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
• • 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
  • F16C25/08—Ball or roller bearings self-adjusting
• • 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
  • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
  • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
• • 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
  • F16C33/588—Races of sheet metal
• • 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
  • F16C2361/00—Apparatus or articles in engineering in general
  • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
• • 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
  • F16C2380/00—Electrical apparatus
  • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

Definitions

• Rolling bearing assembly comprising an elastically deformable element and method of manufacturing such a bearing.
• the present invention rel ates to rolling bearings, in particular rolling bearings having an inner ring and an outer ring with one or more rows of rolling elements held by a cage b etween raceways provided in the two rings .
• the rolling elements may, for example, b e ball s .
• the rolling bearings may be, for example, those used in industrial electric motors or in motor vehicle gearboxes.
• a " solid ring” is to be understood as a ring obtained by machining with removal of material (by turning, grinding) from steel tube stock, bar stock, rough forgings and/or rolled blanks .
• the deep groove b all bearings are mainly loaded radially, often with a relatively weak load compared to the capacity of these bearings .
• the service life of the deep groove ball bearings i s essentially related to the lubrication of the bearing because of the low performance of the lubricant compared to the steel of the solid rings.
• Patent US 3 , 876,266 discloses a rolling bearing compri sing an inner ring, an outer ring made in two separate parts or half rings, a housing holding the two separate parts of the outer ring and a row of ball s held by a cage.
• One of the separate parts of the outer ring, together with the housing, defines a closed space inside which an axially preloaded resilient element i s housed.
• Another obj ect of the present invention i s to provide a rolling bearing assembly having good radial stiffness and less sensitive to reduce vibrations inside the rolling bearing assembly .
• a rolling bearing assembly comprises an inner ring, an outer ring, at least one row of rolling elements disposed between raceways provided on the inner and outer rings, and an annular housing inside which at least one of the rings i s arranged.
• Said one ring compri ses two half ring parts having each a radial portion and two axi al cylindrical portions extending from the radial portion towards the outside respectively by a rounded edge portion and by a toroidal portion defining the raceway.
• the rolling bearing assembly compri ses at least one elastically deformable element located between the two half ring parts of said one ring so as to adj ust the axial clearance between said half ring parts .
• Such an elastically deformable element allows ab sorbing the deformation of the half ring parts as well as vibrations in the bearing assembly.
• the elastically deformable element compri ses a flat washer mounted axially between the radial portions of said one ring and radially in contact with an inner bore of the annular housing.
• the flat washer has a parall elepipedic shape in cross-section.
• the el astically deformable element compri ses an annular ring mounted between the rounded edge portions of said one ring.
• Said annular ring has a toroidal shape in cross- section, and is in contact at three contact areas respectively with an inner bore of the annular housing and with the rounded portions of said one ring.
• the annular ring compri ses a circumferential opening.
• the elastically deformable element can be made of a material more flexible than the material of said ring, such as, for example, a metallic material, such as aluminium or a synthetic material, such as polyamide.
• the radial portion of at least one half ring part of said one ring compri ses at least one protruding elastic portion extending towards the adj acent half ring part.
• the protruding elastic portion i s annular.
• the radial portion of at least one half ring part of said one ring compri ses a plurality of individual protruding elastic portions located at a circumferential di stance from each other.
• Each half ring part of said one ring may compri se a plurality of individual protruding elastic portions located at a circumferential di stance of the protruding portions of the adj acent half ring part.
• the protruding elastic portion may compri se a boss or a stamped lug.
• At least one of the two half ring parts of said one ring may define with the annular housing, a closed space inside which a lubricant can be located; the rolling bearing may further compri se passage means for the lubricant to pass from the closed space to the raceways .
• the passage means for the lubricant comprise axial holes provided in the thi ckness of the radial portion of each of the two half ring parts of said one ring.
• the annular housing can compri se two distinct parts for retaining the half ring parts of said one ring.
• the annular housing can compri se one unique part for retaining the two half ring parts of said one ring.
• a rolling bearing assembly designed by general reference number 1 , comprises an inner ring 2, an outer ring 3 , a row of rolling elements 4 consi sting, in the example illustrated, of ball s, held by a cage 5 between the inner ring 2 and the outer ring 3 and an annular housing 6 surrounding the outer ring 3 .
• the inner ring 2 is solid and has on its outer cylindrical surface 2a a toroidal groove 7, the radius of curvature of which i s slightly greater than the radius of the rolling elements 4 and forms a bearing raceway for the rolling elements 4.
• the inner ring 2 may be manufactured by machining or by pressing a steel blank, which i s then ground and optionally lapped at the bearing raceway 7 in order to give the ring 2 its geometrical characteri stics and its final surface finish.
