WO2013175294A1 - Cage de roulement pourvue d'éléments d'écartement - Google Patents

Cage de roulement pourvue d'éléments d'écartement Download PDF

Info

Publication number
WO2013175294A1
WO2013175294A1 PCT/IB2013/001015 IB2013001015W WO2013175294A1 WO 2013175294 A1 WO2013175294 A1 WO 2013175294A1 IB 2013001015 W IB2013001015 W IB 2013001015W WO 2013175294 A1 WO2013175294 A1 WO 2013175294A1
Authority
WO
WIPO (PCT)
Prior art keywords
cage
elements
spacer element
longitudinal
webs
Prior art date
Application number
PCT/IB2013/001015
Other languages
German (de)
English (en)
Inventor
Hubertus Frank
Original Assignee
Imo Holding Gmbh
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
Priority claimed from EP12004019.1A external-priority patent/EP2667047A1/fr
Priority claimed from DE201210010082 external-priority patent/DE102012010082A1/de
Application filed by Imo Holding Gmbh filed Critical Imo Holding Gmbh
Publication of WO2013175294A1 publication Critical patent/WO2013175294A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
    • 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
    • F16C33/38—Ball cages
    • F16C33/3831—Ball cages with hybrid structure, i.e. with parts made of distinct materials
    • 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
    • F16C2240/60—Thickness, e.g. thickness of coatings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/10—Application independent of particular apparatuses related to size
    • F16C2300/14—Large applications, e.g. bearings having an inner diameter exceeding 500 mm
    • 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
    • F16C33/38—Ball cages
    • F16C33/42—Ball cages made from wire or sheet metal strips
    • F16C33/422—Ball cages made from wire or sheet metal strips made from sheet metal

