• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The roller bearing comprises an inner ring 1, an outer ring 2, at least a row of roller bodies 3 arranged between bearing tracks 6, 15a, 15b provided on the rings, and an annular casing 5 inside which at least one of said rings is arranged, said ring consists of two parts 2a, 2b and wherein each of these two parts together with the housing delimits a closed space 20a, 20b inside which a lubricant 21a, 21b is placed. The roller bearing further comprises a passage for the lubricant so that it can pass from the closed spaces to the bearing tracks. The ratio between the thickness of a guide part 13a, 13b of each of the two parts 2a, 2b delimiting the bearing path and between the outer diameter of the bearing is from 0.7% to 3%, and preferably from 1.1% to 1.9%.
    公开号:SE1351016A1
    申请号:SE1351016
    申请日:2011-03-01
    公开日:2013-08-30
    发明作者:Thierry Adane；Stephane Cordier；Jean-Luc Gardelle
    申请人:Skf Ab；
    IPC主号:
    专利说明:

    1015202530In one embodiment, a roller bearing comprising an inner ring is provided,an outer ring, at least one row of roller bodies arranged between bearing trackswhich are acquired on the rings, and an annular casing inside which at least oneof said rings is arranged, said ring consisting of two parts andeach of these two parts together with the housing delimiting an endspace inside which a lubricant is placed. Furthermore, the roller bearing includespassages for the lubricant so that it can pass from the enclosed spaces tothe bearing tracks. The ratio of the thickness of a guide member to each ofthe two parts of said ring delimiting the bearing path and betweenthe outer diameter of the bearing is from 0.7% to 3%, and preferably from 1.1%to 1.9%.
    In one embodiment, the ratio of the thickness of each is offthe guide members and the diameter of the roller bodies from 5.5% to 22%, andpreferably from 8.5% to 15%.
    Advantageously, the radial parts of the two parts are of saidring in axial contact with each other in a free state of the bearing, and the flexibilityof at least one of said two parts is adapted to, at a predeterminedroller body passage frequency, allow an axial movement of the correspondingradial part towards the outside to leave an axial clearance between the radialthe parts. The predetermined roller body passage frequency may be between:(0.35 x nlR / 60) x Z and (0.45 x nlR / 60) x Z, where nlR corresponds tothe rotational speed of the inner ring in revolutions per minute and Z corresponds to the numberrolling bodies.
    In one embodiment, the passages for the lubricant includethrough holes provided on the radial portion of each of thetwo parts of said ring. Advantageously, the through holes are the smallestpartially facing each other to insert the two enclosed spacescommunication.
    The guide members of each of the two members of said ring may beconnected to the radial part.
    In a preferred embodiment, each of the two parts has saidring a constant thickness.1015202530In one embodiment, the flexural strength of each of the two parts is offsaid ring up to 250 MPa.
    The lubricant may be oil-based grease. Alternatively, the lubricant may beoil contained in porous elements mounted inside the sealed onesthe spaces.
    In one embodiment, each of the two parts comprises said ringan axial part which is connected to the guide parts and which has a radial surfacewhich is spaced from a radial flange of the housing to leave oneaxial clearance that forms the passages for the lubricant. The passages can alsocomprise radial holes provided on the axial portion of each ofthe two parts of said ring.
    In one embodiment, each of the two parts comprises said ringan outer axial part in radial contact with an axial part of the housing, a radial part,the guide parts and an inner axial part, the enclosed space delimited bysaid parts of the ring and a radial flange of the housing.
    In a preferred embodiment, each of the two parts is of saidring made of a punched sheet metal.
    In accordance with another aspect, an electric motor orgenerator comprising at least one roller bearing as described above.
