• 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:
    Assembly for a turbine engine bearing oil chamber (2), comprising a housing (1), a shaft (4) rotatably mounted relative to the housing (1) by means of a bearing (8), and having an upstream end and a downstream end with respect to the direction of flow of the air, the shaft (4) having a first bearing surface (30) and a shoulder (34) extending radially with respect to an axis of rotation (A ) of the shaft (4), an annular gear (5) arranged around the shaft (4) and having a radial surface (5a) mounted to bear against the first bearing surface (30), a joint track (26) disposed about the shaft (4) downstream of the bearing (8), having a downstream end (26b) and a track nut (26c) for securing the seal track (26) to the annular gear (5). ), the bearing (8) being arranged around the annular gear (5) and held axially between an upstream stop (5b) of the annular gear (5), and the track nut (26c), the downstream end (26b) udder said seal (26) being disposed opposite the shoulder (34) along the axis (A) so that a non-zero axial functional clearance (J) exists between said downstream end (26b) and said second surface (d). support (34), so that the shaft (4) does not exert axial compression on the joint track (26).
    公开号:FR3066549A1
    申请号:FR1754336
    申请日:2017-05-17
    公开日:2018-11-23
    发明作者:Serge Rene Morreale；Jean-Christophe DUFFET；Nora Lamharess-Chlaft
    申请人:Safran Aircraft Engines SAS；
    IPC主号:
    专利说明:

    FIELD OF THE INVENTION The present description relates to the general field of rolling bearing oil enclosures for a turbomachine. It relates more precisely to an improved assembly of the various elements of these enclosures.
    STATE OF THE PRIOR ART In a known manner, a turbomachine comprises a certain number of rolling bearings which are intended to rotationally support the rotor of the turbomachine, in particular relative to a fixed support such as the casing thereof .
    In operation, oil is typically injected onto the bearings of these bearings so as to lubricate and cool them. To prevent oil from spreading throughout the engine, it is necessary to confine the rolling bearings inside oil chambers and to ensure that these oil chambers are sealed compared to oil chambers. air close to the engine which must be free of oil.
    More specifically, certain oil enclosures are delimited between the shaft supported in rotation by the rolling bearing and an annular cover secured to a fixed support linked to the turbomachine casing and arranged around the shaft. A dynamic annular seal is generally positioned between the shaft and the cover to ensure a seal between the oil enclosure and an air enclosure adjacent to the latter. Typically, the dynamic seal is mounted inside a flange itself fixed on the cover.
    The dynamic seals typically used in rolling bearing oil chambers for a turbomachine are segmented radial seals (JRS), comprising a plurality of ring segments distributed circumferentially around a track of rotating joint with the shaft rotor. These segments are in sliding contact with the joint track. The friction between the joint segments and the joint track generates heat which must be removed in order to maintain the mechanical integrity of these elements. To do this, one technique is to circulate cooling oil along the inner wall of the seal track. To obtain effective cooling of the segment / joint track contact, it is therefore necessary for the joint track to have a high thermal conductivity. This is why the thickness of the joint track, in the radial direction, is relatively thin. Consequently, the latter is liable to deform under the effect of axial stresses. These deformations (called barreling) risk damaging the sliding joint / track contact and premature wear of the joint, which could degrade the tightness of the enclosure.
    There is therefore a need for a simple and inexpensive device for limiting these constraints, and therefore ensuring the tightness of the enclosure.
    PRESENTATION OF THE INVENTION The present disclosure relates to an assembly for an oil chamber of a turbomachine bearing, comprising:
    a housing;
    a shaft mounted to rotate relative to the casing by means of a bearing, and having an upstream end and a downstream end relative to the direction of flow of the air, the shaft comprising a first bearing surface and a shoulder s 'extending radially with respect to an axis of rotation of the shaft;
    an annular pinion disposed around the shaft and having a radial surface mounted to bear against the first bearing surface;
    a seal track arranged around the shaft downstream of the bearing, comprising a downstream end and a track nut making it possible to fix the seal track to the annular pinion;
    the bearing being disposed around the annular pinion and held axially between an upstream stop of the annular pinion, and the track nut;
    the downstream end of the joint track being disposed opposite the shoulder along the axis so that a non-zero axial functional clearance exists between said downstream end and said second bearing surface, so that the he shaft does not exert axial compression on the joint track.
