Turbine engine assembly provided with a stator and a rotor

Abstract

One aspect of the invention relates to a turbine engine assembly (10) comprising a stator (100) and a rotor (50) having an axis X. The stator comprises fixed blades (20) distributed annularly about the axis X, each of the fixed blades being equipped with an inner platform (210) comprising a guide rail (212); and sectored feet (30) distributed annularly about the axis X, each arranged between at least one fixed blade and the rotor and comprising an engaged portion (310) housed inside the guide rail (212).

Description

TURBOMACHINE ASSEMBLY EQUIPPED WITH A STATOR AND A ROTOR TECHNICAL FIELD OF THE INVENTION

[0001] The present invention relates to the field of stators and rotors of turbomachines such as a turbojet for aircraft.

[0002] The present invention relates more particularly to a turbomachine assembly provided with a stator equipped with fixed blades, that is to say a turbine distributor or a compressor rectifier, and a rotor. TECHNOLOGICAL BACKGROUND OF THE INVENTION

[0003] Conventionally, as shown in FIG. 1, a turbomachine assembly 10 is formed by a stator 100 and a rotor 50 of axis X.

[0004] The stator 100 includes: - fixed blades 20 arranged annularly around the axis X, each of the fixed blades 20 being equipped with: o an internal platform 210 comprising a guide rail 212, o an external platform, not shown, and o a blade 230 extending between the internal platform 210 and the external platform and secured to them, - an annular ferrule 240 of axis X comprising an upstream hook 242 and a downstream hook 244, the upstream hook 242 supporting an annular abradable cartridge 246, and - an annular upstream flange 248 with axis X fixed by a bolted connection 250 to the annular shell 240.

[0005] The rotor 50 comprises sealing lips 54 arranged opposite the abradable cartridge 246 to ensure sealing at the level of the internal platforms 210 of the fixed blades 20 of the stator 100.

[0006] However, during the operating cycle of a turbomachine assembly 10 according to FIG. 1, there is a friction phenomenon between the abradable cartridge 246 at the annular shell 240 of the stator 100 and the sealing lips 54 of the rotor 50 which causes the acceleration of the wear of these two parts and requires the regular replacement of the abradable cartridge 246, which results in a relatively high maintenance cost. In addition, the wear of the abradable cartridge 246 and the sealing wipers 54 increases the space between these two parts, which causes leaks and impacts the performance and efficiency of the turbomachine between two maintenance steps.

[0007] Therefore, as shown in Figure 2, the stator 100 and the rotor 50 of the turbomachine assembly 10 have been modified in order to solve the friction problem. More particularly, the annular shroud 240, the annular upstream flange 248 and the abradable cartridge 246 of the stator 100 have been removed and replaced by at least one sectorized pad 30 (preferably at least three sectorized pads 30, the number of sectorized pads 30 being proportional to the diameter of the stator 100), and the rotor 50 has been modified to have a sealing surface 52 that is substantially flat and devoid of sealing lips 54.

[0008] Each sectored pad 30 of the stator 100 is arranged between at least one fixed blade 20 and the rotor 50 and comprises: - an engaged portion 310 housed inside the guide rail 212 comprising a groove 316 in which a tenon 216 of the internal platform 210 of a fixed blade 20 is inserted, and - a base 320 extending axially between an upstream edge 320A and a downstream edge 320B, supporting the engaged portion 310 and comprising: o an upstream groove 322 and a downstream groove 324 axially opposite one another, and o a sealing surface 325 radially opposite the engaged portion 310.

[0009] The sealing surface 52 of the rotor 50 is arranged opposite the sealing surface 325 of each sectored pad 30 of the stator 10 so that the sealing surfaces 325, 52 are radially spaced from one another by a constant clearance J along the entire circumference of the rotor 50. The clearance J formed below the sealing surface 325 of each sectored pad 30 decreases from the upstream edge 320A towards the downstream edge 320B of the base 320 of the sectored pad 30. Such a geometry of the turbomachine assembly 10 according to FIG. 2 makes it possible to eliminate friction phenomena between the stator 100 and the rotor 50.

