Improved fastening device for turbomachine turbine distributor

Abstract

Improved fastening device for a turbomachine turbine distributor Fastening device (10) for a turbomachine turbine distributor (20) centered on a central axis (X) and comprising at least one fixed blade (22) extending between a radially inner (24) and outer (26) platform, and comprising a root (28) extending radially inward from the radially inner (24) platform, the fastening device (10) comprising an annular flange (30) adapted to be fixed to the root (28) of the distributor (20) and comprising an upstream (31) and downstream (32) flange forming a clamp capable of clamping the root (28), a first sealing means (41) capable of being arranged and clamped between the upstream flange (31) and the root (28), and a second sealing means (42) capable of being arranged and clamped between the downstream flange (32) and the root (28),the first sealing means (41) and the second sealing means (42) each being a single-piece ring which extends without interruption around the central axis (X). Figure for abstract: Fig. 3.,

Description

Title of the invention: Improved fixing device for a turbomachine turbine distributor Technical field

[0001] The present disclosure relates to the fixing of distributors within aircraft turbomachine turbines, in particular low-pressure turbines. In particular, the present disclosure relates to a fixing device for a turbomachine turbine distributor, and a low-pressure turbine comprising such a device. Prior art

[0002] An aircraft turbomachine turbine, in particular a low-pressure turbine, comprises a plurality of rotor and stator stages arranged axially one behind the other in alternation. The stator stages each comprise in particular an annular distributor comprising fixed blades, extending around a central axis of rotation of the turbomachine, and each being typically formed from an assembly of distributor sectors arranged together end to end circumferentially around the central axis.

[0003] In a manner known per se, each distributor, and in particular the first stage of the low-pressure turbine distributors, is fixed at its radially external end to a fixed external casing of the turbine, and at its radially internal end to an annular flange, said flange making it possible to make the junction between the distributor and a fixed part of the turbine, for example an inter-turbine casing arranged between the low-pressure turbine and the high-pressure turbine.

[0004] In operation, the hot air flowing in the engine, in particular the hot air flow veins of the high and low pressure turbines, subjects the parts in contact with this hot air, typically the distributors, to significant stresses, and in particular causes expansions of these parts. It is therefore necessary to provide parts which resist these stresses and which allow these expansions to occur. In particular, the distributor blades, in direct contact with the hot air, are likely to expand more than the internal parts of the turbine which are not in direct contact with the hot air, in particular the annular flange.

[0005] To allow differential expansions between the distributor and the annular flange to which it is fixed, it is known to use an arrangement in which the flange comprises an upstream flange and a downstream flange which pinch a foot of the distributor between them, so as to axially block the latter, while allowing relative radial movement of the distributor due to its expansions.

[0006] Furthermore, in order to obtain a sealed contact zone between the flanges of the plate and the distributor, an assembly of sealing sheets is generally arranged between the flanges and the foot of the distributor. These sealing sheets are typically formed from a plurality of sectors of sheets assembled together so as to form a crown, the sheets being furthermore stacked on top of each other so as to ensure sealing. Typically, at least two layers of sealing sheets are stacked on top of each other between the flanges of the end plate and the distributor, in order to ensure sealing.

[0007] However, such an arrangement, meeting the need to have an assembly allowing the relative expansions and movements of the parts between them, associated with a need for sealing between these parts, is complex to assemble and comprises numerous parts, which also increases the cost and mass of the turbine.

[0008] There is therefore a need for a solution to simplify this fixing system, thereby reducing the assembly time, cost and mass of the turbine. Presentation of the invention

[0009] The present disclosure relates to a fixing device for a turbomachine turbine distributor, the distributor being centered on a central axis and comprising at least one fixed blade extending between a radially inner platform and a radially outer platform, and further comprising a root extending radially inward from the radially inner platform, the fixing device comprising: - an annular flange adapted to be fixed to the foot of the distributor and comprising an upstream flange and a downstream flange arranged to form a clamp capable of gripping the foot of the distributor, - a first sealing means capable of being arranged and clamped between the upstream flange and the foot of the distributor, and a second metallic annular seal capable of being arranged and clamped between the downstream flange and the foot of the distributor, the first sealing means and the second annular seal each being a single-piece annular part capable of extending without interruption around the central axis.

[0010] In the present disclosure, the terms "axial", "radial", "circumferential", "inner", "outer" and their derivatives are defined with respect to the main central axis of the turbomachine. Furthermore, the terms "upstream" and "downstream" are defined with respect to the circulation of air in the turbomachine.

