• 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:
    The invention relates to an annular raceway (80) for turbomachine rotating shaft bearings. According to the invention, the rolling cage (80) comprises a vibration damping rod (92) corresponding to deformation modes of the roll cage (80) and the roll cage (80) further comprises at least an outer rim (800) having an at least partially annular housing (804) extending about a central axis of the rolling stand (80), the damping ring (92) being disposed in the housing (804); ).
    公开号:FR3014155A1
    申请号:FR1361847
    申请日:2013-11-29
    公开日:2015-06-05
    发明作者:Daniel Georges Plona
    申请人:SNECMA SAS；
    IPC主号:
    专利说明:

    [0001] FIELD OF THE INVENTION The invention relates to the technical field of rolling stands for rotating shafts, in particular rotating turbo-machine shafts. More specifically, the invention relates to a roll cage comprising at least one vibration damping means of the roll cage. STATE OF THE PRIOR ART Turbomachine rotating shafts are supported and guided in rotation by bearings bearing bearings. These bearings each comprise a plurality of rolling elements which may be of various types, for example balls, rollers or even needles. In known manner, a turbomachine bearing, such as that disclosed in the patent application Snecma EP 0 769 631, includes an inner ring, an outer ring and a rolling cage comprising one or two rails, and housed between the outer ring and the outer ring. The rolling elements are then located, inside the rolling cage, between the cage bridges which are intended to keep them spaced from each other. The bearings used for turbomachine rotating shafts, in particular in the aerospace industry, are subjected to particularly high stresses in terms of service life, rotation speeds and low power dissipation. This rolling cage is potentially subjected to external vibratory excitations, especially those related to the environment, or internal, for example those related to the operation and the internal kinematics of the bearing. When these excitation frequencies are in phase with the modes of deformation of the cage, they can lead to mechanically deform the cage in operation and prematurely degrade it by mechanical fatigue or by inducing distortions detrimental to the proper functioning of its centering, for example .
    [0002] In order to prevent the roll cage from deforming excessively, it is possible to increase its working section, mainly the section of the rails. Nevertheless, the optimization of the rails is limited by the need to provide means for evacuating the lubricating oil from the bearing. One way to overcome this limitation is to increase the dimensions of the rolling elements. However, the reliability of the bearing operation under low load may then be degraded. When the deformation modes of the cage can not be placed outside the excitation frequencies experienced by the bearing, there is a high risk of prematurely degrading the bearing. In this case, one conceivable solution is to provide the cage with a means of damping the vibrations caused by the excitation frequencies. Nevertheless, the vibration damping means, according to the known designs, do not provide full satisfaction. DISCLOSURE OF THE INVENTION The invention aims to at least partially solve the problems encountered in the solutions of the prior art. In this regard, the subject of the invention is an annular rolling bearing housing for a turbomachine rotating shaft bearing, the rolling bearing comprising a vibration damping rod corresponding to deformation modes of the rolling stand, and the rolling cage comprising at least one outer flange 25 having an at least partially annular housing which extends around a central axis of the rolling cage, the damping ring being disposed in the housing. The damping rod damps the vibrations generated by the mechanical deformation of the roll cage during the operation of the bearing in which the roll cage is integrated.
    [0003] The housing has in particular a sufficiently large mechanical contact area with the damping rod to maintain the damping rod and effectively transmit the mechanical forces of the rolling shaft to the damping ring which then dissipates this energy. The housing is especially designed to cause the rotational damping ring with the rolling cage around the central axis of the bearing housing. The damping rod is for example likely to have relative micro-movements in its housing, and these micro-movements through the coefficient of friction between the rod and the cage will achieve a mechanical damping of the deformation modes of the cage. Thus, the deformation modes of the cage are absorbed and the deformation of the cage is minimized. However, the micro-movements of the damping ring are of almost negligible amplitude in front of the circumferential length of the housing. Therefore, the damping rod can be considered almost integral in rotation housing. The invention may optionally include one or more of the following features combined with one another or not. Advantageously, the vibration damping rod and the outer flange are configured to damp vibrations of eigen modes of mechanical deformation of the rolling cage. As such, the damping rod is preferably configured to dampen the first harmonics of eigen modes of mechanical deformation of the roll cage. More generally, the damping rod is configured to damp, at least in part, the main modes likely to cause the degradation of the cage and the bearing. According to an additional characteristic, the housing holds the damping rod against an outer lateral surface of the rolling cage. Alternatively, the housing could be located in particular on another outer surface of the roll cage.
