Patent Application
20210115806
The invention relates to a turbine ring assembly comprising a plurality of ring sectors made of ceramic-matrix composite material as well as a ring support structure.
The field of application of the invention is in particular that of the aeronautical gas turbine engines. The invention is however applicable to other turbomachines, for example industrial turbines.
In the case of entirely metallic turbine ring assemblies, it is necessary to cool all the elements of the assembly and particularly the turbine ring which is subjected to the hottest flows. This cooling has a significant impact on the engine performance since the cooling flow used is taken from the main flow of the engine. In addition, the use of metal for the turbine ring limits the possibilities to increase the temperature at the turbine, which would however allow improving the performance of the aeronautical engines.
In order to solve these problems, it has been envisaged to produce turbine ring sectors made of ceramic-matrix composite material (CMC) in order to overcome the implementation of a metal material.
CMC materials have good mechanical properties making them capable of forming structural elements and advantageously preserve these properties at high temperatures. The implementation of CMC materials has advantageously allowed reducing the cooling flow to be imposed during the operation and therefore increasing the performance of the turbomachines. In addition, the implementation of CMC materials advantageously allows decreasing the weight of the turbomachines and reducing the effect of hot expansion encountered with the metal parts.
However, the existing solutions proposed can implement an assembling of a CMC ring sector with metal attachment portions of a ring support structure, these attachment portions being subjected to the hot flow. Consequently, these metal attachment portions undergo hot expansions, which can lead to mechanical stressing of the CMC ring sectors and to an embrittlement thereof.
Furthermore, documents FR 2 540 939, GB 2 480 766, EP 1 350 927, US 2014/0271145, US 2012/082540 and FR 2 955 898 which disclose turbine ring assemblies, are known.
There is a need to improve existing turbine ring assemblies and their mounting, and in particular the existing turbine ring assemblies implementing a CMC material in order to reduce the intensity of the mechanical stresses to which the CMC ring sectors are subjected during the operation of the turbine.
The invention aims at proposing a turbine ring assembly allowing to maintain each ring sector in a deterministic manner, that is to say, so as to control its position and prevent it from vibrating, on the one hand, while allowing the ring sector, and by extension the ring, to deform under the effects of temperature rises and pressure variations, and this in particular independently of the interface metal parts and, on the other hand, while improving the sealing between the off-flowpath sector and the flowpath sector and while simplifying the manipulations and reducing their number for the mounting of the ring assembly.
An object of the invention proposes a turbine ring assembly comprising a plurality of ring sectors forming a turbine ring and a ring support structure, each ring sector having, according to a section plane defined by an axial direction and a radial direction of the turbine ring, a portion forming an annular base with, in the radial direction of the turbine ring, an inner face defining the inner face of the turbine ring and an outer face from which a first and a second attachment tabs protrude, the ring support structure including a central shroud from which a first and a second radial clamps protrude between which the first and second attachment tabs of each ring sector are maintained.
According to a general characteristic of the object, the turbine ring assembly comprises a one-piece annular flange removably fastened to the central shroud, the annular flange including a first free end, a second end coupled to the central shroud, a first portion extending from the first end, a second portion extending between the first portion and the second end, the first portion of the flange including a first and a second distinct tabs, the first tab bearing against the first attachment tab and the second tab being spaced apart from the first tab in the axial direction, the second tab being upstream of the first tab relative to the direction of an air flow intended to pass through the turbine ring assembly, and the second portion of the annular flange comprising a bearing shroud protruding downstream in the axial direction, the bearing shroud having a radial bearing in contact with the central shroud of the ring support structure.
In a particular embodiment, the ring sectors may be made of ceramic-matrix composite material (CMC).
The presence on the first portion of the annular flange of a second tab disposed upstream and separated from a first tab in contact with an upstream attachment tab of the ring allows providing the turbine ring assembly with an upstream tab of the annular flange dedicated to take up the force of the high-pressure distributor (DHP). The second tab upstream of the first tab of the turbine ring and free from any contact with the ring is configured to transit the maximum axial force induced by the DHP directly into the ring support structure without passing through the ring which, when it is made of CMC, has a low mechanical permissible element.