[0011] The annular flange is typically a flared annular-shaped part, with a curved plate between a radially inner upstream end and a radially outer downstream end, making it possible to mechanically connect a fixed part of the turbine to the distributor. The fixed part may typically be an inter-turbine casing.

[0012] It is further understood that the upstream flange and the downstream flange of the flange are respec tively arranged axially on either side of the distributor foot. Thus, when the upstream flange and the downstream flange are clamped together while being brought closer to each other, they axially clamp the distributor foot arranged between them. The upstream flange and the downstream flange thus form a clamp axially locking the distributor foot, while allowing radial movements of the foot due to expansion.

[0013] The first sealing means, typically metallic, and the second sealing means, typically metallic, make it possible to improve the contact seal between the upstream and downstream flanges and the foot of the distributor. Unlike the stack of sectorized metal sheets according to the prior art, the first and second metallic annular seals are single pieces, that is to say formed in a single piece so as to extend around the central axis without interruption, in a continuous manner.

[0014] It is thus possible to reduce the number of parts for holding the distributor in position, while maintaining effective sealing. This simplifies the mounting and assembly of the fixing device on the distributor, which consequently reduces the assembly time, the mass and the costs incurred, in particular when replacing parts.

[0015] In some embodiments, the first sealing means is a single metal seal disposed between the upstream flange and the foot, and the second sealing means is a single metal seal disposed between the downstream flange and the foot.

[0016] The number of parts providing sealing between the upstream and downstream flanges of the flange and the distributor is minimized, which makes it possible to simplify the assembly between the flange and the distributor as much as possible, and to limit costs and mass as much as possible.

[0017] In some embodiments, the first sealing means and the second sealing means are O-rings.

[0018] Typically, the sealing means may have a circular section. It is understood that the first sealing means and the second metal sealing means are similar to O-ring seals made of plastic material used for sealing in the context of liquid flows. The metal sealing means thus used have the advantage of being simple, light and easy to assemble on the fixing device.

[0019] In some embodiments, the first sealing means and the second sealing means have a rectangular section.

[0020] The rectangular section allows for flat-shaped sealing means, which limits tightening and improves the strength of the joints.

[0021] In some embodiments, the first sealing means and the second sealing means are capable of being arranged in an annular groove formed in the upstream flange and the downstream flange respectively and / or in the base of the distributor.

[0022] Arranging the sealing means in an annular groove, typically of a shape complementary to the shape of the seals, makes it possible to limit the radial movements of the sealing means relative to the upstream and downstream flanges and / or relative to the base of the distributor, while allowing relative radial movements of the base of the distributor relative to the upstream and downstream flanges. The presence of the annular grooves also makes it possible to simplify the mounting of the fixing device. Furthermore, forming the annular grooves in the base of the distributor makes it possible to further facilitate the mounting of the fixing device.

[0023] In certain embodiments, the upstream flange comprises, at a radially outer end, a first clamping end which projects downstream of the upstream flange and towards an upstream face of the foot, and the downstream flange comprises, at a radially outer end, a second clamping end which projects upstream of the downstream flange and towards a downstream face of the foot, the first sealing means being able to be arranged and clamped between the first clamping end and the upstream face of the foot, and the second sealing means being able to be arranged and clamped between the second clamping end and the downstream face of the foot.

[0024] It is understood that the upstream flange and the downstream flange are capable of exerting a clamping force on the foot of the distributor via the sealing means, only over an area limited to the radially outer end, via the first clamping end and the second clamping end, in the manner of a clothes peg whose two sides come into contact with each other only at one end of the clothes peg. Typically, the first clamping end and the second clamping end represent less than 10% of the total surface area of ​​the upstream flange and the downstream flange respectively. Arranging the first sealing means between the first clamping end and the upstream face of the foot, and the second sealing means between the second clamping end and the downstream face of the foot, makes it possible to simplify the assembly, while improving the contact seal between the flanges and the distributor.

[0025] In some embodiments, the entirety of the first sealing means is disposed between the first clamping end and the upstream face of the foot, and the entirety of the second sealing means is disposed between the second clamping end and the downstream face of the foot.

