EP1565664A2 - Roulement a galets-tonneaux - Google Patents

Roulement a galets-tonneaux

Info

Publication number
EP1565664A2
EP1565664A2 EP03812127A EP03812127A EP1565664A2 EP 1565664 A2 EP1565664 A2 EP 1565664A2 EP 03812127 A EP03812127 A EP 03812127A EP 03812127 A EP03812127 A EP 03812127A EP 1565664 A2 EP1565664 A2 EP 1565664A2
Authority
EP
European Patent Office
Prior art keywords
barrel
groove
cage
rolling element
rolling
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP03812127A
Other languages
German (de)
English (en)
Inventor
Rainer Schröder
Martin Grehn
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHO Holding GmbH and Co KG
Original Assignee
FAG Kugelfischer AG and Co OHG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by FAG Kugelfischer AG and Co OHG filed Critical FAG Kugelfischer AG and Co OHG
Publication of EP1565664A2 publication Critical patent/EP1565664A2/fr
Withdrawn legal-status Critical Current

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
    • F16C33/46—Cages for rollers or needles
    • F16C33/54—Cages for rollers or needles made from wire, strips, or sheet metal
    • F16C33/542—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal
    • F16C33/543—Cages for rollers or needles made from wire, strips, or sheet metal made from sheet metal from a single part
    • 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
    • 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F16C33/363—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces with grooves in the bearing-surfaces
    • 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
    • F16C33/49—Cages for rollers or needles comb-shaped
    • F16C33/494—Massive or moulded comb cages
    • F16C33/495—Massive or moulded comb cages formed as one piece cages, i.e. monoblock comb cages
    • F16C33/497—Massive or moulded comb cages formed as one piece cages, i.e. monoblock comb cages made from metal, e.g. cast or machined comb 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
    • F16C33/52—Cages for rollers or needles with no part entering between, or touching, the bearing surfaces of the rollers

