Crossflow heat exchanger, turbine engine and method for producing the exchanger

Abstract

The invention relates to a crossflow heat exchanger (100) for an aeronautical turbine engine, which is configured to exchange heat between a first fluid and a second fluid and comprises: two or more sub-circuits (10) which form a first circuit which is configured to receive the first fluid (1), the sub-circuits (10) each extending mainly between an inlet (10A) and an outlet (10E) in a first direction (X), the sub-circuits (10) being fluidically independent; the inlets (10A) and outlets (10E) of the sub-circuits (10) being positioned on a first face (F1) of the exchanger; the sub-circuits (10) being delimited by walls (12, 14) which are configured to perform a heat exchange between the first fluid (1) inside the sub-circuits (10) and the second fluid (2) outside the sub-circuits (10).

Description

Description Title of the invention: Cross-flow heat exchanger, turbomachine and method of manufacturing the exchanger Technical Field

[0001] This disclosure relates to cross-flow heat exchangers, in particular a multi-pass cross-flow heat exchanger. Prior art

[0002] Climate change is a major concern for many legislative and regulatory bodies around the world. Indeed, various carbon emission restrictions have been, are being, or will be adopted by various states. In particular, an ambitious standard applies to both new aircraft types and those already in operation, requiring the implementation of technological solutions to bring them into compliance with current regulations. For several years now, civil aviation has been mobilizing to contribute to the fight against climate change.

[0003] Technological research efforts have already led to very significant improvements in the environmental performance of aircraft. The Applicant takes into consideration the impact factors in all phases of design and development to obtain less energy-intensive, more environmentally friendly aeronautical components and products whose integration and use in civil aviation have moderate environmental consequences with the aim of improving the energy efficiency of aircraft.

[0004] Consequently, the Applicant is constantly working to reduce its negative climate impact through the use of methods and the exploitation of virtuous development and manufacturing processes and minimizing greenhouse gas emissions to the minimum possible to reduce the environmental footprint of its activity.

[0005] This ongoing research and development work focuses on new generations of aircraft engines, the weight reduction of aircraft, particularly through the materials used and lighter on-board equipment.

[0006] To this end, the invention is the result of technological research aimed at significantly improving aircraft performance and, in this sense, contributes to reducing the environmental impact of aircraft. For this purpose, the invention relates to a multi-pass cross-flow heat exchanger, in which the fluid circulation circuits comprise sinuosities making it possible to increase the passage time of the fluid within the exchanger, and thus to increase the thermal efficiency of the exchanger.

[0007] The increase in the thermal efficiency of the exchanger by these sinuosities can however be at the expense of increased pressure losses.

[0008] There is then a need for a heat exchanger offering a better compromise between thermal efficiency and pressure losses. Statement of the invention

[0009] This presentation aims to remedy at least part of these drawbacks.

[0010] To this end, the present disclosure relates to a cross-flow heat exchanger for an aeronautical turbomachine, configured to exchange heat between a first fluid and a second fluid, comprising: two or more sub-circuits forming a first circuit configured to receive the first fluid, said sub-circuits each extending mainly between a respective inlet and outlet in a first direction, said sub-circuits being fluidically independent; the inlets and outlets of said sub-circuits being positioned on a first face of the exchanger; said sub-circuits being delimited by walls configured to carry out a heat exchange between the first fluid inside said sub-circuits and the second fluid outside said sub-circuits.

[0011] Hereinafter, and unless otherwise indicated, "one" or "I" element (e.g. branch, sub-circuit, etc.) means "at least one" or "the at least one" or "each" element. Conversely, the generic use of the plural may include the singular. Hereinafter, and unless otherwise indicated, "a plurality" means "at least two".

[0012] By "direction" we mean an unoriented axis, and by "orientation" we mean an orientation along an oriented axis.

[0013] Typically, the first direction is the general direction of flow of the first fluid in the sub-circuit of the first circuit.

