Surface heat exchanger for turbine engine nacelle and turbine engine nacelle equipped with such heat exchanger

Abstract

The invention relates to a surface heat exchanger (20), in particular for an aircraft nacelle, comprising a first metal plate (21) and a second metal plate (22) connected together, and at least three distribution channels (25) arranged between the first metal plate (21) and the second metal plate (22), the exchanger also includes an inlet hydraulic interface (28) and an outlet hydraulic interface (29). Each of the distribution channels (25) is directly connected to the inlet hydraulic connection (28) and the outlet hydraulic connection (29), and the distribution channels (25) are distributed over the entire circumference of the inlet hydraulic connection (28) and / or the outlet hydraulic connection (29).

Description

Technical Field

[0001] The invention relates to the field of heat exchangers and in particular to fairings of aircraft engines, which are known as "nacelles". Background Art

[0002] Generally speaking, an aircraft is propelled by one or more propulsion units, each of which comprises an engine or a jet turbine engine housed in a tubular nacelle.

[0003] The nacelle generally comprises a tubular body, the tubular body comprising an upstream section, a middle section and a downstream section, the upstream section comprising an air inlet located upstream of the jet turbine engine, the middle section being configured to surround the fan of the jet turbine engine, the downstream section being configured to house a thrust reversal device and surround the combustion chamber of the jet turbine engine. The nacelle generally comprises an exhaust nozzle located downstream of the downstream section, and the outlet of the exhaust nozzle is located downstream of the jet turbine engine.

[0004] Furthermore, the nacelle generally includes an outer structure and a fixed inner structure (referred to as an "inner fixed structure", abbreviated as "IFS (inner fixed structure)") The fixed inner structure is concentric with the outer structure at a downstream section and surrounds the core of the jet turbine engine downstream of the fan.

[0005] These external and internal structures define an annular flow duct, called the auxiliary duct, intended to guide a cold air flow, called the auxiliary flow, that circulates outside the jet turbine engine.

[0006] The outer structure comprises an outer fairing defining an outer aerodynamic surface and an inner fairing defining an inner aerodynamic surface. The inner fairing and the outer fairing are connected upstream by a leading edge wall forming an air intake lip.

[0007] In general, a jet turbine engine comprises a set of blades which are rotated by a gas generator through a set of transmissions. The nacelle also comprises a lubricant distribution system to ensure good lubrication of these transmissions and to cool them. The lubricant is advantageously oil.

[0008] For cooling the lubricant, the nacelle usually comprises a cooling system comprising at least one heat exchanger.The cooling system is configured to circulate a fluid, such as the lubricant or a coolant which will cool the lubricant.

[0009] Among the heat exchangers, air / lubricant exchangers are known that use air obtained from the auxiliary duct of the nacelle (the so-called cold stream) or from one of the first stages of the compressor. Suctioning and circulating air through the heat exchanger disturbs the flow of the air stream and causes an additional pressure drop (known as resistance), which is undesirable.

[0010] Heat exchangers are also known whose fins are fixed to one of the walls of the nacelle delimiting the auxiliary duct.The fluid is cooled by the flow of an air flow in the auxiliary duct which circulates along the fins on the surface of the exchanger.

[0011] Such a solution would also result in significant aerodynamic losses.

[0012] This can result in a significant penalty in fuel consumption.

[0013] Fluid cooling systems comprising structured surface exchangers are also known.

[0014] exist Figure 1 and Figure 2 In the example shown, the structural surface exchanger 10 without fins comprises a corrugated first skin 11 and a so-called smooth second skin 12 assembled by welding or brazing or riveting.

[0015] The distribution channel 13 is formed by assembling a first skin 11 with corrugations on a so-called smooth or aerodynamic second skin 12 , said skins 11 , 12 then forming the double wall of the inner and / or outer fairing.

[0016] Each distribution channel 13 is defined by the corrugations on the first surface 11 and the smooth second surface 12 .

