WO2010135135A2 - Palier hydrodynamique - Google Patents

Palier hydrodynamique Download PDF

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Publication number
WO2010135135A2
WO2010135135A2 PCT/US2010/034672 US2010034672W WO2010135135A2 WO 2010135135 A2 WO2010135135 A2 WO 2010135135A2 US 2010034672 W US2010034672 W US 2010034672W WO 2010135135 A2 WO2010135135 A2 WO 2010135135A2
Authority
WO
WIPO (PCT)
Prior art keywords
rotor shaft
bearing
cross
section
hydrodynamic bearing
Prior art date
Application number
PCT/US2010/034672
Other languages
English (en)
Other versions
WO2010135135A3 (fr
Inventor
Joachim Hettmann
Original Assignee
Borgwarner Inc.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Borgwarner Inc. filed Critical Borgwarner Inc.
Publication of WO2010135135A2 publication Critical patent/WO2010135135A2/fr
Publication of WO2010135135A3 publication Critical patent/WO2010135135A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/166—Sliding contact bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/50—Bearings
    • F05D2240/53—Hydrodynamic or hydrostatic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers

Definitions

  • the invention relates to a hydrodynamic bearing for a rotating rotor shaft of an exhaust-gas turbo charger.
  • a rotating exhaust-gas turbocharger rotor shaft which is supported by means of cylindrical plain bearings has an instability in certain operating states (oil whirl and whip effect).
  • the rotor shaft deflects in an uncontrolled fashion, and this can result in contact between said rotor shaft and the plain bearing.
  • This is conventionally prevented by using a multiple-wedge-surface bearing.
  • the rotor shaft is "braced" or supported in the rotor system, with a plurality of pressure fields building up at the periphery of said rotor shaft and stabilizing any occurring deflections of the rotor system.
  • the use of multiple-wedge- surface bearings has the disadvantage, however, that it is very cumbersome and expensive and in part can not yet be technically realized in the case of small supercharger designs.
  • the hydrodynamic bearing according to the invention has the advantage that it provides optimized damping of the rotor shaft on account of rotating oil pressure fields, with the oil film of the lubricant between the bearing shell and the rotor shaft being built up earlier, in particular during the starting phase of the turbocharger. In this way, more stable running of the rotor shaft can be ensured in relation to the use of a multiple-wedge-surface bearing.
  • Figure 1 shows a schematically slightly simplified sectional illustration of a turbocharger
  • Figure 2 shows a schematically simplified sectional illustration of a first embodiment of a hydrodynamic bearing according to the invention with an elliptical rotor shaft.
  • Figure 3 shows a sectional illustration, corresponding to Figure 2. of a second embodiment of the hydrodynamic bearing with a polygonal rotor shaft.
  • Figure 4 shows an alternative cross-sectional shape of a rotor shaft for the hydrodynamic bearing, and
  • Figure 5 shows a further cross-sectional shape of the rotor shaft for the hydrodynamic bearing. Embodiments of the hydrodynamic bearing according to the invention will be described below with reference to Figure 1 to Figure 5.
  • FIG. 1 shows a schematically slightly simplified sectional illustration of a turbocharger 2 in which a hydrodynamic bearing 1 according to the invention, which will be described below on the basis of Figures 2 and 3, can be used.
  • the turbocharger 2 has a compressor housing 8, to which a bearing housing 10 is fastened, and a turbine housing 1 1. which is connected to the bearing housing 10.
  • a rotor shaft 3 which is arranged axially centrally in the bearing housing 10, and which is supported in each case at a region 3a of the rotor shaft 3 in bearing bushes 4, has at its compressor-side end a compressor wheel 9 which is fastened to the rotor shaft 3 and at its turbine-side end a turbine wheel 12 which is fastened to the rotor shaft 3.
  • an oil supply 13 is formed in the bearing housing 10, which oil supply 13 supplies a lubricant to the two hydrodynamic bearings 1 illustrated in Figure 1 and also to an axial bearing (not shown in this figure) between the compressor housing 8 and the bearing housing 10, which lubricant is discharged out of the bearing housing 10 again through an oil outlet 14.