[0014] The terms "inlet" and "outlet" are used in relation to the direction of fluid flow; a conduit or manifold is understood to "extend" in one direction when it allows gas to flow in that direction, regardless of the cross-sectional shape and dimensions in other directions.

[0015] By fluidically independent, we mean that the sub-circuits do not communicate fluidically with each other, that is to say that in a normal operating mode a fluid entering through the inlet of a sub-circuit can only exit through the outlet of said sub-circuit.

[0016] Such an exchanger lacks a common collection area or a first fluid collector box inside the exchanger, typically designed to collect the fluid flowing in a given direction and direction in order to redirect it, resulting in significant edge effects and pressure losses.

[0017] Such an exchanger thus has a reduced volume, a reduction in the risks of poor fluid distribution and a reduction in pressure losses.

[0018] Such an exchanger thus presents, for given dimensions and operating conditions, improved thermal performance.

[0019] Furthermore, this structure is particularly suitable for additive manufacturing, for example by selective powder bed fusion.

[0020] Typically, the walls extend in a plane comprising the first direction and a second direction perpendicular to the first direction so as to obstruct movement of the second fluid in a third direction perpendicular to the first direction and the second direction.

[0021] Typically, the second direction is the general direction of flow of the second fluid within the exchanger.

[0022] Typically, the walls allow the second fluid to be directed in the second direction.

[0023] Typically, the walls comprise first fins on the side of the first circuit, preferably extending in the first direction.

[0024] The first fins help direct the first fluid in the first direction. The first fins help improve the efficiency of heat exchange between the first fluid and the exchange walls, and thus between the first fluid and the second fluid, while reducing pressure losses.

[0025] Typically, the exchanger comprises channels of a second circuit configured to receive the second fluid, said sub-circuits being separated by all or part of the channels.

[0026] Typically, said sub-circuits are successively arranged in the second direction.

[0027] Typically, the walls comprise second fins (secondary exchange surfaces) on the side of the second circuit, preferably extending in the second flow direction.

[0028] The second fins help direct the second fluid in the second flow direction. The second fins help improve the efficiency of heat exchange between the second fluid and the exchange walls, and thus between the first fluid and the second fluid, while reducing pressure losses.

[0029] More generally, the use of fins increases the exchange surface area and thus improves the performance of the exchanger. The fins also allow for better control of fluid flows near the walls, and thus further improve fluid distribution. The fins also improve the thermomechanical resistance of the exchanger in the case of high-pressure fluid flows.

[0030] Typically, viewed in cross-section, each sub-circuit comprises a generally U-shaped conduit extending between the inlet and outlet of the sub-circuit.

[0031] Typically, the generally U-shaped conduit includes an inlet branch extending from the inlet and an outlet branch opening into the outlet.

[0032] Typically, channels of the second circuit are formed between the input and the output of the same sub-circuit, typically between the input branch and the output branch of the same sub-circuit.

[0033] Typically, second circuit channels are formed between the input and output of adjacent subcircuits, typically between the input branch and the output branch of two adjacent subcircuits.

[0034] The U-shape has an elbow to reduce pressure losses, particularly compared to exchangers with a common collector for the inlet and outlet branches.

[0035] Typically, the inputs and outputs of adjacent subcircuits are arranged alternately. Typically, the input branches and output branches of adjacent subcircuits are arranged alternately.

[0036] This alternative arrangement allows the second fluid to always be in contact with a part of the sub-circuit towards the inlet, that is to say to always be in contact with the first fluid in its coldest state if the first fluid is a refrigerant fluid, or in its hottest state if the first fluid is a fluid to be heated.

[0037] Typically, the inputs of consecutive sub-circuits are arranged consecutively and the outputs of consecutive sub-circuits are arranged consecutively. Typically, the input branches of consecutive sub-circuits are arranged consecutively and the output branches of consecutive sub-circuits are arranged consecutively.

[0038] This consecutive arrangement facilitates the distribution of the first fluid to the inlets and the collection of the first fluid from the first fluid outlets.

[0039] Typically, the sub-circuits extend in the first direction of the exchanger over a distance greater than 90% of the length of the exchanger in the first direction, typically greater than 95%.