[0017] A fluid (for example a heat transfer fluid or a lubricant) is intended to circulate in the channels 13 , and air is intended to circulate in contact with the smooth second skin 12 .

[0018] For this purpose, the smooth second skin 12 is intended to come into contact with the airflow. It enables the flow of the airflow to be maximized. An aerodynamic skin is mentioned.

[0019] The heat exchanger 10 further includes a fluid distributor 14 and a fluid collector 15 .

[0020] The fluid distributor 14 is a cavity formed in the corrugated first skin 11 for distributing the fluid at the inlet of the channels 13. The fluid distributor 14 is connected to the inlet hydraulic port 16 of the exchanger.

[0021] The fluid collector 15 is a cavity formed in the corrugated first skin 11 for distributing the fluid at the outlet of the channels 13. The fluid collector 15 is connected to the outlet hydraulic connection 17 of the exchanger.

[0022] The heat exchanger 10 further includes one or more reinforcements or reinforcing members 18 that are welded between the first skin 11 and the second skin 12 and are configured to provide structural strength to the exchanger.

[0023] In this regard, reference may be made to document FR 3 094 657, which describes a method for manufacturing a structural surface exchanger for a nacelle.

[0024] However, the presence of distributors and collectors causes a formation risk due to the orientation of the distribution channel being perpendicular to the orientation of the distributors and collectors. The formation of the connection radius of the distribution channel on the support surface and the connection radius of the distributor and collector on the support surface is not optimized and leads to a high risk of tearing of the metal sheet.

[0025] The hydraulic pressure drop is also high due to the presence of reinforcements between the distributor and the support surface, and between the collector and the support surface.

[0026] Furthermore, the unsupported widths of the points on the distributor, collector and hydraulic interface result in peeling forces that are incompatible with current standards in the field of lap welding.

[0027] There is a need to optimize systems for cooling fluids, in particular the heat exchange between a fluid and air, while optimizing the structural strength of the heat exchanger. Summary of the invention

[0028] It is therefore an object of the present invention to overcome the above-mentioned disadvantages.

[0029] The object of the present invention is to improve the heat exchange between a fluid circulating in a heat exchanger and air circulating outside the heat exchanger while optimizing the structural strength of the heat exchanger.

[0030] The object of the invention is a turbine engine nacelle comprising an outer structure and an inner structure defining an annular auxiliary flow duct intended to guide a flow of cold air (also called auxiliary flow) circulating outside a jet turbine engine. The nacelle comprises a casing for the turbine engine, which casing and the inner structure define an annular main flow duct.

[0031] The nacelle comprises at least one surface heat exchanger which is fixed to the outer structure on the auxiliary duct side or on a side outside the outer structure, or to the inner structure on the auxiliary duct side or on the main duct side.

[0032] When the heat exchanger is fixed to the inner surface of the inner cowl, the heat exchanger is fixed in the auxiliary duct so that the airflow circulating in the auxiliary duct contacts the second metal plate.

[0033] When the heat exchanger is fixed to the outer surface of the inner structure of the nacelle, the heat exchanger is fixed in the auxiliary duct so that the airflow circulating in the auxiliary duct contacts the second metal plate.

[0034] When the heat exchanger is fixed to the outer surface of the outer structure of the nacelle, the heat exchanger is fixed so that the external airflow comes into contact with the second metal plate.

[0035] Thus, the heat exchanger can be used to cool the fluid from the auxiliary flow or from the outside air.

[0036] When the heat exchanger is fixed to the inner surface of the internal structure, ie in the fluid flow of the main conduit, the heat exchanger can be used to heat the fluid from the main flow.

[0037] The surface heat exchanger comprises a first skin or a first metal plate and a second skin or a second metal plate assembled together, and at least three distribution channels arranged between the first metal plate and the second metal plate.

[0038] The exchanger also includes an inlet hydraulic port and an outlet hydraulic port.