    The present invention and its advantages will still be understoodbetter by studying the detailed description of a specificembodiment, which is to be considered as a non-limiting example and whichillustrated by the accompanying drawings where:Figure 1 is an axial half section of a roller bearing according to an example ofthe invention, andFigure 2 is an axial half section of the roller bearing in Figure 1 in a deformedcondition due to applied radial load androlling body passage frequency_As illustrated in Figure 1, which illustrates an embodiment of aroller bearings according to the invention, said bearing comprises an inner ring 1 and aouter ring 2 consisting of two outer parts or half rings 2a, 2b, a row ofroller bodies 3 which in the illustrated example consist of balls, and abearing holder 4 for holding said roller bodies and which is acquired between1015202530the inner ring 1 and the outer ring 2. The roller bearing also comprises an annularenclosing ring or housing 5 enclosing the two outer half-rings 2a, 2b.
    In this example, the inner ring 1 is designed to be mounted on onerotating part. It thus forms the rotating ring of the bearing while the outer ring 2constitutes the non-rotating ring. the inner ring is massive and has a toroidalgroove 6 provided on its outer cylindrical surface 1a and forming onebearing track for the roller bodies 3. The radius of curvature of the groove 6 is slightly largerthe radius of the roller bodies. the inner ring 1 can be manufactured bymachining or by punching a steel blank which is then groundand optionally polished at the bearing path to give the ring 1 its geometricproperties and its final surface treatment.
    The bearing holder 4 comprises a plurality of open cavities 7 which are limitedof external locking claws 8. The cavities 7 are advantageously spherical with adiameter which is slightly larger than that of the roller bodies 3 so that they can takereceive and keep the latter. The cavities 7 are formed along itthe circumference of the annular bearing holder body 4 with a lug 9 left in the middleagainst the openings to the cavities 7. These openings as in each caselimited by two opposing claws 8 has a width slightly less thanthe diameter of the roller bodies 3. The roller bodies 3 are snapped byresiliently move the claws 8. Alternatively, the bearing holder may have other means thancavities 7 and claws 8 to hold the roller bodies. Stock holder 4 canbe made of molded plastic or metal.
    In this embodiment, the two parts 2a and 2b of the outer ring 2identical and symmetrical with respect to the radial plane of symmetry of the bearing forto reduce manufacturing costs. Alternatively, it is also possible to havenon-symmetrical parts 2a, 2b. These two outer half-rings 2a, 2b canadvantageously be made by cutting and punching a sheet metal,wherein the two parts obtained are then cured by heat treatment.
    Each of the two half-rings 2a, 2b has a constant thickness. The bearing trackscan then be ground and / or polished to give them their geometricproperties and their final surface treatment. Since the two half-rings 2a,2b are identical in this example, only one of them, with reference "a",1015202530to be described herein, it being understood that the identical elements ofthe second half ring 2b has referenceThe half ring 2a of the outer ring 2 comprises an outer cylindrical axial part11a, an annular radial portion 12a, a toroidal portion 13a and an inner cylindrical portionaxial part 14a. The radial part 12a is connected to the outer axialpart 11a and with the toroidal part 13a. The toroidal part 13adelimits a toroidal bearing path 15a for the roller bodies 3. The radius of curvature ofthe bearing race 15a is slightly larger than the radius of the roller bodies 3. The toroidalthe part 13a is also connected to the inner axial part 14a. The toroidalthe part 13a extends axially towards the outside of the roller bearing with the inner axial part14a. The two outer half-rings 2a, 2b are located with the radial surfaces 16a,16b of the radial parts 12a, 12b in axial contact with each other, approximately inthe radial plane of symmetry of the roller bearing and the roller bodies 3.
    The housing 5, which is advantageously made of a punched metal plate, comprisestwo radial axes 17a, 17b and an outer axial portion 17c which is assembledwith the two radial flanges 17a, 17b in such a way that they enclose the twothe half-rings 2a, 2b and hold them against each other in an axial direction.