[0040] Typically, sub-circuits have mechanical reinforcements opposite the first face.

[0041] Typically, mechanical reinforcements include support arches.

[0042] The arches provide mechanical reinforcement without significantly disrupting the circulation of the first fluid.

[0043] Typically, the exchanger includes a manifold configured to divide an incoming flow and an outgoing flow to and from the sub-circuits.

[0044] Typically, the exchanger includes a manifold configured to divide an incoming flow and an outgoing flow from and to adjacent sub-circuits.

[0045] Typically, the collector comprises walls having an angle less than 45° with the first direction.

[0046] Such an angle makes it possible to limit the deflection of the second gas flow entering and leaving the walls, and to reduce pressure losses compared to known solutions with angles close to 90°.

[0047] The invention also relates to an aeronautical turbomachine comprising a heat exchanger according to the invention.

[0048] Typically, the first circuit is connected to at least one of a turbomachine compressor and a combustion chamber, for example an area located between a compressor outlet and a combustion chamber inlet, and the second circuit is connected to a turbine, typically downstream, and an exhaust nozzle.

[0049] Typically, the first circuit is connected to a lubrication circuit and the second circuit is connected to a secondary air stream or a third stream, and an exhaust nozzle.

[0050] The invention also relates to a method for manufacturing a heat exchanger for an aeronautical turbomachine according to the invention comprising at least one step of additive manufacturing on a powder bed. Brief description of the drawings

[0051] Other characteristics and advantages of the subject of the present disclosure will emerge from the following description of embodiments, given as non-limiting examples, with reference to the appended figures.

[0052] [Fig. 1] Figure 1 is a cutaway perspective view of a cross-flow heat exchanger.

[0053] [Fig. 2A] Figure 2A is a schematic view along section plane 11-11 of Figure 1.

[0054] [Fig. 2B] Figure 2B is a schematic view corresponding to the view of Figure 2A where the direction of circulation of the first fluid is modified.

[0055] [Fig. 3] Figure 3 is an enlargement of Part III of Figure 2A.

[0056] [Fig. 4] Figure 4 is an enlarged perspective view of Part IV of Figure 1.

[0057] [Fig. 5] Figure 5 is a perspective view of an example of inlet and outlet ducts.

[0058] [Fig. 6] Figure 6 is a schematic representation of the integration of the cross-flow exchanger in a turbomachine. Description of the embodiments

[0059] Figure 1 shows a cutaway view of a cross-flow heat exchanger 100, hereinafter referred to as “exchanger”.

[0060] In the cutaway view of Figure 1, certain sub-circuits 10 are not shown for the purpose of visualizing the internal structure of the exchanger 100. Furthermore, for the purpose of illustration, the collector 19 is not shown and will be described below in relation to Figure 5.

[0061] The exchanger 100 is provided for exchanging heat (heat exchange) between a first fluid 1 circulating substantially in a first flow direction X and a second fluid 2 circulating substantially in a second flow direction Y.

[0062] By flow direction is meant an overall direction of flow of the fluid considered, independently of any local disturbances likely to affect the flow direction.

[0063] The local direction of circulation of the first fluid 1 is represented schematically by an arrow without filling. The local direction of circulation of the second fluid 2 is represented schematically by an arrow with full filling. For reasons of readability of the figures, certain numerical references including the numerical references of these arrows are not systematically represented.

[0064] As shown in Figure 6, the exchanger 100 can receive the first fluid 1 from an element 101, and redirect it to the element 101 after passing through the exchanger 100.

[0065] The exchanger 100 can receive the second fluid 2 from an element 102, and redirect it to an element 103.

[0066] The elements 101, 102, 103 and the exchanger 100 can be integrated into a turbomachine 200.

[0067] The first fluid 1 and the second fluid 2 may be two gases, for example the exchanger 100 receiving and redirecting the respective fluids from or to a turbomachine compressor 101, typically downstream, a combustion chamber 101, typically upstream, or a zone 101 formed between an outlet of a compressor and a combustion chamber inlet, a turbine 102, and an exhaust nozzle 103, for example in the case where the turbomachine 100 comprises a recuperated cycle gas turbine.

