, which forms a discharge connection. The distribution chamber and the collection chamber are fluidically connected to one another via the second flow channels. The second fluid therefore flows once in the transverse direction of the block through the heat exchanger block, namely from the distribution chamber through the second flow channels to the collection chamber. In another embodiment, however, it can be provided that the first chamber has or forms a distribution chamber and a collection chamber, wherein the first connection is then formed on the distribution chamber and forms a supply connection, while the second connection is formed on the collection chamber and forms a discharge connection.In this case, the second chamber forms a deflection chamber. The deflection chamber is fluidically connected to the distribution chamber and the collection chamber via the second flow channels. Thus, in this configuration, the second fluid flows twice through the heat exchanger block: from the distribution chamber through a first group of second flow channels to the deflection chamber, and from the deflection chamber through a second group of second flow channels to the collection chamber. A particularly advantageous embodiment is one in which the heat exchanger is designed as a cross-flow heat exchanger, i.e., the first flow channels and the second flow channels are routed through the heat exchanger block according to the cross-flow principle, thus crossing or intersecting each other in a media-separated manner.Subsequently, the first flow channels pass through the heat exchanger block in the longitudinal direction of the block and fluidically connect an upstream side of the heat exchanger block exposed to the first fluid with an downstream side of the heat exchanger block exposed to the first fluid.

[0034] According to an advantageous embodiment, a plurality of first flow channels can be arranged next to one another in the heat exchanger block in the transverse direction of the block, forming a transverse row of channels. A plurality of transverse rows of channels are then arranged next to one another in the heat exchanger block in the vertical direction of the block. The heat exchanger block has a central vertical region spaced apart from lateral block ends facing away from one another in the vertical direction of the block. The transverse rows of channels can then be passed through the heat exchanger block, at least in the central vertical region of the heat exchanger block, between two adjacent longitudinal rows of channels. This results in an extremely compact design with very large surfaces for contact with the first fluid and with the second fluid.While in a conventional design the heat exchanger block has only one flow-through space between two adjacent connecting pipes, in which fins can be arranged to increase the surface area, in the additively manufactured heat exchanger block several, preferably more than ten, in particular more than twenty, first flow channels can be arranged next to one another in the transverse direction of the block in order to form the respective transverse row of channels. As an alternative to the cross-flow design, in another embodiment the heat exchanger can be designed as a parallel-flow heat exchanger, in which the first flow channels and the second flow channels are guided through the heat exchanger block according to the parallel flow principle, i.e. they extend parallel to one another therein, separated by media. Consequently, the first flow channels penetrate the heat exchanger block in the transverse direction of the block.In particular, it can be provided that first flow channels and second flow channels alternate in the heat exchanger block in the block height direction and / or in the block length direction. This can improve the efficiency of heat transfer.

[0035] According to an advantageous embodiment, it can be provided that the first chamber has or forms a first sub-chamber and a second sub-chamber, wherein the first sub-chamber is fluidically connected to the first flow channels, while the second sub-chamber is fluidically connected to the second flow channels. In addition, it can be provided that the second chamber has or forms a third sub-chamber and a fourth sub-chamber, wherein the third sub-chamber is fluidically connected to the first flow channels, while the fourth sub-chamber is fluidically connected to the second flow channels. Each sub-chamber can expediently have its own connection for supplying or discharging the first or second fluid. This makes it possible to achieve a particularly compact design.

[0036] A particularly advantageous embodiment is one in which the first sub-chamber forms a collection chamber for the first flow channels and has a discharge port for the first fluid, the second sub-chamber forms a distribution chamber for the second flow channels and has a supply port for the second fluid, the third sub-chamber forms a distribution chamber for the first flow channels and has a supply port for the first fluid, and the fourth sub-chamber forms a collection chamber for the second flow channels and has a discharge port for the second fluid. This embodiment also supports a compact design.

[0037] When configured as a parallel-flow heat exchanger, it can also be provided that all first and second flow channels run parallel to each other in a central transverse region, while several or all of the first and second flow channels intersect or cross each other in a media-separated manner in a first transition region leading to the first and second subchambers and / or in a second transition region leading to the third and fourth subchambers. This also supports efficient heat transfer with a compact design.

[0038] If the heat exchanger is designed as a parallel-flow heat exchanger, all of the above-described configurations and features relating to the second flow channels can also be implemented correspondingly in the first flow channels. This applies in particular to the geometric configurations of the openings that open into the respective chamber or sub-chamber and / or to the variation of the flow-through cross-sections in the block transverse direction within the flow channels and in the block longitudinal direction in adjacent flow channels. In particular, the first flow channels in the heat exchanger block can therefore also form longitudinal channel rows with a plurality of first flow channels adjacent in the block longitudinal direction, wherein a plurality of such longitudinal channel rows are adjacent in the block vertical direction.