Definitions

  • the invention is directed to a device for the rotatable coupling of a vehicle, machine or plant part with a chassis or foundation or other vehicle, machine or plant part, by means of at least two annular, mutually concentric connection elements for connection to the parts to be rotated, which are spaced apart by a gap and are thereby rotated about the common axis against each other, wherein in the gap at least one row of rolling elements is provided, which roll between races on each of the two connection elements, and wherein the rolling elements of a row are circumferentially spaced from each other by a cage having a band-shaped structure with at least two mutually approximately parallel longitudinal webs and at least one flanked in both circumferential directions of the gap of transverse webs transverse web, which two openings of the cage for receiving adjacent rolling body separated from each other and is rigidly connected via the at least two longitudinal webs with the flanking transverse webs, wherein the longitudinal and transverse webs together span a band-shaped, openwork surface.
  • CONFIRMATION COPY spherical, cylindrical, conical, barrel or needle-shaped elements which are usually harder than the raceways in which they roll.
  • roller bearings and slewing rings essentially satisfy a service life and wear life or service life which can be calculated from the outset.
  • the actual calculation of the rolling bearings is based on life.
  • the fatigue of the material and the subsequent damage to the components is also due to the formation of dimples (so-called pittings).
  • Pure rolling of steel on steel (as for example when rolling the rolling elements on the track) always causes Hertzian pressure, which can lead to pitting (so-called pitting).
  • the service life calculation can usually be carried out with specially determined Wöhler curves or with the help of relevant calculation formulas.
  • the cages of rolling bearings are designed as steel belt cages. Again, the friction from the steel belt cage and the steel of the track system can lead to friction and damaging abrasion, similar to the cases described above. To prevent material weakening due to abrasion, be in the Practice wider / thicker steel tape cages installed, which are due to the increased material requirements, however, usually heavier. Wider / thicker steel cages require more material and consequently - proportional to the increase in weight - also increase the total cost.
  • the US 2,417,559 discloses an arrangement wherein a cage of a plurality of cage segments, each with only one window for a rolling element is articulated. Only in the region of such joints between the said links are rotary axes which protrude from the respective plane. Since these outstanding axle pins are provided only in the range of articulated connections, the position of the cage is largely left to itself and defined only to a limited extent. Unwanted friction between the cage and the raceway system can not be ruled out.
  • the problem initiating the present invention is to provide a cage or steel cage for rolling bearings, the less material needed, has better sliding friction properties compared to the steel materials of the raceway system, is lightweight and costs less.
  • connection surfaces differ from normal bearings in that the connection surfaces, so the contact surfaces between the rings and the machine or system parts to be connected are cylindrical or hollow cylindrical in normal rolling, according to the gap facing lateral surfaces, for example, pushed by the inner ring on a shaft and there is frictionally fixed while the contact surfaces are flat in large rolling bearings and thus are formed by one end face of the two annular connection elements. These rest against the entire surface on a likewise flat contact surface of the relevant machine or system part and are fixed thereto by means of screws which are inserted and / or screwed into annularly arranged fastening bores in the connection elements which open into the relevant connection surface.
  • connection surfaces of the two connection elements are facing away from each other, that is, they are located on oppositely oriented end faces.
  • the relevant connection surface of a ring is usually designed to be raised in relation to the end face of the other ring, which does not serve as a connection surface, and is oriented in the same direction.
  • a generic device for rotatable coupling of a vehicle, machine or plant part with a chassis or foundation or other vehicle, machine or plant part for example in the form of a rolling bearing or large rolling bearing or in Form of a rotary joint on the basis of at least one roller bearing or slewing bearing, by at least one independently produced by the cage and with that in the region of an inner, flanked in both circumferential directions of transverse webs crosspiece so connected spacer element that it is approximately perpendicular to that of the longitudinal and Transverse webs spanned surface protrudes and slides with an always constant, free end side of a connection element along, preferably only an always constant, free end face of the spacer element comes into contact with the relevant connection element.
  • a rolling bearing or slewing bearings should be regarded as comprising at least two concentric rings with at least one row of rolling elements rolling between two mutually facing raceways.
  • the radial strength of the two rings is dimensioned such that there are space distributed fastener elements, in particular the ring plane approximately perpendicular passing through fixing holes for receiving fastening screws.
  • These mounting holes can be formed as through holes or as provided with internal blind hole holes.
  • Such rotary joints can be combined with rolling elements, but also with slewing bearings.
  • Other components may be provided, for example a housing, in particular for protecting a toothing, and / or gap seals, to retain lubricant contained in the gap, preferably lubricating grease or oil, and on the other dirt and other particles to penetrate to the sensitive areas within the To prevent the gap.
  • attachable or integrated elements are brakes, tachometers and / or incremental encoders.
  • the raceways of the connecting elements may be hardened, preferably surface-hardened, for example by means of induction hardening, in particular in the form of a slip-free hardening by means of two, oppositely movable induction heads.
