FR3096733A1 - Turbomachine assembly - Google Patents

Abstract

The present invention relates to an assembly for a turbomachine comprising: - a first rotor comprising: ○ a disc (120), and ○ a plurality of blades (122) capable of flapping relative to the disc (120), - a second rotor (140 ), and- a damper (2) configured to damp a movement of the first rotor relative to the second rotor (140), in a plane orthogonal to the longitudinal axis, the damper (2) comprising: ○ a first part of support (21) bearing on the first rotor in a first bearing zone extending over a first angular sector around the longitudinal axis, ○ a second bearing portion (22) bearing on the first rotor in a second bearing zone, different from the first bearing zone, the second bearing zone extending over a second angular sector around the longitudinal axis, the second angular sector being smaller than the first angular sector. Figure for the abstract: Fig. 3

Description

Turbomachine Kit

The present invention relates to an assembly for a turbomachine.

The invention relates more specifically to an assembly for a turbomachine comprising a shock absorber.

A turbomachine known from the state of the art comprises a casing and a fan capable of being rotated relative to the casing, around a longitudinal axis, thanks to a fan shaft.

The fan comprises a disc centered on the longitudinal axis, and a plurality of vanes distributed circumferentially at the level of the external part of the disc.

The operating range of the blower is limited. More precisely, the evolution of a compression ratio of the fan as a function of an airflow that it sucks in when it is put into rotation, is restricted to a predetermined domain.

Beyond this range, the fan is in fact subject to aeroelastic phenomena which destabilize it. More precisely, the air circulating through the fan in operation brings energy to the blades, and the blades respond on their own modes at levels that can exceed the endurance limit of the material that constitutes them. This fluid-structure coupling therefore generates vibratory instabilities which accelerate the wear of the fan, and reduce its lifespan.

A fan with a reduced number of blades, and which is subjected to high aerodynamic loads, is very sensitive to this type of phenomenon.

This is the reason why it is necessary to guarantee a sufficient margin between the stable operating range and the areas of instability, so as to accommodate the endurance limits of the fan.

To do this, it is known to provide the fan with dampers. Examples of shock absorbers have been described in documents FR 2 949 142, EP 1 985 810 and FR 2 923 557, in the name of the Applicant. These dampers are all configured to be housed between the platform and the root of each blade, within the housing delimited by the respective stilts of two successive blades. Furthermore, such dampers operate during relative movement between two successive blade platforms, by dissipation of vibration energy, for example by friction. Consequently, these dampers only aim to damp a first vibratory mode of the blades which characterizes a synchronous response of the blades to aerodynamic stresses. In this first vibratory mode, the inter-blade phase shift is non-zero.

However, such dampers are totally ineffective for damping a second vibratory mode in which each blade beats relative to the disc with zero inter-blade phase shift. Indeed, in this second vibratory mode, there is no relative displacement between two successive blade platforms. This particular response of the blades to aerodynamic stresses, although asynchronous, nevertheless implies a non-zero moment on the fan shaft. In addition, this second vibratory mode is coupled between the blades, the disc, and the fan shaft. The amplitude of this second vibratory mode is all the greater as the blades are large.

There is therefore a need to overcome at least one of the disadvantages of the prior art described above.

An object of the invention is to damp a mode of vibration of a rotor in which the phase difference between the blades of said rotor is zero.

Another object of the invention is to influence the damping of vibration modes of a rotor in which the phase difference between the blades of said rotor is non-zero.

Another object of the invention is to propose a damping solution that is simple and easy to implement.

To this end, it is proposed, according to a first aspect of the invention, an assembly for a turbomachine comprising:
- a casing,
- a first rotor:
○ rotatable relative to the housing around a longitudinal axis, and
○ including:
* a disc, and
* a plurality of blades capable of beating relative to the disc during rotation of the first rotor relative to the housing,
- a second rotor rotatable relative to the housing around the longitudinal axis, and
- a damper configured to damp a displacement of the first rotor relative to the second rotor, in a plane orthogonal to the longitudinal axis, the displacement being caused by a beat of at least one blade among the plurality of blades, the damper including:
○ a first support part:
* bearing on the first rotor in a first bearing zone extending over a first angular sector around the longitudinal axis, and
* being configured to apply a first centrifugal force on the first rotor, and
○ a second bearing part bearing on the first rotor in a second bearing zone, different from the first bearing zone, the second bearing zone extending over a second angular sector around the axis longitudinal, the second angular sector being less than the first angular sector.

