US20140241887A1 - Hydrodynamic axial bearing - Google Patents

Hydrodynamic axial bearing Download PDF

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Publication number
US20140241887A1
US20140241887A1 US14/268,466 US201414268466A US2014241887A1 US 20140241887 A1 US20140241887 A1 US 20140241887A1 US 201414268466 A US201414268466 A US 201414268466A US 2014241887 A1 US2014241887 A1 US 2014241887A1
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United States
Prior art keywords
bearing
face
comb
axial
planar sliding
Prior art date
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Abandoned
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US14/268,466
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English (en)
Inventor
Peter Neuenschwander
Bruno Ammann
Marco Di Pietro
Markus Städeli
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Accelleron Industries AG
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ABB Turbo Systems AG
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Filing date
Publication date
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Assigned to ABB TURBO SYSTEMS AG reassignment ABB TURBO SYSTEMS AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMMANN, BRUNO, DI PIETRO, MARCO, NEUENSCHWANDER, PETER, STAEDELI, MARKUS
Publication of US20140241887A1 publication Critical patent/US20140241887A1/en
Abandoned legal-status Critical Current

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    • 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 disclosure relates to the field of hydrodynamic axial mounting of rotating shafts, as are used, for example, in turbomachines, for example in exhaust gas turbochargers.
  • load-bearing axial bearings can be used.
  • hydrodynamic axial bearings can be used to absorb axial forces, which can be high as a result of the flow, and to guide the shaft in an axial direction.
  • disks which float freely in the lubricating oil known as floating disks, can be used in hydrodynamic axial bearings between a bearing comb which rotates at the shaft rotational speed and a non-rotating axial stop on the bearing housing.
  • the lubricating gaps between a rotating bearing comb and the floating disk and between the floating disk and the stationary axial stop on the bearing housing can be delimited in each case by a profiled circular ring face and a plane sliding face which lies opposite the profiled circular ring face.
  • the profiled circular ring face can serve to optimize the pressure build-up in the lubricating gap.
  • the pressure build-up can be decisive for the load-bearing force of the axial bearing.
  • Wedge faces which constrict the lubricating gap in the circumferential direction and via which the lubricating oil introduced into the lubricating oil grooves exits, are formed adjacently with respect to the lubricating oil grooves.
  • the lubricating oil is guided into the wedge face as far as possible over the entire radial height of the lubricating oil grooves.
  • the pressure build-up which is desirable for the load-bearing capability of the axial bearing, takes place substantially in the region of the wedge faces.
  • Rest faces which include a planar face and are provided by the load-bearing face of the profiled circular ring face, are formed adjacently with respect to the wedge faces in the circumferential direction.
  • axial bearings of this type are found, inter alia, in GB 1095999, EP0840027, EP1199486, EP1644647 and EP2042753.
  • the radial guidance of the floating disk takes place either on the rotating body, for example on the shaft or on the bearing comb, by way of a radial bearing which is integrated into the floating disk, as is disclosed, for example, in EP0840027, or else on a stationary bearing collar which surrounds the rotating body concentrically, as is disclosed, for example, in EP1199486.
  • the lubrication of a hydrodynamic axial bearing of this type can take place lubricating oil from a dedicated lubricating oil system or, in the case of exhaust gas turbochargers, via the lubricating oil system of an internal combustion engine which is connected to the exhaust gas turbocharger.
  • all the load-bearing faces of known axial mountings can lie perpendicularly with respect to the rotational axis of the rotor or else at least parallel to one another.
  • the load-bearing faces can be deformed on account of temperature gradients, centrifugal, shearing and other forces. A deformation of this type of the bearing load-bearing faces can impair the load-bearing force of the mounting. Temperature gradients over the comb of the comb bearing can have particularly great effects.
  • the comb which protrudes radially with respect to the shaft can be deformed in an umbrella-shaped manner on account of the temperature difference between the load-bearing face and the rear side.
  • This deformation can lead to rubbing of the comb bearing on the floating disk, particularly in the case of a low oil supply pressure.
  • the deformation on account of the temperature gradient can be critical in a known comb bearing construction, because the deformation can cause a lubricating gap which widens to the outside. This can reduce the load-bearing capability for geometric reasons and can reduce the centrifugal force-induced pressure build-up in the radial direction, because the outflow resistance for the lubricating oil radially to the outside is reduced.
