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
  • F16C33/46—Cages for rollers or needles
  • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
  • F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
  • F16C33/4629—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from metal, e.g. cast or machined window cages
• • 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
  • F16C33/46—Cages for rollers or needles
  • F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
  • F16C33/4676—Details of individual pockets, e.g. shape or roller retaining means of the stays separating adjacent cage pockets, e.g. guide means for the bearing-surface of 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
  • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
  • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the 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
  • F16C19/22—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

Definitions

• the invention relates to a cage for rolling bearings with rollers, with a first side edge, with a second side edge, with webs and with circumferentially adjacent pockets for rollers, the webs and the side edges being formed in one piece with one another and thereby: the webs between the the first side edge and the second side edge are aligned along the axis of rotation of the cage,
• one of the pockets delimit the circumference, the pockets are each delimited by two inner flanks of the side edges opposite one another along the axis of rotation, the greatest tangential free distance between the flanks opposite one another on the pocket is greater than the largest Diameter of the respective roll in the pocket, on which webs holders for the rolls are formed,
• the greatest tangential free distance between two of the brackets opposite each other on a pocket is smaller than the largest nominal diameter of the respective roller in the pocket
• flanks have a finished profile-milled contour and the finished contour is a negative image of a positive outer cutting contour of at least one form milling cutter.
• Such a cage is described in DE100 21 089 A1.
• the pockets of the cage are machined with form cutters, whose cross-sectional contour on the outside shows a positive profile for a finished negative profile of the respective machined surface inside the pocket.
• the rotationally symmetrical profile milling cutters rotating about a tool axis are first introduced radially into a prepared hole in the cage blank and then moved either in the circumferential direction or tangentially of the cage or axially - in the circumferential direction, around the contour of the flanks later turned towards the pockets Corresponding web and axially to mill the inner flanks on the mostly annular side edges and the corner radii.
• the corners of the pockets are also worked out using one of the form cutters, usually the one for the inner flanks.
• the tangential or circumferential free tangential flank spacing in a pocket between the flanks on the webs facing one another via a pocket is greater than the nominal diameter of the roller in the pocket, plus the permissible plus tolerance of the nominal diameter.
• the roller can be moved tangentially within the pocket and also radially within one play between the two opposing flanks from one flank against the other flank.
• the rollers run in a predetermined manner in the cage on the flanks turned into the pockets.
• a disadvantage of the design of the cage described in DE100 21 089 A1 could be that there is not enough lubricant between the curved cage run-up on the web and between the roller starting there. The friction is then relatively high. This results in inadmissible wear and / or excessive temperatures due to high friction.
• the brackets on the pockets hold the rollers back during transport and handling during assembly.
• At least one holder is formed on each of the webs delimiting the pocket.
• Each of the brackets of a pair of at least two brackets opposite and interacting on the pocket protrude tangentially toward one another from the respective web.
• the rollers are held radially in the cage by means of the holders because the greatest distance between the holders protruding tangentially or circumferentially into the pockets is smaller than the nominal diameter of the rollers, minus the permissible negative deviation of the nominal diameter (permissible minus tolerance for the rollers).
• the object of the invention is therefore to create a cage for rollers with an optimal internal geometry for the start of the rollers and with an optimally suitable arrangement of brackets for snapping the rollers.
• the cage should be inexpensive to manufacture by profile milling (form milling).
• All cages in particular made of steel, non-ferrous or light metals and their alloys, are affected by the invention.
• the finished inner profile of the pockets is produced on the cage, which is formed in one piece from side edges and webs, by profile milling.
• the form milling cutter used for the cage according to the invention for milling the flanks on the webs has, on the outside, a cross-sectional contour which is viewed along the axis of the milling cutter and which is a positive counter-shape for a negative finished contour of the flanks on the webs.
• the negative counter shape on the web is considered in any section planes of the cage that cross the cage transversely to the axis of rotation and penetrate perpendicularly from the axis of rotation.
• the flanks on the webs that are directed into the respective pocket therefore have after at least one flat contact surface facing the pockets for the respective roll in the pocket.
• the mutually facing contact surfaces of a pocket are preferably aligned parallel to one another and thus at the same time parallel to a radial plane starting from the axis of rotation and running in the same direction with it.
• the contact surfaces which are formed on a web and face away from one another and each point into another pocket are thus preferably inclined to one another.
• the flat contact surface adjoins radially at least one of the brackets.
• the holder protrudes at least in the tangential direction beyond the contact surface into the pocket or alternatively above or below the pocket in the direction of the roll.