[0039] Each of the distribution channels is directly connected to the inlet hydraulic port and the outlet hydraulic port, and the distribution channels are regularly distributed over the entire circumference of the inlet hydraulic port and / or the outlet hydraulic port.

[0040] Since there is no distributor and collector, the simplicity of forming the distribution channel is improved, and even the operation of forming the first metal plate can be omitted, and the hydraulic pressure drop is reduced and homogenized, which improves the thermal performance.

[0041] Furthermore, the unsupported width is reduced, which increases the structural strength capacity of the heat exchanger.

[0042] "Direct" refers to a direct connection without intermediate elements. In other words, there are no collectors and distributors between the channels and the corresponding inlet and outlet hydraulic connections.

[0043] This makes it possible to have a higher number of channels and, whatever the number of channels, to have a uniform distribution at the inlet or outlet. This also makes it possible to limit the pressure drop by supplying each channel directly from the inlet interface.

[0044] "Surface exchanger" refers to a heat exchanger without fins, which is a smooth exchanger whose walls or skin define tubes that form the heat exchange surface.

[0045] The absence of fins or other forms is intended to increase the contact surface between the flow and the exchanger and may not create any obstruction to the airflow in the duct, thus reducing the aerodynamic pressure drop.

[0046] "Metal sheet" refers to a hot-rolled or cold-rolled flat steel product with a generally smooth surface or sometimes with protrusions. Therefore, metal sheet is a metal material.

[0047] The distribution channel is configured to extend between the inlet hydraulic port and the outlet hydraulic port.

[0048] “Distributed over the entire circumference of the hydraulic ports” means that some channels are connected to one of the hydraulic ports via a first end that extends in a direction opposite to another of the hydraulic ports.

[0049] Each end is extended by a main portion, for example a straight line, which extends towards the other of the hydraulic connections up to a second end.

[0050] The second end may also extend in a direction opposite to one of the hydraulic ports.

[0051] For example, the channel is connected to the inlet hydraulic port through the inlet end, and is connected to the outlet hydraulic port through the outlet end.

[0052] For example, the inlet port is connected to the outlet port through the main portion.

[0053] The inlet end of at least one channel extends in a direction opposite to the outlet hydraulic port, and the outlet end of at least one channel extends in a direction opposite to the inlet hydraulic port.

[0054] For example, the inlet hydraulic port and the outlet hydraulic port have a circular cross section.

[0055] For example, the inlet hydraulic connection and the outlet hydraulic connection each comprise an outlet orifice extending in a plane perpendicular to the extension plane of the metal plate.

[0056] Advantageously, the thickness of each distribution channel is constant over the entire length of the corresponding channel.

[0057] For example, the distribution channels have the same cross-section as one another.

[0058] In a variant, the channels may have different cross-sections between each other. For example, the longest distribution channel may be configured to have a larger cross-section to balance the flow rates between the distribution channels.

[0059] According to one embodiment, each of the first metal plate and the second metal plate is flat.

[0060] In a variation, each of the first metal sheet and the second metal sheet is curved to provide aerodynamic continuity with the rest of the nacelle.

[0061] Advantageously, the exchanger comprises a plurality of struts or spacing members arranged between the first metal plate and the second metal plate, two adjacent spacing members delimiting a distribution channel.

[0062] For example, the first metal plate and the second metal plate are assembled together at the spacing member by an assembly area (eg, welding or brazing), the assembly area extending from the first metal plate to the second metal plate.

[0063] According to a variant, the assembly zone can pass through the corresponding spacing element.

[0064] For example, the thickness of each of the spacing members is between 2 mm and 4 mm, for example equal to 3 mm.

[0065] In a variation, the spacing member may form part of the second metal sheet by machining the inter-channel region and the channels directly on the second metal sheet. In this variation, the assembly region is of reduced thickness and extends from the first metal sheet to an adjacent portion of the second metal sheet.

