• 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:
    Bearing bush (1) of a turbocharger for radial bearing of a shaft of the turbocharger, wherein the bearing bush (1) on one of the shaft to be stored facing inner surface (4), which forms a running surface (5) of the bearing bush, at least partially has a microstructuring of several cup-like recesses , wherein the recesses have a maximum depth such that V = SLW / t MA X ≥ 0.1 and / or Re = (h SS + t MA X) * v MAX / ν SM ≤ 1800, where s LW is the absolute Game between the bushing (1) and shaft, where t M AX is the maximum depth of the cup-like recesses, where h SS is the minimum bearing clearance between the bushing (1) and shaft, where v MAX is the maximum peripheral speed of the shaft, where ν SM is the kinematic viscosity of a lubricant used for lubrication.
    公开号:CH714278A2
    申请号:CH01230/18
    申请日:2018-10-08
    公开日:2019-04-30
    发明作者:brandt Sven；Haag Jan-Christoph；Aurahs Lutz；Heinz Christoph；Benetschik Hannes
    申请人:Man Energy Solutions Se；
    IPC主号:
    专利说明:

    Description: The invention relates to a bearing bush of a turbocharger and a turbocharger.
    A turbocharger has a compressor and a turbine. A first medium is expanded in the turbine and energy is obtained in the process, the energy obtained in the turbine being used to compress a second medium in the compressor. In an exhaust gas turbocharger, the first medium expanded in the turbine is exhaust gas from an internal combustion engine and the second medium compressed in the compressor is charge air to be supplied to an internal combustion engine.
    The compressor of a turbocharger has a compressor housing and a compressor rotor. The turbine of the turbocharger has a turbine housing and a turbine rotor. The compressor rotor and turbine rotor are coupled via a shaft. The shaft is mounted in a bearing housing, which is positioned between the compressor housing and the turbine housing. The shaft is supported in the bearing housing via radial bearings. The radial bearings are bearing bushes.
    An arrangement of a bearing bush and a shaft of a turbocharger to be supported is known from EP 2 599 979 A2. The shaft is supported with a shaft bearing area in the bearing bush, with several channels being introduced into the bearing bush in order to guide a lubricant into a lubrication gap. According to EP 2 599 979 A2, the shaft bearing area of the shaft, which is guided in the bearing bush, is subdivided into several sections, namely into two outer sections and one inner section, at least one of the outer sections having a microstructure on its surface.
    Turbochargers are particularly subject to high wear in the area of their bearing bushes serving as radial bearings, particularly in start-stop operation. In the start-stop mode, a bearing bush is exposed to high loads due to the lack of hydrostatics. This often leads to bearing bush failure.
    There is a need for a bearing sleeve of a turbocharger, which is characterized by low wear and a turbocharger with such a bearing sleeve. Proceeding from this, the present invention is based on the object of creating a novel bearing bush. This object is achieved by a bearing bush according to claim 1.
    According to the invention, the bearing bush on at least in sections on an inner surface facing the shaft to be supported, which forms a running surface of the bearing bush, has a microstructuring comprising a plurality of cup-like recesses. The recesses of the microstructuring have a maximum depth, so the following applies:
    V = SLw / tMAX> 0.1 and / or
    Re = (hss + tMAx) * VMAx / vsM 1800, where
    Slw is the absolute radial play between the bearing bush and shaft, t M Ax is the maximum depth of the cup-like recesses, h S s is the minimum lubrication gap height between the bearing bush and shaft, v M ax is the maximum peripheral speed of the shaft, vsm the kinematic viscosity of a lubricant used for lubrication.
    The microstructuring of the tread of the bearing bush, the susceptibility to wear of the same can be significantly reduced, particularly in start-stop operation. It is important that the maximum depth of the cup-like recesses in the microstructuring fulfills at least one, preferably both, of the above conditions.
    [0009] According to an advantageous further development:
    0.1 <V <10 and / or
    Re = (hss + tMAx) * VMAx / vsM 1800.
    Such a microstructuring is particularly preferred for reducing the susceptibility to wear of the bearing bush, particularly in the start-stop operation of the turbocharger.
    [0011] The microstructuring is preferably introduced at least into those sections of the running surface of the bearing bush that are positioned in the region of a converging lubrication gap between the bearing bush and the shaft. In the conver
    CH 714 278 A2 lubricating gap, the load-bearing capacity is generated. The microstructuring is therefore introduced into the bearing surface of the bearing bush at least in the region of the converging lubrication gap.
