• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    - Rotor disk with centripetal air sampling device, compressor comprising said disk and turbomachine with such a compressor. - The rotor disk (3B) for compressor comprises, with respect to the axis of rotation of the disk: - a radial web (4), vanes (8) at the outer periphery of the fabric, a bore (5) at the periphery interior of the fabric, and a cylindrical side wall (12) extending the fabric adjacent its outer periphery and having an air supply port (18), and - a centripetal air sampling device (15). Advantageously, the device (15) comprises a cylindrical support (23) and at least one air supply tube (16) whose inlet is turned towards the orifice (18) and whose outlet is turned towards the boring (5) of the fabric, and the disc comprises an internal radial flange (40) issuing from the cylindrical side wall (12), the cylindrical support (23) of the device (15) being fixed to said internal radial flange (40) , and a ring (30) from the fabric (4), the cylindrical support (23) being centered on the ring (30).
    公开号:FR3016936A1
    申请号:FR1450616
    申请日:2014-01-24
    公开日:2015-07-31
    发明作者:Nadege Hugon；Nicolas Trappier
    申请人:SNECMA SAS；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a rotor disk with a centripetal air sampling device and, more particularly, although not exclusively, to the arrangement of the device for extracting centripetal air in axial turbomachine (turboprop and turbofan) axial compressor disks. dimension. Generally, the axial compressors, in which circulates the air stream entering the turbomachine, comprise a plurality of coaxial and alternating stages of rotor disks and paddle stator, the latter being traversed by the air stream to be compressed. circulating from upstream to downstream of the engine to go to the combustion chamber thereof. A schematic representation of an axial compressor 2 of turbomachine 1 A axis is illustrated with reference to Figure 1 with its magnifying glass L, the stator vanes having been removed. Such a representation corresponds to that of document FR-2825413 of the applicant. The rotor disks 3 each comprise an annular radial web (or web) 4 with, at its inner periphery, a central bore 5 traversed by the turbine shaft 6 of the turbomachine, for example, a rim 7 terminating the outer periphery of the turbine. 4, and the corresponding blade 8 attached to the rim 7. In order to coaxially associate the rotor disks 3, the latter are made integral by bolt-type connection means 10A fixing, in this embodiment, flanges 11 which terminate cylindrical side walls 12 disks, to the webs 4 adjacent disks. The assembly of the walls 12 thus assembled forms an internal continuous wall delimiting the flow of the air stream 13.
    [0002] In the annular cavity 14 delimited by two consecutive rotor disks of the compressor 2, respectively upstream 3A and downstream 3B (see magnifying glass L) in the direction of the air flow F in the vein 13, the sampling device is then provided. centripetal air 15 which serves to provide ventilation or cooling of certain parts of the turbomachine 1 such as, for example, the ventilation of the high pressure turbine, the ventilation of the bores of the high pressure compressor discs, the pressurization of the lubrication chambers, the ventilation of the low pressure turbine, etc ... This ventilation is advantageously from the internal air flow F of the motor flowing in the vein 13. For this, as shown in particular by the magnifying glass L of Figure 1, the device 15 comprises tubes 16 communicating at their inlets 17 with the air stream 13 through at least one orifice 18 provided in the cylindrical side wall 12 of the downstream disc 3B, and at their outlets 19 located in the vicinity of the central bores of the disks, with the turbine shaft 6 to ventilate. The tubes 16 are arranged substantially radially and are carried by a cylindrical support 23 of the device, which is integral with the disks. In this way, part of the flow of fresh air F flowing in the vein 13 engulfs, centripetally and through the orifices 18, in the internal passages 20 of the radial tubes 16, to be distributed towards the shaft 6 and axially along it to the turbine for cooling, as shown by the arrows F1 in Figure 1.
    [0003] In the type of motor of FIG. 1 (such as a turbojet engine), because of its large dimensions, the air sampling device 15 can be arranged relatively easily in the chosen interdisc cavity, and linked to the disks of the compressor, bolts 10A being thus used as connecting means 10 of the two consecutive bladed disks.