    In the present description, the terms "radially" and "axially", or "radial" and "axial" are considered along the axis of rotation of the shaft. Thus, by “held axially”, it is understood that the bearing cannot move along the axis of rotation of the shaft. Furthermore, "upstream" and "downstream" are considered according to the direction of flow of the air in the turbomachine.
    By “mounted in abutment against the first bearing surface”, it is understood that there is a contact surface between the radial surface of the annular pinion and the first bearing surface, and that the radial surface presses on the first bearing surface in the upstream-downstream direction.
    This device allows to keep a functional clearance between the downstream end of the seal track and the shaft, so that the downstream end of the seal track can not come into abutment on the shaft. The presence of this functional clearance makes it possible not to stress the joint track in compression. Thus, this functional clearance makes it possible to avoid any deformation of the joint track in the radial direction (rollover), due to axial compression stresses. This allows not to damage the contact between the seal track and a dynamic annular seal, when the device is mounted in a turbomachine, and thus to maintain a good seal of the enclosure.
    In some embodiments, the annular gear can be a bevel gear.
    In some embodiments, the axial functional clearance (J) is at least 0.5 mm, preferably greater than 2 mm.
    In some embodiments, the first bearing surface is located on an upstream side of the bearing, and a second bearing surface of the shaft is located on a downstream side of the bearing, the annular pinion being mounted in abutment against the first bearing surface, or against the second bearing surface, the second bearing surface being located axially between the first bearing surface and the shoulder.
    In some embodiments, the radial surface is oriented downstream, and the first bearing surface is oriented upstream. Consequently, when the annular pinion is mounted in abutment against the first bearing surface, the radial surface exerts on the first bearing surface a force in the upstream-downstream direction.
    In some embodiments, the device comprises an adjustment shim disposed around the shaft, and interposed axially between the first bearing surface and the radial surface of the annular pinion.
    The radial surface of the annular pinion is therefore not mounted to bear directly on the first bearing surface, but on the adjustment shim, the latter being mounted to bear against the first bearing surface. This adjustment shim allows the annular pinion to be positioned axially with respect to the shaft, and thus to ensure good quality meshing between the annular pinion and another annular pinion linked to a radial shaft of the turbomachine. The wedge also makes it possible to prevent the annular pinion from moving axially, from upstream to downstream, relative to the shaft. Furthermore, the axial stresses applied to the annular pinion will be neutralized by the adjustment shim and will then propagate in the shaft, but cannot be transmitted to the joint track.
    In some embodiments, the adjustment shim is interposed axially between the track nut and the second bearing surface of the shaft.
    In some embodiments, an upstream nut is mounted in abutment against the annular pinion, so that the annular pinion is held axially between the upstream nut and the first bearing surface.
    In some embodiments, the device is configured so that cooling oil flows along the shaft in a first axial direction between the shaft and the annular pinion. The first axial direction corresponds to a direction in which the cooling oil flows in the upstream-downstream direction.
    In certain embodiments, the seal track is a cylinder comprising an axial orifice, the assembly being configured so that the cooling oil flows in the axial orifice, in a second axial direction opposite to the first axial direction.
    The second axial direction corresponds to a direction in which the cooling oil flows in the downstream-upstream direction. The joint track can be a cylindrical tube enveloping the shaft and the annular pinion. The orifice can be made in the thickness of the cylinder, along the axis of the latter. The flow of oil along the seal track allows, when the device is mounted in a turbomachine, to cool the sliding contact seal track / annular seal by thermal conduction in the wall of the seal track. This makes it possible to limit the deformations of the joint track due to thermal stresses.
