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WO2004079216A1 - Dispositif de roulement - Google Patents

Dispositif de roulement Download PDF

Info

Publication number
WO2004079216A1
WO2004079216A1 PCT/DE2004/000428 DE2004000428W WO2004079216A1 WO 2004079216 A1 WO2004079216 A1 WO 2004079216A1 DE 2004000428 W DE2004000428 W DE 2004000428W WO 2004079216 A1 WO2004079216 A1 WO 2004079216A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
roller bearing
bearing according
rolling
recesses
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/DE2004/000428
Other languages
German (de)
English (en)
Other versions
WO2004079216A8 (fr
Inventor
Achim Wiebelt
Achmed Schulz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Karlsruher Institut fuer Technologie KIT
Original Assignee
Universitaet Karlsruhe
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 Universitaet Karlsruhe filed Critical Universitaet Karlsruhe
Priority to DE112004000011T priority Critical patent/DE112004000011D2/de
Publication of WO2004079216A1 publication Critical patent/WO2004079216A1/fr
Publication of WO2004079216A8 publication Critical patent/WO2004079216A8/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • 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
    • F16C2210/00—Fluids
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/20—Application independent of particular apparatuses related to type of movement
    • F16C2300/22—High-speed rotation
    • 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 present invention relates to what is claimed in the preamble and is therefore concerned with bearings.
  • Bearings serve to reduce the friction between a rotating shaft and a fixed housing or the like.
  • a rotating shaft For this purpose, between the shaft and the solid housing element or the like supporting it, such as balls (ball bearings) or cylinders are arranged, which are rotatable. Since the rotatable bodies rotate at least partially when the shaft rotates, the friction of the shaft when it rotates relative to the housing is reduced.
  • DE 40 37 734 A1 also shows a machine part with a rolling or sliding bearing surface in which a plurality of tiny is formed arbitrarily recesses that have certain statistical properties.
  • DE OS 2162678 discloses a radial or axial roller bearing with rolling elements arranged between two bearing rings or disks, which are guided through fixed or loose ribs in one or both axial directions, with flat spiral grooves or in the contact surfaces of the ribs or the rolling elements the like is provided.
  • WO 94 / 2.4446 shows a self-pumping.
  • Rolling bearings with an inner and an outer ring and a plurality of rolling elements.
  • the inner surface of the outer ring and the outer surface of the inner ring have a channel in the circumferential direction of the bearing and a group of oblique grooves which are cut in the surface of the inner and / or outer ring, so that lubricant from one side of the Rolling bearing can be brought to the other side to lubricate the bearing surface and the rolling elements.
  • US 3 792 911 discloses a radially rotating bearing, in which one of the sections has a specific trough surface.
  • one of the trough rings is equipped with a rim, the front side of which lies in the plane perpendicular to the central axis of the bearing and on which there are spiral grooves.
  • German utility model application 68 10 086 describes a front thrust washer for the journal of the cross member of a universal joint, which is arranged floating between the front side of the journal and the bottom of the associated bearing bush and has lubrication pockets in the end faces thereof. are seen, the face thrust washer made of a heat-stabilized, highly crystalline and heat-resistant plastic into which the lubrication pockets are pressed during manufacture.
  • German Offenlegungsschrift 1 575 500 describes a grease-lubricated thrust bearing consisting of a disk-shaped cage and a number of rolling elements accommodated in pockets of the cage, at least one of the two end faces of the cage being provided with groove-shaped depressions which extend over the whole or approximately the extend the entire radial height of the cage to its outer diameter and are inclined in the direction of rotation of the cage related to the adjacent running disk.
  • US 3 179 478 describes a roller bearing of the form in which a plurality of balls are forced by a cage ring to rotate on a circular path between the inner and the outer tread, the outer ball tread having a groove which corresponds to the shape of the Corresponds to balls and a web is provided on each side of this groove, on which the cage ring slides through hydrodynamic lubrication; the balls are held in spaced apart arrangement by a plurality of ball pockets along the circumference of the ring; it is proposed that the outermost part of the cage be changed by spiral grooves which are directed onto the ball path in the direction of rotation of the cage ring and are dimensioned to produce hydraulic forces which are sufficient to overcome the centrifugal displacement of oil in this bearing, the inner surface of the cage having the largest circumference in the plane of the spherical path and falls to a smaller extent at the end of the cage.