Indeed, leaving a space between the first and second tabs of the annular flange allows deflecting the force received by the second tab, upstream of the first tab which is in contact with the turbine ring, and transiting it directly toward the central shroud of the ring support structure via the second portion of the annular flange, without impacting the first tab of the annular flange and therefore without impacting the turbine ring. The first tab of the annular flange do not undergo a force, the turbine ring is thus preserved from this axial force.
The transit of the DHP force via the second tab of the annular flange can induce its tilting. This tilting can cause an uncontrolled contact between the low portions that is to say between the tabs, of the annular flange, which would have the consequence of directly transmitting the DHP force to the ring.
The downstream bearing shroud ensures higher resistance to the tilting induced by the DHP force. The bearing shroud takes up the significant tangential stresses caused by the DHP force on the upstream tab and thus limits the tilting of the annular flange. The radial bearing of the bearing shroud allows limiting the tilting of the annular flange when the DHP force transits in the flange.
In addition, the removable nature of the annular flange makes it possible to have axial access to the cavity of the turbine ring. This allows assembling the ring sectors together outside the ring support structure and then axially sliding the assembly thus assembled into the cavity of the ring support structure until bearing against the second radial clamp, before fastening the annular flange on the central shroud of the ring support structure.
During the operation of fastening the turbine ring on the support structure of the ring, it is possible to use a tool including a cylinder or a ring on which the ring sectors are pressed or sucked during their crown assembling.
The fact of having an annular flange in one piece, that is to say describing the entirety of a ring over 360°, allows, compared to a sectored annular flange, limiting the passage of the air flow between the off-flowpath sector and the flowpath sector, in so far as all the inter-sector leaks are eliminated, and therefore controlling the sealing.
The solution defined above for the ring assembly thus makes it possible to maintain each ring sector in a deterministic manner, that is to say to control its position and prevent it from starting to vibrate, while improving the sealing between the off-flowpath sector and the flowpath sector, while simplifying the manipulations and while reducing their number for the mounting of the ring assembly, and while allowing the ring to deform under the effect of temperature and pressure in particular independently of the interface metal parts.
According to a first aspect of the turbine ring assembly, the first radial annular clamp forms a first rib protruding in the radial direction of the turbine ring towards the inside of the ring, and the second end of the annular flange includes an axial abutment extending in the radial direction of the turbine ring towards the outside of the ring, the axial abutment being disposed upstream of said first radial annular clamp and bearing in the axial direction of the turbine ring against said first radial annular clamp.
The axial abutment allows pressing the annular flange onto the first radial annular clamp and thus axially positioning the first tab of the annular flange with respect to the upstream radial attachment tab of the ring.
According to a second aspect of the turbine ring assembly, the central shroud of the ring support structure may further comprise a second rib protruding in the radial direction of the turbine ring towards the inside of the ring and having a bearing surface on which the radial bearing of the bearing shroud bears, the second rib being disposed between the first and the second radial clamps of the ring support structure.
The second rib is a radial bearing point which allows the ring support structure to retain the rocker of the second tab of the annular flange when the DHP force is applied. The large distance between the axial abutment and the radial abutment of the bearing shroud allows increasing the lever arm and thus inducing a smaller radial force on the casing at contact of the radial bearing with the second rib of the ring support structure.
The annular flange is fastened by means of two radial shrink-fittings, a first shrink-fitting between the radial bearing and the second rib, and a second shrink-fitting between the surface of the axial abutment extending in a plane comprising the axial direction and the central shroud.
According to a third aspect of the turbine ring assembly, the ring sector may have an inverted Greek letter section pi (π) along the section plane defined by the axial direction and the radial direction, and the assembly may comprise, for each ring sector, at least three pins to radially hold the ring sector in position, the first and second attachment tabs of each ring sector each comprising a first end secured to the outer face of the annular base, a second free end, at least three lugs for receiving said at least three pins, at least two lugs protruding from the second end of one of the first or second attachment tabs in the radial direction of the turbine ring and at least one lug protruding from the second end of the other attachment tab in the radial direction of the turbine ring, each receiving lug including an orifice for receiving one of the pins.
According to a forth aspect of the turbine ring assembly, the ring sector may have a section with an elongated K-shape along the section plane defined by the axial direction and the radial direction, the first and a second attachment tabs having an S-shape.