    In some embodiments, the shaft has an annular groove and a seal arranged in the annular groove, and compressed between the shaft and the seal track.
    The seal can be an O-ring. The presence of this O-ring makes it possible to seal the contact between the seal track and the shaft, so as to avoid any leakage of oil in the turbomachine.
    The present description also relates to a turbomachine comprising the device according to any one of the preceding embodiments.
    BRIEF DESCRIPTION OF THE DRAWINGS The present description and its advantages will be better understood on reading the detailed description given below of various embodiments given by way of nonlimiting examples. This description refers to the pages of attached figures, on which:
    - Figure 1 shows a schematic sectional view of an assembly for an oil chamber according to one embodiment;
    - Figure 2 shows a schematic sectional view of an assembly for oil enclosure according to another embodiment;
    DETAILED DESCRIPTION OF EXAMPLES OF EMBODIMENT FIGS. 1 and 2 schematically and partially represent an assembly comprising an oil chamber 2 of a turbomachine bearing to which such an assembly applies.
    This oil enclosure 2 is delimited, on the inside, by a shaft 4 (or shaft journal) rotating around an axis X, and on the outside by an annular cover 6 which is secured to a support fixed linked to the casing 1 of the turbomachine and which is arranged around the shaft 4. The device further comprises a bevel gear 5 disposed around the shaft 4 coaxially therewith, and driven in rotation by the latter by through grooves 5d. The bevel gear 5 also has an oil passage 5e for injecting cooling oil between the bevel gear 5 and the shaft 4.
    The oil enclosure 2 contains a bearing 8 comprising a plurality of rolling elements 10 engaged between an internal ring 12 mounted on the shaft 4 of the turbomachine and an external ring 14 secured to a casing 1 of the turbomachine (not shown in the figure). In the example illustrated in the figures, the rolling elements 10 are ball bearings. However, the assembly for oil chamber of this presentation applies to all types of bearings.
    Furthermore, oil is injected into the oil chamber 2 in order to lubricate and cool the rolling elements 10 of the bearing. To this end, oil circulates from upstream to downstream inside axial conduits produced along the shaft 4 and opening radially at the level of the rolling elements 10 by passing through the internal ring 12 of the bearing ( the path T of the oil is illustrated by arrows in Figures 1 and 2).
    The oil enclosure 2 comprises a sealing device intended to seal this oil enclosure relative to an adjacent air enclosure 20 which must be free of oil.
    To this end, the sealing device comprises in particular a dynamic annular seal 22. Typically, this dynamic seal 22 is composed of carbon ring segments. The dynamic seal 22 is held in an annular flange 28 itself mounted inside the cover 6. The flange 28 has a portion 28a of L-shaped section which receives the dynamic seal 22. The dynamic annular seal 22 is associated to a rotating seal track 26 and carried by the shaft 4. The seal track 26 has a contact surface 26a, in sliding contact with the dynamic annular seal 22. The contact surface 26a of the seal track 26 is treated to improve joint / track slip and minimize wear on the dynamic annular seal 22. In its path T, the oil also flows from downstream to upstream along an internal face of the joint track 26, in particular by passing through an orifice 26d made in the thickness of the joint track 26. This makes it possible to limit heating caused by the sliding joint / track contact. The oil is then injected into the oil chamber 2. This device also makes it possible to minimize the section between the seal and the seal track. The sealing device also includes a labyrinth seal 23 disposed downstream of the dynamic seal 22 between the shaft 4 and the cover 6, on a shoulder 34 of the shaft 4.