[0068] For example, the first fluid 1 and the second fluid 2 may respectively comprise a gas and a liquid, in particular oil, for example the exchanger 100 receiving and redirecting the respective fluids from or to a lubrication circuit 101, a secondary air stream 102 or a third stream 102, an exhaust nozzle 103.

[0069] The exchanger 100 comprises two or more sub-circuits 10 forming a first circuit receiving the first fluid 1.

[0070] Subcircuit 10 will be described in more detail with respect to Figures 1, 2A, 2B and 3.

[0071] The sub-circuit 10 extends on the one hand along the first direction X. The sub-circuit 10 extends on the other hand along the second direction Y. The sub-circuit 10 is substantially invariant by translation along the second direction Y, so that the structure of the sub-circuit 10 described below extends along the second direction Y.

[0072] Along the path of the first fluid 1, the sub-circuit 10 extends between an inlet 10A and an outlet 10E.

[0073] The inputs 10A and outputs 10E of the sub-circuits 10 are typically provided on the same face of the exchanger, for example designated by “first face” F1 illustrated in figure 1.

[0074] As shown in the view of Figures 2A and 3, between the inlet 10A and the outlet 10E, the circuit may comprise a conduit in the general shape of a U seen in a plane perpendicular to the second direction Y.

[0075] In particular, along the path of the first fluid 1, the sub-circuit 10 may comprise, in this order, between the inlet 10A and the outlet 10E: an inlet branch 10B, a half-turn 10C (“U-turn” or 180° flow diversion) and an outlet branch 10D.

[0076] Seen in a plane perpendicular to the second direction Y (figures 2A and 3), that is to say a plane comprising the first direction X and a third direction Z perpendicular to the first direction X and to the second direction Y, the half-turn 10C takes the form of a 180° elbow redirecting the fluid from the inlet branch 10B to the outlet branch 10D with a common direction and an opposite direction.

[0077] The input branch 10B and the output branch 10D are each delimited by an inner wall 12 and an outer wall 14.

[0078] Here we designate interior and exterior in relation to the whole formed by sub-circuit 10.

[0079] Typically, the inlet branch 10B and the outlet branch 10D surround a common channel 22 of a second circuit, configured to receive the second fluid 2.

[0080] The inner 12 and outer 14 walls thus contribute to the heat exchanges between the first fluid 1 and the second fluid 2. The inner 12 and outer 14 walls are thus typically exchange walls.

[0081] Within the meaning of the previous definition, channel 22 framed by an input branch 10B and an output branch 10D of the same sub-circuit 10 is thus considered to be internal to sub-circuit 10.

[0082] The input branch 10B and the output branch 10D are each delimited by an inner wall 12. The inner walls 12 which delimit the input branch 10B and the output branch 10D of the same sub-circuit 10 typically delimit the so-called inner channel 22.

[0083] A channel 22 can also be formed between two consecutive sub-circuits 10, that is to say two sub-circuits 10 consecutively arranged in a third direction Z, for example between adjacent outer walls 14 of branches 10B, 10D of two consecutive sub-circuits 10.

[0084] Such a channel 22 formed between two consecutive sub-circuits 10 is thus considered external.

[0085] The inner 12 and outer 14 walls typically extend in a plane formed by the first direction X and the second direction Y. Thus, the channels 22 typically extend between the first direction X and the second direction Y, thus allowing the circulation of the second fluid 2 in the second direction Y.

[0086] As shown in Figure 1, the direction of circulation of the first fluid 1 in the sub-circuits 10 can be the same for all the sub- circuits 10. In other words, the inputs 10A and the outputs 10E of the sub-circuits 10 can be arranged alternately, that is to say alternately according to the third direction Z. In other words, according to the third direction Z, the inputs 10A and the outputs 10E are arranged according to an “input - output - input - output” pattern.