    The half rings 2a, 2b are centered in the axial part 17 of the housing 5 throughradial contact between the two axial parts 11a, 11b and the hole in the axialsection 17c. The outer radial surfaces 18a, 18b which form the annular onesthe edges of the two outer axial parts 11a, 11b are in contact with themthe respective radial flanges 17a, 17b of the housing 5. The two radial flanges17a, 17b extend radially inwardly towards the outer cylindrical surface 1a ofinner ring 1. The inner edges 19a, 19b leave a radial clearance withwith respect to said cylindrical surface 1a. The outer radial surface of eachthe flange 17a, 17b lies in a radial plane containing a radial surface ofinner ring 1.
    Each of the outer half-rings 2a, 2b defines, together withthe housing 5, an annular closed space 20a, 20b which functions as onelubrication reservoir, the lubricant 21a, 21b contained thereinspaces 20a, 20b are shown schematically. More specifically, the closed is delimitedthe space 20a of the outer axial part 11a, the radial part 12a, the1015202530the toroidal part 13a and the inner axial part 14a, and opposite these parts,a portion of the radial flange 17a of the housing.
    Passages can be obtained to allow the lubricant to pass from the closed onesthe spaces 20a, 20b to the bearing tracks 6 and 15a, 15b. These passages are offabout four types. There is an axial clearance 22a and 22b, respectively, between the interiorthe surface of the radial axis 17a and 17b, respectively, and the outer radial surface23a and 23b, respectively, which form an annular edge of the inner axial part14a and 14b, respectively. These clearances 22a, 22b allow the lubricant, which isenclosed in the annular reservoirs 20a, 20b, to leak against or reachto the roller bodies 3. It is possible to replace the clearances 22a, 22b with onemultiple radial grooves or grooves defined between protrusions that areacquired on surfaces 23a, 23b.
    Other passages for the delivery of the lubricant 21 a, 21 b consist, in itillustrated the example, of a plurality of radial through communication holes24a, 24b, which are made in the same thickness as the inner axial part 14a,14b, which allows the lubricant 21a, 21b to disperse in the radial spacedefined between the inner ring 1 and the outer ring 2 wherein the roller bodies 3ryms. The lubricant 21a, 21b enclosed in the closed spaces 20a, 20bcan flow against the roller bodies 3 through the axial clearances 22a, 22b and thethrough holes 24a, 24b. Alternatively, or in combination, a pluralitythrough-hole communication holes are provided in the thickness of the toroidalpart 13a, 13b or in the region where the inner axial part 14a, 14b and thethe toroidal part 13a, 13b meet. Such an arrangement allows the lubricant21a, 21b disperse directly on the roller bodies 3 in the bearing tracks 15a, 15b.
    As will be described in more detail later, the passages includefor the lubricant 21a, 21b to pass from the closed spaces 20a, 20b tothe bearing tracks 6 and 15a, 15b also have a plurality of axial through holes 25a,25b which are made in the same thickness as the radial part 12, 12b of thetwo half-rings 2a, 2b and which are at least partially facing each other. Thisarrangement also allows the two enclosed spaces 20a, 20b to communicatetogether. In the illustrated embodiment, the through holes are25a, 25b facing each other.1015202530The various units of the roller bearing are assembled as follows. Thenthe roller bodies have been inserted into the cavities 7 in the bearing holder 4 and the whole hasfitted into the inner ring 1, the two half rings 2a, 2b are placed around the row ofroller bodies 3. The lubricant 21a is provided inside the space 20a which constitutes itthe first lubrication reservoir between the half ring 2b and the housing 5. The lubricant21b is also provided within the space 20b which constitutes the otherthe lubrication reservoir and inside the volume remaining between the inner ring 1and the outer ring 2. It should be noted that the lubricant used for fillingthe spaces 20a and 20b may be different from those placed between the inner ring 1and the outer ring 2 in contact with the roller bodies 3.