[0026] It is understood that the entire volume of the first sealing means is arranged between the first clamping end and the upstream face of the foot, preferably being housed in a first annular groove, and the entire volume of the second sealing means is arranged between the second clamping end and the downstream face of the foot, preferably by being housed in a second annular groove. This makes it possible to improve the arrangement of the fixing device and the assembly between said device and the distributor, and therefore to further simplify the assembly of the assembly.

[0027] In certain embodiments, the first sealing means is able to be arranged in a first annular groove formed in the first clamping end of the upstream flange and / or in the upstream face of the foot, and the second sealing means is able to be arranged in a second annular groove formed in the second clamping end of the downstream flange and / or in the downstream face of the foot.

[0028] In certain embodiments, the first sealing means and the second sealing means are capable of being mounted so as to be under stress respectively between the upstream flange and the foot, and between the downstream flange and the foot.

[0029] It is understood that the first sealing means and the second sealing means are dimensioned so as to be under stress between the upstream flange and the foot, and between the downstream flange and the foot, even when cold when the engine is not in operation. In other words, the sealing means are under permanent stress between the flanges of the annular flange and the distributor. This makes it possible to improve the contact seal permanently between the flange and the distributor. Furthermore, since the sealing means are metallic, when the temperature increases during the operating phases, the expansion of the sealing means increases the stresses to which they are subjected, which further increases the seal.

[0030] In certain embodiments, the annular flange comprises a first end capable of being fixed to a turbine casing, a second end capable of being fixed to the foot of the distributor, and a central portion connecting the first and second ends, the upstream flange being formed in continuity with the central portion in a single-piece manner therewith, and the downstream flange being a separate part attached to the upstream flange while being fixed thereto.

[0031] The present disclosure relates to a low pressure turbine of a turbomachine, comprising a distributor and a fixing device according to any one of the preceding embodiments, in which the distributor is a first stage of the low pressure turbine. Brief description of the drawings

[0032] The invention and its advantages will be better understood upon reading the detailed description given below of different embodiments of the invention given as non-limiting examples. This description refers to the appended pages of figures, in which:

[0033] [Fig.l] [Fig.l] represents a schematic view in longitudinal section of a tur- bomachine;

[0034] [Fig.2] [Fig.2] represents a perspective, partial and exploded view of a assembly comprising a dispenser and a fixing device according to the invention;

[0035] [Fig.3] [Fig.3] represents an axial sectional view of a fixing device according to the invention attached to a dispenser;

[0036] [Fig.4] [Fig.4] shows a detailed view of the attachment between the device of fixing and the distributor of [Fig.3]. Description of the embodiments

[0037] In the remainder of the description, the terms “upstream” and “downstream” are subsequently defined in relation to the direction of flow of the gases through a turbomachine, indicated by the arrow F in [Fig. 1], representing the flow of the hot gases in the combustion chamber 4. Furthermore, the terms “internal” and “external” are considered in a radial direction perpendicular to the central axis X.

[0038] [Fig.l] illustrates a double-flow turbomachine 100 comprising in a known manner from upstream to downstream successively at least one fan S, a gas turbine engine part 1 successively comprising at least one low-pressure compressor stage 2, high-pressure compressor stage 3, a combustion chamber 4, at least one high-pressure turbine stage 5 and low-pressure turbine stage 6. The rotors of the compressors 2, 3, of the turbines 5, 6 and of the fan S rotate around the central axis X of the turbomachine 100, and can be coupled together by different transmission and gear systems.

[0039] In the remainder of the description, reference is made to the low-pressure turbine 6. It will be noted, however, that the invention can be applied to both the low-pressure turbine 6 and the high-pressure turbine 5. This low-pressure turbine 6 comprises a plurality of rotor stages and stator stages succeeding one another from upstream to downstream. For the purposes of simplification, only one stator stage, in particular the first stage of the low-pressure turbine 6, is shown in the remainder of the description.

[0040] In particular, a fixing device 10, described in the remainder of the description with reference to FIGS. 2 to 4, is typically arranged at the distributor 20 of the first stage of the low-pressure turbine 6. The fixing device 10 is for example arranged at the inlet of the low-pressure turbine 6, at the connection between the fixed part of the turbomachine and the low-pressure turbine 6, for example at the connection between the inter-turbine casing 7 and the low-pressure turbine 6.

[0041] In particular, the fixing device 10 comprises an annular flange 30 described later, making it possible to make the junction between the inter-turbine casing 7 and the distributor 20 of the first stage of the low-pressure turbine 6.

