• 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, said turbine having a turbine housing and a turbine rotor, with a compressor for compressing a second medium using energy recovered in the turbine upon expansion of the first medium, the compressor comprising a compressor housing and a turbine comprising a compressor rotor coupled to the turbine rotor via a shaft, with a bearing housing (9) arranged between the turbine housing and the compressor housing, wherein both the turbine housing and the compressor housing are connected to the bearing housing (9) with at least one bearing (10) in which the shaft is mounted in the bearing housing (9), the respective bearing (10) having a bearing bush (11) rotatably mounted in the bearing housing (9), 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, wherein the radially inner lubrication gap (14) via at least one in the bearing bush (11) introduced line (20) can be supplied with lubricating oil, wherein the or each in the bearing bush (11) introduced line (20), the oil supply of the radially inner lubricating gap (14), in each case a lubricating oil bag (21) of the bearing bush (11) opens, which is placed eccentrically relative to the axial length of the bearing bush (11).
    公开号:CH714385A2
    申请号:CH01251/18
    申请日:2018-10-12
    公开日:2019-05-31
    发明作者:brandt Sven
    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, which is formed between the bearing housing and the bearing bush mounted in a rotationally fixed manner in the bearing housing, is also referred to as a squeeze oil damper.
    The radially inner lubricating gap can be supplied with lubricating oil via at least one line introduced into the bearing bush, in turbochargers known from practice starting from the radially outer lubricating gap.
    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 or each line, which is introduced into the bearing bush and serves to supply oil to the radially inner lubricating gap, opens into a lubricating oil pocket of the bearing bush, which is positioned eccentrically in relation to the axial length of the bearing bush and which is preferably opposite the axial direction of the bearing bush and the direction of rotation of the Shaft is inclined. The fact that in the turbocharger according to the invention the respective line introduced into the bearing bush, which serves to supply oil to the radially inner gap, opens into an eccentric lubricating oil pocket of the bearing bush, which is preferably inclined relative to the axial direction of the bearing bush and relative to the direction of rotation of the shaft, the lubricating oil can in particular are advantageously conveyed in the direction of the radially inner lubricating gap, namely in that the rotation of the shaft promotes or supports the conveyance of the lubricating oil in the direction of the radially inner lubricating gap.
    Preferably, the or each lubricating oil pocket merges into a lubricating oil groove, which is also inclined relative to the axial direction of the bearing bush and the direction of rotation of the shaft, in particular in such a way that lubricating oil grooves introduced into the bearing bush starting from an axial end of the bearing bush via which the oil supply to the Bearing bush is made to diverge towards an opposite axial end of the bearing bush. This configuration of the lubricating oil grooves allows the lubricating oil to be conveyed into the radially inner lubricating gap in a particularly advantageous manner using the shaft rotation.
    According to an advantageous development of the invention, the radially outer lubricating gap and the radially inner lubricating gap can be supplied with lubricating oil independently of one another, starting from an oil supply main line. The radially outer lubricating gap can preferably be supplied with lubricating oil via at least one first line branching off the main oil supply line, the radially inner lubricating gap being able to be supplied with lubricating oil via at least one second line branching off the main oil supply line. The inner lubricating gap is then not supplied with lubricating oil starting from the outer lubricating gap, but rather starting from the main oil supply line. There is then no danger that the functionality of the radially outer lubrication gap is impaired by the oil supply to the radially inner lubrication gap. The radially outer lubricating gap can function undisturbed as a squeeze oil damper.
    According to an advantageous development of the invention, the or each first line opens radially outside into the radially outer lubricating gap, the or every second line opening on an axial side of the bearing bush into an annular channel of the bearing housing. The or each line introduced into the bearing bush conveys the lubricating oil from the ring channel into the area of the radially inner lubricating gap. The or each line introduced into the bearing bush is preferably inclined with respect to the axial direction and / or with respect to the radial direction of the bearing bush. This also serves to support the delivery of lubricating oil into the area of the radially inner lubricating gap without the risk of impairing the squeeze oil damper function of the radially outer lubricating gap.
    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.
    CH 714 385 A2
    2 shows a cross section through a first turbocharger according to the invention in the region of a bearing of the bearing housing; and
    3 shows detail III of FIG. 2.
    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.
    2, 3 show details of a turbocharger according to the invention in the region of a bearing 10 of the bearing housing 9, the bearing 10 shown in FIG. 2 of the bearing of the shaft 8 of the turbocharger 1 coupling the turbine rotor 5 and the compressor rotor 7 in the bearing housing 9 serves. There are preferably two such bearings 10, a first bearing 10 engaging on a section facing the turbine rotor 5 and a second bearing 10 engaging on a section of the shaft 8 facing the compressor rotor 7.
    The bearing 10 of Fig. 2, 3 has a bearing bush 11 which is rotatably mounted in the bearing housing 9 or non-rotatably on the bearing housing 9 by means not shown.
    Due to this rotationally fixed mounting of the bearing bush 11 in the bearing housing 9, the bearing bush 11 is designed as a housing-fixed assembly which stands still during the rotation of the shaft 8.