  • Figure 2 shows a schematic sectional illustration of a first embodiment of the hydrodynamic bearing 1 according to the invention, having a cylindrical bearing bush 4 in which the rotor shaft 3 is arranged.
  • the region 3a of the rotor shaft 3 in the bearing bush 4 (see Figure 1) has an elliptical cross section 5.
  • the cross section 5, which deviates from the cylindrical cross section of the bearing bush 4, of the rotor shaft forms a space 6 which is filled with oil.
  • the rotation of the rotor shaft 3 causes a pressure field 7 and 7' to be built up in each case in a region B, B', in which a spacing A between the inner periphery of the bearing bush 4 and the outer periphery of the rotor shaft (3) has a minimum value, as a result of the increased pressure of the oil in the space 6 in said region.
  • the two pressure fields 7, 7' which are built up in the regions B and B' in the space 6 between the rotor shaft 3 and the bearing bush 4 rotate synchronously with the rotational speed of the rotor shaft 3.
  • FIG. 3 shows a sectional illustration, corresponding to Figure 2, of a second embodiment of the hydrodynamic bearing 1 according to the invention.
  • identical components are denoted by the same reference symbols as in the first embodiment illustrated in Figure 1.
  • the region 3 a of the rotor shaft 3 in the bearing bush 4 has a polygonal cross section 5'.
  • the rotor shaft 3 with the polygonal cross section 5' in said second embodiment causes three pressure fields 7, 7', 7" with increased oil pressure to be built up in the three regions B, B', B", which pressure fields 7, T, 7" serve to stabilize the rotor shaft 3 in the bearing bush 4.
  • Figure 4 shows a sectional illustration of an alternative cross-sectional shape of the rotor shaft 3 for the hydrodynamic bearing 1 according to the invention.
  • the region 3a of the rotor shaft 3 has a substantially circular cross section 5" in which three peripheral regions, the central points of which have in each case an angular interval of 120°, are truncated in the form of circle segments 15.
  • FIG. 4 shows an illustration, corresponding to Figure 4, of a further alternative cross-sectional shape of the rotor shaft 3 for the hydrodynamic bearing 1 according to the invention.
  • the region 3a of the rotor shaft 3 has a substantially circular cross section 5'", like the rotor shaft 3 illustrated in Figure 4.
  • the rotor shaft 3 has three peripheral regions whose centers have in each case an angular interval of 120° and which in each case are cut out in the form of wedge-shaped indentations 16 on the periphery 3b of the rotor shaft 3.
  • Said indentations 16 on the periphery 3b of the rotor shaft 3 have in each case one straight region 16a which slopes inward in the rotational direction and which, at the end of the indentation 16 in the rotational direction of the rotor shaft 3, projects outward again, in the form of a shoulder 16b, to the original outer periphery 3b of the rotor shaft 3.
  • the cross-sectional shape of the rotor shaft 3 illustrated here generates a pressure which initially constantly falls slightly in the peripheral direction in relation to the oil pressure prevailing in the regions B, B', B" in the space 6 between the bearing bush 4 and the rotor shaft 3, and said pressure then rises again abruptly at the end of the indentation 16 to the pressure prevailing in the region B, B' and B".
  • any cross-sectional shape based on polygonal cross sections or modified circular cross sections not illustrated here which generate three or more rotating pressure fields 7, 7', 7".
  • the pressure fields 1, T, T generated as a result of the change in the spacing A between the outer periphery 3b of the rotor shaft and the inner periphery 4a of the bearing bush 4 rotate with the same frequency as the rotor shaft 3.
  • the pressure fields rotate with a bush rotational speed which is significantly lower than the rotor rotational speed, and which cannot satisfactorily dampen a possible deflection of the rotor shaft 3, in particular in the event of a rotational speed change occurring as a result of a load shift of the exhaust-gas turbo charger.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Supercharger (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