[0042] The distributor 20 typically comprises a plurality of sectors assembled circum- relative to each other around the central axis X, so as to form the annular distributor 20 centered on the central axis X. The distributor 20 comprises a plurality of fixed blades 22 each extending between an internal platform 24 and an external platform 26. Furthermore, a foot 28 of the distributor 20 extends radially inward from the internal platform 24. In this example, the foot 28 extends from a central region, along the central axis X, of the internal platform 24. The external platform 26 is secured to a fixed casing 70 external to the low-pressure turbine 6, and the internal platform 24 is secured to the annular flange 30 via the foot 28, the annular flange 30 thus forming the junction between the distributor 20 and a fixed part of the turbine 6, for example the inter-turbine casing 7.

[0043] More precisely, the annular flange 30 comprises a first end 30a, or inner end, fixed to the inter-turbine casing 7 (the fixing means not being shown in [Fig.2]), and a second end 30b, or outer end, fixed to the foot 28 of the distributor 20. The first end 30a and the second end 30b are connected to each other by a central portion 30c, which is a plate curved from the first end 30a downstream and outward to the second end 30b. The central portion 30c is typically annular and axisymmetrical around the central axis X, and ensures the mechanical strength of the flange 30.

[0044] At its second end 30b, the flange 30 comprises an upstream flange 31 and a downstream flange 32, arranged so as to be disposed axially on either side of the foot 28 of the distributor 20. In this example, the upstream flange 31 is formed in continuity with the central portion 30c, in a single piece with the latter, and the downstream flange 32 is a separate part attached to the upstream flange 31 while being fixed to the latter. To do this, the upstream flange 31 comprises a plurality of upstream orifices 311 distributed circumferentially around the central axis X, and the downstream flange 32 comprises a plurality of downstream orifices 321 also distributed circumferentially around the central axis X. Fixing means 50, typically comprising screws 51 inserted through the orifices 311, 321, and nuts 52, allowing the upstream and downstream flanges 31, 32 to be fixed to each other, by tightening them against each other.

[0045] It will be noted that in this example, the fixing device 10 may also comprise a rear flange, or downstream covering sheet 60, making it possible to limit a flow of hot air coming from the hot air flow duct towards an internal cavity of the turbine 6. In this case, the fixing means 50 are also inserted into orifices 62 of the downstream covering sheet 60 so as to fix the latter to the downstream flange 32.

[0046] Furthermore, the upstream and downstream flanges 31, 32 are arranged in such a way that only one radially external end exerts pressure on the foot 28 of the distributor 20, by means of the sealing means described below, the rest of the flanges 31, 32 being separated from the foot 28 by a space forming a space for receiving the foot 28 of the distributor 20. More precisely, the upstream flange 31 comprises, at its radially external end, a first clamping end 312 capable of exerting a force against an upstream face 281 of the foot 28, and the downstream flange 32 comprises, at its radially external end, a second clamping end 322 capable of exerting a force against a downstream face 282 of the foot 28.

[0047] Given this arrangement, the tightening of the upstream 31 and downstream 32 flanges against each other by the fixing means 50 respectively causes the first tightening end 312 to be tightened against the upstream face 281 of the foot 28, and the second tightening end 322 to be tightened against the downstream face 282 of the foot 28. The upstream 31 and downstream 32 flanges thus act as a clamp tightening the foot 28 of the distributor 20.

[0048] Unlike the fixing devices according to the state of the art, comprising several layers of sectored sheets stacked on top of each other to allow sealed contact between the upstream 31 and downstream 32 flanges, and the foot 28, the fixing device 10 according to the invention has a simplified structure.

[0049] In particular, the fixing device 10 according to the invention comprises a first metallic and annular-shaped sealing means 41, capable of being arranged and clamped between the upstream flange 31 and the foot 28 of the distributor 20, and a second metallic and annular-shaped sealing means 42, capable of being arranged and clamped between the downstream flange 32 and the foot 28 of the distributor 20. The first and annular-shaped 41 and the second and annular-shaped 42 are each a single-piece annular part extending without interruption around the central axis X. In other words, the sealing means 41, 42 have the shape of a ring, or metallic O-ring, preferably of circular section. This shape is however not limiting, the sealing means 41, 42 being able to have a flat or rectangular section. The sealing means 41, 42 are made of metal, comprising for example steel and nickel.

[0050] Thus, preferably, the fixing device 10 comprises a single metal seal, namely the first sealing means 41, between the upstream flange 31 and the foot 28, and a single metal seal, namely the second sealing means 42, between the downstream flange 32 and the foot 28.

