WO2013064638A1 - Palier axial hydrodynamique - Google Patents

Palier axial hydrodynamique Download PDF

Info

Publication number
WO2013064638A1
WO2013064638A1 PCT/EP2012/071729 EP2012071729W WO2013064638A1 WO 2013064638 A1 WO2013064638 A1 WO 2013064638A1 EP 2012071729 W EP2012071729 W EP 2012071729W WO 2013064638 A1 WO2013064638 A1 WO 2013064638A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
comb
axial stop
shaft
gap
Prior art date
Application number
PCT/EP2012/071729
Other languages
German (de)
English (en)
Inventor
Peter Neuenschwander
Bruno Ammann
Marco Di Pietro
Markus Städeli
Original Assignee
Abb Turbo Systems Ag
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 Abb Turbo Systems Ag filed Critical Abb Turbo Systems Ag
Priority to EP12790812.7A priority Critical patent/EP2773877A1/fr
Priority to SG11201401938WA priority patent/SG11201401938WA/en
Priority to CN201280054248.5A priority patent/CN103906936A/zh
Priority to KR1020147014511A priority patent/KR20140083051A/ko
Priority to CA2852164A priority patent/CA2852164A1/fr
Priority to JP2014540406A priority patent/JP2014533342A/ja
Priority to BR112014010582A priority patent/BR112014010582A2/pt
Publication of WO2013064638A1 publication Critical patent/WO2013064638A1/fr
Priority to US14/268,466 priority patent/US20140241887A1/en
Priority to HK14112459.3A priority patent/HK1199084A1/xx