    [0012] The microstructuring is preferably introduced into the running surface of the bearing bush outside of lubrication pockets. Then, when the microstructuring is introduced into the entire area of the bearing sleeve's running surface except for the lubrication pockets, the bearing sleeve can be manufactured easily and, even if the bearing sleeve can rotate, it can be reduced in susceptibility to wear.
    [0013] The turbocharger according to the invention is defined in claim 10.
    Preferred further developments of the invention result from the dependent claims and the following description. Exemplary embodiments of the invention are explained in more detail with reference to the drawing, without being restricted to this. It shows:
    1 shows an axial section through a bearing bush.
    2 shows a radial section through a bearing bush together with a mounted shaft;
    3a-3d different microstructuring of several cup-like recesses in plan view;
    4a-4h cross sections through a cup-like recess in each case;
    5a-5b cross sections through several cup-like recesses.
    The invention relates to a bearing bush of a turbocharger for the radial mounting of a shaft of the turbocharger. The basic structure of such a bearing bush is shown in Fig. 1. 1 shows a bearing bush 1 in cross section, which comprises a recess 2 for guiding and supporting a shaft 3. 2 shows a cross section rotated through 90 ° through the bearing bush 1 together with the shaft 3.
    The recess 2 of the bearing bush 1, which serves to guide and support the shaft 3, is seen in the axial section of FIG. 1 by an inner surface 4 which has a cylindrically contoured section 4 a in the middle and conical or at axial ends comprises frustoconically contoured sections 4b, 4c. The cylindrically contoured section 4a of the inner surface 4 of the liner 1 defines a running surface 5 of the bearing liner 1.
    As can be seen in Fig. 1, in the bearing bush 1 extending in the radial direction lubricating channels 6 are introduced, which serve to supply the bearing bush 1 with a lubricant. Thus, a lubrication gap 7 is formed between the tread 5 of the bearing bush 1 and the shaft 3 to be supported, which is to be supplied with the lubricant. The lubrication channels 6 extend in the radial direction through the bearing bush 1 and open into lubrication pockets 8 in the area of the running surface 5. In the exemplary embodiment, three such lubrication pockets 8 are distributed over the circumference of the bearing bush 1 and serve to supply the lubrication gap 7 with lubricant.
    Fig. 2 shows a possible relative position between the shaft 3 and the tread 5 of the bearing bush 1, which can form during operation. 2 that the lubrication gap 7 does not have a uniform dimension when viewed in the circumferential direction, but that the radial thickness of the lubrication gap 7 changes. In FIG. 2, the dimension h S s denotes the so-called minimal bearing play between the running surface 5 of the bearing bush 1 and the shaft 3. When viewed in the direction of rotation and thus in the direction of movement 9 of the shaft 3, the lubricating gap 7 has a h ss in the direction of this minimal bearing play converging lubrication gap section 7a and a lubrication gap section 7b diverging away from this minimal bearing play h ss as seen in the direction of movement 9.
    In the bearing bush 1 according to the invention, the tread 5 of the same has a microstructuring, at least in sections, of a plurality of cup-like recesses 10. The recesses 10 have a maximum depth, so that the following applies:
    V = SLw / tMAX> 0.1 and / or
    Re = (hss + tMAx) * VMAx / vsM 1800, where s L w is the absolute clearance between bearing bush 1 and shaft 3, t M Ax is the maximum depth of the cup-like recesses 10, h S s is the minimum load clearance between bearing bush 1 and Shaft 3, vmax is the maximum peripheral speed of shaft 3, vsm is the kinematic viscosity of a lubricant used for lubrication.
    CH 714 278 A2 The absolute play between the bearing bush 1 and shaft 3 is the difference between an inner diameter of the running surface 5 of the bearing bush 1 and an outer diameter of a section of the shaft 3 supported in the bearing bush 1.
    The following preferably applies:
    0.1 <V <10 and / or
    Re = (hss + tMAx) * VMAx / vsM 2 1800.
    If the cup-like recesses 10 of the microstructuring meet at least one, preferably both, of the above conditions, the bearing bush 1 is less prone to wear.
    As already stated, the microstructuring is introduced at least in sections into the running surface 5 of the bearing bush 1.
    The microstructuring is introduced at least into those sections of the running surface 5 of the bearing bush 1 which are positioned in the region of the converging lubrication gap section 7a between the bearing bush 1 and shaft 3 or which limit the converging lubrication gap section 7a on the outside.
    The microstructuring can also be introduced in the circumferential direction over the entire area of the tread 5 into the tread, but with the recess of the lubrication pockets 8.