    [0004] However, in the case of smaller size engines with smaller compressors and less accessible parts, the air sampling device is more difficult to mount in the interdiscque cavity then reduced, despite the fact that we use as connection means 10 between the consecutive disks, toothed or gear-coupled connection means (referred to in English as "curvic coupling" and described for example in FR-2952138). This is particularly the case of the turboprop compressor 2 partially shown in FIG. 2, in which identical references designate elements similar to those of FIG. 1. These toothed connection means 10 make it possible to reduce the axial space requirement compared to the means connection 10 by bolts 10A and flanges, since the cylindrical walls 12 of the disks are directly engaged by conical teeth 10B and 10C, as shown in Figure 2, while not weakening the disks. Indeed, it weakens the latter when pierced in order to fix the flanges so that thicker discs are needed, which weighs on other parameters. The conical teeth ensure the rotational drive and coaxiality of all the discs 3 of the compressor. A generally conical toothing 10B terminates the transverse free end of the cylindrical lateral wall 12 of a disc and meshes with a complementary toothing 10C terminating the transverse free end of the side wall facing the disc to be associated. Note, moreover, the air supply port 18 of the vein, formed in the cylindrical wall 12 of the downstream rotor disc 3B, and the stator 21 coming into contact with a seals device with an abradable material 22, provided in correspondence of the cylindrical wall 12 of the rotor disk. In the representation of Figure 2, the air sampling device 15 comprises a cylindrical support 23 which is previously mounted on an annular flange 24 perpendicularly projecting from the radial web 4 of the upstream disk 3A, being located near the central bore 5. The support 23 is fixed to the flange 24 by bolts 25. The radial air supply tubes 16 are then mounted through facing holes 26, 27 provided in the support 23 and the flange 24 to radially open in the annular cavity 14 of the disks 3A, 3B between the webs 4 and coming, by their inputs 17, near the side wall 12 of the disks and, by their outputs 19, near the central bores opposite the shaft of turbine to ventilate. A locking means 28 maintains the air sampling tubes 16 in the support 23 and the flange 24. In addition, in the downstream disc is provided an annular ring or flange 30 perpendicularly projecting from the radial fabric 4 and in which engages the support 23 for purposes of centering the latter. Thus, the sampling device is attached to one of the disks and centered on the other disk.
    [0005] Although the realization of the air sampling device with such a rotor disc compressor with toothed connections is technically possible, it nevertheless has drawbacks.
    [0006] Firstly, since the device is attached to one of the disks and then centered on the other disk, the mounting of it is delicate, tedious, and takes a while. Moreover, since the webs of the compressor rotor disks are of limited thickness for this type of compact motor, the centripetal air sampling device tends to generate stresses in the upstream rotor disk to which it is attached. so that over-stresses can appear in the disk, which is undesirable. In addition, this may lead to a deterioration of the centering at the device and the downstream rotor disc, the centering between them likely to "open", resulting in the appearance of leaks at this level. As there are potential leaks, it is necessary to over-size the air intake, which then reduces the performance of the engine because the air taken is extracted from the main vein. Moreover, with such an embodiment (FIG. 2), it is impossible to directly machine the diametrically opposed teeth of the toothed connection of the upstream disk by the presence of the projecting annular flange 24 of the fabric used for fixing the support of tubes. Indeed, this flange extends, in radial projection on the axis A, well beyond the teeth 10B of the connecting means 10. Thus, tooth-to-tooth machining is necessary, which implies a machining time. longer and additional costs. The present invention aims to overcome the above drawbacks and concerns a compressor rotor disk, the design of which makes it possible to easily mount the centripetal air sampling device, to improve the mechanical strength of the disk, to reduce the risks of leakage and machining diametrically teeth curvic connections of the two disks enclosing the sampling device. For this purpose, the rotor disc, particularly for a compressor, comprises, with respect to the axis of rotation of the disc: a radial web, vanes at the outer periphery of the fabric, a bore at the inner periphery of the fabric, and a cylindrical side wall extending the fabric in the vicinity of its outer periphery and having an air supply port, and - a centripetal radial air sampling device. According to the invention, the rotor disk is remarkable in that the air sampling device comprises a cylindrical support and at least one air supply tube whose inlet is turned towards the supply orifice. of air and whose outlet is turned towards the bore of the fabric, and that it comprises an internal radial flange from the cylindrical side wall, the cylindrical support of the device being fixed to said internal radial flange, and a crown of the fabric, the cylindrical support being centered on the crown. Thus, thanks to the invention, instead of coming to clamp the air sampling device on one of the two consecutive rotor disks and to center on the other rotor disk, the device is fixed and s' applies only on one of the rotor discs, which on the one hand facilitates assembly operations (and disassembly) of said device and the intervention on inaccessible parts and, on the other hand, to stiffen the assembly disc-device by distributing the best efforts passing through them. Indeed, the centrifugal force created by the device is taken up by its fixing and its centering on the same disk. In addition, the air sampling device is reported, in full, in the internal space defined by the fabric and the side wall of the disc, so that the axial space is consequently necessarily reduced, which is advantageous for engines of contained dimension. Note also the structurally simple and reliable mounting of the device on the disc, by fixing it on the radial flange (via clamping means) and centering it in the disc crown, while being housed in the internal space of the disc.
