BE1030018B1 - TRIPLE-FLOW AXIAL TURBOMACHINE WITH DIVERGING HEAT EXCHANGER IN THE THIRD FLOW - Google Patents

Abstract

Axial turbomachine, comprising: a first separation nozzle capable of separating an incoming air flow into a radially internal air flow and a radially external air flow, called secondary flow; a second separation nozzle capable of separating the radially internal air flow into a primary flow and a tertiary flow (F3), the tertiary flow being in a tertiary flow vein (16) radially external to said primary flow, delimited by a wall inner (13) and an outer wall (11); and a heat exchanger (18) of the air/oil type, arranged in the tertiary flow stream; remarkable in that the heat exchanger comprises several angular sectors (38), each angular sector comprising an oil inlet (48) on the internal wall at one angular end of said sector, and an oil outlet (50) on said internal wall at an opposite angular end of said sector.

Description

Description

AXIAL TRIPLE-FLOW TURBOMACHINE WITH HEAT EXCHANGER

DIVERGING IN THE THIRD FLOW

Domain

The invention relates to the field of turbomachines and more particularly three-flow turbomachines. The invention relates to the arrangement of a heat exchanger intended for cooling the oil of the turbomachine.

Prior art

In a turbomachine (turbojet), it is generally necessary to cool oil in the lubrication circuit. For this purpose, it is known to place one or more heat exchanger(s) in the secondary flow, that is to say downstream of the fan.

However, the provision of a heat exchanger at the level of the secondary circuit penalizes the performance and the overall efficiency of the turbomachine. Indeed, the thrust force generated by the fan is partly slowed down by the bulky heat exchanger. In addition, aerodynamic disturbances of the secondary flow can take place causing vibrations and noise pollution.

The published patent document EP 3 674 531 A1 discloses a heat exchanger of the air-oil type placed in the vein of the secondary flow. Such a heat exchanger generates significant disturbances in the secondary flow path. Indeed, the air traversed in this vein has too high a speed for the aerodynamic or thrust losses to be negligible.

The state of the art therefore has drawbacks relating to performance penalties, to which is added the constraint linked to the fragility of the exchanger. Indeed, the latter cannot be placed directly upstream of the turbomachine to avoid disturbing its thrust force, in particular because of the risk of impact with foreign bodies which could enter the turbomachine.

Summary of the invention

Technical problem

The invention aims to solve the drawbacks of the design/manufacture of turbomachines of the state of the art. In particular, the invention aims to propose a solution which allows effective cooling in a restricted space while reducing the impact on the efficiency of the turbomachine.

Technical solution

The invention relates to an axial turbomachine, comprising: a first separation nozzle capable of separating an incoming air flow into a radially internal air flow and a radially external air flow, called secondary flow; a second separation nozzle capable of separating the radially internal air flow into a primary flow and a tertiary flow, the tertiary flow being in a tertiary flow vein radially external to said primary flow, delimited by an internal wall and an external wall; and a heat exchanger of the air/oil type, arranged in the tertiary flow stream; remarkable in that the heat exchanger comprises several angular sectors, each angular sector comprising an oil inlet on the internal wall at one angular end of said sector, and an oil outlet on said internal wall at an opposite angular end of said sector.

The turbomachine is in the form of a turboprop or a three-flow turbomachine.

According to an advantageous embodiment of the invention, each angular sector of the heat exchanger comprises one or more oil passages extending in the tertiary flow stream and, fluidically, between the corresponding oil inlet and the corresponding oil outlet.

According to an advantageous embodiment of the invention, each angular sector of the heat exchanger comprises an oil distributor extending circumferentially along the internal wall and comprising the oil inlet, and an oil collector. oil extending circumferentially along the inner wall and including the oil outlet.

According to an advantageous embodiment of the invention, each angular sector of the heat exchanger comprises several oil passages extending in the tertiary flow stream and, in a fluidic manner, between the oil distributor and the manifold. oil.

According to an advantageous embodiment of the invention, for each angular sector of the heat exchanger, the oil inlet and/or the oil outlet is integrally formed in the internal wall.

According to an advantageous embodiment of the invention, at least one of the sectors comprises a passage for short-circuiting said sector, extending fluidically between the oil inlet and the oil outlet along the wall internal.

According to an advantageous embodiment of the invention, the or each of the short-circuiting passages comprises a normally closed valve capable of opening in the presence of a pressure difference between the oil inlet and the oil outlet. oil, greater than or equal to a limit value.

According to an advantageous embodiment of the invention, the or each of the short-circuiting passages is formed entirely in the internal wall.