  • the aforementioned arrangements show rolling bearings that are lubricated with oil or the like.
  • Such bearings are known, for example, from DE 29 31 348 C2, which shows a radial cylindrical roller bearing, consisting of a race with radial rims provided at both ends, which with the end faces of cylindrical rollers, which with only a small mutual distance the circumference of the race almost completely fill cooperate in order to guide and extending radially at least bis- to the cylinder, the successive through the lines of contact the cylindrical rollers is, wherein the raceway on the circumferential distributed feed bores for a hydrostatic 'medium are provided, wherein full between the The end faces of all cylindrical rollers and the adjacent ribs are only thin Liquid gaps are present and the feed bores, the number of which corresponds at least to the number of cylindrical rollers, are designed as throttle bores.
  • a multi-row cylindrical roller bearing preferably a support roller, is known, consisting of two concentric races, which have radial, opposing ribs at both axial ends and roll between which cylindrical rollers, each of which has one flange On-board pair has a circumferential groove open to the other board, into which a sealing ring slotted at one circumferential point, which is supported under pretension on the other board, engages with slight play on all sides, one of the races providing a bore for the supply of oil mist in a manner known per se is, wherein at least one of the rims has a plurality of axially extending through openings, at least some of which are closed with removable plugs, the through openings being arranged in the radial region between the raceway of the associated race and the sealing ring.
  • the object of the present invention is to provide something new for commercial use.
  • the present invention thus proposes, in a first basic concept, a rolling bearing with a plurality of rotating rolling elements and a lateral flange for this purpose, in which it is provided that the rolling elements have recesses on the end face of the rolling element.
  • the rims in a fluid cage roller bearing be structured in such a way that the end face of the rolling element does not rest on the entire surface. This can significantly reduce the friction between the ribs and the roller bearing body.
  • the indentation already provides a further design parameter, which makes it possible to better adapt the rolling bearing design to the respective specific applications.
  • the rolling bearing will typically be an air cage. '' act in which air is pressed under the circumference under pressure into the rolling element area between the outer circumference and the shaft.
  • a fluid cage roller bearing is therefore a roller bearing with a fluid cage.
  • an air cage bearing for the purposes of the present invention is also referred to as an air cage roller bearing or fluid cage roller bearing and is also referred to as an aerostatic roller bearing if not air but a different, compressible fluid such as helium or the like is used becomes.
  • special applications in particular may require storage in which neither conventional liquid lubricants nor oxidizable or oxidizing gases are used for storage.
  • the rolling bearing assembly of the present invention will be readily usable in such cases, as will be apparent to those skilled in the art from the entire description.
  • the rolling bearing is typically used for high-speed applications, in particular with rotational speeds of at least 12,000 rpm, preferably above 20,000 rpm. At such speeds of rotation, the friction between the rolling element face and the rims becomes significant and the indentations can contribute to an improvement to a greater extent.
  • the high rotational speeds in connection with compressible fluids in the rolling element area allow this Floating the end faces of the rolling elements on fluid cushions, the cushion-forming fluid being pressed by the rolling element as it moves over the recess into the recess.
  • the rolling element which moves over the recess, thus initially pushes air or another fluid into the recess and then slides on the air compressed in this way.
  • At least six, preferably at least eight, rolling elements are typically provided. These numbers allow a very smooth movement. In a practical embodiment, about ten to fourteen rolling elements are distributed around the circumference.
  • the rolling element dimensions, etc. experience from other bearings with an aerostatic cage can be used.
  • the rolling elements will preferably have two flat end faces, which can in particular be parallel to one another.
  • the term “even” also includes such configurations on which a chamfer and / or crowning is present.
  • Barrel-shaped, frustoconical or conical rolling elements can be used with the invention, if this is desired and appropriate bearing training is provided.
  • the side rims will preferably be profiled with depressions on both rolling element end faces, the recesses preferably being designed such that this is the preferred behavior desired.
  • a recess for example as a circumferential groove, and optionally to make further depressions in this recess