[0010] However, during the operating cycle of a turbomachine assembly 10 according to FIG. 2, each sectored shoe 30 is movable between the fixed blade 20 and the rotor 50 by an air bearing effect. The air bearing effect corresponds to the pressure difference, at the upstream edge 320A of the base 320 of each sectored shoe 30, between a lower pressure Pi exerted radially against the sealing face 325 and a higher pressure Ps exerted radially in the upstream groove 322, the lower pressures Pi and upper pressures Ps being exerted in an opposite direction relative to each other.

[0011] This air bearing effect has the consequence of controlling the clearance J formed between the sealing surface 325 of the stator 100 and the sealing surface 52 of the rotor 50, at the downstream edge 320B of the base 320 of the sectored pad 30, the clearance J being constant along the entire circumference of the rotor 50. In the case of an assembly 10 such as shown in FIG. 2, the clearance J can vary both between the phase in which the turbomachine is stopped and its operating cycle and both during the cruising phase of each operating cycle of the turbomachine, corresponding to the phase during which the consumption of the turbomachine is the highest. However, the variation of the clearance J during the cruising phase can alter the performance and efficiency of the turbomachine unlike the variation of the clearance J between the stopping phase and the machine operating cycle. SUMMARY OF THE INVENTION

[0012] The invention provides a solution to the problems mentioned above, by proposing a turbomachine assembly provided with a rotor and a turbomachine stator equipped with fixed blades and sectored pads, which have a particular geometry.

[0013] A first aspect of the invention relates to a turbomachine assembly comprising a stator and an X-axis rotor according to which the stator comprises: - fixed blades distributed annularly around the X axis, each of the fixed blades being equipped with an internal platform comprising a guide rail, and - sectored pads distributed annularly around the X axis, each arranged between at least one fixed blade and the rotor and comprising an engaged portion housed inside the guide rail.

[0014] The stator comprises at least one spring mounted compressed in the sectored pads.

[0015] The turbomachine assembly according to the invention allows, thanks to the presence of at least one spring in the sectored pads, a compensating movement of each sectored pad in the guide rail of the internal platform of the fixed blade so as to absorb the thermomechanical movements of the surrounding elements. Such an assembly makes it possible to obtain a constant clearance between the sectored pads and the rotor, along the entire circumference of the rotor, in the cruising phase of the operating cycle of the turbomachine assembly, even in the presence of air bearing effects. In addition, the presence of a spring makes it possible to ensure the connection between each sectored pad and thus maintain a constant diameter of revolution, along the entire circumference of the rotor, during the phase in which the turbomachine is stopped and the operating phases of the turbomachine.Therefore, the clearance does not vary between the phase in which the turbomachine is at a standstill and its operating cycle and neither during the cruising phase of each operating cycle of the turbomachine, which reduces wear of the parts.

[0016] Advantageously, the internal platform of at least one fixed blade, preferably at least three fixed blades, comprises a tenon received in a groove of one of the sectored pads. Such a feature makes it possible to guide the movement of the sectored pads in a radial direction to ensure coaxiality between the stator, i.e. the sectored pads, and the rotor.

[0017] Advantageously, the rotor and the sectored pads are radially spaced apart by a constant clearance J from each other. The value of the clearance J depends on the balance of the pads without spring action.

[0018] Preferably, the turbomachine assembly comprises a tenon received in a groove of one of the sectored pads and the sectored pads are radially spaced apart by a constant clearance J relative to each other. The tenon-spring combination forms a sliding connection in the radial direction guaranteeing a calibrated clearance J during the phase in which the turbomachine is at a standstill.

[0019] According to a first embodiment of the invention, the stator spring comprises a single elastic ring arranged inside the engaged portions and surrounding the sectored pads.

[0020] According to a second embodiment of the invention, the engaged portion of each sectored pad is supported by a base comprising at least one upstream or downstream groove, and the stator comprises a spring comprising an elastic ring arranged in one of the upstream or downstream grooves and surrounding the sectored pads.

[0021] Advantageously, according to the second embodiment of the invention, the elastic ring of the spring is corrugated and received alternately in a lower housing and in an upper housing of one of the upstream or downstream grooves, each housing having a shape complementary to that of the elastic ring.