    The axial position of the bearing bush 11 is fixed on the one hand by the bearing housing 9 and on the other hand by a cover, with one axial end of the bearing bush 11 coming to rest on a stop formed by the bearing housing 9 and an opposite axial end of the bearing bush 11 with the cover 12 interacts. An axial gap 19 is formed between the axial end of the bearing bush 11, which comes to rest against the stop formed by the bearing housing 9, and the bearing housing 9.
    Between the rotatably mounted in or on the bearing housing 9 bearing bush 11 and the bearing housing 9, a radially outer lubricating gap 13 is formed, between the bearing bush 11 and the shaft 8, a radially inner lubricating gap 14 is formed. The radially outer lubricating gap 13 functions in particular as a squeeze oil damper.
    Both the radially outer lubricating gap 13 and the radially inner lubricating gap 14 can be supplied with lubricating oil starting from an oil supply main line 15, either depending on one another or preferably independently of one another. In any case, at least one line 20 is introduced into the bearing bush 11, via which the radially inner lubricating gap 14 can be supplied with lubricating oil, namely with a lubricating oil supply dependent on the outer lubricating oil gap 13 starting from the outer lubricating oil gap 13 and with a lubricating oil supply independent of the outer lubricating oil gap starting from the main oil supply line 15.
    According to the present invention, it is proposed that the or each line 20 introduced into the bearing bush 11, which serves to supply oil to the radially inner lubricating gap 14, opens into a lubricating oil pocket 21 which is introduced into a radially inner surface of the bearing bush 11, the respective lubricating oil pocket 21 is positioned off-center in relation to the axial length of the bearing bush 11 and is preferably inclined relative to the axial direction A of the bearing bush 11 and thus also with respect to the direction of rotation R of the shaft 8.
    Preferably, a plurality of lines 20 are introduced into the bearing bush 11, which serve to supply the lubricating oil to the inner lubricating oil gap 14, each of these lines 20 opening into a lubricating oil pocket 21 which is eccentrically placed with respect to the axial length of the bearing bush 11 and preferably opposite one another the axial direction A of the bearing bush 11 and the direction of rotation R of the shaft 8 is inclined.
    The lubricating oil pockets 21 merge into lubricating oil grooves 23, which are designed to be narrower in the circumferential direction than the lubricating oil pockets 21, each of the lubricating oil grooves 23 also being inclined with respect to the axial direction of the bearing bush 11 and the radial direction of the shaft 8. The lubricating oil grooves 23 are so inclined relative to the axial direction A of the bearing bush 11 and the direction of rotation R of the shaft 8 that lubricating oil grooves 23 introduced into the bearing bush 11 proceed in the direction from the axial end of the bearing bush 11, via which the oil supply to the bearing bush 11 takes place diverge on an opposite axial end of the bearing bush 11, so that the respective lubricating oil groove 23, starting from the axial end of the bearing bush 11, via which the oil supply to the bearing bush 11 takes place, drops towards the opposite axial end of the bearing bush 11.
    2, 3, the oil supply to the bearing bush 11 takes place via that axial end of the bearing bush 11 which interacts with the stop of the bearing housing 9. Starting from this axial end
    CH 714 385 A2, the lubricating oil grooves 23 drop in the direction of the opposite axial end of the bearing bush 11 or diverge in the direction of this opposite axial end, which cooperates with the cover 12.
    The lubricating oil grooves 23 extend between the axial ends of the bearing bush 11. The lubricating oil pockets 21, into which a respective line 20 introduced into the bearing bush 11 for supplying lubricating oil to the radially inner lubricating gap 14 with an orifice point 22, have a smaller width in Circumferential direction than the lubricating oil grooves 23, wherein the lubricating oil grooves 23, viewed in the axial direction, extend almost continuously from one axial end of the bearing bush 11 towards the other axial end of the bearing bush 11. In particular, the lubricating oil grooves 23 each end at a defined distance in front of these axial ends, this distance being defined by the axial depth of a chamfer formed in the region of the axial ends on the radially inner surface of the bearing bush 11. The lubricating oil pockets 21 are positioned eccentrically in the respective lubricating oil groove 23 in relation to the axial length of the bearing bush 11.
    As shown in FIG. 2, the radially inner lubricating gap 14 and the radially outer lubricating gap 13 can be supplied independently with lubricating oil starting from the main oil supply line 15. 2, at least one first line 16 branches off from the main oil supply line 15, via which oil starting from the main oil supply line 15 can be fed to the radially outer lubricating gap 13. At least one second line 17 branches off from the main oil supply line 15, via which the radially inner lubricating gap 14 can be supplied with lubricating oil starting from the main oil supply line 15 independently of the radially outer lubricating gap 13.
    In the embodiment shown in Fig. 2, the or each first line 16, which serves to supply the outer lubricating gap 13 with oil, opens radially outside into the radially outer lubricating gap 13. The or every second line 17, which is the oil supply to the radial inner lubricating gap 14, opens at an axial end or on an axial side of the bearing bush 11 into an annular channel 18 of the bearing housing 19, namely on the side of the bearing bush 11 opposite the cover 12.