[0087] For example, from left to right in Figure 1 along the third direction Z, there are arranged consecutively and in this order an output 10E, an input 10A of a first sub-circuit 10 then an output 10E and an input 10E of a second sub-circuit 10 adjacent to the first sub-circuit 10.

[0088] In such an alternative arrangement between inputs 10A and outputs 10E illustrated in FIG. 2A, a channel 22 is then formed between the outer walls 14 of respective input branches 10B of two alternative sub-circuits 10, or between the outer walls 14 of output branches 10D.

[0089] In the view of Figure 2B, the directions of circulation of the first fluid 1 have been altered compared to the view of Figure 2A, corresponding to an alternative embodiment.

[0090] As shown in Figure 2B, the direction of circulation of the first fluid 1 in the sub-circuits 10 can be reversed between two consecutive sub-circuits 10. In other words, the inlets 10A and the outlets 10E of the sub-circuits 10 can be arranged consecutively, that is to say that two inlets 10A are arranged consecutively and that two outlets 10E are arranged consecutively in the third direction Z. In other words, in the third direction Z, the inlets 10A and the outlets 10E are arranged according to an “inlet - outlet - outlet - inlet” pattern.

[0091] In such an alternative arrangement of the inputs 10A and outputs 10E, and thus of the input branches 10B and output 10D, a channel 22 is then formed between the outer walls 14 of an input branch 10B and an output branch 10D of two consecutive sub-circuits 10.

[0092] The sub-circuits 10 can also extend along the second direction Y. In other words, the inner walls 12 and the outer walls 14 can extend substantially in a plane comprising the first direction X and the second direction Y, so as to allow heat exchanges between the first fluid 1 and the second fluid 2.

[0093] The inner walls 12 and the outer walls 14 may comprise fins.

[0094] For example, as illustrated in detail in Figure 3, the inner walls 12 and the outer walls 14 may have first fins 13 and / or second fins 15.

[0095] The first fins 13 are typically provided on the side of the first circuit, so as to direct the first fluid 1 within the sub-circuit 10.

[0096] For example, the first fins 13 are provided to extend mainly in the first direction X, as well as in the third direction Z, so as to reduce a local movement of the first fluid 1 in the second direction Y, and thus to channel the first fluid 1 locally in the first direction X.

[0097] For example, the second fins 15 are provided to extend mainly in the second direction Y, as well as in the third direction Z, so as to reduce a local movement of the second fluid in the direction X, and thus to channel the second fluid 2 locally in the second direction Y.

[0098] The fins 13, 15 also contribute to the thermal exchanges between the fluids 1, 2 and the walls 12, 14 present.

[0099] The fins 13, 15 may or may not extend continuously from one wall 12, 14 to the other in the third direction Z, thus defining a honeycomb structure further reducing local fluid movements in the corresponding direction among the first direction X and the second direction Y, i.e. encouraging the circulation of fluids 1,2 according to their general flow direction among the first direction X and the second direction Y.

[0100] The fins 13, 15 may extend over all or part of the length of the walls 12, 14 in the direction of flow of the corresponding fluid among the first fluid 1 and the second fluid 2.

[0101] The fins 13, 15 may for example be arranged on the walls 12, 14 along the entire path of the respective fluid among the first fluid 1 and the second fluid 2. Typically, the fins 13, 15 may be continuous along the entire direction of circulation of the corresponding fluid among the first fluid 1 and the second fluid 2, or else be discontinuous. Where appropriate, the discontinuous fins 13, 15 may be provided in the extension of one another in the direction of circulation of the corresponding fluid among the first fluid 1 and the second fluid 2.

[0102] The sub-circuit 10 may comprise a mechanical reinforcement 18. The reinforcement 18 typically comprises one or more support arches 18.

[0103] Reinforcement 18 is for example provided in half-turn 10C.

[0104] An example of a support arch is shown in the enlargement of Figure 4.

[0105] The support arch 18, for example, has a ribbed vault shape.

