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), in which a plurality of first flow channels (9) for conducting a first fluid are formed, which channels pass through the heat exchanger block (2), a first chamber (4) being formed at a first transverse end (3) of the heat exchanger block (2), and a second chamber (5) being formed at a second transverse end (6) of the heat exchanger block (2). Wherein a second chamber (7) is formed on a second transverse end (6) of the heat exchanger block (2), and wherein a plurality of second flow channels (15) for conducting a second fluid are formed in the heat exchanger block (2), which channels are fluidically separated from the first flow channels (9), pass through the heat exchanger block (2) in the block transverse direction (Y), and fluidically connect the first chamber (4) to the second chamber (7). The distribution of thermal and / or mechanical stresses is advantageous if a plurality of second flow channels (15) are arranged next to one another in the block longitudinal direction (X) and form a channel longitudinal row (17) in the heat exchanger block (2), and if a plurality of channel longitudinal rows (17) are arranged next to one another in the block height direction (Z) in the heat exchanger block (2).

Description

Technical Field

[0001] The present invention relates to an additively manufactured heat exchanger for media-divided heat transfer between a first fluid and a second fluid, in particular for cooling a gas. Background Art

[0002] Additive manufacturing, especially 3D printing, allows for the realization of geometries that are impossible or only very cost-effective using conventional manufacturing methods such as casting and machining. Additive manufacturing can be performed using both plastics and metals.

[0003] The heat exchanger has a heat exchanger block In this heat exchanger block, heat transfer occurs between two different fluids in a medium-separated manner. In conventional designs, heat exchanger blocks consist of multiple separate components that are assembled together in a suitable manner. For example, a conventional heat exchanger block includes distribution pipes or distribution boxes and headers or headers, which are fluidically connected by a large number of connecting pipes. Interspaces are formed between adjacent connecting pipes, where fins are typically located. A first fluid to be heated or cooled passes through these interspaces. A second fluid to be supplied or removed from heat passes through the connecting pipes. The second fluid is supplied to the connecting pipes via the distribution pipes or distribution boxes. The second fluid is discharged from the connecting pipes via the headers or headers. During operation of the heat exchanger, thermal and / or mechanical stress peaks occur, particularly at the transitions between the connecting pipes and the distribution pipes or headers, which the heat exchanger block must be able to withstand. As a result, the heat exchanger block is inevitably oversized in many areas. Furthermore, the heat transfer performance of a heat exchanger is dependent on the surface area available for heat transfer. The number of connecting pipes that can be implemented is limited, for example, by their manufacturability, space requirements, and the connection technology used (typically welding). Summary of the Invention

[0004] The present invention is directed to the problem of providing an improved or at least another embodiment of a heat exchanger, which embodiment is characterized 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] According to the invention, this problem is solved by the subject matter of the independent claims. Advantageous embodiments are the subject matter of the dependent claims.

[0006] The present invention is based on the following general concept: additively manufacture a heat exchanger block such that a plurality of first flow channels for conducting a first fluid are formed in the heat exchanger block. These first flow channels extend through the heat exchanger block in one direction, for example, in the longitudinal or transverse direction of the block, so that the first fluid can flow through the heat exchanger block in the first flow channels in a direction defined by these channels. Furthermore, a first chamber is formed at a first transverse end of the heat exchanger block, extending, for example, in the direction of the block's height. The heat exchanger has a first connection for supplying or draining a second fluid. Furthermore, a second chamber is formed at a second transverse end of the heat exchanger block (opposite the first transverse end in the transverse direction of the block), extending in the direction of the block's height. The heat exchanger has a second connection for supplying or draining the second fluid. Furthermore, a plurality of second flow channels for conducting the second fluid are formed in the heat exchanger block. These second flow channels are fluidically separate from the first flow channels, extend through the heat exchanger block in the transverse direction of the block, and fluidically connect the first and second chambers. Here, additive manufacturing of a heat exchanger block enables the arrangement of multiple second flow channels in the heat exchanger block, either side by side or sequentially in the block's longitudinal direction, to form a longitudinal channel row. Multiple such longitudinal channel rows can then be arranged side by side in the heat exchanger block's height. For example, within a corresponding longitudinal channel row, at least three, preferably at least five, and particularly at least ten connecting channels can be arranged side by side in the block's longitudinal direction. Compared to conventionally manufactured heat exchanger blocks (where a maximum of two connecting pipes are arranged side by side in the block's longitudinal direction), the proposed structure significantly increases the surface area available for heat transfer within the same installation space requirement. Furthermore, the additively manufactured structure allows for more material to be available for heat transfer in the heat exchanger block because the second and first flow channels extend through the material of the heat exchanger block. In contrast, in conventional structures, the material of the heat exchanger block consists solely of the walls of the connecting pipes and, if necessary, the walls of the fins arranged between them. Consequently, the additively manufactured heat exchanger block offers a greater amount of material available for heat transfer.

[0007] During conventional manufacturing of heat exchanger blocks, the connecting pipes pass through the side walls defining the distribution pipes or distribution boxes and the headers or headers and thus extend into the interior of the distribution pipes / distribution boxes or headers / distribution boxes, forming flow obstacles there. However, in additive manufacturing, such protrusions are not required, thereby significantly reducing the flow resistance of the second fluid in the heat exchanger.

[0008] Such heat exchangers can be used, for example, in hydrogen filling stations to cool the hydrogen when filling vehicle tanks.

[0009] According to one advantageous embodiment, the first chamber can constitute or include a distribution chamber that supplies the second fluid to the second flow channel, wherein the first connection constitutes a supply connection for supplying the second fluid to the distribution chamber. The heat exchanger block can have a block longitudinal midplane extending transversely to the block longitudinal direction and extending centrally through the heat exchanger block relative to the block longitudinal direction. Furthermore, the second flow channels can each have an inlet opening at the distribution chamber, each having a round (smooth, no corners) 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 be configured with respect to their inlet cross sections such that, in each longitudinal channel row, the size of the inlet cross section of the inlet opening of each second flow channel is correlated with the distance of the second flow channel from the block longitudinal midplane. Specifically, second flow channels that are at a greater distance from the block longitudinal midplane have an inlet cross section with a larger longitudinal diameter than second flow channels that are at a smaller distance from the block longitudinal midplane. In other words, the longitudinal diameter of the inlet cross section of the inlet opening increases with increasing distance from the longitudinal mid-plane of the block.This measure helps to reduce thermal and / or mechanical stress peaks.

