Cooling assembly for a blower blade foot support using a Peltier-cooled airflow

Abstract

Cooling assembly for a blower blade foot support by a Peltier-cooled airflow. The invention relates to a cooling assembly (2) comprising a support (8) for blower blade feet (7) (4) (5), a front bearing enclosure wall (20) (19) located opposite said support, and a hollow annular volume (21) located between the two. The assembly further comprises: a pressurized air circuit (24), extending between an inlet (26) connected to the air stream (30) of the compressor assembly and an outlet (27) opening into the hollow annular volume, and a Peltier effect heat exchanger (31), comprising: at least one electrically powered Peltier module (33) comprising a cold plate (37) and a hot plate, and a heat exchange chamber (32), belonging to the pressurized air circuit, which is positioned against the cold plate of the Peltier module. Figure to be published with the abbreviation: Figure 1

Description

Title of the invention: Cooling assembly for a blower blade support using a Peltier-cooled airflow. TECHNICAL FIELD OF THE INVENTION

[0001] The present invention relates to a cooling assembly for the blade roots of a turbomachine blower, as well as a turbomachine comprising such a cooling assembly.

[0002] More specifically, the invention relates to a cooling assembly for the support of the blade feet of a blower by means of a pressurized airflow cooled by Peltier effect.

[0003] The invention finds applications in the field of aircraft turbomachinery, in particular turbojet engines for civil and military aircraft. TECHNOLOGICAL BACKGROUND OF THE INVENTION

[0004] In aircraft turbomachinery, particularly jet engines, the fan blade roots are typically made of resin. While this material offers the advantage of producing blade roots that are lightweight, strong, and of precise, complex shapes, it has the disadvantage of poor resistance to high temperatures. To avoid any risk of deformation and / or deterioration, the temperature of the resin parts must be kept below the glass transition temperature of the resin from which they are made.

[0005] Now, in general, the upstream bearing enclosure of the blower shaft, also called the front bearing enclosure, in which bearings and other lubricated devices such as, for example, a reducer are located, is situated directly below the blower, with its outer wall placed opposite and at a short distance from the support of the blower blade feet.

[0006] Due to the high temperature of the lubricating oil circulating in this enclosure and the heating due to the operation of the bearings, one of which is often located just below the blower, the outer wall of the enclosure heats up rapidly during the operation of the turbomachine and reaches significant temperatures which can approach the glass transition temperature of the resin of the blade roots.

[0007] However, since there is only a weak current of hot air circulating between the hot wall of the enclosure and the blade support, with a flow rate too low and a temperature too high to effectively dissipate the heat from the enclosure, this results in a stratification of the thermal environment in this area. The hot wall of the enclosure, located near and opposite the blade support, is thus responsible for a significant rise in the temperature of the feet of the blower blades, both by radiation and by convection.

[0008] Moreover, this problematic situation tends to worsen in recent turbomachines, due to a general tendency to want to decrease the flow rate and increase the temperature of the oil injected into the bearing housings in order to optimize the operation of the lubrication system and the performance of the turbomachine in general, which further increases the resulting temperature of the wall of these housings.

[0009] There is therefore a need, not yet met, for a device which would allow the feet of the blower blades to be cooled, in order to ensure that their temperature remains below the glass transition temperature of the resin which composes them, despite the hot environment in which they are placed. Summary of the invention

[0010] The invention aims to solve this technical problem.

[0011] For this purpose, a first aspect of the invention teaches a cooling assembly for a blade foot support of an aircraft turbomachine blower.

[0012] This cooling assembly comprises: • a fan blade support in which at least one fan blade support is mounted, • a front landing enclosure wall located opposite said support, and • a hollow annular volume located between said support and said front landing enclosure wall.

[0013] It is characterized in that it further comprises: • a pressurized air circuit, in which a pressurized airflow circulates, extending between an inlet intended to be connected to an air stream of a compressor assembly of the turbomachine and through which the pressurized airflow enters, and an outlet opening into said hollow annular volume and through which the pressurized airflow exits, and • a Peltier effect heat exchanger, comprising: • at least one Peltier thermoelectric module (also called a "Peltier module"), electrically powered and comprising a cold plate and a hot plate, and • a heat exchange chamber, positioned against the cold plate of the Peltier module, which is part of the pressurized air circuit and is traversed by the pressurized air flow.