[0039] Further important features and advantages of the invention emerge from the subclaims, from the drawings and from the associated description of the figures based on the drawings.

[0040] It is understood that the features mentioned above and those to be explained below can be used not only in the respective combination specified, but also in other combinations or on their own, without departing from the scope of the invention defined by the claims. Components mentioned above and to be mentioned below of a higher-level unit, such as a device, apparatus, or arrangement, which are designated separately, may form separate parts or components of this unit or be integral areas or sections of this unit, even if this is shown differently in the drawings.

[0041] Preferred embodiments of the invention are illustrated in the drawings and are explained in more detail in the following description, wherein the same reference numerals refer to the same or similar or functionally identical components.

[0042] They show, schematically,

[0043] Figure 1 is a highly simplified side view of a heat exchanger,

[0044] Figure 2 is a sectioned isometric view of the heat exchanger in

[0045] area of ​​a distribution chamber,

[0046] Figure 3 is a sectional isometric view of the heat exchanger in the area of ​​a collection chamber,

[0047] Figure 4 shows an enlarged detail IV from Figure 2, Figure 5 shows highly simplified cross sections of second flow channels at inlet openings or outlet openings for different flow channels A and B,

[0048] Figure 6 Cross sections as in Figure 5, but with a different embodiment,

[0049] Figure 7 different views of a second flow channel in a transition area in different viewing directions A, B, C,

[0050] Figure 8 is an isometric view of several second flow channels in a transition area,

[0051] Figure 9 is an isometric view of a longitudinal section of a second flow channel or a first flow channel with ribs,

[0052] Figure 10 is a highly simplified sectional view in the area of ​​recesses,

[0053] Figure 11 is a highly simplified sectional view of the heat exchanger in a cross-flow embodiment,

[0054] Figure 12 is a highly simplified sectional view of the heat exchanger in a parallel flow embodiment,

[0055] Figure 13 is a highly simplified sectional view of the heat exchanger in the region of a chamber in another embodiment.

[0056] According to Figure 1, an additively manufactured heat exchanger 1 comprises an additively manufactured heat exchanger block 2, which has a block longitudinal direction X, a block transverse direction Y, and a block height direction Z, which run perpendicular to one another. In Figure 1, the block longitudinal direction X extends perpendicular to the plane of the drawing, while the block transverse direction Y runs vertically and the block height direction Z runs horizontally.

[0057] On the heat exchanger block 2, a first chamber 4 is formed at a first transverse end 3, which extends longitudinally in the block height direction Z and has a first connection 5. In the example shown here, the first chamber 4 forms a distribution chamber 4 and the first connection 5 forms a supply connection 5. On the heat exchanger block 2, a second chamber 7 is also formed at a second transverse end 6, which faces away from the first transverse end 3 in the block transverse direction Y, which second chamber 7 extends longitudinally in the block height direction Z and has a second connection 8. In the example shown here, the second chamber 7 forms a collection chamber 7 and the second connection 8 forms a discharge connection 8.

[0058] According to Figures 1 to 3, a plurality of first flow channels 9 for guiding a first fluid are formed in the heat exchanger block 2, which first flow channels 9 penetrate the heat exchanger block 2 in the block longitudinal direction X and which fluidically connect an inflow side 10 of the heat exchanger block 2 exposed to the first fluid, which is located at a first longitudinal end 11 of the heat exchanger block 2 facing the viewer in Figures 1 to 3, with an outflow side 12 exposed to the first fluid, which is located at a second longitudinal end 13 of the heat exchanger block 2 facing away from the viewer in Figures 1 to 3. A flow of the first fluid through the heat exchanger block 2 or the first flow channels 9 that occurs during operation of the heat exchanger 1 is indicated by arrows in Figures 2 and designated 14.According to Figures 2 and 3, a plurality of second flow channels 15 for conducting a second fluid are also formed in the heat exchanger block 2, which second flow channels 15 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 distribution chamber 4 to the collection chamber 7. A flow of the second fluid through the heat exchanger block 2 or the distribution chamber 4, the connecting pipes 15 and the collection chamber 7, which occurs during operation of the heat exchanger 1, is indicated by arrows in Figures 1 to 3 and designated by 16.

[0059] According to Figures 2 and 3, in the heat exchanger block 2, a plurality of second flow channels 15 are arranged next to one another in the block longitudinal direction X and form a longitudinal channel row 17. In the example shown, each longitudinal channel row 17 contains ten second flow channels 15. In the heat exchanger block 2, a plurality of longitudinal channel rows 17 are arranged next to one another in the block height direction Z. For example, nine such longitudinal channel rows 17 can be seen in each of Figures 2 and 3. It is clear that in the heat exchanger block 2, significantly more longitudinal channel rows 17 can be arranged next to one another in the block height direction Z, for example, more than fifty.