It is by damping a displacement of the first rotor relative to the second rotor, in a plane orthogonal to the longitudinal axis, that it is possible to influence the second vibration mode. In fact, unlike the first vibratory mode, the second vibratory mode is characterized by a zero inter-blade phase shift. Consequently, placing a damper between two successive blades of a rotor, as has already been proposed in the prior art, produces no effect on the second vibratory mode. The damper of the previously described assembly has, for its part, the advantage of influencing the second vibratory mode because it plays on an effect of the second vibratory mode: the displacement of the first rotor relative to the second rotor, in the plane orthogonal to the longitudinal axis. By opposing this effect, the damper disrupts the cause, i.e. dampens the second vibrational mode. It should nevertheless be noted that the first vibratory mode also participates in the displacement of the first rotor relative to the second rotor, in the plane orthogonal to the longitudinal axis. Therefore, by opposing this effect, the damper also participates in disturbing another cause, that is to say damping the first vibrational mode. In addition, the second support part improves the stability of the shock absorber.

Advantageously, but optionally, the assembly according to the invention may further comprise one of the following characteristics, taken alone or in combination with one or more of the other of the following characteristics:
- the first support part is mounted fixed on the first rotor,
- the shock absorber comprises a third support part:
○ bearing on the second rotor, and
○ being configured to apply a second centrifugal force on the second rotor,
- the shock absorber comprises a connecting part:
○ connecting the first bearing part to the third bearing part, and
○ being thinned with respect to the first support part and the third support part,
- in such a set:
○ the first bearing part has a first bearing surface arranged to apply a first force on the second rotor, the first force having a first longitudinal component in a first direction parallel to the longitudinal axis, and a first radial component in a second direction orthogonal to the longitudinal axis, the first longitudinal component being greater than the first radial component,
○ the third bearing part has a second bearing surface arranged to apply a second force on the second rotor, the second force having a second longitudinal component in the first direction, and a second radial component in the second direction, the second radial component being greater than the second longitudinal component,
- it also includes a sacrificial plate:
○ fixed mounted on the third support part, and
○ bearing on the second rotor,
- it also includes:
○ a first sacrificial pad fixedly mounted on the first bearing part and having the first bearing surface, and
○ a second sacrificial plate fixedly mounted on the third bearing part and presenting the second bearing surface,
- a slot is provided in the first support part, the assembly further comprising a metal insert inserted into the slot, the second sacrificial plate being fixedly mounted on the metal insert,
- it further comprises a flyweight mounted fixed on the shock absorber,
- the flyweight is mounted fixed on the first support part,
- it further comprises a flyweight fixedly mounted on the third support part,
- it also includes:
○ a first flyweight mounted fixed on the first support part, and
○ a second flyweight mounted fixed on the third support part
- each of the vanes among the plurality of vanes comprises:
○ a blade root connecting the blade to the disc,
○ profiled blading,
○ a stilt connecting the blading to the blade root, and
○ a platform connecting the blade to the stilt and extending transversely to the stilt, the first support part coming to rest on the platform of a blade from among the plurality of blades, and
- the second rotor comprises a shroud, the shroud comprising a circumferential extension, the third support part bearing on the circumferential extension.

According to a second aspect of the invention, a turbomachine is proposed comprising an assembly as previously described, and in which the first rotor is a fan, and the second rotor is a low-pressure compressor.

Other characteristics, objects and advantages of the invention will emerge from the description which follows, which is purely illustrative and not limiting, and which must be read in conjunction with the appended drawings in which:

Figure 1 schematically illustrates a turbomachine,

FIG. 2 comprises a sectional view of part of a turbomachine, and a curve indicating a tangential displacement of various elements of this part of the turbomachine as a function of the position of said elements along a longitudinal axis of the turbomachine,

Figure 3 is a sectional view of part of an embodiment of an assembly according to the invention,

Figure 4 is a perspective view of part of an embodiment of an assembly according to the invention,

Figure 5 is a perspective view of part of an embodiment of an assembly according to the invention,

Figure 6 is a perspective view of a damper of an embodiment of an assembly according to the invention,

Figure 7 is a perspective view of a damper of an embodiment of an assembly according to the invention,

Figure 8 is a perspective view of a damper of an embodiment of an assembly according to the invention,

Figure 9 is a perspective view of part of an embodiment of an assembly according to the invention,

Figure 10 is a perspective view of part of an embodiment of an assembly according to the invention, and

Figure 11 is a perspective view of a damper of an embodiment of an assembly according to the invention.