[0014] Thanks to the device according to the invention, pressurized air is sent into the pressurized air circuit, where it passes through the heat exchange chamber of the exchanger, before to be released into the hollow annular volume located between the support of the blower blade feet and the hot wall of the front bearing enclosure.

[0015] As the heat exchange chamber is positioned against the cold plate of the electrically powered Peltier module, the hot air from the turbomachine duct cools down when it passes near the cold plate of the module through the heat exchange chamber.

[0016] Thus, cold air is sent into the hollow annular volume at a sufficient flow rate to extract heat from the blade root and its support. Continuous cooling of the support and blade roots is thereby ensured, guaranteeing that their temperature is maintained at an acceptable low value, below the glass transition temperature of the resin.

[0017] Advantageously, the outlet of the pressurized air circuit may include a device for guiding the outgoing airflow towards the blade foot support, such as a nozzle or a deflector for example.

[0018] In addition, this cold air circulation advantageously creates a cold screen which is interposed between the blade foot support and the hot wall of the front bearing enclosure and thermally insulates the support from the opposite heat source.

[0019] Finally, when released into the hollow annular volume, this cold air helps to lower the overall temperature of this volume, as well as that of the external face of the wall of the front bearing enclosure.

[0020] All these cumulative phenomena make it possible to guarantee an acceptable temperature for the support and the blade feet it contains, which thus remains largely below the glass transition temperature of the resin, despite the proximity of the hot wall of the front bearing enclosure.

[0021] Furthermore, the use of a Peltier effect exchanger to cool the pressurized airflow has many advantages.

[0022] First of all, it is compatible with the temperature differentials of the area concerned and the thermal powers to be evacuated.

[0023] Furthermore, since its operation is based on the action of one or more Peltier modules, it is not necessary to use another heat transfer fluid in the exchanger to cool the pressurized air. The installation of a second heat transfer fluid circulation circuit in the turbomachine is thus avoided, saving space and, above all, weight, and reducing the risk of leaks and failures. In addition, it is not necessary to provide a second air intake from a turbomachine duct to cool the pressurized air, which limits the overall performance degradation caused by such intake.

[0024] On the other hand, the Peltier effect heat exchanger has a small footprint and no moving parts. It is also insensitive to vibrations.

[0025] All these characteristics of the Peltier effect exchanger make the cooling assembly according to the invention particularly advantageous.

[0026] Advantageously, in the heat exchange chamber, the pressurized airflow can be in direct contact with the cold plate. Since there is no additional wall interposed between the pressurized air passing through the heat exchange chamber and the cold plate of the Peltier module, the efficiency of cooling the pressurized air is improved.

[0027] Advantageously, the heat exchange chamber can contain internal walls, fins, or baffles. These walls, fins, or baffles thus increase the exchange surface area between the pressurized air and the cold plate inside the exchange chamber. The efficiency of the pressurized air cooling is thereby improved, as it is possible to extract more heat from the same exchanger volume. The exchanger volume can also be reduced for the same amount of heat extracted, thereby reducing the exchanger's overall size.

[0028] Alternatively, the heat exchange chamber can be a section of coiled tubing. The coiled sections of tubing also lengthen the airflow path, increasing the heat exchange surface area with the cold wall of the Peltier module. This improves the efficiency of cooling the pressurized air.

[0029] Advantageously, the support, or at least one of the blade feet mounted in said support, may include one or more passages or cavities opening into the hollow annular volume. Cooled air present in the hollow annular volume can thus rush into this or these passages or cavities and penetrate the interior of the support or the blade feet, facilitating their thorough cooling and making them more efficient.

[0030] Advantageously, the cooling assembly may further comprise a Seebeck effect thermoelectric generator, comprising at least one Seebeck effect thermoelectric module (referred to as a "Seebeck module"), which electrically supplies the Peltier module(s) of the Peltier effect exchanger.

[0031] The Seebeck module(s) of the Seebeck-effect thermo-electricity generator produce electricity when a temperature difference exists between their two plates. The electricity produced is sent to the Peltier module(s) of the Peltier heat exchanger, which are then electrically powered and can produce cooling. It is therefore unnecessary to add a dedicated electric generator or to use part of the electricity produced by an electric generator already present in the turbomachine or aircraft for another function.

[0032] Advantageously, such a Seebeck effect thermo-electricity generating device has a small footprint, has no moving parts and is insensitive to vibrations.

[0033] A second aspect of the invention relates to a turbomachine comprising a cooling assembly as described above.

