• 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:
    A turbocharger having a turbine for relaxing a first medium, wherein the turbine comprises a turbine housing and a turbine rotor, with a compressor for compressing a second medium using energy recovered in the turbine during expansion of the first medium, wherein the compressor comprises a compressor housing and a the turbine rotor coupled via a shaft compressor rotor, with an arranged between the turbine housing and the compressor housing bearing housing (9), wherein both the turbine housing and the compressor housing are connected to the bearing housing, with at least one bearing (10), via which the shaft in the bearing housing (9) is mounted, wherein the respective bearing (10) rotatably on the bearing housing (9) mounted bearing bush (11), wherein between the bearing bush (11) and the bearing housing (9) has a radially outer lubrication gap (13) and between the bearing bush (11) and the shaft, a radially inner lubrication gap (14) is formed, and wherein axial ends of the respective bearing bush (11) at a radially outer portion (18, 19) thereof have a greater axial extent than at a radially inner portion (24, 25) thereof.
    公开号:CH714387A2
    申请号:CH01265/18
    申请日:2018-10-17
    公开日:2019-05-31
    发明作者:brandt Sven；Wurm Claudius；Denkel Harald
    申请人:Man Energy Solutions Se；
    IPC主号:
    专利说明:

    Description: The invention relates to a turbocharger.
    [0002] The basic structure of a turbocharger is known from DE 10 2013 002 605 A1. A turbocharger has a turbine in which a first medium is expanded. Furthermore, a turbocharger has a compressor in which a second medium is compressed, using the energy obtained in the turbine when the first medium is expanded. The turbine of the turbocharger has a turbine housing and a turbine rotor. The turbocharger's compressor has a compressor housing and a compressor rotor. A bearing housing is positioned between the turbine housing of the turbine and the compressor housing of the compressor, the bearing housing being connected on the one hand to the turbine housing and on the other hand to the compressor housing. A shaft is mounted in the bearing housing, via which the turbine rotor is coupled to the compressor rotor.
    From practice it is known that the shaft, which couples the turbine rotor of the turbine to the compressor rotor of the compressor, is mounted in the bearing housing via at least one bearing. The respective bearing of the bearing housing for supporting the shaft has a bearing bush, which is either mounted in the bearing housing in a rotationally fixed manner or can rotate. The present invention relates to a turbocharger in which the bearing bush of the bearing is mounted in the bearing housing in a rotationally fixed manner in the region of at least one bearing of the bearing housing. A radially outer lubricating gap is formed between the bearing housing and the bearing bush and a radially inner lubricating gap between the bearing bush and the shaft. The radially outer lubricating gap formed between the bearing housing and the bearing bush is also referred to as a squeeze oil damper.
    In turbochargers known from practice, the respective bearing of the bearing housing is fixed in its axial position in the bearing housing in that the respective bearing bush cooperates with a first axial end with a stop provided by the bearing housing, and that the opposite axial end of the bearing bush with one Lid interacts. The axial end faces of the bearing bush, which are formed at the axial ends of the bearing bush and are opposite either the stop of the bearing housing or the cover, are designed in turbochargers known from practice in such a way that they run continuously perpendicular to the axial direction of the bearing bush. According to this, the respective bearing bush comes to rest over the entire area of the shoulder of the bearing housing and on the cover via its axial end faces. In order to avoid excessive friction between the axial end faces of the bearing bush and the stop of the bearing housing or the cover, a defined axial gap is set between the axial end faces of the bearing bush and the stop of the bearing housing and the cover, but this leads to oil losses, particularly in the area of the radially outer lubricating gap, which acts as an oil damper.
    Proceeding from this, the present invention has for its object to provide a novel turbocharger. This object is achieved by a turbocharger according to claim 1. According to the invention, the axial ends of the respective bearing bush have a greater axial extent on a radially outer section thereof than on a radially inner section thereof. With the invention, the axial play for the bearing bush of the respective bearing of the bearing housing of the turbocharger can be reduced without the risk of excessive friction between the axial end faces of the bearing bush and the bearing housing or cover. Because the axial ends of the respective bearing bush have a greater axial extent radially on the outside than radially on the inside, a very small axial gap can be set between the bearing bush and the bearing housing or cover. Oil losses can be reduced. The outer lubrication gap, which acts as an oil damper, can optimally provide its squeeze oil damper function.