According to a fifth aspect of the turbine ring assembly, the ring sector may have, on at least one radial range of the ring sector, an O-section along the section plane defined by the axial direction and the radial direction, the first and second attachment tabs each having a first end secured to the outer face and a second free end, and each ring sector comprising a third and a fourth attachment tabs each extending, in the axial direction of the turbine ring, between a second end of the first attachment tab and a second end of the second attachment tab, each ring sector being fastened to the ring support structure by a fastening screw including a screw head bearing against the ring support structure and a thread cooperating with a tapping formed in a fastening plate, the fastening plate cooperating with the third and fourth attachment tabs.
Another object of the invention proposes a turbomachine comprising a turbine ring assembly as defined above.
The invention will be better understood upon reading the following, by way of indication but without limitation, with reference to the appended drawings in which:
As illustrated in
The annular base 12 includes, along the radial direction DR of the ring 1, an inner face 12a and an outer face 12b opposite to each other. The inner face 12a of the annular base 12 is coated with a layer 13 of abradable material forming a thermal and environmental barrier and defines a flow path of gas flow in the turbine. The terms “inner” and “outer” are used herein with reference to the radial direction DR in the turbine.
The upstream and downstream radial attachment tabs 14 and 16 protrude, along the direction DR, from the outer face 12b of the annular base 12 away from the upstream and downstream ends 121 and 122 of the annular base 12. The upstream and downstream radial attachment tabs 14 and 16 extend over the entire width of the ring sector 10, that is to say, over the entire arc of circle described by the ring sector 10, or over the entire circumferential length of the ring sector 10.
As illustrated in
The second radial annular clamp 36 extends in the circumferential direction of the ring 1 and, along the radial direction DR, from the central shroud 31 towards the center of the ring 1. It comprises a first free end 361 and a second end 362 secured to the central shroud 31. The second radial annular clamp 36 includes a first portion 363, a second portion 364, and a third portion 365 comprised between the first portion 363 and the second portion 364. The first portion 363 extends between the first end 361 and the third portion 365, and the second portion 364 extends between the third portion 365 and the second end 362. The first portion 363 of the second radial annular clamp 36 is in contact with the downstream radial attachment clamp 16. The second portion 364 is thinned relative to the first portion 363 and the third portion 365 so as to give some flexibility to the second radial annular clamp 36 and thus not to stress too much the CMC turbine ring 1.
The first radial annular clamp 32 forms a first radial annular rib extending in the circumferential direction of the ring 1 as well as in the radial direction DR of the ring, from the central shroud 31 to the center of the ring 1.
As illustrated in
The first portion 353 comprises a first tab 33 and a second tab 34 distinct from the first tab 33 and distant from the latter in the axial direction DA, the second tab 34 being upstream of the first tab 33 relative to the direction of the air flow F intended to pass through the turbine ring assembly 1. When the ring assembly is mounted, the first tab 33 of the removable flange 35 bears against the upstream radial attachment tab 14 of each of the ring sectors 10 forming the turbine ring 1.
The radial holding of the ring 1 is ensured by the first tab 33 of the annular flange 35 which is pressed on the upstream radial attachment tab 14 and by the first portion 363 of the second radial annular clamp 36 which is pressed against the first downstream radial attachment clamp 16. The first tab 33 of the annular flange 35 ensures the sealing between the flowpath cavity and the off-flowpath cavity of the ring.
The second tab 34 of the removable annular flange 35 is dedicated to take up the force of the high-pressure distributor (DHP) on the removable annular flange 35, on the one hand, by deforming and, on the other hand, by transiting this force towards the casing line which is more mechanically robust, that is to say toward the line of the ring support structure 3 as illustrated by the force arrows E represented in
The first tab 33 and the second tab 34 of the removable annular flange 35 meet at the second portion 354 of the removable annular flange 35.
In the first embodiment illustrated in
The axial abutment 355 is disposed upstream of the first radial rib formed by the first radial annular clamp 32, the latter is therefore downstream of the axial abutment 355. The axial abutment 355 has an upstream face 355a receiving the gas flow F and a downstream face 355b opposite to the upstream face 355a and facing the first radial rib 312. The first radial rib 32, that is to say the first radial annular clamp, has an upstream face 32a facing the axial abutment 355 of the annular flange 35 and a downstream face 32b opposite to the upstream face 32a and facing the second radial annular clamp 36. When the turbine ring assembly is mounted, the downstream face 355b of the axial abutment 355 is bearing against the upstream face 32a of the first radial rib 32 of the central shroud 31 of the ring structure.