[0034] Advantageously, when the turbomachine is a twin-body turbomachine whose compressor assembly includes a low-pressure compressor and a high-pressure compressor, the inlet of the pressurized air circuit can be connected to the air stream between the low-pressure compressor and the high-pressure compressor.

[0035] Between the low-pressure compressor and the high-pressure compressor, there is sufficient space to provide an air inlet located away from moving parts and which does not interfere with the operation of the turbomachine. Furthermore, the temperature of the air drawn in at this point is lower than at the outlet of the high-pressure compressor, while its pressure is already sufficient.

[0036] However, air sampling can also be carried out on a stage of the low pressure compressor or the high pressure compressor.

[0037] Advantageously, when the turbomachine is a double-flow turbomachine comprising an inter-flow compartment located between a primary air flow that passes through the compressor assembly and a secondary air flow, the Peltier effect exchanger can be disposed in the inter-flow compartment, with the hot plate of the Peltier module(s) placed against a wall separating the inter-flow compartment from the secondary air flow.

[0038] The inter-vein compartment is sufficiently spacious to accommodate the Peltier effect exchanger. Furthermore, when the hot plate of the Peltier module(s) is placed against the wall of the casing that separates the inter-vein compartment from the secondary air vein, the heat from this hot wall is transferred to this wall and can advantageously be dissipated by the airflow circulating in the secondary air vein and flowing against this wall.

[0039] Advantageously, when the turbomachine is a double-flow turbomachine comprising an inter-flow compartment located between a primary air flow which passes through the compressor assembly and a secondary air flow, and when the turbomachine further comprises a Seebeck effect thermo-generator of electricity, comprising at least one Seebeck module, which electrically supplies the Peltier module(s) of the Peltier effect exchanger, this Seebeck effect thermo-generator of electricity can be disposed in the inter-flow compartment, with a plate of the Seebeck module(s) placed against a wall separating the inter-flow compartment from the secondary air flow.

[0040] The inter-vein compartment is sufficiently spacious to house the Seebeck effect thermo-electricity generator. Furthermore, when a plate of the Seebeck module(s) is placed against the casing wall separating the inter-vein compartment from the secondary airflow, there is a suitable and sufficient temperature differential, which does not reverse during the different phases of flight, to continuously produce electricity between its two plates, with one plate subjected to the temperature of this wall, which is cooled by the airflow circulating in the secondary airflow on the other side of the wall, and another plate subjected to the relatively warm temperature prevailing in the inter-vein compartment.

[0041] The invention and its various applications will be better understood by reading the following description and examining the accompanying figures. BRIEF DESCRIPTION OF THE FIGURES

[0042] The figures are presented for illustrative purposes only and are in no way limiting of the invention.

[0043] [Fig.1] and [Fig.2] are schematic cross-sectional views of a first and second example of a cooling assembly according to the invention.

[0044] [Fig.3] and [Fig.4] are schematic overall cross-sectional views of a third and of a fourth example of a cooling assembly according to the invention.

[0045] [Fig.5] is a schematic top view of an example of a Peltier effect heat exchanger cooling assembly according to the invention.

[0046] [Fig.6] and [Fig.7] are schematic cross-sectional views along the VLVI axis shown on [Fig.5], of two variants of the Peltier effect exchanger of [Fig.5].

[0047] [Fig.8] is a schematic top view of another example of an effect heat exchanger Peltier cooling assembly according to the invention.

[0048] [Fig. 9] and [Fig. 10] are schematic cross-sectional views along the IX-IX axis shown on [Fig.8], of two variants of the Peltier effect exchanger of [Fig.8]. DETAILED DESCRIPTION

[0049] Unless otherwise specified, the same element appearing on different figures has a unique reference.

[0050] In the present application, the terms "upstream" or "front" and "downstream" or "rear" are defined with respect to the normal direction of gas flow (from upstream / front to downstream / rear) through a turbomachine.

[0051] The "turbomachine axis" is the longitudinal axis of the turbomachine corresponding to the axis of rotation of the turbomachine's rotor. A radial direction is a direction perpendicular to the turbomachine axis and intersecting this axis.

[0052] Unless otherwise specified, the adjectives "internal" and "external" are used with reference to a radial direction, so that the internal part of an element is, according a radial direction, closer to the axis of the turbomachine than the outer part of the same element.