    At this stage in the assembly process, the housing 5 has an L-shapestructure with an outer cylindrical part forming the axial part 17c which isconnected to a radial part forming one of the radial flanges, toexample flange 17b. The casing thus formed is then fitted over themtwo half rings 2a, 2b. When the two outer half-rings 2a, 2b have been put in placein the L-shaped structure of the housing, the outer cylindrical part of the housing 5 is folded over itside opposite the radial flange 17b to form a second radial flange17a opposite the first and to hold the two half rings 2a, 2b againsteach other by means of their respective outer axial parts 11a, 11b. Whenthe assembly process is completed, delimiting the housing 5 and the two outer onesthe half-rings 2a, 2b annular closed volumes or spaces 20a, 20b asforms lubrication reservoirs.
    In the described embodiment, the lubricant 21a, 21b is advantageousoil-based grease that is compatible with the lubricant as originallywas placed between the inner ring 1 and the outer ring 2. The lubricant can passthrough different passages towards the inner part of the roller bearing and the roller bodies 3.
    This passage arises from the axial clearances 22a, 22b and from themthrough holes 24a, 24b. The viscosity of the lubricant 21a, 21b can be easilyadapted depending on conditions such as the lubricant being able to passthrough the above passages at the normal operating temperature.
    Preferably, the inner sides of the spaces 20a, 20b have an oleophobiccoating that prevents the lubricant from adhering to the interior walls andthereby promoting its movement.1015202530According to an analysis made by the applicant, it turned out that a goodlubrication of the roller bodies 3 is obtained at a ratio between the thickness ofeach of the toroidal portions 13a, 13b of the two outer half-rings 2a, 2band the outer diameter of the housing 5 from 0.7% to 3%, and preferably from1.1% to 1.9%.
    The applicant has found that, within such a range, leadsthe circulation of the roller bodies 3 in the bearing tracks 15a, 15 of the toroidal parts13a, 13b to vibrations of said parts which are adapted to increasethe oil bleeding phenomenon of the fat enclosed in the closed spaces 20a,20b. The oil flow passing through the axial clearances 22a, 22b and thethrough holes 24a, 24b increase and thus allow satisfactorylubrication of the roller bodies 3. The rotational speed considered for thisoil bleeding phenomenon is up to 650,000 n x dm, where n corresponds tothe rotational speed in speed per minute (rpm) and dm = 0.5 (d + D) where dcorresponds to the diameter of the hole in the inner ring in mm and D corresponds to the diameterat the outer surface of the outer ring in mm. As previously mentioned, they have twothe half-rings 2a, 2b a constant thickness. The ratio of the thicknesses ofthe half rings 2a, 2b and the outer diameter of the roller bearing are from 0.7% to 3%, andpreferably from 1.1% to 1.9%. The ratio of the thickness of eachof the guide parts 13a, 13b and the diameter of the roller bodies 3 is from 5.5% to22%, and preferably from 8.5% to 15%. For example, the thickness ofthe half-rings 2a, 2b lie between 1.48 mm and 2.6 mm, and preferably aroundabout 2 mm, for a roller bearing with a housing that has an outer diameter of 130 mmand roller bodies 3 with a diameter of 17,462 mm.
    When the rolling stock crossing frequency is between (0.35 x nlR / 60) x Z and(0.45 x nlR / 60) x Z, where nlR corresponds to the rotational speed of the inner ring inspeed per minute (rpm) and Z corresponds to the number of rollers, thispassage frequency leads to vibrations of the outer half-rings 2a and 2b,and in the design of said half-rings and the above-mentioned ratiobetween the thickness of the rings and the outer diameter of the bearing, allowsthe flexibility of each of the half-rings 2a, 2b slightly radial for fl expansionsof each of the toroidal portions 13a, 13b toward the axial portions 11a, 11b,i.e. towards the outside. With such deformations of the outer half-rings 2a,10152025302b there are also slightly axial displacements of the radial parts 12a, 12btowards the outside and leaves an axial clearance 26 between the radial surfaces 16a, 16bof said radial parts as shown in Figure 2. The axial parts 11a, 11bis also slightly deformed radially inwards. In Figure 2, the deformations of thethe outer half-rings 2a, 2b have been enlarged for the sake of the drawing.