Links

Classifications

    • 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
    • F01D25/168—Sliding contact bearing for axial load mainly
    • 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
    • F01D25/18—Lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • 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
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
    • 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
    • F16C33/1075—Wedges, e.g. ramps or lobes, for generating pressure
    • 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 the field of hydrodynamic axial bearing of rotating shafts, as used for example in turbomachines, in particular in exhaust gas turbochargers.
  • thrust bearings are used.
  • turbomachines such as exhaust gas turbochargers
  • hydrodynamic thrust bearings are used to accommodate flow-induced high axial forces and to guide the shaft in the axial direction.
  • floating in floating oil disks so-called floating disks can be used in hydrodynamic thrust bearings between a rotatable shaft shaft bearing cam and a non-rotating axial stop on the bearing housing.
  • the lubrication gaps between the rotating bearing comb and the floating disk and between the floating disk and the stationary axial stop on the bearing housing are advantageously each bounded by a profiled annular surface and a profiled annular surface opposite, flat sliding surface.
  • the profiled annular surface serves to optimize the decisive for the load capacity of the thrust bearing pressure build-up in the lubrication gap.
  • the lubricating oil is guided as possible over the entire radial height of the lubricating oil grooves in the wedge surface.
  • the pressure build-up required for the bearing capacity of the axial bearing takes place essentially in the region of the wedge surfaces.
  • Adjacent latching surfaces are formed, which comprise a flat surface and which makes up the bearing surface of the profiled annular surface
  • thrust bearings can be found inter alia in GB1095999, EP0840027, EP1 199486, EP1644647 and EP2042753.
  • the radial guidance of the floating disk takes place either on the rotating body, i. on the shaft or on the bearing comb by means of a radial bearing integrated in the floating disk, as disclosed, for example, in EP0840027, or on a stationary bearing collar concentrically surrounding the rotating body, as disclosed, for example, in EP 1 199 486.
  • the lubrication of such a hydrodynamic thrust bearing is usually carried out by means of lubricating oil from its own lubricating oil system or exhaust gas turbochargers via the lubricating oil system of an internal combustion engine connected to the exhaust gas turbocharger.
  • All wings conventional thrust bearings are in the cold state, at rest, perpendicular to the axis of rotation of the rotor or at least parallel to each other.
  • the wings may deform due to temperature gradients, centrifugal, thrust and other forces.
  • Such deformation of the bearing surfaces may affect the bearing capacity of the bearing.
  • Particularly large effects can have temperature gradients above the crest of the comb bearing.
  • the radially outwardly projecting comb deforms umbrella-shaped due to the temperature difference between the wing and the back. This deformation can cause the comb bearing to rub against the floating disk, especially at low oil supply pressure.
  • the deformation due to the temperature gradient is particularly critical with a conventional comb bearing construction because it causes an outwardly widening lubrication gap.
  • this constellation reduces the carrying capacity for geometric reasons and on the other hand reduces the centrifugal pressure build-up in the radial direction, since the outflow resistance for the lubricating oil is reduced radially outwards.
  • Object of the present invention is therefore to improve the carrying capacity of a hydrodynamic thrust bearing for supporting a rotatably mounted in a bearing housing shaft. If the gap formed between the bearing surfaces of the axial bearing is formed narrowing in the radial direction to the outside by the wings are arranged obliquely relative to each other at least in the radially outer region, resulting in a reduction of the relative inclination of the wings in operation due to the above-mentioned deformation of the rotating support surface , The constriction in the radially outer region is reduced, so that the wings rest more evenly on each other during operation.
  • the bearing comb is manufactured with a conical bearing surface which is thus inclined towards the opposite bearing surface, the temperature deformation in the comb bearing can be compensated.
  • the temperature deformation in the comb bearing can be compensated.
  • the lubrication gap becomes smaller under certain operating conditions in the radial direction. This situation is more favorable than today's with extended lubrication gap, since the load capacity is reduced less and the centrifugal pressure build-up in the radial direction is favored.
  • the compensation for wing deformations by temperature gradients, centrifugal, thrust and other forces can also be done on the floating disk, or in a floating disc thrust bearing on the axial stop of the bearing housing. Any temperature-induced deformations in the areas of the axial stop on the bearing housing can be carried out in a similar manner as on the comb bearing.
  • the comb bearing deformation can also be compensated by a conical design of the axial stop on the bearing housing. Due to compensation of the deformation, the axial bearing against rubbing the floating disk or the bearing comb, or - at a Floating washer thrust bearing - the thrust bearing, more robust on the adjacent bearing parts.
  • the turbocharger will be more reliable and wear-related costs can be reduced.
