CN103906936A - Hydrodynamic axial bearing - Google Patents
Hydrodynamic axial bearing Download PDFInfo
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- CN103906936A CN103906936A CN201280054248.5A CN201280054248A CN103906936A CN 103906936 A CN103906936 A CN 103906936A CN 201280054248 A CN201280054248 A CN 201280054248A CN 103906936 A CN103906936 A CN 103906936A
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- Prior art keywords
- bearing
- lubrication gap
- cod
- comb
- hydrodynamic
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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
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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
- F01D25/18—Lubricating arrangements
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- 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
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- 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
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- 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
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- 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
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- 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
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- 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
Abstract
A hydrodynamic axial bearing for the mounting of a shaft (40) which is mounted rotatably in a bearing housing (20), comprising an axial stop (21) of the bearing housing and a bearing collar (10) rotating with the shaft. A lubricating gap (52) which is delimited by a profiled circular ring surface (31) and a sliding surface (11) and is acted upon by lubricating oil is formed between the axial stop (21) and the bearing collar (10). The profiled circular ring surface (31) and the sliding surface (11) are formed in such a manner that the lubricating gap (52) tapers radially outwards with respect to the axial direction. As a result, temperature deformations occurring during operation and deformation because of centrifugal forces, shearing forces and other forces in the bearing collar can be compensated for.
Description
Technical field
The field that the present invention relates to Hydrodynamic (hydrodynamisch) axially mounting of running shaft, it is for example applied in fluid machinery, is applied in exhaust-gas turbocharger in particular.
Background technique
If load atwirl rotor with axial thrust, use the cod that can carry.For example, at fluid machinery for example in exhaust-gas turbocharger, using liquid dynamic pressure cod is to bear and to flow relevant high axial force and for leading axle in the axial direction.In order to improve oblique position compensation ability and polishing machine in this application, in Hydrodynamic cod between the bearing comb (Lagerkamm) with axle rotating speed rotation and the axial stop in the not rotation at bearing housing place freely unsteady dish, so-called floating disc in lubricant oil of application.Between the bearing comb of rotation and floating disc and in floating disc and the lubrication gap between the static axial stop in bearing housing place advantageously respectively by thering is (profiliert) toroidal surface of contoured and the flat slip surface restriction relative with the toroidal surface with contoured.This toroidal surface with contoured is set up for the important pressure of the supporting force for cod of optimizing in lubrication gap.The lubricant oil of carrying in order to be distributed in the region that is arranged in inner radial of the toroidal surface with contoured, the oil groove that exists radially outward to guide.Contiguous oil groove is configured with the sphenoid surface that upwards makes lubrication gap narrow in week, and the lubricant oil being introduced in oil groove flows out by this sphenoid surface.At this, lubricant oil is directed in sphenoid surface as far as possible in the whole radial height of oil groove.Set up and substantially in the region of sphenoid surface, realize for the pressure of bearing capacity necessity of cod.To be upwards configured with stop surface (Rastfl che) in abutting connection with the mode of sphenoid surface in week, it comprises that flat face and formation (ausmachen) have the supporting plane of the toroidal surface of contoured.
Especially the example of known such cod in document GB1095999, EP0840027, EP1199486, EP1644647 and EP2042753.The radial directed of floating disc or that is to say on axle or on bearing comb that in the main body of rotation the radial bearing (for example disclosed in document EP0840027) by being integrated in floating disc realizes, but or for example, in bearing flange (Lagerbund) upper (disclosed in document EP1199486) realization of the fixing main body of surrounding with one heart rotation.The lubricated of this Hydrodynamic cod realized by means of the lubricant oil of the lubricating oil system from special conventionally, or the lubricating oil system by the internal-combustion engine that is connected with exhaust-gas turbocharger realizes the in the situation that of exhaust-gas turbocharger.
All supporting planes of traditional axially mounting in cold state in state of rest the spin axis perpendicular to rotor, but or at least parallel to each other.Be in operation, supporting plane may be out of shape due to temperature gradient, centrifugal force, thrust and other power.Such distortion of loading ability of bearing face can damage the bearing capacity of supporting.Temperature gradient on the comb (Kamm) of comb shape bearing (Kammlager) can have especially large effect.With respect to the radially-protruding comb of axle because the temperature difference between supporting plane and rear side is out of shape in the mode of umbrella shape.This distortion can cause comb shape bearing touching (anstreifen) floating disc, supplies with pressure in particular at low oil.In the case of traditional comb shape bearing structure, because the distortion that temperature gradient causes is very serious, because it causes the lubrication gap of outside expansion.This layout (Konstellation) has reduced bearing capacity for the reason of geometrical shape on the one hand and it has reduced to set up at the pressure relevant to centrifugal force in the radial direction on the other hand, because reduced the outflow resistance of radially outward for lubricant oil.