    3a, 3b, 3c and 3d each show a top view of a section of the running surface 5 of the bearing bush 1, which has cup-like recesses 10 for providing the microstructuring, in the radial viewing direction.
    In Fig. 3a, these cup-like recesses 10 are arranged to form a cluster 11 in the form of columns and rows, in Fig. 3a, the recesses 10 are arranged equidistant to each other in each column or row, and being seen in plan view the cup-like recesses 10 are all contoured identically rectangular. 3b shows a modification in which all the recesses are contoured in a rectangular shape in plan view, but the recesses 10 are linearly offset with respect to one another in relation to immediately adjacent rows. In Fig. 3c, all cup-like recesses 10 are again contoured rectangular, but have contours differing in size in plan view. In Fig. 3d not only rectangular, cup-like recesses are shown, but also cup-like recesses, which are contoured in a trapezoidal manner, both converging and diverging as seen in the direction of movement 9 of the shaft 3.
    The invention is not limited to rectangular or trapezoidal contoured cup-like recesses 10, rather the cup-like recesses can also be contoured triangular, round, circular, elliptical or the like. The cup-like recesses 10 can not only be seen in the direction of movement 9 of the rotating shaft 3 and linearly offset from one another as seen transversely to the direction of movement 9 of the shaft 3, rather the cup-like recesses can also be rotated relative to one another.
    4a, 4b, 4c, 4d, 4e, 4f, 4g and 4h each show possible cross sections through a cup-like recess 10 of the microstructuring on the running surface 5 of the bearing bushing 1.
    In Fig. 4a, the cup-like recess 10 is contoured in a rectangular manner, with a constant groove base 10a seen in the direction of movement and thus a constant depth of the cup-like recess 10 seen in the direction of movement 9. The groove base 10a and thus the depth of the cup-like recess 10 is also constant in FIG. 4d in the direction of movement 9, likewise in FIG. 4f, but in FIGS. 4d and 4f boundaries adjacent to the groove base 10a do not run perpendicular to the groove base 10a, but are inclined relative to the same. 4b and 4c and in FIG. 4e, the groove base 10 is inclined at least in sections in the direction of movement 9, so that in FIG. 4b the depth of the cup-like recess 10 changes in the direction of movement 9 and converges in FIGS. 4c and 4e. 4g and 4h, the groove base 10a of the respective cup-like recess 10, in contrast to the exemplary embodiments of FIGS. 4a to 4f, is not contoured in a straight line, but rather is curved, namely, in FIG. 4g, it is curved outwards in the direction of the shaft 3 and in Fig. 4b arched inwards away from the shaft 3.
    5a, 5b show a cross section through the bearing bush 4a and shaft 3 analogous to FIGS. 4a to 4h, but not through a cup-like recess 10, but in each case through a plurality of cup-like recesses positioned one behind the other in the direction of movement 9 of the shaft 3 10. In FIG. 5 a, all cup-like recesses have an identical depth, in FIG. 5 b the depth of the cup-like recesses 10 varies.
    The invention accordingly relates to a bearing bush 1 for a turbocharger with a defined microstructuring in the area of its running surface 5. A shaft section of the shaft 3 mounted in the bearing bush 1 can be smooth or also have a microstructuring.
    CH 714 278 A2 With the microstructuring of the running surface 5 of the bearing bush 1, the susceptibility to wear of the bearing bush 1 is reduced, in particular in start-stop operation.
    The cup-like recesses 10 form a kind of lubricant reservoir for the start-stop operation. Furthermore, the cup-like recesses 10 improve the rotor dynamic carrying behavior. Overall, the rotor dynamic behavior of the bearing bush 1 can be improved. The susceptibility to wear of the bearing bush 1 is reduced.
    The bearing bush 1 can be secured against rotation or alternatively rotate relative to the shaft 3.
    LIST OF REFERENCE NUMERALS [0036]
    bearing bush
    recess
    wave
    Inner surface
    4a section of the inner surface
    4b section of the inner surface
    4c section of the inner surface
    tread
    lubrication channel
    lubricating gap
    7a lubrication gap section
    7b lubrication gap section
    lubrication pocket
    direction
    recess
    10a groove base
    cluster
    权利要求:
    Claims (10)
    [1]
    claims
    1. Bearing bush (1) of a turbocharger for the radial mounting of a shaft (3) of the turbocharger, characterized in that the bearing bush (1) on an inner surface (4) facing the shaft (3) to be supported, which has a running surface (5) of the bearing bush forms, at least in sections, has a microstructuring composed of a plurality of cup-like recesses (10), the recesses (10) having a maximum depth, so that:
    V = SlwAmax 0.1 and / or
    Re = (h ss + t M Ax) * VMAx / vsM 1800, where Slw is the absolute clearance between the bearing bush and shaft, where t M Ax is the maximum depth of the cup-like recesses, where h S s is the minimum clearance between the bearing bush and shaft is, where v M ax is the maximum peripheral speed of the shaft, where vsm is the kinematic viscosity of a lubricant used for lubrication.