  • Fig. 1 in the right part of a guided along the axis of rotation section through a trained according to the prior art embodiment of a thrust bearing with a rotating bearing comb, a fixed axial stop and a floating disk, and in the left part of a front view in the axial direction of the corresponding floating disk with a profiled annular surface,
  • FIG. 3 is a schematically illustrated Axialgleitlager according to a first embodiment according to the invention, with a conically shaped bearing comb, and a resulting, radially outwardly tapered lubrication gap,
  • FIG. 5 shows a schematically illustrated axial plain bearing according to a third embodiment according to the invention, with a conically shaped axial bearing and a conically shaped bearing comb, and two resulting, radially outwardly tapered lubricating gaps
  • 6 a schematically illustrated axial plain bearing according to a fourth embodiment according to the invention with a conically shaped axial bearing and a bearing comb side conically shaped floating disk, and two resulting, radially outwardly tapered lubricating gaps
  • FIG. 7 shows a schematically illustrated axial plain bearing according to a fifth embodiment according to the invention with a conically shaped floating disk on both sides, and two resulting, radially outwardly tapered lubricating gaps
  • FIG. 8 a schematically illustrated axial plain bearing according to a sixth embodiment according to the invention with a conically shaped
  • one 9 shows a schematically illustrated axial plain bearing according to a seventh embodiment according to the invention, without floating disk, with a conically shaped bearing comb, and a resulting,, itself radially outwardly tapered lubrication gap
  • FIG. 10 shows a schematically illustrated axial plain bearing according to an eighth embodiment according to the invention, again without a floating disk, with a conically shaped axial stop, and a resulting, radially outwardly tapered lubricating gap.
  • Fig. 1 shows an example of a hydrodynamic thrust bearing according to the prior art, wherein in the right part of the figure in an axially guided along the rotation shaft section, the three essential components of the thrust bearing are made visible.
  • the bearing comb 10 is mounted on the rotating shaft 40 - or optionally materially connected to the shaft or made with the shaft of one piece - and rotates with the shaft with.
  • a floating disk 30 is arranged.
  • a lubricating gap is formed, in which there is a thin lubricating oil layer between the wings.
  • the support surface 22 on the axial stop and the support surface 1 1 on the bearing comb each have a circumferentially planarized sliding surface, while the two wings of the floating disk are part of a profiled annular surface.
  • This basic structure of the two lubrication gaps is also adopted in all embodiments of the inventive hydrodynamic axial plain bearings with floating disk described below.
  • the sliding surfaces and the profiled annular surfaces can be arranged at one or both of the lubrication gaps on the other side of the lubricating gap, so that for example the floating disk on both sides each have a flat sliding surface while the profiled annular surface on the support surface of Lagerkamms and the axial stop of the bearing housing are mounted.
  • the profiled annular surface would be arranged according to the rotating bearing comb and the flat sliding surface on the axial stop of the bearing housing or possibly vice versa, ie the flat sliding surface on the rotating bearing comb and the profiled annular surface on the axial stop of the bearing housing.
  • the structure of the profiled annular surface can be seen from the left part of Figure 1, in which the floating disk is rotated by 90 °, so that in a plan view of the one of the end faces of the floating disk can be seen.
  • the profiled annular surface serves to optimize the decisive for the load capacity of the thrust bearing pressure build-up in the lubrication gap between the wings.
  • the profiling of the annular surface comprises a plurality of segments, each with a leading radially outward Schmierölnut 33 for distributing the in the radially inner region of the profiled annular surface supplied lubricating oil.
  • the lubricating oil grooves 33 adjacent the lubrication gap are formed in the circumferential direction narrowing wedge surfaces 34 through which the lubricating oil introduced into the lubricating oil grooves 33 exits according to the thick arrows.
  • the lubricating oil is guided as possible over the entire radial height of the lubricating oil grooves 33 in the wedge surface 34.
  • the necessary pressure for the load capacity of the thrust bearing is essentially in Area of wedge surfaces.
  • adjacent locking surfaces 35 are formed, which comprise a flat surface having the smallest distance to the mating contour, as the sliding surface described above.
  • the axial extent (thickness) of the lubrication gap can thus be described as a distance between the latching surfaces 35 and the opposite sliding surface.
  • the lubricating oil groove and the wedge surface can be closed radially outwards with a web narrowing the lubricating gap. The web typically comes to lie down to the height of the locking surface, so that locking surface and web lie in one plane.
  • the formation of the lubricating oil groove and the wedge surface is neglected. Accordingly, the terms of the profiled annular surface and the sliding surface are no longer used below.
  • the lubricating gaps, as described above are advantageously limited in each case by a profiled annular surface and a planar sliding surface.
  • that area of the profiled annular surface is meant, which is generally referred to as a latching surface.
  • the locking surfaces are typically located in the direction of flow of the lubricating oil, following the wedge surfaces.