According to an advantageous embodiment of the invention, for each angular sector of the heat exchanger, the oil inlet and/or the oil outlet are located on a terminal downstream portion of said heat exchanger.

According to an advantageous embodiment of the invention, for each angular sector of the heat exchanger, the oil inlet and/or the oil outlet are located at a distance from a downstream edge of said heat exchanger at the level of the inner wall, which is less than 20% of a total extent of said heat exchanger along said inner wall.

According to an advantageous embodiment of the invention, said turbomachine comprises structural arms extending radially in the tertiary flow stream at junctions between the sectors of the heat exchanger.

According to an advantageous embodiment of the invention, each structural arm has, in the tertiary flow stream, a cross section with a width decreasing over a downstream half of said section.

According to an advantageous embodiment of the invention, for each angular sector of the heat exchanger, the oil inlet and the oil outlet are located at the level of the downstream half in axial projections of the cross section of more great width of the structural arms adjacent to said angular sector.

According to an advantageous embodiment of the invention, the heat exchanger comprises, over a total extent of the heat exchanger following the tertiary flow, a free portion of material forming an air bypass, said air bypass. the air being adjacent to the inner wall and adjacent to the collector and/or the distributor.

According to an advantageous embodiment of the invention, the air bypass is delimited radially inwards by the internal wall.

According to an advantageous embodiment of the invention, each angular sector of the heat exchanger comprises an oil inlet passage extending radially and laterally to the air by-pass from the oil inlet and a passage oil outlet extending radially and laterally from the air bypass to the oil outlet, said oil inlet and oil outlet passages being located at the downstream half in projections axial sections of the widest cross-section of the structural arms adjacent to said angular sector.

According to an advantageous embodiment of the invention, the oil inlet passage is distant from the oil outlet passage by a distance greater than at most 20% more than the circumferential width of the air by-pass.

Advantages of the invention

The invention is particularly advantageous in that it makes it possible to circulate in the heat exchanger an air which is cold and at an adequate speed, in particular thanks to the divergence of the exchanger in the direction of flow of the air, thus ensuring efficient cooling. Indeed, good cooling efficiency allows the use of less imposing and therefore less bulky, less heavy and less expensive exchangers.

In addition, the positioning of the exchanger at the level of the vein of the tertiary flow makes it possible to avoid hindering the efficiency of the engine, which results in energy efficiency and optimized thrust which advantageously makes it possible to reduce carbon dioxide emissions. .

Description of the drawings

Figure 1 is a longitudinal sectional view of a turbomachine comprising a heat exchanger, according to a first embodiment of the invention;

Figure 2 is a detail view of the heat exchanger of the turbine engine of Figure 1;

FIG. 3 is a front view of the tertiary flow stream comprising the heat exchanger, according to the first embodiment; Figure 4 schematically illustrates the oil paths in the heat exchanger over an angular sector, according to the first embodiment;

Figure 5 is a perspective and longitudinal section of a heat exchanger of a turbomachine according to a second embodiment;

FIG. 6 represents a cross-sectional view from above of the heat exchanger in the tertiary flow stream according to the second embodiment;

FIG. 7 represents a partial top view of the heat exchanger according to a third embodiment;

Figure 8 illustrates a density evolution of the heat exchange surfaces in the axial and circumferential directions.

Description of an embodiment

The turbomachine 2 evolves in an air flow F whose movement relative to the turbomachine 2 is generated by the rotation of the propeller 4 and the advancement of the aircraft on which the turbomachine 2 is mounted.

The air flow F is separated by a first splitter 10 into a radially internal air flow F′ and a radially external air flow F2, called secondary flow F2.

The propeller 4 can be arranged upstream of the first separation nozzle 10 or downstream.

The radially internal air flow F' passes through a mobile wheel 12 which directs the latter towards a second separation nozzle 14 capable of separating the radially internal air flow F' into a primary flow F1 and a tertiary flow F3, the latter is distinct from the secondary stream F2.

The first separation beak 10 comprises an internal wall forming a first external guide wall 11 of the radially internal air flow F', said first external guide wall 11 forming a convex profile seen from said radially internal air flow F' .

The second separation beak 14 comprises an external wall forming a second external guide wall 13 of the radially internal air flow F' having passed through the movable wheel 12, said second external guide wall 13 forming a convex profile seen from the tertiary flow F3.

The tertiary flow F3 enters a tertiary flow stream 16 radially external to said primary flow F1. The tertiary flow F3 passes through a heat exchanger 18 arranged in the tertiary flow vein 16.

The turbomachine 2 further comprises a stator (not shown) arranged upstream of the heat exchanger 18 at the level of the tertiary flow stream 16.

