WO2011061570A1 - Palier à roulement et procédé pour monter un tel palier à roulement - Google Patents

Palier à roulement et procédé pour monter un tel palier à roulement Download PDF

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Publication number
WO2011061570A1
WO2011061570A1 PCT/IB2009/056010 IB2009056010W WO2011061570A1 WO 2011061570 A1 WO2011061570 A1 WO 2011061570A1 IB 2009056010 W IB2009056010 W IB 2009056010W WO 2011061570 A1 WO2011061570 A1 WO 2011061570A1
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WO
WIPO (PCT)
Prior art keywords
groove
rolling bearing
engraved
rolling
ring
Prior art date
Application number
PCT/IB2009/056010
Other languages
English (en)
Inventor
Laurent Varnoux
Joël GERBAUD
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Priority to PCT/IB2009/056010 priority Critical patent/WO2011061570A1/fr
Publication of WO2011061570A1 publication Critical patent/WO2011061570A1/fr

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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
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller 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
    • 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
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/664—Retaining the liquid in or near the bearing
    • F16C33/6651—Retaining the liquid in or near the bearing in recesses or cavities provided in retainers, races or rolling elements
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/42—Groove sizes
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/60—Thickness, e.g. thickness of coatings

Definitions

  • the present invention relates to a preloadable rolling bearing comprising at least two rings, each ring having a raceway, and rolling elements which are interposed between the rings and which travel along both raceways. Besides, the present invention relates to a method for preloading such a rolling bearing upon its installation within a mechanical system, like a rolling bearing assembly.
  • a rolling bearing be in a condition such that a preloading, that is to say a negative clearance, always exists inside the bearing during its operation.
  • a preloading that is to say a negative clearance
  • Such a requirement exists for instance in a rolling bearing of the radial kind, when axial forces are applied onto the rolling bearing alternatively in one direction or in the opposite direction.
  • an axial clearance exists inside the rolling bearing, so that the rolling elements can have small axial displacements back and forth between the rings, thus generating a click noise and vibrations which can alter the lifespan of the rolling bearing.
  • a solution consists of using an already preloaded rolling bearing, that is to say a bearing which has been manufactured in such a way as to create an internal preloading during its manufacturing operation. It is however expensive and complex to manufacture such a rolling bearing.
  • US-B-6 682 226 describes a rolling bearing equipped with cylindrical rollers and with a preloading mechanism allowing an elastic deformation of one ring along a radial direction.
  • the rolling bearing of US-B-6 682 226 decreases or eliminates the radial clearance between the inner ring and the outer ring.
  • One object of the present invention is to overcome the aforementioned drawbacks, by providing a rolling bearing which has an increased limit of tolerance to axial clearance and which particularly permits modification of the internal clearance, either positive or negative, inside the rolling bearing in its assembled state.
  • a subject matter of the present invention is a rolling bearing comprising an inner ring, an outer ring and rolling elements arranged between the inner ring and the outer ring so as to rotate around a rotation axis, wherein at least one of the inner ring and the outer ring is engraved with at least one groove, the or each groove being of a substantially annular shape, the or each groove being empty, the or each groove being arranged to allow an elastic deformation of the or each engraved ring upon application on the or each engraved ring of a preloading force along a direction parallel to the rotation axis so as to reduce a clearance, either positive or negative, inside the rolling bearing.
  • such a rolling bearing has at least one ring which can be slightly bent and compressed around the or each groove, in order to modify the clearance inside the bearing.