  • a not inconsiderable advantage of the invention is that the potential contact points between the cage and the connection elements are minimized by means of spacer elements, namely reduced to the surface of the free end faces of the spacer elements.
  • the frictional properties of these free end faces of the spacer elements can be selectively influenced, in particular by the selection of the material of the spacer elements.
  • particularly smooth or soft materials can be used, and / or the respective end faces can be specially processed, for example, be provided with a special coating material.
  • the rings are provided with axial, annularly distributed mounting holes. Because there may arise a particularly intense friction between the cage and the nearest areas of the annular connection elements, which is minimized and / or mitigated by the present invention.
  • the rolling bearing cage according to the invention may be made predominantly of steel and is designed for a rotary joint or a rolling bearing or a large rolling bearing with the parallel purpose to provide several receptacles for cylindrical roller, or ball, or needle, or conical, or tapered roller-shaped rolling elements.
  • the use of steel is advantageous because the cage is sufficient stable and thus able to impose the mutual relative position in approximately equidistant intervals even in heavily loaded large roller bearings the local Wälzkörpem.
  • a band-shaped cage of small thickness H is used, for example in the order of 1 to 20 mm: 1 mm ⁇ H ⁇ 20 mm, up to a maximum of 35 mm - depending on the size of the rolling bearing or the rotary joint and depending on the size the rolling element to be received by the steel cage.
  • a thin-walled steel cage for example with a thickness of the order of 1 to 5 mm: 1 mm ⁇ H ⁇ 5 mm, is preferred.
  • Such cages have a comparatively low weight and, moreover, allow for small gap widths between the connecting elements involved, so that they can be approximated to one another to a maximum, whereby the construction volume of the rotary coupling device according to the invention can be minimized.
  • the invention makes it possible to choose the thickness H of the cage smaller than the radius of the rolling bodies accommodated therein, without the protruding spacer elements. Because of the invention, it is possible to keep the cage always at a certain radial position within the gap, in the region of the equator of the rolling elements. Therefore, it is impossible that the cage displaced radially and then the rolling elements could possibly move within their windows.
  • the thickness H of the cage for reasons of dimensional stability should be greater than 1/50 of the transverse radius of curvature of the raceways, between which spherical rolling elements roll, preferably greater than 1/20 of the transverse radius of curvature of the raceways, in particular greater than 1/10 of the transverse radius of curvature of raceways.
  • At least one, preferably several, spacer elements can be used in receiving means, ie depressions, in the cage according to the invention.
  • These receiving means may be, for example, material recesses in the form of holes or in particular in the form of blind holes. Alternatively, receiving means have proven in the form of through holes.
  • Each such receiving means can accommodate at least one inserted spacer element, preferably in each case exactly one spacer element. These inserts contact the rolling bearing cage along the relevant bore circumference. This results in a positive connection in two dimensions, namely within the band surface; the spacers can only be detached in one direction perpendicular to this surface of the cage.
  • Each of these spacer elements used can be releasably or permanently connected to the rolling bearing cage.
  • the respective insert can be pressed mechanically into the cage after insertion into the respective receiving means. Alternatively, the inserts are screwed into the respective receiving means.
  • through holes or alternatively blind holes are introduced into predefined locations in the cage part.
  • the introduction of these holes can be done for example by means of material removal by laser beam machining.
  • the introduction of these holes is done by deep drawing, stamping, fine blanking or by conventional chip removal process such as drilling.
  • the rolling bearing cage according to the invention made of steel is suitable to be used in all conventional mechanical bearings, such as bearings and slewing bearings, slewing rings and torque bearings.
  • rolling elements of these bearings are for example spherical, cylindrical, conical, barrel or needle-shaped elements, which are usually harder than the raceways on which they roll.
  • a lower friction of the steel cage with the raceway system is achieved in particular by the fact that in the holes of this cage separate inserts Brass or plastic, or be introduced from another iron or non-ferrous material with lower hardness values than the bearing steel of the raceway system. These inserts serve as spacers and have the property to keep the steel cage from the contact surface of the raceway system at a sufficient distance to avoid direct contact.
  • Brass or plastic is particularly recommended as a material for the spacers or inserts, since brass or plastic is lighter than steel and thus the weight reduction resulting from the object of the invention is achieved, and secondly because brass or plastic is less hard than the steel materials of the track or the raceway system, and thus have better sliding properties. This difference in hardness also results in less dangerous steel chips, which could lead to increased pitting in the raceway (s) or in the raceway system.
  • the height of the spacing is dependent on the respective protruding height of the insert.
  • all inserts placed in the steel cage should have the same shape, and in particular the same projecting height, to ensure the most homogeneous running of the steel cage in the raceway system.
  • Important in the sense of the cited invention is also the diameter of the projecting part of the insert. This diameter should be greater than the bore diameter of the insert to reduce the risk of slippage of the insert from the bore.
  • the invention therefore prefers spacer elements which have an at least one-time stepped cross-section in their longitudinal direction perpendicular to the respective surface of the cage, preferably a reduced cross-sectional area within a receiving recess in the cage, while an area of expanded cross-section over the respective surface of the cage should survive.