• the cage 5 compri ses a plurality of cavities 8 designed to house the rolling elements 4 and keep them uniformly circumferentially spaced.
• the cavities 8 are advantageously of spherical shape with a diameter slightly greater than that of the rolling elements 4.
• the cavities 8 are provided in the radial thickness of the cage 5 having a radial portion 5 a radially facing the outer ring 3 and extending radially inwards by a conical portion 5b .
• the coni cal portion 5b is located radially facing the inner ring 2 and extend s axially towards the rolling elements 4.
• the radial portion 5 a and the conical portion 5b define the cavities 8.
• the conical portion 5b form s a guide portion for the rolling elements 4.
• the outer ring 3 compri ses two half ring parts 3 a, 3 b .
• the half ring parts 3 a, 3 b are identical and symmetric with respect to the axial plane of symmetry Y 1 of the b earing 1 , in order to reduce manufacturing costs .
• These two outer half ring parts 3 a, 3b may advantageously be manufactured by cutting and stamping a metal sheet, the pi eces obtained being then hardened by heat treatment.
• the bearing races intended for the rolling elements 4 may be ground and/or lapped in order to give them their geometric characteristics and their definitive surface fini sh.
• the half-ring part 3 a of the outer ring 3 compri ses an outer axial cylindrical portion 9a, a radi al portion 1 1 a, a toroidal portion 12a and an inner axial cylindrical portion 13 a.
• the radial portion 1 1 a is connected to the outer axial portion 9a via a rounded edge portion 10a, and to the toroidal portion 12a.
• the toroidal portion 12a defines part of a raceway 14a for the rolling elements 4.
• the radius of curvature of the raceway 14a slightly exceeds the radius of the rolling elements 4.
• the toroidal portion 12a extends axially towards the outside of the rolling bearing assembly 1 with the inner axial portion 13 a.
• the two outer half-ring parts 3 a, 3b are arranged with an axial clearance between the axially internal radial faces 1 5 a, 1 5b of the radi al portions 1 1 a, l i b respectively.
• the housing 6, which i s advantageously made of a stamped metal sheet, compri ses two distinct annular parts 16, 17 surrounding the two outer half-ring parts 3 a, 3 b so as to hold them firmly together in the axial direction.
• the parts 16, 17 of the housing 6 may advantageously be produced in an economical way from a single metal sheet by cutting and pressing.
• Each di stinct part 16, 1 7 have an L-shaped structure.
• the first part 16 compri ses an inner axial cylindrical portion 1 8 for retaining radially said outer rings 3 a, 3 b .
• the inner axi al cylindrical portion 1 8 surrounds the outer rings 3 a, 3 b and i s in contact with the outer surface of the axial portions 9a, 9b of the outer ring parts 3 a, 3 b .
• the first part 16 further compri ses a radial fl ange 19 extending radially from the inner axial cylindrical portion 1 8 towards the immediate vicinity of the outer cylindrical surface 2a of the inner ring 2, so as to leave a clearance between the inner edge 19a of the radi al flange 19 and the cylindrical surface 2a of the inner ring 2.
• the second part 17 of the housing 6 compri ses an outer axial cylindrical portion 20 surrounding the inner axial cylindrical portion 1 8 of the first part 16.
• the second part 17 further compri ses a radial flange 21 extending radially from the outer cylindrical portion 20 towards the immediate vi cinity of the outer cylindrical surface 2a of the inner ring 2, so as to leave a clearance between the inner edge 2 1 a of the radial flange 2 1 and the outer cylindrical surface 2a of the inner ring 2.
• the housing 6 may comprise a single part having an axial cylindri cal portion and two radial flanges extending from the axial cylindrical portion towards the inner ring.
• the half-ring parts 3 a, 3 b are centred in the inner axial portion 1 8 of the part first 16 of the housing 6 by contact between the axial portions 9a, 9b and the inner bore 1 8 a of the said inner axial portion 1 8.
• the outer radial faces 22a, 22b which form the outer edges of the outer axial portions 9a, 9b are respectively in contact with the inner surface 19b, 21 b of the radial flanges 19, 21 of the parts 16, 17 of the housing 6, thus axially clamping the two half-ring parts 3 a, 3 b together.
• the outer radial faces 23 a, 23 b whi ch form the outer edges of the inner axial portions 13 a, 13b are al so in contact with said radial flanges 19, 21 .
• an axial clearance (not shown) may b e provided between the outer edges 23 a, 23 b of the inner axial portions 13 a, 13 b and the radial flanges 19, 21 of the housing 6.
• each of the half-ring parts 3 a, 3 b defines, with the housing 6, an annular clo sed space 24a, 24b . More specifically, the closed space 24a i s delimited by the outer axial portion 9a, the radial portion 1 1 a, the toroidal portion 12a, and the inner axial portion 13 a, and, adj acent to these portions, the radial flange 19 of the first part 16 of the housing 6.