    [0007] According to another characteristic, the cylindrical side wall is provided, at its free end, toothed connection means, said fixing flange being located (axially offset) of the tooth connection means. Thus, the internal space of the disc above the connection means is free, so that one can perform the diametrical machining of the teeth of this disc.
    [0008] Advantageously, locking means are provided between the cylindrical support of the air sampling device and the centering ring of the radial web. The support of the sampling device, thus adjusted and locked, therefore remains in contact with the ring gear reducing the risk of leakage, which avoids oversizing the air intake and maintain the performance of the engine. For example, the locking means are defined by at least one axial lateral slot formed in the centering ring of the disc and ending in an angular slot, and by a radial lug protruding from the cylindrical support and successively engaging in the slots , locking the support in the crown of the veil. In addition, the internal radial clamping flange is attached by welding to the side wall of the disc. This is particularly advantageous for engines of reduced size for which machining difficulties may be otherwise encountered. Preferably, vibratory damping means is provided between the air supply tube and the support of the air sampling device.
    [0009] In particular, the damping means comprises a split tube with elastically deformable petals engaging in the air supply tube to be applied against it and absorb the vibrations, the assembly "supply tube d air and damper tube "being held in the holder of the air bleeding device.
    [0010] Moreover, to ensure efficient and homogeneous cooling, said air sampling device comprises a plurality of air supply tubes arranged substantially radially in receiving holes of the cylindrical support, and regularly distributed angularly around it . The invention also relates to a compressor comprising: - coaxial rotor disks each having a radial web, vanes at the outer periphery of the fabric, traversed by an air stream, and a bore at the inner periphery of the fabric, said disks being rotatably associated by tooth connection means terminating cylindrical sidewalls discs, and - a centripetal air sampling device arranged between the webs of two consecutive discs and bringing air from the vein towards the bores.
    [0011] Advantageously, the compressor is remarkable in that said device for extracting centripetal air is reported, in its entirety, in the internal space between the fabric and the side wall of one of said consecutive disks in the manner defined herein. above, with the tooth connection means of the disc projecting from the attached device, and in that the internal space of the other of said consecutive discs, delimited by the side wall with toothed connection means, is free, devoid of obstacles, at least in line with its toothed connection means. Thus, by fixing and centering the device on the same disk, the fixing flange as described with reference to FIG. 2 is omitted and the diametrical machining of the teeth of the toothed connection (curvic) of the rotor disk in question can be eliminated. to be done directly, as well as that of the disc with the air intake device reported, since the latter is not in line with the tooth connection means.
    [0012] Preferably, with respect to the direction of flow of the air stream, the centripetal air sampling device is integral with the downstream disk of the two consecutive disks, respectively upstream and downstream. The invention also relates to a turbomachine for an aircraft, of the type comprising at least one axial compressor with an air sampling device, a combustion chamber and a turbine. Advantageously, the axial compressor is as defined above. The figures of the appended drawing will make it clear how the invention can be realized. In these figures, identical references designate similar elements.
    [0013] FIG. 1 is a longitudinal and schematic half-section of a high-pressure axial compressor for a turbomachine with rotor disks associated by bolt connection means and a centripetal radial air sampling device, in accordance with the prior art described above. FIG. 2 is a longitudinal and schematic half-section of a part of a turbomachine compressor with rotor discs associated by tooth connection means and a centripetal radial air sampling device, according to the prior art described above.
    [0014] Figure 3 is a view similar to Figure 2 with, according to the invention, the arrangement of the centripetal air sampling device in one of the compressor discs. Figure 4 shows the air bleeding device of Figure 3 before mounting on the downstream disk concerned. Figure 5 shows the two rotor disks separated with the toothed connections for their diametrical machining. Figures 6a, 6b and 6c show the assembly with centering and locking of the air bleeding device on the downstream disk of the compressor.
