• 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:
    ROTATING CENTER AND GUIDE DEVICE OF A TURBOMAQUINE TREE, AND, TURBOMAQUINE Centering and rotating guide device (110) of a turbomachine tree (112), comprising a roller bearing (116) and a ball bearing (114) mounted around the tree and carried respectively by first and second flexible annular supports (120,118), and a oil film compression damper (139) comprising a rigid annular support (140) arranged around the roller bearing, the ball and damper bearing supports and the roller bearing being stacked transversely and extending around each other.
    公开号:BR112012007838B1
    申请号:R112012007838-0
    申请日:2010-09-27
    公开日:2020-11-24
    发明作者:Ivan Guy Rouesne
    申请人:Snecma；
    IPC主号:
    专利说明:

    [0001] The present invention relates to a centering and guide device in rotation of an axis, in particular turbomachinery.
    [0002] In general, a turbomachine axis is centered and guided in rotation by two support means, upstream and downstream respectively, one of these support means being able to comprise two bearings with bearings mounted next to each other.
    [0003] When a shaft guide bearing comprises a single bearing, this guide bearing is currently called "simplex" in the art and the bearing and for example rollers or balls is carried by a rigid annular support extending around the axis.
    [0004] When a guide bearing comprises two bearing bearings, this guide bearing is currently called “duplex” and generally comprises a bearing or roller bearing and a bearing or ball bearing.
    [0005] The bearing or ball bearing of the duplex is carried by an annular support having a certain flexibility so that it deforms in operation and allows the ball bearing to be offset in the event of imbalance, thus allowing the bearing or roller bearing to ensure the compensation of radial loads.
    [0006] This roller bearing is carried by an annular support which preferably also has a certain flexibility to avoid problems of dynamics. However, for the roller bearing to compensate for the required radial loads, the flexibility of the ball bearing support must be at least three times greater than that of the roller bearing support.
    [0007] When the bearing supports are both flexible, an oil film compression damper is generally arranged around the roller bearing. This damper comprises an annular space filled with oil and which is bounded by a part of the roller bearing support and by a rigid annular element surrounding this part, and which is closed axially by free sealing rings in rotation in the annular flutes of the part of the support and that cooperate in tightness with an internal cylindrical surface of the rigid annular element.
    [0008] In current technology, the supports of the roller bearing and the ball bearing are arranged one behind the other and fixed to each other by means of the screw-nut type. Such a device is relatively bulky, particularly in the axial direction, which prevents it from being mounted on a small engine.
    [0009] In addition, to provide flexibility, each bearing support comprises an elastically deformable annular part. The increase in the flexibility of a bearing support can notably result from the elongation of the deformable annular part of this support, which nevertheless leads to an increase in the axial occupied volume of the device and can decrease the mechanical resistance of the deformable part of the support.
    [0010] Additionally, the efficiency of the oil film compression damper is notably a function of the relationship of the length of the pre-filled space filled with oil over its radius. The more this relationship is increased the more the damping is effective. In other words, it is preferable that this space has a long length and a relatively small radius to increase the efficiency of the damping. The elongation of this space, however, also causes an increase in the axial occupied volume of the device.
    [0011] The invention is notably intended to introduce a simple, effective and economical solution to the problem of occupied volume of the centering and guide devices of the prior art.
    [0012] It proposes for this purpose a centering and guide device in rotation of a turbomachine shaft, comprising a roller bearing designed to be mounted around the shaft and carried by a first annular support, a ball bearing designed for be mounted around the shaft and carried by a second annular support, and an oil film compression damper arranged around the roller bearing and comprising an annular space filled with oil and bounded by a rigid annular support surrounding a part of the support of roller bearings, the bearing supports being intended to be fixed as a rigid annular support of the damper on a housing and each comprising an elastically deformable annular part, on which the ball bearing support, the annular support of the damper and the roller bearing are stacked transversely and extend around each other.
    [0013] The device according to the invention is relatively compact thanks to the cross stacking of the ball bearing support, the annular support of the damper and the roller bearing. These handles extend around each other, which allows to limit the occupied volume, in particular axial, of the device that can be mounted on a small motor. The invention thus makes it possible to integrate a flexible-flexible 'duplex' (ie a device comprising a roller bearing and a ball bearing carried respectively by two relatively flexible supports) in a small motor, which was not possible in the prior art.