[0060] The heat exchanger block 2 has a block longitudinal center plane 18, indicated in Figures 2 and 3 by a dash-dotted line, which runs transversely to the block longitudinal direction X. According to Figure 4, the second flow channels 15 each have a first opening 19 on the distribution chamber 4, which here forms an inlet opening 19 and has a flow-through circular inlet cross-section 43. 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 regard to their inlet cross-sections 43 such that in the respective longitudinal channel row 17, the size of the longitudinal diameter 20 correlates with the distance of the respective second flow channel 15 from the block longitudinal center plane 18, specifically such that the second flow channels 15, which are at a greater distance from the block longitudinal center plane 18, have an inlet cross-section 43 with a larger longitudinal diameter 20 than second flow channels 15, which are at a smaller distance from the block longitudinal center plane 18. This transition from a larger longitudinal diameter 20 to a smaller longitudinal diameter 20 is shown purely as an example in Figure 5. Figure 5A shows the inlet cross-section 43 of an inlet opening 19 of a second flow channel 15, which is comparatively far away from the block longitudinal center plane 18.In contrast, Figure 5B shows the inlet cross-section 43 of an inlet opening 19 of a second flow channel 15, which is located relatively close to the block's longitudinal center plane 18. The longitudinal diameter 20 clearly increases with increasing distance from the block's longitudinal center plane 18. A corresponding transition is indicated in Figure 5 by an arrow and designated 22. In the example shown, it can also be provided that the vertical diameter 21 of the inlet cross-section 43 of the inlet opening 19 is the same size for all second flow channels 15 of the respective channel longitudinal row 17, i.e., remains constant.

[0061] The same can optionally also apply in the area of ​​the collection chamber 7. For simplification, this relationship is also explained using Figures 4 and 5. If the chamber shown in Figure 4 is the collection chamber 7, the outlet openings of the second flow channels 15 are not inlet openings 19, but rather second openings 23 or outlet openings 23, whose outlet cross-sections 44 also have a longitudinal diameter 20 and a vertical diameter 21.The second flow channels 15 are then configured with regard to their outlet cross-section 44 such that, in the respective longitudinal channel row 17, the size of the longitudinal diameter 20 correlates with the distance of the respective second flow channel 15 from the block longitudinal center plane 18, such that the second flow channels 15 that are at a greater distance from the block longitudinal center plane 18 have an outlet cross-section 44 with a larger longitudinal diameter 20 than second flow channels 15 that are at a smaller distance from the block longitudinal center plane 18. Here too, according to Figures 5A and 5B, it can be provided that the height diameter 21 of the outlet cross-section 44 is the same for all second flow channels 15 of the respective longitudinal channel row 17.

[0062] In the example of Figure 5, in the second flow channels 15, which are arranged close to the block longitudinal center plane 18, the respective cross section 43, 44 at the inlet openings 19 and at the outlet openings 23 is circular, whereas in the second flow channels 15 spaced from the block longitudinal center plane 18, the respective cross section 43, 44 at the inlet openings 19 and at the outlet openings 23 is elliptical.

[0063] In another embodiment, which is explained in more detail in connection with Figure 6, the second flow channels 15 can be configured with regard to their flow resistance such that in the respective longitudinal channel row 17, the size of the flow resistance of the respective second flow channel 15 correlates with the distance of the respective second flow channel 15 from the block longitudinal center plane 18, in such a way that the second flow channels 15 that are at a greater distance from the block longitudinal center plane 18 have a greater flow resistance than second flow channels 15 that are at a smaller distance from the port block longitudinal center plane 18. It is conceivable that the flow resistance of the second flow channels 15 is increased by obstacles that are formed in the second flow channels 15 for this purpose.In this case, this embodiment can also be combined with the embodiment described above, in which the longitudinal diameters 20 vary for second flow channels 15 adjacent in the block longitudinal direction X.

[0064] In conjunction with Figures 6A and 6B, another embodiment is explained in more detail, in which the flow resistance of the respective second flow channel 15 is varied with the aid of the flow-through cross-sectional area 24 of the respective second flow channel 15. In the example of Figures 6A and 6B, the second flow channels 15 each have a circular flow-through cross-section 45. It can now be expediently provided that in the respective longitudinal row 17 of channels, the size of the flow-through cross-sectional area 24 of the respective second flow channel 15 correlates with the distance of the respective second flow channel 15 from the block longitudinal center plane 18, in such a way that the second flow channels 15 which are at a greater distance from the block longitudinal center plane 18 have a smaller flow-through cross-sectional area 24 than second flow channels 15 which are at a smaller distance from the block longitudinal center plane 18.Figure 6A shows the permeable cross-sectional area 24 of a second flow channel 15, which is at a comparatively large distance from the block's longitudinal center plane 18, while Figure 6B shows the permeable cross-sectional area 24 of a second flow channel 15, which is at a comparatively small distance from the block's longitudinal center plane 18. The permeable cross-sectional area 24 clearly decreases with increasing distance from the block's longitudinal center plane 18. A corresponding transition is indicated in Figure 6 by an arrow and designated 25.