  • At least one groove is engraved on a rolling surface delimiting at least one raceway for the rolling elements, the rolling surface belonging to the surface oriented towards the rolling elements;
  • At least one of the inner ring and the outer ring is engraved with at least two grooves, at least one groove being located on the surface oriented towards the rolling elements and at least one groove being located on the surface oriented opposite the rolling elements;
  • At least one groove has a substantially U-shaped cross section, considered in a plane comprising the rotation axis;
  • At least one groove has a cross section, considered in a plane comprising the rotation axis, substantially in the shape of a trapezoid, preferably of an isosceles trapezoid, the sides of the trapezoid diverging towards the open end of the groove;
  • the or each groove has a radial depth representing between 20% and 80%, and preferably between 40% and 60%, of the radial height of the corresponding engraved ring;
  • the or each groove has an axial width representing between 1 % and
  • the rolling elements are balls
  • every rolling element has two points of contact respectively with the raceway of the inner ring and with the raceway of the outer ring, when considered in a plane comprising the rotation axis;
  • the rolling bearing comprises two rows of rolling elements.
  • another object of the present invention is to provide a method for mounting a rolling bearing as here-above described, so as to preload the rolling bearing in order to compensate for axial clearance.
  • a subject matter of the present invention is a method for mounting a rolling bearing as here-above described in a rolling bearing assembly, wherein the method comprises the steps of:
  • the axial force is appl ied until a predetermined axial preloading of the rolling bearing is obtained.
  • FIG. 1 is a cross section of a rolling bearing according to a first embodiment of the present invention, considered in a plane comprising the rotation axis;
  • FIG. 2 is a view, at a larger scale, of detail II on figure 1 ;
  • FIG. 3 is a view similar to figure 2 of a rolling bearing assembly according to the present invention and comprising the rolling bearing of figure 2;
  • FIG. 4 is a view similar to figure 2 of the rolling bearing according to a second embodiment of the present invention.
  • FIG. 5 is a view similar to figure 2 of the rolling bearing according to a third embodiment of the present invention.
  • FIG. 6 is a view similar to figure 2 of the rolling bearing according to a fourth embodiment of the present invention.
  • Figure 1 and figure 2 depict a ball bearing 100 which forms a rolling bearing and which comprises an inner ring 1 10, an outer ring 130 and balls 150 as rolling elements.
  • Balls 150 are arranged between inner ring 1 10 and outer ring 130 so as to rotate around a rotation axis X-X'. Balls 150 are held apart from one another by a cage 151 . Every ball 150 forms a rolling element which comprises only one spherical surface. Indeed, every ball 150 is in the shape of a sphere.
  • Inner ring 1 10 has an internal surface 121 , an external surface 122 and two lateral surfaces 123 and 124.
  • Internal surface 121 is oriented towards balls 150.
  • Internal surface 121 comprises a rolling surface 125 which delimits at least one raceway for the balls 150.
  • External surface 122 is oriented opposite balls 150. Both internal surface 121 and external surface 122 extend between the two lateral surfaces 123 and 124, along an axial direction.
  • outer ring 130 has an internal surface 141 , an external surface 142 and two lateral surfaces 143 and 144.
  • Internal surface 141 is oriented towards balls 150.
  • Internal surface 141 comprises a rolling surface 145 which delimits at least one raceway for the balls 150.
  • External surface 142 is oriented opposite balls 150. Both internal surface 141 and external surface 142 extend between the two lateral surfaces 143 and 144, along an axial direction.
  • Inner ring 1 10 is engraved with a groove 1 1 1 .
  • Groove 1 1 1 is arranged to allow an elastic deformation of the inner ring 1 10 along an axial direction upon application on the inner ring 1 10 of a preloading force along axis X-X' so as to reduce a clearance, either positive or negative, inside rolling bearing 100.
  • Groove 1 1 1 has an annular shape.
  • Groove 1 1 1 extends all around the rotation axis X-X'.
  • Groove 1 1 1 1 is engraved on the internal surface 121 . Such a position of groove 1 1 1 allows an axial elastic deformation of the region of inner ring 1 10 which is located farthest from the rotation axis X-X'.