Advantageously, the stator makes it possible to straighten the tertiary flow F3 before the latter passes through the heat exchanger 18 in order to minimize the aerodynamic disturbances of the tertiary flow F3 which can be caused by the mobile wheel 12, this makes it possible to optimize the exchange heat between air and oil.

The heat exchanger 18 extends radially and axially in an upstream section 20 of the tertiary flow stream 16, presenting a divergent longitudinal section in the direction of the flow of the tertiary flow F3.

The heat exchanger 18 can overlap axially a high pressure compressor 15 as well as a low pressure compressor 17, called "booster" 17, said heat exchanger 18 can also be positioned axially above the low pressure compressor 17. Preferably, the heat exchanger 18 is arranged axially between the low pressure compressor 17 and the high pressure compressor 15.

A "VBV" channel 19 (Variabe Bleed Valve) having an outlet passing through an internal wall of the tertiary flow stream 16 and arranged axially downstream of the heat exchanger 18, the "VBV" channel makes it possible to ensure a function of discharge by returning part of the primary flow F1 to the tertiary flow F3, this makes it possible, for example, to evacuate any ice particles from the primary flow F1 to avoid jamming of the high pressure compressor 15, in particular when the flow rate of the primary flow F1 becomes too weak.

Advantageously, the arrangement of the outlet of the “VBV” channel 19 downstream of the heat exchanger 18 makes it possible to protect the latter from a possible risk of jamming.

The heat exchanger 18 can extend continuously over 360° in the upstream section 20 of the stream 16 around the longitudinal axis 8 of the turbomachine 2. Preferably, the heat exchanger 18 extends so discontinuous over 360° around the longitudinal axis 8 by being subdivided into several angular segments and each can ensure a heat exchange function between the air and the oil which can be different from one segment to another. Examples of the different heat exchange functions will be given later in this description.

The tertiary flow F3 crosses the heat exchanger 18 occupying the upstream section 20 of the vein 16 at a speed having a Mach number comprised in an interval ranging from 0.1 to 0.6, generally 0.3. Advantageously, the divergence of the upstream section 20 of the stream 16 makes it possible to contribute to the slowing down of the air by reducing its speed.

The tertiary flow stream 16 also includes a downstream section 22 having a convergent longitudinal section following the tertiary flow F3.

Advantageously, this makes it possible to accelerate the tertiary flow F3 at its exit from the heat exchanger 18 thus joining the secondary flow F2 to promote the thrust of the aircraft.

The heat exchanger 18 is of the "ACOC" type, an acronym for the English expression "Air-Cooled Oil Cooler", comprising oil passages which extend into the tertiary flow vein, said oil passages d extend particularly in a radial and axial direction between an upper wall and a lower wall of said heat exchanger 18.

Indeed, the heat exchanger 18 of the present invention is different from a "SACOC" surface air-oil exchanger, in which the oil remains in the lower and upper walls and does not cross the exchanger radially.

Advantageously, the “ACOC” heat exchanger 18 allows heat exchange between the air and the oil, preferably cooling of the oil by the air.

Indeed, the oil temperature can reach an operating temperature of up to 180°C and a flow rate of up to 30,000 l/h.

In this respect, the exchanger 18 can ensure the cooling of the oil used in several components of the aircraft, in particular, an engine, a gearbox,

an engine generator and any electronic component requiring cooling.

A single heat exchanger 18 can combine the cooling of several functions or oil circuits of the turbomachine, and this according to different parameters related to the need for oil cooling, i.e. inlet temperatures, flow rates, outlet temperature requested or the air conditions, the various circuits can be placed in thermal contact or isolated.

The exchanger 18 and in particular its oil passages can withstand low oil temperature down to -54°C.

Figure 2 is a detail view of the heat exchanger 18 of Figure 1.

Referring to Figure 2, the heat exchanger 18 is of the air / oil type with heat exchange surfaces with the air 26 which are in contact with the oil passages 24.

The exchange surfaces 26 have a divergent longitudinal section along the tertiary flow F3, i.e. the radial height separating two exchange surfaces 26 downstream of the exchanger is greater than the radial height separating said two exchange surfaces at the upstream of the interchange. In addition, the exchange surfaces 26 have a cross section which increases along the tertiary flow F3. Preferably, the heat exchanger 18 is a one-piece part obtained by additive manufacturing, and more preferably obtained by laser fusion on a bed of aluminum powder. The exchange surfaces 26 are preferably formed by thin plates, and each plate advantageously defines two exchange surfaces 26.

The oil passages 24 are arranged side by side with a number between 1 and 50, and preferably between 5 and 30, and more preferably between 10 and 25. Alternatively, the oil passages 24 can be merged so as to form a single channel.