Summary of the invention
Therefore target of the present invention is, improves the bearing capacity of the Hydrodynamic cod for supporting the axle that can be rotated to support on bearing housing.
If at least relative to each other arrange obliquely in the region of radially outer that by supporting plane the gap that makes to be configured between the supporting plane of cod is configured to outwards narrowing in the radial direction, be in operation and obtain the reducing of relative tilt state of supporting plane due to the above-mentioned distortion of the supporting plane of rotation.Narrowing in radially outer region reduces, thereby supporting plane is in operation and is more positioned evenly over each other and goes up.
If for example bearing comb is made the supporting plane tilting towards relative supporting plane with taper, can compensate the temperature deformation in comb shape bearing.In the time of compensation, must consider equally the distortion causing due to centrifugal force, thrust and other power.
Because comb shape bearing deformation is relevant to operating point, therefore lubrication gap is diminishing in the radial direction under certain operating conditions.This situation, such as the present is more favourable with the situation of the lubrication gap expanding, is set up at the pressure relevant to centrifugal force in the radial direction because bearing capacity less reduces and is conducive to.
Because being out of shape the compensation carried out, the supporting plane causing by temperature gradient, centrifugal force, thrust and other power can or not have at floating disc place to realize at the axial stop place of bearing housing the cod of floating disc yet.In the region of the axial stop at bearing housing place that may occur and distortion temperature correlation can to implement in the similar mode in comb shape bearing place.
If use the floating disc of bilateral taper or the floating disc that the very thin geometry situation that is in operation with changes matches, comb shape bearing deformation also can be by the conical configuration scheme compensation of the axial stop at bearing housing place.
By means of the compensation to distortion, cod prevent aspect the contiguous bearing part of bearing part that the touching of floating disc or bearing comb is contiguous or the touching of (not having the cod of floating disc) cod more firm.The operation of turbosupercharger is more reliable and can reduce the cost relevant to wearing and tearing.
Brief description of the drawings
Following according to drawing explanation form of implementation of the present invention in detail.Wherein:
Fig. 1 has shown along the cross section of the form of implementation through the axial plain bearing of constructing according to prior art of spin axis guiding in the part of right side, this axial plain bearing is with the bearing comb of rotation, fixing axial stop and floating disc, and in left part, show with the front elevation in the axial direction of corresponding floating disc of toroidal surface with contoured
Fig. 2 has shown the schematically illustrated axial plain bearing according to Fig. 1, wherein, this figure and all after figure in respectively at bearing comb shown in cold state, and additionally point out in running state owing to heating and the distortion of the bearing comb that fast rotational causes and the lubrication gap obtaining thus with dotted line
Fig. 3 has shown according to according to the schematically illustrated axial plain bearing of the first form of implementation of the present invention, the lubrication gap that its bearing comb with taper ground moulding and the radially outward obtaining thus narrow,
Fig. 4 shown according to according to the schematically illustrated axial plain bearing of the second form of implementation of the present invention, the lubrication gap that it narrows with the floating disc in bearing comb side taper ground moulding and the radially outward that obtains thus,
Fig. 5 has shown according to according to the schematically illustrated axial plain bearing of the 3rd form of implementation of the present invention, the bearing comb of its cod with taper ground moulding and taper ground moulding, and two lubrication gaps that the radially outward obtaining thus narrows,
Fig. 6 has shown according to according to the schematically illustrated axial plain bearing of the 4th form of implementation of the present invention, it is with the cod of taper ground moulding with at the floating disc of bearing comb side taper ground moulding, the lubrication gap narrowing with two radially outwards that obtain thus
Fig. 7 shown according to according to the schematically illustrated axial plain bearing of the 5th form of implementation of the present invention, and it is with the floating disc of both sides taper ground moulding, and two lubrication gaps that the radially outward obtaining thus narrows,
Fig. 8 has shown according to according to the schematically illustrated axial plain bearing of the 6th form of implementation of the present invention, it is with the bearing comb of taper ground moulding with at the floating disc of cod side taper ground moulding, the lubrication gap narrowing with two radially outwards that obtain thus
Fig. 9 shown according to according to the schematically illustrated axial plain bearing of the 7th form of implementation of the present invention, its not with floating disc, the lubrication gap that narrows with the bearing comb of taper ground moulding and the radially outward that obtains thus, and
Figure 10 shown according to according to the schematically illustrated axial plain bearing of the 8th form of implementation of the present invention, its again not with floating disc, the lubrication gap that narrows with the axial stop of taper ground moulding and the radially outward that obtains thus.