• One of the two or both spaces 24a, 24b may act as a lubricant reservoir, the lubricant contained in these spaces 24a, 24b not being depicted in the figures.
• the lubricant used may be grease or oil .
• Lubricant can be packed into the space 24a which constitutes a first lubricant reservoir between the half-ring part 3 a and the inner ring 2. Lubricant can al so be packed into the second space 24b and into the volume remaining between the inner and outer rings 2, 3 .
• Each half ring part 3 a, 3b of the outer ring 3 compri ses passage means for the lubricant contained in the clo sed spaces 24a, 24b .
• these passage means compri se a plurality of axial through-holes 25a, 25b provided the thickness of the radial portions 11a, lib of the outer half-ring parts 3a, 3b.
• other types of passage means may be used; for example, radial through-holes (not represented) provided in the thickness of the axial portions 13a, 13b, in order to allow the lubricant contained in the closed spaces 24a, 24b to flow by gravity directly towards the rolling elements 4.
• the half ring parts 3a, 3b may be provided with no passage means.
• the outer axial cylindrical portion 20 is fixed to the inner axial cylindrical portion 18 by means of welding, brazing or glue.
• the rolling bearing assembly 1 further comprises an elastically deformable element 30 located between the radial portions 11a, lib of the outer ring 3, in order to adjust the axial clearance between the half ring parts 3a, 3b.
• the elastically deformable element 30 comprises a flat washer mounted axially between the inner radial faces 15a, 15b of the radial portions 11a, lib and radially in contact with the inner bore 18a of the annular housing 6.
• the flat washer 30 has a parallelepipedic shape in cross- section and has an inner diameter substantially smaller than the inner diameter of the rounded edge portions 10a, 10b and an outer diameter substantially similar to the inner diameter of the inner bore 18a of the housing 6.
• the flat washer 30 is made of a material more flexible than the material of the outer ring 3, in order to absorb the deformation of the half ring parts 3a, 3b, as well as vibrations in the bearing 1.
• the washer 30 is made of a metallic material, such as aluminium, or of a synthetic material, such as polyamide.
• the flat washer 30 makes it possible to adjust the axial clearance between the half ring parts 3a, 3b of the outer ring 3.
• the rolling bearing 1 operates thus with an internal preload.
• it is preferred that the rolling bearing has an internal preload, that is to say a preload both in the radial and axial directions.
• such a bearing advantageously supports in rotation the rotor of the vehicle motor in order to prevent any click noise.
• the elastically deformable element 31 comprises an annular ring having a toroidal shape in cross-section and mounted so as to be in contact in three contact zones respectively with the rounded edge portions 10a, 10b of the outer ring 3 and with the inner bore 18a of the housing 6.
• the annular ring 31 is solid; however, the annular ring can be hollowed in order to improve its deformation properties.
• the annular ring 31 may comprises a circumferential opening (not illustrated).
• the annular ring 31 is made of a material more flexible than the material of the outer ring 3.
• the elastically deformable element comprises at least one protruding elastic portion 32, 33 provided on the radial portion 11a, lib of at least one half ring parts 3a, 3b of the outer ring 3.
• the radial portion lib of one of the half ring part 3b comprises a protruding elastic portion 32 extending towards the radial portion 11a of the adjacent half ring part 3a.
• the protruding elastic portion 32 is a boss made by stamping the radial portion lib of the half ring part 3b.
• the radial portion may comprise one unique annular boss 32 or a plurality of individual bosses disposed circumferentially at a circumferential distance from each other.
• the number of bosses can be at least three.
• each half ring part 3a, 3b of the outer ring 3 comprises a plurality of individual protruding portions 32a, 32b, having the shape of bosses.
• the bosses 32a of one half ring part 3a are located at a circumferential distance of the bosses 32b of the adjacent half ring part 3b, so that each boss 32a, 32b contacts the adjacent radial portion 11a, lib respectively.
• each half ring part 3a, 3b of the outer ring 3 comprises passage means for the lubricant contained in the closed spaces 24a, 24b.
• These passage means comprise a plurality of axial through-holes 25a, 25b provided the thickness of the radial portions 11a, lib of the outer half-ring parts 3a, 3b.
• other types of passage means may be used; for example, radial through- holes (not represented) provided in the thickness of the axial portions 13a, 13b, in order to allow the lubricant contained in the closed spaces 24a, 24b to flow by gravity directly towards the rolling elements 4.
• the half ring parts 3a, 3b may be provided with no passage means.