    [0015] As shown in FIGS. 3 and 4, the centripetal air sampling device 15 is housed in the respective interdiscal annular cavity 14 of the compressor 2 and, according to the invention, is attached to one of the two rotor disks. respectively upstream 3A and downstream 3B delimiting the cavity, in this case in the internal space 14B of the downstream disk 3B in the embodiment shown. For this, the downstream disk 3B includes the air sampling device 15 which comprises a cylindrical support 23 in the orifices 26 which are radially mounted air supply tubes 16 identical to each other. For example, four air supply tubes may be provided at 90 ° from each other to ensure a suitable air supply to the bore of the discs in which the turbine shaft to be cooled. A different number of tubes is of course possible. Each sampling tube or air intake tube 16 terminates at its outlet 19 by a base 31 which abuts against an annular portion 32 of the cylindrical support 23.
    [0016] In the internal passages 20 of these air sampling tubes arranged radially with respect to the axis A of the engine, are engaged damping means 29 such as damping slotted tubes with petals 33 intended to absorb, by means of elasticity of the petals applying against the wall of the respective tubes 16, the centrifugal effect and vibrations occurring during operation of the engine. Each damping tube 33 also ends with a base 34 which is pressed against the base 31 of the sampling tube 16. The set of pairs of tubes 16-33 is held axially in position in the holes 26 of the support 23 by any appropriate locking means 28 such as a circlip type ring disposed in the support and preventing the exit of the tubes to the inside of the compressor. The cylindrical support 23 has, on the side intended to be turned towards the upstream disk 3A, a substantially flat part 35 extending radially outwards from the annular part 32 with, in the vicinity of its periphery, holes 36 in which are adapted to engage bolts 37. In Figure 4, we see that the screw 38 of the bolt 37 shown is mounted in the hole concerned and that the nut 39 is placed against an inner radial flange 40 of the downstream disc 3B, this flange is intended for fixing the device 15 on the disk 3B and it comes perpendicularly from the cylindrical side wall 12 of the latter. In Figure 3, the nut 39 of the bolt 37 is mounted on the screw 38 immobilizing the sampling device 15 on the upstream disk. On the side intended to be turned towards the downstream disk 3B, the cylindrical support 23 has an outer annular flange 41 on which we will return and which is intended to cooperate, for centering and locking purposes, with the crown 30 issuing perpendicularly from the radial web 4 of the downstream rotor disk 3B. As shown more particularly in FIGS. 4 and 5, in the internal space 14B of the downstream disc, delimited by the cylindrical lateral wall 12 and the radial web 4 of said disc, will be housed, in its entirety, the sampling device 15. For this, the inner radial flange 40, of annular shape, is arranged close to the toothing 10C of the connecting means 10 of the downstream disc and it projects radially inwardly of the side wall, in the internal space 14B. . It can be seen, particularly in FIG. 5, that the machining of the teeth, two to two diametrically opposite, toothed connection means 10 does not pose any problems, neither for the teeth 10C of the downstream disc 3B, nor for the teeth 10B of the upstream disk 3A, because the internal spaces, in line with the teeth 10B, 10C, are empty, free of obstacles. Indeed, with respect to the radial plane PR delimiting the meshing of the two toothing of the connecting means 10, it can be seen that the fastening flange 40 of the downstream disk, situated in the space 14B, is axially offset towards the right of the plane PR. and is therefore not under the teeth 10C, and that the internal space 14A of the upstream disk is now free of flanges or any other obstacle, internally to the teeth 10B of the connecting means, in particular at the base of the teeth 10B thereof. The upstream disk 3A comprises only the radial web 4 and the cylindrical side wall 12 at the free end of which are formed the teeth 10B of the connection. This also makes it possible to limit the interdiscos cavity 14, corresponding to the two spaces 14A, 14B together, to the right axial dimension (length) necessary for the connection and the integration of the sampling device 15 into the space 14B of the 3B downstream disk, resulting in a reduced, optimized size of it. The arrangement of the device 15 in this disc is shown in detail with reference to FIG. 3. It can be seen, on the one hand, that the radial portion 35 of the cylindrical support 23 is applied against the flange 40 while engaging under the side wall 12 of the downstream disc 3B, with fixation of the support to the disc by the bolts 37, and secondly, that the annular flange 41 of the annular portion 32 of said support engages simultaneously in the crown 30 from the fabric of the 3B disk, which ensures not only the adjusted centering of the set "device-disk", but also the locking thereof by means 42 described below. Such a simplified mounting design of the air bleed device 15 fully reported in the internal space 14B of only one of the disks further allows to stiffen the device itself and the associated disks. The centrifugal force generated by the device 15 during the operation of the engine 1 is partly taken up by the radial annular clamping flange 40 and partly by the ring 30 serving as a centering bearing, so that the risks of stress in the disk (especially the canvas) are greatly reduced. The passage of PE forces in the disk and the device is shown in broken lines in Figure 3.