  • the support surfaces of the axial bearings in the cold state ie at a standstill of the rotor, perpendicular to the axis of rotation of the rotor or at least parallel to each other.
  • the bearing surface in the bearing comb can deform due to temperature gradients, centrifugal, thrust and other forces.
  • the relative to the shaft radially projecting comb deforms umbrella-shaped due to the temperature difference between the relevant for the thrust bearing wing and the rear facing away from this. This deformation, indicated by dashed lines in FIG.
  • FIG. 3 shows a schematically illustrated hydrodynamic axial plain bearing according to a first embodiment according to the invention.
  • the effective support surface 31 on the bearing comb facing side of the floating disk 30 strictly radial, that is aligned perpendicular to the axis of rotation of the shaft 40.
  • the wing 1 1 of the bearing comb is inclined towards the floating disk 30, so that in the radially outer region of the lubricating gap 52 results in a narrowing in the axial direction.
  • the inclination of the support surface 1 1 of the bearing comb can be realized in this embodiment, as well as in the other embodiments described below by a uniform, straight slope or by a curved slope.
  • the deformations of the rotating components and the narrowing of the lubricating gaps are greatly exaggerated.
  • the angle of inclination provided according to the invention over the entire radius of the inclined component is in the range of a few hundredths of a degree, resulting in a narrowing of the lubricating gap at the radially outer edge of a few hundredths of a millimeter, for example for a disk having a diameter of 200 millimeters.
  • the invention extends in the cold state to the floating disk inclined support surface 1 1 of the bearing comb such that decreases in nominal operation, the angle of narrowing of the lubricating gap 52 ' and the two wings 31 and 1 1 ' of the bearing parallel to each other or, while maintaining a opposite the cold state less pronounced lubrication gap narrowing, at least almost parallel to each other. That in the cold state, ie at a standstill and even at low speeds, the inventive design of the Axialgleitlagers leads to a narrowing of the lubricating gap in the radially outer region, no problem, since the pent-up lubricating oil provides additional pressure build-up.
  • 4 shows a schematically illustrated hydrodynamic axial plain bearing according to a second embodiment according to the invention.
  • the support surface 1 1 of the bearing comb is strictly radial, that is perpendicular to the axis of rotation of the shaft 40th aligned.
  • the support surface 31 is formed on the side facing the bearing comb side of the floating disk 30 in this embodiment inclined to the bearing block 10, so that in turn results in the radially outer region of the lubricating gap 52, the narrowing in the axial direction.
  • the floating disk is thus formed conically on the side facing the bearing comb, while it is aligned on the other, the axial stop on the bearing housing side facing perpendicular to the axis of rotation of the shaft 40.
  • the supporting surface 11 of the bearing comb aligned in the cold state perpendicular to the axis of rotation of the shaft 40 bends so that the narrowing angle of the lubricating gap 52 'is reduced during nominal operation and the two bearing surfaces 31 and 11 ' of the bearing are parallel or nearly parallel to one another run.
  • the lubricating gap 51 between the axial stop 21 and the floating disk 30 is formed with a constriction in the axial direction in the radially outer region.
  • FIG. 5 shows a schematically illustrated hydrodynamic axial plain bearing according to a third embodiment according to the invention.
  • the support surface 31 on the bearing comb facing side of the floating disk 30 strictly radial, that is aligned perpendicular to the axis of rotation of the shaft 40.
  • the wing 1 1 of the bearing comb is inclined towards the floating disk 30, so that in the radially outer region of the lubricating gap 52 results in a narrowing in the axial direction.
  • the second also provided with a constriction in the axial direction in the radially outer region lubrication gap extends between the strictly radially, that is perpendicular to the axis of rotation of the shaft 40, aligned support surface 32 on the axial stop facing side of the floating disk 30 and the floating disk 30 back inclined support surface 22 of the axial stop 21 on the bearing housing.
  • the floating disk is thus provided with two perpendicular to the axis of rotation of the shaft 40 aligned, mutually parallel sides.
  • the invention extends in the cold state to the floating disk inclined support surface 1 1 of the bearing comb such that decreases in nominal operation, the angle of narrowing of the lubricating gap 52 ' and the two wings 31 and 1 1 ' of the bearing parallel to each other or almost parallel to each other.
  • FIG. 6 shows a schematically illustrated hydrodynamic axial plain bearing according to a fourth embodiment according to the invention, which differs from the previous one in that the support surface 11 of the bearing comb is oriented strictly radially, that is perpendicular to the axis of rotation of the shaft 40 and for this the support surface 31 on the the bearing comb facing side of the floating disk 30 is inclined to the bearing comb 10 is formed.
  • the second likewise provided with a constriction in the axial direction in the radially outer region lubrication gap extends again between the strictly radial, that is perpendicular to the axis of rotation of the shaft 40 aligned bearing surface 32 on the axial stop facing side of the floating disk and the floating disk 30 towards inclined Support surface 22 of the axial stop 21 on the bearing housing.