[0053] The term "bearing enclosure" refers to a pressurized chamber in which one or more lubricated bearings are housed. The terms "upstream or forward bearing enclosure" and "upstream or forward enclosure" are synonymous and refer to the bearing enclosure located furthest upstream of the turbomachine.

[0054] Figures 1 and 2 schematically represent a front portion of a turbomachine 1 in which an example of a cooling assembly 2 according to the invention has been installed. The turbomachine 1 shown includes a reduction gear to decrease the rotational speed of the fan relative to that of the low-pressure shaft, but it is understood that the invention also applies to a turbomachine without a reduction gear.

[0055] In this forward portion of turbomachine 1 there is conventionally a fan shaft 3, on which is mounted a ring of movable blades 4 called a fan 5. Each of these blades 4 has a body 6 (also called a blade) and a foot 7 and extends radially from a support 8 of blade feet mounted on the fan shaft 3 and in which the feet 7 of the blades 4 are engaged.

[0056] The blade feet support 8 shown is an annular support comprising a hub 9 fixed to the shaft 3, a disc-shaped flange 10 and a rim 11 on which the feet 7 of the blades 4 are fixed.

[0057] The blower shaft 3, the blade foot support 8 and the blower 5 form an assembly which is mobile in rotation around an axis X corresponding to the longitudinal axis of the turbomachine 1.

[0058] For this purpose, the shaft 3 is assembled to the fixed housing 12 of the turbomachine 1 by means of bearings 13, such as the ball bearing 14 and the cylindrical roller bearing 15 located in the front portion shown. These bearings 13, which are lubricated devices, are arranged in ventilated enclosures 16, the pressure of which is maintained below that of the external environment to prevent oil leaks, which are delimited by walls 17 and the blower shaft 3, and which are closed by seals 18, preferably of the labyrinth type.

[0059] The enclosure 16 containing the ball bearing 14 and the cylindrical roller bearing 15 shown is the upstream bearing enclosure 19. This enclosure 16 is annular and extends all around the blower shaft 3, with the X-axis as its axis of rotational symmetry. As can be seen in the figures, it has an external wall portion 20, located opposite the blade root support 8. More precisely, this wall portion 20 is located just below the downstream part of the rim 11, opposite and at a short distance from it.

[0060] Between the blade root support 8 and the portion of wall 20 of the upstream bearing housing 19 is a hollow annular volume 21 which extends both upstream and downstream. This hollow annular volume 21, whose axis X constitutes the axis of symmetry of revolution, is bounded by the external wall 17 of the upstream bearing housing 19, the portion of wall 20, the blower shaft 3, the blade root support 8, a wall 22 of the fixed casing 12 and a sealing ferrule 23.

[0061] Due to the high temperature of the lubricating oil in the upstream bearing housing 19 and the heating of the cylindrical roller bearing 15 directly below it, the wall portion 20 heats up rapidly when the turbomachine 1 is operating. As it is located below and in the immediate vicinity of the blade foot support 8, its heat is transferred to the support 8 and to the resin blade feet 7 it contains.

[0062] To avoid this, a cooling device 2 is provided.

[0063] It includes a pressurized air circuit 24, in which a pressurized air flow 25 (symbolized by dashed arrows in the figures) circulates between an inlet 26 and an outlet 27 opening into the hollow annular volume 21.

[0064] As shown in Figures 1 and 2, this pressurized air circuit 24 can advantageously pass through a service arm 28 or inside a straightener 29 downstream of the blower 5 to cross the air stream 30 of the turbomachine 1, before arriving at the hollow annular volume 21 into which it opens through the outlet 27.

[0065] The cooling device 2 also includes a Peltier effect exchanger 31, comprising a heat exchange chamber 32 and at least one Peltier module 33.

[0066] In a conventional manner and as shown in Figures 6, 7, 9 and 10, this Peltier module 33 comprises two ceramic plates 34 between which is arranged a succession of semiconductor elements 35 of alternating polarity, connected to each other by a conductor 36. When an electric current flows in the conductor 36, a heat flux is generated by the semiconductor elements 35 between the two plates 34, one of which, called the cold plate 37, becomes colder, and the other, called the hot plate 38, becomes hotter.

[0067] To produce the desired heat flux, this Peltier module 33 is electrically powered, via the electrical wires 39, for example by means of an electrical generator 40 as shown in [Fig.1].