[0066] For example, the cross section of each distribution channel is in the form of a quadrilateral, such as a trapezoid, a square, a rectangle, and the like.

[0067] According to one embodiment, the first metal sheet comprises a plurality of corrugations, and each distribution channel is defined by a corrugation of the corrugated first metal sheet and the second metal sheet.

[0068] For example, each distribution channel has a semicircular cross section.

[0069] Generally, the thickness of the first metal plate is between 1 mm and 2 mm, and the thickness of the second metal plate is between 0.6 mm and 2 mm.

[0070] The first metal plate and / or the second metal plate is made of aluminum or an alloy including aluminum. This improves the lightness and formability of the metal plate and the heat exchanger.

[0071] Advantageously, the exchanger comprises an axis of symmetry passing through the inlet hydraulic connection and the outlet hydraulic connection, the distribution channels being arranged symmetrically with respect to the axis of symmetry. BRIEF DESCRIPTION OF THE DRAWINGS

[0072] Other objects, features and advantages of the present invention will become apparent from a reading of the following description given only as a non-limiting example and with reference to the accompanying drawings, in which:

[0073] [ Figure 1 ]

[0074] is a schematic diagram of a structural surface exchanger according to the prior art;

[0075] [ Figure 2 ]

[0076] yes[ Figure 1 ] Detailed view of a partial cross section of an exchanger,

[0077] [ Figure 3 ]

[0078] is a schematic diagram of a surface heat exchanger according to one embodiment of the present invention;

[0079] [ Figure 4 ]

[0080] yes[ Figure 3 ] Detailed view of a partial cross section of an exchanger,

[0081] [ Figure 5 ]

[0082] is a schematic diagram of a surface heat exchanger according to a second embodiment of the present invention;

[0083] [ Figure 6 ]

[0084] yes[ Figure 5 ] Detailed view of a partial cross section of an exchanger,

[0085] [ Figure 7 ]

[0086] is a schematic diagram of a surface heat exchanger according to a third embodiment of the present invention;

[0087] [ Figure 8 ]

[0088] is a schematic diagram of a surface heat exchanger according to a fourth embodiment of the present invention;

[0089] [ Fig. 9 ]

[0090] is a schematic diagram of a surface heat exchanger according to a fifth embodiment of the present invention;

[0091] [ Fig.10 ]

[0092] is a schematic diagram of a surface heat exchanger according to a sixth embodiment of the present invention; and

[0093] [ Fig.11 ]

[0094] is a schematic diagram of a turbine engine according to one of the embodiments of the invention, the turbine engine comprising an aircraft nacelle equipped with a heat exchanger. DETAILED DESCRIPTION

[0095] In the following description, the terms "upstream" and "downstream" are defined relative to the direction of air circulation in the turbine engine. The terms "inner" and "outer" are defined relative to the longitudinal axis of the turbine engine, the term "inner" defining an element closer to said axis than an outer element.

[0096] Reference Figure 3 and Figure 4 In the example shown, the heat exchanger 20 includes a heat exchanger 20 comprising: Figure 4 ] visible struts or spacer members 23, 24 are a first skin or first metal plate 21 and a second skin or second metal plate 22 assembled one on the other.

[0097] The struts 23 , 24 and the second skin 22 form a single piece.

[0098] Each of the first skin 21 and the second skin 22 is flat. In a modification, the first skin 21 and the second skin 22 may be provided as curved skins.

[0099] The exchanger 20 comprises a plurality of distribution channels 25 , each distribution channel being defined laterally between two adjacent struts 23 and 24 and vertically between the first skin 21 and the second skin 22 .

[0100] The cross section of each distribution channel 25 is in the form of a rectangle here, and this is by no means restrictive. In a variant, the cross section can be set to the general form of any quadrilateral, such as a trapezoid, a square, etc. In general, the cross section of each distribution channel 25 can have any form.

[0101] As shown, the distribution channels 25 have the same cross-section as each other.