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

[0011] An advantageous configuration is that at all inlet openings the longitudinal diameter of the inlet cross section is at least as large as the height diameter. The inlet cross section can in particular be circular (perfectly circular) or elliptical.

[0012] According to an advantageous embodiment, the inlet cross-sections of the inlet openings of all second flow channels in each longitudinal channel row can have the same height diameter. Consequently, the inlet cross-sections of the inlet openings of the second flow channels that are spaced apart from the longitudinal midplane of the block are flat or elongated. Furthermore, the inlet cross-sections of the inlet openings of the second flow channels arranged in the region of the longitudinal midplane of the block can be circular, while the inlet cross-sections of the inlet openings of the second flow channels that are spaced apart from the longitudinal midplane of the block can be elliptical, with the elliptical cross-section becoming increasingly flatter or elongated as the distance of the second flow channels from the longitudinal midplane of the block increases.

[0013] According to another embodiment, it can be provided that the second chamber forms or has a collecting chamber which receives the second fluid from the second flow channel, wherein the second connection forms an outlet connection for discharging the second fluid from the collecting chamber.

[0014] The above description of the transition between the distribution chamber and the second flow channel also applies to the transition between the second flow channel and the collecting chamber. Accordingly, the second flow channels preferably each have an outlet opening at the collecting chamber, each having a circular outlet cross-section through which flow can pass, 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. The second flow channels are preferably configured with respect to their outlet cross-sections such that, in each longitudinal channel row, the size of the longitudinal diameter of the outlet cross-section of each second flow channel is correlated with the distance of the second flow channel from the longitudinal midplane of the block, so that second flow channels that are at a greater distance from the longitudinal midplane of the block have an outlet cross-section with a larger longitudinal diameter than second flow channels that are at a smaller distance from the longitudinal midplane of the block. Preferably, it can also be provided that the height diameter of the outlet cross-section of each second flow channel is the same for all second flow channels in each longitudinal channel row. It is also preferably provided that the longitudinal diameter is equal to or greater than the height diameter. Thus, the outlet cross section in the region of the block longitudinal midplane can in particular be circular, while the outlet cross section away from the block longitudinal midplane can be elliptical, wherein the elliptical cross section becomes increasingly flatter or elongated with increasing distance from the block longitudinal midplane.

[0015] According to an advantageous embodiment, the heat exchanger block has a block longitudinal midplane extending transversely to the block longitudinal direction, the block longitudinal midplane extending centrally through the heat exchanger block relative to the block longitudinal direction. Furthermore, the connecting channels can be configured with respect to their flow resistance such that, within each longitudinal channel row, the magnitude of the flow resistance of each second flow channel is correlated with its distance from the block longitudinal midplane, such that second flow channels at a greater distance from the block longitudinal midplane have a greater flow resistance than second flow channels at a smaller distance from the block longitudinal midplane. This measure ensures that, during operation of the heat exchanger, the volume flow of the second fluid is unevenly distributed among the second flow channels within each longitudinal channel row, such that the volume flow through the second flow channels in the region of the block longitudinal midplane is greater than the volume flow through the second flow channels spaced apart from the block longitudinal midplane, with the volume flow decreasing further with increasing distance from the block longitudinal midplane. This reduces stress peaks. This configuration utilizes the knowledge that thermal and / or mechanical stresses at the transition between the second flow channel and the first and / or second chambers (particularly the distribution chamber and / or the manifold chamber) are correlated with the distance from the longitudinal midplane of the block. These stresses increase with increasing distance from the longitudinal midplane of the block. By reducing the flow rate, the stresses in the longitudinal direction of the block can be evened out.

[0016] In this regard, a particularly suitable embodiment is to configure the second flow channels in terms of their flowable cross-sectional area so that, in each longitudinal row of channels, the size of the flowable cross-sectional area of ​​each second flow channel is correlated with its distance from the longitudinal midplane of the block. More precisely, second flow channels at a greater distance from the longitudinal midplane of the block have a smaller flowable cross-sectional area than second flow channels at a smaller distance from the longitudinal midplane of the block. The flow resistance of each second flow channel is correlated with the flowable cross-sectional area of ​​the second flow channel. The larger the flowable cross-sectional area, the lower the flow resistance. Therefore, the flow resistance can be particularly easily influenced by the flowable cross-sectional area. Alternatively, the flow resistance of the second flow channels can also be influenced by other measures. For example, within the scope of additive manufacturing, flow obstacles such as baffles, guide surfaces, fins, and bumps can be provided in second flow channels that are required to have a higher flow resistance.

[0017] The heat exchanger block includes a central transverse region that is spaced apart from the first and second transverse ends and transitions 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 previously described configuration of the second flow channel with respect to its flowable cross-sectional area preferably applies at least to the central transverse region, where the length of the second flow channel, measured in the transverse direction of the block, has the greatest influence on the flow resistance. The previously described configuration of the second flow channel with respect to its flowable cross-sectional area also advantageously applies to the first transition region connecting the first chamber to the central transverse region. Alternatively, the previously described configuration of the second flow channel with respect to its flowable cross-sectional area may also apply to the second transition region connecting the central transverse region to the second chamber.

[0018] According to an advantageous embodiment, the heat exchanger block can have a middle transverse region that is spaced apart from the first and second transverse ends. The second flow channels have a flowable cross-sectional area and can be configured such that their flowable cross-sectional area decreases from a first opening into the first chamber to the middle transverse region and / or increases from the middle transverse region to a second opening into the second chamber. In other words, the second flow channels have a flowable cross-sectional area that varies along the height of the block. This reduces thermal and / or mechanical stress peaks at the transition between the connecting channel and the first and / or second chambers.