  • the recesses are completely fluidly separated from one another, that is to say fluid from one recess into the next only via one can flow not deepened board area. In this case, the desired reduction in the friction behavior results in a special way.
  • the recess or recess is preferably dimensioned and / or shaped such that it can be covered completely by the individual rolling element or by its end face.
  • the recess can also have an inclination to the shelf level. Is preferred when viewed in the case of asymmetrical depressions in the typical direction of rotation, the rolling element first passes over a further deepened area and then a less deep area of the deepening. Instead of an inclination, a gradation or the like can obviously also be provided. During production, however, there are manufacturing advantages due to a continuous inclination, since the recesses can be provided by spark erosion, for example.
  • the inclination or, in the case of gradation, imaginary inclination will typically be less than 10 ° ' and in particular be in the range between above 0 ° and below 5 °. Inclinations that are too large result in a volume that is too large with reasonable indentation surfaces, which leads to a late onset of the effect, that is to say a reduction only at very high speeds. At too low inclinations in to sensitive ⁇ royal air cushion results. For reasons of disclosure, it should be mentioned that a plateau without inclination can be provided in the depression area. Advantageous precise designs of the inclination, recess shape etc.
  • the recesses will preferably be arranged close to one another, the distance between two recesses in particular being smaller than the diameter of the rolling element end face.
  • the rolling element covers recess on recess practically without interruption.
  • the distance between the recesses is less than the radius of the rolling element. It should be pointed out, however, that recesses that are too narrow can possibly result in the desired effect no longer being able to be achieved in the manner required for a significant improvement in behavior if the recesses are too close to one another.
  • Fig. 1 is a developed sectional view through a
  • FIG. 2 shows a plan view of a section of a flange
  • FIG. 3 shows a plan view of a rolling bearing from above with the ribs partially broken away
  • FIG. 4 shows a perspective view of a rolling bearing of the invention.
  • a rolling bearing 1, generally designated 1 comprises a plurality of rotating rolling elements 2a, two of which, namely rolling elements 2a and 2a2, are shown in FIG. 1, and a lateral flange 3 therefor, the recesses 4 towards the rolling element end face 2b having.
  • the roller bearing 1 is formed as possible from 100 Cr6 roller bearing steel, which is already good Has tribological properties and is cheaper than the materials that can also be used for the purposes of the invention, such as ceramics, etc.
  • the roller bearing 1 is formed as an aerostatic cage known per se, in which, as can be seen in particular in FIG. 3, air flows in from the circumferential side through inlet bores 1 a between roller elements 2 a 1, 2 a 2 lying close to one another, passes between them and near the mounted shaft 5 exits through the spaces 6 between the cylinder bodies and the shaft 5. Pressure chambers 7 are thus formed between the rolling elements in a manner known per se.
  • the rolling elements 2 are cylindrical in the present case, the rollers being slightly spherical and having a small chamfer in order to avoid the occurrence of critical edge stresses in the generally cylindrical rolling element.
  • the chamfer is selected so small that the leakage gap that arises between a rolling element and the outer raceway is at most small, that is to say the aerostatic cage effect is not significantly impaired.
  • FIGS. 3 and 4 a large number of rolling elements, approximately 10 (FIG. 3) and 14 (FIG. 4) respectively, are provided.
  • the rims 3 do not extend exactly to the shaft 5, but leave a free area 8 open to it.
  • the width of the shelves is selected so that more than half of the rolling element end is covered by the shelves 3, as can be seen in particular from FIG. 3.
  • each indentation 4 is things formed inclined with changing height in the running direction.
  • the selected shape is only shown as an example as a semicircle, since such a design can be produced particularly easily. Obviously, other training courses would be feasible without any problems. It can be seen that - as possible, but not absolutely necessary - the indentations in the radial-radial direction extend over more than half of a rolling element end face, as can be seen from the rolling element end face shown in broken lines. In the running direction, each indentation is smaller than the rolling element diameter at the widest point.
  • the recess 4 is inclined, namely at an angle to the general plane of the shelves 3 in a preferred embodiment 5 °. (Fig. 1 is drawn exaggerated.)
  • the bearing is fastened in a suitable manner with the shaft to be supported on a fixed part, such as a machine housing, relative to which the bearing is to be carried out. Then the pressure lines for supplying the aerostatic cage are connected.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