  • the word “engraved” means that the groove forms a recess or a cavity into a surface of the inner ring or of the outer ring and that the groove emerges at this surface, i.e. opens to the outside.
  • the world “engraved” shall not be construed as directed to a particular manufacturing process, because the groove can be made by any suitable manufacturing process, for instance by turning, by milling, by electro-erosion or even by molding.
  • the word “engraved” solely refers to the recess form of the groove.
  • Groove 1 1 1 is empty, which means that it is not filled with any stiff, solid material which could hinder the axial elastic deformation of the engraved ring.
  • groove 1 1 1 does not contain any material.
  • the word "empty" also means that the groove can be filled with a resilient material, such that the groove can be compressed to allow an axial elastic deformation of the engraved ring.
  • the adjective “axial” refers to a direction which is parallel to the rotation axis X-X'.
  • the adjective “radial” refers to a direction which is second and perpendicular to the rotation axis ⁇ - ⁇ ', like axis Y-Y' on figure 2.
  • a surface is said to be “axial” or “radial” by reference to the direction which is locally or globally perpendicular to that surface.
  • groove 1 1 1 is engraved on a rolling surface 125 which delimits at least one raceway for balls 150.
  • Rolling surface 1 25 belongs to the internal surface 121 .
  • Groove 1 1 1 extends symmetrically with respect to a median plane P of the balls 150.
  • Median plane P corresponds to the equatorial plane of inner ring 1 10 and outer ring 1 30.
  • groove 1 1 1 extends about the mid-l ine between lateral surfaces 123 and 124.
  • Such a position of groove 1 1 1 provides a symmetrical elastic deformation of the two halves of inner ring 1 10 located on both sides of groove 1 1 1 or of median plane P.
  • Groove 1 1 1 has a substantially U-shaped cross section when considered in a plane comprising the rotation axis, like the plane of figure 2.
  • groove 1 1 1 is substantially in the shape of a flat annulus.
  • Such a shape of groove 1 1 1 is relatively easy to produce by a suitable manufacturing process. .
  • Groove 1 1 1 has a radial depth D1 1 1 representing approximately 40% of the radial height H 1 1 0 of inner ring 1 10.
  • the radial depth D1 1 1 and the radial height H 1 1 0 are measured along a radial direction, like axis Y-Y' .
  • Such a percentage of radial depth D1 1 1 over radial height H1 10 allows a determined elastic deformation of inner ring 1 10 upon application of a force along axis X-X'.
  • This elastic deformation is also determined by the material constituting inner ring
  • Inner ring 1 10 can for instance be made of 100Cr6.
  • Groove 1 1 1 has an axial width W1 1 1 which represents 5% of the axial width W1 10 of inner ring 1 10.
  • Axial width 1 10 and axial width 1 1 1 are measured along an axial direction, for instance along axis X-X'.
  • Such an axial width W1 1 1 of groove 1 1 1 allows a determined elastic deformation of inner ring 1 10 along an axial direction.
  • Ball bearing 100 is a so called "four points of contact" ball bearing. Indeed, every ball 150 has two points of contact with the raceway 125 of inner ring 1 10 pl us two points of contact with the raceway 1 45 of outer ring 130, when considered in a plane comprising the rotation axis X-X', like the plane of figure 2. When balls 150 rotate around rotation axis X-X', the contact between balls 150 and raceways 125 and 145 take place along four circles to which belong the four points of contact.
  • Ball bearings having four points of contact are designed to bear loads having both an axial component and a rad ial component.
  • rol l ing su rfaces 125 and 145 are respectively defined by the junction of two truncated tori at the middle of the inner ring 1 10 and of the outer ring 130. The not-shown centers of these tori are located on the rotation axis X-X'. The centers of these tori are offset from one another.
  • Rolling surface 125 or 145 is a concave surface.
  • Figure 3 illustrates a rolling bearing assembly 1 comprising the rolling bearing 100, a shaft 160 and a nut 170.
  • Shaft 160 defines a receiving surface 161 having a cylindrical shape in order to receive the external surface 122 of inner ring 1 10. Receiving surface 161 and external surface 122 approximately have the same diameter.
  • Shaft 160 has a thread 162 onto which nut 170 can be screwed.
  • Shaft 160 also has a shoulder 162 extending radially in front of a portion of lateral surface 123.