[0019] According to one advantageous embodiment, the heat exchanger block can have a central transverse region that is spaced apart from the first and second transverse ends. Furthermore, the heat exchanger block has a first transition region at the first transverse end connecting the first chamber to the central transverse region, and a second transition region at the second transverse end connecting the second chamber to the central transverse region. Furthermore, the heat exchanger block has a block longitudinal center plane extending transversely to the block longitudinal direction. The second flow channel can now be configured so that it extends parallel to the block transverse direction in the central transverse region. Furthermore, the second flow channel can be configured so that the second flow channel, spaced apart from the block longitudinal center plane, extends obliquely relative to the block transverse direction in the first and / or second transition regions, with the inclination increasing from the central transverse region to the first and / or second chambers. This results in the second flow channel in the respective transition region forming a fan-shaped profile. This configuration has been shown to reduce thermal and / or mechanical stress peaks in the respective transition regions.

[0020] According to an advantageous embodiment, the heat exchanger block has a central transverse region that is spaced apart from a first transverse end and a second transverse end. The heat exchanger block has a first transition region at the first transverse end, connecting the first chamber to the central transverse region, and a second transition region at the second transverse end, connecting the second chamber to the central transverse region. The heat exchanger block also has a block longitudinal midplane extending transversely to the block longitudinal direction. Advantageously, the second flow channels can now be configured such that at least those second flow channels spaced apart from or facing away from the block longitudinal midplane have a geometrically varying opening cross section along the block transverse direction in the first and / or second transition regions. Second flow channels facing away from the block longitudinal midplane are those second flow channels that are at the greatest distance from the block longitudinal midplane in the corresponding longitudinal channel row. The geometrically varying opening cross section can reduce thermal and / or mechanical stress peaks in the corresponding transition region.

[0021] According to an advantageous development, at least those second flow channels which are spaced apart from or facing away from the block longitudinal midplane 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 and varies in the two transition regions.

[0022] In principle, an embodiment is preferred in which the second flow channels of each longitudinal channel row extend separately and independently from the first chamber to the second chamber and each have a separate and independent inlet opening and / or outlet opening there. In another embodiment, provision can be made for the flow channels of each longitudinal channel row to extend separately and independently from one another at least in a central transverse region of the heat exchanger block (which is spaced apart from the first and second transverse ends) and to merge into a common channel in a first transition region to the first chamber and / or a second transition region to the second chamber of the heat exchanger block.

[0023] According to another refinement, at least those second flow channels that are spaced apart from or facing away from the block longitudinal midplane can have an elliptical opening cross section at their first opening into the first chamber, this opening cross section being elongated in the block longitudinal direction and transitioning to a circular opening cross section in a first transition region in the block transverse direction at a middle transverse region. Additionally or alternatively, at least those second flow channels that are spaced apart from or facing away from the block longitudinal midplane can have an elliptical opening cross section at their second opening into the second chamber, this opening cross section being elongated in the block longitudinal direction and transitioning to a circular opening cross section in a second transition region in the block transverse direction at a middle transverse region. Thus, in particular, the elliptical first opening can transition to a circular opening cross section in the first transition region, these circular opening cross sections particularly remaining constantly circular in the middle transverse region, and can transition again to an elliptical second opening in the second transition region. Using a circular cross section, in particular an elliptical and a circular cross section, in the second flow channels reduces thermal and / or mechanical stresses.

[0024] According to another advantageous embodiment, it can be provided that the first chamber constitutes or has a distribution chamber, which supplies the second fluid to the second flow channel, wherein the first interface constitutes a supply interface for supplying the second fluid to the distribution chamber. In this case, the distribution chamber can have a profile extending transversely to the block height direction on the distribution side facing the connecting channel, which is arched concavely toward the interior of the distribution chamber. Additionally or alternatively, in an embodiment in which the second chamber constitutes or has a collecting chamber (which receives the second fluid from the second flow channel) and the second interface constitutes a discharge interface for discharging the second fluid from the collecting chamber, it can be optionally provided that the collecting chamber has a profile extending transversely to the block height direction on the collecting side facing the connecting channel, which is arched concavely toward the interior of the collecting chamber. Thermal stress peaks and / or mechanical stress peaks can be reduced by the arched or curved profile on the distribution side of the distribution chamber and / or the collecting side of the collecting chamber.

[0025] The second flow channels, whose geometric cross-section varies in the block transverse direction, can optionally be configured such that their throughflow cross-sectional area 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 fins or projections extend into the through-flow cross section so that the fins or projections can be passed by the second fluid. and / or flow bypass As a result, the surface area available for heat transfer in the respective connecting channel can be increased.

[0027] According to an advantageous embodiment, the fins can be helical in shape, 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. Helical fins increase the surface area available for heat transfer and have a relatively low flow resistance.

[0028] According to an advantageous embodiment, the first chamber and / or the second chamber may have a recessed portion on the inner side receiving the second fluid to increase the inner surface area. In particular, in heat exchangers used in cooling circuits and forming evaporators therein, these recessed portions can significantly improve refrigerant evaporation. Such recessed portions are also referred to as re-entry cavities.

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

[0030] A particularly advantageous embodiment provides that the recess has a constriction at the transition to the inner side, so that the cross-section of the respective recess, extending transversely to the normal direction of the inner side, is larger within the recess than within the constriction. The constriction thus forms an undercut. Such a recess or undercut cannot be produced using conventional manufacturing methods, or can only be produced with great difficulty. It has been shown that a recess having such a constriction significantly supports the boiling behavior of the second fluid and increases 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 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 evaporates in the evaporator and is therefore predominantly liquid at the supply connection and predominantly gaseous at the discharge connection.

[0033] As described above, according to a preferred embodiment, the first chamber can be provided as a distribution chamber and have a first interface, which in turn forms the supply interface. The second chamber can be provided as a collecting chamber and have a second interface, which in turn forms the discharge interface. The distribution chamber and the collecting chamber are fluidically connected via a second flow channel. Thus, the second fluid flows through the heat exchanger block once in the transverse direction of the block, namely, from the distribution chamber through the second flow channel to the collecting chamber. In another embodiment, the first chamber can be provided as or as a distribution chamber and a collecting chamber, wherein the first interface is constructed on the distribution chamber and forms the supply interface, while the second interface is constructed on the collecting chamber and forms the discharge interface. In this case, the second chamber forms a deflection chamber. The deflection chamber is fluidically connected to the distribution chamber and the collecting chamber via a second flow channel. Therefore, in this configuration, the second fluid flows through the heat exchanger block twice, namely, from the distribution chamber through the first set of second flow channels to the deflection chamber, and from the deflection chamber through the second set of second flow channels to the collecting chamber.