  • a hydrodynamic axial bearing for mounting a shaft mounted rotatably in a bearing housing, the hydrodynamic axial bearing comprising: an axial stop; a bearing comb for rotation with a shaft when installed; and at least one lubricating gap formed between the axial stop and the bearing comb for receiving lubricating oil, and delimited by a profiled circular ring face and a planar sliding face which lies opposite the circular ring face, the profiled circular ring face being configured so as to rotate around or with the shaft, the profile of the circular ring face having a plurality of segments, each segment including one radially running lubricating oil groove, a wedge face connected to the lubricating oil groove in a circumferential direction, and a rest face which adjoins the wedge face in the circumferential direction, wherein, for the at least one lubricating gap, the rest face and the planar sliding face are configured such that the lubricating gap, delimited by the rest face and the planar sliding face, is constricted radially to the outside with regard
  • a turbomachine comprising: a shaft mounted rotatably in a bearing housing; and a hydrodynamic axial bearing for mounting the shaft in the bearing housing, the hydrodynamic axial bearing including: an axial stop; a bearing comb for rotating with the shaft; and at least one lubricating gap formed between the axial stop and the bearing comb for being loaded with lubricating oil and delimited by a profiled circular ring face and a planar sliding face which lies opposite the circular ring face, the profiled circular ring face being configured so as to rotate around or with the shaft, the profile of the circular ring face having a plurality of segments, each segment including one radially running lubricating oil groove, a wedge face connected to the lubricating oil groove in a circumferential direction, and a rest face which adjoins the wedge face in the circumferential direction, wherein, for the at least one lubricating gap, the rest face and the planar sliding face are configured such that the lubricating gap, delimited by the rest face and the planar
  • An exhaust gas turbocharger comprising: a shaft mounted rotatably in a bearing housing; and a hydrodynamic axial bearing for mounting the shaft in the bearing housing the hydrodynamic axial bearing including: an axial stop; a bearing comb for rotating with the shaft; and at least one lubricating gap formed between the axial stop and the bearing comb for being loaded with lubricating oil and delimited by a profiled circular ring face and a planar sliding face which lies opposite the circular ring face, the profiled circular ring face being configured so as to rotate around or with the shaft, the profile of the circular ring face having a plurality of segments, each segment including one radially running lubricating oil groove, a wedge face connected to the lubricating oil groove in a circumferential direction, and a rest face which adjoins the wedge face in the circumferential direction, wherein, for the at least one lubricating gap, the rest face and the planar sliding face are configured such that the lubricating gap, delimited by the rest face and the plan
  • FIG. 1 shows, in the right-hand part, a section which is guided along the rotational axis of a known axial sliding bearing with a rotating bearing comb, a stationary axial stop and a floating disk, and shows, in the left-hand part, a frontal view in the axial direction of the corresponding floating disk with a profiled circular ring face;
  • FIG. 2 shows a diagrammatically illustrated axial sliding bearing according to FIG. 1 , the bearing comb being shown in each case in the cold state in this figure and in all following figures, and additionally the deformation of the bearing comb in the operating state on account of the heating and the rapid rotation and the resulting lubricating gap being indicated by way of dashed lines;
  • FIG. 3 shows a diagrammatically illustrated axial sliding bearing according to a first exemplary embodiment according to the disclosure, with a conically shaped bearing comb and a lubricating gap which results therefrom and tapers radially toward the outside;
  • FIG. 4 shows a diagrammatically illustrated axial sliding bearing according to a second exemplary embodiment according to the disclosure with a floating disk which is shaped conically on the bearing comb side and a lubricating gap which results therefrom and tapers radially toward the outside;
  • FIG. 5 shows a diagrammatically illustrated axial sliding bearing according to a third exemplary embodiment according to the disclosure, with a conically shaped axial bearing and conically shaped bearing comb, and two lubricating gaps which result therefrom and taper radially toward the outside;
  • FIG. 6 shows a diagrammatically illustrated axial sliding bearing according to a fourth exemplary embodiment according to the disclosure with a conically shaped axial bearing and a floating disk which is shaped conically on the bearing comb side, and two lubricating gaps which result therefrom and taper radially toward the outside;
  • FIG. 7 shows a diagrammatically illustrated axial sliding bearing according to a fifth exemplary embodiment according to the disclosure with a floating disk which is shaped conically on both sides, and two lubricating gaps which result therefrom and taper radially toward the outside;
  • FIG. 8 shows a diagrammatically illustrated axial sliding bearing according to a sixth exemplary embodiment according to the disclosure with a conically shaped bearing comb and a floating disk which is shaped conically on the axial bearing side, and two lubricating gaps which result therefrom and taper radially toward the outside;