  • a counterbore or recess 165 extends radially on the annular internal surface of shoulder 162.
  • Recess 165 extends from the receiving surface 161 towards outer ring 130 but only partially along shoulder 162.
  • the radial end of shoulder 162 defines an axially protruding surface 163 which is intended to bear against lateral surface 123 of inner ring 1 10.
  • nut 170 has a recess 175 similar and symmetric to recess 165.
  • the radial end of nut 170 defines an axially protruding surface 174 which is intended to bear against lateral surface 124 of inner ring 1 10.
  • the positions and dimensions of axially protruding surfaces 163 and 174 are selected so as to permit an elastic deformation of inner ring 1 10.
  • this elastic deformation is an elastic bending.
  • the distance DF separating the bottom of groove 1 1 1 from the application radius of forces F1 60 and F1 70 is greater than the height D1 1 1 of groove 1 1 1 . The greater the distance DF is, the larger the bending will be.
  • a method accord ing to th e present invention for mounting rolling bearing 100 according to the present invention in rolling bearing assembly 1 , comprises the steps of:
  • rolling bearing 1 00 which initially copes with an axial positive clearance, is mounted onto shaft 160 until inner ring 1 10 abuts shoulder 162 on shaft 160.
  • Nut 1 70 is then screwed on thread 1 62.
  • inner ring 1 10 is under compression and axial resultant forces F160 and F170 are generated .
  • inner ring 1 1 0 bends around groove 1 1 1 with lateral surfaces 123 and 124 moving towards outer ring 130.
  • the axial clearance inside rolling bearing 100 is reduced and eventually becomes null. Moreover, axial forces F160 and F170 can be applied until a predetermined axial preloading of rolling bearing 100 is obtained. Thus, upon further tightening, the axial clearance inside rolling bearing 100 becomes negative, i.e. the rolling bearing 100 is preloaded. For instance, a preload, or initial deformation, of say 5 microns to 10 microns can be reached for a rolling bearing having an internal clearance of say 20 microns before tightening of the nut.
  • Figure 4 depicts a ball bearing 200 according to a second embodiment of the invention.
  • the description of the ball bearing 100 given above with reference to figures 1 and 2 can be transposed to bal l bearing 200 of figure 4.
  • Ball bearing 200 is similar to ball bearing 100, except for the hereafter stated differences.
  • An element of ball bearing 200 that is identical or corresponding to an element of ball bearing 100 is allocated the same reference sign plus 100.
  • Ball bearing 200 differs from ball bearing 1 00 in that the groove 212 is engraved on the external surface 222 of inner ring 210, i .e. on the surface oriented opposite balls 250. Such a position of groove 212 allows an axial elastic deformation, upon application of an axial preloading force, of the region of inner ring 210 which is located closest to rotation axis X-X'. Upon tightening of not shown nut, an initial positive axial clearance inside rolling bearing 200 can be reduced and eventually made null . Besides, further tightening of this nut shall preload rolling bearing 200, because the axial clearance inside rolling bearing 200 becomes negative.
  • Figure 5 depicts a ball bearing 300 according to a third embodiment of the invention .
  • the description of ball bearing 1 00 given above with reference to figure 2 can be transposed to ball bearing 300.
  • Ball bearing 300 is similar to ball bearing 1 00, except for the hereafter stated differences.
  • An element of ball bearing 300 that is identical or corresponding to an element of ball bearing 100 is allocated with the same reference sign plus 200.
  • Ball bearing 300 differs from ball bearing 1 00 in that the groove 312 is engraved on the external surface 322 of inner ring 310, like groove 212.
  • groove 31 2 has a cross section wh ich is substantially in the shape of a trapezoid, when considered in a plane comprising the rotation axis X- X', like the plane of figure 5. More precisely, groove 312 has a cross section in the shape of an isosceles trapezoid, the sides of which diverge towards external surface 322. Such a shape of groove 312 allows an axial elastic deformation of inner ring 310 which has greater amplitude than the elastic deformation allowed by groove 212.
  • ball bearing 300 differs from ball bearing 100 in that the axial width W31 2 represents approximately 20% of the axial width W310 of inner ring 310. Such a percentage also increases the axial elastic deformation of inner ring 310 as compared to inner ring 1 10.