    [0017] It is also emphasized that the flange 40 is attached by welding inside the side wall 12 of the disc 3B, which is easier than a machining realization given the compact size of the engine. The welding is performed after the machining of the rotor disc and, since it is not located in a zone of significant effort, the mechanical strength of the disc is not affected. Welding is easier to control. The locking means 42 between the support 23 and the downstream disk 3B are advantageously of bayonet or dog type ensuring the maintenance of the centering by preventing it from "open". For this, as shown in Figure 6a, at least one lateral slot 43, parallel to the axis A, is formed in the thickness of the ring 30, which lateral slot 43 is extended and terminates in a blind slot 44 , bent at right angles to the axial slot 43. On the flange 41 of the annular portion 32 of the support is then provided at least one radial lug 45, similar in size to the width of the slots and which is intended to come s' engage successively in these. In practice, FIG. 6b shows, according to the arrow F2, the radial lug 45 of the cylindrical support 23 of the centripetal device facing the lateral slot 43 of the ring, and the annular portion 32 of the support is axially introduced into the ring until at the moment when the lug 45 reaches the bottom of the lateral slot 43. Then, FIG. 6c, the device 15 is rotated angularly along the arrow F3 so that the lug 45 moves in the angular slot 44 until that it comes to a stop against the bottom of it. The centripetal device 15 is then prevented from dissociating from the downstream disk 3B and an always optimal centering of the part 32 of the support 23 in the ring 30 is ensured with a maximum reduction of the risks of leakage at this level. The flat part 35 of the support facing the annular flange 40 of the downstream disc, is stopped in rotation by the bolts 37, which ensures the immobilization of the sampling device 15 in the internal space 14B of the 3B downstream disk. Thus, a preassembled assembly "centripetal device 15 - downstream rotor disk 3B" ready to cooperate with the upstream rotor disk 3A by the toothed connections 10 is obtained.
    [0018] By such an axial compressor design with centripetal radial cooling device reported on a single disk, it can also be noted that, as the centering is maintained between the two disks by limiting the risk of leakage, the removal of air from the vein of the compressor can be reduced. In addition, as the connection between the two discs is more rigid, with better disc dynamics, the disc web can remain thin, implying a gain in mass.
    权利要求:
    Claims (11)
    [0001]
    REVENDICATIONS1. Rotor disk, particularly for a compressor, comprising, with respect to the axis of rotation of the disk: - a radial web (4), vanes (8) at the outer periphery of the web, a bore (5) at the inner periphery of the web the fabric, and a cylindrical side wall (12) extending the fabric in the vicinity of its outer periphery and having an air supply port (18), and - a centripetal radial air sampling device (15), characterized in that the air sampling device (15) comprises a cylindrical support (23) and at least one air supply tube (16) whose inlet is turned towards the supply port of air (18) and whose outlet is turned towards the bore (5) of the fabric, and that it comprises an internal radial flange (40) issuing from the cylindrical side wall (12), the cylindrical support (23) of the device (15) being attached to said inner radial flange (40), and a ring (30) issuing from the wire (4), the cylindrical support (23) ) being centered on the crown (30).
    [0002]
    2. Disc according to claim 1, wherein the cylindrical side wall (12) is provided at its free end with toothed connection means (10C), said fixing flange (40) being set back from the connecting means 2 0 toothed.
    [0003]
    3. Disk according to one of claims 1 or 2, wherein locking means (42) are provided between the cylindrical support (23) of the air sampling device and the crown (30) of centering of the radial fabric. .
    [0004]
    A disc according to claim 3, wherein the locking means (42) is defined by at least one axial side slot (43) in the centering ring (30) of the disc and terminating in an angular slot ( 44), and by a radial lug (45) protruding from the cylindrical support (23) and engaging successively in the slots, locking the support in the crown of the fabric. 30
    [0005]
    5. Disc according to one of claims 1 to 4, wherein the radial inner clamping flange (40) is attached by welding to the side wall (12) of the disc.
    [0006]
    6. Disc according to one of claims 1 to 5, wherein a vibratory damping means (29) is provided between the air supply tube (16) and the support (23) of the sampling device of air.
    [0007]
    7. Disc according to claim 6, wherein the damping means comprises a split tube (33) with elastically deformable petals engaging in the air supply tube (16) to be applied against it and absorb the vibrations, the assembly "air intake tube and damper tube" being maintained in the support of the air bleed device.