Advantageously, the divergence of the heat exchanger 18 is sized to reduce the speed of the air by around 25%, i.e. the tertiary flow F3 passes for example from a speed of Mach 0.33 to a number of Mach about 0.2 at the exit of interchange 18.

In order to promote heat exchange between the oil passages 24 and the exchange surfaces 26, 60% of the cumulative length of said oil passages 24 extend in longitudinal planes distributed angularly around the longitudinal axis 8, and preferably 80% of the cumulative length, in said longitudinal planes. Advantageously, the oil passages 24 extending in the longitudinal planes are parallel to the direction of air flow.

To this end, the remaining 20% of the length of the oil passages 24 correspond to a transition 28 from one longitudinal plane to another allowing the oil to travel circumferentially through the heat exchanger 18. The upstream section 20 of the tertiary flow stream 16 comprises an external casing 30 and an internal casing 32. The upstream section 20 further comprises an external intermediate casing 31 and an internal intermediate casing 33, each of said external 31 and internal 33 intermediate casings is integral with the interchange 18.

Advantageously, the oil passages 24 and/or the exchange surfaces 26 are integrally formed with the external intermediate casing 31 as well as with the internal intermediate casing 33 of the exchanger 18.

The outer casing 30 is an integral part of the outer intermediate casing 31, and at the same time, the inner casing 32 is an integral part of the inner intermediate casing 33.

In this respect, the outer casing 30 comprises at an upstream end and/or at a downstream end, a fixing flange 34. Preferably, the outer casing 30 comprises two fixing flanges 34 arranged both at the upstream end and at the the downstream end of exchanger 18.

Similarly, the outer intermediate casing 31 of the exchanger 18 comprises at its upstream end and/or at its downstream end, at least one fixing flange 36.

To this end, each fixing flange 34 is configured to be fixed to the fixing flange 36 belonging to the exchanger 18. Preferably, the fixing flanges 34, 36 are circumferentially continuous around the longitudinal axis 8.

The mounting direction of the exchanger 18 in the turbomachine is preferably from downstream to upstream, i.e. in the opposite direction to the tertiary flow F3. In this configuration, the fixing of the exchanger 18 to the outer casing 30 can be ensured by screwing.

The fixing of the exchanger 18 with the internal casing 32 can be obtained by means of a rigid connection between a fixing flange belonging to the internal casing 32 with another fixing flange belonging to the exchanger 18, and precisely belonging to a angular sector 38 of the exchanger 18.

Indeed, the angular sector 38 is an integral part of the exchanger 18 and comprises an oil inlet passage 40 allowing the distribution of the oil in the oil passages 24. In this configuration, the fixing is preferably obtained by screwing between the two flanges (not shown) which can be arranged circumferentially around the longitudinal axis 8.

The exchanger 18 comprises over its total extent following the tertiary flow F3, a free portion of material 42 forming a bypass 42, commonly called an air bypass 42, and can also be called a "FOD" bypass, an acronym for the English expression "Foreign Object Debris". Indeed, the main role of an air bypass is to allow the passage of debris contained in the air flow through the turbomachine. Debris or “FOD” can, for example, be birds, hail, hailstones or any other object that could obstruct or damage the exchanger.

In this regard, the exchanger 18 includes the bypass 42 to allow debris to cross the vein 16 without blocking the passage of the tertiary flow F3 through the exchanger 18 or damaging the latter.

In parallel with the air bypass 42, a protective grid can be placed on the front face of the exchanger 18 to further protect the oil passages 24 and the exchange surfaces 26, and without hindering their ability to heat exchange.

With reference to FIG. 1 and FIG. 2, the air bypass 42 is adjacent to the outer casing 30 of the upstream section 22 of the tertiary flow stream 16. The air bypass 42 is delimited radially towards the outside by the outer intermediate casing 31 and more precisely delimited radially towards the outside by an upper face 44 belonging to the outer intermediate casing 31 of the exchanger 18, said upper face 44 is adjacent to the first outer guide wall 11 belonging to the outer casing 30.

The air bypass 42 is delimited radially inwards by a face 45 belonging to a wall radially delimiting the heat exchange surfaces 26, said wall having a constant radial height.

The air by-pass 42 extends radially over a height corresponding to a maximum of 20% of a total radial height of the upstream section 22 of the tertiary flow stream 16. Preferably, the height of the by-pass of air 42 extends radially to a maximum of 15% of a total radial height corresponding to the divergent longitudinal section of the vein 16.