  • a spacer may have rotational symmetry. It is also advantageous if the inserts are fixed by appropriate security measures in the steel cage. In particular, a mechanical pressing of the respective insert in the bore has been found to be advantageous. Synonymous and equivalent conceivable are also positive geometries of each insert, so due to this shape / geometry, a release of the insert from the steel cage - or from the holes of this steel cage is impossible.
  • the insert or the spacer can be screwed to the steel cage by the cage and the insert or the spacer element are provided with corresponding thread devices.
  • the insert may have an external thread and the cage may have an inserted or cut internal thread.
  • Further advantages arise when the spacers or inserts survive on both sides of the respective receiving bore to a certain extent. In particular, it is advisable to choose this measure according to a common height, because then the inserts survive on both sides by an identical amount. This is particularly useful in order to achieve an approximately central guidance of the cage between the two raceways or in the raceway system.
  • an inserted spacer element may be flush with the base of the respective receiving bore or its lower edge, so that only a one-sided projection results.
  • the supernatant is basically equated with the protrusion of the respective insert relative to the surface of a rolling bearing cage side.
  • the steel rolling bearing cage can be made as an "endless belt", for example by connecting two ends of a belt to each other at the joint, or it can be formed as a belt-like cage segment accommodating all the rolling elements in a row, or as a true cage segment having only one Part of the rolling elements of a series absorbs.
  • Fig. 1 is a perspective view of rotary joints with
  • FIG. 2 shows an exemplary segment of a roller bearing cage with receptacles / windows for rolling elements and with a plurality of spacer elements in a perspective, wherein at the left lower edge of the joint is visible.
  • Figure 2a shows a section through a segment of the rolling bearing cage according to the invention of Figure 2 with inserts, wherein the way is shown how the spacer elements contact the raceway system ..;
  • FIG. 2b shows a representation corresponding to FIG. 2a of another embodiment of the invention, wherein the spacer elements each protrude only on one side of the cage;
  • Fig. 2c is a representation corresponding to Fig. 2a of another embodiment of the invention, wherein the spacer elements each protrude on both sides of the cage relative to the surface thereof;
  • Fig. 2d is a representation corresponding to Figure 2a of another embodiment of the invention, wherein the spacer elements are inserted into blind holes within the cage.
  • 2e another exemplary section of a segment of a roller bearing cage according to the invention with spacer elements, from which the position can be seen, at which the rolling bearing cage according to the invention is guided within the raceway system;
  • Fig. 3 is a Fig. 2 corresponding representation of a modified again
  • Fig. 4 shows a band-shaped cage in a perspective view
  • Fig. 4a is a representation corresponding to Fig. 4 a modified again
  • FIG. 4b shows a spacer element used in the embodiment according to FIG. 4a in a perspective view
  • Fig. 5 is a representation corresponding to Fig. 4 another modified
  • FIG. 5a seen in the embodiment of Figure 5 used spacer element in a perspective view of its broad side; 5b shows a perspective view of the spacer element according to FIG. 5a, seen from its end side; and a band-shaped cage element, wherein, for example, the spacer elements according to FIGS. 5a and 5b can be used.
  • Fig. 1 shows a plurality of rotary coupling devices 1, each consisting of two concentric rings, namely in each case an outer ring 2 and a concentric inner ring 3.
  • the rolling elements 6 are balls.
  • the raceways 5 have neither a cylindrical nor a hollow cylindrical shape. Rather, they have a concave curved cross-section, wherein the Querwölbungsradius the raceways 5 is equal to or preferably slightly larger than the radius of the spherical rolling elements. 6
  • the rings 2, 3 each serve as connection elements and are used to connect to a vehicle, machine or system part, chassis or foundation to be connected. For this purpose, they have at least one connecting surface, preferably extending circumferentially all around.
  • fastening screws can be inserted and / or screwed, which additionally aligned holes in the relevant machine or plant part, chassis od. Like. Pass through and generate a tightened state sufficient normal force between the adjacent planar contact surfaces to cause a sufficient frictional force between these elements.
  • a rotary joint drive elements in the form of at least one completely or partially circumferentially continuously arranged row of teeth are provided on at least one ring 2, 3, with which a pinion or a worm meshes.
  • a toothing is preferably located in each case at the circumferential surface of the ring 2, 3 facing away from the gap.
  • the spherical rolling elements 6 are held at positions at approximately constant intervals by a band-shaped roller bearing cage 11. This has at each desired position of a rolling element 6 depending on a window-like recess for the respective rolling element 6, which is embraced approximately at the level of its equator.
  • This plurality of windows of the cage 1 is replaced by a structure with two edge-side longitudinal edges, which are interconnected at approximately equidistant intervals of transverse webs. This has the consequence that these rolling elements 6 are guided and spaced in and through the cage 1.
  • the roller bearing cage 11 has an approximately band-shaped basic shape with two base surfaces 12 and two longitudinal edges 13.
  • the cage 11 consists of a steel strip.
  • the window 14 for receiving the rolling elements 6 are punched or cut or otherwise removed.
  • the outline of the window 14 corresponds approximately to the sectional area through a rolling element 6 along a plane which runs through the center of the rolling element 6, but is slightly larger than that, so that the rolling elements 6 can run as smoothly as possible within the window 14.
  • the windows 14 each have a circular shape. Since the maximum extent of the window 14 in the direction of the bearing axis of rotation, in particular the diameter of the circular window 14, is smaller than the width b of the cage strip 11, remain between the windows 14 and two longitudinal edges 13 each extending over the entire cage segment away longitudinal webs 15.