In all the figures, similar elements bear identical references.

Turbomachine 1

Referring to Figure 1, a turbomachine 1 comprises a casing 10, a fan 12, a low pressure compressor 140, a high pressure compressor 142, a combustion chamber 16, a high pressure turbine 180 and a low pressure turbine 182.

Each of the fan 12, the low pressure compressor 140, the high pressure compressor 142, the high pressure turbine 180, and the low pressure turbine 182, is rotatable relative to the casing 10 around a longitudinal axis X-X.

In the embodiment illustrated in Figure 1, and as also visible in Figures 2 and 3, the fan 12 and the low pressure compressor 140 are integral in rotation, and are capable of being rotated by a low pressure shaft 13 which is itself capable of being rotated by the low pressure turbine 182. The high pressure compressor 142 is, for its part, capable of being rotated by a high pressure shaft 15, which is itself capable to be rotated by the high pressure turbine 180.

In operation, the fan 12 draws in a flow of air 110 which separates between a secondary flow 112, circulating around the casing 10, and a primary flow 111, successively compressed within the low pressure compressor 140 and the high pressure compressor 142, ignited within the combustion chamber 16, then successively expanded within the high pressure turbine 180 and the low pressure turbine 182.

Upstream and downstream are defined here with respect to the direction of normal air flow 110, 111, 112 through the turbine engine 1. Similarly, an axial direction corresponds to the direction of the longitudinal axis XX, an radial direction is a direction which is perpendicular to this longitudinal axis XX and which passes through said longitudinal axis XX, and a circumferential or tangential direction corresponds to the direction of a plane and closed curved line, all the points of which lie at equal distance from the longitudinal axis XX. Finally, and unless otherwise specified, the terms “internal (or interior)” and “external (or exterior)”, respectively, are used with reference to a radial direction so that the internal (ie radially internal) part or face d an element is closer to the longitudinal axis XX than the external (ie radially external) part or face of the same element.

Blower 12 and low pressure compressor 140

Referring to Figures 1 to 3, the fan 12 comprises a disc 120 and a plurality of vanes 122 distributed circumferentially at an outer part of the disc 120.

Referring to Figures 2 and 3, each of the vanes 122 of the plurality of vanes 122 comprises:
- a blade root 1220 connecting the blade 122 to the disc 120,
- a profiled blading 1222,
- a stilt 1224 connecting the blading 1222 to the root of the blade 1220, and
- a platform 1226 connecting the blading 1222 to the stilt 1224, and extending transversely to the stilt 1224.

The blade root 1220 can be integral with the disk 120 when the fan 12 is a one-piece bladed disk. Alternatively, as shown in Figure 3, the blade root 1220 can be configured to be housed in a cell 1200 of the disc 120 provided for this purpose.

As visible in Figures 2 and 3, the low pressure compressor 140 also comprises a plurality of blades 1400 mounted fixed at an outer part of a shroud 1402, said shroud 1402 comprising a circumferential extension 1404 at the outer end from which radial sealing wipers 1406 extend. The radial sealing wipers 1406 come opposite the platforms 1226 of the blades 122 of the fan 12, so as to guarantee the internal sealing of the flow stream within which the primary flow 111 circulates. Figure 3, the shroud 1402 of the low pressure compressor 140 is fixed to the disc 120 of the fan 12, for example by bolting.

Each of the blades 122 of the plurality of blades 122 of the fan 12 is capable of beating, by vibrating with respect to the disc 120 during a rotation of the fan 12 with respect to the casing 10. More precisely, during the coupling between the air 110 circulating within the fan 12 and the profiled blades 1222, the blades 122 are the seat of aeroelastic phenomena of flutter on different vibratory modes, and whose amplitude can be such that it exceeds the endurance limits of the materials constituting the fan 12. These vibratory modes are furthermore coupled to the opposing forces of compression upstream of the turbine engine 1, and of expansion downstream of the latter.