The air bypass 42 has a constant radial height over the total extent of the exchanger 18 following the tertiary flow F3. Indeed, the height of the air bypass 42 remains constant and does not change in any way according to the flow of air because it is not desired to modify the speed of the latter, only the passage of debris is expected from the air bypass 42. Advantageously, this makes it possible to limit the difference in pressure drops between the air bypass 42 and the rest of the exchanger 18.

However, the radial height of the air by-pass 42 may vary in order to compensate for any pressure drops which may be caused by aerodynamic disturbances downstream of the exchanger. In this regard, the air bypass 42 may have a convergent and/or divergent longitudinal section.

Figure 3 is a front view, i.e. in the direction of air flow, of the tertiary flow stream 16 comprising the exchanger 18, of the turbomachine of Figure 1.

Referring to Figure 3, the exchanger 18 is distributed angularly in the tertiary flow stream 16, indeed, it can be considered that a plurality of exchangers 18 in the stream 16 represents a single exchanger 18.

The exchanger 18 comprises several angular sectors 38, each angular sector 38 comprises an oil inlet 48 on the second external guide wall 13 of the radially internal air flow, called internal wall 13 at one end ... angular of said sector 38.

The angular sector 38 also comprises at an opposite angular end an oil outlet 50 on the internal wall 13, the opposition of one end relative to the other relates to a radial axis (not shown) located in the middle of the angular sector.

The oil inlet 48 or the oil outlet 50 is integrally formed in the inner wall 13. Preferably, the oil inlet 48 and the oil outlet 50 are integrally formed in the inner wall 13.

Figure 4 illustrates a simplified sectional view of the heat exchanger 18 of the turbomachine of Figure 1, in which the air bypass 42 is located radially adjacent to the outer casing. The exchange surfaces 26 are not shown in order to simplify Figure 4.

The angular sector 38 comprises an oil distributor 52 extending circumferentially along the internal wall 13 and an oil collector 54 also extending circumferentially along the internal wall 13.

Several angular sectors 38 can comprise a single distributor 52 and a single oil collector 54. In this configuration, a single distributor can for example be connected to several cooling circuits of the axial turbomachine.

The oil distributor 54 includes the oil inlet 48 and the oil manifold includes the oil outlet 50. In this regard, the oil passages 24 extending fluidly into the tertiary flow stream between the corresponding oil inlet 48 and the corresponding oil outlet 50.

An oil outlet passage 55 is arranged between the oil passages 24 and the oil manifold 54, and a shorting passage may connect the oil inlet passage 40 to the oil outlet passage. oil 55.

Referring to Figure 2, the angular sector 38 comprises a short-circuiting passage 56 of said sector 38, also called oil bypass 56, the latter is integrally formed in the internal wall 13 and extends from fluidically between the oil inlet 48 and the oil outlet 50 along the internal wall 13. The exchanger 18 can comprise several oil bypasses 56.

Advantageously, the oil bypass 56 makes it possible to ensure the cold operation of the exchanger 18, in particular at temperatures around -40° C., in fact, cold oil has a high viscosity which is not suitable for allowing its passage through the exchanger 18, the oil therefore passes through the oil bypass 56 until it reaches a suitable viscosity.

In this regard, another circuit called the defrost circuit (not shown) may be arranged near or in contact with the oil bypass 56, and may also be in contact with the oil passages 24, the defrosting can ensure the heating of the oil included in the exchanger 18.

The oil bypass 56 comprises a normally closed valve 58 and capable of opening in the presence of a pressure difference between the oil inlet 48 and the oil outlet 50, greater than or equal to a value limit. Valve 58 can also open when the viscosity of the oil is too high compared to a previously identified threshold.

The oil inlet 48 is located on a terminal downstream portion of the exchanger 18 while the oil outlet 50 is located on an upstream portion of the exchanger 18.

However, reverse can be done or both inlet 48 and outlet 50 can be located at the downstream or upstream portion.

Figure 5 shows a partial perspective view of an exchanger 118 according to a second embodiment of the invention. It should be noted that a perspective view of interchange 118 is supposed to have an arcuate profile, however Figure 5 has been greatly simplified in order to facilitate understanding.

Indeed, the first embodiment consists in positioning the air by-pass 42 being adjacent to the outer casing 30. While the second embodiment consists mainly in positioning an air by-pass 142, having the same geometric configuration as the air bypass 42 described above. In this respect, the exchange surfaces 26 as well as the oil passages and all the other elements forming the exchanger 118 are identical to the exchanger 18.

The air bypass 142 is configured to be adjacent to the internal casing 32, this involves structural adjustments which will be fully detailed later in this description.