  • these transverse webs 16 widen to the longitudinal webs 15, each up to a maximum width, which is greater than the diameter of a circular window 14, namely the sum of just this window diameter plus the minimum width of a transverse web approximately on a Central line of the cage tape 1 corresponds.
  • the spacer elements 17 are provided in pairs, at both widened end portions of a transverse web 16, but not necessarily at each cross bar 16, but for example only on every second crossbar 16.
  • the spacer elements 17 have an approximately cylindrical shape.
  • the spacers 17 are inserted into through holes 18.
  • the inserts 17 are each fixed separately in the holes 18, for example by gluing or pressing.
  • Each insert 17 has a bore 18 is provided.
  • FIGS. 2 a to 2 c show various embodiments of spacer elements 17 which can be inserted into the cage belt 11 according to FIG. 2: In the embodiment according to FIG. 2a, two different types of spacer elements 17, 17a are used, the manner in which these spacer elements 17, 7a contact the connection elements 2, 3: at least one end face 20 each of a spacer element 17, 17a contacted with a connection element 2, 3, in such a way that a flat contact results.
  • the inserts 17, 17a may preferably be made of brass or plastic.
  • Fig. 2a further shows that different inserts 7, 17a or spacer elements may have different lengths.
  • the spacer elements 7, 17a have an approximately identical structure, namely a rotationally symmetrical shape with two longitudinally successive aligned cylindrical sections, namely a thickened head section 22 and a tapered shaft section 23.
  • the illustrated spacer elements 17, 17a have different overall lengths:
  • FIG. 2 a shows, different spacer elements 17, 17 a can be oriented differently, so that the respective head sections 22 lie on different base sides 12 of the cage 11.
  • the shank portions 23 respectively pass through the relevant through hole 18.
  • only spacers 17 with an overall length H + H50 are used, which are inserted from different bases 12 into the bores 18 of the cage 11.
  • 2d and 2e relate to a further embodiment of the invention, wherein the bores 18 'are not formed continuously, but are formed as so-called. Blind holes.
  • FIG. 2e shows a section across a raceway system 21.
  • Fig. 3 shows a segment of a again modified roller bearing cage 1 1 ", also with inserted rolling elements 6", in a perspective side view similar to in Fig. 2.
  • the spacers 17c are not included in through holes, but in only one side accessible holes 18 ", so-called blind holes, used in each case two such blind holes 18" from different bases 12 "ago introduced in a common flight and are separated from each other only by a thin disc 24.
  • the spacers 17c may be fixed in the respective holes 18" for example glued or screwed.
  • the heads of the shafts need not be staggered stage. Rather, the spacers 17c have a constant over its entire length cross section, in particular a constant diameter.
  • 4a and 4b has a cage strip 1 1 (3) similar to the cage strip 1 of FIG. 2, namely with through holes 18 (3) in the transition areas of the transverse webs 16 (3) to the longitudinal webs 15 (3) .
  • the spacers 17d used therein are constructed differently. Because these are indeed rotationally symmetrical. However, they have two radially expanded, preferably disc-shaped head portions 22d, which are connected by a contrast tapered shaft portion 23d with each other. The total length of such a spacer element 17d in turn corresponds to the width W of the gap 4 at the relevant point.
  • the length S of the shaft portion 23d corresponds to the thickness H of the cage belt 1 1, the length K of a head portion 22d the dimension H50. Both head portions 22d are preferably congruent and mirror images of each other.
  • a head portion 22d could have a hollow cylindrical shaft portion, wherein the other correspondingly tapered shaft portion is insertable.
  • FIGs. 5, 5a, 5b and 6 A further modified embodiment of the invention is shown in Figs. 5, 5a, 5b and 6 reproduced.
  • the spacer elements 17e have no cylindrical or rotationally symmetrical shape, but - as seen in Figs. 5a and 5b - have an approximately triangular, more precisely pentagonal shape.
  • its spacer element 17e also consists of two congruent disks or head sections 22e, which are connected to one another by an approximately central axis 23e and by an edge-side web 23f, such that the two disks or head sections 22e are at a mutual distance, parallel to each other and congruent and / or mirror image arrangement to each other, are fixed.
  • the side of a pentagonal head portion 22e adjacent to the peripheral land 23f forms its largest edge length, while the adjacent sides approximately perpendicularly away from the longest side represent the shortest edge lengths.
  • the remaining two sides are mirror images of each other and meet on a mid-perpendicular to the first, longest side, approximately at a distance from this longest side, which corresponds to about half of this longest side.
  • a cage strip is 11 (4) according to Fig. 6. This has in the transition region of its transverse ribs 16 () to the longitudinal webs 15 (4) via two edge side in the longitudinal webs approximately slit-shaped incorporated recesses 18 (4) , which are open to the respective longitudinal edge 13 () of the cage strip 11 (4) .
  • These recesses 18 (Fig. 4) have approximately a footprint corresponding to a comparatively sharp wedge whose base is open to the longitudinal edge 13 ( Fig. 4) and taper towards its inner tip, but not continuously, but with an approximately central thickening a superimposed circle whose diameter corresponds approximately to the (narrow) base of the wedge.
  • an axis 23e of a spacer element 17e is used in each case until the edge-side connecting web 23f of the respective spacer element 17e on the longitudinal web 15 (4) of the cage 1 1 ⁇ 4) . Since the thickened region of the wedge-shaped recess 18 (4) is a kind of undercut with a local extension of the recess 18 ⁇ 4) , an axle 23e can engage in this extension in order to fix the relevant spacer element 17e in the recess 18 (4) .
  • the spacer elements 50 should be made of a softer and / or wear-free material as the actual cage 10. It is also possible to provide the frictional faces of the spacer elements with a friction-reducing coating, such as Teflon.