A first vibratory mode characterizes a synchronous response of the blades 122 to aerodynamic stresses, in which the inter-blade phase shift is non-zero.

A second vibratory mode characterizes an asynchronous response of the blades 122 to aerodynamic stresses, in which the inter-blade phase shift is zero. The amplitude of the beats of the second vibratory mode is also greater than the blades 122 of fan 12 are large. Furthermore, this second vibratory mode is coupled between the blades 122, the disc 120, and the fan shaft 13. The frequency of the second vibratory mode is, moreover, one and a half times higher than that of the first vibratory mode. Finally, the second vibratory mode has a nodal deformation at mid-height of the blades 122 of the fan 12.

In vibrational modes, including the second vibrational mode, the beating of the blades 122 implies a non-zero moment on the low pressure shaft 13. In particular, these vibrational modes lead to intense torsional forces within the low pressure shaft 13.

The vibrations induced by the beating of the blades 122 of the fan 12, but also by the beating of the blades 1400 of the low pressure compressor 140, lead to significant relative tangential displacements between the fan 12 and the low pressure compressor 140. Indeed, the length of the blades 122 of the fan 12 is greater than the length of the blades 1400 of the low pressure compressor 140. Consequently, the tangential bending moment caused by the beats of a blade 122 of the fan 12 is greater than the tangential bending moment driven by beats of a blade 1400 of the low pressure compressor 140. The blades of the blades 122 of the fan 12 and of the blades 1400 of the low pressure compressor 140 then have very different behaviors. Furthermore, the mounting stiffness within the fan 12 is different from the mounting stiffness within the low pressure compressor 140.

As can be seen more specifically in FIG. 2, this results in particular in a large-amplitude displacement of the fan 12 relative to the low-pressure compressor 140, in a plane orthogonal to the longitudinal axis XX, at the interface between the platforms 1226 of the blades 122 of the fan 12 and the radial sealing wipers 1406 of the circumferential extension 1404 of the shroud 1402 of the low pressure compressor 140. The amplitude of this displacement for the second vibratory mode is for example between 0.01 and 0.09 millimeters, typically of the order of 0.06 millimeters, or, in another example, is of the order of a few tenths of a millimeter, for example 0.1 or 0.2 or 0.3 millimeters.

Shock absorber 2

A damper 2 is used in order to dampen these vibrations of the fan 12 and/or of the low pressure compressor 140.

The damper 2 is in particular configured to damp a displacement of the fan 12 relative to the low pressure compressor 140, in a plane orthogonal to the longitudinal axis XX, the displacement being caused by a beat of at least one blade 122 among the plurality of blades 122 of the fan 12.

Referring to Figures 3 to 7, 9 and 11, the damper 2 comprises:
- a first support part 21:
○ bearing on the fan 12 in a first bearing zone extending over a first angular sector A1 around the longitudinal axis XX, and
○ being configured to apply a first centrifugal force C1 on the fan, and
- A second support part 22 also bearing on the fan 12, but in a second support zone, different from the first support zone.

As visible in particular in Figure 5, the second support zone extends over a second angular sector A2 around the longitudinal axis X-X, the second angular sector A2 being lower than the first angular sector A1.

All or part of the blades 122 of the fan 12 can moreover be equipped with such a damper 2, depending on the desired damping, but also the assembly and/or maintenance characteristics.

In one embodiment, the first support part 21 is mounted fixed on the fan 12, for example by gluing. This facilitates the integration of the damper 2 within the turbomachine 1, and guarantees the support of the first support part 21 on the fan 12. As a variant, as for example illustrated in FIG. 10, the third part support 22 is mounted fixed on the low pressure compressor 140, for example by gluing. The first support part 21 can then be mounted free to rub on the fan 12.

Advantageously, with reference to FIGS. 4 and 5, the first angular sector A1 corresponds to the angular sector occupied by the platform 1226 of a blade 122 of the fan 12. In other words, the first support part 21 extends over the entire circumferential dimension of the platform 1226 of the blade 122, at the level of an internal surface of said platform 1226. The support of the damper 2 on the fan 12 is thus improved.

In an advantageous variant, the second support part 22 comes, for its part, to bear on a downstream surface of the stilt 1224 of the blade 122, as can be seen in FIGS. 4 and 5.