[0106] The reinforcement 18 comprises for example a plurality of support arches 18 arranged in the second direction Y, typically regularly arranged in the second direction Y.

[0107] Such a structure makes it possible to provide a mechanical reinforcement function, in particular of the internal walls 12, and is in particular compatible with manufacturing by additive methods.

[0108] The reinforcement 18 is typically provided so as to extend in the first direction X between a second face F2 opposite the first face F1 and one end of the channel 22 at a height h, shown in Figure 1.

[0109] The height h is for example between 1.2 mm and 5 mm. The height h can for example be between 0.5xd4 and 2xd4, where d4 is a dimension (not shown) chosen from the height of a fin 13 measured along the third direction Z, the total height measured along the third direction Z of two fins 13 respectively provided on the walls 12 and 14 in the extension of one another, and the width of the inlet branch 10B or the outlet branch 10D measured along the third direction Z.

[0110] The reinforcement 18 can for example have a length d3 along the third direction Z (figure 3), and a depth p1 along the second direction Y (figure 4). [01 1 1 ] The length d3 and the length p1 can be between 1 mm and 20 mm, for example the length d3 and the depth p1 can be equal to each other.

[0112] Such a structure thus makes it possible to provide structural reinforcement of the channel 22 without significantly reducing the passage section of the first fluid 1.

[0113] Such a structure also makes it possible to provide mechanical support to the exchanger 100 during manufacturing operations using additive methods, in particular reducing the overhang of the supported sub-circuit 10.

[0114] The length (represented vertically in Figure 1) L of the exchanger in the first direction X is typically between 30 mm and 400 mm, for example between 100 mm and 300 mm. The length L is for example measured between the first face F1 and the second face F2 opposite the first face F1.

[0115] The depth P of the exchanger in the second direction Y is typically between 50 mm and 1 m, for example between 50 mm and 500 mm, or between 100 mm and 300 mm. For example, the depth P is between 10 mm and 400 mm, for example between 20 mm and 250 mm

[0116] The width d1 of a sub-circuit 10 along the third direction Z (fig. 2A and 2B) is typically between 10 mm and 400 mm, for example between 20 mm and 250 mm. The width d2 of the channel 22 along the third direction Z is typically between 10 mm and 250 mm.

[0117] For illustrative purposes, the exchanger 100 has been shown with two sub-circuits 10. It is understood, however, that the exchanger 100 may comprise more sub-circuits, 10, typically between five and fifty sub-circuits 10.

[0118] The width D along the third direction Z may be equal to the sum of the total widths of the sub-circuits 10 and the channels 22, where the number of channels 22 is one less than the number of sub-circuits 10.

[0119] For example, the width D of the exchanger in the third direction Z is typically between 50 mm and 1 m, for example between 50 mm and 500 mm, or between 100 mm and 300 mm. For example, the width D is between 10 mm and 400 mm, for example between 20 mm and 250 mm.

[0120] The exchanger 100 may comprise a collector 19 provided to divide an incoming flow and an outgoing flow of the first fluid 1 from and to the different sub-circuits 10.

[0121] A collector 19 is shown in Figure 5. The collector 19 is typically provided adjacent to the first face F1, that is to say fluidically in the extension of the sub-circuit 10, in particular in the extension of the inlet 10A and the outlet 10E of the sub-circuit 10, in other words in the extension of the inlet branch 10B and the outlet branch 10D of the sub-circuit 10.

[0122] The collector 19 comprises, for example, walls 19A, inclined in a plane formed by the first direction X and the second direction Y, configured to direct in the second direction Y an incoming flow and / or an outgoing flow of the sub-circuit 10.

[0123] The collector 19 comprises, for example, walls 19B, inclined in a plane formed by the first direction X and the third direction Z, configured to direct in the third direction Z an incoming flow and / or an outgoing flow of the sub-circuit 10.

[0124] The inclination of the walls 19A, 19B is the angle formed between the direction normal to the walls 19A, 19B and the first direction X.

[0125] The walls 19A, 19B may for example have an inclination of less than 45°, for example between 10° and 45°.