[0102] In a variant, the channels may have different cross-sections from one another.

[0103] For example, the longest distribution channel can be set to have a larger cross-section to balance the flow rates between the distribution channels, as shown in [ Figure 8 ] as shown in the example.

[0104] The distribution channel 25 is directly connected to an inlet hydraulic port 28 and an outlet hydraulic port 29 , respectively.

[0105] In other words, there are no longer any collectors and distributors between the channel 25 and the corresponding inlet hydraulic connection 28 and outlet hydraulic connection 29 .

[0106] like[ Figure 3] As shown in FIG. 1 , the inlet end 25a of the distribution channel 25 is evenly distributed (ie, regularly distributed) over the entire circumference of the inlet hydraulic interface 28, and the outlet end 25b of the distribution channel 25 is evenly distributed over the entire circumference of the outlet hydraulic interface 29.

[0107] Preferably, the distribution channels 25 may be regularly circumferentially distributed between the inlet hydraulic interface 28 and / or the outlet hydraulic interface 29. In other words, at the connection with the inlet hydraulic interface 28 and / or the outlet hydraulic interface 29, the “center” of each distribution channel 25 is regularly circumferentially spaced from the “center” of the adjacent distribution channel.

[0108] In general, the distribution channels 25 are distributed over the entire circumference of the inlet hydraulic connection 28 and / or the outlet hydraulic connection 29 .

[0109] “Distributed over the entire circumference” means that the inlet end 25 a of at least one channel 25 extends in a direction opposite to the outlet hydraulic port 29 , and the outlet end 25 b of at least one channel 25 extends in a direction opposite to the inlet hydraulic port 28 .

[0110] The inlet end 25a of the passage 25 and the outlet end 25b of the passage 25 have an arc shape.

[0111] The inlet end 25 a and the outlet end 25 b of the channel 25 are recessed toward the center of the exchanger 20 .

[0112] The inlet end 25a and the outlet end 25b are connected together by a main portion 25d (here, linear).

[0113] The first skin 21 and the second skin 22 are assembled at the pillars 23 and 24 by assembly areas 26 and 27 (for example, welding areas or brazing areas 26 and 27). The assembly areas 26 and 27 extend from the first skin 21 to the second skin 22, passing through the corresponding pillars 23 and 24.

[0114] In a variation, the spacing member may form part of the second metal sheet by machining the inter-channel region and the channels directly in the second metal sheet. In this variation, the assembly region is reduced in thickness and extends from the first metal sheet to an adjacent portion of the second metal sheet.

[0115] like[ Figure 3 ] as shown, the exchanger 20 comprises eight distribution channels 25, without this being restrictive in any way.

[0116] In a variant, the heat exchanger 20 may include a different number of distribution channels 25, for example greater than or equal to three (eg, Figure 7 ]), or greater than or equal to four (as shown in [ Fig. 9 ] as shown in the example in FIG. 1 , in which the same elements have the same figure marks.

[0117] exist Figure 3 , Figure 5 , Figures 7 to 9 In the embodiment shown, the exchanger 20, 30 comprises an axis of symmetry S1-S1 passing through the inlet connection 28 and the outlet connection 29. The distribution channels 25, 35 are arranged symmetrically with respect to said axis of symmetry S1, S1.

[0118] exist[ Fig.10 ], the inlet end 25a and the outlet end 25b of the channel 25 have depressions pointing to the center of the exchanger 20. The inlet end 25a and the outlet end 25b are connected together by a main portion, which includes a straight first portion 25d, a portion 25e having a depression pointing to the center of the exchanger 20, and a straight second portion 25f.

[0119] The thickness of each of the pillars 23 , 24 is between 2 and 4 mm, for example equal to 3 mm.

[0120] The exchanger 20 is a surface heat exchanger between a first fluid F1 and air F2 . The fluid F1 is intended to circulate in channels 25 , and the air is intended to circulate in contact with a smooth second skin 22 .