In one embodiment, the damper 2 comprises a material from the range having the trade name “SMACTANE® ST” and/or “SMACTANE® SP”, for example a material of the “SMACTANE® ST 70” type and/or “SMACTANE® SP 50”. It has indeed been observed that such materials have appropriate damping properties.

Referring to Figures 3 to 11, in one embodiment, the damper 2 comprises a third support part 23:
- bearing against the low pressure compressor 140, and
- Being configured to apply a second centrifugal force C2 on the low pressure compressor 140.

The third bearing part 23 bears against the low pressure compressor 140 in a third bearing zone extending over a third angular sector A3 around the longitudinal axis X-X.

In an advantageous variant of this embodiment, for example illustrated in Figures 4, 6, 7, and 9 to 11, the damper 2 further comprises a connecting part 20:
- connecting the first support part 21 to the third support part 23, and
- being thinned with respect to the first support part 21 and the third support part 23.

More specifically, as illustrated in Figures 4, 6, 7, and 9 to 11 the first support part 21 has a first radial thickness E1 in a section plane which includes the longitudinal axis XX, the third support part 23 has a third radial thickness E3 in the section plane, and the connecting part 20 has a radial connecting thickness E0 in the section plane. Figure 3 provides an example of a view in such a section plane. As visible in Figures 4, 6, 7, and 9 to 11, the radial connection thickness E0 is smaller than the first radial thickness E1 and the third radial thickness E3. The connecting part 20 is therefore thinner than the first support part 21 and the third support part 23.

Thus, the first support part 21 and the third support part 23 are solid. Consequently, in operation, each of the first support part 21 and of the third support part 23 exerts a respective centrifugal force C1, C2 on the fan 12 and the low pressure compressor 140, on which said support parts 21, 23 support. In this way, the support parts 21, 23 are each dynamically coupled respectively to the fan 12 and to the low pressure compressor 140 on which each bears, so as to undergo the same vibrations as each of the fan 12 and of the compressor. low pressure 140. In addition, the support parts 21, 23 are stiffer than the connecting part 20, in particular in a tangential direction. Advantageously, as for example visible in Figure 4, the third radial thickness E3 is greater than the first radial thickness E1, so as to better guarantee the support of the third support part 23.

The connecting part 20, which is thinner, is more flexible, in particular in a tangential direction. It therefore allows the fan 12 to transmit the vibrations to which it is subject to the low pressure compressor 140 and, conversely, it allows the low pressure compressor 140 to transmit the vibrations to which it is subject to the fan 12. Indeed, for frequencies high vibrations, the damping is in particular provided by the shearing work of the connecting part 20, that is to say by viscoelastic dissipation For low vibration frequencies, the damping is in particular provided by friction of one or the other of the first support part 21 or third support part 23 respectively against the fan 12 or against the low pressure compressor 140.

In addition, the third support part 23 comes to bear on the circumferential extension 1404 of the shroud 1402 of the low pressure compressor 140, at the level of an internal surface of the radial sealing wipers 1406. Indeed, it is at this position that the displacement of the fan 12 relative to the low pressure compressor 140, in the plane orthogonal to the longitudinal axis XX, is of greater amplitude, typically a few millimeters. Consequently, the damper 2 is particularly effective there. In addition, the thinning of the connecting part 20 provides clearance which allows the damper 2 to avoid rubbing on a corner of the radial sealing wipers 1406.