Embodiment
Fig. 1 has exemplarily shown the Hydrodynamic cod according to prior art, wherein, can see three critical pieces of cod in the part of the right side of figure in the cross section axially guiding along running shaft.Bearing comb 10 is installed on running shaft 40 (or be connected ordinatedly with shaft material alternatively or make integratedly with axle) and rotates together with the axis.Axially between the upper axial stop 21 at bearing housing 20 places and bearing comb, be furnished with floating disc 30.Between axial stop and floating disc and on the other hand, between floating disc and bearing comb, be configured with respectively lubrication gap on the one hand, in this lubrication gap, between supporting plane, having thin lube layer.In shown form of implementation, have respectively in week and be upwards designed to flat slip surface at the supporting plane 22 at axial stop place with at the supporting plane 11 at bearing comb place, and two supporting planes of floating disc are parts with the toroidal surface of contoured.All described below according to this basic structure that also adopts two lubrication gaps in the form of implementation of the Hydrodynamic axial plain bearing with floating disc of the present invention.What be suitable for for all these forms of implementation is, situation lower slider face in Huo Liangge lubrication gap, a lubrication gap also can be arranged on the corresponding opposite side of lubrication gap with the toroidal surface with contoured, thereby for example floating disc has respectively flat slip surface in both sides, and the toroidal surface with contoured is arranged on the supporting plane of bearing comb and in the axial stop of bearing housing.The toroidal surface correspondingly in the form of implementation that there is no floating disc with contoured can be arranged on the bearing comb of rotation, and flat slip surface is arranged in the axial stop of bearing housing or in any case can be contrary, flat slip surface is arranged on the bearing comb of rotation and the toroidal surface with contoured is arranged in the axial stop of bearing housing.
From the left part among Fig. 1, can find out the structure of the toroidal surface with contoured, therein, floating disc has rotated 90 °, thereby in plan view, can find out in floating disc distolateral.
The toroidal surface with contoured is set up for the important pressure of the bearing capacity for cod of optimizing the lubrication gap between supporting plane.The contoured of toroidal surface comprises multiple sections, its respectively with radially outward guiding for being distributed in the oil groove 33 of the lubricant oil that the region of inner radial of the toroidal surface with contoured is transferred.With the sense of rotation of the toroidal surface with contoured of pointing out by black arrow on the contrary, contiguous oil groove 33 ground are configured with at the sphenoid surface 34 that upwards makes lubrication gap narrow in week, and the lubricant oil being introduced in oil groove 33 flows out according to thick arrow by this sphenoid surface 34.In whole radial height at oil groove 33, be directed in sphenoid surface 34 as far as possible at this lubricant oil.Set up and substantially in the region of sphenoid surface, realize for the pressure of bearing capacity necessity of cod.Be configured with stop surface 35 in the mode that is upwards contiguous to sphenoid surface 34 places in week, it comprises flat face, this flat face with there is minimum range as the conjugate profile of slip surface described above.Thus, the axial elongation of lubrication gap (thickness) can be described as be at the distance between stop surface 35 and relative slip surface.Set up the bridge part sealing that oil groove and the utilization of sphenoid surface radially outward narrow lubrication gap in order to optimize the pressure in oil groove and on sphenoid surface in direction radially.Typically extend until on the height of stop surface at this bridge part, thereby stop surface and bridge part are arranged in a plane.
Form of implementation described below is saved to the structure of oil groove and sphenoid surface.Correspondingly, below, do not re-use toroidal surface and slip surface that concept has contoured.But be to be noted that for actual implementation lubrication gap advantageously limited by the slip surface of the toroidal surface peace with contoured respectively as described above.Such region of mentioning the toroidal surface with contoured in the concept of the following effective supporting plane using, it is commonly called stop surface.Stop surface is typically observed and then sphenoid surface on the flow direction of lubricant oil.
As in Fig. 1 and point out according to the details shown in the amplification of Fig. 2, but the supporting plane of axially mounting is configured to perpendicular to the spin axis of rotor is or at least parallel to each other in cold state in the time of stationary rotor.Be in operation, the supporting plane in bearing comb is because temperature gradient, centrifugal force, thrust and other power are out of shape.With respect to the radially-protruding comb of axle due to the supporting plane important for cod and deviate from temperature difference between the rear side of this supporting plane and umbrella shape be out of shape.This distortion of pointing out with dotted line in Fig. 2 can cause comb shape bearing to touch floating disc in the region of inner radial, because the supporting plane 31 that the bearing capacity of lubrication gap is dispersed due to the radially outward of cod and 11' and the clog-free outflow of lubricant oil related to this reduce, in particular in the time that low fluid is supplied with pressure, make-up oil fully in the time that low fluid is supplied with pressure.