[0065] According to Figure 1, the heat exchanger block 2 has a central transverse region 26, which is spaced apart from the first transverse end 3 and the second transverse end 6. Furthermore, the heat exchanger block 2 has a first transition region 27, which connects the central transverse region 26 to the distribution chamber 4. Furthermore, the heat exchanger block 2 has a second transition region 28, which connects the central transverse region 26 to the collection chamber 27.

[0066] The relationship described above, according to which the flow-through cross-sectional area 24 of the respective second flow channel 15 decreases with increasing distance of the respective second flow channel 15 from the block longitudinal center plane 18, applies at least to the central transverse region 26 of the heat exchanger block 2. This relationship also expediently applies in the first transition region 27 and / or in the second transition region 28.

[0067] In principle, the second flow channels 15 can be configured such that their flow-through cross-sectional area 24 decreases from the inlet opening 19 opening at the distribution chamber 4 to the central transverse region 26 and / or increases from the central transverse region 26 to the outlet opening 23 opening at the collection chamber 7. Preferably, it can be provided that in the second flow channels 15, the flow-through cross-sectional area 24 decreases from the inlet opening 19 within the first transition region 27 to the central transverse region 26, is constant in the central transverse region 26, and increases from the central transverse region 26 to the outlet opening 23, i.e. within the second transition region 28. The decrease in cross-section in the central transverse region 26 also makes it possible, in particular, to vary the flow resistance of the second flow channels 15.

[0068] In an alternative embodiment, however, it can be provided that the second flow channels 15 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 opening cross-section 45 can be constant or can vary.

[0069] According to Figures 2 and 3, the second flow channels 15 can optionally also be configured such that second flow channels 15, which are spaced apart from or facing away from the block longitudinal center plane 18, run inclined to the block transverse direction Y in the first transition region 27 or in the second transition region 28. In Figures 2 and 3, for each second flow channel 15 which faces away from the block longitudinal center plane 18, i.e., has the greatest distance from the block longitudinal center plane 18 within the respective channel longitudinal row 17, a longitudinal center axis 29 is shown as an example and representative of 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 angle of inclination 30 or an inclination 30 with respect to the block transverse direction Y.Particularly advantageous is the embodiment shown here, in which the inclination 30 increases from the central transverse region 26 in the first transition region 27 to the distribution chamber 4 and increases in the second transition region 28 from the central transverse region 26 to the collection chamber 7. Thus, the second flow channels 15 at the distribution chamber 4 and at the collection chamber 7 are distributed in the block longitudinal direction X over a larger area than in the central transverse region 26 of the heat exchanger block 2.

[0070] Figures 7 and 8 show second flow channels 15 or wall material of the heat exchanger block 2 which delimits the second flow channels 15, either in the first transition region 27 leading to the distribution chamber 4 or in the second transition region 28 leading to the collection chamber 7. Figure 7A shows an isometric view of a second flow channel 15. Figure 7B shows a side view of the second flow channel 15 in a viewing direction parallel to the block height direction Z. Figure 7C shows a side view of the second flow channel 15 in a viewing direction parallel to the block longitudinal direction X. Figure 8 shows an isometric view of a plurality of second flow channels 15 which are arranged next to one another in the block height direction Z. Figures 7 and 8 each show second flow channels 15 which are at a comparatively large distance from the block longitudinal center plane 18.In particular, these may be the second flow channels 15 which are furthest away from the block longitudinal center plane 18.

[0071] The second flow channels 15 can now expediently be configured such that those second flow channels 15 which are spaced apart from or facing away from the block longitudinal center plane 18 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 central transverse region 26 along the block transverse direction Y. In the examples in Figures 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 in Figure 5A, has the larger longitudinal diameter 20 in the block longitudinal direction X.This elliptical opening cross-section 45 then transitions into a circular opening cross-section 45 along the block transverse direction Y within the first transition region 27 up to the central transverse region 26. This circular opening cross-section 45 is located in Figures 7 and 8 at the lower end of the section of the second flow channel 15 shown. Circular cross-sections 45 are shown purely as examples in Figures 5B, 6A and 6B. The same can optionally also apply in the second transition region 28. The second flow channels 15 then have an elliptical opening cross-section 45 in their outlet opening 23 opening into the collection chamber 7, which is elongated in the block longitudinal direction X and which transitions into a circular opening cross-section 45 along the block transverse direction Y within the second transition region 28 up to the central transverse region 26.