    According to an advantageous development, at least one of the axial ends of the respective bearing bush lies only with the respective radially outer section on the bearing housing or on the cover. In this area, a very small axial gap is set between the bearing bush and the bearing housing or cover, which means that oil losses can be reduced. Preferably, a first axial end of the respective bearing bush lies only with a radially outer section on the bearing housing, a second axial end of the respective bearing bush lying only with a radially outer section on the cover. These features serve to ensure minimal axial play with regard to the axial position of the respective bearing bush in the bearing housing while avoiding excessive friction and reducing oil losses.
    According to an advantageous development of the invention, a groove is formed at the axial end of the respective bearing bush, which adjoins the cover, into which a projection of the cover engages to form an anti-rotation device, the groove being at a radial distance from the radially outer surface the bearing sleeve and to the radially outer portion of the axial end. This can be used to secure the bearing bush against rotation without the risk of oil loss for the radially outer lubricating gap.
    The axial ends of the respective bearing bush are chamfered on the end faces either funnel-like radially inward or the same are contoured in a step-like manner radially inward. These contours of the axial ends or axial end faces of the bearing bush are particularly preferred in order to ensure that axial ends of the respective bearing bush have a greater axial extent on a radially outer section thereof than on a radially inner section thereof, and that in particular the bearing bush only has radially outer sections on the bearing housing and on the cover comes into contact.
    CH 714 387 A2 Preferred 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 a cross section through a turbocharger according to the prior art.
    2 shows a cross section through a turbocharger in the region of a bearing of the bearing housing;
    3 shows a detail of a first turbocharger according to the invention in the region of a bearing of the bearing housing;
    4 shows a detail of a second turbocharger according to the invention in the region of a bearing of the bearing housing;
    5 is a side view of the detail of FIG. 4.
    The invention relates to a turbocharger.
    A turbocharger 1 has a turbine 2 for expanding a first medium, in particular for expanding exhaust gas from an internal combustion engine. Furthermore, a turbocharger 1 has a compressor 3 for compressing a second medium, in particular charge air, using energy obtained in the turbine 2 when the first medium is expanded. The turbine 2 has a turbine housing 4 and a turbine rotor 5. The compressor 3 has a compressor housing 6 and a compressor rotor 7. The compressor rotor 7 is coupled to the turbine rotor 5 via a shaft 8 which is mounted in a bearing housing 9, the Bearing housing 9 positioned between the turbine housing 4 and the compressor housing 5 and is connected to both the turbine housing 4 and the compressor housing 5.
    The shaft 8, which couples the turbine rotor 5 of the turbine 2 to the compressor rotor 7 of the compressor 3, is mounted in the bearing housing 9, namely via at least one bearing 10 of the bearing housing 9. Preferably, the bearing housing 9 comprises two bearings 10 for Bearing of the shaft 8, a first bearing 10 engaging on a section of the shaft 8 facing the turbine rotor 5, and a second bearing 10 engaging on an end of the shaft 8 facing the compressor rotor 7.
    The respective bearing 10 has a bearing bush 11, which is mounted in the bearing housing 9, in particular in a bearing body of the bearing housing 9, in a rotationally fixed manner. Such a bearing bush 11 mounted in a rotationally fixed manner in the bearing housing 9 or in a rotationally fixed manner on the bearing housing 9 is a housing-side, stator-side assembly which stands still when the shaft 8 rotates.
    Between the rotatably mounted in the bearing housing 9 bearing bush 11 and the bearing housing 9, a radially outer lubricating gap 13 and a radially inner lubricating gap 14 is formed between the bearing bush 11 and the shaft 8. The radially outer lubricating gap 13 formed between the bearing housing 9 and the bearing bush 11 acts as a squeeze oil damper.
    The bearing bush 11 is inserted into a recess in the bearing housing 9 and adjoins with an axial end on a stop formed by the bearing housing 9. A cover 12 is positioned at the opposite axial end of the bearing bush 11, which together with the bearing housing 9 provides the axial positioning of the bearing bush 11 in the bearing housing 9.
    For the purposes of the present invention, it is provided that axial ends of the respective bearing bush 11 have a greater axial extent on a radially outer section 18, 19 thereof than on a radially inner section 24, 25 of the same.
    Preferably, the bearing bush 11 at both opposite axial ends with its axial end faces 16, 17 only with the radially outer portion 18 and 19 on the bearing housing 9, namely on the shoulder 15 of the bearing housing 9, and on the cover 12, but not with the radially inner section 24, 25.
    In the area of the axial ends or end faces 16, 17 of the bearing bush 11, a minimal axial play between the bearing bush 11 and the bearing housing 9 and cover 12 is provided without the risk of excessive friction between the bearing bush 11 and cover 12 and between the bearing bush 11 and bearing housing 9, with this minimal axial gap preventing oil losses in the region of the radially outer lubricating gap 13 serving as an oil-damping damper.