[0051] Typically, the first clamping end 312, intended to exert pressure on the upstream face 281 of the foot 28 via the first sealing means 41, comprises a first annular groove 314 extending circumferentially around the central axis X over the entire circumference of said first clamping end 312. The first annular groove 314 has a concave shape adapted to receive the first sealing means 4L. Thus, when the first sealing means 41 is housed in the first annular groove 314, a portion of the first sealing means 41 projects downstream beyond the first clamping end 312. Consequently, when the upstream flange 31 is clamped against the upstream face 281 of the foot 28, the first sealing means 41 is itself clamped against said upstream face 281, being compressed between the bottom of the first annular groove 314 and the upstream face 281.

[0052] It will be noted in this respect that given the presence of the first sealing means 41, the first clamping end 312 is not directly in contact with the upstream face 281, a small clearance (not visible in [Fig.4]), for example of approximately 1 mm, exists between these two surfaces, the first sealing means 41 thus being compressed between the first clamping end 312 and the upstream face 281.

[0053] In the same way, the second clamping end 322, intended to exert pressure on the downstream face 282 of the foot 28 via the second sealing means 42, comprises a second annular groove 324 extending circumferentially around the central axis X over the entire circumference of said second clamping end 322. The second annular groove 324 has a concave shape adapted to receive the second sealing means 42. Thus, when the second sealing means 42 is housed in the second annular groove 324, a portion of the second sealing means 42 projects upstream beyond the second clamping end 322. Consequently, when the downstream flange 32 is clamped against the downstream face 282 of the foot 28, the second sealing means 42 is itself clamped against said downstream face 282, being compressed between the bottom of the second annular groove 324 and the downstream face 282.

[0054] Similarly, given the presence of the second sealing means 42, the second clamping end 322 is not directly in contact with the upstream face 281, a small clearance (not visible in [Fig.4]), for example of approximately 1 mm, exists between these two surfaces, the second sealing means 42 thus being compressed between the second clamping end 322 and the upstream face 281.

[0055] Thus, the entirety of the first sealing means 41 is arranged between the first clamping end 312 and the upstream face 281 of the foot 28, and the entirety of the second sealing means 42 is arranged between the second clamping end 322 and the downstream face 282 of the foot 28. In other words, in a sectional view along a section plane parallel to the central axis X (Figures 3 and 4), the first sealing means 41 extends radially over a distance less than the radial distance over which the first clamping end 312 extends, and the second sealing means 42 extends radially over a distance less than the radial distance over which the second clamping end 322 extends. Thus, the volume, and consequently the mass, of each of the first sealing means 41 and the second sealing means 42 are at least five times lower, preferably at least ten times lower than those of metal sheets according to the prior art.

[0056] Preferably, the first sealing means 41 and the second sealing means 42 are dimensioned and mounted in the grooves 314, 324 so as to be prestressed between the upstream and downstream flanges 31, 32 and the foot 28. In other words, during cold assembly, i.e. with the engine stopped, of the device and the turbine, a clamping pressure is exerted on the first sealing means 41, which is compressed between the upstream flange 31, in particular the first clamping end 312, and the upstream face 281 of the foot 28, and on the second sealing means 42, which is compressed between the downstream flange 32, in particular the second clamping end 322, and the downstream face 282 of the foot 28.

[0057] Sealing can thus be ensured when cold. Furthermore, the engine in operation causes an increase in the internal temperature of the turbine, and therefore an expansion of the sealing means 41, 42. This expansion causes an increase in the stress exerted on the sealing means 41, 42 caught in a vice between the flanges 31, 32 and the foot 28, further reinforcing the contact seal.

[0058] Furthermore, when the engine is in operation, the increase in temperature also causes the distributor 20 to expand, and consequently a relative movement of the foot 28 of the distributor 20 with respect to the upstream 31 and downstream 32 flanges. The sealing means 41, 42 remain held in the grooves 314, 324, but the frictional contact between the sealing means 41, 42 and the upstream 281 and downstream 282 faces of the foot 28 allows radial sliding of the sealing means 41, 42 along said upstream 281 and downstream 282 faces of the foot 28.

[0059] It will also be noted that, although in this example, the annular grooves 314, 324 are formed on the upstream 31 and downstream 32 flanges, in particular on the clamping ends 312, 322, the annular grooves 314, 324 could also be formed respectively on the upstream 281 and downstream 282 faces of the foot 28, or both on the clamping ends 312, 322 and on the upstream 281 and downstream 282 faces, without departing from the scope of the invention.