[0034] A particularly advantageous embodiment provides for the heat exchanger to be designed as a cross-flow heat exchanger, i.e., in which the first flow channel and the second flow channel pass through the heat exchanger block according to the cross-flow principle, i.e., they cross or cross each other in a media-separating manner. Thus, the first flow channel passes through the heat exchanger block in the longitudinal direction of the block and fluidically connects the upstream side of the heat exchanger block, which is subject to the first fluid, with the downstream side of the heat exchanger block, which is subject 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 form a transverse channel row. In the heat exchanger block, a plurality of transverse channel rows are arranged side by side in the height direction of the block. The heat exchanger block has an intermediate height region that is spaced apart from the lateral ends of the block that face away from each other in the height direction of the block. At least in the intermediate height region of the heat exchanger block, the transverse channel rows can each extend through the heat exchanger block between two adjacent longitudinal channel rows. This results in an extremely compact design with a very large surface area for contact with the first and second fluids. In conventional designs, the heat exchanger block has only one flow-through gap between two adjacent connecting pipes, in which fins can be arranged to increase the surface area. In an additively manufactured heat exchanger block, a plurality of, preferably more than ten, and in particular more than twenty, first flow channels can be arranged side by side in the transverse direction of the block to form corresponding transverse channel rows.

[0036] As an alternative to a cross-flow configuration, in another embodiment, the heat exchanger can be configured as a parallel-flow heat exchanger, i.e., in which the first and second flow channels extend through the heat exchanger block according to the parallel-flow principle, i.e., they extend parallel to one another in a media-separated manner. Thus, the first flow channels extend through the heat exchanger block in the transverse direction of the block. In particular, it can be provided that the first and second flow channels in the heat exchanger block are arranged alternately in the block height direction and / or in the block longitudinal direction. This can improve the heat transfer efficiency.

[0037] According to an advantageous embodiment, the first chamber can include or form 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. Additionally, the second chamber can include or form 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. It is advantageous for each subchamber to have its own connection for supplying and / or discharging the first or second fluid. This allows for a particularly compact design.

[0038] A particularly advantageous configuration is one in which the first subchamber forms a manifold for the first flow channel and has an outlet connection for the first fluid, the second subchamber forms a distribution chamber for the second flow channel and has a supply connection for the second fluid, the third subchamber forms a distribution chamber for the first flow channel and has a supply connection for the first fluid, and the fourth subchamber forms a manifold for the second flow channel and has an outlet connection for the second fluid. This configuration also contributes to a compact design.

[0039] In the case of a parallel-flow heat exchanger, it can also be provided that all first and second flow channels extend parallel to one another in the intermediate transverse region, while several or all first and second flow channels intersect or traverse in a medium-dividing manner in the first transition region leading to the first and second subchambers and / or in the second transition region leading to the third and fourth subchambers. This also contributes to efficient heat transfer in a compact configuration.

[0040] If the heat exchanger is designed as a parallel-flow heat exchanger, all of the above-described configurations and features regarding the second flow channels can also be implemented correspondingly in the first flow channels. This applies in particular to the geometry of the openings leading to the respective chambers or subchambers and / or the variation of the flowable cross-sections within the flow channels in the transverse direction of the block, as well as the variation of the flowable cross-sections between adjacent flow channels in the longitudinal direction of the block. Thus, in particular, the first flow channels can also form longitudinal channel rows in the heat exchanger block, with a plurality of first flow channels adjacent to each other in the longitudinal direction of the block, wherein a plurality of such longitudinal channel rows are adjacent to each other in the height direction of the block.

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

[0042] It is understood that the features described above and still to be explained below can be used not only in the respectively specified combination but also in other combinations or alone without departing from the scope of the invention as defined by the claims. Individually named components of a superordinate unit (e.g., a device, an apparatus or an arrangement) described above and still to be mentioned below can form individual components or parts of this unit or be integrated regions or sections of this unit, even if not shown as such in the drawings. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0044] They are shown in schematic diagrams:

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

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

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

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

[0049] Figure 5A and Figure 5B shows a highly simplified cross section of different flow channels at the inlet opening or outlet opening,

[0050] FIG6 shows a cross section similar to FIG5 , but in another embodiment,

[0051] Figure 7A 、 Figure 7B 、 Figure 7C Different views of the second flow channel are shown in the transition region in different viewing directions,

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

[0053] Figure 9 An isometric view showing a longitudinal section of the second flow channel or the first flow channel with fins,

[0054] Figure 10 shows a highly simplified cross-sectional view in the region of the recess,

[0055] Figure 11 A highly simplified cross-sectional view showing a heat exchanger in a cross-flow embodiment,

[0056] Figure 12 A highly simplified cross-sectional view showing a heat exchanger in a parallel flow embodiment,

[0057] Figure 13 A highly 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 one another. Figure 1 , the block longitudinal direction X extends perpendicular to the drawing plane, the block transverse direction Y extends vertically, and the block height direction Z extends horizontally.

[0059] A first chamber 4 is formed at the first transverse end 3 of the heat exchanger block 2, extending lengthwise in the block height direction Z and having a first connection 5. In the example shown, the first chamber 4 forms a distribution chamber 4, and the first connection 5 forms a supply connection 5. Furthermore, a second chamber 7 is formed at the second transverse end 6 of the heat exchanger block 2 (which faces away from the first transverse end 3 in the block transverse direction Y), extending lengthwise in the block height direction Z and having a second connection 8. In the example shown, the second chamber 7 forms a collecting chamber 7, and the second connection 8 forms a discharge connection 8.

[0060] according to Figures 1 to 3 A plurality of first flow channels 9 for guiding the first fluid are constructed in the heat exchanger block 2. These first flow channels pass through the heat exchanger block 2 in the block longitudinal direction X and connect the upstream side 10 of the heat exchanger block 2 (which is located at the end of the heat exchanger block 2) that receives the first fluid. Figures 1 to 3The heat exchanger block 2 is provided with a first longitudinal end 11 facing the observer) and an outflow side 12 receiving the first fluid (which is located at the end of the heat exchanger block 2 Figures 1 to 3 The first fluid that occurs during operation of the heat exchanger 1 flows through the heat exchanger block 2 or the first flow channel 9. Figure 2 and Figure 3 The arrow in FIG. 1 is schematically indicated and marked as 14 .