  • the invention can also apply to a rolling bearing which already has a negative internal clearance before tightening of the nut is already negative, that is to say a bearing which is already in a preloaded condition.
  • the negative clearance will become even smaller, for instance, starting from minus 5 microns, it is possible to reach minus 20 microns of negative clearance of preloading.
  • Figure 6 depicts a ball bearing 400 according to a fourth embodiment of the invention.
  • the description of the ball bearing 100 given above with reference to figures 1 and 2 can be transposed to ball bearing 400.
  • Ball bearing 400 is sim ilar to ball bearing 1 00, except for the hereafter stated d ifferences.
  • An element of ball bearing 400 that is identical or corresponding to an element of ball bearing 100 is allocated the same reference sign plus 100.
  • Ball bearing 400 differs from ball bearing 100 in that the outer ring 430 is engraved with two grooves, i.e. an internal 431 and an external 432.
  • Internal groove 431 is located on the internal surface, i.e. on the surface oriented towards balls 450.
  • External groove 432 is located on the external surface 442, i.e. on the surface opposite balls 450.
  • the location of grooves 431 and 432 on the outer ring 430 allows an elastic deformation of outer ring 430 along an axial direction. This location of grooves 431 and 432 provides an elastic deformation both of the region of outer ring 430 located closest to rotation axis X-X' and of the region of outer ring 430 located farthest from rotation axis X-X'.
  • ball bearing 400 differs from ball bearing 100 in that the sum of radial depth D431 of internal groove 431 plus rad ial depth D432 of external groove 432 represents approximately 55% of rad ial height H430 of outer ring 430.
  • internal groove 431 and external groove 432 allow a higher elastic deformation than the one allowed by groove 1 1 1 or 21 1 .
  • the elastic deformation e.g . the bending
  • the outer ring 130 by way of a tightening applied on a not shown nut, as here-above described in relation with figure 3.
  • - more than two grooves can be engraved on the outer ring or on the inner ring, e.g. three grooves;
  • one groove can be engraved on the inner ring while one groove can be engraved on the outer ring.
  • one groove extends on a part of the perimeter of the engraved ring, either the inner ring or the outer ring. Such a groove does not extend all around the rotation axis.
  • two semi-annular grooves can be engraved on the inner ring or the outer ring, which grooves do not extend all around the rotation axis, but rather extend approximately on two halves of the engraved ring with two bridges of matter disconnecting these two grooves.
  • the present invention has been described in relation with four points of contact ball bearings.
  • the present invention can also be implemented to other kinds of rolling bearings, for instance a deep groove ball bearing (DGBB), a cylindrical ball bearing (CRB) or a tapered roller bearing (TRB),
  • DGBB deep groove ball bearing
  • CB cylindrical ball bearing
  • TRB tapered roller bearing
  • the rolling bearing can comprise two or more rows of rolling elements.
  • the radial depth of a groove can represent between 20% and 80% of the radial height of the corresponding engraved ring.
  • the depth of the groove represents between 40% and 60% of its radial height.
  • the groove can have an axial width representing between 1 % and 20% of the axial width of the corresponding engraved ring.
  • the width of the groove represents between 5% and 10% of the width of the engraved ring.
  • a rolling bearing according to the present invention has an increased limit of tolerance to axial clearance. Furthermore, such a rolling bearing permits modification of the internal clearance, either positive or negative, inside the rolling bearing in its assembled state.
  • the groove when it is engraved on an internal surface, it can serve as a lubricant reservoir storing and releasing lubricant close to the raceways, i.e. the areas of contact between rolling elements and inner ring or outer ring. Thanks to the groove or grooves in the engraved ring or rings, the mass of the rolling bearing is reduced.
  • a mounting method according to the present invention makes it possible to reduce the clearance in a rolling bearing or even to set a preload in a rolling bearing whenever required.