• Each of the rollers therefore runs against a flat and not a curved contact surface in the pocket.
• the contact surface extends in the radial region of the web at least to such an extent that the partial circle, which is preferably common to all the rollers of the cage, penetrates the contact surfaces in the circumferential direction of the webs located opposite each other on the pockets.
• the pitch circle is a term known to a person skilled in the art of rolling bearing technology and defines a circle running around the axis of rotation of the respective bearing / cage, which intersects the center axes of all rollers of the same diameter when they bear radially against at least one bearing raceway.
• the center axes of the rollers are the axes of rotation of the rotationally symmetrical roller and generally run parallel to the axis of rotation of the cage / bearing.
• each roller is also ensured by the fact that the maximum tangential free distance between the roller in the pocket and between the webs lying on the pitch circle is smaller than any other tangential free distance between radially above and radially below the pitch circle the role and between the webs.
• the supply of lubricant to the contact is further improved if the holder radially adjoining the contact surface has an inclined surface facing into the pocket.
• the distance between the inclined surface and the roller also preferably increases with increasing distance from the smallest distance between the roller and the contact surface defined by the play of movement.
• the inclined surface is inclined at an obtuse angle to the contact surface. Due to the rollers rolling around their central axis, a lubricating wedge is preformed on the inclined surface of the holder and drawn in between the contact surface and the roller by means of the roller.
• the holder has a curved surface that merges into the contact surface.
• the curved surface extends either as a transition surface from an inclined surface facing the pocket as mentioned above out and into the contact surface, or the holder is generally described on the pocket side by such a curved surface that merges into the contact surface.
• the distance between the curved surface and the roller also preferably increases with increasing distance from the smallest distance defined by the play of movement between the roller and the contact surface.
• the curvature of the surface is preferably described in a longitudinal section of the cage along the axis of rotation by a radius. The radius is larger than half the nominal diameter of the roll in the respective pocket.
• Pocket corners are generally understood to mean the right-angled transition of the webs into the side edges. It is known that in stressed cages in the pocket corners with small transition radii from the web to the side edge, peak stresses occur, which can lead to cracks and the destruction of the cages. Therefore, these pocket corner radii should be as large as possible.
• an outlet for the form milling cutters is required in the profile-milled pockets in the corners, as a result of which overlaps between the milling contour of the axially guided and the longitudinally guided form milling cutter are avoided in the corner.
• the contact surface preferably does not run longitudinally over the entire width of the web, but instead, in the same direction as the axis of rotation, from one pocket corner to another pocket corner up to a curved corner surface.
• the pockets are convexly curved at least in places in the web by the corner surfaces.
• the corners are described by a corner surface extending from the contact surface to the inner flanks, the contour of which is preferably predetermined by at least one radius.
• the flat contact surface is arranged radially between two of the holders, the holders projecting beyond the contact surface at least in the tangential direction, so that a pair of outer holders located opposite one another on the pocket radially partially overlap the respective roller in the pocket radially above the central axis engages behind, and in each case another pair of inner holders located opposite one another on the pocket radially engages behind the roller radially below that of the central axis of the roller.
• the aforementioned features of the invention can optionally also be combined with those of the further independent claim, according to which at least some of the webs of the cage have at least one holder of the brackets projecting radially beyond the web from the web.
• the independent claim provides for features that can also be viewed separately from the aforementioned features.
• the weight of the cage is significantly reduced. Furthermore, with the arrangement described below, gap cross-sections of large dimensions can be realized for an improved oil flow in the cage.
• the holder stands radially beyond the side edge and beyond the second side edge, the radial overall height of the side edge and thus its moving weight is less.
• the radial gap between the side of the cage and a rim of a race or a raceway of the rolling bearing is larger.
• the radially directed lateral surfaces on the side edges, on which the holder projects radially beyond the side edges are preferably at the same distance from the axis of rotation.
• the resulting increased gap between the side edge of the cage and a raceway is preferably at least 0.6 to 0.9 times the nominal diameter of the roller, as a result of which the radial distance of the holder is less than 0.6 times to 0 , 9 times the role.
• bracket or brackets terminate radially at the same height as the side edge of the cage, the bracket is at most radially as far beyond the web as at least one of the side edges, preferably all side edges, is radially aligned with the bracket at most beyond the web.
• an enlarged radial gap is created between a raceway and the webs.
• radially enlarged gap cross sections from the cage to the surroundings are created for improved lubricant circulation in the bearing.