Abstract

L'invention concerne un dispositif de couplage rotatif d'une partie d'un véhicule, d'une machine ou d'une installation avec un châssis ou un bâti ou bien une autre partie de véhicule, de machine ou d'installation, à l'aide d'au moins deux éléments de raccordement annulaires et mutuellement concentriques destinés au raccordement aux parties à faire tourner, ces éléments de raccordement étant espacés par une fente et pouvant ainsi tourner l'un par rapport à l'autre autour d'un axe commun ; au moins une rangée de corps roulants étant agencés dans la fente, et roulant entre des chemins de roulement de chacun des deux éléments de raccordement ; et les corps roulants d'une rangée étant mutuellement espacés dans la direction circonférentielle par une cage présentant une structure en forme de bande, dotée d'au moins deux segments longitudinaux approximativement parallèles et, dans les deux directions circonférentielles de la fente, d'au moins un segment transversal flanqué de segments transversaux, ledit segment transversal séparant deux perforations de la cage destinées à recevoir des corps roulants adjacents, et étant relié de manière rigide, avec les segments transversaux le flanquant, sur les au moins deux segments longitudinaux, les segments longitudinaux et transversaux définissant ensemble une surface ajourée et en forme de bande, ledit dispositif comprenant au moins un élément d'écartement qui est fabriqué indépendamment de la cage et qui est relié à cette cage dans la zone d'un segment transversal interne flanqué dans les deux directions circonférentielles de segments transversaux, de manière à faire saillie approximativement perpendiculairement à la surface définie par les segments longitudinaux et transversaux, et à glisser, par une face frontale libre ne variant jamais, sur un élément de raccordement.
PCT/IB2013/001015 2012-05-23 2013-05-23 Cage de roulement pourvue d'éléments d'écartement WO2013175294A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP12004019.1A EP2667047A1 (fr) 2012-05-23 2012-05-23 Cage de palier de roulement avec inserts
EP12004019 2012-05-23
DE201210010082 DE102012010082A1 (de) 2012-05-23 2012-05-23 Wälzlagerkäfig mit Einsätzen
DE102012010082.5 2012-05-23