  • FIG. 9 shows a diagrammatically illustrated axial sliding bearing according to a seventh exemplary embodiment according to the disclosure, without a floating disk, with a conically shaped bearing comb, and a lubricating gap which results therefrom and tapers radially toward the outside;
  • FIG. 10 shows a diagrammatically illustrated axial sliding bearing according to an eighth exemplary embodiment according to the disclosure, without a floating disk, with a conically shaped axial stop, and a lubricating gap which results therefrom and tapers radially toward the outside.
  • Exemplary embodiments of the disclosure can improve the load-bearing capability of a hydrodynamic axial bearing for mounting a shaft which is mounted rotatably in a bearing housing.
  • the gap which is formed between the load-bearing faces of the axial bearing, is configured so as to be constricted to the outside in the radial direction, by the load-bearing faces being arranged obliquely relative to one another at least in the radially outer region, a reduction in the relative oblique position of the load-bearing faces results during operation on account of the abovementioned deformation of the rotating load-bearing face.
  • the constriction in the radially outer region is reduced, with the result that the load-bearing faces can rest more uniformly on one another during operation.
  • the bearing comb is manufactured with a conical load-bearing face, that is to say a load-bearing face which is inclined toward the load-bearing face which lies opposite it, the temperature deformation in the comb bearing can be compensated for. During the compensation, the deformations on account of centrifugal, shearing and further forces likewise have to be taken into consideration.
  • the lubricating gap becomes smaller in the radial direction under certain operating conditions. This situation is more favorable than the current one with a widened lubricating gap, because the load-bearing capability is reduced to a lesser extent and the centrifugal force-induced pressure build-up in the radial direction is aided.
  • the compensation on account of load-bearing face deformations as a result of temperature gradients, centrifugal, shearing and further forces can also take place at the floating disk, or at the axial stop of the bearing housing in the case of an axial bearing without floating disk. Any temperature-induced deformations which occur in the region of the axial stop on the bearing housing can be carried out in a similar way as on the comb bearing.
  • the comb bearing deformation can also be compensated for by way of a conical configuration of the axial stop on the bearing housing.
  • the axial mounting can become more robust at the adjacent bearing parts with respect to rubbing of the floating disk or the bearing comb, or, in the case of an axial bearing without floating disk, of the axial bearing.
  • the turbocharger can become more operationally reliable and wear-induced costs can be reduced.
  • FIG. 1 shows by way of example a known hydrodynamic axial bearing, the three components of the axial bearing being made visible in the right-hand part of the figure in a section which is guided axially along the rotational shaft.
  • the bearing comb 10 is placed on the rotating shaft 40 , or is optionally connected in a material-to-material manner to the shaft, or is produced with the shaft from one piece, and rotates with the shaft.
  • a floating disk 30 is arranged axially between an axial stop 21 on the bearing housing 20 and the bearing comb. In each case one lubricating gap is formed firstly between the axial stop and the floating disk and secondly between the floating disk and the bearing comb, in which lubricating gap a thin lubricating oil layer is situated between the load-bearing faces.
  • the load-bearing face 22 on the axial stop and the load-bearing face 11 on the bearing comb in each case have a sliding face which is of planar configuration in the circumferential direction, whereas the two load-bearing faces of the floating disk are part of a profiled circular ring face.
  • This basic construction of the two lubricating gaps is also adopted in all the exemplary embodiments described in the disclosure of the hydrodynamic axial sliding bearings according to the exemplary embodiment of the disclosure with a floating disk.
  • the sliding faces and the profiled circular ring faces in the case of one or both of the lubricating gaps can also be arranged on the respectively other side of the lubricating gap, with the result that, for example, the floating disk has in each case one planar sliding face on both sides whereas the profiled circular ring face is attached on the load-bearing face of the bearing comb and the axial stop of the bearing housing.
  • the profiled circular ring face would correspondingly be arranged on the rotating bearing comb and the planar sliding face would be arranged on the axial stop of the bearing housing or at any rate vice versa, that is to say the planar sliding face on the rotating bearing comb and the profiled circular ring face on the axial stop of the bearing housing.
  • the profiled circular ring face can optimize the pressure build-up in the lubricating gap between the load-bearing faces, which pressure build-up can be decisive for the load-bearing force of the axial bearing.