  • the floating disk is thus formed konusformig on the bearing comb side facing, while it is aligned on the other, the axial stop on the bearing housing side facing perpendicular to the axis of rotation of the shaft 40.
  • the supporting surface 1 1 of the bearing comb aligned in the cold state perpendicular to the axis of rotation of the shaft 40 bends so that the narrowing angle of the lubricating gap 52 'is reduced during nominal operation and the two bearing surfaces 31 and 11 ' of the bearing parallel to each other or nearly parallel to each other.
  • FIG. 7 shows a schematically illustrated hydrodynamic axial plain bearing according to a fifth embodiment according to the invention.
  • the support surface 1 1 of the bearing comb is strictly radial, that is aligned perpendicular to the axis of rotation of the shaft 40.
  • the bearing surface 31 on the bearing comb facing side of the floating disk 30, however, is inclined to the bearing block 10, so that in the radially outer region of the lubricating gap 52, a constriction in the axial Direction results.
  • the second also provided with a constriction in the axial direction in the radially outer region lubrication gap extends between the strictly radial, that is perpendicular to the axis of rotation of the shaft 40 aligned bearing surface of the axial stop 21 on the bearing housing and the axial stop inclined towards the support surface 32 on the Axial stop facing side of the floating disk.
  • the floating disk 30 is thus formed on both sides of a cone.
  • the supporting surface 1 1 of the bearing comb aligned in the cold state perpendicular to the axis of rotation of the shaft 40 bends so that the narrowing angle of the lubricating gap 52 'is reduced during nominal operation and the two bearing surfaces 31 and 11 ' of the bearing parallel to each other or nearly parallel to each other.
  • FIG. 8 shows a schematically illustrated hydrodynamic axial plain bearing according to a sixth embodiment according to the invention, which differs from the previous one in that the support surface 31 is aligned strictly radially, that is perpendicular to the axis of rotation of the shaft 40, on the side of the floating disk 30 facing the bearing comb for the support surface 1 1 of the bearing comb, is inclined to the floating disk 30, so that in turn results in the radially outer region of the lubricating gap 52, a constriction in the axial direction.
  • the second, also provided with a constriction in the axial direction in the radially outer region lubrication gap extends in turn between the strictly radial, that is perpendicular to the axis of rotation of the shaft 40 aligned bearing surface 22 of the axial stop 21 on the bearing housing and the axial stop inclined towards the support surface 32 the axial stop facing side of the floating disk.
  • the floating disk is thus formed conically on the side facing the axial stop on the bearing housing side, while it is aligned on the other, the bearing comb side facing perpendicular to the axis of rotation of the shaft 40.
  • the support surface 1 1 of the bearing comb inclined in the cold state towards the floating disk stretches in such a way that, during nominal operation, the angle of the narrowing of the lubricating gap 52 'is reduced and the both wings 31 and 1 1 'of the bearing parallel to each other or almost parallel to each other.
  • the last two figures each show a hydrodynamic thrust bearing without floating disk, in which a support surface 12 on the rotating bearing comb 10 and a support surface 22 on the axial stop 21 of the bearing housing 20 is arranged.
  • the lubricating gap 53 which results therebetween is in turn designed to converge radially outwards, that is to say that the lubricating gap tapers in the radially outer region.
  • the seventh inventive embodiment of a hydrodynamic axial plain bearing shown in FIG. 9 has a support surface 12 of the bearing comb 10, which is inclined towards the axial stop 21 of the bearing housing 20, so that in the radially outer region of the lubrication gap 53 the constriction in the axial direction results.
  • the support surface 22 of the axial stop 21 of the bearing housing 20 is in this embodiment strictly radial, that is aligned perpendicular to the axis of rotation of the shaft 40.
  • the invention extends in the cold state to the support surface of the axial stop 21 inclined support surface 12 of the bearing comb such that decreases in nominal operation, the angle of narrowing of the lubricating gap 53 ' and the two wings 12 ' and 22 of the bearing parallel to each other or almost parallel to each other ,
  • the eighth embodiment according to the invention of a hydrodynamic axial plain bearing shown in FIG. 10 has a bearing surface 12 of the bearing comb 10, which is oriented strictly radially, that is to say perpendicular to the axis of rotation of the shaft 40.
  • the support surface 22 of the axial stop 21 on the bearing housing 20 in this embodiment is inclined towards the bearing comb 10, so that the narrowing in the axial direction results in the radially outer region of the lubrication gap 53.
  • the axial stop is thus formed conically on the bearing comb side facing.
  • each one of the wings is deviating from the plane which is oriented perpendicular to the axis of rotation of the shaft and the other wing as strictly radial, ie along this plane extending, which is aligned perpendicular to the axis of rotation of the shaft described.
  • the narrowing lubricating gaps can also be realized by the respective wings both differ from respective planes, which are aligned perpendicular to the axis of rotation of the shaft, but at an angle to each other.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sliding-Contact Bearings (AREA)
  • Supercharger (AREA)
  • Support Of The Bearing (AREA)