[0061] according to Figure 2 and Figure 3 In the heat exchanger block 2, a plurality of second flow channels 15 for guiding a second fluid are further formed, which are fluidically separated from the first flow channels 9. The second flow channels 15 pass through the heat exchanger block 2 in the block transverse direction Y and fluidically connect the distribution chamber 4 to the manifold 7. The flow of the second fluid occurring during operation of the heat exchanger 1 in the heat exchanger block 2 or the distribution chamber 4, the connecting pipe 15 and the manifold 7 is carried out by Figures 1 to 3 The arrow in FIG. 1 is schematically indicated and marked as 16 .

[0062] according to Figure 2 and Figure 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 a channel longitudinal row 17. In the example shown, each channel longitudinal row 17 contains ten second flow channels 15. In the heat exchanger block 2, a plurality of channel longitudinal rows 17 are arranged side by side in the block height direction Z. For example, Figure 2 and Figure 3 Nine such longitudinal channel rows 17 can be seen in FIG. Obviously, significantly more longitudinal channel rows 17 can also be arranged side by side in the block height direction Z in the heat exchanger block 2 , for example more than fifty.

[0063] Heat exchanger block 2 has Figure 2 and Figure 3 The block longitudinal midplane 18 is indicated by a dashed line and extends transversely to the block longitudinal direction X. Figure 4The second flow channels 15 each have a first opening 19 at the distribution chamber 4, which here forms the inlet opening 19 and has a circular inlet cross-section 43 through which flow can pass. 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 configured with respect 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. More specifically, second flow channels 15 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 at a smaller distance from the block longitudinal center plane 18. Purely by way of example, FIG. 5 shows this transition from a larger longitudinal diameter 20 to a smaller longitudinal diameter 20. Figure 5A The inlet cross section 43 of the inlet opening 19 of the second flow channel 15 is shown, which is at a greater distance from the block longitudinal midplane 18. In contrast, Figure 5B The inlet cross section 43 of the inlet opening 19 of the second flow channel 15 at a smaller distance from the block longitudinal midplane 18 is shown. It can be seen that the longitudinal diameter 20 increases with increasing distance from the block longitudinal midplane 18. The corresponding transition is schematically indicated in FIG5 by an arrow and is referenced as 22. In the example shown, it can also be provided that the height diameter 21 of the inlet cross section 43 of the inlet opening 19 is the same, i.e., remains constant, in all second flow channels 15 of the corresponding longitudinal channel row 17.

[0064] Alternatively, the same applies to the region of the manifold 7. For simplicity, reference is also made to Figure 4 and Figure 5 illustrate this relationship. Figure 4 If the chamber shown is a collecting chamber 7, the 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 a longitudinal diameter 20 and a height diameter 21. The second flow channels 15 are configured with respect to their outlet cross section 44 such that in the respective channel longitudinal 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 midplane 18, so that the second flow channels 15 at a greater distance from the block longitudinal midplane 18 have an outlet cross section 44 with a larger longitudinal diameter 20 than the second flow channels 15 at a smaller distance from the block longitudinal midplane 18. Figure 5A and Figure 5B Here, it can also be provided that the height diameter 21 of the outlet cross section 44 is identical in all second flow channels 15 of the corresponding longitudinal channel row 17 .

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

[0066] In another embodiment, explained in detail in conjunction with FIG. 6 , the second flow channels 15 can be configured with respect to their flow resistance such that, in the respective longitudinal 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 midplane 18 . Specifically, second flow channels 15 that are at a greater distance from the block longitudinal midplane 18 have a greater flow resistance than second flow channels 15 that are at a smaller distance from the block longitudinal midplane 18 . It is conceivable that the flow resistance of the second flow channels 15 is increased by obstacles formed in the second flow channels 15 for this purpose. In this case, this embodiment can also be combined with the above-described embodiment in which the longitudinal diameters 20 of adjacent second flow channels 15 in the block longitudinal direction X vary.

[0067] Combine Figure 6A and Figure 6B Another embodiment is further explained in detail, in which the flow resistance of the respective second flow channel 15 is changed by means of the flowable cross-sectional area 24 of the respective second flow channel 15. Figure 6A and Figure 6B In the example of FIG, the second flow channels 15 each have a circular through-flow cross-section 45. It can be expediently provided that, in the respective longitudinal channel row 17, the size of the through-flow cross-section 24 of the respective second flow channel 15 is correlated with the distance of the respective second flow channel 15 from the block longitudinal mid-plane 18, and more precisely, that the second flow channels 15 at a greater distance from the block longitudinal mid-plane 18 have a smaller through-flow cross-section 24 than the second flow channels 15 at a smaller distance from the block longitudinal mid-plane 18. Figure 6A The throughflow cross-sectional area 24 of the second flow channel 15 is shown at a greater distance from the block longitudinal midplane 18, while Figure 6B The through-flow cross-sectional area 24 of the second flow channel 15 at a smaller distance from the block longitudinal midplane 18 is shown. It can be seen that the through-flow cross-sectional area 24 decreases significantly with increasing distance from the block longitudinal midplane 18. The corresponding transition is schematically indicated in FIG6 by arrows and is labeled 25.

[0068] according to Figure 1The 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. The heat exchanger block 2 also has a first transition region 27 which connects the central transverse region 26 to the distribution chamber 4. The heat exchanger block 2 also has a second transition region 28 which connects the central transverse region 26 to the collecting chamber 27.

[0069] The aforementioned relationship, that the flowable cross-sectional area 24 of the respective second flow channel 15 decreases as the distance of the respective second flow channel 15 from the block longitudinal midplane 18 increases, applies at least to the middle transverse region 26 of the heat exchanger block 2. This relationship also applies in the first transition region 27 and / or the second transition region 28.