  • the profiling of the circular ring face includes a plurality of segments with, in each case, one lubricating oil groove 33 which is led radially to the outside in order to distribute the lubricating oil which is supplied in the radially inner region of the profiled circular ring face.
  • wedge faces 34 which constrict the lubricating gap in the circumferential direction are formed adjacently with respect to the lubricating oil grooves 33 , via which wedge faces 34 the lubricating oil which is introduced into the lubricating oil grooves 33 exits in accordance with the thick arrows.
  • the lubricating oil is guided into the wedge face 34 as far as possible over the entire radial height of the lubricating oil grooves 33 .
  • the pressure build-up which is desirable for the load-bearing capability of the axial bearing, takes place substantially in the region of the wedge faces.
  • Rest faces 35 are formed adjacently with respect to the wedge faces 34 in the circumferential direction, which rest faces 35 include a planar face which is at the smallest spacing from the corresponding contact, as the above-described sliding face.
  • the axial extent (thickness) of the lubricating gap can therefore be described as the spacing between the rest faces 35 and the sliding face which lies opposite.
  • the lubricating oil groove and wedge face can be closed radially to the outside by way of a web which constricts the lubricating gap.
  • the web can come to lie as far as the height of the rest face, with the result that the rest face and web lie in one plane.
  • the configuration of the lubricating oil groove and the wedge face is disregarded for the exemplary embodiments which are described in the disclosure. Accordingly, the expressions of the profiled circular ring face and the sliding face are no longer used in the disclosure. For the practical implementation, however, reference is made to the fact that the lubricating gaps, as described above, are advantageously delimited in each case by a profiled circular ring face and a planar sliding face.
  • the expression used in the following text of the active load-bearing face means that region of the profiled circular ring face which can be called a rest face. The rest faces can be situated so as to adjoin the wedge faces as viewed in the flow direction of the lubricating oil.
  • the load-bearing faces of the axial mountings are configured perpendicularly with respect to the rotational axis of the rotor or else at least parallel to one another.
  • the load-bearing face in the bearing comb can be deformed on account of temperature gradients, centrifugal, shearing and further forces.
  • the comb which protrudes radially with respect to the shaft can be deformed in an umbrella-shaped manner on account of the temperature difference between the load-bearing face, which is relevant for the axial bearing, and the rear side which faces away from the load-bearing face.
  • This deformation (indicated in FIG. 2 by way of dashed lines) can lead to rubbing of the comb bearing on the floating disk in the radially inner region, because the load-bearing force of the lubricating gap diminishes on account of the radially outwardly diverging load-bearing faces 31 and 11 ′ of the axial bearing and the associated unimpeded escape of the lubricating oil, for example in the case of a low oil supply pressure, at which sufficient lubricating oil cannot be replenished.
  • FIG. 3 shows a diagrammatically illustrated hydrodynamic axial sliding bearing according to a first exemplary embodiment according to the disclosure.
  • the active load-bearing face 31 on that side of the floating disk 30 which faces the bearing comb is oriented strictly radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 .
  • the load-bearing face 11 of the bearing comb is shaped so as to be inclined toward the floating disk 30 , which results in a constriction in the axial direction in the radially outer region of the lubricating gap 52 .
  • the inclination of the load-bearing face 11 of the bearing comb can be realized by way of a uniform, straight inclination or by way of a curved inclination.
  • the deformations of the rotating components and the constrictions of the lubricating gaps are illustrated in a greatly exaggerated manner.
  • the inclination angles which are provided according to the disclosure move over the entire radius of the inclined component in the range of a few hundredths of a degree, which results in a constriction of the lubricating gap at the radially outer edge of a few hundredths of a millimeter in the case of a disk with a diameter of 200 mm.
  • a deformation of the bearing comb can result on account of the above-described heating of the bearing comb and as a result of the action of the stated forces.
  • the load-bearing face 11 which is inclined towards the floating disk in the cold state, of the bearing comb stretches in such a way that the angle of the constriction of the lubricating gap 52 ′ is reduced during nominal operation and the two load-bearing faces 31 and 11 ′ of the bearing run parallel to one another or, while maintaining a lubricating gap constriction which is less pronounced than in the cold state, run at least virtually parallel to one another.
  • the configuration according to the exemplary embodiment of the disclosure of the axial sliding bearing leads to a constriction of the lubricating gap in the radial outer region. This is not a problem, because the accumulated lubricating oil ensures an additional pressure build-up.