[0072] According to Figures 2 and 4, the distribution chamber 4 has, on a distribution side 31 facing the second flow channels 15, a profile running transversely to the block height direction Z, which is concavely curved towards the interior of the distribution chamber 4. The inlet openings 19 are located in the distribution side 31. According to Figures 3 and 4, the collection chamber 7 has, on a collection side 32 facing the second flow channels 15, a profile running transversely to the block height direction Z, which is concavely curved towards the interior of the collection chamber 7. The outlet openings 23 are located in the collection side 32. This design achieves a flow-optimized transition from the distribution chamber 4 into the second flow channels 15 and from the second flow channels 15 into the collection chamber 7, which is characterized by reduced flow resistance.

[0073] As can be seen in particular from Figures 1 to 3, in the heat exchanger block 2, a plurality of first flow channels 9 are arranged next to one another in the block transverse direction Y, such that they form a transverse channel row 33. For example, each transverse channel row 33 can have more than twenty or more than fifty first flow channels 9. In the heat exchanger block 2, a plurality of transverse channel rows 33 are now arranged next to one another in the block height direction Z. According to Figure 1, the heat exchanger block 1 has a central height region 34 which is spaced from lateral block ends 35, 36 which face away from one another in the block height direction Z. The transverse channel rows 33 are each guided through the heat exchanger block 2 between two adjacent longitudinal channel rows 17, at least in this central height region 34.This results in a particularly compact arrangement of intersecting first flow channels 9 and second flow channels 15, which promotes intensive heat transfer.

[0074] In several or all of the second flow channels 15 and / or in several or all of the first flow channels 9, ribs or knobs can protrude into the flow-through cross-section 45, so that the first fluid or the second fluid can flow against and / or around these ribs or knobs. Without limiting the generality, Figure 9 shows an example of two helically designed ribs 37 that extend helically along the respective second flow channel 15, i.e. along the block transverse direction Y, or along the respective first flow channel 9, i.e. along the block longitudinal direction X. It is clear that more than two such ribs 37 can also be present in the respective channel 9, 15.

[0075] In Figure 10, depressions 38 can be seen which are formed in an inner side 39 which is exposed to the second fluid. The inner side 39 can belong to the collection chamber 7 or to the distribution chamber 4 or to one of the second flow channels 15, there preferably in the first transition region 27 or in the second transition region 28. The depressions 38 enlarge the surface area of ​​the respective inner side 39. For example, the depressions 38 can have a constriction 40 at the transition to the inner side 39. As a result, a cross-section 41 of the respective depression 38 is larger within the respective depression 38 than within the constriction 40. 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 Figure 10, the cross-section 41 measured within the respective depression 38 is also designated 411.The significantly smaller cross-section 41 within the constriction 40 is also designated 412.

[0076] In Figures 1 to 10, the heat exchanger 1 is designed as a cross-flow heat exchanger 1, so that the first flow channels 9 pass through the heat exchanger block 2 in the block longitudinal direction X and fluidically connect 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.

[0077] Furthermore, in the example of Figures 1 to 10, it is provided that the first chamber 4 forms a distribution chamber 4 and has the supply connection 5, while the second chamber 7 forms a collection chamber 7 and has the discharge connection 8.

[0078] Figure 11 now shows, purely by way of example and in a highly simplified manner, another embodiment in which the first chamber 4 has or forms a distribution chamber 46 and a collection chamber 47. This can be achieved, for example, by means of a partition wall 48, which divides the first chamber 4 in order to form the distribution chamber 46 and the collection chamber 47 therein. The first connection 5 is then formed on the distribution chamber 46 and forms a supply connection 5, while the second connection 8 is formed on the collection chamber 47 and forms a discharge connection 8. In this case, the second chamber 7 forms a deflection chamber 49. For example, a web 50 can be formed in the second chamber 7 for this purpose, which guides or supports the flow deflection of the second fluid in the deflection chamber 49. A first group 51 of several second flow channels 15 connects the distribution chamber 46 to the deflection chamber 49.A second group 52 of several second flow channels 15 connects the deflection chamber 49 to the collection chamber 47. In another alternative embodiment, which is indicated purely by way of example and in a highly simplified manner in Figure 12, the heat exchanger 1 can, however, 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 first flow channels 9 and second flow channels 15 alternate in the block height direction Z and / or in the block longitudinal direction X. Figure 12 shows how in the central transverse region 26 first flow channels 9 and second flow channels 15 alternate in the block longitudinal direction X and cross over in the transition regions 27, 28 in a media-separated manner.