• the radially protruding holder can - but does not have to be produced by means of the shape milling cutter working on the flanks.
• the flow of lubricant in the cage is further improved if the cage has at least two of the brackets per bar instead of a holder extending from pocket corner to pocket corner. has.
• the brackets on the common web are spaced apart axially of the cage, that is to say in the longitudinal direction of the axis of rotation. Lubricant can be added or removed between the brackets for contact in the cage and for rolling contact on the leaf tracks.
• the resistance to the snapping of rollers over two of the narrow brackets is less than with brackets extending lengthwise from corner to corner. The depiction of scraping marks on the rolling elements by snapping in is avoided or possible scraping marks are kept away from the main load zone of the rollers.
• the cage according to the invention is suitable for the reception of cylindrical as well as for the reception of crowned rolls. Therefore, an embodiment of the invention also provides that the maximum value of the tangential distance at the tangentially narrowest point between two of the holders opposite one another on a roller is at least smaller than the smallest dimension of the diameter of the roller at the narrowest point.
• the diameter of the roller in cylindrical rollers at the narrowest point is equal to the nominal diameter, but in the case of spherically shaped rollers, due to the diameter decreasing towards the end faces of the rollers, at the narrowest point it is smaller than the nominal diameter.
• the specification of diameter includes the usually permissible diameter tolerances of the rollers.
• the tangential distance can thus be elastically extended at least to the size of the largest dimension of the diameter of the roller at the narrowest point by means of elastic deformation of the mutually opposite holders at the narrowest point by means of the roller.
• the tangential distance is preferably at least a thousandth of a millimeter smaller than the smallest dimension of the diameter of the roller at the narrowest point.
• the invention applies to all one-piece cages which are i.) Led outboard, ii.) Led inboard or iii.) Guided in rolling elements.
• the between the The races of a bearing cage are optionally:
• the maximum radial annular gap between the respective cylindrical outer circumferential surfaces of the side edges and the respective radially outer guide rim is smaller than the radial movement play with which the roller in the pocket between a pair of inner and a pair of outer holders is radially movable (roll sag).
• the radial annular gap between the cylindrical inner circumferential surface of the side edges and the respective radially inner inner rim or an inner raceway is larger than the gap between the cylindrical outer peripheral surface of the side edges and the guide rim.
• the cage is accordingly, e.g.
• the maximum radial annular gap between the cylindrical inner circumferential surfaces of the side edges and the respective radially inner guide rim is smaller than the radial play with which the roller in the pocket can move radially between a pair of inner and a pair of outer holders (Character sag).
• the radial annular gaps between the cylindrical outer surface of the side edges and the respective radially outer rim or an outer raceway are larger than the gap between the cylindrical inner peripheral surface of the side edges Management board.
• the cage is therefore pressed radially against the inboard, for example due to centrifugal forces during operation, and slides there, guided along the circumferential direction by the guide board, without the cage being held back on the rollers by means of the outer brackets and without the cage also the outer lateral surface of the side edges touches the respective outboard.
• the respective maximum radial annular gap between the cylindrical inner peripheral surfaces of the side edges to the respective radially inner rims / raceways and the maximum radial annular gap between the cylindrical outer peripheral surfaces of the side edges to the radially outer rims / raceways is greater than the radial movement play with which the roller in the pocket can move radially between a pair of inner and a pair of outer holders (roll slack).
• the cage is accordingly, e.g. due to centrifugal forces during operation moved radially outwards and held by the inner brackets on the rollers without touching the inner or outer rims.
• brackets protrude radially outside the cage radially beyond the web - mainly applies to ii.) But optionally also for iii.)
• the brackets protrude radially inside the cage radially beyond the web - applies primarily to i.) but also for iii.).
• FIG. 1 shows in simplified form an exemplary embodiment of a cage 1 for rolling bearings with rollers 5, with a first side edge 6, with a second side edge 6, with webs 7 and with pockets 8 for the rollers 5 that are adjacent to one another on the circumference.
• the cage 1 is in one piece with the webs 7 and the side edges 6 are formed.
• the webs 7 are aligned between the first side edge 6 and the second side edge 6 along the axis of rotation 1 a of the cage.
• FIG. 2 shows an example of the longitudinal section through a pocket 9 along the axis of rotation, in this case for a cage 2 guided on the inboard of an inner ring (not shown).
• FIG. 2a shows the top view of the pocket 9.
• FIG. 2b shows the cross section of the pocket 9 along transverse to Axis of rotation with a roller 5 and Figure 2c enlarged the cross section of Figure 2b and not to scale.