[0022] Preferably, according to the second embodiment of the invention, the lower and upper housings of one of the upstream or downstream grooves are arranged parallel to one another and each have a succession of alternately concave and convex curved surfaces, the elastic ring of the spring has a succession of alternately concave and convex curves; and the elastic ring of the spring is arranged so that each convex curve of the elastic ring is arranged to bear against one of the concave curved surfaces of one of the lower or upper housings and each concave curve is arranged to bear against one of the convex curved surfaces of the other of the upper or lower housings.

[0023] Preferably, according to the second embodiment of the invention, each sectored pad comprises locking rods each arranged axially in one of the lower or upper housings of one of the upstream or downstream grooves and received in a locking notch of the elastic ring.

[0024] According to a third embodiment of the invention, the stator comprises several springs each arranged in two adjacent sectorized pads.

[0025] Advantageously, according to the third embodiment of the invention, each sectored pad comprises a holding channel arranged in the engaged portion and receiving at least part of a spring.

[0026] According to a first variant of the third embodiment of the invention, each spring comprises a corrugated strip, and each sectored pad comprises two locking rods each arranged axially in the holding channel of one of the adjacent sectored pads, in the vicinity of one end of the sectored pad, so that each corrugated strip is mounted compressed in the holding channel to allow elastic deformation of the corrugated strip by exerting a tangential force between the locking rods of two adjacent sectored pads.

[0027] According to a second variant of the third embodiment of the invention, each spring is a double spring comprising two support tabs each arranged in the holding channel of the engaged portion of one of the adjacent sectored pads, and a connecting portion connecting the two support tabs and extending radially outside the holding channels.

[0028] Preferably, according to the second variant of the third embodiment, the connecting portion of each double spring is mounted compressed in the engaged portion of each of the adjacent sectored pads to allow elastic deformation of the double spring by exerting a radial force against an inner wall of the guide rail.

[0029] A second aspect of the invention relates to a turbomachine comprising an assembly according to the first aspect of the invention.

[0030] 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

[0031] Other advantages and characteristics of the invention will appear on reading the following description, illustrated by the figures in which: - Figure 1, already described, is a partial schematic view of a first turbomachine assembly comprising a stator and a rotor according to a first example of the state of the art; - Figure 2, already described, is a partial schematic view of a second turbomachine assembly comprising a stator and a rotor according to a second example of the state of the art; - Figure 3 is an exploded perspective view of a turbomachine assembly comprising a stator and a rotor according to the invention; - Figure 4 is a partially exploded perspective view of a stator of the turbomachine assembly of Figure 3 provided with fixed blades and sectored pads according to the invention; - Figure 5 is a perspective view of a sectored stator pad according to a first and a second embodiment of the invention; - Figure 5A is a partial sectional view of the sectored pad and rotor of Figure 5; - Figure 6 is a partial perspective view of two adjacent sectored pads according to Figure 5, comprising a spring according to the first embodiment of the invention, in the mounted position of the spring in the sectored pads; - Figure 7 is a partial exploded perspective view of a sectored skate according to Figure 5 comprising a spring according to the second embodiment of the invention; - Figure 8 is a partial perspective view of a sectored pad according to Figure 5 comprising a spring according to Figure 7 in the mounted and locked position of the spring in the sectored pad; - Figure 9 is a perspective view of a sectored stator pad according to a third embodiment of the invention; - Figure 10 is a partial exploded perspective view of a turbomachine assembly comprising a stator provided with sectored pads according to Figure 8 and a spring according to a first variant of the third embodiment of the invention; - Figure 11 is a partial exploded perspective view of a turbomachine assembly comprising a stator provided with sectored pads according to Figure 8 and a spring according to a second variant of the third embodiment of the invention; - Figure 12 is a partial perspective view of a sectored pad according to Figure 8 and of a spring according to a second variant of the third embodiment of the invention. DETAILED DESCRIPTION

[0032] An exemplary embodiment of a turbomachine assembly according to the invention is described in detail below, with reference to the appended drawings. This example illustrates the characteristics and advantages of the invention.

[0033] Unless otherwise specified, the same element appearing in different figures has a single reference.