L'invention concerne un roulement à cage fluidique (1) comprenant une pluralité d'éléments de roulement rotatifs (2a) et un rebord latéral (3), lequel comporte des évidements (4) sur la face des éléments de roulement.
PCT/DE2004/000428 2003-03-05 2004-03-04 Dispositif de roulement Ceased WO2004079216A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112004000011T DE112004000011D2 (de) 2003-03-05 2004-03-04 Wälzlageranordnung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10309828.3 2003-03-05
DE10309828A DE10309828A1 (de) 2003-03-05 2003-03-05 Wälzlageranordnung

Publications (2)

Publication Number Publication Date
WO2004079216A1 true WO2004079216A1 (fr) 2004-09-16
WO2004079216A8 WO2004079216A8 (fr) 2005-08-25

Family

ID=32864212

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2004/000428 Ceased WO2004079216A1 (fr) 2003-03-05 2004-03-04 Dispositif de roulement

Country Status (2)

Country Link
DE (2) DE10309828A1 (fr)
WO (1) WO2004079216A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4254702B2 (ja) * 2004-12-03 2009-04-15 トヨタ自動車株式会社 ベアリング、ベアリング機構、およびプランジヤポンプ
DE102006052835A1 (de) * 2006-11-09 2008-05-15 Schaeffler Kg Radiallager
DE102011104261A1 (de) 2011-06-15 2011-12-22 Daimler Ag Wälzlager, Wälzlageranordnung und Verfahren zum Betrieb einer Wälzlageranordnung
DE102015119864B3 (de) 2015-11-17 2017-03-30 Schuler Pressen Gmbh Schwungradlagerung für eine Umformmaschine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3174571A (en) * 1960-06-16 1965-03-23 Hovercraft Dev Ltd Means for supporting loads
US3549222A (en) * 1967-11-29 1970-12-22 Motoren Turbinen Union High speed anti-friction bearing
GB1408159A (en) * 1971-12-17 1975-10-01 Skf Ind Trading & Dev Roller bearings
DE3722408A1 (de) * 1986-07-15 1988-01-28 Rolls Royce Plc Reibungsarmes radialwaelzlager
US6371656B1 (en) * 1997-09-08 2002-04-16 Skf Engineering & Research Centre B.V. Rolling element bearing with improved rolling contact surfaces

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3179478A (en) * 1963-02-11 1965-04-20 Massachusetts Inst Technology Ball bearing and retainer therefor
FR1464889A (fr) * 1965-11-26 1967-01-06 Roulement
DE1575500A1 (de) * 1966-09-16 1970-01-15 Schaeffler Ohg Industriewerk Fettgeschmiertes Axiallager
DE6810086U (de) * 1968-12-05 1969-04-17 Gelenkwellenbau Gmbh Stirnanlaufscheibe eines kreuzgelenkes
CS157741B2 (fr) * 1971-03-03 1974-09-16 Skf Ind Trading & Dev
DE2931348C2 (de) * 1979-08-02 1986-02-13 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Radial-Zylinderrollenlager
DE3223007C2 (de) * 1982-06-19 1987-02-12 INA Wälzlager Schaeffler KG, 8522 Herzogenaurach Mehrreihiges Zylinderrollenlager
US4887914A (en) * 1988-10-26 1989-12-19 Industrial Technology Research Institute Aerostatic bearing with an adjustable stabilizing structure
JP2548811B2 (ja) * 1989-11-30 1996-10-30 エヌティエヌ株式会社 機械部品
WO1994024446A1 (fr) * 1993-04-19 1994-10-27 Chang Chun Du Roulements a rouleaux capables de pomper le lubrifiant
JPH11108065A (ja) * 1997-08-06 1999-04-20 Ntn Corp 針状ころ軸受

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3174571A (en) * 1960-06-16 1965-03-23 Hovercraft Dev Ltd Means for supporting loads
US3549222A (en) * 1967-11-29 1970-12-22 Motoren Turbinen Union High speed anti-friction bearing
GB1408159A (en) * 1971-12-17 1975-10-01 Skf Ind Trading & Dev Roller bearings
DE3722408A1 (de) * 1986-07-15 1988-01-28 Rolls Royce Plc Reibungsarmes radialwaelzlager
US6371656B1 (en) * 1997-09-08 2002-04-16 Skf Engineering & Research Centre B.V. Rolling element bearing with improved rolling contact surfaces

Also Published As

Publication number Publication date
WO2004079216A8 (fr) 2005-08-25
DE112004000011D2 (de) 2005-02-03
DE10309828A1 (de) 2004-09-16

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