Referring to Figure 6, in one embodiment, a sacrificial plate 230 bears against the low pressure compressor 140. The sacrificial plate 230 is mounted fixed on the third support part 23, for example by gluing, and / or by being housed within a groove 2300 of the third support part 23 provided for this purpose, as shown in FIG. 6. The sacrificial plate 230 is configured to guarantee the support of the third support part 23 on the low pressure compressor 140. Indeed, the mechanical stresses in operation are such that slight tangential, axial and radial movements of the damper 2 are to be expected. These movements are in particular due to the vibrations to be damped, but also to the centrifugal loading of the damper 2. It is necessary that these movements do not wear out the low pressure compressor 140. In this respect, the sacrificial plate 230 comprises an anti- wear, for example of the Teflon type and/or any type of composite material. In an advantageous configuration, the sacrificial plate 230 is also treated by dry lubrication, with a view to perpetuating the value of the coefficient of friction between the damper 2 and the low-pressure compressor 140. This material with lubricating properties is for example of the type MoS2. Advantageously, the sacrificial plate 230 can also comprise an additional coating, configured to reduce the friction and/or the wear of the low pressure compressor 140. This additional coating is mounted fixed on the sacrificial plate 230, for example by gluing. The additional coating is of the dissipative and/or viscoelastic and/or damping type. It may in fact comprise a material from the range having the trade name “SMACTANE® ST” and/or “SMACTANE® SP”, for example a material of the “SMACTANE® ST 70” and/or “SMACTANE® SP 50” type. . It can also comprise a material chosen from among those having mechanical properties similar to those of vespel, Teflon or any other material with lubricating properties. More generally, the additional coating material advantageously has a friction coefficient of between 0.3 and 0.07. The sacrificial wafer 230 is optionally combined by juxtaposition with its additional coating. Indeed, it makes it possible to increase the friction, in particular tangential, of the damper 2 when, in operation, the sacrificial plate 230 is sufficiently constrained by the second centrifugal force C2 so that the movement of the fan 12 with respect to the low compressor pressure 140, in the plane orthogonal to the longitudinal axis XX, is damped by energy dissipation by means of viscoelastic shearing of the sacrificial plate 230.

Referring to Figure 7, in one embodiment:
- the first support part has a first support surface 2100 arranged to apply a first force F1 on the low pressure compressor 140, the first force F1 having a first longitudinal component F1L in a first direction parallel to the longitudinal axis XX , and a first radial component F1R in a second direction orthogonal to the longitudinal axis XX, the first longitudinal component F1L being greater than the first radial component F1R,
- the third support part 23 has a second support surface 2320 arranged to apply a second force F2 on the low-pressure compressor 140, the second force F2 having a second longitudinal component F2L in the first direction, and a second radial component F2R in the second direction, the second radial component F2R being greater than the second longitudinal component F2L.

In other words, the first support surface 2100 provides support with axial positioning of the damper 2, while the second support surface 2320 provides support with radial positioning of the damper 2. In addition , in operation, the second support surface 2320 participates in the application of the second centrifugal force C2 on the low pressure compressor 140.

Referring to Figure 8, in an advantageous variant of the embodiment illustrated in Figure 7:
- a first sacrificial plate 210 is mounted fixed on the first support part 21, for example by gluing, and has the first support surface 2100, and
- a second sacrificial plate 232 is mounted fixed on the third support part 23, for example by gluing, and has the second support surface 2320.

The first sacrificial plate 210 and the second sacrificial plate 232 advantageously have the same characteristics as those described with reference to the sacrificial plate 230 of the embodiment illustrated in FIG. 6, with the same benefits for the damping of a movement of the fan 12 with respect to the low pressure compressor 140, in the plane orthogonal to the longitudinal axis XX.

Still with reference to FIG. 8, also advantageously, a slot 213 is made in the first bearing part 21, a metal insert 233 being inserted into the slot 213, the second sacrificial plate 232 being fixedly mounted on the insert metal 233, for example by gluing. The metal insert 233 makes it possible to stiffen the damper 2. In addition, the metal insert 233 facilitates the deformation of the first sacrificial plate 210 and of the second sacrificial plate 232.

Referring to Figures 9 to 11, in one embodiment, a flyweight 3 is mounted fixed on the damper 2, for example by gluing. The flyweight 3 makes it possible to adjust the centrifugal forces C1, C2 exerted by the damper 2 on the fan 12 and on the low pressure compressor 140, so as to improve the dynamic coupling between the first support part 21 and the fan 12 , and between the third support part 23 and the low pressure compressor 140. Advantageously, the counterweight 3 comprises an elastomeric material. Referring to Figure 9, the flyweight 3 can then be mounted fixed both on the first support part 21 and on the third support part 23, for example by gluing.