Fig. 3 has shown according to according to the schematically illustrated Hydrodynamic cod of the first form of implementation of the present invention.At this, be strictly radially orientated at the effective supporting plane 31 of facing on the side of bearing comb of floating disc 30, that is to say the spin axis orientation perpendicular to axle 40.On the contrary, the mode moulding of the supporting plane 11 of bearing comb to tilt towards floating disc 30, thus in the region of the radially outer of lubrication gap 52, obtain narrowing in the axial direction.Being tilted in this form of implementation of the supporting plane 11 of bearing comb, same can be by uniformly straight inclination or by curved inclination realization in other form of implementation described below.In the accompanying drawings, show very large the distortion of member and the narrowing of lubrication gap of rotation.In fact, angle of inclination arranged according to the present invention all changes on the whole radius of the member tilting in the scope in percent several years, for example in the dish with 200 mm dias, obtains thus lubrication gap narrowing at radially outward edge place a few percent millimeter.Be in operation, due to the heating of bearing comb described above and obtain the distortion of bearing comb by mentioned power effect, it is pointed out with dotted line again.According to the present invention, the supporting plane 11 of the bearing comb tilting towards lubricated dish in cold state so stretches, reduces and two supporting planes 31 of bearing and 11' is parallel to each other or present lubrication gap still less with respect to cold state in maintenance at least almost stretches in parallel with each other narrowing in the angle of the portion that narrows of specified lubrication gap 52' in service.In cold state in state of rest and also in the time of the slow-speed of revolution structural scheme according to the present invention of axial plain bearing to cause lubrication gap to narrow in the region of radially outer be no problem because the lubricant oil being plugged is set up for additional pressure.
Fig. 4 has shown according to according to the schematically illustrated Hydrodynamic axial plain bearing of the second form of implementation of the present invention.Supporting plane 11 at this bearing comb is strictly radially orientated, and that is to say the spin axis orientation perpendicular to axle 40.For this reason, in this form of implementation, be configured to tilt towards bearing comb 10 at the supporting plane 31 in the face of on the side of bearing comb of floating disc 30, thereby in the radially outer region of lubrication gap 52, again obtain narrowing in the axial direction.Thus, floating disc is being configured to taper in the face of on the side of bearing comb, and its spin axis perpendicular to axle 40 on another side of the axial stop in the face of at bearing housing place is orientated.Be in operation, due to the heating of bearing comb described above and obtain the distortion of bearing comb by the effect of mentioned power, it utilizes dotted line to point out again.According to the present invention, supporting plane 11 perpendicular to the bearing comb of the spin axis orientation of axle 40 in cold state is so bending, reduces and two supporting planes 31 and the 11' of bearing stretch in parallel with each other or almost in parallel with each other in the angle of the portion that narrows of specified lubrication gap 52' in service.
According in the form of implementation of Fig. 5 to 8, except the lubrication gap 52 between floating disc 30 and bearing comb 10, in the lubrication gap 51 between axial stop 21 and the floating disc 30 also region at radially outer, be configured to narrowing in the axial direction.
Fig. 5 has shown according to according to the schematically illustrated Hydrodynamic axial plain bearing of the 3rd form of implementation of the present invention.At this, be strictly radially orientated at the supporting plane 31 of facing on the side of bearing comb of floating disc 30, that is to say the spin axis orientation perpendicular to axle 40.On the contrary, the mode moulding of the supporting plane 11 of bearing comb to tilt towards floating disc 30, thus in the region of the radially outer of lubrication gap 52, obtain narrowing in the axial direction.Same the second lubrication gap that is provided with the portion that narrows in the axial direction in the region of radially outer floating disc 30 radially that is to say perpendicular to the supporting plane 32 of the spin axis orientation of axle 40 and the supporting plane tilting towards floating disc 30 22 in the axial stop 21 at bearing housing place in the face of strict on the side of axial stop between extend.Floating disc is provided with the side stretching in parallel with each other of two orientations of the spin axis perpendicular to axle 40 thus.Be in operation, due to the heating described above of bearing comb and obtain the distortion of bearing comb 10 by the effect of mentioned power, it is pointed out with dotted line again.According to the present invention, the supporting plane 11 of the bearing comb tilting towards floating disc in cold state is so bending, reduces and two supporting planes 31 and the 11' of bearing stretch in parallel with each other or almost in parallel with each other in the angle of the portion that narrows of specified lubrication gap 52' in service.