    To limit oil leakage through the sealing device, a twist 28b is arranged upstream of the dynamic seal 22 and carried by the flange 28. The twist 28b is also positioned opposite the seal track 26, and is intended to remove oil droplets from the sealing device. To avoid oil splashes directly on the sealing device or on the spin 28b, there is a drop lance 18, carried by the seal track 26. The drop lance 18 makes it possible in particular to centrifuge the cooling oil of the seal dynamic 22 towards the largest internal radius of the oil chamber and deflecting the oil particles. The seal track 26 is of annular shape and arranged around the shaft 4. It also has a fine portion extending axially between the drip lance 18 and a downstream end 26b. The seal track 26 further comprises a portion forming a track nut 26c, located on an upstream side of the seal track 26, and making it possible to secure the seal track 26 to the bevel gear 5. The track nut 26c also makes it possible to limit the axial displacements of the bearing 8 relative to the bevel gear 5, by tightening the bearing 8 against an intermediate shim 64 disposed between the bevel gear 5 and the bearing 8, upstream of the latter. In addition, the bevel gear 5 is coupled to a radial shaft (not shown), by means of another bevel gear connected to this shaft. The intermediate shim 64 makes it possible to precisely adjust the axial spacing between the bearing 8 and the bevel gear 5, making it possible to precisely adjust the position of the latter relative to the bevel gear of the radial shaft, and thus to ensure engagement good quality between these two gables. This meshing between these two bevel gears makes it possible to rotate the radial shaft, the latter itself driving in rotation the accessory housing of the turbomachine (not shown).
    The shaft 4 has a first radial shoulder 30, here shown as being located upstream of the bearing 8 and facing a radial surface 5a of the bevel gear 5, a second radial shoulder 32, here shown as being located downstream of the bearing 8 and facing the track nut 26c, and the third radial shoulder 34 downstream of the joint track 26 and facing the downstream end 26b of the joint track 26. The first radial shoulder 30, the second radial shoulder 32 and the third shoulder 34 each define a stop in a direction from upstream to downstream. There is thus a clearance between the third shoulder 34 and the downstream end 26b, this clearance being defined by a distance J corresponding to the minimum distance between the downstream end 26b of the joint track 26, and the third shoulder 34, in the axial direction.
    The shaft 4 further comprises an annular groove 40, located downstream of the second shoulder 32. An O-ring 42 is disposed in this annular groove 40. This O-ring 42 is compressed radially between the seal track 26 and the bottom of the annular groove 40. This makes it possible to prevent oil leaks downstream of the assembly and therefore to maintain the sealing thereof.
    An upstream nut 50 is also fixed around the shaft 4, upstream of the bevel gear 5. When this nut is tightened, the latter exerts an axial force on the flange 5c of the bevel gear 5 having a radial face 5a resting on a wedge 60, itself resting on its opposite face on the first shoulder 30 of the shaft 4. The upstream nut 50 and the first shoulder 30 thus ensure axial locking of the bevel gear 5, the flange 5c being clamped between the upstream nut 50 and the first shoulder 30.
    The correct axial positioning of the pinion 5 on the shaft 4 is obtained by adjusting the thickness of the shim 60. If a high precision of this positioning is not required or according to the tolerances achievable via the manufacturing process used, the shim 60 can be eliminated by moving the first shoulder 30 of the shaft 4 upstream by a value corresponding to the thickness “E” of this shim, so that the flange 5c of the bevel gear 5 takes directly support on this shoulder. In the absence of this first shoulder 30 (with or without shim 60) this axial force can propagate axially through the bevel gear 5 and the bearing 8, to reach the joint track 26, the downstream end 26B of which would take support on the third shoulder 34 after having consumed all of the clearance “J”. Sandwiched between the inner ring 12 of the bearing 8 and the third shoulder 34 of the shaft 4, the joint track 26 would then be subjected to an axial compressive stress, generating a radial deformation of the contact surface 26a which would then come arching (this is commonly known as "barrel-laying"), thus deteriorating the sliding joint / track contact, and therefore the sealing of the assembly 1.