[0126] The exchanger 100 has a structure which is particularly suitable for production by an additive manufacturing process. A manufacturing process for the exchanger 100 can then be implemented, entirely or partially, by additive manufacturing, for example by a laser powder bed fusion process.

[0127] Although the present invention has been described with reference to specific exemplary embodiments, it is obvious that modifications and changes may be made to these examples without departing from the general scope of the invention as defined by the claims. In particular, individual features of the various illustrated / mentioned embodiments may be combined in additional embodiments. Therefore, the description and drawings should be considered in an illustrative rather than restrictive sense.

Claims

Claims

1. Cross-flow heat exchanger (100) for an aeronautical turbomachine, configured to exchange heat between a first fluid and a second fluid, comprising: two or more sub-circuits (10) forming a first circuit configured to receive the first fluid (1), said sub-circuits (10) each extending mainly between a respective inlet (10A) and outlet (10E) in a first direction (X), said sub-circuits (10) being fluidically independent; the inlets (10A) and outlets (10E) of said sub-circuits (10) being positioned on a first face (F1) of the exchanger; said sub-circuits (10) being delimited by walls (12, 14) configured to carry out a heat exchange between the first fluid (1) inside said sub-circuits (10) and the second fluid (2) outside said sub-circuits (10).

2. Cross-flow heat exchanger (100) for an aeronautical turbomachine according to claim 1, in which the walls (12, 14) extend in a plane comprising the first direction (X) and a second direction (Y) perpendicular to the first direction (X) so as to obstruct a movement of the second fluid in a third direction (Z) perpendicular to the first direction (X) and to the second direction (Y).

3. Cross-flow heat exchanger (100) for an aeronautical turbomachine according to claim 1 or 2, in which the walls (12, 14) comprise, on the side of the first circuit, first fins (13), preferably extending in the first direction (X).

4. Cross-flow heat exchanger (100) for an aeronautical turbomachine according to any one of claims 1 to 3, comprising channels (22) of a second circuit configured to receive the second fluid (2), said sub-circuits (10) being separated by all or part of the channels (22).

5. Cross-flow heat exchanger (100) for an aeronautical turbomachine according to claim 4, in which the walls (12, 14) comprise second fins (15) on the side of the second circuit.

6. Cross-flow heat exchanger (100) for an aeronautical turbomachine according to any one of claims 1 to 5, in which seen in a cross-section, each sub-circuit (10) comprises a generally U-shaped conduit extending between the inlet (10A) and the outlet (10E) of the sub-circuit (10).

7. Cross-flow heat exchanger (100) for an aeronautical turbomachine according to any one of claims 1 to 6, in which the inlets (10A) and the outlets (10E) of adjacent sub-circuits (10) are arranged alternately.

8. Cross-flow heat exchanger (100) for an aeronautical turbomachine according to any one of claims 1 to 7, in which the sub-circuits (10) extend in the first direction (X) over a distance greater than 90% of the length of the exchanger in the first direction (X).

9. Cross-flow heat exchanger (100) for an aeronautical turbomachine according to any one of claims 1 to 8, in which the sub-circuits (10) comprise mechanical reinforcements (18) opposite the first face (F1).

10. A cross-flow heat exchanger (100) for an aeronautical turbomachine according to any one of claims 1 to 9, comprising a manifold (19) configured to divide an incoming flow and an outgoing flow of the first fluid (1) from and to the sub-circuits (10).

11. An aeronautical turbomachine (200) comprising a cross-flow heat exchanger (100) for an aeronautical turbomachine according to any one of claims 1 to 10.

12. An aeronautical turbomachine (200) according to claim 11, wherein the first circuit is connected to at least one of a turbomachine compressor and a combustion chamber (101) and the second circuit is connected to a turbine (102) and an exhaust nozzle (103).

13. Method of manufacturing a cross-flow heat exchanger (100) for an aeronautical turbomachine according to any one of claims 1 to 10, comprising at least one step of additive manufacturing on a powder bed.

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