  • FIG. 4 shows a diagrammatically illustrated hydrodynamic axial sliding bearing according to a second exemplary embodiment according to the disclosure.
  • the load-bearing face 11 of the bearing comb is oriented strictly radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 .
  • the load-bearing face 31 on that side of the floating disk 30 which faces the bearing comb is configured so as to be inclined toward the bearing comb 10 in this exemplary embodiment, which results in the constriction in the axial direction in the radially outer region of the lubricating gap 52 .
  • the floating disk is therefore of conical configuration on the side which faces the bearing comb, whereas it is oriented perpendicularly with respect to the rotational axis of the shaft 40 on the other side which faces the axial stop on the bearing housing.
  • the lubricating gap 51 between the axial stop 21 and the floating disk 30 can also be configured with a constriction in the axial direction in the radially outer region.
  • FIG. 5 shows a diagrammatically illustrated hydrodynamic axial sliding bearing according to a third exemplary embodiment according to the disclosure.
  • the load-bearing face 31 is oriented radially on that side of the floating disk 30 which faces the bearing comb, that is to say perpendicularly with respect to the rotational axis of the shaft 40 .
  • the load-bearing face 11 of the bearing comb is shaped such that it is inclined toward the floating disk 30 , which results in a constriction in the axial direction in the radially outer region of the lubricating gap 52 .
  • the second lubricating gap which is likewise provided with a constriction in the axial direction in the radially outer region extends between the load-bearing face 32 which is oriented radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 , on that side of the floating disk 30 which faces the axial stop and the load-bearing face 22 of the axial stop 21 on the bearing housing, which load-bearing face 22 is inclined toward the floating disk 30 .
  • the floating disk is therefore provided with two sides which run parallel to one another and are oriented perpendicularly with respect to the rotational axis of the shaft 40 .
  • the load-bearing face 11 which is inclined toward the floating disk in the cold state, of the bearing comb, stretches in such a way that, during nominal operation, the angle of the constriction of the lubricating gap 52 ′ is reduced and the two load-bearing faces 31 and 11 ′ of the bearing run parallel to one another or virtually parallel to one another.
  • FIG. 6 shows a diagrammatically illustrated hydrodynamic axial sliding bearing according to a fourth exemplary embodiment according to the disclosure, which hydrodynamic axial sliding bearing differs from the preceding one in that the load-bearing face 11 of the bearing comb is oriented radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 .
  • the load-bearing face 31 is configured so as to be inclined toward the bearing comb 10 on that side of the floating disk 30 which faces the bearing comb.
  • the second lubricating gap which is likewise provided with a constriction in the axial direction in the radially outer region, extends between the load-bearing face 32 which is oriented strictly radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 , on that side of the floating disk which faces the axial stop and the load-bearing face 22 of the axial stop 21 on the bearing housing, which load-bearing face 22 is inclined toward the floating disk 30 .
  • the floating disk is therefore of conical configuration on the side which faces the bearing comb, whereas it is oriented perpendicularly with respect to the rotational axis of the shaft 40 on the other side which faces the axial stop on the bearing housing.
  • the load-bearing face 11 of the bearing comb which is oriented perpendicularly with respect to the rotational axis of the shaft 40 in the cold state, bends in such a way that, during nominal operation, the angle of the constriction of the lubricating gap 52 ′ is reduced and the two load-bearing faces 31 and 11 ′ of the bearing run parallel to one another or virtually parallel to one another.
  • FIG. 7 shows a diagrammatically illustrated hydrodynamic axial sliding bearing according to a fifth exemplary embodiment according to the disclosure.
  • the load-bearing face 11 of the bearing comb is oriented radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 .
  • the load-bearing face 31 is configured so as to be inclined toward the bearing comb 10 , which results in a constriction in the axial direction in the radially outer region of the lubricating gap 52 .
  • the second lubricating gap which is likewise provided with a constriction in the axial direction in the radially outer region, extends between the load-bearing face, which is oriented strictly radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 , of the axial stop 21 on the bearing housing and the load-bearing face 32 which is inclined toward the axial stop on that side of the floating disk which faces the axial stop.
  • the floating disk 30 is therefore configured so as to be conical on both sides.
  • the load-bearing face 11 which is oriented perpendicularly with respect to the rotational axis of the shaft 40 in the cold state, of the bearing comb bends in such a way that, during nominal operation, the angle of the constriction of the lubricating gap 52 ′ is reduced and the two load-bearing faces 31 and 11 ′ of the bearing run parallel to one another or virtually parallel to one another.