[0068] This electric generator 40 is any source of electrical power, for example a specific generator dedicated to this purpose or a generator fulfilling another function in the turbomachine (the supply of one or more other electrical elements of the turbomachine or of the aircraft).

[0069] Alternatively, the Peltier module 33 can advantageously be electrically powered by a Seebeck effect thermo-electricity generator device 41 as shown in [Fig.2].

[0070] This Seebeck effect thermo-electricity generator device 41 comprises at least one Seebeck module 42 which has a structure identical to the Peltier module 33 described previously, i.e. it also comprises two ceramic plates 34 between which are arranged semiconductor elements 35 connected to each other by a conductor 36. However, it operates in the opposite direction.

[0071] Indeed, such a Seebeck module 42 generates electricity in the conductor 36 when a temperature differential exists between its two plates 34. This electricity is sent via the electrical wires 39 to the Peltier module(s) 33 of the Peltier effect exchanger 31 which are then electrically powered.

[0072] Since the efficiency of a Seebeck module 42 is relatively low, the Seebeck effect thermogenerator device 41 preferentially includes several of them to produce more electricity.

[0073] Similarly, the Peltier effect exchanger 31 preferably comprises several Peltier modules 33 in order to increase the total cooling surface, which corresponds to the surface of all the cold plates 37 of the Peltier modules 33.

[0074] These Peltier 33 or Seebeck 42 modules can be electrically connected in series, but are preferably in parallel in order to avoid a possible failure of one of them.

[0075] The heat exchange chamber 32 of the Peltier effect exchanger 31 is in fluidic connection with and is integrated into the pressurized air circuit 24 of which it constitutes an element located between the inlet 26 and the outlet 27.

[0076] Depending on the variants, this heat exchange chamber 32 can have different shapes, several examples of which are illustrated in figures 5 to 10.

[0077] It may be a serpentine tube 43 as in figures 1, 2 and 5 to 7, that is to say a tube having several successive bent portions in alternating directions, or a spiral tube.

[0078] Alternatively, as in Figures 8 to 10, it may be a hollow body 44 that is substantially flat or has a low height compared to its other dimensions, and is, for example, parallelepiped-shaped. The example shown has, inside the hollow body 44, internal walls 45, arranged in a staggered, quincunx pattern, which create in its internal volume a longer path that the pressurized airflow 25 is forced to take when it passes through the heat exchange chamber 32.

[0079] In order to cool the pressurized airflow 25 circulating inside, the heat exchange chamber 32 is positioned against the successive cold plate(s) 37 of the Peltier module(s) 33.

[0080] To improve this cooling, the cold plate(s) 37 can directly form one of the walls 46 of the heat exchange chamber 32, the support wall 47 of the heat exchange chamber 32 against the cold plate 37 being omitted. Thus, the pressurized airflow 25 is in direct contact with the cold plate 37 without the interposition of an intermediate support wall 47. Two examples of this embodiment are shown, with a coiled heat exchange chamber 32 43 in [Fig. 7] or a flat hollow body 44 in [Fig. 10].

[0081] Figure 3 shows a preferred location for the Peltier heat exchanger 31 in the case of a twin-spool, twin-flow turbomachine 1. The heat exchanger 31 is located downstream of the fan 5, in the inter-flow compartment 48 situated between the primary air stream 49 and the secondary air stream 50.

[0082] The hot plate 38 of the Peltier module(s) 33 is advantageously placed against the wall 51 of the housing separating the inter-vein compartment 48 from the secondary vein 50, so that its heat is dissipated by the cold air circulating in the secondary vein 50. Alternatively, the hot plate 38 could not be in contact with the wall 51 but simply placed in the inter-vein compartment 48 which is generally ventilated.

[0083] The inlet 26 of the air circuit 24 is connected to the primary air stream 49, at the level of the compressor assembly 52, and preferably between the low pressure compressor 53 and the high pressure compressor 54, in order to have a significant inlet pressure for the air taken from it.

[0084] In order to limit the lengths of the pipes of the pressurized air circuit 24, the Peltier effect exchanger 31 is preferably arranged axially between the high pressure compressor 54 and the hollow annular volume 21 where it opens through its outlet 27.

[0085] As shown in [Fig.4], in the case where the Peltier effect exchanger 31 is powered by a Seebeck effect thermo-electricity generator 41, the latter is preferably also housed in the inter-vein compartment 48, but is axially offset downstream, for example between the high-pressure 55 and low-pressure 56 turbines. One of the plates 4 of the Seebeck module(s) 42 can then be placed against the wall 51 to benefit from a suitable temperature differential with the second plate 34 which is located at this level in the inter-vein compartment 48.