    [2]
    2. Bearing bush according to claim 1, characterized in that the microstructuring outside of lubrication pockets (8) is introduced into the running surface (5) of the bearing bush.
    [3]
    3. Bearing bush according to claim 1 or 2, characterized in that the microstructuring is introduced at least into those sections of the running surface (5) of the bearing bush which are positioned in the region of a converging lubricating gap section (7a) between the bearing bush (1) and shaft (3) ,
    CH 714 278 A2
    [4]
    4. Bearing bush according to one of claims 1 to 3, characterized in that the depth of the cup-like recesses (10) varies.
    [5]
    5. Bearing bush according to one of claims 1 to 4, characterized in that a contour of the cup-like recesses varies in the radial viewing direction in plan view of the cup-like recesses (10).
    [6]
    6. Bearing bush according to one of claims 1 to 5, characterized in that the cup-like recesses (10) are rectangular or triangular or the trapezoidal or round contoured.
    [7]
    7. Bearing bush according to one of claims 1 to 6, characterized in that the cross-sectional area of the cup-like recesses (10) varies in the axial viewing direction.
    [8]
    8. Bearing bush according to one of claims 1 to 7, characterized in that a groove base (10a) of the cup-like recesses (10) with a constant and / or increasing and / or decreasing depth seen in the direction of rotation of the shaft (3) and / or curved runs.
    [9]
    9. Bearing bush according to one of claims 1 to 8, characterized in that the cup-like recesses (10) of the microstructuring form at least one array-like cluster of equidistant or non-equidistant recesses (10), the recesses (10) being offset linearly from one another in the respective cluster and / or are twisted to each other.
    [10]
    10. Turbocharger, with a turbine for expanding a first medium, the turbine and having a turbine rotor, with a compressor for compressing a second medium using energy obtained in the turbine when expanding, the compressor running one with the turbine rotor via a shaft Coupled compressor rotor, with at least one bearing bush (1) for radial bearing of the shaft, characterized in that the or each bearing bush (1) is designed according to one of claims 1 to 9.
    类似技术:
    公开号 | 公开日 | 专利标题
    EP0227991B1|1990-03-14|Dynamic air bearing
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    EP2282080B1|2014-03-12|Counterbalancing gear
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    EP2052165A2|2009-04-29|Hydrodynamic radial plain bearing having a maximum bearing capacity for large turbo-generators
    EP2094983B1|2013-06-12|Radial roller bearing, in particular for storing shafts in wind turbine transmissions
    DE102005022205A1|2006-11-16|Four row tapered roller bearing
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    EP2507529A1|2012-10-10|Ball bearing cage
    DE10357134A1|2005-06-30|Rotor for a compressor
    EP2333367A1|2011-06-15|Radial roller bearing, in particular for shafts in combustion engines
    DE3936069C2|1993-02-11|
    CH621827A5|1981-02-27|
    CH622863A5|1981-04-30|
    DE2909973A1|1980-10-09|AERODYNAMIC MULTIPLE SPRING BEARING
    CH714278A2|2019-04-30|Bushing of a turbocharger and turbocharger.
    DE102015223975A1|2017-06-08|Balance shaft for an internal combustion engine
    DE102017105576A1|2018-09-20|Bearing arrangement and wind turbine
    DE10309828A1|2004-09-16|roller bearing assembly
    DE102004019530B4|2012-10-31|High-speed bearing for the storage of the spinning rotor of a rotor spinning machine
    DE102012210418A1|2013-12-24|Crankshaft for internal combustion engine of e.g. passenger car, has crankshaft portion that is formed on surface of carrier for rolling elements
    DE102016203147A1|2017-08-31|Hydrodynamic plain bearing
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    同族专利:
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    引用文献:
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    JP2000504089A|1996-01-30|2000-04-04|グリコ―メタル―ウエルケ・グリコ・ベー・ファウ・ウント・コンパニー・コマンディトゲゼルシャフト|Plain bearing element with lubricating oil pocket|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102017125137.5A|DE102017125137A1|2017-10-26|2017-10-26|Bushing of a turbocharger and turbocharger|
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