[0070] In principle, the second flow channels 15 can be configured such that their flowable cross-sectional area 24 decreases from the inlet opening 19, which opens into the distribution chamber 4, to the intermediate transverse region 26 and / or increases from the intermediate transverse region 26 to the outlet opening 23, which opens into the collecting chamber 7. It can preferably be provided that in the second flow channel 15, the flowable cross-sectional area 24 decreases from the inlet opening 19 in a first transition region 27 to the intermediate transverse region 26, remains constant in the intermediate transverse region 26, and increases from the intermediate transverse region 26 to the outlet opening 23 (i.e., in the second transition region 28). The reduction in cross section in the intermediate transverse region 26 can also, in particular, vary the flow resistance of the second flow channel 15.

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

[0072] according to Figure 2 and Figure 3 The second flow channel 15 can optionally also be configured such that the second flow channel 15 is spaced apart from the block longitudinal middle plane 18 or faces away from the block longitudinal middle plane 18 and extends obliquely relative to the block transverse direction Y in the first transition region 27 and / or the second transition region 28. Figure 2 and Figure 3In the diagram, for each second flow channel 15 facing away from the block longitudinal center plane 18 (i.e., the second flow channel 15 at the greatest distance from the block longitudinal center plane 18 in the corresponding longitudinal channel row 17), a longitudinal center axis 29 is drawn, by way of example and representative of all other second flow channels 15. The corresponding second flow channel 15 has this longitudinal center axis in its inlet opening 19 or outlet opening 23. This longitudinal center axis 29 has an inclination angle 30, or inclination 30, relative to the block transverse direction Y. The embodiment shown here is particularly advantageous in which the inclination 30 increases from the middle transverse region 26 in the first transition region 27 to the distribution chamber 4, and increases from the middle transverse region 26 in the second transition region 28 to the collecting chamber 7. Consequently, the second flow channels 15 are distributed over a greater area in the block longitudinal direction X in the distribution chamber 4 and the collecting chamber 7 than in the middle transverse region 26 of the heat exchanger block 2.

[0073] Figure 7 and Figure 8 The second flow channel 15 or the wall material of the heat exchanger block 2 defining the second flow channel 15 is shown, specifically, selectively in a first transition region 27 to the distribution chamber 4 or in a second transition region 28 to the collecting chamber 7 . Figure 7A An isometric view of the second flow channel 15 is shown. Figure 7B A side view of the second flow channel 15 is shown in a viewing direction extending parallel to the block height direction Z. Figure 7C A side view of the second flow channel 15 is shown in a viewing direction extending parallel to the block longitudinal direction X. Figure 8 An isometric view of a plurality of second flow channels 15 arranged side by side in the block height direction Z is shown. Figure 8 The second flow channels 15 are shown in each case at a greater distance from the block longitudinal midplane 18. In particular, these can be the second flow channels 15 which are each furthest away from the block longitudinal midplane 18.

[0074] The second flow channels 15 can be configured such that those second flow channels 15 that are spaced apart from or facing away from the block longitudinal midplane 18 have a geometrically varying opening cross section 45 in the first transition region 27 and / or 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 FIG. 7 and FIG. Figure 8 In the example of FIG. 1 , the second flow channel 15 has in its inlet opening 19 an elliptical opening cross section 45 which is long in the block longitudinal direction X, i.e. Figure 5AAs shown, it has a larger longitudinal diameter 20 in the block longitudinal direction X. The oval opening cross section 45 then transitions to a circular opening cross section 45 in the first transition region 27 to the middle transverse region 26 along the block transverse direction Y. The circular opening cross section 45 is shown in FIG. Figure 8 The circular cross section 45 is located at the lower end of the section shown in the second flow channel 15. Figure 5B 、 Figure 6A and Figure 6B The figure is shown purely by way of example. Optionally, the same situation may also apply in the second transition region 28. Thus, the second flow channel 15 has an oval opening cross section 45 at its outlet opening 23 into the collecting chamber 7, which is long in the block longitudinal direction X and transitions to a circular opening cross section 45 in the second transition region 28 in the middle transverse region 26 along the block transverse direction Y.

[0075] according to Figure 2 and Figure 4 The distribution chamber 4 has a profile on the distribution side 31 facing the second flow channel 15 that extends transversely to the block height direction Z and is concavely curved toward the interior of the distribution chamber 4. The inlet opening 19 is located in the distribution side 31. Figure 3 and Figure 4 On the collecting side 32 facing the second flow channel 15, the collecting chamber 7 has a profile that 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. This configuration achieves a flow-favorable transition from the distribution chamber 4 to the second flow channel 15 and from the second flow channel 15 to the collecting chamber 7, which is characterized by reduced flow resistance.

[0076] from Figures 1 to 3 In particular, it can be seen that in the heat exchanger block 2, a plurality of first flow channels 9 are arranged side by side in the block transverse direction Y, thereby forming a channel transverse row 33. For example, each channel transverse row 33 can have more than twenty or more than fifty first flow channels 9. In the heat exchanger block 2, a plurality of channel transverse rows 33 are arranged side by side in the block height direction Z. Figure 1 The heat exchanger block 1 has an intermediate height region 34, which is spaced apart from the block lateral ends 35, 36 facing away from one another in the block height direction Z. At least in this intermediate height region 34, the transverse channel rows 33 each extend through the heat exchanger block 2 between two adjacent longitudinal channel rows 17. This results in a particularly compact arrangement of the first flow channels 9 and the second flow channels 15 intersecting each other, which facilitates a strong heat transfer.

[0077] In a plurality of or all second flow channels 15 and / or a plurality of or all first flow channels 9, fins or projections may extend into the flowable cross section 45, so that the first fluid or the second fluid may flow through these fins or projections and / or around these fins or projections. Without limiting the generality, Figure 9 The example of two spirally configured fins 37 is shown, which extend helically 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). Obviously, more than two such fins 37 can also be present in the respective channels 9, 15.