Referring to Figure 5, the air bypass 142 is adjacent to the internal casing (not shown) of the upstream section of the tertiary flow stream. The air bypass 142 is delimited radially inwards by the internal intermediate casing 33 and more precisely delimited radially inwards by a lower face 46 belonging to the internal intermediate casing of the exchanger 118, said lower face 46 is adjacent to the internal casing and particularly adjacent to the internal wall 13 illustrated in the preceding figures.

In this configuration, the lower face 46 forms a continuity of the tertiary flow vein with the internal wall 13, it can therefore be considered that the air bypass 142 is delimited radially inwards by the internal wall 13.

The air bypass 142 is delimited radially outwards by a face 47 belonging to a wall radially delimiting the heat exchange surfaces 26, said wall having a constant radial height.

The choice of the embodiment of the present invention can be made according to the overall arrangement of the various elements of the axial turbomachine, and more precisely according to the radial position of the top of one of the blades of the moving wheel with respect to the heat exchanger 18, 118 in combination with the geometric shape of the second outer guide wall 13 as shown in Figure 1.

Indeed, the modification of the position of the top of the blade of the impeller and the geometric shape of the wall of the tertiary flow stream results in the modification of the trajectory of the “FOD” debris.

Advantageously, the exchanger 18, 118 can be manufactured and adapted according to the architecture of the turbomachine in which it will be mounted in order to anticipate the radial part of the stream 16 which comprises the greatest risk of impact with the debris so that the air bypass 42, 142 is arranged there.

FIG. 6 represents a sectional view from above of the exchanger 118 in the tertiary flow stream according to the second embodiment.

The turbomachine comprises structural arms 60 adjacent to the angular sectors and extending radially in the tertiary flow stream at junctions between said angular sectors of the exchanger 118.

Each angular sector of the exchanger 118 extends circumferentially between two structural arms 60, so in the case where the exchanger 118 is angularly subdivided in the tertiary flow stream, said subdivision can be ensured by the structural arms 60.

The structural arms 60 are arranged axially downstream of the stator in the tertiary flow stream, and preferably between the low pressure compressor and the high pressure compressor.

Each structural arm 60 comprises an upstream portion comprising a leading edge, the exchanger 118 is arranged downstream of the latter. Advantageously,

this arrangement makes it possible to further minimize the aerodynamic disturbances of the tertiary flow F3 which may be caused by the moving wheel.

The structural arm 60 has a cross section with a width decreasing over a downstream half of said section forming a convergent downstream portion 62 of the structural arm 60.

The downstream portion 62 of each structural arm 60 comprises a trailing edge, the exchanger 118 is arranged upstream of said trailing edge. Preferably, the exchanger 118 is arranged between the leading edge and said trailing edge.

Advantageously, this makes it possible to improve the rigidity of the assembly of the exchanger 118 in the turbomachine and to better control the pressure drops and the aerodynamic disturbances. In addition, the leading edges of the structural arms 60 make it possible to promote heat exchange in convection between the oil and the tertiary flow F3.

The exchanger 118 extends circumferentially between two structural arms so that said exchanger 118 is in direct contact with each of the two structural arms 60. In this configuration, the heat exchange surfaces 26 are adjacent to the downstream portions 62 of the structural arms 60. Preferably, the heat exchange surfaces 26 have a diverging circumferential profile conforming to the downstream portions 62 of the structural arms 60.

Advantageously, this makes it possible to limit pressure drops.

The circumferential profile diverging from the heat exchange surfaces 26 is formed by side profiles 64 directly adjacent to the structural arms 60 and each comprising the downstream portion 62. In this respect, each downstream portion 62 comprises at least one inclined side profile 65, this last is inclined with respect to an axial direction and extends over at least 5% of the side profile 64 corresponding and preferably.

The inclined side profile 65 has an average inclination which depends on its axial extent compared to that of the side profile 64, the inclination can vary between 5° and 60°.

Preferably, the inclination of the inclined side profile 65 is of the order of 30° relative to the side profile 64, said inclination preferably extends over 30% of the axial length of the structural arm 60.

The oil passages 24 can partially or totally follow the inclination of the inclined side profile 65 of the structural arms 60.

It should be noted that the arrangement of the oil inlet as well as the oil outlet in the angular sector of the exchanger 118 depends on the embodiment of the invention.

Indeed, Figure 6 illustrates the second embodiment in which the air bypass 42 is delimited radially inwardly by the internal casing. In this respect, for each angular sector of the exchanger 118, the oil inlet 40 and oil outlet 55 passages are located at the level of the downstream half 62 in axial projections 61 of the cross section of more large width of the structural arms 60.