    [0014] The invention also makes it possible to facilitate the development of the flexibility of each support, the ball bearing support being able to have a more than three times greater flexibility than the roller bearing support while respecting the mechanical stresses acceptable by these supports, as well as the development of the relationship between the length and radius of the damper oil film. This relationship is according to the invention greater than or equal to about 0.3-0.4.
    [0015] The annular rigid support of the damper is preferably substantially L-shaped and comprises a cylindrical part surrounding the roller bearing support, and a radial part for fixing to the housing. The radial part of this support can be interspersed between annular flanges for securing the supports to the housing.
    [0016] The deformable part of each bearing support can comprise through crevices regularly distributed around the axis of the support and delimiting between them elastically deformable tongues or sleeves.
    [0017] The tongues or sleeves of the roller bearing support advantageously have a substantially C or pin shape, in order to limit their occupied volume in axial direction. This particular shape of the sleeves makes it possible to mount the device in the vicinity of the conical pine cone of a turbomachine countershaft.
    [0018] These C sleeves are intended to deform essentially in radial direction during the transmission of the radial loads compensated by the roller bearing.
    [0019] The tongues or sleeves of the ball bearing support can be substantially rectilinear and longitudinally oriented. These tongues or sleeves are arranged at least in part around the annular support of the damper and its length is determined in order to optimize the flexibility of the ball bearing support. The stretching of these tongues or sleeves is less penalizing from the point of view of the axial occupied volume of the device than in the prior art because most of the latter extends around the annular support of the damper.
    [0020] These tongues or sleeves preferably have at least one end of greater width, giving it a substantially I or T shape. The extended ends of the sleeves are stiffer than the rest of these sleeves and therefore resist mechanical stresses better. which they are subjected to during operation, thus limiting the appearance of cracks or cracks on these ends.
    [0021] According to another feature of the invention, the rigid annular support of the shock absorber comprises longitudinal ribs of reinforcement formed in projection on its external cylindrical surface and intended, in position of assembly, to be engaged in the crevices of the bearing support. spheres, in order to optimize the stacking of the different handles.
    [0022] The annular support of the damper may comprise means of supplying oil to the damper, these means comprising at least one conduit formed, for example, in one of the reinforcement ribs of this support.
    [0023] The feed conduit can be connected to a tip connecting to oil inlet means, this tip being intended, in an assembly position, to be engaged in one of the slots of the roller bearing support.
    [0024] Advantageously, the part of the roller bearing support disposed between the shock absorber and the roller bearing has an I-shaped section and comprises an internal cylindrical wall forming the outer ring of the roller bearing and an external cylindrical wall on the external surface from which annular grooves are formed for housing the sealing rings of the damper. This particular shape in I allows to stiffen the part of the support surrounding the rollers, which limits the deformations of this part in operation and translates into an increase in the life of the roller bearing and a better efficiency of the oil film compression damper . In effect, the stiffening of this part of the roller bearing support prevents, on the one hand, the conical placement of this part, resulting in early and localized wear of the rollers, and on the other hand, the ovalization of the annular support of the damper by dragging a oil of non-uniform thickness around the roller bearing and therefore poor damping of the vibrations to which this bearing is subjected in operation.
    [0025] The ball bearing support can be formed from a single handle with the outer ring of this bearing.
    [0026] The present invention also deals with a turbomachine, as well as a turbo-reactor or an aircraft turboprop, comprising at least one device as described above, the bearing and shock absorber supports being fixed to an annular flange of an intermediate character of the turbomachinery, this flange being located on a transverse piano passing sensibly through the shock absorber and the roller bearing. The flange of the intermediate housing can be crimped over the longitudinal ribs of the annular support of the damper. The radial loads compensated by the roller bearing are thus directly transmitted to the intermediate housing, the east which allows to prolong the life of the device handles.