The axial abutment 355 has two uses. It allows, on the one hand, the axial positioning of the annular flange 35, which allows accurately adjusting the axial position of the first tab 33 with respect to the upstream radial attachment tab 14 of the ring, to ensure controlled axial contact between the two parts. The axial abutment 355 allows, on the other hand, limiting the tilting of the second tab 34 and transiting the DHP force axially on the central shroud 31 of the ring support structure 3.
Further, the second end 352 of the annular flange 35 comprises a bearing shroud 356 protruding downstream in the axial direction DA.
In other words, the annular flange 35 has an upstream face 35a receiving the gas flow F and a downstream face 35b opposite to the upstream face 35a and facing the first radial annular clamp 32 and the upstream radial attachment tab 14. The second portion 354 of the annular flange 35 comprises a bearing shroud 356 extending in the axial direction DA from the downstream face 35b of the annular flange 35.
The bearing shroud 356 has an inner face 356a and an outer face 356b opposite to the inner face 356a, a first free end 3561, and a second end 3562 secured to the downstream face 35b of the annular flange 35, the first end 3561 being downstream of the second end 3562 when the turbine ring assembly is mounted. The bearing shroud 356 comprises, on its first end 3561, a radial bearing 358 protruding from the outer face 356b of the bearing shroud 356.
In the embodiment illustrated in
When the turbine ring assembly is mounted, the outer radial face 358b of the radial bearing 358 bears against the inner radial face 314a of the second radial rib 314.
The bearing shroud 356 ensures higher resistance to the tilting induced by the DHP force. The bearing shroud 356 takes up the significant tangential stresses caused by the DHP force and thus limits the tilting of the annular flange 36.
The second embodiment illustrated in
The third and forth embodiments illustrated in
In each of the embodiments of the invention illustrated in
In the first embodiment illustrated in
In the first embodiment, for each corresponding ring sector 10, the second portion 354 of the annular flange 35 comprises two orifices 3540 for receiving the two first pins 119, and the third portion 365 of the radial annular clamp 36 comprises two orifices 3650 configured to receive the two second pins 120.
For each ring sector 10, each of the upstream and downstream radial attachment tabs 14 and 16 comprises a first end 141 and 161 secured to the outer face 12b of the annular base 12 and a second free end 142 and 162. The second end 142 of the upstream radial attachment tab 14 comprises two first lugs 17 each including an orifice 170 configured to receive a first pin 119. Similarly, the second end 162 of the downstream radial attachment tab 16 comprises two second lugs 18 each including an orifice 180 configured to receive a second pin 120. The first and second lugs 17 and 18 protrude in the radial direction DR of the turbine ring 1 respectively from the second end 142 of the upstream radial attachment tab 14 and from second end 162 of the downstream radial attachment tab 16.
The orifices 170 and 180 may be circular or oblong. Preferably, all the orifices 170 and 180 comprise a portion of circular orifices and a portion of oblong orifices. The circular orifices make it possible to tangentially index the rings and to prevent them from moving tangentially (in particular in the event of contact by the vane). The oblong orifices allow accommodating the differential expansions between the CMC and the metal. The CMC has a coefficient of expansion much lower than that of the metal. At high temperature, the lengths in the tangential direction of the ring sector and of the casing portion vis-à-vis each other will therefore be different. If there were only circular orifices, the metal casing would impose its displacements to the CMC ring, which would be a source of very high mechanical stresses in the ring sector. Having oblong holes in the ring assembly allows the pin to slide into this hole and to avoid the overstress phenomenon mentioned above. Therefore, two drilling patterns can be imagined: a first drilling pattern, for a case with three lugs, would comprise a radial circular orifice on a radial attachment clamp and two tangential oblong orifices on the other radial attachment clamp, and a second drilling pattern, for a case with at least four lugs, would comprise a circular orifice and an oblong orifice by radial attachment clamp vis-à-vis each other each time. Other appended cases may be considered as well.
For each ring sector 10, the two first lugs 17 are positioned at two different angular positions with respect to the axis of revolution of the turbine ring 1. Likewise, for each ring sector 10, the two seconds lugs 18 are positioned at two different angular positions with respect to the axis of revolution of the turbine ring 1.