• Figure 3 shows an example of the longitudinal section through a pocket 10 along the axis of rotation of the cage for a, in this case on the outboard of an outer ring, not shown, or a cage 3 guided over the rollers 5.
• Figure 3a shows the cross section of the pocket, cut transversely to the axis of rotation , for the outboard-guided cage 3 and FIG. 4, the section of the pocket 11 transverse to the axis of rotation for the cage 4 guided over the rollers, both representations enlarged and not to scale.
• FIG. 5 is the simplified sectional illustration along another pocket 12, in which the holders 14 project radially in the direction of the axis of rotation beyond the web and the side edges.
• the pocket 12 is shown in a sectional plane running transversely to the axis of rotation.
• FIG. 6 is the simplified sectional illustration along another pocket 13, in which the holders 14 project radially in the direction of the axis of rotation beyond the web 7 and end with the side edges 6 at the same radial height.
• the pocket 13 is shown in a sectional plane running transversely to the axis of rotation.
• Figure 7 shows schematically and greatly enlarged the contact of a roller 5 with a flank 16 of a web.
• FIG. 8 shows the measurement results for temperature measurements during the operation of rolling bearings 17, 18, 19 on different designs of one-piece cages.
• the pockets are delimited on the circumference by opposing flanks 16 on the webs 7 and by two inner flanks 20 of the side edges 6 opposite one another along the axis of rotation.
• the greatest tangential free distance U between the flanks 16 located opposite one of the pockets 8, 9, 10, 11 is greater than the largest diameter D of the respective roller 5 in the pockets 8, 9, 10, 11 Holders 14, 15 are formed for the rollers.
• the largest tangential free distance T, and T 2 between two brackets 14, 15, each located opposite one another on a pocket 8, 9, 10, 11, is smaller than the largest nominal diameter D N of the respective roller 5 in the pocket 8, 9, 10 , 11
• the flanks 16 have a finished profile-milled contour, which is a negative image of a positive outer cutting contour of a form cutter 21 shown in dashed lines in FIG. 6a.
• the flanks 16 each have at least one flat contact surface 22 facing the pockets 8, 9, 10, 11 for the respective roller 5 in the pocket 8, 9, 10, 11, the contact surface 22 being radial between the radially inner holder 14, 15 and the radially outer bracket 14, 15 is formed.
• the brackets 14, 15 protrude in the tangential direction beyond the respective contact surface.
• the respective roller 5 in the pocket 8, 9, 10, 11 is partially gripped radially by the holder 14 or 15 radially above the central axis 5a of the roller 5 and by the holder 14 or 15 radially below the central axis 5a of the roller 5.
• brackets 14 and 15 located opposite one another on the pocket 8, 9, 10, 11, of two webs 7 adjacent to one another on the pocket 8, 9, 10, 11, engages behind the respective roller 5 in the pocket 8, 9, 10, 11 radially above the central axis 5a and in each case a further pair of brackets 14 and 15 located opposite one another on the pocket 8, 9, 10, 11, the roller 5 radially partially radially below the central axis 5a.
• the contact surface 22 runs in the same direction as the axis of rotation, from one pocket corner 23 to another pocket corner 23 (FIG. 2a).
• the webs 7 merge into one of the side edges 6 at the corners 23.
• the contact surface 22 merges at the corners 23 into a curved corner surface 23a.
• the pocket 8, 9, 10, 11 is at the corners 23 by the corner surfaces 23a at least partially convex in the web 7.
• the curvature is described by the radii and r 2 and a flat surface 25 on which the curved sections of the corner surface 23a terminate.
• the radii ⁇ and r 2 correspond to 0.05 times to 0.2 times the nominal diameter D N of the respective roller 5 in the pocket.
• Figure 7 shows the start of the rollers 5 on the contact 27 in the circumferential direction.
• the maximum free distance T s formed between the contact point 27 and the roller 5 is smaller than any further tangential free distance T S1 -T sx between the roller 5 between the webs 7 in the radial circle above and radially below the pitch circle Bag. It should be taken into account here that in the illustration according to FIG. 7, to describe the free distance Ts (pocket play), the roller rests on the opposite contact (not shown) of the other web of the same pocket.
• the brackets 14, 15 each have an inclined surface 28 or 29 which faces into the pocket, each of the inclined surfaces 28, 29 being inclined at an obtuse angle to the contact surface.
• the holders 14 merge into the contact surface 22 on the inclined surface 28 into the contact surface 22.