[0060] Although the present invention has been described with reference to specific exemplary embodiments, it is obvious that modifications and changes may be made to these examples without departing from the general scope of the invention as defined by the claims. In particular, individual features of the various illustrated / mentioned embodiments may be combined in additional embodiments. Therefore, the description and drawings should be considered in an illustrative rather than restrictive sense.

Claims

Claims

1. A fastening device (10) for a turbine distributor (20) of a turbomachine, the distributor (20) being centered on a central axis (X) and comprising at least one fixed blade (22) extending between a radially inner platform (24) and a radially outer platform (26), and further comprising a foot (28) extending radially inward from the radially inner platform (24), the fastening device (10) comprising: - an annular flange (30) adapted to be fixed to the foot (28) of the distributor (20) and comprising an upstream flange (31) and a downstream flange (32) arranged to form a clamp capable of clamping the foot (28) of the distributor (20), - a first sealing means (41) capable of being arranged and clamped between the upstream flange (31) and the foot (28) of the distributor, and a second sealing means (42) capable of being arranged and clamped between the downstream flange (32) and the foot (28) of the distributor,the first sealing means (41) and the second sealing means (42) each being a single-piece ring which extends without interruption around the central axis (X).,

2. A fixing device (10) according to claim 1, wherein the first sealing means (41) is a single metal seal disposed between the upstream flange (31) and the foot (28), and the second sealing means (42) is a single metal seal disposed between the downstream flange (32) and the foot (28).

3. A fastening device (10) according to claim 1 or 2, wherein the first sealing means (41) and the second sealing means (42) are O-rings.

4. A fixing device (10) according to claim 1 or 2, wherein the first sealing means (41) and the second sealing means (42) have a rectangular section.

5. Fixing device (10) according to any one of claims 1 to 4, wherein the first sealing means (41) and the second sealing means (42) are capable of being arranged in an annular groove (314, 324) formed in the upstream flange (31) and the downstream flange (32) respectively and / or in the foot (28) of the distributor (20).

6. A fastening device (10) according to any one of claims 1 to 5, wherein the upstream flange (31) comprises, at a radially outer end, a first clamping end (312) which extends projecting downstream from the upstream flange (31) and towards an upstream face (281) of the foot (28), and the downstream flange (32) comprises, at a radially external end, a second clamping end (322) which extends projecting upstream from the downstream flange (32) and towards a downstream face (282) of the foot (28), the first sealing means (41) being able to be arranged and clamped between the first clamping end (312) and the upstream face (281) of the foot (28), and the second sealing means (42) being able to be arranged and clamped between the second clamping end (322) and the downstream face (282) of the foot (28).

7. A fastening device (10) according to claim 6, wherein the entire first sealing means (41) is disposed between the first clamping end (312) and the upstream face (281) of the foot (28), and the entire second sealing means (42) is disposed between the second clamping end (322) and the downstream face (282) of the foot (28).

8. Fastening device (10) according to claim 6 or 7, wherein the first sealing means (41) is adapted to be arranged in a first annular groove (314) formed in the first clamping end (312) of the upstream flange (31) and / or in the upstream face (281) of the foot (28), and the second sealing means (42) is adapted to be arranged in a second annular groove (324) formed in the second clamping end (322) of the downstream flange (32) and / or in the downstream face (282) of the foot (28).

9. A fixing device (10) according to any one of claims 1 to 8, wherein the first sealing means (41) and the second sealing means (42) are capable of being mounted so as to be under stress respectively between the upstream flange (31) and the foot (28), and between the downstream flange (32) and the foot (28).

10. Fixing device (10) according to any one of claims 1 to 9, in which the annular flange (30) comprises a first end (30a) capable of being fixed to a turbine casing, a second end (30b) capable of being fixed to the foot (28) of the distributor (20), and a central portion (30c) connecting the first and second ends (30a, 30b), the upstream flange (31) being formed in continuity with the central portion (30c) in a single piece therewith, and the downstream flange (32) being a separate part attached to the upstream flange (31) while being fixed thereto.

11. Low pressure turbine (6) of a turbomachine, comprising a distributor (20) and a fixing device (10) according to any one of the claims- preceding indications, in which the distributor (20) is a first stage of the low pressure turbine (6).

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