[0121] Since there is a support between the first skin 21 and the second skin 22, the step of forming the first skin is eliminated.

[0122] exist Figure 3 In the example shown, the hydraulic connections 28 , 29 are aligned on the longitudinal axis and the distribution channel 25 extends between them.

[0123] In a variation, the hydraulic ports 28, 29 may be arranged on another axis (e.g. Fig.10 The embodiments are aligned on a transverse axis as shown in the example in FIG. 2 , wherein like elements have like reference numerals.

[0124] In general, the invention is not limited to the form of distribution channels which are configured to extend between the inlet hydraulic connection 28 and the outlet hydraulic connection 29 .

[0125] Figure 5 and Figure 6 Shows that different from Figure 3 and Figure 4 Another embodiment of the illustrated embodiment differs only in that the first skin or the first metal sheet comprises a plurality of corrugations produced by forming the first skin.

[0126] like Figure 5 and Figure 6As shown, the heat exchanger 30 includes a first skin or a first metal plate 31 and a second skin or a second metal plate 32 .

[0127] The first skin 31 comprises a plurality of corrugations 35 c , and the second skin 32 is flat here.

[0128] The exchanger 30 comprises a plurality of distribution channels 35 , each of which is delimited by the corrugations 35 c of the corrugated first skin 31 , and the second skin 32 is smooth.

[0129] The exchanger 30 is a heat exchanger between a first fluid F1 and air F2 , the fluid F1 being intended to circulate in channels 35 and the air being intended to circulate in contact with a smooth second skin 32 .

[0130] Each distribution channel 35 has a semicircular cross section.

[0131] As shown, the distribution channels 25 have cross-sections that are the same size as each other.

[0132] In a variant, the channels may have cross-sections of different sizes from one another.

[0133] For example, the longest distribution channel can be arranged to have a larger cross section in order to balance the flow rates between the distribution channels.

[0134] The distribution channel 25 is directly connected to the inlet hydraulic port 38 and the outlet hydraulic port 39 , respectively.

[0135] In other words, there are no longer any collectors and distributors between the channel 35 and the corresponding inlet hydraulic connection 38 and outlet hydraulic connection 39 .

[0136] like[ Figure 5 ] As shown in FIG. 1 , the inlet end 35a of the distribution channel 35 is evenly distributed (ie, regularly distributed) over the entire circumference of the inlet hydraulic interface 38, and the outlet end 35b of the distribution channel 35 is evenly distributed over the entire circumference of the outlet hydraulic interface 39.

[0137] “Distributed over the entire circumference” means that the inlet end 35 a of at least one channel 35 extends in a direction opposite to the outlet hydraulic port 39 , while the outlet end 35 b of at least one channel 35 extends in a direction opposite to the inlet hydraulic port 38 .

[0138] The inlet end 35a of the passage 35 and the outlet end 35b of the passage 35 have an arc shape.

[0139] The inlet end 35a and the outlet end 35b of the channel 35 are recessed toward the center of the heat exchanger 30. The inlet end 35a and the outlet end 35b are connected together by a straight main portion 35d.

[0140] In a variation, a more complex form can be set, such as [ Fig.10 ] can be seen in ].

[0141] The first skin 31 and the second skin 32 are assembled on either side of the corrugation 35c of the corrugated skin 31 by welding or brazing areas 36, 37. The welding or brazing areas 36, 37 extend from the first skin 31 to the second skin 32.

[0142] Generally speaking, the thickness of the first skin 21 , 31 is between 1 mm and 2 mm, and the thickness of the second skin 22 , 32 is between 0.6 mm and 2 mm.

[0143] The first skin 21, 31 and / or the second skin 22, 32 are made of aluminum or an alloy including aluminum. This improves the lightness, heat exchange and formability of the skin.

[0144] For example, the exchanger is fluid-tight below 10 bar.