La présente invention concerne un palier hydrodynamique (1) pour un arbre de rotor rotatif (3) d'un turbocompresseur à échappement de gaz (2) ayant au moins un coussinet de palier cylindrique (4), l'arbre de rotor (3) comprenant, dans une région (3a) qui est agencée dans le coussinet de palier (4), une coupe transversale (5) s'écartant d'une coupe transversale circulaire et un espace (6) situé entre la périphérie interne (4a) du coussinet de palier (4) et la périphérie externe (3b) de l'arbre de rotor (3)est rempli d'huile.
PCT/US2010/034672 2009-05-18 2010-05-13 Palier hydrodynamique WO2010135135A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009021746 2009-05-18
DE102009021746.0 2009-05-18

Publications (2)

Publication Number Publication Date
WO2010135135A2 true WO2010135135A2 (fr) 2010-11-25
WO2010135135A3 WO2010135135A3 (fr) 2011-03-31

Family

ID=43126705

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2010/034672 WO2010135135A2 (fr) 2009-05-18 2010-05-13 Palier hydrodynamique

Country Status (1)

Country Link
WO (1) WO2010135135A2 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104405771A (zh) * 2014-11-29 2015-03-11 哈尔滨广瀚燃气轮机有限公司 新型分段轴瓦反轴承
WO2016028501A1 (fr) * 2014-08-19 2016-02-25 Borgwarner Inc. Turbocompresseur à gaz d'échappement
WO2019126615A1 (fr) * 2017-12-22 2019-06-27 Borgwarner Inc. Turbocompresseur pour moteur à combustion interne à palier hydrodynamique flottant
CN111971462A (zh) * 2018-02-20 2020-11-20 三菱重工发动机和增压器株式会社 增压器
US11959388B2 (en) 2018-10-18 2024-04-16 Turbo Systems Switzerland Ltd Turbocharger having improved shaft seal

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07145812A (ja) * 1993-11-24 1995-06-06 Ricoh Co Ltd 動圧気体軸受およびその動圧気体軸受の製造方法
JPH1030419A (ja) * 1996-07-17 1998-02-03 Nippon Soken Inc 内燃機関の軸受装置
US6024493A (en) * 1997-05-08 2000-02-15 Westwind Air Bearing Ltd Air bearing
JP2003035310A (ja) * 2001-07-24 2003-02-07 Hitachi Powdered Metals Co Ltd 動圧滑り軸受構造

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07145812A (ja) * 1993-11-24 1995-06-06 Ricoh Co Ltd 動圧気体軸受およびその動圧気体軸受の製造方法
JPH1030419A (ja) * 1996-07-17 1998-02-03 Nippon Soken Inc 内燃機関の軸受装置
US6024493A (en) * 1997-05-08 2000-02-15 Westwind Air Bearing Ltd Air bearing
JP2003035310A (ja) * 2001-07-24 2003-02-07 Hitachi Powdered Metals Co Ltd 動圧滑り軸受構造

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016028501A1 (fr) * 2014-08-19 2016-02-25 Borgwarner Inc. Turbocompresseur à gaz d'échappement
CN104405771A (zh) * 2014-11-29 2015-03-11 哈尔滨广瀚燃气轮机有限公司 新型分段轴瓦反轴承
WO2019126615A1 (fr) * 2017-12-22 2019-06-27 Borgwarner Inc. Turbocompresseur pour moteur à combustion interne à palier hydrodynamique flottant
US11319835B2 (en) 2017-12-22 2022-05-03 Borgwarner Inc. Turbocharger for an internal combustion engine with a hydrodynamic floating bearing
CN111971462A (zh) * 2018-02-20 2020-11-20 三菱重工发动机和增压器株式会社 增压器
US20210115811A1 (en) * 2018-02-20 2021-04-22 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Forced induction device
CN111971462B (zh) * 2018-02-20 2023-01-10 三菱重工发动机和增压器株式会社 增压器
US11603772B2 (en) * 2018-02-20 2023-03-14 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Forced induction device
US11959388B2 (en) 2018-10-18 2024-04-16 Turbo Systems Switzerland Ltd Turbocharger having improved shaft seal

Also Published As

Publication number Publication date
WO2010135135A3 (fr) 2011-03-31

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