Fig. 6 has shown according to according to the schematically illustrated Hydrodynamic axial plain bearing of the 4th form of implementation of the present invention, they are different from above-mentioned form of implementation in the following manner, and the strict radially orientation of the supporting plane 11 of bearing comb that is to say perpendicular to the spin axis orientation of axle 40 and is configured to tilt towards bearing comb 10 at the supporting plane 31 in the face of on the side of bearing comb of floating disc 30 for this reason.Same the second lubrication gap that is provided with the portion that narrows in the axial direction in the region of radially outer floating disc radially that is to say perpendicular to the supporting plane 32 of the spin axis orientation of axle 40 and the supporting plane tilting towards floating disc 30 22 in the axial stop 21 at bearing housing place in the face of strict on the side of axial stop between extend.Floating disc is thus in the face of being configured to taper on the side of bearing comb, and its on another side of the axial stop in the face of at bearing housing place perpendicular to spin axis orientation of axle 40.Be in operation, due to the heating described above of bearing comb and obtain the distortion of bearing comb by the effect of mentioned power, it is pointed out with dotted line again.According to the present invention, supporting plane 11 perpendicular to the bearing comb of the spin axis orientation of axle 40 in cold state is so bending, reduces and two supporting planes 31 and the 11' of bearing stretch in parallel with each other or almost in parallel with each other in the angle of the portion that narrows of specified lubrication gap 52' in service.
Fig. 7 has shown according to according to the schematically illustrated Hydrodynamic axial plain bearing of the 5th form of implementation of the present invention.At this, the supporting plane 11 of bearing comb is strictly radially orientated, and that is to say the spin axis orientation perpendicular to axle 40.On the contrary, be configured to tilt towards bearing comb 10 at the supporting plane 31 in the face of on the side of bearing comb of floating disc 30, thereby obtain the portion that narrows in the axial direction in the region of the radially outer of lubrication gap 52.Same the second lubrication gap that is provided with the portion that narrows in the axial direction in the region of radially outer radially that is to say the supporting plane being orientated perpendicular to the spin axis of axle 40 and extends facing between the supporting plane 32 tilting towards axial stop on the side of axial stop of floating disc at the strict of axial stop 21 at bearing housing place.Floating disc 30 is configured to taper in both sides thus.Be in operation, due to the heating described above of bearing comb and obtain the distortion of bearing comb 10 by the effect of mentioned power, it is pointed out with dotted line again.According to the present invention, supporting plane 11 perpendicular to the bearing comb of the spin axis orientation of axle 40 in cold state is so bending, reduces and two supporting planes 31 and the 11' of bearing stretch in parallel with each other or almost in parallel with each other in the angle of the portion that narrows of specified lubrication gap 52' in service.
Fig. 8 has shown according to according to the schematically illustrated Hydrodynamic axial plain bearing of the 6th form of implementation of the present invention, they are different from above-mentioned form of implementation in the following manner, be strictly radially orientated at the supporting plane 31 of facing on the side of bearing comb of floating disc 30, that is to say the spin axis orientation perpendicular to axle 40, and the mode moulding of the supporting plane 11 of bearing comb to tilt towards floating disc 30 for this reason, thereby in the region of the radially outer of lubrication gap 52, again obtain narrowing in the axial direction.Same the second lubrication gap that is provided with the portion that narrows in the axial direction in the region of radially outer again the axial stop 21 at bearing housing place strict radially, that is to say perpendicular to the supporting plane 22 of the spin axis orientation of axle 40 and floating disc in the face of the supporting plane 32 tilting towards axial stop on the side of axial stop between extend.Floating disc is configured to taper thus on the side of the axial stop in the face of at bearing housing place, and it is being orientated in the face of the spin axis perpendicular to axle 40 on another side of bearing comb.Be in operation, due to the heating described above of bearing comb and obtain the distortion of bearing comb by the effect of mentioned power, it is pointed out with dotted line again.According to the present invention, the supporting plane 11 of the bearing comb tilting towards floating disc in cold state is so bending, reduces and two supporting planes 31 and the 11' of bearing stretch in parallel with each other or almost in parallel with each other in the angle of the portion that narrows of specified lubrication gap 52' in service.
Latter two figures has shown respectively the not Hydrodynamic cod with floating disc, and therein, supporting plane 12 is arranged on the bearing comb 10 of rotation and supporting plane 22 is arranged in the axial stop 21 of bearing housing 20.The lubrication gap 53 obtaining between it according to the present invention again radially outward be configured to convergence, that is to say that lubrication gap narrows in the region of radially outer.
The 7th form of implementation according to the present invention of the Hydrodynamic axial plain bearing showing in Fig. 9 has the supporting plane 12 of bearing comb 10, the mode moulding that it tilts with the axial stop 21 towards bearing housing 20, thus narrowing in the axial direction in the radially outer region of lubrication gap 53, obtained.The supporting plane 22 of the axial stop 21 of bearing housing 20 is to be strictly radially orientated in this form of implementation, that is to say the spin axis orientation perpendicular to axle 40.Be in operation, due to the heating described above of bearing comb and again obtain the distortion of bearing comb by the effect of mentioned power, it is pointed out with dotted line again.According to the present invention, the supporting plane 12 of the bearing comb tilting towards the supporting plane of axial stop 21 in cold state so stretches,, reduce and two supporting plane 12' and 22 of bearing stretch in parallel with each other or almost in parallel with each other in the angle of the portion that narrows of specified lubrication gap 53' in service.