    [0027] The invention will be better understood and other features, details and advantages of the same will appear more clearly by reading the description that follows, given by way of non-limiting example and with reference to the attached drawings in which: - figure 1 is a schematic half-axial sectional view of a device according to the prior art of centering and guiding in rotation of a turbomachine axis; figure 2 is a schematic half axial sectional view of a device according to the invention for centering and rotating guide of a turbomachine axis; figure 3 is a partial schematic view in perspective and axial section of the device of figure 2, on a larger scale, and represents the first and second bearing supports and the annular support of the oil film compression damper; figure 4 is a schematic perspective view of the device of figure 2, seen from upstream and from the side; figure 5 is a partial schematic view in perspective and in axial section of the device of figure 2, the section passing through the oil supply means of the damper; figure 6 is another schematic perspective view of the device of figure 2, seen from downstream and from the side; figure 7 is a schematic perspective view of the first bearing support of the device of figure 2; figure 8 is a schematic perspective view of the annular support of the damper of the device of figure 2; and - figure 9 is a schematic perspective view of the second bearing support of the device of figure 2.
    [0028] Initially reference is made to figure 1, which represents a device 10 according to the prior art of centering and rotating guide of an axis 12 of high pressure turbomachinery compressor, this device comprising a ball bearing 14 and a roller bearing 16 mounted around the axis 12 and carried respectively by two relatively flexible ring supports 18, 20. This device 10 is called "flexible duplex" in the art.
    [0029] The ball bearing 14 comprises a series of guided balls on a bearing path defined by an inner ring 22 and an outer ring 24, the inner ring 22 being fixed on the axis 12 and the outer ring 24 being fixed to a end of the annular support 18 of which the other end comprises a fixing annular flange 26 on an annular flange 28 of a turbomachine intermediate character. This support 18 has a substantially C-shaped section and comprises an elastically deformable annular part 30 giving the support a certain flexibility.
    [0030] The roller bearing 16 is mounted downstream of the ball bearing 14 and comprises a series of rollers guided on a bearing path defined by an inner ring 32 and an outer ring 34, the inner ring 32 being fixed on the shaft 12 and the outer ring being fixed to an end downstream of the annular support 20 of which the upstream end comprises an annular flange 36 for fixing on the flange 28 of the intermediate housing. This support 20 is substantially cylindrical in shape and comprises an annularly deformable annular part 38 giving the support a certain flexibility. Most of the support 20 extends downstream of the support 18.
    The device 10 further comprises an oil film compression damper 39, which comprises an annular space filled with oil and bounded by the downstream end part of the support 20 and the downstream end part of a rigid annular support 40 extending around the support 20 and fixed by its end upstream to the flange 28.
    [0032] This device 10 is relatively bulky in axial direction and may be difficult or even impossible to integrate it in a motor of reduced size.
    [0033] The invention provides a solution to this problem thanks to the cross stacking of the ball bearing support, the oil film compression damper support and the roller bearing, so that they extend around each other .
    [0034] In the example of the invention shown in Figures 2 to 9, device 110 comprises a roller bearing 116 mounted upstream of a ball bearing 114, roller bearing 116 being mounted around axis 112 and carried by an annular support 120 which is surrounded by the rigid annular support 140 of the damper. The ball bearing 11 14 is mounted around the axis 112 and is carried by an annular support 118 surrounding the support 140.
    [0035] The support 120 of the roller bearing 116 (figures 2 to 7) comprises an annular portion of the I-section which is connected by an annularly deformable annular portion 138 to an annular fixing flange 136 extending radially outwardly.
    The I-part of the support 120 comprises two cylindrical walls, respectively internal 142 and external 144, extending inside each other and connected between them by a radial annular wall 146.
    [0037] The inner cylindrical wall 142 forms the outer ring of the roller bearing 1 16 whose inner ring 132 is attached to the shaft 112. The outer wall 144 has an outer cylindrical surface within the oil-filled annular space of the shock absorber 139 of compression of oil film.
    This shock absorber 139 is closed axially at its ends upstream and downstream by two sealing rings 148 mounted free in rotation on external annular flutes of the external surface of the wall 144.
    [0039] The deformable part 138 of the support 1 18, best visible in figures 3 and 4, has a substantially C or pin shape in section and comprises a plurality of through slits defining between them tongues or sleeves 150 in the form of C. These tongues or sleeves 150 are evenly distributed around the axis of the support 11 18 and are deformable, in particular in radial direction.