    [0004] According to a particular embodiment, the housing is a groove for holding the damping ring. In this case, the damping rod is located in the groove, preferably being in mechanical contact with the bottom of the groove. In an alternative configuration, the housing is for example a cavity, completely closed or almost, around the damping ring. According to an advantageous embodiment, the outer flange comprises an outer retaining shoulder having the shape of a hook in cross section. The damping rod can be monobloc or sectorized. The ring is preferably monobloc, being split so as to create two ends having a non-zero gap between them. The ring is in particular split at its ends, so as to facilitate its mounting on the roll cage. The damping rod preferably extends over an angle of between 350 ° and 360 ° along the roll cage. According to another advantageous embodiment, the outer flange forms a guide rail of at least one rolling rolling element. The rolling cage is in particular configured to maintain spaced apart a plurality of rolling elements between guide rails. These rolling elements may be of various kinds, for example balls, rollers or even needles. According to another particular embodiment, the rolling cage comprises a main body comprising the outer rim, the main body being made of metallic material, in particular steel, the damping ring being made of a metallic material of mechanical strength comparable to that of the main body. The damping rod is preferably made of cast iron or steel. According to another particular embodiment, the rolling cage comprises a pair of damping rods and a pair of outer flanges each having a housing, at least partially annular about the central axis, in which one of the damping rods is disposed, the damping rods and the outer edges of each pair being arranged substantially symmetrically by plane symmetry with respect to the same median plane of the roll cage. The damping rod is in particular maintained substantially integral in rotation of the rolling cage by rotation about the central axis.
    [0005] The invention also relates to a bearing for a turbomachine rotating shaft, comprising a rolling cage as defined above. The invention also relates to a turbomachine bearing, the bearing comprising a bearing as defined above. The invention also relates to a turbomachine rotor, the rotor comprising a turbomachine bearing as defined above. The invention also relates to a turbomachine comprising at least one bearing, a bearing and / or a rotor, as defined above. Finally, the invention relates to a method of manufacturing an annular raceway as defined above, the method comprising a step of determining the eigenmodes of mechanical deformation of the rolling frame without damping ring, during which step a damping rod configured to damp the vibrations generated by the bearing is mounted in the housing, so that the housing is designed to cause the damping ring in rotation about the central axis of the bearing housing.
    [0006] The damping rod is then integral in rotation with the rolling stand, with the exception of micro-displacements of the damping rod in its housing. BRIEF DESCRIPTION OF THE DRAWINGS The present invention will be better understood on reading the description of exemplary embodiments, given purely by way of indication and in no way limiting, with reference to the appended drawings in which: FIG. 1 represents a diagrammatic sectional view longitudinal flow of a turbofan engine for aircraft; Figure 2 is a partial section with a perspective view of a bearing according to a first embodiment of the invention; FIG. 3 is a partial view of the rolling cage of FIG.
    [0007] DETAILED DESCRIPTION OF PARTICULAR EMBODIMENTS Identical, similar or equivalent parts of the different figures bear the same numerical references so as to facilitate the passage from one figure to another.
    [0008] FIG. 1 schematically represents a turbomachine 1 with a double flow according to one embodiment of the invention. The turbomachine 1 comprises a rotating shaft 30 of a turbomachine 1 movable about the longitudinal main axis 3 of the turbomachine 1. The shaft 30 comprises in particular a front portion 31 and a rear portion 32 coaxial. The front 31 and rear 32 parts are joined by a gear 2 shown very schematically. They carry fan blades 6, rectifying vanes 8 and compressor blades 10. The shaft 30, the fan blades 6 and the compressor blades 10 and the gear unit to which they are mechanically connected form part of the rotor. 5 of the turbomachine 1.