The 8th form of implementation according to the present invention of the Hydrodynamic axial plain bearing showing in Figure 10 has the supporting plane 12 of bearing comb 10, its strictly radially, that is to say the spin axis orientation perpendicular to axle 40., construct in the mode tilting towards bearing comb 10 in this form of implementation at the supporting plane 22 of the axial stop 21 at bearing housing 20 places for this reason, thereby in the radially outer region of lubrication gap 53, again obtain narrowing in the axial direction.Axial stop is in the face of being configured to taper on the side of bearing comb thus.Be in operation, due to the heating described above of bearing comb and again obtain the distortion of bearing comb by the effect of mentioned power, it is pointed out with dotted line again.According to the present invention, supporting plane 12 perpendicular to the bearing comb 10 of the spin axis orientation of axle 40 in cold state is so bending, reduces and two supporting plane 12' and 22 of bearing stretch in parallel with each other or almost in parallel with each other in the angle of the portion that narrows of specified lubrication gap 53' in service.
In all embodiments, in supporting plane one is described as respectively the plane being different from perpendicular to the spin axis orientation of axle, and another in supporting plane is described as strictly the plane radially stretching, be orientated along the spin axis perpendicular to axle and stretches.According to the present invention, by both departing from perpendicular to the plane of the spin axis orientation of axle but there is each other angle in respective carrier face, also can realize the lubrication gap narrowing.For example, in the form of implementation with floating disc, not only in the lubrication gap that mode stretches and restriction narrows thus to tilt with respect to the plane of the spin axis orientation perpendicular to axle towards lubrication gap in the face of the supporting plane on the side of bearing comb but also the supporting plane on bearing comb of floating disc.
Although only set forth respectively supporting plane in all above-mentioned forms of implementation, should again be pointed out that at this, there is the surface with contoured with oil groove, sphenoid surface and stop surface if limit one or two in the member of corresponding lubrication gap, concept supporting plane represents respectively to have surperficial such region of contoured, and this region description becomes stop surface.In the time there is no stop surface, supporting plane is raised and is extended in corresponding next oil groove along the maximum of the sphenoid surface in transition region.
List of reference characters
10 bearing combs
11,12 supporting planes at bearing comb place
11', 12' is at the supporting plane (in running state) at bearing comb place
20 bearing housinges
21 axial stop
22 slip surfaces
30 floating discs
The supporting plane of 31,32 floating discs
33 oil grooves
34 sphenoid surface
35 stop surfaces
40 axles
51 lubrication gaps between axial stop and floating disc
52 lubrication gaps between floating disc and bearing comb
The lubrication gap (in running state) of 52' between floating disc and bearing comb
53 lubrication gaps between axial stop and bearing comb
The lubrication gap (in running state) of 53' between axial stop and bearing comb
Claims (9)
1. one kind can be rotated to support on the Hydrodynamic cod of the axle (40) of bearing housing (20) for supporting, this cod comprises the axial stop (21) of bearing housing (20) and the bearing comb (10) along with axle rotation, wherein between described axial stop (21) and described bearing comb (10), be configured with the lubrication gap that is loaded with lubricant oil (51 that at least one limits with the flat slip surface (22) relative with the toroidal surface with contoured by having the toroidal surface of contoured, 52, 53), the wherein said toroidal surface with contoured is configured to around described axle (40) rotation or along with described axle (40) rotates together, the contoured of wherein said toroidal surface has multiple sections, these sections are respectively with the oil groove radially stretching (33), at the sphenoid surface (34) being upwards connected with described oil groove (33) in week and the stop surface (35) that is upwards being contiguous to described sphenoid surface (34) week and locates, it is characterized in that, in at least one lubrication gap (51, 52, 53) in situation, described stop surface (35) and described flat slip surface (22) are so constructed, narrow about axial direction by lubrication gap (52) radially outward of described stop surface (35) and described flat slip surface (22) restriction.
2. Hydrodynamic cod according to claim 1, it is characterized in that, the flat slip surface (22) of the axial stop of the lubrication gap (51,53) that restriction radially outward narrows at least is differently configured to tilt towards described bearing comb (10) in the part of radially outer Yu perpendicular to the plane of institute's spin axis.
3. according to the Hydrodynamic cod described in any one in claim 1 or 2, it is characterized in that, the flat slip surface (22) of the bearing comb (10) of the lubrication gap (52,53) that narrows of restriction radially outward be differently configured to tilt towards described axial stop (21) perpendicular to the plane of institute's spin axis.
4. according to the Hydrodynamic cod described in any one in claims 1 to 3, it is characterized in that, axially above between described axial stop (21) and described bearing comb (10), be furnished with floating disc (30), and wherein, be configured between described lubricated dish (30) and described bearing comb (10) by thering is the toroidal surface of contoured and relative flat slip surface (22) lubrication gap (52) restriction and that radially outward narrows.