[0034] For the understanding of the invention, the radial, tangential and axial orientations will be adopted according to the RTA reference frame indicated in the figures, the tangent axes T and axial A of which extend in a vertical plane according to the orientation in the figures. The axial axis A is parallel to an axis X of the rotor and the stator of the turbomachine assembly. The rotor towards the stator of the turbomachine assembly is oriented according to the radial axis R of the RTA reference frame.

[0035] In the description, the terms "upstream" and "downstream" are defined in relation to the direction of flow of the gas flow in the turbomachine. In addition, the terms "internal" and "external" are defined in relation to the X axis, the term "internal" designates the element closest to the X axis of rotation, as opposed to the term "external" which designates the element furthest from the X axis, in particular in the expression "internal platform" and "external platform".

[0036] Figure 3 represents a turbomachine assembly 10, formed by a stator 100 and a rotor 50 of axis X.

[0037] The stator 100 according to the invention comprises fixed blades 20 arranged annularly around the axis x, sectored pads 30 each arranged radially between at least one fixed blade 20 and the rotor 50 and at least one spring 40 (visible in figures 6, 7, 9, 10 and 11) mounted compressed in the sectored pads 30.

[0038] As shown in Figure 4, each fixed vane 20 of the stator 100 comprises: - an internal platform 210 extending tangentially between a first and a second end 210A, 210B and comprising a U-shaped guide rail 212, - an external platform 220 substantially parallel to the internal platform 210, and - a blade 230 extending radially between the internal platform 210 and the external platform 220 and secured to them.

[0039] The upstream end 210A of the internal platform 210 of each fixed blade 20 is arranged opposite the downstream end 210B of the internal platform 210 of the adjacent fixed blade 20.

[0040] As shown in Figure 4, each sectored pad 30 of the stator 100 extends tangentially between a first and a second end 30A, 30B and comprises: - a committed portion 310, and - a base 320 extending axially between an upstream edge 320A and a downstream edge 320B, supporting the engaged portion 310 and comprising: o an upstream groove 322 (visible in figure 5) and a downstream groove 324 axially opposite one another, and o a sealing surface 325 radially opposite the engaged portion 310.

[0041] The upstream end 30A of each sectored pad 30 is arranged opposite the downstream end 30B of the adjacent sectored pad 30.

[0042] As illustrated in Figures 3 and 4, the internal platform 210 of at least one fixed blade 20 is equipped with a tenon 216 and each sectored pad 30 comprises a groove 316 so that in the assembled position of the stator 100, the tenon 216 is received in the groove 316. Each tenon 216 and each groove 316 extend in a radial direction so as to radially guide the compensating movement of the sectored pads 30 relative to the fixed blades 20.

[0043] Advantageously, each sectored pad 30 is arranged opposite several fixed blades 20, the number of sectored pads 30 is therefore strictly less than the number of fixed blades 20. In addition, each sectored pad 30 comprises a single groove 316 and the number of fixed blades 20 equipped with a tenon 216 is equal to the total number of sectored pads 30 of the stator 100. The stator 100 according to an example shown in FIG. 4 comprises four sectored pads 30 (the number of sectored pads 30 being proportional to the diameter of the stator 100) and thirty-eight fixed blades 20, each of the four sectored pads 30 comprising a groove 316 and only four fixed blades 20 are equipped with a tenon 216.

[0044] In the assembled position of the assembly 10 as shown in the figures - the engaged portion 310 of a sectored pad 30 is housed inside the guide rail 212 of each fixed blade 20 arranged opposite this sectored pad 30, - the tenon 216 of the fixed blade 20 which is equipped is received in the groove 316 of the sectored pad 30, and - the sealing surface 325 of each sectored pad 30 of the stator 100 is arranged opposite a sealing surface 52 of the rotor 50, the sealing surfaces 325 and 52 being radially spaced from each other by a clearance J, the clearance J being minimal at the downstream edge 320B of the base 320 of the sectored pad 30 and constant along the entire circumference of the rotor 50.

[0045] As shown in Figure 5, the engaged portion 310 of each sectored pad 30 of the assembly 10 according to a first and a second embodiment of the invention comprises: - a U-shaped housing 311 formed inside the engaged portion 310, and - an inner wall 312 arranged in the engaged portion 310 opposite an inner wall 214 of the internal platform 210 of the fixed blade 20.