    [0009] The front shaft 31 is generally supported from upstream to downstream by a ball bearing 22 and by a roller bearing 42 placed in the area of the gearbox 2. The rear portion 32 of the shaft 30, much longer, is in this case supported from upstream to downstream first by a pair of ball bearings 24 and 26 configured to support high axial loads and then by a pair of roller bearings 44 and 46 configured to support high radial loads. Each of these six bearings 22, 24, 26, 42, 44, 46 is part of a turbomachine bearing 1, which is generally fixed firmly to a housing of the stator 12 of the turbomachine 1 by a support means 11. Each of six bearings 22, 24, 26, 42, 44, 46 is likely to be a bearing with a configuration identical to that of a bearing 70 shown in Figures 2 and 3. The bearing 70 can also be mounted on a rotating shaft of low pressure turbine (not shown) or possibly on a turbomachine shaft configured to rotate at high rotational speeds, such as a high pressure turbine shaft (not shown).
    [0010] Referring to Figure 2 and Figure 3, there is shown a rotating shaft bearing 70 30, 31, 32 of turbomachine 1, according to a first embodiment of the invention. The bearing 70 comprises an outer ring 60, an inner ring 50 and rolling elements 74. The rolling elements 74 are generally guided in displacement in at least one race 64 formed on the outer ring 60 and / or the inner ring 50. In order for the rolling elements 74 to remain spaced apart from one another in operation, the bearing 70 also comprises an annular rolling cage 80 situated between the inner ring 50 and the outer ring 60. The bearing 70 is substantially symmetrical with revolution around the outside. central axis 73 of the bearing housing 80. Furthermore, the bearing 70 is substantially symmetrical by plane symmetry with respect to a median plane "P". The plane "P" is substantially orthogonal to the central axis 73. The rolling cage 80 is traversed by cavities 82 delimited by walls 84 spacing the rolling elements 74. On either side of the cells 82, the rolling cage 80 comprises an outer rim 800 intended to serve as a guide rail of the rolling elements 74. The walls 84 spacing of the rolling elements 74 are made of particular material with the outer flanges 800, so as to form a main ring body 80 which is likely to withstand the severe operating constraints of the bearing 70. For this, the main body of the roller cage 80 is manufactured in a known manner of metal material, especially steel. Common metals or their alloys are particularly preferred for their relatively high thermal and mechanical resistance. To further improve the resistance of the bearing cage 80, the main body of the bearing ring 80 is more generally monobloc. In this case, the cells 82 are made for example by drilling or broaching. Preferably, the walls 84 spacing the rolling elements 74 and the two outer flanges 800 extend along the rolling cage 80 about the central axis 73, each outer flange 800 being located on the lateral periphery of the Roller cage 80. An outer rim 800 includes an inner side wall 814 delimiting the guide rail of the rolling elements 74 and an outer side wall 812 opposite to the inner side wall 814. The inner side wall 814 and the outer side wall 812 are delimited by a radially lower wall 818 facing the inner ring 50 and a radially upper wall 816 facing the outer ring 60. In operation, the rolling cage 80 is capable of being deformed mechanically, which can reduce its service life. However, the roll cage 80 is preferably configured so that the first clean mode of deformation of the roll cage 80 is never reached, in particular because of the stiffness of the roll cage 80. In order to limit still the effect of mechanical vibrations on the bearing 70, the bearing housing 80 comprises at least one vibration damping ring 92 located in a housing 804 provided on one of the outer flanges 800. The damping rod 92 is preferably also capable of damping the vibrations of at least one specific mode of mechanical deformation of the rolling cage 80, which is determined in the absence of damping ring 92. In practice, since the bearing 70 is symmetrical relative to its median plane "P", the rolling cage 80 comprises at least one pair of damping rods 92 each located in a housing 804 provided on an outer rim 800. The damping rods 92 mounted on each outer rim 800 is preferably substantially identical. Each damping ring 92 extends at least over an angular portion along the annular outer flange 800, preferably 360 ° along the rolling cage 80.