    In the example of Figure 1, the annular adjustment shim 60 is arranged around the shaft 4. According to one embodiment, this adjustment shim 60 has the shape of an annular ring, and is arranged on the upstream side of the bearing 8, so as to be interposed axially between the first shoulder 30, being in abutment against the latter, and the radial surface 5a of the flange 5c of the bevel gear 5. This adjustment shim 60 also has a thickness E, measured in the axial direction, which can be adjusted to ensure the correct axial positioning of the pinion 5 on the shaft 4.
    The value of this adjustment may not exceed the value of the clearance "J" between the third shoulder 34 and the downstream end 26B of the joint track 26. Consequently, when the upstream nut 50 exerts an axial force on the bevel gear 5, the radial surface 5a thereof abuts on the adjustment shim 60, so that the latter is sandwiched between the radial surface 5a and the first shoulder 30. The adjustment shim 60 thus neutralizes the axial stresses induced by the upstream nut 50. The latter remaining located around the first shoulder 30, the joint track 26 is not subjected to axial stresses and the distance J remains non-zero, thus avoiding any deformation of the joint track 26 .
    According to another embodiment, an annular adjustment shim 62, also having the shape of an annular ring, is disposed on the downstream side of the bearing 8, so as to be interposed axially between the second shoulder 32, being in abutment against it, and the track nut 26c. This adjustment shim 62 also has a thickness E ′, measured in the axial direction, which can be adjusted to ensure the correct axial positioning of the pinion 5 on the shaft 4. The value of this adjustment cannot exceed the value of the clearance "J" between the third shoulder 34 and the downstream end 26B of the joint track 26.
    Consequently, when the track nut 26c tends to loosen, for example due to the axial stresses coming from the upstream nut 50 or to the vibrations of the turbomachine in operation, and thus moves downstream, the track nut 26c then abuts against the adjustment shim 62, so that the latter is sandwiched between the track nut 26c and the second shoulder 32. The adjustment shim 62 thus neutralizes the axial stresses originating from of the upstream nut 50, the latter propagating along the shaft 4 passing under the downstream end 26b of the joint track 26. The joint track 26 then does not undergo axial stresses, and the distance J can be kept non-zero, thus avoiding any deformation of the joint track 26.
    In addition, the adjustment shim 62 comprises at least one radial orifice 62a allowing the passage of the oil, the latter thus being able to flow to the drop lance 18.
    Although the present description has been described with reference to specific exemplary embodiments, it is obvious that modifications and changes can be made to these examples without departing from the general scope of the description as defined by the revendications. In particular, individual features of the various illustrated / mentioned embodiments can be combined in additional embodiments. Therefore, the description and the drawings should be considered in an illustrative rather than restrictive sense.
    It is also obvious that all the characteristics described with reference to a device can be transposed, alone or in combination, to a process.
    权利要求:
    Claims (9)
    [1" id="c-fr-0001]
    1. Assembly for an oil chamber (2) of a turbomachine bearing, comprising:
    a housing (1);
    a shaft (4) mounted to rotate relative to the casing (1) by means of a bearing (8), and having an upstream end and a downstream end relative to the direction of air flow, the shaft (4 ) comprising a first bearing surface (30) and a shoulder (34) extending radially with respect to an axis of rotation (A) of the shaft (4);
    an annular pinion (5) disposed around the shaft (4) and comprising a radial surface (5a) mounted in abutment against the first bearing surface (30);
    a seal track (26) arranged around the shaft (4) downstream of the bearing (8), comprising a downstream end (26b) and a track nut (26c) making it possible to fix the seal track (26) to the annular gear (5);
    the bearing (8) being arranged around the annular pinion (5) and held axially between an upstream stop (5b) of the annular pinion (5), and the track nut (26c);
    the downstream end (26b) of the joint track (26) being arranged opposite the shoulder (34) along the axis (A) so that a non-zero axial functional clearance (J) exists between said end downstream (26b) and said second bearing surface (34), so that the shaft (4) does not exert axial compression on the joint track (26).