[0046] During the operating cycle of the turbomachine assembly 10, each sectored pad 30 is movable between the fixed blade 20 and the rotor 50 by an air bearing effect. As shown in FIG. 5A, the air bearing effect corresponds to the pressure difference, at the upstream edge 320A of the base 320 of each sectored pad 30, between a lower pressure Pi exerted radially against the sealing face 325 and a higher pressure Ps exerted radially in the upstream groove 322, the lower pressures Pi and higher pressures Ps being exerted in an opposite direction relative to each other. This air bearing effect has the consequence of controlling the clearance J formed between the sealing surface 325 of the stator 100 and the sealing surface 52 of the rotor 50.The variation of the upper pressures Ps allows the base 320 of each sectored pad 30 to be pressed against the rotor at the upstream edge 320A and thus to balance the leakage pressure between the rotor 50 and the stator 100.

[0047] As shown in Figure 5A, the sealing surface 325 of the base 320 of each sectored pad 30 is divided into an upstream section 325A comprising the upstream edge 320A and a downstream section 325B comprising the downstream edge 320B, in the axial direction A. The upstream section 325A forms a conical portion of the rotor 50 which does not extend parallel to the sealing surface 52 of the rotor 50 and the downstream section 325B extends parallel to the sealing surface 52 of the rotor, the clearance J at the downstream edge 320B of the base 320 of the sectored pad 30 is constant so as to control the leakage between the rotor 50 and the stator 100 in all operating phases of the turbomachine assembly 10.

[0048] According to the first embodiment of the invention shown in Figure 6, the stator 100 comprises a single spring 40 comprising an elastic ring 410 arranged inside the engaged portion 310 of each of the sectored pads 30 and surrounding all of the sectored pads 30 of the stator 100. The elastic ring 410 is therefore mounted in the U-shaped housing 311 of the engaged portion 310 and extends along the entire circumference of this U-shaped housing 311. Advantageously, the elastic ring 410 makes several circumferential turns in the U-shaped housing 311.

[0049] In the mounted position of the spring 40 in the sectored pads 30, the elastic ring 410 is compressed in the engaged portions 310 of the sectored pads 30 to allow elastic deformation of this elastic ring 410 by exerting a tangential force against the inner wall 312 of the engaged portion 310 of each sectored pad 30.

[0050] According to the second embodiment of the invention shown in Figures 7 and 8, the stator 100 comprises a single spring 40 comprising an elastic ring 411 arranged in the downstream groove 324 of the base 320 of each of the sectored pads 30 and surrounding all of the sectored pads 30. Advantageously, the elastic ring 411 makes a single circumferential turn in the downstream groove 324.

[0051] In the mounted and locked position of the spring 40 in the sectored pads 30 as shown in FIG. 8, the elastic ring 411 is compressed in the downstream groove 324 of the sectored pads 30 to allow elastic deformation of the elastic ring 411 by exerting a tangential force against an inner wall of the downstream groove 322 of the base 320 of each sectored pad 30.

[0052] Advantageously, as shown in Figures 7 and 8, the downstream groove 324 of each sectored pad 30 comprises a lower housing 326 and a housing upper 328 radially opposed to each other. The lower 326 and upper 328 housings are scalloped in the form of a succession of alternately concave and convex curved surfaces, and the lower 326 and upper 328 housings are arranged parallel to each other.

[0053] The elastic ring 411 of the spring 40 is undulated in the form of a succession of alternating concave and convex curves. In the mounted and locked position of the spring 40 in the sectored pads 30 as shown in FIG. 8, the elastic ring 411 is received alternately in the lower housing 326 and in the upper housing 328 of the downstream groove 324 so that each convex curve of the elastic ring 411 is arranged to bear against one of the concave curved surfaces of one of the lower housings 326 or upper housings 328 and each concave curve of the elastic ring 411 is arranged to bear against one of the convex curved surfaces of the other of the upper housings 328 or lower housings 326. More particularly, the lower housings 326 and upper housings 328 have a shape complementary to that of the elastic ring 411.