  • FIG. 8 shows a diagrammatically illustrated hydrodynamic axial sliding bearing according to a sixth exemplary embodiment according to the disclosure, which hydrodynamic axial sliding bearing differs from the preceding one in that the load-bearing face 31 on that side of the floating disk 30 which faces the bearing comb is oriented radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 .
  • the load-bearing face 11 of the bearing comb is shaped so as to be inclined toward the floating disk 30 , which results once again in a constriction in the axial direction in the radially outer region of the lubricating gap 52 .
  • the second lubricating gap which is likewise provided with a constriction in the axial direction in the radially outer region once again extends between the load-bearing face 22 , which is oriented radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 , of the axial stop 21 on the bearing housing and the load-bearing face 32 which is inclined toward the axial stop on that side of the floating disk which faces the axial stop.
  • the floating disk is therefore of conical configuration on the side which faces the axial stop on the bearing housing, whereas it is oriented perpendicularly with respect to the rotational axis of the shaft 40 on the other side which faces the bearing comb.
  • the load-bearing face 11 which is inclined toward the floating disk in the cold state, of the bearing comb stretches in such a way that, during nominal operation, the angle of the constriction of the lubricating gap 52 ′ is reduced and the two load-bearing faces 31 and 11 ′ of the bearing run parallel to one another or virtually parallel to one another.
  • FIG. 9 and FIG. 10 in each case show a hydrodynamic axial sliding bearing without a floating disk, in which a load-bearing face 12 is arranged on the rotating bearing comb 10 and a load-bearing face 22 is arranged on the axial stop 21 of the bearing housing 20 .
  • the lubricating gap 53 which results between them is configured so as to converge radially to the outside, that is to say the lubricating gap tapers in the radially outer region.
  • the seventh exemplary embodiment according to the disclosure (shown in FIG. 9 ) of a hydrodynamic axial sliding bearing has a load-bearing face 12 of the bearing comb 10 , which load-bearing face 12 is shaped so as to be inclined toward the axial stop 21 of the bearing housing 20 , which results in the constriction in the axial direction in the radially outer region of the lubricating gap 53 .
  • the load-bearing face 22 of the axial stop 21 of the bearing housing 20 is oriented strictly radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 , in this exemplary embodiment.
  • the load-bearing face 12 of the bearing comb which is inclined toward the load-bearing face of the axial stop 21 in the cold state, stretches in such a way that, during nominal operation, the angle of the constriction of the lubricating gap 53 ′ is reduced and the two load-bearing faces 12 ′ and 22 of the bearing run parallel to one another or virtually parallel to one another.
  • the eighth exemplary embodiment according to the disclosure (shown in FIG. 10 ) of a hydrodynamic axial sliding bearing has a load-bearing face 12 of the bearing comb 10 , which load-bearing face 12 is oriented radially, that is to say perpendicularly with respect to the rotational axis of the shaft 40 .
  • the load-bearing face 22 of the axial stop 21 on the bearing housing 20 is configured so as to be inclined toward the bearing comb 10 , which results once again in the constriction in the axial direction in the radially outer region of the lubricating gap 53 .
  • the axial stop is therefore of conical configuration on the side which faces the bearing comb.
  • the load-bearing face 12 of the bearing comb 10 which is oriented perpendicularly with respect to the rotational axis of the shaft 40 in the cold state, bends in such a way that, during nominal operation, the angle of the constriction of the lubricating gap 53 ′ is reduced and the two load-bearing faces 12 ′ and 22 of the bearing run parallel to one another or virtually parallel to one another.
  • the load-bearing faces in each case one of the load-bearing faces is described as deviating from the plane which is oriented perpendicularly with respect to the rotational axis of the shaft and the other load-bearing face is described as running radially, that is to say along a plane which is oriented perpendicularly with respect to the rotational axis of the shaft.
  • the narrowing lubricating gaps can also be realized by the respective load-bearing faces both deviating from respective planes which are oriented perpendicularly with respect to the rotational axis of the shaft, but being at an angle with respect to one another.
  • both the load-bearing face on that side of the floating disk which faces the bearing comb and the load-bearing face on the bearing comb can run so as to be inclined toward the lubricating gap in comparison with the plane which is oriented perpendicularly with respect to the rotational axis of the shaft, and can thus delimit the narrowing lubricating gap.
  • load-bearing face means in each case that region of the profiled surface which is called rest face. In the absence of a rest face, the load-bearing face extends along the maximum elevation of the wedge faces in the transition region to the respectively next lubricating oil groove.