    The volume of each of the closed spaces 20a, 20b is reduced,which increases the fate of lubricants 21a, 21b passing through the axialthe clearances 22a, 22b and the through holes 24a, 24b. In suchdeformed condition of the outer half-rings 2a and 2b, they soundthrough the holes 25a, 25b in addition the lubricant 21a, 21b to passfrom the closed spaces 20a, 20b to the axial clearance 26 between themradial parts 12a, 12b for guiding the lubricant directly on the roller bodies 3 inbearing tracks 15a, 15b. In the deformed state of the outer half-ringsthus forming the through holes 25a, 25b and the axial clearance 26passages for the lubricant so that it can pass from the enclosed spaces20a, 20b towards the bearing tracks 15a, 15b. If the radial load asplaced on the roller bearing increases, allowing the flexibility of each of the half-rings 2a, 2ba higher flow of lubricant to pass through the axial clearances 22,22b, the through holes 24a, 24b, 25a, 25b and the axial clearance 26,which reduces the temperature of the roller bearing and contributes to a longer service life.
    The flexural strength of each of the two half-rings 2a, 2b can be up to250 MPa. The elongation strength of each of the two half rings 2a, 2b is up to0.01% of the deformation before plastic deformation.
    In the embodiment shown, the closed spaces 20a, 20b are filledwith grease and / or oil as previously described. Alternatively, they could goto provide the two enclosed spaces with a cellular or porous annular unitwhich is saturated with oil. The cellular or porous annular unitsacts as sponges and can release under the influence of vibrationslubricating oil which then, as before, passes through passages as abovedescribed. The cellular or porous annular units can take up all of themenclosed spaces 21a, 21b or only parts thereof.
    In the embodiment shown, the outer ring 2 comprises two half rings 2a,2b and the inner ring 1 are of the solid type. Alternatively, the outer ring would10152010could be massive and the inner ring could consist of two half rings in stylewith the half-rings 2a, 2b in the embodiments shown. The two half ringsof the inner ring would then be mounted on the inside of the housing. The event isidentical to that in the illustrated embodiment, but with the unitsinverted.
    In such a case, it is advantageous that the inner ring formed by twohalf rings are the rotating ring in the roller bearing during operation. This depends, in thiscase, that the lubricant in the two spaces in the half-rings is exposedcentrifugal forces when the roller bearing rotates and that it tends to diffusethrough passages towards the roller bearing bearings.
    In another embodiment it may also be possible to have a roller bearing inwhich the inner ring and the outer ring each comprise two half rings which areenclosed in a housing as previously described. In such an embodiment,the roller bearing four enclosed spaces that act as lubrication reservoirs.Although the present invention has been illustrated on the basis of oneroller bearings with a single row of balls, it is understood that the invention alsocan be applied to bearings with several rows of roller bodies without the needundergo some major modifications. The invention can also be applied todifferent types of ball bearings, such as angular contact ball bearings or pendulum bearings.
    权利要求:
    Claims (15)
    [1]
    Roller bearings comprising an inner ring (1), an outer ring (2), at least one row of roller bodies (3) arranged between bearing tracks (6, 15a, 15b) provided on the rings, and an annular height (5) inside which at least one of said rings is arranged, said ring consisting of two parts (2a, 2b) and each of these two parts together with the housing delimiting a closed space (20a, 20b) inside which a lubricant (21a, 21b) is positioned, the roller bearing further comprising a passage for the lubricant so that it can pass from the closed spaces to the bearing tracks, characterized in that the ratio of the thickness of a guide part (13a, 13b) of each of the two parts (2a, 2b) of said ring which delimits the bearing path (15a, 15b) and between the outer diameter of the bearing is from 0.7% to 3%, and preferably from 1.1% to 1.9%.