• the inclined surface 29 is followed by a curved surface 30.
• the inclined surface 29 and the surface 30 run in the same direction as the axis of rotation along the pocket 8, 9, 10, 11.
• the surface 30 is from the pocket 8, 9, 10, 11 curved out of convex.
• the curvature is described by the radius R ⁇ , which is larger than the nominal diameter D N of the roller 5.
• the lubricant, oil or grease forms a wedge shape before entering contact 27 and reaches tangential to the roller circumference in contact 27 (FIG. 7). A constant supply of lubricant to the contact 27 is ensured.
• the lubricating wedge 41 is preformed on the inclined surface 28, 29 of the holder 14, 15 and drawn in between the contact surface and the roller by means of the roller 5.
• the inboard cage 2 has two first brackets 14 (in this case outer brackets) projecting radially beyond the web 7 and the side edges 6 as well as a second bracket 15 protruding tangentially into the pocket (in this case inner brackets). on.
• the brackets 14 on the common web 7 are axially spaced from one another, that is to say in the longitudinal direction of the axis of rotation, and are both equidistant from the pocket center M. Both brackets 14 are equidistant from the axis of rotation.
• the bracket 15 runs longitudinally between the corner surfaces 23a.
• the radially outwardly directed lateral surfaces 31 on the side edges 6 and the radial upper edge or lateral surface 32 for the radial delimitation of the web 7 are equidistant from the axis of rotation.
• one roller 5 per pocket 9 is held in the pocket 9 radially outwards by the holders 14 and radially inwards by the holder 15.
• the roller 5 can be moved radially freely in the pocket 9 within a predetermined sag dH.
• the brackets 14 are each described by an end face 33 facing the pocket 9 and an inclined surface 28 which adjoins the end face 33 radially inwards (FIG. 2c).
• the inclined surface 28 is inclined by the angle ⁇ to a plane E which runs parallel to the longitudinal plane of the cage.
• the holder 15 has an end face 33, which is followed radially inwards by an inclined surface 29.
• the inclined surface 29 is inclined by the angle ⁇ to a plane which runs parallel to the axis of rotation of the cage 2.
• the inclined surface 29 viewed tangentially to the cylindrical outer surface 5b of the roller 5, merges into the contact surface 22.
• the tangentially narrowest point at which the holders 14 of a pocket 9 lie opposite one another is the snap dimension S.
• the cage 2 is accordingly filled with the rollers 5 radially from the outside.
• the closest distance A between the brackets 15 is smaller than the snap dimension S.
• the outboard-guided cage 3 has, per web 7, two brackets 14 projecting radially inwards over the web 7 and the side edges 6 and a bracket 15 projecting tangentially into the pocket.
• the brackets 14 on the common web 7 are axially spaced from one another, that is to say in the longitudinal direction of the axis of rotation, and are both equidistant from the pocket center M.
• the axial distance V between the holders 14 corresponds to at least two fifths up to a quarter of the axially rectified length of the respective roll in the pocket at the narrowest point.
• the bracket 15 runs longitudinally between the corner surfaces 23a.
• the radially outwardly directed lateral surfaces 31 on the side edges and the radial upper edge or lateral surface 32 for the radial delimitation of the web 7 are the same distance from the axis of rotation away.
• the brackets 14 located radially on the inside are each described by an end face 33 facing the pocket 10 and an inclined surface 28 which adjoins the end face 33 radially inwards (FIG. 3a).
• the inclined surface 28 is inclined by the angle ⁇ to a plane which runs parallel to the longitudinal plane of the cage 5.
• the holder 15 has an end face 33, which is followed radially inwards by an inclined surface 29.
• the inclined surface 29 is inclined by the angle ⁇ to a plane E which runs parallel to the axis of rotation of the cage 5.
• the inclined surface 29, viewed tangentially to the cylindrical outer surface 5b of the roller 5 merges into the contact surface 22.
• the radius R ⁇ is greater than half the nominal diameter DN of the roller 5.
• the tangentially narrowest point at which the holders 14 of a pocket lie opposite one another is the snap dimension S.
• the snap dimension S is at least a thousandth of a millimeter smaller than the smallest dimension of the diameter Roller 5 at the narrowest point between the brackets 14.
• the cage 2 is therefore filled radially from the inside with the rollers.
• the closest distance A between the brackets 15 is smaller than the snap size S and corresponds to 0.92 to 0.96 times the nominal diameter DN of the roller 5 in the pocket 10.