5. Hydrodynamic cod according to claim 4, it is characterized in that, the flat slip surface of the toroidal surface with contoured of described floating disc (30) and described bearing comb (10) limits the lubrication gap (52) that described radially outward narrows, and wherein, described flat slip surface at least is differently configured to tilt towards described axial stop (21) in the part of radially outer Yu perpendicular to the plane of institute's spin axis.
6. according to the Hydrodynamic cod described in any one in claim 4 or 5, it is characterized in that, limit another lubrication gap (51) by described axial stop (21) and described floating disc, described in the restriction of wherein said axial stop (21) the flat slip surface (22) of another lubrication gap (51) be differently configured to tilt towards described floating disc (30) perpendicular to the plane of institute's spin axis.
7. a fluid machinery, comprises the axle (40) can be rotated to support in housing (20), with the Hydrodynamic cod described in any one in good grounds claim 1 to 6.
8. an exhaust-gas turbocharger, comprises the axle (40) can be rotated to support in housing (20), with the Hydrodynamic cod described in any one in good grounds claim 1 to 6.
9. exhaust-gas turbocharger according to claim 8, is characterized in that, described bearing comb (10) is connected ordinatedly or is made up of single-piece with described axle (40) material.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011085681.1 | 2011-11-03 | ||
| DE102011085681A DE102011085681A1 (en) | 2011-11-03 | 2011-11-03 | Hydrodynamic thrust bearing |
| PCT/EP2012/071729 WO2013064638A1 (en) | 2011-11-03 | 2012-11-02 | Hydrodynamic axial bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103906936A true CN103906936A (en) | 2014-07-02 |
Family
ID=47222025
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280054248.5A Pending CN103906936A (en) | 2011-11-03 | 2012-11-02 | Hydrodynamic axial bearing |
Country Status (11)
| Country | Link |
|---|---|
| US (1) | US20140241887A1 (en) |
| EP (1) | EP2773877A1 (en) |
| JP (1) | JP2014533342A (en) |
| KR (1) | KR20140083051A (en) |
| CN (1) | CN103906936A (en) |
| BR (1) | BR112014010582A2 (en) |
| CA (1) | CA2852164A1 (en) |
| DE (1) | DE102011085681A1 (en) |
| HK (1) | HK1199084A1 (en) |
| SG (1) | SG11201401938WA (en) |
| WO (1) | WO2013064638A1 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106438678A (en) * | 2015-08-11 | 2017-02-22 | 西门子医疗有限公司 | Liquid metal plain bearing |
| CN107407425A (en) * | 2015-04-30 | 2017-11-28 | 斯堪尼亚商用车有限公司 | Sealing device for fluid dynamic machinery |
| CN110249144A (en) * | 2017-02-08 | 2019-09-17 | Abb涡轮系统有限公司 | The sliding bearing of axial retention with fluid power |
| CN114321155A (en) * | 2020-09-30 | 2022-04-12 | 株式会社丰田自动织机 | Fluid machinery |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10113586B2 (en) * | 2015-10-16 | 2018-10-30 | Ford Global Technologies, Llc | Hydrodynamic axial plain bearing |
| JP6521838B2 (en) * | 2015-11-06 | 2019-05-29 | トヨタ自動車株式会社 | Support structure of rotating shaft |
| GB2547008B (en) * | 2016-02-04 | 2020-07-29 | Rolls Royce Plc | Balancing of axial thrust forces within a gas turbine engine |
| WO2019015753A1 (en) * | 2017-07-19 | 2019-01-24 | Konzelmann Gmbh | Hydrodynamic bearing |
| US10513928B2 (en) * | 2017-08-31 | 2019-12-24 | Flowserve Management Company | Axial thrust balancing device |
| WO2020038655A1 (en) * | 2018-08-21 | 2020-02-27 | Zf Friedrichshafen Ag | Run-on element for a hydrodynamic axial bearing, and hydrodynamic axial bearing |
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| GB1095999A (en) * | 1964-05-28 | 1967-12-20 | Hawker Siddeley Canada Ltd | Improvements in fluid thrust bearing |
| CN1188192A (en) * | 1996-10-11 | 1998-07-22 | 亚瑞亚·勃朗勃威力有限公司 | Axial sliding bearing |
| EP1199486A1 (en) * | 2000-10-17 | 2002-04-24 | ABB Turbo Systems AG | Hydrodynamic axial bearing with floating disc |