    [0011] With reference to FIG. 3, the housing 804 allows the damping rod 92 to be held by its elastic return against the external lateral surface 812 of the roll cage 80. In fact, in this embodiment, the housing 804 presents the shape of a groove for holding the damping ring 92 along the outer lateral surface 812. The outer rim 800 has an outer retaining shoulder 822 of the damping ring 92, formed by an outer edge of the groove maintaining the damping rod 92. This outer bearing shoulder 822 has the shape of a cross-section hook, that is to say along a section plane which contains the central axis 73 and is therefore perpendicular to the plane median "P". The damping rod 92, thus housed in the holding groove, does not rub against the inner ring 50 or the outer ring 60. In addition, the housing 804 is oriented towards the inner ring 50, so that use, the centrifugal force generated by the rotation of the roll cage 80 is not likely to get out the damping rod 92 of the holding groove.
    [0012] In general, the damping rod 92 is housed in the outer rim 800 so as to be integral in rotation with the roll cage 80. There is therefore almost no movement of the damping rod 92 relative to the Roller cage 80. More precisely, there can be only a very limited displacement of damping rod 92 by relative micro-movements in its housing 804, during the deformation of roll cage 80 in its deformed modes. . The dissipation of the friction energy between the rod 92 and the cage 80 during these relative micro-movements provides a mechanical damping of the deformation modes of the roll cage 80. As the damping rod 92 is maintained in contact with the bearing cage 80 by the outer rim 800, the damping ring 92 is not in direct mechanical contact with the rolling elements 74. Consequently, the damping ring 92 makes it possible to damp the mechanical vibrations transmitted by the main body of the rolling cage 80 without degrading the reliability of the bearing 70. In addition, the evacuation of the lubricating oil of the bearing 70 is not disturbed by the presence of the damping rod 92, since it is located in the outer rim 800. More specifically, the lubricating oil is all the better discharged that the damping ring 92 is relatively far from at least one raceway 64. The damping rod 92 is mono block in the example shown in Figure 3, but can also be formed by several sectors of successive elementary rods along the groove of the damper rod 92. The one-piece damping ring is preferably split so as to form two ends and thus facilitate its mounting in the housing 804, as explained below. In this configuration, the end portions of the damping rod 92, located near the slot of the damping rod 92, preferably have a radius of curvature substantially equal to or slightly smaller than that of the housing 804, of so that these end portions remain facing each other when the damping ring 92 is mounted in the housing 804. In this way, it is particularly possible to prevent solid particles from becoming deposit between the bottom of the groove 804 and the damping ring 92, which would lead to an unwanted modification of the coefficient of friction between the damping ring 92 and the cage, and possibly to premature wear of the roll cage Advantageously, the distal portion of the damping rod 92, opposite to the end portions, then has a greater radius of curvature than the rest of the housing 804, so as to facilitate the maintenance of the damping rod. 92 in the housing 804 by the elastic return of the ring. The damping rod 92 may consist of a helical spring, advantageously with contiguous turns so as to optimize the coefficient of friction between the rod and the cage. The damping rod 92 is for example made of cast iron or steel. More generally, the damping rod 92 is made of material of mechanical strength comparable to that of the main body of the cage that it must dampen. To manufacture a roll cage 80 comprising vibration damping means 90 according to the invention, the eigen modes of mechanical deformation of the roll cage 80 are determined beforehand without vibration damping means. Subsequently, at least one damping ring 92 as described above is mounted in the housing 804 of the outer rim 800, so that the damping ring 92 is integral, in particular in rotation, the cage The damping rod 92 can move with friction in its housing 804, and can therefore rotate with micro-movements relative to the running cage 80 in operation. To assemble the damping rod 92 in the roll cage 80, a clearance will be provided to split the damping rod 92 and create a non-zero gap between the two ends of the damping rod 92 thus formed. The ring 92 can therefore be closed at the time of assembly by making it join its two ends, in order to be inserted from below into the outer holding shoulder 822. Once the damping ring 92 has been put into place in the housing 804 , the ring 92 extends at an angle preferably between 350 ° and 360 ° along the rolling cage 80. Generally, the angle is less than 360 °, which means that a gap remains between the two ends of the ring 92 in place. This spacing implies a discontinuity in the angular distribution of the mass of the rod 92. The resulting unbalance will be particularly acceptable in the balancing tolerances of the bearing cage 80, the unbalance will be compensated in particular by making a segment of rush 92 of variable section. For example, a smaller section of the ring 92 may be provided on the side diametrically opposed to the two ends, so as to locally reduce the linear mass of the ring 92.