[0079] Furthermore, in the embodiment as a parallel flow heat exchanger 1 according to Figure 12, 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 channels 9, while the second sub-chamber 54 is fluidically connected to the second flow channels 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 channels 9, while the fourth sub-chamber 56 is fluidically connected to the second flow channels 15.

[0080] Optionally, according to Figure 12, it can then also be provided that the first sub-chamber 53 forms a collecting chamber 53 for the first flow channels 9, that the second sub-chamber 54 forms a distribution chamber 54 for the second flow channels 15, that the third sub-chamber 55 forms a distribution chamber 55 for the first flow channels 9, and that the fourth sub-chamber 56 forms a collecting chamber 7 for the second flow channels 15. The first connection 5 serves as a supply connection 5 for the second fluid and is formed on the second sub-chamber. The second connection 8 serves as a discharge connection 8 for the second fluid and is formed on the fourth sub-chamber 56. A third connection 57 serves as a supply connection 57 for the first fluid and is formed on the third sub-chamber 55. A fourth connection 58 serves as a discharge connection 58 for the first fluid and is formed on the first sub-chamber 53.

[0081] If the heat exchanger 1 is designed as a parallel-flow heat exchanger 1, all of the configurations and features described above with regard to Figures 1 to 10, which relate to the second flow channels 15, can also be implemented correspondingly in the first flow channels 9. This applies in particular to the geometric configurations of the openings which open into the respective chamber 4, 7 or sub-chamber 53, 54, 55, 56, and / or to the variation of the flow-through cross-sections in the block transverse direction Y within the flow channels 9, 15 and in the block longitudinal direction X for adjacent flow channels 9, 15. In particular, the first flow channels 9 in the heat exchanger block 2 can therefore also form longitudinal channel rows with a plurality of first flow channels 9 adjacent in the block longitudinal direction X, wherein a plurality of such longitudinal channel rows are adjacent in the block height direction Z.

[0082] Basically, according to Figures 1 to 12, an embodiment is preferred in which the second flow channels 15 of the respective longitudinal row 17 of channels extend separately from the first chamber 4 to the second chamber 7 and each have separate inlet openings 19 and separate outlet openings 23 there. In another embodiment, shown purely by way of example and in a highly simplified manner in Figure 13, it can be provided that the second flow channels 15 of the respective longitudinal row 17 of channels run separately from one another at least in the central transverse region 26 of the heat exchanger block 2, while they are combined to form 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

Claims 1 . Additively manufactured heat exchanger (1 ) for media-separated heat transfer between a first fluid and a second fluid, in particular for cooling a gas, - with an additively manufactured heat exchanger block (2) which has a block longitudinal direction (X), a block transverse direction (Y) and a block height direction (Z) which run perpendicular to one another, - wherein a plurality of first flow channels (9) for guiding a first fluid are formed in the heat transfer block (2), which flow channels penetrate the heat transfer block (2), - wherein a first chamber (4) is formed on the heat exchanger block (2) at a first transverse end (3), which extends 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) which faces away from the first transverse end (3) in the block transverse direction (Y), said second chamber extending in the block height direction (Z), - wherein a plurality of second flow channels (15) for conducting a second fluid are formed in the heat exchanger block (2), which second flow channels (15) are fluidically separated from the first flow channels (9), which penetrate the heat exchanger block (2) in the block transverse direction (Y) and which fluidically connect the first chamber (4) to the second chamber (7), - wherein the heat exchanger (1) has a first connection (5) for supplying or discharging the second fluid and a second connection (8) for discharging or supplying the second fluid, - wherein in the heat exchanger block (2) a plurality of second flow channels (15) are arranged next to one another in the block longitudinal direction (X) and form a longitudinal channel row (17), - wherein in the heat exchanger block (2) several longitudinal rows of channels (17) are arranged next to one another in the block height direction (Z).

2. Heat exchanger (1) according to claim 1, characterized in that - that the heat exchanger block (2) has a longitudinal center plane (18) running transversely to the block longitudinal direction (X), - that the second flow channels (15) are configured with regard to their flow resistance such that in the respective channel longitudinal row (17) the size of the flow resistance of the respective second flow channel (15) correlates with the distance of the respective second flow channel (15) from the block longitudinal center plane (18), so that the second flow channels (15) which are at a greater distance from the block longitudinal center plane (18) have a greater flow resistance than second flow channels (15) which are at a smaller distance from the block longitudinal center plane (18).