Abstract

La présente invention concerne un palier axial hydrodynamique destiné à porter un arbre (40) monté rotatif dans un carter de palier (20) et comprenant une butée axiale (21) du carter de palier et un collier de palier (10) tournant avec l'arbre. Entre la butée axiale (21) et le collier de palier (10) est formée une fente de lubrification (52) délimitée par une surface annulaire (31) profilée et une surface de glissement (11) et soumise à l'effet d'une huile de lubrification (52). La surface annulaire profilée (31) et la surface de glissement (11) sont conçues de telle sorte que la fente de lubrification (52) rétrécisse radialement vers l'extérieur par rapport à la direction axiale. De ce fait, il est possible de compenser des déformations thermiques se produisant lors du fonctionnement et des déformations dues à la force centrifuge, à la force de poussée et à d'autres forces dans le collier de palier.
PCT/EP2012/071729 2011-11-03 2012-11-02 Palier axial hydrodynamique WO2013064638A1 (fr)

Priority Applications (9)

Application Number Priority Date Filing Date Title
EP12790812.7A EP2773877A1 (fr) 2011-11-03 2012-11-02 Palier axial hydrodynamique
SG11201401938WA SG11201401938WA (en) 2011-11-03 2012-11-02 Hydrodynamic axial bearing
CN201280054248.5A CN103906936A (zh) 2011-11-03 2012-11-02 液体动压轴向轴承
KR1020147014511A KR20140083051A (ko) 2011-11-03 2012-11-02 유체역학적 액시얼 베어링
CA2852164A CA2852164A1 (fr) 2011-11-03 2012-11-02 Palier axial hydrodynamique
JP2014540406A JP2014533342A (ja) 2011-11-03 2012-11-02 流体動圧スラスト軸受
BR112014010582A BR112014010582A2 (pt) 2011-11-03 2012-11-02 mancal axial hidrodinâmico
US14/268,466 US20140241887A1 (en) 2011-11-03 2014-05-02 Hydrodynamic axial bearing
HK14112459.3A HK1199084A1 (en) 2011-11-03 2014-12-11 Hydrodynamic axial bearing

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011085681.1 2011-11-03
DE102011085681A DE102011085681A1 (de) 2011-11-03 2011-11-03 Hydrodynamisches Axiallager

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US14/268,466 Continuation US20140241887A1 (en) 2011-11-03 2014-05-02 Hydrodynamic axial bearing

Publications (1)

Publication Number Publication Date
WO2013064638A1 true WO2013064638A1 (fr) 2013-05-10

Family

ID=47222025

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/071729 WO2013064638A1 (fr) 2011-11-03 2012-11-02 Palier axial hydrodynamique

Country Status (11)