• the two brackets 15 have the end face 33 per web, which is followed by a curved surface 35 described by the radius R x .
• the surface 35 merges into the contact surface 22.
• FIGS. 5 and 5a describe how the brackets 14 protrude radially inwards beyond the side edges 6 and the web 7.
• the radially inwardly facing lateral surfaces 31, 32 of the side edges 6 and the webs 7 terminate radially at the same height.
• the brackets 14 facing away from each other on a web 7 and thereby facing another one of two adjacent pockets are formed on a common rib 36 which extends in the circumferential direction between two mutually adjacent pockets 12.
• FIGS. 6 and 6a show the pocket 13 of a cage, in which the first holder 14 (in this case inner holders) is at most radially as far beyond the web 7 as at least one of the side edges 6 is radially rectified with the first holder 14 at most above the Bridge 7 stands out.
• the brackets 14 are accordingly on this cage radially inwards over the web 7, but not beyond the side edges 6.
• the contact surfaces 22 merge into a curved surface 34 on the second holders 15 (in this case outer holders).
• the side edges 6 according to FIGS. 5 and 6 each have a chamfer 37 on the part of the side edges 6 projecting radially beyond the webs 7 on the inside and outside. This chamfer 37 serves to reduce peak voltages and to reduce the weight of the cages.
• brackets 14 project radially inward beyond the web 7 and beyond the side edges 6 and that the smallest radial distance 24 of the side edges 6 on the radial side of the side edges 6, beyond which the first bracket 14 extends stands, for a surface 38 of the rollers 5 which adjoins the side edges 6 in the radial direction corresponds to at least 0.6 times to 0.9 times the nominal diameter DN of the roller 5. Accordingly, the radial distance of the first holder 14 is smaller than 0.6 times to 0.9 times the Nominal diameter D N of a roll 5.
• the invention makes it possible that for the profile milling of the pockets 8, 9, 10, 11 on cages 1, 2, 3, 4 in bearings of different dimensions and thus different load ratings, but with rollers 5 of the same nominal diameter D N , the same form cutters are used can be, since the cross section of the pockets 8, 9, 10, 11 is the same and the longitudinal section is only dependent on the nominal length of the rollers 5.
• FIG. 8 shows a diagram in which the measured values of rolling bearings 17, 18, 19 one-piece solid brass cages NU / NUP214 from a load test WS18 are compared with in-house tests.
• the test conditions were:
• a bearing with a cage 18 in which the rollers run against a flat contact surface of the flanks of the webs - but in which all the brackets do not yet protrude radially beyond the web hen and a bearing with a cage 19 according to the invention, in which the rollers start on a flat contact surface of the flanks of the webs and in which a pair of brackets on a web projects radially beyond the web and over the side edges.
• both the statistical mean values 39 and the maximum values 40 of the temperatures for the bearing 17 are above the values of the bearings 18 and 19.
• the bearing 18 already has an improved state of the art compared to the bearing 17 Temperature behavior with regard to both the statistical mean values 39 and the maximum values 40.
• the temperatures at the bearing 19 are advantageously significantly lower.
• Cage 21 form cutter rotation axis 22 contact surface cage 23 pocket corner cage 23a corner surface cage 24 distance roller 25 flat surfacea central axis 26 pitch circle outer surface surface 27 contact side edge 28 inclined surface web 29 inclined surface pocket 30 surface pocket 31 outer surface0 pocket 32 outer surface1 pocket 33 end surface2 pocket 34 surface3 pocket 35 surface4 holder 36 Rib5 Bracket 37 Chamfer6 Flank 38 Race7 Rolling Bearings 39 Average8 Rolling Bearings 40 Maximum9 Rolling Bearings 41 Lubricating Wedge0 Inner Flank

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

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• 2004
  • 2004-05-28 DE DE102004026291A patent/DE102004026291A1/de not_active Ceased
• 2005
  • 2005-05-21 EP EP05750296A patent/EP1751441A1/de not_active Withdrawn
  • 2005-05-21 US US11/569,614 patent/US7670058B2/en not_active Expired - Fee Related
  • 2005-05-21 CN CN2005800172454A patent/CN101044333B/zh not_active Expired - Fee Related
  • 2005-05-21 JP JP2007516960A patent/JP4924951B2/ja not_active Expired - Fee Related
  • 2005-05-21 CN CN201010168732A patent/CN101813133A/zh active Pending
  • 2005-05-21 WO PCT/DE2005/000938 patent/WO2005116469A1/de active Application Filing

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