• the radial portion lib of one of the half ring part 3b comprises a protruding elastic portion 33 extending towards the radial portion 11a of the adjacent half ring part 3a.
• the protruding elastic portion 33 is a stamped lug made by stamping or cutting the radial portion lib of the half ring part 3b.
• the radial portion lib may comprise one unique annular stamped lug 33 or a plurality of stamped lug 33 disposed circumferentially at a circumferential distance from each other.
• the embodiment of Figure 6 differs from the embodiment of Figure 5 only in that the radial portion 11a, lib of each half ring part 3a, 3b of the outer ring 3 comprises a plurality of individual protruding portions 33a, 33b, having the shape of stamped lugs.
• the stamped lugs 33a of one half ring part 3a are located at a circumferential distance of the stamped lug 33b of the adjacent half ring part 3b, so that each stamped lug 33a, 33b contacts the adjacent radial portion 11a, lib.
• each half ring part 3a, 3b of the outer ring 3 comprises passage means for the lubricant contained in the closed spaces 24a, 24b.
• These passage means comprise a plurality of axial through-holes 25a, 25b provided the thickness of the radial portions 11a, lib of the outer half-ring parts 3a, 3b.
• other types of passage means may be used; for example, radial through- holes (not represented) provided in the thickness of the axial portions 13a, 13b, in order to allow the lubricant contained in the closed spaces 24a, 24b to flow by gravity directly towards the rolling elements 4.
• the half ring parts 3a, 3b may be provided with no passage means.
• the machining of the radial portions 11a, lib of the outer ring 3, as described according to Figures 3 to 6, is easier if the half ring parts 3a, 3b have a local surface treatment such as quenching, for example on the raceways 14a, 14b of the toroidal portions 12a, 12b.
• One of the half ring parts 3a of the outer ring 3 is inserted in the L-shaped structure of the first part 16 of the housing 6, with the radial faces 22a, 23a of the half ring part 3a resting on the inner surface 19b of the radial flange 19 and the outer surface of the axial portion 9a in contact with the inner bore 18a of the axial cylindrical portion 18 of the first part 16.
• the inner ring 2 is then mounted. Having inserted the rolling elements 4 into the cavities 8 of the cage 5 and having mounted that subassembly on the inner ring 2, the elastically deformable element, such as the flat washer 30 or the annular ring 31, is then positioned in contact with the radial portion 11a of the first half ring part 3a.
• the elastically deformable element such as the flat washer 30 or the annular ring 31
• the second half ring part 3b is positioned around the row of rolling elements 4 in the L-shaped structure 17 with the radial face 15b of the radial portion 11a in contact with the elastically deformable element 30, 31.
• the outer surface of the outer axial portion 9b is in contact with the inner bore 18a of the inner axial cylindrical portion 18.
• the axial clearance between the half ring parts 3a, 3b is then adjusted by measuring the axial clearance between the radial face 23b of one half ring part 3 b and the radial face 2b of the inner ring 2, and by positioning the second half ring part 3b in a final position
• the second part 17 of the housing 6 i s then positioned so that its outer axial cylindrical portion 20 surrounds the inner axial cylindrical portion 1 8 of the first part 16.
• the outer radial faces 22b, 23b of the axial portions 9b, 13 b are in contact with the inner radial face 21 b of the radial flange 21 of the second part 17.
• the second part 17 of the housing 6 i s fitted to retain the half ring parts 3 a, 3 b axially .
• the invention can al so be applied to rolling bearings having a housing surrounding the inner ring.
• it i s the outer ring that is solid while the two half ring parts forming the inner ring are produced by stamping a metal sheet.
• the arrangement i s identical to that of the embodiment of figures 1 to 6, but with the elements inverted.
• the invention can al so be applied to rolling bearings in which the inner ring and the outer ring are both surrounded by an annular housing.
• the two rings have the same structure.
• the inner ring i s surrounded by a first annular housing and the outer ring i s surrounded by a second annular housing.
• the rolling bearing has four closed spaces acting as lubricant reservoirs .
• the rolling bearing assembly according to the invention i s less sensitive to deformation, and therefore has a good radial stiffness. Furthermore, such a rolling bearing assembly all ows the vibrations inside the rolling bearing to be ab sorbed by the elastically deformable element.

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• 2012
  • 2012-01-23 EP EP12701494.2A patent/EP2807385A1/en not_active Withdrawn
  • 2012-01-23 WO PCT/EP2012/050983 patent/WO2013110318A1/en active Application Filing
  • 2012-01-23 KR KR1020147018418A patent/KR20140114820A/ko not_active Application Discontinuation
  • 2012-01-23 JP JP2014552531A patent/JP2015504147A/ja active Pending
  • 2012-01-23 CN CN201280071662.7A patent/CN104204565A/zh active Pending

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