[0145] The heat exchangers 20, 30 described above are advantageously intended to be equipped in Fig. 9 Visible in the drawing is a turbine engine 50 or a nacelle 40 of an aircraft engine.

[0146] Fig. 9 An axial section of a turbine engine 50 with a general longitudinal axis XX', for example of a twin-shaft bypass jet turbine engine type, is shown highly schematically, the turbine engine comprising a fan 51 coupled to a gas turbine engine comprising a low-pressure compressor 52, a high-pressure compressor 53, an annular combustion chamber 54, a high-pressure turbine 55 and a low-pressure turbine 56.

[0147] The rotor of the high-pressure compressor and the rotor of the high-pressure turbine are connected together by a high-pressure (HP) shaft (not shown) and form a high-pressure body with them. The rotor of the low-pressure compressor and the rotor of the low-pressure turbine are connected together by a low-pressure (LP) shaft (not shown) and form a low-pressure body with them. The HP shaft and the LP shaft extend along the longitudinal axis XX' of the turbine engine 50.

[0148] The fan shaft is rotationally connected to the LP shaft directly or indirectly.

[0149] It should be noted that the invention is not limited to this turbine engine structure and can be applied to turbine engines of a different structure, for example of the bypass jet turbine engine type in which the low-pressure compressor acts as a fan.

[0150] The nacelle 40 of the turbine engine comprises a casing 41 for the turbine engine 50 and has a tubular structure comprising an external fairing 42 defining an external aerodynamic surface and an internal fairing 43 defining an internal aerodynamic surface for the flow through the turbine engine 50 , in particular the fan 51 .

[0151] The outer fairing 42 and the inner fairing 43 are connected upstream by an air intake lip 44 forming the front edge of the nacelle 40 .

[0152] The outer fairing 42 and the inner fairing 43 delimit an external structure generally comprising a fixed part and a movable part (not shown), such as a thrust reversal device.

[0153] The nacelle 40 also includes a fixed inner structure 45 , which is called an “inner fixed structure”, or “IFS” for short. The fixed inner structure 45 is concentric with the outer structure at a downstream section and surrounds the core of the jet turbine engine 50 downstream of the fan 51 .

[0154] These external and internal structures define an annular flow duct, called the auxiliary duct VS, intended to guide a cold air flow, called the auxiliary air flow, that circulates outside the jet turbine engine 50 .

[0155] Downstream of the fan 51 , the primary airflow F is separated by the fixed internal structure 45 of the nacelle (which serves here as a separation member) into a primary airflow FP and a secondary airflow FS.

[0156] The primary air flow FP travels through an internal passage or primary duct VP upon entering the low pressure compressor 52 , for example at an inlet guide vane 57 (abbreviated “IGV”).

[0157] The secondary air flow FS travels, for example, in the direction of the outlet guide vanes 58 (abbreviated as “OGV” (outlet guide vane)) through an outer annular channel or secondary duct VS and reaches the outlet of the turbine engine.

[0158] The nacelle 40 is equipped with the heat exchanger 20, 30, which is fixed here to the inner surface of the inner fairing 43. Therefore, the heat exchanger 20, 30 is fixed in the auxiliary duct VS so that the airflow circulating in the auxiliary duct VS contacts the second skin 22, 32 of the heat exchanger 20, 30.

[0159] In a variant, the heat exchangers 20 , 30 may be arranged to be fixed here to the outer surface of the inner structure 45 of the nacelle 40 .

[0160] According to another variant, the heat exchangers 20, 30 may be fixed to the outer surface of the outer fairing 42 of the nacelle 40. Thus, the heat exchangers 20, 30 may be used to cool a fluid coming from the secondary flow FS or from the outside air.

[0161] According to yet another variant, the heat exchangers 20 , 30 may be fixed to the inner surface of the internal structure 45 , ie in the fluid flow of the main pipe VP.