    This ring channel 18 is circumferentially introduced into the bearing housing 9, namely axially laterally next to the bearing bush 11 on the side of the bearing bush 11 opposite the cover 12.
    2, the lubricating oil can be fed from the annular channel 18 to the radially inner lubricating gap 14 via the or each line 20 introduced into the bearing bushing 11, which extends from the annular channel 18 into the region of the radially inner lubricating gap 14 and there in the Area of the lubricating oil pocket 21 opens. Here, the or each line 20 introduced into the bearing bush 11 is inclined with respect to the axial direction of the bearing bush 11 and / or with respect to the radial direction of the bearing bush 11.
    Reference symbol list [0026]
    turbocharger
    turbine
    compressor
    turbine housing
    turbine rotor
    compressor housing
    compressor rotor
    wave
    bearing housing
    camp
    bearing bush
    cover
    lubricating gap
    lubricating gap
    Oil supply main line
    management
    CH 714 385 A2
    management
    annular gap
    axial gap
    management
    Oil bag
    mouth end
    lubricating oil groove
    权利要求:
    Claims (12)
    [1]
    claims
    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 in a rotationally fixed manner in the bearing housing (9), a between the bearing bush (11) and the bearing housing (9) radially outer lubricating gap (13) u nd a radially inner lubricating gap (14) is formed between the bearing bush (11) and the shaft (8), the radially inner lubricating gap (14) being able to be supplied with lubricating oil via at least one line (20) introduced into the bearing bush (11), characterized in that the or each line (20) introduced into the bearing bush (11) and used to supply oil to the radially inner lubricating gap (14) opens into a respective lubricating oil pocket (21) of the bearing bush (11), which is related to the axial one Length of the bearing bush (11) is placed off-center.
    [2]
    2. Turbocharger according to claim 1, characterized in that the or each lubricating oil pocket (21) is inclined relative to the axial direction of the bearing bush (11).
    [3]
    3. Turbocharger according to claim 1 or 2, characterized in that the or each lubricating oil pocket (21) is inclined relative to the direction of rotation of the shaft (8).
    [4]
    4. Turbocharger according to one of claims 1 to 3, characterized in that the or each lubricating oil pocket (21) merges into a respective lubricating oil groove (23) which is inclined with respect to the direction of rotation of the shaft (8).
    [5]
    5. Turbocharger according to claim 4, characterized in that the or each lubricating oil groove (23) is inclined with respect to the axial direction of the bearing bush (11)
    [6]
    6. Turbocharger according to claim 4 or 5, characterized in that the or each in the bearing bush (11) introduced lubricating oil groove (23) starting from an axial end of the bearing bush (11), via which the oil supply to the bearing bush (11) takes place in Direction drops to an opposite axial end of the bearing bush (11).
    [7]
    7. Turbocharger according to one of claims 4 to 6, characterized in that in the bearing bush (11) introduced lubricating oil grooves (23) starting from an axial end of the bearing bush (11), via which the oil supply to the bearing bush (11) takes place in the direction diverge on an opposite axial end of the bearing bush (11).
    [8]
    8. Turbocharger according to one of claims 1 to 7, characterized in that the radially outer lubricating gap (13) and the radially inner lubricating gap (14) can be supplied independently of one another with lubricating oil starting from an oil supply main line (15), the radially outer lubricating gap ( 13) can be supplied with lubricating oil via at least one first line (16) branching off from the main oil supply line (15), and the radially inner lubricating gap (14) can be supplied with lubricating oil via at least one second line (17) branching off from the main oil supply line (15) ,
    [9]
    9. Turbocharger according to claim 8, characterized in that the or each first line (16) opens radially outside into the radially outer lubricating gap (13).
    [10]
    10. Turbocharger according to claim 8 or 9, characterized in that the or every second line (17) on an axial side of the bearing bush (11) opens into an annular channel (18) of the bearing housing (9).
    CH 714 385 A2
    [11]
    11. Turbocharger according to claim 9, characterized in that the or each line (20) introduced into the bearing bush (11) conveys the lubricating oil starting from the annular channel (18) into the region of the radially inner lubricating gap (14).
    [12]
    12. Turbocharger according to claim 11, characterized in that the or each line (20) introduced into the bearing bush (11) is inclined with respect to the axial direction and / or with respect to the radial direction of the bearing bush (11).
    CH 714 385 A2
    Ιη
    CH 714 385 A2
    类似技术:
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    EP1396612A1|2004-03-10|Sealing for a fluid energy machine
    CH714387A2|2019-05-31|Turbocharger.
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    DE102010031200B4|2013-10-24|Main and / or connecting rod bearing with a bearing metal layer and a sliding layer
    同族专利:
    公开号 | 公开日
    CN109798190A|2019-05-24|
    KR20190056309A|2019-05-24|
    DE102017126933A1|2019-05-16|
    US20190145279A1|2019-05-16|
    US10648364B2|2020-05-12|
    JP2019090408A|2019-06-13|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102017126933.9A|DE102017126933A1|2017-11-16|2017-11-16|turbocharger|
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