Referring to Figure 10, in an advantageous variant, the counterweight 3 is mounted fixed on the first support part 21, for example by gluing, preferably only on the first support part 21. Advantageously, as shown in the figure 10, the flyweight is offset upstream of the first bearing part 21, so as to leave the connecting part 20 free so that, in operation, it can effectively work in shear to damp a movement of the fan 12 by relative to the low pressure compressor 140, in a plane orthogonal to the longitudinal axis XX. Alternatively, the flyweight 3 is mounted fixed on the third support part 23, for example by gluing, preferably only on the third support part 23. Advantageously, and for the same reasons as those mentioned with reference to the first part of support 21, the flyweight 3 is offset downstream of the third support part 23. Preferably, the flyweight 3 is mounted fixed only on the first support part 21 if the third support part 23 is mounted fixed on the low pressure compressor 140.

In another advantageous variant, with reference to Figure 11:
- a first flyweight 31 is fixedly mounted on the first support part 21, and
- a second flyweight 32 is mounted fixed on the third support part 23.

In this way, it is possible to independently adjust the first centrifugal force C1 and the second centrifugal force C2. This makes it possible to improve the damping of vibrations by targeting the vibration modes specific to the fan 12 and specific to the low pressure compressor 140.

In all that has been described above, the damper 2 is configured to damp a displacement of the fan 12 relative to the low pressure compressor 140, in the plane orthogonal to the longitudinal axis X-X.

This is however not limiting, since the damper 2 is also configured to damp a displacement of any first rotor 12 relative to any second rotor 140, in a plane orthogonal to the longitudinal axis XX, as long as the first rotor 12 is rotatable relative to the casing 10 around the longitudinal axis XX and comprises a disc 120 as well as a plurality of blades 122 capable of beating by vibrating relative to the disc 120 during a rotation of the first rotor 12 relative to the casing 10, and that the second rotor 140 is also rotatable relative to the casing 10 around the longitudinal axis XX.

Thus, the first rotor 12 can be a first stage of the high pressure compressor 142 or low pressure compressor 140, and the second rotor 140 be a second stage of said compressor 140, 142, successive to the first compressor stage 140, 142, upstream or downstream from it. Alternatively, the first rotor 12 can be a first stage of a high pressure turbine 180 or a low pressure turbine 182, and the second rotor 140 can be a second stage of said turbine 180, 182, successive to the first turbine stage 180, 182, in upstream or downstream of it.

In any event, the damper 2 has a restricted size. Therefore, it can easily be integrated into existing turbomachinery.

Moreover, by being configured to exert centrifugal forces C1, C2 on the first rotor 12 and, optionally, on the second rotor 140, the damper 2 ensures a high tangential stiffness between the first rotor 12 and the second rotor 140. It thus stands out from an overly flexible damper which would only become deformed when the first rotor 12 moves relative to the second rotor 140, in the plane orthogonal to the longitudinal axis XX. On the contrary, damper 2 dissipates such a displacement:
- either by friction and/or oscillations between a state where the damper 2 is stuck on the rotors 12, 140 and a state where the damper 2 slides on the rotors 12, 140, which makes it possible to dampen in particular the low frequencies ,
- Or by viscoelastic shearing within the damper 2, which makes it possible to dampen the high frequencies in particular.

However, the damper 2 remains flexible enough to maximize the contact surfaces between said damper 2 and the rotors 12, 140 on which it bears. To do this, the damper 2 has a greater tangential stiffness than an axial stiffness and a radial stiffness.

The contact forces between the damper 2 and the rotors 12, 140 can in particular be adjusted by means of flyweights 3 and/or sacrificial pads 230, 210, 232 and/or additional coatings on said sacrificial pads 230, 210, 232 At low frequencies, it is indeed necessary to ensure that the centrifugal forces C1, C2 exerted by the damper 2 on the rotors 12, 140 are not too great, in order to guarantee that the damper 2 can oscillate between a glued state and a slippery state on the rotors 12, 140, and thus dampen by friction. At high frequencies, on the other hand, it is necessary to ensure that the centrifugal forces C1, C2 exerted by the damper 2 on the rotors 12, 140 are sufficiently great for the preload of the damper 2 on the rotors 12, 140 is sufficient to ensure that the damper 2 can be the viscoelastic shear seat.

The wear of the rotors 12, 140 is in particular limited by treatment of the surfaces of the damper 2 resting on the rotors 12, 140, for example to provide them with a coating with a low coefficient of friction.