[0078] exist Figure 10 In the figure, recesses 38 can be seen, which are formed in the inner side 39 that is subjected to the second fluid. In this case, the inner side 39 can belong to the collecting chamber 7 or the distribution chamber 4 or to one of the second flow channels 15, preferably in the first transition region 27 or the second transition region 28. The recesses 38 increase the surface area of ​​the respective inner side 39. For example, the recess 38 can have a constriction 40 at the transition to the inner side 39. Therefore, the cross section 41 of the respective recess 38 is larger in the respective recess 38 than in the constriction 40. The cross section 41 is measured here transversely to the normal direction 42 of the inner side 39, which is perpendicular to the inner side 39. In the figure, the recesses 38 are formed in a manner similar to the embodiment of the embodiment of the invention. Figure 10 In FIG. 4 , the cross section 41 measured in the respective recess 38 is also designated as 411 . The significantly smaller cross section 41 in the constriction 40 is also designated as 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 the upstream side 10 of the heat exchanger block 2 that is subjected to the first fluid with the downstream side 12 of the heat exchanger block 2 that is subjected to the first fluid.

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

[0081] Figure 11Another embodiment is now shown by way of example and in a highly simplified manner, in which the first chamber 4 has or forms a distribution chamber 46 and a collecting chamber 47. This can be achieved, for example, by a partition wall 48 that separates the first chamber 4 so that the distribution chamber 46 and the collecting chamber 47 are constructed therein. The first interface 5 is then constructed on the distribution chamber 46 and forms the supply interface 5, while the second interface 8 is constructed on the collecting chamber 47 and forms the discharge interface 8. In this case, the second chamber 7 forms the deflection chamber 49. For example, a web 50 can be constructed in the second chamber 7 for this purpose, which web causes or assists in the flow deflection of the second fluid in the deflection chamber 49. A first group 51 consisting of a plurality of second flow channels 15 connects the distribution chamber 46 to the deflection chamber 49. A second group 52 consisting of a plurality of second flow channels 15 connects the deflection chamber 49 to the collecting chamber 47.

[0082] And in an exemplary and highly simplified manner Figure 12 In another alternative embodiment shown in FIG, 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 particular, it can be provided that in the heat exchanger block 2, the first flow channels 9 and the second flow channels 15 are arranged alternately in the block height direction Z and / or in the block longitudinal direction X. Figure 12 It is shown how in the middle transverse region 26 the first flow channels 9 and the second flow channels 15 are arranged alternately in the block longitudinal direction X and cross in a media-dividing manner in the transition regions 27 , 28 .

[0083] In addition, according to Figure 12 In the case of a parallel flow heat exchanger 1, the first chamber 4 may include or constitute a first subchamber 53 and a second subchamber 54, wherein 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. Furthermore, the second chamber 7 may include or constitute a third subchamber 55 and a fourth subchamber 56, wherein 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. For example, the first chamber 4 and the second chamber 7 may be separated by a partition wall 48 for this purpose.

[0084] In addition, optionally, Figure 12It is provided that the first subchamber 53 forms a collecting chamber 53 for the first flow channel 9, the second subchamber 54 forms a distribution chamber 54 for the second flow channel 15, the third subchamber 55 forms a distribution chamber 55 for the first flow channel 9, and the fourth subchamber 56 forms a collecting chamber 7 for the second flow channel 15. The first interface 5 serves as a supply interface 5 for the second fluid and is configured on the second subchamber. The second interface 8 serves as a discharge interface 8 for the second fluid and is configured on the fourth subchamber 56. The third interface 57 serves as a supply interface 57 for the first fluid and is configured on the third subchamber 55. The fourth interface 58 serves as a discharge interface 58 for the first fluid and is configured on the first subchamber 53.

[0085] If the heat exchanger 1 is configured as a parallel flow heat exchanger 1, all of the above combinations Figures 1 to 10 The configuration and features described with respect to the second flow channels 15 can also be implemented correspondingly in the first flow channels 9. This applies in particular to the geometric configuration of the openings that open into the respective chambers 4, 7 or subchambers 53, 54, 55, 56, and / or the variation of the throughflow cross-section within the flow channels 9, 15 in the block transverse direction Y, as well as the variation of the throughflow cross-section with respect to adjacent flow channels 9, 15 in the block longitudinal direction X. Thus, the first flow channels 9 in the heat exchanger block 2 can also form, in particular, a channel longitudinal row having a plurality of first flow channels 9 adjacent in the block longitudinal direction X, wherein a plurality of such channel longitudinal rows are adjacent in the block height direction Z.

[0086] In principle, according to Figures 1 to 12 , an embodiment is preferred in which the second flow channels 15 of the respective longitudinal channel row 17 extend individually from the first chamber 4 to the second chamber 7 and each have a separate inlet opening 19 and / or a separate outlet opening 23 there. Figure 13 In another embodiment shown in , it can be provided that the second flow channels 15 of the corresponding longitudinal channel rows 17 extend separately from one another at least in the middle transverse region 26 of the heat exchanger block 2 and 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. Additively manufactured heat exchanger (1) for medium-separated heat transfer between a first fluid and a second fluid, in particular for cooling gases, The heat exchanger 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 one another, in, A plurality of first flow channels (9) for conducting a first fluid are formed in the heat exchanger block (2), the first flow channels passing through the heat exchanger block (2). 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). 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), and extends in the block height direction (Z). 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 passing through 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). The heat exchanger (1) has a first connection (5) for supplying or discharging a 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 side by side in the longitudinal direction (X) of the block and form a channel longitudinal row (17), Therein, in the heat exchanger block (2), a plurality of longitudinal rows (17) of channels 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 first chamber (4) constitutes or comprises a distribution chamber (4) which supplies the second fluid to the second flow channel (15), The first connection (5) is configured on the distribution chamber (4) and constitutes a supply connection (5) for supplying the second fluid to the distribution chamber (4). The heat exchanger block (2) has a block longitudinal midplane (18) extending transversely to the block longitudinal direction (X), The second flow channels (15) each have an inlet opening (19) at the distribution chamber (4) with a throughflowable, round inlet cross section (43). The inlet cross section (43) has a longitudinal diameter (20) measured in the longitudinal direction (X) of the block and a height diameter (21) measured in the height direction (Z) of the block, The second flow channels (15) are configured with respect to their inlet cross-sections (43) such that, in the respective channel longitudinal row (17), the size of the longitudinal diameter (20) of the inlet cross-section (43) of the respective second flow channel (15) is correlated with the distance of the respective second flow channel (15) from the block longitudinal mid-plane (18): second flow channels (15) at a greater distance from the block longitudinal mid-plane (18) have an inlet cross-section (43) with a larger longitudinal diameter (20) than second flow channels (15) at a smaller distance from the block longitudinal mid-plane (18).