    According to the preferred embodiments shown, the bearing bush 11 lies at a first axial end with the corresponding first axial end face 16 in the region of the radially outer section 18 on the projection 15 of the bearing housing 9, at the opposite axial end or the opposite axial end face 17 of the bearing bush 11 lies against the cover 12 with the radially outer section 19.
    It is also possible that the radially outer section 18 does not abut the projection 15 of the bearing housing 9 and / or the radially outer section 19 does not rest on the cover 12. In this case, there is at least one of the axial ends of the respective bearing bush 11 between the respective radially outer section 18, 19 and the bearing housing
    CH 714 387 A2 and / or the cover 12 an axial play is formed which is smaller than the axial play in the area of the respective radially inner section 24, 25 of the respective axial end of the respective bearing bush 11.
    In the embodiment of FIG. 3, the bearing bush 11 is chamfered radially inward in the region of its axial end faces 16, 17, in the exemplary embodiment of FIG. 4 the axial end faces 16, 17 of the bearing bush 11 are contoured in a stepped manner radially inward, so that Accordingly, in both exemplary embodiments, the bearing bush 11 only comes into contact with its radially outer sections 18, 19 on the shoulder 15 of the bearing housing 9 and on the cover 12.
    In the exemplary embodiments shown, a groove 20 is formed on that axial end of the bearing bush 11 or on that axial end face 17 which lies opposite the cover 12 or adjoins the cover 12, into which a projection 21 forms an anti-rotation device of the lid 12 engages. This groove 20 ends at a radial distance from the radially outer surface of the bearing bush 11 or at a radial distance from the radially outer section 19 of the end face 17, which comes to rest on the cover 12 in the exemplary embodiments shown. The radial distance between the radially outer end of the groove 20 and the radially outer surface of the bearing bush 11 is accordingly dimensioned such that the groove 20 ends at a distance from the radially outer portion 19 of the axial end of the bearing bush 11, with which in the exemplary embodiments shown the bearing bush 11 abuts the cover 12.
    In other words, the groove 20 does not extend into the radially outer portion 19 of the axial end face 17 of the bearing bush 11, with which the bearing bush 11 rests on the cover 12 in the exemplary embodiments shown.
    The acting as a pinch oil damper, radially outer lubricating gap 13 between the bearing bush 11 and the bearing housing 9 is supplied with lubricating oil via at least one line 22 starting from an oil supply main line 23 of the bearing housing 9 (see FIG. 2), the or each line 22 , which, starting from the main oil supply line 23, supplies the radially outer lubricating gap 13 with oil, opens radially outside into the radially outer lubricating gap 13.
    Via lines, not shown, which extend through the bearing bush 11 in the radial direction, starting from the radially outer lubricating gap 13, the radially inner lubricating gap 14 can also be supplied with lubricating oil.
    With the invention, modified designs or contours of the axial end faces 16, 17 of the bearing bush 11, which are also referred to as bearing bush flanks, are proposed in order to reduce the axial play between the bearing bush 11, the bearing housing 9 and the cover 12. The axial end faces 16, 17 of the bearing bush 11 are designed or contoured in such a way that the axial ends of the bearing bush 11 have a greater axial extent on the radially outer section 18, 19 thereof than on the radially inner section 24, 25 of the same. The axial end faces 16, 17 of the bearing bush 11 can be designed or contoured in such a way that the bearing bush 11 only bears on the bearing housing 9 and cover 12 via its axial ends with radially outer sections 18, 19. Friction in the area of the bearing bush 11 is reduced, and oil losses via the axial gap between the bearing bush 11 and the bearing housing 9 and the axial gap between the bearing bush 11 and the cover 12 are also reduced. The radially outer lubricating gap 13 can optimally provide its function as a lubricating oil damper.
    According to a particularly preferred development, a novel anti-rotation device for the bearing bush 11 is further proposed, namely by the interaction of the groove 20 introduced into the axial end face 17 of the bearing bush 11 and the projection 21 of the cover 12, this groove 20 not extends into the area or not into the radially outer section 19 of the bearing bush 11, with which the bearing bush 11 comes to rest on the cover 12 in the exemplary embodiment shown. Accordingly, the anti-rotation device does not impair the damping effect of the radially outer lubricating gap or the squeeze oil damper and does not impair the reduction in the axial play between the bearing bush 11 and the bearing housing 9 and the cover 12.