    [0008]
    8. Disc according to one of claims 1 to 7, wherein said air sampling device (15) comprises a plurality of air supply tubes (16) arranged substantially radially in receiving holes of the cylindrical support (23), and regularly angularly distributed around it.
    [0009]
    Compressor comprising coaxial rotor disks (3) each having a radial web (4), vanes (8) at the outer periphery of the web, traversed by an air stream, and a bore (5) at the inner periphery. of the web, said disks being rotationally associated by tooth-connecting means (10) terminating cylindrical side walls of the disks, and one (3B) of said disks being defined according to one of claims 1 to 8, characterized by the fact that: - said centripetal air sampling device (15) is arranged between the webs of two consecutive disks (3A, 3B), - said centripetal air sampling device (15) is reported, in its entirety, in the inner space (14B) between the fabric and the side wall of the disc (3B) comprising said insert (15), the tooth connection means (10C) of said disc (3B) protruding from said insert (15) , and - the inner space (14A) of the other (3A) of said consecutive discs, delimited by the side wall with toothed connection means, is free, free of obstacles, at least vertically above its tooth connection means (10B).
    [0010]
    10. The compressor according to claim 9, wherein, with respect to the direction of flow of the air stream (13), the centripetal air sampling device (15) is integral with the downstream disk (3B) of the two consecutive disks. , respectively upstream and downstream.
    [0011]
    11. Turbomachine for an aircraft, of the type comprising at least one axial compressor (2) with an air sampling device (15), a combustion chamber and a turbine, characterized in that the axial compressor (2) is such that defined by any one of claims 9 to 10. 10
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    同族专利:
    公开号 | 公开日
    GB2537293B|2020-05-27|
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    FR3016936B1|2019-05-17|
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    FR3073560B1|2017-11-10|2020-11-20|Safran Helicopter Engines|AIRCRAFT TURBOMACHINE MONOBLOC WHEEL|
    FR3077327B1|2018-01-30|2020-02-21|Safran Aircraft Engines|TURBOMACHINE TURBINE ASSEMBLY COMPRISING A MOBILE SEAL|
    FR3081027B1|2018-05-09|2020-10-02|Safran Aircraft Engines|TURBOMACHINE INCLUDING AN AIR TAKE-OFF CIRCUIT|
    US10954796B2|2018-08-13|2021-03-23|Raytheon Technologies Corporation|Rotor bore conditioning for a gas turbine engine|
    法律状态:
    2015-01-16| PLFP| Fee payment|Year of fee payment: 2 |
    2016-01-12| PLFP| Fee payment|Year of fee payment: 3 |
    2016-05-06| RM| Correction of a material error|Effective date: 20160404 |
    2017-01-13| PLFP| Fee payment|Year of fee payment: 4 |
    2017-12-21| PLFP| Fee payment|Year of fee payment: 5 |
    2018-02-02| CD| Change of name or company name|Owner name: SAFRAN AIRCRAFT ENGINES, FR Effective date: 20170719 |
    2018-12-20| PLFP| Fee payment|Year of fee payment: 6 |
    2019-12-19| PLFP| Fee payment|Year of fee payment: 7 |
    2020-12-17| PLFP| Fee payment|Year of fee payment: 8 |
    2021-12-15| PLFP| Fee payment|Year of fee payment: 9 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1450616A|FR3016936B1|2014-01-24|2014-01-24|ROTOR DISK HAVING A CENTRIFIC AIR LEVELING DEVICE, COMPRESSOR COMPRISING SAID DISK AND TURBOMACHINE WITH SUCH A COMPRESSOR|
    FR1450616|2014-01-24|FR1450616A| FR3016936B1|2014-01-24|2014-01-24|ROTOR DISK HAVING A CENTRIFIC AIR LEVELING DEVICE, COMPRESSOR COMPRISING SAID DISK AND TURBOMACHINE WITH SUCH A COMPRESSOR|
    PCT/FR2015/050135| WO2015110751A1|2014-01-24|2015-01-20|Rotor disk having a centripetal air collection device, compressor comprising said disc and turbomachine with such a compressor|
    GB1612128.7A| GB2537293B|2014-01-24|2015-01-20|Rotor disk having a centripetal air collection device, compressor comprising said disc and turbomachine with such a compressor|
    US15/111,314| US10598096B2|2014-01-24|2015-01-20|Rotor disk having a centripetal air collection device, compressor comprising said disc and turbomachine with such a compressor|
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