Claims (15)

Turbomachine assembly (1) comprising:
- a casing (10),
- a first rotor (12):
○ rotatable relative to the housing (10) around a longitudinal axis (XX), and
○ including:
* a disc (120), and
* a plurality of blades (122) capable of beating relative to the disc (120) during rotation of the first rotor (12) relative to the housing (10),
- a second rotor (140) rotatable relative to the housing (10) around the longitudinal axis (XX), and
- a damper (2) configured to damp a displacement of the first rotor (12) relative to the second rotor (140), in a plane orthogonal to the longitudinal axis (XX), the displacement being caused by a beat of at least a vane (122) among the plurality of vanes (122), the damper (2) comprising:
○ a first support part (21):
* bearing on the first rotor (12) in a first bearing zone extending over a first angular sector (A1) around the longitudinal axis (XX), and
* being configured to apply a first centrifugal force (C1) on the first rotor (12), and
○ a second bearing part (22) bearing on the first rotor (12) in a second bearing zone, different from the first bearing zone, the second bearing zone extending over a second sector angular (A2) around the longitudinal axis (XX), the second angular sector (A2) being smaller than the first angular sector (A1). Assembly according to claim 1, in which the first support part (21) is fixedly mounted on the first rotor (12). Assembly according to one of Claims 1 and 2, in which the damper (2) comprises a third support part (23):
- bearing on the second rotor (140), and
- Being configured to apply a second centrifugal force (C2) on the second rotor (140). Assembly according to claim 3, in which the damper (2) comprises a connecting part (20):
- connecting the first support part (21) to the third support part (23), and
- being thinned with respect to the first support part (21) and the third support part (23). Assembly according to one of Claims 3 and 4, in which:
- the first support part (21) has a first support surface (2100) arranged to apply a first force (F1) on the second rotor (140), the first force (F1) having a first longitudinal component (F1L ) in a first direction parallel to the longitudinal axis (XX), and a first radial component (F1R) in a second direction orthogonal to the longitudinal axis (XX), the first longitudinal component (F1L) being greater than the first component radial (F1R),
- the third support part (23) has a second support surface (2320) arranged to apply a second force (F2) on the second rotor (140), the second force (F2) having a second longitudinal component (F2L ) in the first direction, and a second radial component (F2R) in the second direction, the second radial component (F2R) being greater than the second longitudinal component (F2L). Assembly according to one of Claims 3 to 5, the assembly further comprising a sacrificial plate (230):
- Fixed mounted on the third support part (23), and
- Coming to bear on the second rotor (140). Assembly according to one of Claims 5 and 6, the assembly further comprising:
- a first sacrificial plate (210) fixedly mounted on the first support part (21) and having the first support surface (2100), and
- a second sacrificial plate (232) fixedly mounted on the third bearing part (23) and having the second bearing surface (2320). Assembly according to Claim 7, in which a slot (213) is made in the first support part (21), the assembly further comprising a metal insert (233) inserted into the slot (213), the second sacrificial plate (232) being fixedly mounted on the metal insert (233). Assembly according to one of Claims 1 to 8, the assembly further comprising a flyweight (3) fixedly mounted on the shock absorber (2). Assembly according to Claim 9, in which the flyweight (3) is fixedly mounted on the first support part (21). Assembly according to one of Claims 3 to 10, the assembly further comprising a flyweight (3) fixedly mounted on the third support part (23). Assembly according to one of Claims 3 to 11, the assembly further comprising:
- a first flyweight (31) fixedly mounted on the first support part (21), and
- A second flyweight (32) fixedly mounted on the third support part (23). Assembly according to one of claims 1 to 12, in which each of the vanes (122) among the plurality of vanes (122) comprises:
- a blade root (1220) connecting the blade (122) to the disc (120),
- a profiled blading (1222),
- a stilt (1224) connecting the blading (1222) to the blade root (1220), and
- a platform (1226) connecting the blading (1222) to the stilt (1224) and extending transversely to the stilt (1224), the first support part (21) coming to rest on the platform (1226 ) of a blade (122) among the plurality of blades (122). Assembly according to one of Claims 3 to 13, in which the second rotor (140) comprises a shroud (1402), the shroud (1402) comprising a circumferential extension (1404), the third support part (23) coming into pressing on the circumferential extension (1404). Turbomachine (1) comprising an assembly according to one of Claims 1 to 14, and in which the first rotor (12) is a fan and the second rotor (140) is a low-pressure compressor.