Country Link
US (1) US20140241887A1 (fr)
EP (1) EP2773877A1 (fr)
JP (1) JP2014533342A (fr)
KR (1) KR20140083051A (fr)
CN (1) CN103906936A (fr)
BR (1) BR112014010582A2 (fr)
CA (1) CA2852164A1 (fr)
DE (1) DE102011085681A1 (fr)
HK (1) HK1199084A1 (fr)
SG (1) SG11201401938WA (fr)
WO (1) WO2013064638A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE540190C2 (en) * 2015-04-30 2018-04-24 Scania Cv Ab A sealing arrangement for a hydrodynamic machine
DE102015215306B4 (de) * 2015-08-11 2018-08-02 Siemens Healthcare Gmbh Flüssigmetall-Gleitlager
US10113586B2 (en) * 2015-10-16 2018-10-30 Ford Global Technologies, Llc Hydrodynamic axial plain bearing
JP6521838B2 (ja) * 2015-11-06 2019-05-29 トヨタ自動車株式会社 回転軸の支持構造
GB2547008B (en) * 2016-02-04 2020-07-29 Rolls Royce Plc Balancing of axial thrust forces within a gas turbine engine
DE102017102420A1 (de) * 2017-02-08 2018-08-09 Abb Turbo Systems Ag Gleitlagerung mit hydrodynamischer axialsicherung
WO2019015753A1 (fr) * 2017-07-19 2019-01-24 Konzelmann Gmbh Palier à action hydrodynamique
US10513928B2 (en) * 2017-08-31 2019-12-24 Flowserve Management Company Axial thrust balancing device
WO2020038655A1 (fr) * 2018-08-21 2020-02-27 Zf Friedrichshafen Ag Élément d'appui pour un palier axial hydrodynamique et palier axial hydrodynamique
JP7392620B2 (ja) * 2020-09-30 2023-12-06 株式会社豊田自動織機 遠心圧縮機
WO2024104529A1 (fr) * 2022-11-15 2024-05-23 Ihi Charging Systems International Gmbh Palier axial pour supporter un arbre rotatif et turbocompresseur à gaz d'échappement possédant un palier axial

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1095999A (en) 1964-05-28 1967-12-20 Hawker Siddeley Canada Ltd Improvements in fluid thrust bearing
US4348065A (en) * 1979-07-13 1982-09-07 Hitachi, Ltd. Thrust bearing
EP0840027A2 (fr) 1996-10-11 1998-05-06 Asea Brown Boveri AG Palier axial à glissement.
EP1199486A1 (fr) 2000-10-17 2002-04-24 ABB Turbo Systems AG Palier axial hydrodynamique avec disque flottant
DE29624507U1 (de) * 1996-10-11 2004-11-25 Abb Turbo Systems Ag Axialgleitlager
EP1644647A1 (fr) 2003-07-05 2006-04-12 MAN B & W Diesel AG Palier lisse axial
EP2042753A1 (fr) 2007-09-26 2009-04-01 ABB Turbo Systems AG Palier axial hydrodynamique

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0575519U (ja) * 1992-03-16 1993-10-15 三菱重工業株式会社 回転軸のスラストカラー
JP3338117B2 (ja) * 1993-04-28 2002-10-28 日本電産株式会社 スピンドルモータおよび軸受け用部品の製造方法
JP2003056553A (ja) * 2001-08-10 2003-02-26 Koyo Seiko Co Ltd スラスト動圧軸受
JP2003222123A (ja) * 2002-01-25 2003-08-08 Mitsubishi Heavy Ind Ltd テーパランドスラスト軸受およびそれを備えた回転機械
JP4340855B2 (ja) * 2003-04-22 2009-10-07 株式会社ジェイテクト 動圧発生用溝の製造方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1095999A (en) 1964-05-28 1967-12-20 Hawker Siddeley Canada Ltd Improvements in fluid thrust bearing
US4348065A (en) * 1979-07-13 1982-09-07 Hitachi, Ltd. Thrust bearing
EP0840027A2 (fr) 1996-10-11 1998-05-06 Asea Brown Boveri AG Palier axial à glissement.
DE29624507U1 (de) * 1996-10-11 2004-11-25 Abb Turbo Systems Ag Axialgleitlager
EP1199486A1 (fr) 2000-10-17 2002-04-24 ABB Turbo Systems AG Palier axial hydrodynamique avec disque flottant
EP1644647A1 (fr) 2003-07-05 2006-04-12 MAN B & W Diesel AG Palier lisse axial
EP2042753A1 (fr) 2007-09-26 2009-04-01 ABB Turbo Systems AG Palier axial hydrodynamique