As illustrated in
The radial attachment tabs 140 and 160 have a first end, referenced respectively 1410 and 1610, secured to the annular base 12 and a second free end, referenced respectively 1420 and 1620. The free ends 1420 and 1620 of the upstream and downstream radial attachment tabs 140 and 160 extend either parallel to the plane in which the annular base 12 extends, that is to say along a circular plane, or rectilinearly while the attachment tabs 140 and 160 extend annularly. In this second configuration where the ends are rectilinear and the annular attachment tabs, in the case of a possible swing of the ring during the operation, the surface bearings then become linear bearings thereby providing a greater sealing than in the case of ad hoc bearings. The second end 1620 of the downstream radial attachment tab 160 is held between a portion 3610 of the second radial annular clamp 36 protruding in the axial direction DA from the first end 361 of the second radial annular clamp 36 in the opposite direction to the flow F direction and the free end of the associated screw 38, that is to say the screw opposite to the screw head. The second end 1410 of the upstream radial attachment tab 140 is held between a portion 3310 of the first tab 33 of the annular flange 35 protruding in the axial direction DA from the first end 331 of the first tab 33 in the flow F direction and the free end of the associated screw 38.
In the third embodiment illustrated in
The axial attachment tab 17′ comprises an upstream end 171′ and a downstream end 172′ separated by a central portion 170′. The upstream and downstream ends 171′ and 172′ of the axial attachment tab 17′ protrude, in the radial direction DR, from the second end 142, 162 of the radial attachment tab 14, 16 to which they are coupled, so as to have a central portion 170′ of axial attachment tab 17′ raised relative to the second ends 142 and 162 of the upstream and downstream radial attachment tabs 14 and 16.
For each ring sector 10, the turbine ring assembly comprises a screw 19 and a fastener 20. The fastener 20 is fastened on the axial attachment tab 17′.
The fastener 20 further comprises an orifice 21 equipped with a tapping cooperating with a thread of the screw 19 to fasten the fastener 20 to the screw 19. The screw 19 comprises a screw head 190 whose diameter is greater than the diameter of an orifice 39 made in the central shroud 31 of the support structure of the ring 3 through which the screw 19 is inserted before being screwed to the fastener 20.
The bearing shroud 356 further comprises an orifice 3560 traversed by the screw 19 and by a portion of the fastener 20. The orifice 3560 has a diameter greater than that of the fastener 20.
The radial securing of the ring sector 10 with the ring support structure 3 is carried out using the screw 19, whose head 190 bears on the central crown 31 of the ring support structure 3, and the fastener 20 screwed to the screw 19 and fastened to the axial attachment tab 17′ of the ring sector 10, the screw head 190 and the fastener 20 exerting forces of opposite directions in order to hold together the ring 1 and the ring support structure 3.
The fourth embodiment illustrated in
In the fourth embodiment, the ring sector 10 is fastened directly to the bearing shroud 356 using the screw 19 and the fastening part 20. The bearing shroud 356 comprises an orifice 3560 traversed by the screw 19. The orifice 3560 has a diameter smaller than that of the screw head 190.
The radial securing of the ring sector 10 with the ring support structure 3 is carried out using the screw 19, whose head 190 bears on the bearing shroud 356 of the annular flange 35, and the fastening part 20 screwed to the screw 19 and fastened to the axial attachment tab 17′ of the ring sector 10, the screw head 190 and the fastener 20 exerting forces of opposite directions to hold together the ring 1 and the ring support structure 3.
In each of the embodiments of the invention illustrated in
The rectilinear bearings 110 allow having controlled sealing areas. Indeed, the bearing surfaces 110 between the upstream radial attachment tab 14 and the first tab 33 of the annular flange 35 on the one hand, and between the downstream radial attachment tab 16 and the second radial annular clamp 36 on the other hand, are comprised in the same rectilinear plane.
More precisely, having bearings on radial planes allows overcoming the effects of de-cambering in the turbine ring 1.
A method for producing a turbine ring assembly corresponding to that represented in
Each ring sector 10 described above is made of ceramic-matrix composite material (CMC) by formation of a fibrous preform having a shape close to that of the ring sector and densification of the ring sector by a ceramic matrix.
For the production of the fibrous preform, it is possible to use ceramic fiber yarns, for example SiC fiber yarns, such as those marketed by the Japanese company Nippon Carbon under the name “Hi-NicalonS”, or carbon fiber yarns.