    In the area of the radially outer portions 18, 19 of the bearing bush 11, with which the bearing bush 11 comes to rest on the projection 15 of the bearing housing 9 and on the cover 12, so-called run-in wear on the end faces 16, 17 of the bearing bush 11 can be optimally adjusted ,
    [0028] The invention can be used in any type of turbocharger. The invention is independent of the specific design of the turbine and the compressor. The invention is also independent of the specific design of an internal combustion engine which interacts with the turbocharger.
    Reference symbol list [0029]
    turbocharger
    turbine
    compressor
    turbine housing
    turbine rotor
    CH 714 387 A2
    compressor housing
    compressor rotor
    wave
    bearing housing
    camp
    bearing bush
    cover
    lubricating gap
    lubricating gap
    attack
    face
    End face of radially outer section of radially outer section
    groove
    head Start
    management
    Main oil supply line, radially inner section, radially inner section
    权利要求:
    Claims (10)
    [1]
    1. Turbocharger (1), with a turbine (2) for expanding a first medium, the turbine (2) having a turbine housing (4) and a turbine rotor (5), with a compressor (3) for compressing a second medium Use of energy obtained in the turbine (2) when the first medium relaxes, the compressor (3) having a compressor housing (6) and a compressor rotor (7) coupled to the turbine rotor (5) via a shaft (8), with a bearing housing (9) arranged between the turbine housing (4) and the compressor housing (6), both the turbine housing (4) and the compressor housing (6) being connected to the bearing housing (9), with at least one bearing (10) which the shaft (8) is mounted in the bearing housing (9), the respective bearing (10) having a bearing bush (11) mounted on the bearing housing (9) in a manner fixed against relative rotation, with a bearing bush (11) and the bearing housing (9) between radially outer lubricating gap (13) u A radially inner lubricating gap (14) is formed between the bearing bush (11) and the shaft (8), characterized in that axial ends of the respective bearing bush (11) have a greater axial extent at a radially outer section (18, 19) thereof than on a radially inner portion (24, 25) of the same.
    [2]
    2. Turbocharger according to claim 1, characterized in that at least one of the axial ends of the respective bearing bush (11) abuts only with the respective radially outer section (18, 19) on the bearing housing (9) or on a cover (12).
    [3]
    3. Turbocharger according to claim 1 or 2, characterized in that a first axial end of the respective bearing bush (11) abuts only with the respective radially outer section (18) on the bearing housing (9), and / or a second axial end of the respective bearing bush (11) only bears with the respective radially outer section (19) on the cover (12).
    CH 714 387 A2
    [4]
    4. Turbocharger according to one of claims 1 to 3, characterized in that on at least one of the axial ends of the respective bearing bush (11) between the respective radially outer section (18, 19) and the bearing housing (9) or on a cover (12 ) an axial play is formed.
    [5]
    5. Turbocharger according to one of claims 2 to 4, characterized in that at the axial end of the respective bearing bush (11), which is adjacent to the cover (20), a groove (20) is formed, into which a projection (21) of the cover (12) engages to form an anti-rotation device.
    [6]
    6. Turbocharger according to claim 5, characterized in that the groove (20) ends at a radial distance from the radially outer surface of the bearing bush (11).
    [7]
    7. Turbocharger according to claim 6, characterized in that the radial distance between the end of the groove (20) and the radially outer surface of the bearing bush (11) is dimensioned such that the groove (20) is spaced from the radially outer section ( 19) of the axial end of the bearing bush (11), which adjoins the cover (20).
    [8]
    8. Turbocharger according to claim 6 or 7, characterized in that the radial distance between the end of the groove (20) and the radially outer surface of the bearing bush (11) is dimensioned such that the groove (20) is not in the radially outer Section (19) of the axial end of the bearing bush (11) extends into it, which adjoins the cover (20).
    [9]
    9. Turbocharger according to one of claims 1 to 8, characterized in that the axial ends of the respective bearing bush (11) on end faces (16, 17) are chamfered radially inwards.
    [10]
    10. Turbocharger according to one of claims 1 to 8, characterized in that the axial ends of the respective bearing bush (11) on end faces (16, 17) are contoured radially inward in steps.
    CH 714 387 A2
    CH 714 387 A2 /
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    CH 714 387 A2
    类似技术:
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    同族专利:
    公开号 | 公开日
    US10598043B2|2020-03-24|
    KR20190056312A|2019-05-24|
    DE102017126950A1|2019-05-16|
    JP2019090413A|2019-06-13|
    CN109798188A|2019-05-24|
    US20190145281A1|2019-05-16|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102017126950.9A|DE102017126950A1|2017-11-16|2017-11-16|turbocharger|
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