    [0040] This C-shape of the sleeves 150 allows the assembly of the device around a countershaft 151 mounted on the shaft 112 and having at its upstream end a conical pinion 153. The sleeves 150 extend here around and distance from this pine cone 153.
    [0041] The support 118 of the ball bearing 114 (figures 2 to 6 and 9) is formed of a single handle with the outer ring 124 of this bearing and comprises a deformable annular part 130 connected by its end downstream to this ring 124 and through its upstream end to an annular flange 126 for fixing to flange 136 of the other support 120.
    [0042] The deformable part 130 of the support 118, best visible in figures 3 and 9, comprises several through slits defining between them tongues or sleeves 152 straight and longitudinal, which are elastically deformable in axial and / or radial direction. These tongues or sleeves 152 are regularly distributed around the longitudinal axis of the support 118.
    [0043] The inner surfaces of the wall 142 of the support 120 and the inner rim 124 of the support 1 18 are preferably covered with a thin layer of a hard material that limits the wear of these handles by friction of the balls and the bearing rollers.
    [0044] The support 140 (figures 2 to 6 and 8) has an L-shape and comprises a cylindrical part connected by its upstream end to a radial part extending outwards. The radial part of the support 140 is interspersed between the flanges 136, 128 of the bearing supports, these handles being applied together and fixed by means of the screw-nut type on an annular flange 128 of an intermediate character.
    [0045] The cylindrical part of the support 140 extends around the I-part of the support 120 and its internal surface outwardly delimits the oil-filled precharged annular space of the damper 139. Rings 148 cooperate with the internal cylindrical surface of this cylindrical part of the support 140 to ensure the tightness of this space.
    [0046] Longitudinal ribs of reinforcement 154 are formed in projection, on the external surface of the cylindrical part of the support 140. As is visible in figures 3 and 6, these ribs are intended, in an assembly position, to be engaged in the cracks of the part deformable 130 of the support 118. Each rib 154 of the support 140 therefore extends between two adjacent tongues or sleeves 152 of this support 11.
    [0047] The support 140 comprises oil supply means of the damper 139, these means comprising an oil conduit 158 which is formed in one of the ribs 154 of the support 140 and which ends at a first end on the inner surface of the cylindrical part of the support 140 (figure 5). The second end of the conduit 158 is connected to a tip 162 connecting to oil inlet means, this tip 162 being formed projecting on the face upstream of the radial part of the support 140 and extending, in a mounting position, between two adjacent sleeves 150 of support 120 (figures 4 and 5). The oil line 158 has a substantially L shape here.
    [0048] The outer surface of the wall 144 of the support 120 comprises, between the airtightness rings 148 mentioned, an annular flute 160 for the distribution of oil admitted through the flue 158. This flute 160 is located approximately perpendicular to the flue and allows to distribute evenly the oil over the entire damper penimeter and thus form an oil film of uniform thickness (figure 5). The operation of this type of shock absorber is well known in the art and will therefore not be explained in detail here.
    [0049] In operation, the part 130 of the support 118 deforms to allow off-centering of the ball bearing 114, for example under the effect of an imbalance. The roller bearing 1 16 is then intended to compensate for the radial loads caused by this imbalance, which are then transmitted by the support 120 to the intermediate housing.
    [0050] The flange 128 of the intermediate housing is advantageously curved in C (figure 2) on the reinforcement ribs 154 of the support 140, in order to ensure a good transmission of these radial loads. The flange 128 of the intermediate housing is located here on a transverse piano passing sensibly through the shock absorber 140 and the roller bearing 116 (see the line 170 for passing the stresses, schematically represented by dotted swallows), which allows to effectively transmit the required loads directly on the intermediate housing without requiring much of the device's handles. The damper 139 is designed to dampen vibrations to which roller bearing 114 is subjected in operation.
    权利要求:
    Claims (13)
    [0001]
    1. Centering and rotating guide device (110) of a turbomachine shaft (112), comprising a roller bearing (116) intended to be mounted around the shaft and carried by a first annular support (120), a ball bearing (114) intended to be mounted around the shaft and carried by a second annular support (118), and an oil film compression damper (139) arranged around the roller bearing and comprising a filled annular space by oil and bounded by a rigid annular support (140) surrounding a part of the roller bearing support, the bearing supports being intended to be fixed with the annular support of the damper on a housing and each comprising an annular part ( 130, 138) elastically deformable, characterized by the fact that the ball bearing support, the damper, the annular support of the damper and the roller bearing are stacked transversely and extend around each other.