The fibrous preform is advantageously made by three-dimensional weaving, or multilayer weaving with arrangement of debonding areas allowing the portions of preforms corresponding to the attachment tabs 14 and 16 of the sectors 10 to be spaced apart.
The weaving can be of the interlock type, as illustrated. Other weaves of three-dimensional or multilayer weaving can be used such as for example multi-plain or multi-satin weaves. Reference can be made to document WO 2006/136755.
After weaving, the blank can be shaped to obtain a ring sector preform which is consolidated and densified by a ceramic matrix, the densification can be achieved in particular by gas-phase chemical infiltration (CVI) which is well known per se. In a variant, the textile preform can be a little cured by CVI so that it is rigid enough to be manipulated, before raising liquid silicon by capillarity in the textile for carrying out the densification (“Melt Infiltration”).
A detailed example of manufacture of CMC ring sectors is in particular described in document US 2012/0027572.
The ring support structure 3 is for its part made of a metal material such as a Waspaloy® or inconel 718® or C263® alloy.
The production of the turbine ring assembly is continued by the mounting of the ring sectors 10 on the ring support structure 3.
For this, the ring sectors 10 are assembled together on an annular tool of the “spider” type including, for example, suckers configured to each hold a ring sector 10.
Then, the two second pins 120 are inserted into the two orifices 3650 provided in the third portion 365 of the second radial annular clamp 36 of the ring support structure 3.
The ring 1 is then mounted on the ring support structure 3 by inserting each second pin 120 into each of the orifices 180 of the second lugs 18 of the downstream radial attachment clamps 16 of each ring sector 10 forming the ring 1.
All the first pins 119 are then placed in the orifices 170 provided in the first lugs 17 of the radial attachment tab 14 of the ring 1.
Then, the annular flange 35 is fastened to the ring support structure 3 and to the ring 1. The annular flange 35 is cold-mounted on the ring support structure 3 in contact with the abutment 32. During the temperature rise of the annular flange 35, the shrink-fitting occurs at the two radial contacts.
In order to radially hold the ring 1 in position, the annular flange 35 is fastened to the ring by inserting each first pin 119 into each of the orifices 170 of the first lugs 17 of the upstream radial attachment tabs 14 of each ring sector 10 forming the ring 1.
The ring 1 is thus axially held in position using the first tab 33 of the annular flange 35 and the second radial annular clamp 36 bearing respectively upstream and downstream on the rectilinear bearing surfaces 110 of the respectively upstream 14 and downstream 16 radial attachment tabs. During the installation of the annular flange 35, an axial pre-stressing may be applied to the first tab 33 of the annular flange 35 and to the upstream radial attachment tab 14 to overcome the effect of differential expansion between the CMC material of the ring 1 and the metal of the ring support structure 3. The first tab 33 of the annular flange 35 is maintained in axial stress by mechanical elements placed upstream as illustrated in dashed lines in
The ring 1 is radially held in position using the first and second pins 119 and 120 cooperating with the first and second lugs 17 and 18 and the orifices 3540 and 3650 of the annular flange 35 and the radial annular clamp 36.
The invention thus provides a turbine ring assembly allowing to maintain each ring sector in a deterministic manner while allowing, on the one hand, the ring sector, and by extension the ring, to deform under the effects of temperature rises and pressure variations, and in particular independently of the interface metal parts and, on the other hand, while improving the sealing between the off-flowpath sector and the flowpath sector and while simplifying manipulations and reducing their number for the mounting of the ring assembly.
In addition, the invention provides a turbine ring assembly comprising an upstream annular flange dedicated to take up the DHP force and thus to induce low levels of forces in the CMC ring, a contact abutment between the annular flange dedicated to take up the DHP force and the annular flange used to maintain the ring, the abutment allowing to ensure the non-contact of the low portions of the two flanges upon tilting of the upstream flange. The turbine ring assembly according to the invention also allows controlling the rigidity at the upstream and downstream axial contacts between the CMC ring and the metal casing. As a result, the sealing is ensured in all circumstances without inducing too high axial forces on the ring.
| Number | Date | Country | Kind |
|---|---|---|---|
| 1752151 | Mar 2017 | FR | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/FR2018/050589 | 3/13/2018 | WO | 00 |