    [0013] Of course, various modifications may be made by those skilled in the art to the invention which has just been described without departing from the scope of the disclosure of the invention. The bearing according to the invention may comprise, for example, additional vibration damping means of the bearing.
    权利要求:
    Claims (10)
    [0001]
    REVENDICATIONS1. Bearing casing (80) annular for rotating shaft bearing (30, 31, 32) of turbomachine (1), characterized in that it comprises a ring (92) for damping vibrations corresponding to modes deformation of the bearing housing (80), and further comprising at least one outer rim (800) having an at least partially annular housing (804) extending about a central axis (73). ) of the rolling stand (80), the damping ring (92) being disposed in the housing (804).
    [0002]
    2. Rolling cage (80) according to the preceding claim, characterized in that the housing (804) holds the damping ring (92) against an outer lateral surface (812) of the rolling cage (80).
    [0003]
    3. Roll cage (80) according to any one of the preceding claims, characterized in that the housing (804) is a groove for holding the damping ring (92).
    [0004]
    4. Roll cage (80) according to any one of the preceding claims, characterized in that the outer flange (800) comprises a holding outer shoulder (822) having the shape of a hook in cross section.
    [0005]
    5. Rolling cage (80) according to any one of the preceding claims, characterized in that the damping ring (92) is in one piece and is split so as to create two ends having a non-zero gap between them, the rod damping member (92) extending at an angle of between 350 ° and 360 ° along the rolling stand (80).
    [0006]
    6. Roll cage (80) according to any one of the preceding claims, characterized in that the outer flange (800) forms a guide rail of at least one rolling element (74) rolling (70).
    [0007]
    7. Roll cage (80) according to any one of the preceding claims, characterized in that it comprises a main body (800, 82, 84) comprising the outer flange (800), the main body (800, 82, 84) being made of metallic material, in particular steel, and in that the damping ring (92) is made of a metal material of mechanical strength comparable to that of said main body.
    [0008]
    8. Roll cage (80) according to any one of the preceding claims, characterized in that it comprises a pair of damping rods (92) and a pair of outer flanges (800) each having a housing (804) at least partially annular about the central axis (73), wherein one of the damping rods (92) is disposed, the damping rods (92) and the outer flanges (800) of each pair being arranged substantially symmetrically by plane symmetry with respect to the same median plane (P) of the cage.
    [0009]
    9. Bearing (70) for a turbomachine rotating shaft (30, 31, 32), comprising a rolling cage (80) according to any one of the preceding claims.
    [0010]
    10. Turbomachine (1) comprising at least one bearing (70) according to the preceding claim.
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    同族专利:
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    GB2522324A|2015-07-22|
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    GB201421199D0|2015-01-14|
    FR3014155B1|2016-05-06|
    US9341215B2|2016-05-17|
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    DE102019112095A1|2019-05-09|2020-11-12|Schaeffler Technologies AG & Co. KG|Rolling bearing cage|
    法律状态:
    2015-11-13| PLFP| Fee payment|Year of fee payment: 3 |
    2016-11-09| PLFP| Fee payment|Year of fee payment: 4 |
    2017-10-20| PLFP| Fee payment|Year of fee payment: 5 |
    2017-11-10| CD| Change of name or company name|Owner name: SNECMA, FR Effective date: 20170713 |
    2018-10-24| PLFP| Fee payment|Year of fee payment: 6 |
    2019-10-22| PLFP| Fee payment|Year of fee payment: 7 |
    2020-10-21| PLFP| Fee payment|Year of fee payment: 8 |
    2021-10-20| PLFP| Fee payment|Year of fee payment: 9 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1361847A|FR3014155B1|2013-11-29|2013-11-29|BEARING CAGE WITH PERIPHERAL PERIPHERAL VIBRATION DAMPING|FR1361847A| FR3014155B1|2013-11-29|2013-11-29|BEARING CAGE WITH PERIPHERAL PERIPHERAL VIBRATION DAMPING|
    US14/538,227| US9341215B2|2013-11-29|2014-11-11|Bearing cage with a peripheral vibration damping ring|
    GB1421199.9A| GB2522324B|2013-11-29|2014-11-28|Bearing cage with a peripheral vibration damping ring|
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