The axial projections 61 are called terminal downstream portions 61, the oil inlet 40 and oil outlet 55 passages are arranged in said terminal downstream portions 61.

Preferably, the exchanger is arranged axially at the level of the greatest width of the structural arms 60, this advantageously makes it possible to facilitate the assembly of said exchanger which is done from downstream to upstream.

Preferably, the oil inlet and/or the oil outlet are located at a distance from a downstream edge 63 of the exchanger 118 which is less than 20% of its total axial extent, and more preferably, at a distance less than 5% of its total extent.

The air bypass 142 is delimited circumferentially by the sides 43, the latter can conform to the side profile 64, in Figure 6, the sides 43 do not conform to the inclined side profile 65.

The oil inlet passage 40 as well as the oil outlet passage 55 extend radially and laterally to the air bypass 142, the latter two being separated from each other by a distance greater than the circumferential width of the air bypass 142, i.e. between two sides 43.

Preferably, the oil inlet passage 40 is distant from the oil outlet passage 55 by a distance greater than at most 20% more than the circumferential width of the air bypass 142, and more preferably , by a distance greater than at most 5% more than the circumferential width of the air bypass 142.

It should be noted that the arrangement of the oil inlet passage 40 and the oil outlet passage 55 illustrated in FIG. 6 may be suitable for the exchanger 18 according to the first embodiment.

FIG. 7 represents a partial top view of the exchanger 18 or 118 illustrating a third embodiment of the invention in which the exchanger 18, 118 presents a change in the number per unit area of its surfaces d exchange 26, called density evolution, located in a portion 66 adjacent to the structural arms 60, with respect to the number per unit area of the exchange surfaces 26 located in a central part 68.

The adjacent portion 66 can be considered as being a boundary layer to the exchanger, and the evolution of the density is in the circumferential direction and it is at least 20% and preferably 50%.

The exchanger 18, 118 therefore has 50% more exchange surfaces 26 at the level of the adjacent portion 66 compared to the number of exchange surfaces at the level of the central part 68.

Advantageously, the evolution of density in the circumferential direction makes it possible to slow down the air and to accompany its flow up to the downstream portion 62, thus promoting heat exchange between the oil and the air. The reduction in pressure drops and the reduction in the generation of drag at the level of the flow of the tertiary flow F3 also present another advantage of the invention.

Figure 8 illustrates the evolution of the density of the exchange surfaces 26 in the axial and circumferential direction.

The exchange surfaces 26 of the exchanger have a cross section having a pattern preferably in hexagonal form, however, in order to illustrate the evolution in a simplified way, a rectangular pattern has been illustrated in Figures 7 and 8.

With reference to FIG. 7 and FIG. 8, the number of exchange surfaces 26 per surface unit increases in the adjacent part 66 as the circumferential increase of the cross section at the tertiary flow F3.

Indeed, the flow of the tertiary flow F3 gradually diverges in the circumferential direction to follow the inclined side profile 65 of the downstream portion 62 of each structural arm 60.

To this end, the increase in the number of exchange surfaces 26 per unit area takes place along one or more sectors 67, 69, and between each sector of the adjacent part 66, the increase per unit area of the number exchange surfaces 26 is at least 20% and preferably 50%.

The evolution of the density of the exchange surfaces is also possible in the radial direction by following the divergence of the tertiary flow vein in the longitudinal section, this allows to have the same advantages as the evolution of the density in the axial and circumferential directions.

Advantageously, the arrangement of the heat exchanger according to the invention and in particular the divergent tertiary flow stream, makes it possible to supply the exchanger with air that is cold enough and slow enough so that both the cooling efficiency of oil is ensured and that the aerodynamic losses linked to the presence of the heat exchanger are limited, thus favoring the thrust of the aircraft while contributing to the reduction of carbon dioxide emissions.

It should be noted that the invention is not limited to the examples described in the figures. The teachings of the present invention may in particular be applicable to another type of turbomachine.

Each technical characteristic of each illustrated example is applicable to the other examples. In particular, the evolution of the density of the heat exchange surfaces can apply to the exchanger in the three directions, with an air bypass radially adjacent to the external or internal casing.