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP2773877A1

Also Published As

Publication number Publication date
KR20140083051A (ko) 2014-07-03
JP2014533342A (ja) 2014-12-11
US20140241887A1 (en) 2014-08-28
CA2852164A1 (fr) 2013-05-10
BR112014010582A2 (pt) 2017-05-02
SG11201401938WA (en) 2014-10-30
EP2773877A1 (fr) 2014-09-10
DE102011085681A1 (de) 2013-05-08
HK1199084A1 (en) 2015-06-19
CN103906936A (zh) 2014-07-02

Similar Documents

Publication Publication Date Title
EP2773877A1 (fr) Palier axial hydrodynamique
EP2193279B1 (fr) Palier axial hydrodynamique
EP1644647B1 (fr) Palier lisse axial
EP0840027B1 (fr) Palier axial à glissement.
EP3032037B1 (fr) Stator et turbomachine
EP2715162B2 (fr) Couronne d'orientation
DE102007027427A1 (de) Schaufeldeckband mit Überstand
EP3488125B1 (fr) Palier de roue satellite d'un engrenage planétaire
DE112013001368T5 (de) Turbolader mit Axiallager zur Bereitstellung von kombinierten Zapfen- und Axiallager-Funktionen
EP3186524B1 (fr) Palier axial et support
EP2716874B1 (fr) Stator, procédé de montage et turbomachine
DE102009007696A1 (de) Lageranordnung
EP2535606B1 (fr) Agencement de palier axial
EP3580465B1 (fr) Palier lisse à fixation axiale hydrodynamique
DE102006053726B4 (de) Axialgleitlager
EP3613952B1 (fr) Dispositif d'aube directrice variable, aube directrice, porte-joint et turbomachine
EP3183430B1 (fr) Aube mobile de turbine
WO2018006999A1 (fr) Dispositif palier pour un turbocompresseur à gaz d'échappement et turbocompresseur à gaz d'échappement
EP2982834B1 (fr) Palier a roulement, en particulier palier a aiguilles, destine a l'agencement sur un pivot d'une aube variable de turbomachine
DE102017221903A1 (de) Wälzlager, insbesondere Wälzlager mit großem Durchmesser
EP3246521B1 (fr) Rampe pour plaque de recouvrement d'aube directrice et embase d'aube mobile
WO2021110191A1 (fr) Support d'étanchéité conçu pour une turbomachine comportant des ouvertures de type fentes dans le corps d'étanchéité
WO2021115510A1 (fr) Rotor pour une turbomachine et turbomachine
WO2024104528A1 (fr) Palier axial pour supporter un arbre rotatif et turbocompresseur à gaz d'échappement ayant un palier axial
DE102022116105A1 (de) Dichtung für einen Radialspalt

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12790812

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2012790812

Country of ref document: EP

ENP Entry into the national phase

Ref document number: 2852164

Country of ref document: CA

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2014540406

Country of ref document: JP

Kind code of ref document: A

ENP Entry into the national phase

Ref document number: 20147014511

Country of ref document: KR

Kind code of ref document: A

REG Reference to national code

Ref country code: BR

Ref legal event code: B01A

Ref document number: 112014010582

Country of ref document: BR

ENP Entry into the national phase

Ref document number: 112014010582

Country of ref document: BR

Kind code of ref document: A2

Effective date: 20140430