    [0002]
    Device according to claim 1, characterized in that the annular support (140) of the damper is substantially L-shaped and comprises a cylindrical part surrounding the roller bearing support (120), and a radial part of fixing to the character.
    [0003]
    Device according to claim 1 or 2, characterized in that the deformable part (130, 138) of each bearing support (118, 120) comprises through slots regularly distributed around the axis of the support and delimiting between them tongues or sleeves (150, 152) elastically deformable.
    [0004]
    Device according to claim 3, characterized in that the tongues or sleeves (150) of the roller bearing support (120) have a substantially C or pin shape.
    [0005]
    Device according to claim 3 or 4, characterized in that the tongues or sleeves (152) of the ball bearing support (118) are substantially straight and longitudinally oriented.
    [0006]
    Device according to claim 5, characterized in that the tongues or sleeves (152) of the ball bearing support (118) have at least one wider end, giving it a substantially T or I shape.
    [0007]
    Device according to any one of claims 3 to 6, characterized in that the annular support (140) of the shock absorber comprises longitudinal ribs (154) formed in projection on its external cylindrical surface and intended, in mounting position , to be engaged in the slots of the ball bearing support (118).
    [0008]
    Device according to claim 7, characterized in that the annular support (140) of the damper comprises means for supplying oil to the damper, these means comprising at least one conduit (158) formed in one of the reinforcement ribs ( 154) of this support.
    [0009]
    Device according to claim 8, characterized in that the conduit is connected to a tip (162) connecting to oil inlet means, this tip being formed in projection on a radial face of the support (140) of the damper and being destined, in an assembly position, to be engaged in one of the above mentioned slots of the roller bearing support (120).
    [0010]
    Device according to one of Claims 1 to 9, characterized in that the part of the roller bearing support (120) disposed between the shock absorber (139) and the roller bearing (116) has a shape in section in I e comprises an inner cylindrical wall (142) forming the outer ring of the roller bearing and an outer cylindrical wall (144) on the outer surface from which annular grooves (148) are formed for sealing the damper's sealing rings.
    [0011]
    Device according to any one of claims 1 to 10, characterized in that the support (118) of the ball bearing (114) is formed of a single handle with the outer ring (124) of this bearing.
    [0012]
    12. Turbomachine, either as a turbo-reactor or an aircraft turboprop, comprising at least one device (110) as defined in any of claims 1 to 11, characterized by the fact that the bearing supports (118, 120) and the shock absorber ( 140) are attached to an annular flange (128) of an intermediate turbomachine housing, this flange being located on a transverse piano passing substantially through the shock absorber (139) and the roller bearing (116)
    [0013]
    13. Turbomachine according to claim 12, characterized in that the flange (128) of the intermediate housing is crimped on longitudinal ribs (154) of reinforcement of the annular support (140) of the shock absorber.
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    同族专利:
    公开号 | 公开日
    CA2776313A1|2011-04-14|
    US20120213629A1|2012-08-23|
    EP2486247A1|2012-08-15|
    CA2776313C|2017-07-25|
    US9279449B2|2016-03-08|
    FR2951232B1|2017-06-09|
    CN102549238B|2015-08-26|
    BR112012007838A2|2016-03-15|
    WO2011042638A1|2011-04-14|
    CN102549238A|2012-07-04|
    RU2542630C2|2015-02-20|
    EP2486247B1|2015-09-16|
    RU2012118628A|2013-11-20|
    FR2951232A1|2011-04-15|
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    法律状态:
    2019-01-08| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-10-01| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2020-06-30| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2020-11-24| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 10 (DEZ) ANOS CONTADOS A PARTIR DE 24/11/2020, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    FR09/04816|2009-10-08|
    FR0904816A|FR2951232B1|2009-10-08|2009-10-08|DEVICE FOR CENTERING AND GUIDING ROTATION OF A TURBOMACHINE SHAFT|
    PCT/FR2010/052025|WO2011042638A1|2009-10-08|2010-09-27|Device for centring and guiding the rotation of a turbomachine shaft|
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