Publications (1)

Publication Number Publication Date
WO2013175294A1 true WO2013175294A1 (fr) 2013-11-28

Family

ID=48783277

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IB2013/001015 WO2013175294A1 (fr) 2012-05-23 2013-05-23 Cage de roulement pourvue d'éléments d'écartement

Country Status (1)

Country Link
WO (1) WO2013175294A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015101464A1 (de) * 2015-02-02 2016-08-04 Thyssenkrupp Ag Wälzlagerkäfig, Wälzlager und Verfahren zum Herstellen eines Wälzlagerkäfigs
DE102015208838A1 (de) * 2015-05-13 2016-11-17 Schaeffler Technologies AG & Co. KG Verbindungselement zur Befestigung von Bauteilen an Wälzlagern und Wälzlageranordnung
US20170102032A1 (en) * 2015-10-12 2017-04-13 Schaeffler Technologies AG & Co. KG Low friction ball bearing cage design with optimized contact surface
EP3690268A2 (fr) 2019-02-01 2020-08-05 thyssenkrupp rothe erde Germany GmbH Cage de corps de roulement pour palier à roulements
CN111981043A (zh) * 2019-05-24 2020-11-24 斯凯孚公司 滚动轴承保持架

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2417559A (en) 1944-06-26 1947-03-18 Cread Engineering And Res Comp Antifriction bearing retainer
GB835389A (en) 1957-08-06 1960-05-18 Schaeffler Wilhelm Improvements in or relating to needle or roller bearings
JP2004076928A (ja) * 2002-06-19 2004-03-11 Nsk Ltd 転がり軸受用合成樹脂製保持器及び転がり軸受
EP2031259A2 (fr) * 2007-08-31 2009-03-04 JTEKT Corporation Cage pour roulement à rouleaux
DE102008026893A1 (de) 2008-06-05 2009-12-10 Schaeffler Kg Verfahren zum Herstellen eines Käfigelements für einen Wälzlagerkäfig und Wälzlagerkäfig
DE102009037420A1 (de) * 2009-08-13 2011-02-17 Schaeffler Technologies Gmbh & Co. Kg Käfigsegment für einen Kunststoffkäfig eines Wälzlagers und Wälzlager mit einem solchen Käfigsegment
WO2012110345A1 (fr) * 2011-02-16 2012-08-23 Schaeffler Technologies AG & Co. KG Palier à roulement

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2417559A (en) 1944-06-26 1947-03-18 Cread Engineering And Res Comp Antifriction bearing retainer
GB835389A (en) 1957-08-06 1960-05-18 Schaeffler Wilhelm Improvements in or relating to needle or roller bearings
JP2004076928A (ja) * 2002-06-19 2004-03-11 Nsk Ltd 転がり軸受用合成樹脂製保持器及び転がり軸受
EP2031259A2 (fr) * 2007-08-31 2009-03-04 JTEKT Corporation Cage pour roulement à rouleaux
DE102008026893A1 (de) 2008-06-05 2009-12-10 Schaeffler Kg Verfahren zum Herstellen eines Käfigelements für einen Wälzlagerkäfig und Wälzlagerkäfig
DE102009037420A1 (de) * 2009-08-13 2011-02-17 Schaeffler Technologies Gmbh & Co. Kg Käfigsegment für einen Kunststoffkäfig eines Wälzlagers und Wälzlager mit einem solchen Käfigsegment
WO2012110345A1 (fr) * 2011-02-16 2012-08-23 Schaeffler Technologies AG & Co. KG Palier à roulement