[0162] Thus, the heat exchangers 20, 30 may be used to heat fluid from the main flow FP.

[0163] The cooling air circulates through the exchanger, in particular the so-called smooth second skin 22 , 32 , where it recovers part of the thermal energy of the heat transfer fluid.

[0164] The present invention optimizes the heat exchange between the fluid circulating in the heat exchanger and the air circulating outside the heat exchanger, while improving the structural strength of the heat exchanger and reducing the aerodynamic pressure drop.

[0165] Furthermore, the absence of distributors and collectors improves the ease of forming the distribution channels, and even allows the formation operation to be omitted, thereby reducing and equalizing the hydraulic pressure drop.

Claims

1. A turbine engine nacelle (40), comprising an outer structure (42, 43) and an inner structure (45) defining an annular auxiliary flow duct (VS), the nacelle (40) comprising a casing for a turbine engine (50), the casing and the inner structure (45) defining an annular main flow duct (VP), the nacelle comprising at least one surface heat exchanger (20, 30), the at least one surface heat exchanger being fixed to the outer structure (42, 43) on the side of the auxiliary duct (VS) or on the side outside the inner structure (42, 43), or on the side of the auxiliary duct (VS) or on the side of the main flow duct (VP) The pipe (VP) is fixed to the internal structure (45) on one side, the surface heat exchanger (20, 30) includes a first metal plate (21, 31) and a second metal plate (22, 32) connected together, and at least three distribution channels (25, 35) arranged between the first metal plate (21, 31) and the second metal plate (22, 32), the exchanger also includes an inlet hydraulic interface (28, 38) and an outlet hydraulic interface (29, 39), each of the distribution channels (25, 35) is directly connected to the inlet hydraulic interface (28, 38) and the outlet hydraulic interface (29, 39), characterized in that The distribution channels (25, 35) are regularly distributed over the entire circumference of the inlet hydraulic interface (28, 38) and / or the outlet hydraulic interface (29, 39), and each of the distribution channels (25, 35) includes an inlet end (25a, 25b) and an outlet end (25b, 35b) each having a curved form.

2. The nacelle (40) according to claim 1, wherein: The distribution channels (25, 35) have the same cross-section as each other.

3. The nacelle (40) according to claim 1, wherein: The distribution channels (25, 35) have cross sections that are different from each other.

4. The nacelle (40) according to any of the preceding claims, comprising a plurality of spacing members (23, 24) arranged between the first metal plate (21) and the second metal plate (22), two adjacent spacing members (23, 24) defining a distribution channel (25).

5. The nacelle (40) according to claim 4, wherein: The first metal plate (21) and the second metal plate (22) are assembled together at the spacing members (23, 24) via an assembly area (26, 27), and the assembly area (26, 27) extends from the first metal plate (21) to the second metal plate (22).

6. The nacelle (40) according to any one of claims 1 to 3, wherein: The first metal plate (31) includes a plurality of corrugations (35c), and each of the distribution channels (35) is defined by the corrugations (35c) on the first corrugated metal plate (31) and the second metal plate (32).

7. The nacelle (40) according to claim 6, wherein: Each of the distribution channels (35) has a semicircular cross-section.

8. The nacelle (40) according to any one of the preceding claims, wherein: The exchanger (20, 30) comprises a symmetry axis (S1-S1) passing through the inlet hydraulic connection (28) and the outlet hydraulic connection (29), and the distribution channels (25, 35) are arranged symmetrically with respect to the symmetry axis (S1, S1).

9. The nacelle (40) according to any one of the preceding claims, wherein: The inlet hydraulic connection (28, 38) and the outlet hydraulic connection (29, 39) have a circular cross section and each include an outlet orifice extending in a plane perpendicular to the extension plane of the metal plate (21, 31; 22, 32).

10. The nacelle (40) according to any one of the preceding claims, wherein: The thickness of each distribution channel (25, 35) is constant over the entire length of the corresponding channel.

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