[0054] In addition, each sectorized pad 30 comprises one or more locking rods 330, each arranged axially in a locking hole 332 of the downstream groove 324. Each locking rod 330 comprises a locking notch 412 receiving the elastic ring 411. According to an example shown in FIGS. 7 and 8, the locking hole 332 is formed in the lower housing 326 of the downstream groove 324. The presence of locking rods 330 makes it possible to tangentially block the positioning of the elastic ring 411 inside the downstream groove 324 and prevent any movement of the elastic ring 411, during the operating cycle of the turbomachine.

[0055] Preferably, the two elastic rings 411 of the springs 40 according to the second embodiment of the invention are identical.

[0056] As shown in Figure 9, the engaged portion 310 of each sectored pad 30 of the assembly 10 according to a third embodiment of the invention comprises a holding channel 314 arranged in the engaged portion 310 and comprising the inner wall 312, and the U-shaped section housing 311.

[0057] According to the third embodiment of the invention shown in Figures 10, 11 and 12, the stator 100 comprises several springs 40 each received in the holding channel 314 of two adjacent sectored pads 30.

[0058] According to the first and second embodiments of the invention, in the mounted position of the elastic ring 410 of the spring 40 in the sectored pads 30, the tangential force exerted by the elastic ring 410 causes the displacement of all of the sectored pads 30 towards the axis X and thus forms a continuous ring coaxial with the rotor 50. This elastic ring 411 thus makes it possible to control the compensating displacement of the sectored pads 30 radially towards the axis X. In addition, the control of the constant clearance J is carried out only during the operating cycle of the turbomachine, by the centrifugal force generated by the very high rotation speed of the turbomachine.

[0059] According to a first variant of the third embodiment of the invention as shown in Figure 10, each spring 40 comprises a corrugated strip 420 extending tangentially between a first and a second end 420A, 420B. Each sectored pad 30 comprises two locking rods 330 each arranged axially in the holding channel 314, in the vicinity of one end 30A, 30B of the sectored pad 30.

[0060] In the mounted position of the spring 40 in the sectored pads 30 according to the first variant of the third embodiment of the invention, not shown, each corrugated strip 420 is compressed in the holding channel 314, between the two locking rods 330, to allow elastic deformation of the corrugated strip 420 and exert a tangential force between the locking rods 330 of the two adjacent sectored pads 30. According to this variant, the tangential force exerted by each corrugated strip 420 causes the displacement of all the sectored pads 30 towards the axis X and thus forms a continuous ring coaxial with the rotor 50. In addition, the control of the constant clearance J is carried out only during the operating cycle of the turbomachine, by the centrifugal force generated by the very high rotational speed of the turbomachine.

[0061] According to a second variant of the third embodiment of the invention as shown in Figures 11 and 12, each spring 40 is a double spring 44 comprising: - two support legs 440 in the form of corrugated strips, each arranged in the holding channel 314 of the engaged portion 310, and - a connecting portion 442 connecting the two support legs 440 and extending radially outside the holding channel 314; the connecting portion 442 comprises a central body 444 in the form of a strip substantially folded into a U

[0062] As shown in Figures 11 and 12, the two support legs 440 and the central body 444 of the connecting portion 442 of the double spring 44 form a single piece whose section has the shape of a Greek letter omega (Q).

[0063] According to a particular example of the double spring 44 as shown in Figures 11 and 12, the connecting portion 442 comprises an upper body 446 in the form of a part, independent or attached to the central body 444, arranged between the inner wall 214 of the guide rail 212 and the top of the central body 444 of the connecting portion 442 of the double spring 44. For example, the section of the upper body 446 of the connecting portion 442 has a substantially triangular shape whose vertices are rounded.

[0064] In the mounted position of the double spring 44 in the sectored pads 30 according to the second variant of the third embodiment of the invention, as shown in FIG. 12, the support lugs 440 are mounted in the holding channels 314 of two adjacent sectored pads 30 and the connecting portion 442 of each spring 40 is compressed radially in the engaged portion 310 to allow elastic deformation of the spring 40 and exert a radial force both against the inner wall 214 of the guide rail 212 and the inner wall 312 of the holding channel 314. In addition, the control of the constant clearance J is carried out only during the operating cycle of the turbomachine, by the centrifugal force generated by the very high rotational speed of the turbomachine.