| JP2003222123A (en) * | 2002-01-25 | 2003-08-08 | Mitsubishi Heavy Ind Ltd | Taper land thrust bearing and rotary machine equipped with this bearing |
| JP2010540857A (en) * | 2007-09-26 | 2010-12-24 | アーベーベー ターボ システムズ アクチエンゲゼルシャフト | Fluid type axial bearing |
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| JPS5945850B2 (en) * | 1979-07-13 | 1984-11-09 | 株式会社日立製作所 | thrust bearing |
| JPH0575519U (en) * | 1992-03-16 | 1993-10-15 | 三菱重工業株式会社 | Thrust color of rotating shaft |
| JP3338117B2 (en) * | 1993-04-28 | 2002-10-28 | 日本電産株式会社 | Method of manufacturing spindle motor and bearing parts |
| DE29624507U1 (en) * | 1996-10-11 | 2004-11-25 | Abb Turbo Systems Ag | Axial slide bearing turbocharger shaft in IC engine - has lubrication gap with profiled ring surface rotating with/around shaft, and wedge surfaces defined radially by sealing web |
| JP2003056553A (en) * | 2001-08-10 | 2003-02-26 | Koyo Seiko Co Ltd | Thrust dynamic pressure bearing |
| JP4340855B2 (en) * | 2003-04-22 | 2009-10-07 | 株式会社ジェイテクト | Manufacturing method of dynamic pressure generating groove |
| DE20317497U1 (en) | 2003-07-05 | 2004-03-11 | Man B & W Diesel Ag | Plain thrust bearing for bearings in an exhaust gas turbocharger's rotating shaft linked to a lubricating oil circuit, has a sliding surface and a bearing surface with lubricating gap |
-
2011
- 2011-11-03 DE DE102011085681A patent/DE102011085681A1/en not_active Withdrawn
-
2012
- 2012-11-02 KR KR1020147014511A patent/KR20140083051A/en not_active Application Discontinuation
- 2012-11-02 BR BR112014010582A patent/BR112014010582A2/en not_active IP Right Cessation
- 2012-11-02 SG SG11201401938WA patent/SG11201401938WA/en unknown
- 2012-11-02 EP EP12790812.7A patent/EP2773877A1/en not_active Withdrawn
- 2012-11-02 JP JP2014540406A patent/JP2014533342A/en not_active Withdrawn
- 2012-11-02 WO PCT/EP2012/071729 patent/WO2013064638A1/en active Application Filing
- 2012-11-02 CA CA2852164A patent/CA2852164A1/en not_active Abandoned
- 2012-11-02 CN CN201280054248.5A patent/CN103906936A/en active Pending
-
2014
- 2014-05-02 US US14/268,466 patent/US20140241887A1/en not_active Abandoned
- 2014-12-11 HK HK14112459.3A patent/HK1199084A1/en unknown
Patent Citations (5)
| 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 |
| CN1188192A (en) * | 1996-10-11 | 1998-07-22 | 亚瑞亚·勃朗勃威力有限公司 | Axial sliding bearing |
| EP1199486A1 (en) * | 2000-10-17 | 2002-04-24 | ABB Turbo Systems AG | Hydrodynamic axial bearing with floating disc |
| JP2003222123A (en) * | 2002-01-25 | 2003-08-08 | Mitsubishi Heavy Ind Ltd | Taper land thrust bearing and rotary machine equipped with this bearing |
| JP2010540857A (en) * | 2007-09-26 | 2010-12-24 | アーベーベー ターボ システムズ アクチエンゲゼルシャフト | Fluid type axial bearing |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107407425A (en) * | 2015-04-30 | 2017-11-28 | 斯堪尼亚商用车有限公司 | Sealing device for fluid dynamic machinery |
| CN106438678A (en) * | 2015-08-11 | 2017-02-22 | 西门子医疗有限公司 | Liquid metal plain bearing |
| CN110249144A (en) * | 2017-02-08 | 2019-09-17 | Abb涡轮系统有限公司 | The sliding bearing of axial retention with fluid power |
| CN110249144B (en) * | 2017-02-08 | 2021-03-12 | Abb瑞士股份有限公司 | Sliding bearing with hydraulic axial stop |
| CN114321155A (en) * | 2020-09-30 | 2022-04-12 | 株式会社丰田自动织机 | Fluid machinery |
| CN114321155B (en) * | 2020-09-30 | 2024-02-13 | 株式会社丰田自动织机 | fluid machinery |
Also Published As
| Publication number | Publication date |
|---|---|
| US20140241887A1 (en) | 2014-08-28 |
| BR112014010582A2 (en) | 2017-05-02 |
| DE102011085681A1 (en) | 2013-05-08 |
| SG11201401938WA (en) | 2014-10-30 |
| WO2013064638A1 (en) | 2013-05-10 |
| CA2852164A1 (en) | 2013-05-10 |
| EP2773877A1 (en) | 2014-09-10 |
| KR20140083051A (en) | 2014-07-03 |
| JP2014533342A (en) | 2014-12-11 |
| HK1199084A1 (en) | 2015-06-19 |
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Application publication date: 20140702 |