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

Abstract

Le palier à roulement (100) selon l'invention comprend un anneau interne (110), un anneau externe (130) et des éléments de roulement (150) tournant autour d'un axe de rotation (X-X'). Au moins un renfoncement (111) est gravé sur l'anneau interne (110) et/ou l'anneau externe (130). Le renfoncement (111) est essentiellement annulaire et vide. Le ou les renfoncements (111) sont agencés de façon à permettre une déformation élastique du ou des anneaux gravés (110) parallèles à l'axe de rotation (X-X') lors de l'application sur l'anneau ou sur les anneaux (110) d'une force de précharge le long d'une direction parallèle à l'axe de rotation (X-X') de façon à réduire un espace, positif ou négatif, à l'intérieur du palier de roulement (100).
PCT/IB2009/056010 2009-11-18 2009-11-18 Palier à roulement et procédé pour monter un tel palier à roulement WO2011061570A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/IB2009/056010 WO2011061570A1 (fr) 2009-11-18 2009-11-18 Palier à roulement et procédé pour monter un tel palier à roulement

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Application Number Priority Date Filing Date Title
PCT/IB2009/056010 WO2011061570A1 (fr) 2009-11-18 2009-11-18 Palier à roulement et procédé pour monter un tel palier à roulement

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU183720U1 (ru) * 2017-09-12 2018-10-01 Общество с ограниченной ответственностью "Стратегическое бюро" Подшипник шариковый закрытый

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FR1141520A (fr) * 1955-12-26 1957-09-03 Vyzk A Zkusebni Letecky Ustav Roulement à billes
DE1066389B (fr) * 1959-10-01
US3801171A (en) * 1972-06-30 1974-04-02 Heim Universal Corp Preloading anti-friction bearing assembly
AU451806B2 (en) * 1970-09-16 1974-08-02 Low stress ball bearings
DE7333927U (de) * 1976-11-18 Mueller, Paul, 5180 Eschweiler Vierpunktwälzkugelager mit verstellbarer Vorspannung bzw. verstellbarem Spiel
US4707151A (en) * 1986-05-14 1987-11-17 Ina Walzlager Schaeffler Kg Radial rolling bearings
DE3725972A1 (de) * 1987-08-05 1989-02-16 Schaeffler Waelzlager Kg Waelzlager-drehverbindung
EP0769631A1 (fr) * 1995-10-18 1997-04-23 SOCIETE NATIONALE D'ETUDE ET DE CONSTRUCTION DE MOTEURS D'AVIATION -Snecma Roulement avec drainage dynamique alimenté en lubrifiant
US6682226B2 (en) 2002-05-09 2004-01-27 The Timken Company Cylindrical roller bearing with preload capability
EP1803947A1 (fr) * 2005-12-15 2007-07-04 IMO Momentenlager GmbH Palier à roulement sans jeu
DE102006054341A1 (de) * 2006-11-17 2008-05-21 Schaeffler Kg Zweireihiges Schrägkugellager, beispielsweise zur Lagerung einer Spindel einer Werkzeugmaschine

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1066389B (fr) * 1959-10-01
DE7333927U (de) * 1976-11-18 Mueller, Paul, 5180 Eschweiler Vierpunktwälzkugelager mit verstellbarer Vorspannung bzw. verstellbarem Spiel
FR1141520A (fr) * 1955-12-26 1957-09-03 Vyzk A Zkusebni Letecky Ustav Roulement à billes
AU451806B2 (en) * 1970-09-16 1974-08-02 Low stress ball bearings
US3801171A (en) * 1972-06-30 1974-04-02 Heim Universal Corp Preloading anti-friction bearing assembly
US4707151A (en) * 1986-05-14 1987-11-17 Ina Walzlager Schaeffler Kg Radial rolling bearings
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DE102006054341A1 (de) * 2006-11-17 2008-05-21 Schaeffler Kg Zweireihiges Schrägkugellager, beispielsweise zur Lagerung einer Spindel einer Werkzeugmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU183720U1 (ru) * 2017-09-12 2018-10-01 Общество с ограниченной ответственностью "Стратегическое бюро" Подшипник шариковый закрытый

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