3. Heat exchanger (1) according to claim 1 or 2, characterized in that - that the heat exchanger block (2) has a longitudinal center plane (18) running transversely to the block longitudinal direction (X), - that the second flow channels (15) are configured with regard to their flow-through cross-sectional area (24) such that in the respective channel longitudinal row (17) the size of the flow-through cross-sectional area (24) of the respective second flow channel (15) correlates with the distance of the respective second flow channel (15) from the block longitudinal center plane (18), so that the second flow channels (15) which are separated from the block longitudinal center plane (18) a greater distance, have a smaller flow-through cross-sectional area (24) than second flow channels (15), which have a smaller distance from the block longitudinal center plane (18).

4. Heat exchanger (1) according to claim 3, characterized in that - that the heat exchanger block (2) has a central transverse region (26) which is spaced from the first transverse end (3) and the second transverse end (6), - that the second flow channels (15) are configured with regard to their flow-through cross-sectional area (24) such that, at least in the central transverse region (26) in the respective channel longitudinal row (17), the size of the flow-through cross-sectional area (24) of the respective second flow channel (15) correlates with the distance of the respective second flow channel (15) from the block longitudinal center plane (18), so that the second flow channels (15) which are at a greater distance from the block longitudinal center plane (18) have a smaller flow-through cross-sectional area (24) than second flow channels (15) which are at a smaller distance from the block longitudinal center plane (18).

5. Heat exchanger (1) according to one of claims 1 to 4, characterized in that - that the heat exchanger block (2) has a central transverse region (26) which is spaced from the first transverse end (3) and the second transverse end (6), - that the second flow channels (15) have a cross-sectional area (24) through which flow can take place, which decreases from a first opening (19) opening into the first chamber (4) to the central transverse region (26) and / or increases from the central transverse region (26) to a second opening (23) opening into the second chamber (7).

6. Heat exchanger (1) according to one of claims 1 to 5, characterized in that - that the heat exchanger block (2) has a central transverse region (26) which is spaced from the first transverse end (3) and the second transverse end (6), - that the heat exchanger block (2) has a first transition region (27) at the first transverse end (3) which connects the first chamber (4) to the central transverse region (26), and a second transition region (28) at the second transverse end (6) which connects the second chamber (7) to the central transverse region (26), - that the heat exchanger block (2) has a longitudinal center plane (18) running transversely to the block longitudinal direction (X), - that the second flow channels (15) in the central transverse region (26) run parallel to the block transverse direction (Y), - that second flow channels (15), which are spaced apart from or facing away from the block longitudinal center plane (18), run in the first transition region (27) and / or in the second transition region (28) inclined to the block transverse direction (Y), wherein the inclination (30) increases from the central transverse region (26) to the distribution chamber (4) and / or to the collection chamber (7).

7. Heat exchanger (1) according to one of claims 1 to 6, characterized in that - that the heat exchanger block (2) has a central transverse region (26) which is spaced from the first transverse end (3) and the second transverse end (6), - that the heat exchanger block (2) has a first transition region (27) at the first transverse end (3) which connects the first chamber (4) to the central transverse region (26), and a second transition region (28) at the second transverse end (6) which connects the second chamber (7) to the central transverse region (26), - that the heat exchanger block (2) has a longitudinal center plane (18) running transversely to the block longitudinal direction (X), - that at least the second flow channels (15), which are spaced apart from or facing away from the block longitudinal center plane (18), have a varying opening cross-section (45) in the first transition region (17) and / or in the second transition region (28) along the block transverse direction (Y).

8. Heat exchanger (1) according to claim 7, characterized in that - that at least the second flow channels (15), which are spaced apart from or facing away from the block longitudinal center plane (18), have an opening cross-section (45) in the central transverse region (26) which is constant along the block transverse direction (Y).

9. Heat exchanger (1) according to claim 7 or 8, characterized in that - that at least the second flow channels (15), which are spaced apart from or facing away from the block longitudinal center plane (18), have an elliptical opening cross-section (45) in a first opening (19) opening into the first chamber (4), which is elongated in the block longitudinal direction (X) and which merges into a circular opening cross-section (45) along the block transverse direction (Y) within the first transition region (27) up to the central transverse region (26), and / or - that at least the second flow channels (15), which are spaced apart from or facing away from the block longitudinal center plane (18), have an elliptical opening cross-section (45) in a second opening (23) opening into the second chamber (7), which is elongated in the block longitudinal direction (X) and which extends along the block transverse direction (Y) within the second transition region (28) to to the central transverse region (26) into a circular opening cross-section (45).

10. Heat exchanger (1) according to one of claims 1 to 9, characterized in that - that the first chamber (4) forms or has a distribution chamber (4) which supplies the second fluid to the second flow channels (15), - that the first connection (5) is formed on the distribution chamber (4) and forms a supply connection (5) for supplying the second fluid to the distribution chamber (4), - that the distribution chamber (4) has, on a distribution side (31) facing the second flow channels (15), a profile running transversely to the block height direction (Z) which is concavely curved towards the interior of the distribution chamber (4).