    [2" id="c-fr-0002]
    2. Assembly according to claim 1, in which the first bearing surface (30) is situated on an upstream side of the bearing (8), and a second bearing surface (32) of the shaft (4) is located on a downstream side of the bearing (8), the annular pinion (5) being mounted in abutment against the first bearing surface (30), or against the second bearing surface (32), the second surface support (32) being located axially between the first support surface (30) and the shoulder (34).
    [3" id="c-fr-0003]
    3. The assembly of claim 1 or 2, wherein the radial surface (5a) is oriented downstream, and the first bearing surface (30) is oriented upstream.
    [4" id="c-fr-0004]
    4. Assembly according to any one of claims 1 to 3, comprising an adjustment shim (60) disposed around the shaft (4), and interposed axially between the first bearing surface (30) and the radial surface ( 5a) of the annular pinion (5).
    [5" id="c-fr-0005]
    5. Assembly according to any one of claims 1 to 3, in which the adjustment shim (62) is interposed axially between the track nut (26c) and the second bearing surface (32) of the shaft ( 4).
    [6" id="c-fr-0006]
    6. Assembly according to any one of claims 1 to 5, in which an upstream nut (50) is mounted in abutment against the annular pinion (5), so that the annular pinion is held axially between the upstream nut (50 ) and the first bearing surface (30).
    [7" id="c-fr-0007]
    7. Assembly according to any one of claims 1 to 6, configured so that cooling oil flows along the shaft (4) in a first axial direction between the shaft (4) and the pinion annular (5).
    [8" id="c-fr-0008]
    8. The assembly of claim 7, wherein the seal track (26) is a cylinder having an axial port (26d), the assembly being configured so that the cooling oil flows into the axial port (26d ), in a second axial direction opposite to the first axial direction.
    [9" id="c-fr-0009]
    9. An assembly according to any one of claims 1 to 8, wherein the shaft (4) has an annular groove (40) and a seal (42) disposed in the annular groove (40), and compressed between the shaft (4) and the joint track (26).
    lO.Turbomachine comprising the assembly according to any one of the preceding claims.
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    同族专利:
    公开号 | 公开日
    FR3066549B1|2019-07-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP0042320A1|1980-06-13|1981-12-23|Societe Nationale D'etude Et De Construction De Moteurs D'aviation, "S.N.E.C.M.A."|Oil-film damped bearing between shafts of a multi-spool turbomachine|
    EP1406026A1|2002-10-01|2004-04-07|Snecma Moteurs|Oil-film damped roller bearing|WO2021032924A1|2019-08-19|2021-02-25|Safran Aircraft Engines|Device for distributing oil from a rolling bearing for an aircraft turbine engine|
    FR3107310A1|2020-02-17|2021-08-20|Safran Aircraft Engines|OIL DISTRIBUTION DEVICE OF AN AIRCRAFT TURBOMACHINE BEARING BEARING|
    WO2021198583A1|2020-04-02|2021-10-07|Safran Aircraft Engines|Device for distributing oil from a rolling bearing for an aircraft turbine engine|
    法律状态:
    2018-04-23| PLFP| Fee payment|Year of fee payment: 2 |
    2018-11-23| PLSC| Search report ready|Effective date: 20181123 |
    2019-04-19| PLFP| Fee payment|Year of fee payment: 3 |
    2020-04-22| PLFP| Fee payment|Year of fee payment: 4 |
    2021-04-21| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1754336|2017-05-17|
    FR1754336A|FR3066549B1|2017-05-17|2017-05-17|IMPROVED ASSEMBLY FOR OIL ENCLOSURE|FR1754336A| FR3066549B1|2017-05-17|2017-05-17|IMPROVED ASSEMBLY FOR OIL ENCLOSURE|
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