[0065] According to the second variant of the second embodiment of the invention, in the mounted position of each double spring 44 in the sectored pads 30, the tangential force exerted by each double spring 44 causes the displacement of all of the sectored pads 30 towards the axis X and thus forms a continuous ring coaxial with the rotor 50. In addition, the control of the constant clearance J is carried out by the radial force exerted by each double spring 44 both during the phase in which the turbomachine is at a standstill and during its operating cycle.

[0066] The turbomachine assembly 10 according to the invention thus makes it possible to maintain a constant clearance J between the stator 30 and the rotor 50, throughout the operating cycle of the assembly 10 thanks to the presence of one or more springs 40 and the compensating displacement of the sectored pads in the radial direction. Such characteristics make it possible to maintain constant performance and efficiency of the turbomachine and thus to increase its service life. In addition, during the operating cycle of such a turbomachine assembly 10, no friction phenomenon between the stator 100 and the rotor 50 is present, which considerably limits the wear of these two parts compared to an assembly 10 according to the state of the art and avoids the exchange of parts and the associated maintenance costs.

Claims

CLAIMS

1. Turbomachine assembly (10) comprising a stator (100) and a rotor (50) of axis X according to which the stator (100) comprises: - fixed blades (20) distributed annularly around the X axis, each of the fixed blades (20) being equipped with an internal platform (210) comprising a guide rail (212), and - sectored pads (30) distributed annularly around the axis X, each arranged between at least one fixed blade (20) and the rotor (50) and comprising an engaged portion (310) housed inside the guide rail (212). characterized in that the stator (100) comprises at least one spring (40) mounted compressed in the sectored pads (30).

2. Turbomachine assembly (10) according to claim 1, characterized in that the internal platform (210) of at least one fixed blade (20) comprises a tenon (216) received in a groove (316) of the engaged portion (310) of one of the sectored pads (30) of the stator (100). [Claim s] Turbomachine assembly (10) according to claim 1 or 2, characterized in that the spring (40) of the stator (100) comprises a single elastic ring (410) arranged inside the engaged portions (310) and surrounding the sectored pads (30).

4. Turbomachine assembly (10) according to claim 1 or 2, characterized: - in that the engaged portion (310) of each sectored pad (30) is supported by a base (320) comprising at least one upstream (322) or downstream (324) groove, - and in that the stator (100) comprises a spring (40) comprising an elastic ring (411) arranged in one of the upstream (322) or downstream (324) grooves and surrounding the sectored pads (30). [Claim s] Turbomachine assembly (10) according to claim 4, characterized in that the elastic ring (411) of the spring (40) is corrugated and received alternately in a lower housing (326) and in an upper housing (328) of one of the upstream (322) or downstream (324) grooves [Claim s] Turbomachine assembly (10) according to claim 1 or 2, characterized in that the stator (100) comprises several springs (40) each arranged in two adjacent sectorized pads (30).

7. Turbomachine assembly (10) according to claim 6, characterized in that each sectored pad (30) comprises a holding channel (314) arranged in the engaged portion (310) and receiving at least part of a spring (40). [Claim s] Turbomachine assembly (10) according to claim 7, characterized in that: - each spring (40) comprises a corrugated strip (420), and - each sectored pad (30) comprises two locking rods (330), each arranged axially in the holding channel (314) of one of the adjacent sectored pads (30), in the vicinity of one end (30A, 30B) of the sectored pad (30), such that each corrugated strip (420) is mounted compressed in the holding channel (314) to allow elastic deformation of the corrugated strip (420) by exerting a tangential force between the locking rods (330) of two adjacent sectored pads (30).

9. Turbomachine assembly (10) according to claim 7, characterized in that each spring (40) is a double spring (44) comprising: - two support legs (440), each arranged in the holding channel (314) of the engaged portion (310) of one of the adjacent sectored pads (30), and - a connecting portion (442) connecting the two support legs (440) and extending radially outside the holding channels (314).

10. Turbomachine assembly (10) according to claim 9, characterized in that the connecting portion (442) of each double spring (44) is mounted compressed in the engaged portion (310) of each of the sectored pads (30) adjacent to allow elastic deformation of the double spring (44) by exerting a radial force against an inner wall (214) of the guide rail (212).

11. Turbomachine characterized in that it comprises an assembly (10) according to any one of the preceding claims.

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