11. Heat exchanger according to one of claims 1 to 10, characterized in that - that the second chamber (7) forms or has a collecting chamber (7) which receives the second fluid coming from the second flow channels (15), - that the second connection (8) is formed on the collecting chamber (7) and forms a discharge connection (8) for discharging the second fluid from the collecting chamber (7), - that the collecting chamber (7) has, on a collecting side (32) facing the connecting channels (15), a profile running transversely to the block height direction (Z) which is concavely curved towards the interior of the collecting chamber (7).

12. Heat exchanger (1) according to one of claims 1 to 11, characterized by - that in several or in all second flow channels (15) ribs (37) or knobs protrude into the flow-through cross-section (45), so that the ribs (37) or knobs can be flowed against and / or around by the second fluid.

13. Heat exchanger (1) according to one of claims 1 to 12, characterized in that - that in several or in all of the first flow channels (9) ribs (37) or knobs protrude into the flow-through cross-section (45), so that the ribs (37) or knobs can be flowed against and / or around by the first fluid.

14. Heat exchanger (1) according to claim 12 or 13, characterized in that - that the ribs (37) are designed helically so that they extend helically along the respective second flow channel (15) or along the respective first flow channel (9).

15. Heat exchanger (1) according to one of the preceding claims, characterized in that - that the first or second chamber (4, 7) has recesses (38) on its inner side (39) exposed to the second fluid in order to enlarge the surface of the inner side (39).

16. Heat exchanger (1) according to one of the preceding claims, characterized in that - that several or all second flow channels (15) are arranged at least in a transition region (27, 28) of the heat exchanger block (2) have recesses (38) on their inner side (39) exposed to the second fluid in order to enlarge the surface of the inner side (39).

17. Heat exchanger (1) according to claim 15 or 16, characterized in that - that the depressions (38) have a constriction (40) at the transition to the inner side (39), so that a cross-section (41) of the respective depression (38) running transversely to the normal direction (42) of the inner side (39) is larger within the respective depression (38) than in the constriction (40).

18. Heat exchanger (1) according to one of claims 1 to 9 and 12 to 17, characterized in that - that the first chamber (4) has or forms a distribution chamber (46) and a collection chamber (47), - that the first connection (5) is formed on the distribution chamber (46) and forms a supply connection (5), - that the second connection (8) is formed on the collecting chamber (47) and forms a discharge connection (8), - that the second chamber (7) forms a deflection chamber (49).

19. Heat exchanger (1) according to one of claims 1 to 18, characterized in that - that the heat exchanger (1 ) is designed as a cross-flow heat exchanger (1 ), - that the first flow channels (9) pass through the heat exchanger block (2) in the block longitudinal direction (X) and connect an inflow side (10) of the heat exchanger block (2) exposed to the first fluid with a first fluid exposed downstream side (12) of the heat exchanger block (2).

20. Heat exchanger (1) according to claim 19, characterized in that - that in the heat exchanger block (2) several first flow channels (9) are arranged next to one another in the block transverse direction (Y) and form a transverse row of channels (33), - that in the heat exchanger block (2) several transverse rows of channels (33) are arranged next to one another in the block height direction (Z), - that the heat exchanger block (2) has a central height region (34) which is spaced from lateral block ends (35, 36) which face away from each other in the block height direction (Z), - that the transverse rows of channels (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 longitudinal rows of channels (17).

21. Heat exchanger (1) according to one of claims 1 to 17, characterized in that - that the heat exchanger (1 ) is designed as a parallel flow heat exchanger (1 ), - that the first flow channels (9) pass through the heat exchanger block (2) in the block transverse direction (Y), - that 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. Heat exchanger (1) according to claim 21, characterized in that - that the first chamber (4) has or forms a first sub-chamber (53) and a second sub-chamber (54), - that the first sub-chamber (53) is fluidically connected to the first flow channels (9), while the second sub-chamber (54) is fluidically connected to the second flow channels (15), - that the second chamber (7) has or forms a third sub-chamber (55) and a fourth sub-chamber (56), - that the third sub-chamber (55) is fluidically connected to the first flow channels (9), while the fourth sub-chamber (56) is fluidically connected to the second flow channels (15).

23. Heat exchanger according to claim 22, characterized in that - that the first sub-chamber (53) forms a collecting chamber for the first flow channels (9), - that the second sub-chamber (54) forms a distribution chamber for the second flow channels (15), - that the third sub-chamber (55) forms a distribution chamber for the first flow channels (9), - that the fourth sub-chamber (56) forms a collecting chamber for the second flow channels (15). *****

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