    [2]
    Roller bearing according to claim 1, wherein the ratio between the thickness of each of the guide parts (13a, 13b) and the diameter of the roller bodies (3) is from 5.5% to 22%, and preferably from 8.5% to 15%.
    [3]
    Roller bearings according to claim 1 or 2, wherein radial parts (12a, 12b) of the two parts (2a, 2b) of said ring are in axial contact with each other in a free state of the bearing, wherein the flexibility of at least one of said two parts is adapted to, at a predetermined roller body passage speed, allow an axial movement of the corresponding radial part towards the outside to leave an axial clearance between the radial parts (12a, 12b).
    [4]
    The roller bearing according to claim 3, wherein the predetermined roller body passage frequency is between: (0.35 X nlR / 60) x Z and (0.45 x nlR / 60) x Z, where nlR corresponds to the rotational speed of the inner ring in revolutions per minute and Z corresponds to the number of roller bodies. 10 15 20 25 30 12
    [5]
    Roller bearings according to claim 3 or 4, wherein the passage for the lubricant comprises through holes (25a, 25b) provided on the radial part (12a, 12b) of each of the two parts (2a, 2b) of said ring.
    [6]
    Roller bearings according to claim 5, wherein the through holes (25a, 25b) are at least partially facing each other to put the two closed spaces (20a, 20b) in communication.
    [7]
    Roller bearings according to any one of the preceding claims 3 to 6, wherein the guide parts (13a, 13b) of each of the two parts (2a, 2b) of said ring are connected to the radial part (12a, 12b).
    [8]
    Roller bearing according to any one of the preceding claims, wherein each of the two parts (2a, 2b) of said ring has a constant thickness.
    [9]
    Roller bearing according to any one of the preceding claims, wherein the flexural strength of each of the two parts (2a, 2b) of said ring is up to 250 MPa.
    [10]
    Roller bearing according to one of the preceding claims, wherein the lubricant (21a, 21b) is oil-based grease.
    [11]
    Roller bearing according to any one of the preceding claims 1 to 9, wherein the lubricant (21a, 21b) is oil enclosed in porous elements mounted inside the closed spaces (20a, 20b).
    [12]
    Roller bearing according to any one of the preceding claims, wherein each of the two parts (2a, 2b) of said ring comprises an axial part (14a, 14b) which is connected to the guide parts (13a, 13b) and which has a radial surface (23a , 23b) which is spaced from a radial flange (17a, 17b) of the housing so as to leave an axial clearance (22a, 22b) forming the passage of the lubricant. 10 13
    [13]
    Roller bearings according to claim 12, wherein the passage also comprises radial holes (24a, 24b) provided on the axial part (14a, 14b) of each of the two parts (2a, 2b) of said ring.
    [14]
    A roller bearing according to any one of the preceding claims, wherein each of the two parts of said ring comprises an outer axial part (11a, 11b) in radial contact with an axial part (17c) of the housing, a radial part (12a, 12b), the guide members (13a, 13b) and an inner axial portion (14a, 14b), the closed space (20a, 20b) defined by said portions of the ring and by a radial flange (17a, 17b) of the housing.
    [15]
    An electric motor or generator comprising at least one roller bearing according to any one of the preceding claims.
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    同族专利:
    公开号 | 公开日
    CN103380306A|2013-10-30|
    DE112011104991T5|2014-01-16|
    WO2012116735A1|2012-09-07|
    JP2014506984A|2014-03-20|
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    法律状态:
    2015-09-22| NAV| Patent application has lapsed|
    优先权:
    申请号 | 申请日 | 专利标题
    PCT/EP2011/053029|WO2012116735A1|2011-03-01|2011-03-01|Rolling bearing having internal lubrication.|
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