3. The heat exchanger (1) according to claim 2, It is characterized in that In all second flow channels (15) of the corresponding longitudinal channel row (17), the height diameter (21) of the inlet cross section (43) of the corresponding second flow channel (15) is of the same size.

4. The heat exchanger (1) according to any one of claims 1 to 3, It is characterized in that The second chamber (7) constitutes or comprises a manifold (7) which receives the second fluid from the second flow channel (15), The second connection (8) is constructed on the collecting chamber (7) and forms an outlet connection (8) for discharging the second fluid from the collecting chamber (7). The heat exchanger block (2) has a block longitudinal midplane (18) extending transversely to the block longitudinal direction (X), The second flow channels (15) each have an outlet opening (23) on the collecting chamber (4), which has a throughflowable, round outlet cross section (44). The outlet cross section (44) has a longitudinal diameter (20) measured in the longitudinal direction (X) of the block and a height diameter (21) measured in the height direction (Z) of the block, The second flow channels (15) are configured with respect to their outlet cross-sections (44) such that, in the respective channel longitudinal row (17), the size of the longitudinal diameter (20) of the outlet cross-section (44) of the respective second flow channel (15) is correlated with the distance of the respective second flow channel (15) from the block longitudinal mid-plane (18): second flow channels (15) at a greater distance from the block longitudinal mid-plane (18) have an outlet cross-section (44) with a larger longitudinal diameter (20) than second flow channels (15) at a smaller distance from the block longitudinal mid-plane (18).

5. The heat exchanger (1) according to claim 4, It is characterized in that In all second flow channels (15) of the corresponding longitudinal channel row (17), the height diameter (21) of the outlet cross section (44) of the corresponding second flow channel (15) is of the same size.

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 the second transverse end (6). The second flow channel (15) has a flowable cross-sectional area (24), which decreases from a first opening (19) opening into the first chamber (4) to a middle transverse region (26) and / or increases from the middle transverse region (26) to a second opening (23) opening into the second 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 the second transverse end (6). The heat exchanger block (2) has a first transition region (27) at the first transverse end (3) connecting the first chamber (4) with the intermediate transverse region (26), and a second transition region (28) at the second transverse end (6) connecting the second chamber (7) with the intermediate transverse region (26), The heat exchanger block (2) has a block longitudinal midplane (18) extending transversely to the block longitudinal direction (X), The second flow channel (15) extends parallel to the block transverse direction (Y) in the middle transverse region (26), A second flow channel (15) spaced apart from or facing away from the block longitudinal center plane (18) extends in a first transition region (27) and / or a second transition region (28) at an angle relative to the block transverse direction (Y), wherein the inclination (30) increases from the center transverse region (26) to the distribution chamber (4) and / or to the collecting chamber (7).

8. The heat exchanger (1) according to any one of claims 1 to 7, 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 the second transverse end (6). The heat exchanger block (2) has a first transition region (27) at the first transverse end (3) connecting the first chamber (4) with the intermediate transverse region (26), and a second transition region (28) at the second transverse end (6) connecting the second chamber (7) with the intermediate transverse region (26), The heat exchanger block (2) has a block longitudinal midplane (18) extending transversely to the block longitudinal direction (X), A second flow channel (15) spaced apart from or facing away from at least the block longitudinal center plane (18) has a varying opening cross section (45) in the first transition region (17) and / or the second transition region (28) along the block transverse direction (Y).

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

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

11. The heat exchanger (1) according to any one of claims 1 to 10, It is characterized in that The first chamber (4) constitutes or comprises a distribution chamber (4) which supplies the second fluid to the second flow channel (15), The first connection (5) is configured on the distribution chamber (4) and constitutes a supply connection (5) for supplying the second fluid to the distribution chamber (4). The distribution chamber (4) has, on a distribution side (31) facing the second flow channel (15), a contour extending transversely to the block height direction (Z) and curving concavely toward the interior of the distribution chamber (4).

12. The heat exchanger according to any one of claims 1 to 11, It is characterized in that The second chamber (7) constitutes or comprises a manifold (7) which receives the second fluid from the second flow channel (15), The second connection (8) is constructed on the collecting chamber (7) and forms an outlet connection (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 extending transversely to the block height direction (Z) and curving concavely toward the interior of the collecting chamber (7).

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 second flow channels (15), the fins (37) or the projections extend into the throughflow cross section (45), so that the second fluid can flow through and / or around the fins (37) or the projections.

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

15. The heat exchanger (1) according to claim 13 or 14, It is characterized in that The fins (37) are configured in a spiral shape so that the fins extend in a spiral shape along the corresponding second flow channel (15) or along the corresponding first flow channel (9).

16. 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) receiving the second fluid, so as to increase the surface area of ​​the inner side (39).

17. 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 a recess (38) on their inner side (39) receiving the second fluid, at least in a transition region (27, 28) of the heat exchanger block (2) to the first or second chamber (4, 7), in order to increase the surface area of ​​the inner side (39).

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

19. The heat exchanger (1) according to any one of claims 1, 6 to 10 and 13 to 18, It is characterized in that The first chamber (4) has or forms a distribution chamber (46) and a collecting chamber (47), The first connection (5) is formed on the distribution chamber (46) and forms the supply connection (5), The second connection (8) is formed on the collecting chamber (47) and forms the discharge connection (8). The second chamber (7) constitutes the deflection chamber (49).

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

21. The heat exchanger (1) according to claim 20, 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 block transverse direction (Y) and form a channel transverse row (33), In the heat exchanger block (2), a plurality of channel transverse 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 the block lateral ends (35, 36) facing away from each other in the block height direction (Z). The transverse rows (33) of channels each pass through the heat exchanger block (2) between two adjacent longitudinal rows (17) of channels, at least in a mid-height region (34) of the heat exchanger block (2).

22. 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 parallel flow heat exchanger (1). A 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).

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

24. The heat exchanger according to claim 23, 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 distribution chamber for the second flow channel (15), The third subchamber (55) constitutes a distribution 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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