[0086] If the Seebeck effect thermo-electricity generator device 41 comprises several Seebeck modules 42, these can advantageously be distributed circumferentially against the wall 51, thus forming an annular ring with axis X.

[0087] As schematically represented in Figures 1 and 2, after being cooled, the pressurized airflow 25 is injected into the hollow annular volume 21 with sufficient pressure to propagate along the outer wall 17 and the portion of wall 20 from the upstream bearing enclosure 19, and reach the support 8 and the feet 7 of the blades against which it flows continuously causing their cooling.

[0088] As shown in [Fig.2], this cooling is improved by the presence of gaps 57 between the support 8 and the blade feet 7, open towards the hollow annular volume 21, into which part of the airflow 25 can rush to cool in depth said support 8 and the feet 7 it contains.

[0089] Advantageously, another part of the pressurized airflow 25 enters the upstream bearing enclosure 19 through its labyrinth seal 18, allowing the enclosure to be pressurized.

Claims

Demands

1. Cooling assembly (2) for a fan blade support (8) (7) of an aircraft turbomachine (1) fan (5), comprising: - a fan blade support (8) in which at least one fan blade support (7) (4) is mounted, - a front bearing enclosure wall (20) (19) located opposite said support (8), and - a hollow annular volume (21) located between said support (8) and said front bearing enclosure wall (20) (19), - cooling assembly (2) characterized in that it further comprises: - a pressurized air circuit (24), in which a pressurized airflow (25) circulates, extending from an inlet (26) intended to be connected to an air stream (30) of a compressor assembly (52) of the turbomachine and through which between the pressurized airflow (25), and an outlet (27) opening into said hollow annular volume (21) and through which the pressurized airflow (25) exits,and - a Peltier effect heat exchanger (31), comprising: • at least one electrically powered Peltier module (33) comprising a cold plate (37) and a hot plate (38), and • a heat exchange chamber (32), positioned against the cold plate (37) of the Peltier module, which forms part of the pressurized air circuit (24) and is traversed by the pressurized air flow (25).

2. Cooling assembly (2) according to claim 1 characterized in that, in the heat exchange chamber (32), the pressurized airflow (25) is in direct contact with the cold plate (37).

3. Cooling assembly (2) according to any one of the preceding claims characterized in that the heat exchange chamber (32) contains internal walls (45), fins or baffles which increase the exchange surface in the heat exchange chamber (32).

4. Cooling assembly (2) according to claim 1 or 2 characterized in that the heat exchange chamber (32) is a portion of a serpentine bent tube (43).

5. Cooling assembly (2) according to any one of the preceding claims characterized in that it further comprises a Seebeck effect thermo-electricity generating device (41), comprising at least one Seebeck module (42), which electrically supplies the Peltier module(s) (33) of the Peltier effect exchanger (31).

6. Turbomachine (1) comprising a cooling assembly (2) according to any one of the preceding claims.

7. Turbomachine (1) according to claim 6 which is a twin-body turbomachine whose compressor assembly (52) comprises a low pressure compressor (53) and a high pressure compressor (54), characterized in that the inlet (26) of the pressurized air circuit (24) is connected to the air stream (30, 49) between the low pressure compressor (53) and the high pressure compressor (54).

8. Turbomachine (1) according to claim 6 or 7, which is a double-flow turbomachine comprising an inter-flow compartment (48) located between a primary air flow (49) which passes through the compressor assembly (52) and a secondary air flow (50), characterized in that the Peltier effect exchanger (31) is disposed in the inter-flow compartment (48), with the hot plate (38) of the Peltier module(s) (33) placed against a wall (51) separating the inter-flow compartment (48) from the secondary air flow (50).

9. Turbomachine (1) according to any one of claims 6 to 8 when dependent on claim 5, which is a dual-flow turbomachine comprising an inter-flow compartment (48) located between a primary air flow (49) which passes through the compressor assembly (52) and a secondary air flow (50), characterized in that the Seebeck effect thermo-electricity generator device (41) is disposed in the inter-flow compartment (48), with a plate (34) of the Seebeck module(s) (42) placed against a wall (51) separating the inter-flow compartment (48) from the secondary air flow (50).

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