Claims (17)

Claims 1. Axial turbomachine (2), comprising: - a first separation nozzle (10) capable of separating an incoming air flow (F) into a radially internal air flow (F') and a radially external (F2), called secondary flow (F2); - a second separation nozzle (14) capable of separating the radially internal air flow (F') into a primary flow (F1) and a tertiary flow (F3), the tertiary flow (F3) being in a flow stream tertiary (16) radially external to said primary flow (F1), delimited by an internal wall (13) and an external wall (11); and - a heat exchanger (18, 118) of the air/oil type, arranged in the tertiary flow stream (16); characterized in that the heat exchanger (18, 118) comprises several angular sectors (38), each angular sector (38) comprising an oil inlet (48) on the internal wall (13) at an angular end of said sector (38), and an oil outlet (50) on said inner wall (13) at an opposite angular end of said sector (38). 2. Axial turbomachine (2), according to claim 1, characterized in that each angular sector (38) of the heat exchanger (18, 118) comprises one or more oil passages (24) extending in the tertiary flow vein (16) and, fluidically, between the corresponding oil inlet (48) and the corresponding oil outlet (50). 3. Axial turbomachine (2), according to claim 1, characterized in that each angular sector (38) of the heat exchanger (18) comprises an oil distributor (52) extending circumferentially along the inner wall (13) and comprising the oil inlet (48), and an oil collector (54) extending circumferentially along the inner wall (13) and comprising the oil outlet ( 50). 4. Axial turbomachine (2), according to claim 3, characterized in that each angular sector (38) of the heat exchanger (18, 118) comprises several oil passages (24) extending in the vein of tertiary flow (16) and fluidically between the oil distributor (52) and the oil collector (54). 5. Axial turbomachine (2), according to one of claims 1 to 4, characterized in that for each angular sector (38) of the heat exchanger (18, 118), the oil inlet (48) and/or the oil outlet (50) is integrally formed in the inner wall (13). 6. Axial turbomachine (2), according to one of claims 1 to 5, characterized in that at least one of the sectors (38) comprises a short-circuiting passage (56) of said sector (38), s extending fluidly between the oil inlet (48) and the oil outlet (50) along the inner wall (13). 7. Axial turbomachine (2), according to claim 6, characterized in that the or each of the short-circuiting passages (56) comprises a normally closed valve (58) and capable of opening in the presence of a pressure difference between the oil inlet (48) and the oil outlet (50), greater than or equal to a limit value. 8. Axial turbomachine (2), according to one of claims 6 to 7, characterized in that the or each of the short-circuiting passages (56) is integrally formed in the internal wall (13). 9. Axial turbomachine (2), according to one of claims 1 to 8, characterized in that for each angular sector (38) of the heat exchanger (118), the oil inlet (48) and/ or the oil outlet (50) are located on a terminal downstream portion (61) of said heat exchanger (18). 10. Axial turbomachine (2), according to claim 9, characterized in that for each angular sector (38) of the heat exchanger (118), the oil inlet (48) and/or the oil outlet (50) are located at a distance from a downstream edge (63) of said heat exchanger (18) at the inner wall (13), which is less than 20% of a total extent of said heat exchanger ( 118) along said inner wall (13). 11. Axial turbomachine (2), according to one of claims 1 to 10, characterized in that said turbomachine (2) comprises structural arms (60) extending radially in the tertiary flow stream (16) at junctions between the sectors (38) of the heat exchanger (18, 118). 12. Axial turbomachine (2), according to claim 11, characterized in that each structural arm (60) has, in the tertiary flow stream (16), a cross section with a width decreasing over a downstream half (62) of said section. 13. Axial turbomachine (2), according to claim 12, characterized in that for each angular sector (38) of the heat exchanger (118), the oil inlet (48) and the oil outlet ( 50) are located at the downstream half (62) in axial projections (61) of the widest cross-section of the structural arms (60) adjacent said angular sector (38). 14. Axial turbomachine (2), according to one of claims 1 to 13, characterized in that the heat exchanger (118) comprises, over a total extent of the heat exchanger (118) following the tertiary flow ( F3), a free portion of material (142) forming an air bypass (142), said air bypass (142) being adjacent to the internal wall (13) and adjacent to the collector (54) and /or to the distributor (52). 15. Axial turbomachine (2), according to claim 14, characterized in that the air bypass (142) is delimited radially inwards by the internal wall (13). 16. Axial turbomachine (2), according to claim 13 and according to one of claims 14 and 15, characterized in that each angular sector (38) of the heat exchanger (118) comprises an inlet passage of oil passage (40) extending radially and laterally to the air bypass (142) from the oil inlet (48) and an oil outlet passage (55) extending radially and laterally to the by- air passage (142) to the oil outlet (50), said oil inlet (40) and oil outlet (55) passages being located at the level of the downstream half (62) in axial projections (61) of the widest cross-section of the structural arms (60) adjacent to said angular sector (38). 17. Axial turbomachine (2), according to claim 16, characterized in that the oil inlet passage (40) is distant from the oil outlet passage (55) by a distance greater than at most 20% more than the circumferential width of the air bypass (142).