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"Maschinenelemente. Normung Berechnung Gestaltung", 1976, pages: 345 - 350

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015101464A1 (de) * 2015-02-02 2016-08-04 Thyssenkrupp Ag Wälzlagerkäfig, Wälzlager und Verfahren zum Herstellen eines Wälzlagerkäfigs
DE102015208838A1 (de) * 2015-05-13 2016-11-17 Schaeffler Technologies AG & Co. KG Verbindungselement zur Befestigung von Bauteilen an Wälzlagern und Wälzlageranordnung
US10180156B2 (en) 2015-05-13 2019-01-15 Schaeffler Technologies AG & Co. KG Connecting element for fastening components to rolling-element bearings, and rolling-element bearing assembly
DE102015208838B4 (de) * 2015-05-13 2020-07-09 Schaeffler Technologies AG & Co. KG Wälzlageranordnung
US20170102032A1 (en) * 2015-10-12 2017-04-13 Schaeffler Technologies AG & Co. KG Low friction ball bearing cage design with optimized contact surface
EP3690268A2 (fr) 2019-02-01 2020-08-05 thyssenkrupp rothe erde Germany GmbH Cage de corps de roulement pour palier à roulements
DE102019201331A1 (de) 2019-02-01 2020-08-06 Thyssenkrupp Ag Wälzkörperkäfig für Wälzlager
CN111981043A (zh) * 2019-05-24 2020-11-24 斯凯孚公司 滚动轴承保持架

Similar Documents

Publication Publication Date Title
DE60124063T2 (de) Führungseinrichtung für lineare Bewegung
DE3308735A1 (de) Kreuzwalzenlager
EP3147239B1 (fr) Courroie dentée avec rouleaux intégrés pour le support
WO2013175294A1 (fr) Cage de roulement pourvue d'éléments d'écartement
DE102005058152A1 (de) Käfig für Wälzrollenlager
DE10335415B4 (de) Wälzlager
DE19740435A1 (de) Verfahren zum Herstellen eines Käfigs
DE3520814A1 (de) Kaefig fuer schraegrollenlager
WO2015048948A1 (fr) Dispositif de roulement à aiguilles
DE2608308C2 (de) Rollenkranz
DE2227312A1 (de) Laengslager
DE102010022964A1 (de) Segment-Wälzlager mit Synchronisationseinrichtung
DE112004002814T5 (de) Zusammengesetztes Wälzlager
DE102004049968A1 (de) Zapfenkäfig, insbesondere für größere Radial- oder Axialrollenlager
DE2838481C2 (de) Kreuz-Linearlager-Anordnung zum Halten und zur Verschiebebewegung einer schweren Last in zwei zueinander senkrechten Richtungen
DE102004003655A1 (de) Käfig für ein Zylinderrollenlager
WO2008116707A1 (fr) Palier à roulement radial
DE102006051129B3 (de) Verbindung einer Antriebswelle
EP2702287B1 (fr) Cage de palier à roulement composé de segments interconnectés
DE102017129773A1 (de) Pendelrollenlager
CH401599A (de) Käfig für zylindrische Wälzkörper, insbesondere Nadelkäfig
DE2338687A1 (de) Kaefigloses waelzlager mit vorbelasteten hohlrollen
DE202012005052U1 (de) Wälzlagerkäfig mit Einsätzen
DE102020130707B3 (de) Rollenlager
DE102015216467B4 (de) Wälzlagerkäfig oder -segment

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13736619

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13736619

Country of ref document: EP

Kind code of ref document: A1