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  • 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)
US14/268,466 2011-11-03 2014-05-02 Hydrodynamic axial bearing Abandoned US20140241887A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102011085681.1 2011-11-03
DE102011085681A DE102011085681A1 (de) 2011-11-03 2011-11-03 Hydrodynamisches Axiallager
PCT/EP2012/071729 WO2013064638A1 (fr) 2011-11-03 2012-11-02 Palier axial hydrodynamique

Related Parent Applications (1)

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

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US20140241887A1 true US20140241887A1 (en) 2014-08-28

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US14/268,466 Abandoned US20140241887A1 (en) 2011-11-03 2014-05-02 Hydrodynamic axial bearing

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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)

Cited By (5)

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Publication number Priority date Publication date Assignee Title
WO2016175695A1 (fr) * 2015-04-30 2016-11-03 Scania Cv Ab Agencement d'étanchéité pour machine hydrodynamique
US20170226859A1 (en) * 2016-02-04 2017-08-10 Rolls-Royce Plc Balancing of axial thrust forces within a gas turbine engine
US10113586B2 (en) * 2015-10-16 2018-10-30 Ford Global Technologies, Llc Hydrodynamic axial plain bearing
US10513928B2 (en) * 2017-08-31 2019-12-24 Flowserve Management Company Axial thrust balancing device
US11047420B2 (en) 2017-07-19 2021-06-29 Konzelmann Gmbh Hydrodynamic bearing

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DE102015215306B4 (de) * 2015-08-11 2018-08-02 Siemens Healthcare Gmbh Flüssigmetall-Gleitlager
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
DE102017102420A1 (de) * 2017-02-08 2018-08-09 Abb Turbo Systems Ag Gleitlagerung mit hydrodynamischer axialsicherung
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
WO2024104528A1 (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 ayant un palier axial

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016175695A1 (fr) * 2015-04-30 2016-11-03 Scania Cv Ab Agencement d'étanchéité pour machine hydrodynamique
CN107407425A (zh) * 2015-04-30 2017-11-28 斯堪尼亚商用车有限公司 用于流体动力机械的密封装置
US10113586B2 (en) * 2015-10-16 2018-10-30 Ford Global Technologies, Llc Hydrodynamic axial plain bearing
US20170226859A1 (en) * 2016-02-04 2017-08-10 Rolls-Royce Plc Balancing of axial thrust forces within a gas turbine engine
US10539021B2 (en) * 2016-02-04 2020-01-21 Rolls-Royce Plc Balancing of axial thrust forces within a gas turbine engine
US11047420B2 (en) 2017-07-19 2021-06-29 Konzelmann Gmbh Hydrodynamic bearing
US10513928B2 (en) * 2017-08-31 2019-12-24 Flowserve Management Company Axial thrust balancing device

Also Published As

Publication number Publication date
DE102011085681A1 (de) 2013-05-08
CN103906936A (zh) 2014-07-02
BR112014010582A2 (pt) 2017-05-02
HK1199084A1 (en) 2015-06-19
KR20140083051A (ko) 2014-07-03
CA2852164A1 (fr) 2013-05-10
EP2773877A1 (fr) 2014-09-10
SG11201401938WA (en) 2014-10-30
WO2013064638A1 (fr) 2013-05-10
JP2014533342A (ja) 2014-12-11

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