Definitions

  • the invention relates to a barrel bearing with an outer and an inner ring, with at least one row of barrel-shaped rolling elements arranged therebetween and with at least one disk-shaped cage rotating with the rolling bodies, which engages in a circumferential groove in the rolling bodies of a row and has an outer circumference has the number of recesses corresponding to the number of rolling elements in a row.
  • German Patent 663 179 shows a roller roller bearing, the rolling bodies having a stepped cross section and rolling with their distal regions on the outer ring and with their proximal regions on the inner ring.
  • the distance from the bottom of a recess in the disc cage to its inner circumference is smaller than the depth of the groove in a rolling element. This enables the desired, purely concave cross-sectional geometry of the tread of the inner ring.
  • the rolling elements can be gripped around the diametrically opposite regions of the groove base and thereby held securely , even if the outer ring is pivoted very much in relation to the other bearing components.
  • the maximum (radial) width of the annular disc cage between its inner and outer circumferential circle should be equal to or larger than the diameter of a rolling element in the area of the groove surrounding it, in order to maintain sufficient stability on the one hand despite the recesses on the outer circumference and on the other hand the individual To be able to grip the rolling elements safely.
  • a recess in the disc cage is bordered by a curve (regionally) of constant curvature.
  • the radius of curvature rs of this curve should be somewhat larger than half the diameter of a rolling element in the area of its groove base, so that a (slight) play ensures that the rolling element in question can be easily rotated.
  • circumferential groove in the casing of a barrel-shaped rolling element has side faces that are parallel to one another or diverge outward from one another.
  • the width of the groove in the shell of a barrel-shaped rolling element should always be slightly larger than the (axial) width d of the disc cage.
  • individual rolling elements can be forced to tilt relative to the disc cage in special load cases, and such a movement can possibly be facilitated by a groove shape with outwardly diverging side surfaces.
  • This feature of the invention can be further developed in such a way that the side surfaces of the circumferential groove run in the shell of a barrel-shaped rolling element along conical surface surfaces. It is a simple geometric shape that meets all requirements.
  • the conical lateral surfaces each have an opening angle a of less than 179 °
  • a tilting angle caused by the play between these elements, so that the maximum tilting angle of the rolling element rotation axes with respect to the solder on the base of the disc cage can be, for example, in the order of 5 ° to 10 °.
  • This play-related tilt angle is influenced by the groove width w at the groove base.
  • this value should at least correspond to the (axial) thickness d of the disc cage;
  • the difference between the groove width b at the groove base and the (axial) thickness d of the disc cage can preferably be set according to the following relation to the opening angle a of the cone-shaped groove side surfaces:
  • the cross section of the inner and outer ring and the rolling elements is dimensioned such that there are a total of 3 or 4 contact points per rolling element.
  • This feature relates in particular to the radius of curvature of the cross-sectional concave treads of the inner and outer rings. This radius of curvature should be somewhat larger than the radius of curvature of the barrel-shaped rolling elements within a longitudinal section plane through the rolling element in question.
  • the resulting two points of contact can split into three or four points of contact.
  • This effect is desirable because it increases the load capacity of a rolling element and can are further reinforced by the fact that the centers of the transverse curvature radii of the two barrel "hemispheres" on both sides of the (equatorial) groove for the disk are spaced apart from each other in the direction of the axis of rotation or symmetry of the barrel-shaped rolling element in question, but preferably only by a small amount x, which is, for example, smaller than the groove width b N at the groove base: x ⁇ bN-
  • Figure 1 is an end view of a barrel storage according to the invention.
  • FIG. 2 shows a section through FIG. 1 along the line II-II;
  • FIG. 3 shows a representation corresponding to FIG. 2 with the radii of curvature entered
  • FIG. 4 shows a perspective view of the barrel bearing from FIG. 1, the outer ring being partially broken off, so that the view of the rolling elements held by the cage is released;
  • FIG. 5 shows a representation corresponding to FIG. 4, with some rolling elements having been removed from the exposed cage
  • FIG. 6 shows a side view of the casing of a roller body removed from the cage according to FIG. 5;
  • FIG. 7 shows a representation corresponding to FIG. 6 of a modified embodiment of the invention.
  • FIGS. 4 and 5 shows a plan view of a segment broken out of the cage from FIGS. 4 and 5; such as
  • FIG. 9 is a representation corresponding to FIG. 8 of an again modified embodiment of the invention.
  • FIG. 1 shows a barrel bearing 1 according to the invention with an outer ring 2, an inner ring 3 and a row of barrel-shaped rolling elements 4 arranged between them, which are held by an encircling cage 5 at approximately equidistant intervals.
  • the outer ring 2 can be tilted 3 to 5 relative to the other bearing components. This is made possible by the fact that the rolling bearing tread 6 on the outer ring 2 has a concave cross section with a constant radius of curvature.
  • the cage 5 holds the rolling elements 4 in position when the outer ring 2 is tilted relative to the other bearing components 3 to 5. On the other hand, so that it neither tilts the outer ring 2 nor the movement of the rolling elements 4 hindered, it extends through a circumferential groove 7 of each rolling element 4, as shown in FIGS. 2 and 3.
  • the cage 5 can be produced from a disk with a constant thickness d, for example punched out of a sheet metal. As shown in FIG. 8, a number of recesses 9 corresponding to the number of rolling elements 4 are cut out of an annular basic structure with a constant radial width from the radially outer circumference 8. These each take up a rolling element 4.
  • the inner circumference 10 of the disc-shaped cage 5 corresponds to the maximum outer circumference of the inner ring 3, in particular at an edge 11 of its running surface 12, so that the cage 5 can easily be placed over the inner ring 3, for example mechanically.
  • the insertion of the rolling elements 4 into the recesses 9 of the disk-shaped cage 5 can also be effected automatically, the rolling elements 4 then being held in place because they are encompassed by the cage 5 in the area of the groove base 13 in question.
  • the barrel-shaped rolling elements 4 are therefore divided approximately in the middle between their two end faces 14 in their “equatorial” plane by the circumferential groove 7 into two halves 15, so to speak “hemispheres”.
  • the two contact areas of a bearing with undivided (not grooved) rolling elements are therefore divided into four contact areas in the rolling elements 4 according to the invention. This has the advantage that the radial loads to be transmitted are distributed over a larger total area. This effect is therefore additionally supported by giving the two “hemispheres” 15 of a rolling element 4 different cross-sectional geometries.
  • a cross-section through the circumferential surface 16 of a rolling element in its two hemispheres 15 each shows an arc-shaped course with preferably identical radii of curvature rr
  • Cross-sectional curvature centers 17, 18 of the two hemispheres do not coincide, however, but are slightly offset from one another in the axial direction of the barrel bearing 1, namely towards the relevant rolling element hemisphere 15 or end face 14.
  • osculation factors k A , k 1 should preferably be on the order of 0.01 to 0.1, in particular between 0.02 and 0.05. Since the cross-sectional center of curvature 19 of the running surface 6 of the outer ring 2 lies on the axis of rotation or symmetry 20 thereof, namely on the central base plane thereof, the cross-sectional center of curvature 17, 18 of the lateral surfaces 16 of both rolling element hemispheres 15 lie by y from the axis of rotation according to FIG. 3 20 offset radially outwards and offset by x / 2 relative to the central base plane to the relevant end face 14.
  • FIGS. 6 and 7 Two possible groove shapes are shown in FIGS. 6 and 7:
  • the groove 7 has flat side surfaces 21, as are produced, for example, by a straight recess.
  • the width N of the groove 7 is approximately constant.
  • the groove base 13 follows a cylindrical outer surface with the radius of curvature ⁇ n.
  • the transition regions between the groove base 13 and the groove side surfaces 21, between the latter and the outer surfaces 16 and between the outer surfaces 16 and end surfaces 14 are rounded in order to avoid burrs and notch effects.
  • the embodiment of a rolling element 22 according to FIG. 7 differs from that according to FIG. 6 only in that the groove side surfaces 23 run along conical lateral surfaces. These are very blunt cones with preferably identical opening angles a of almost 180 ° in each case (for example 170 ° to 179 °).
  • the groove side surfaces 23 therefore diverge towards each other at an angle ⁇ , viewed outward from the axis of symmetry 24 along a radial plane.
  • the (axial) width of the groove base is again b N and its radius of curvature ⁇ N. This embodiment tolerates larger set angles of the barrel-shaped rolling elements 22 with the same values for b and d and therefore leads to less wear under corresponding stresses.
  • a section of the cage 5 is shown in Fig. 8.
  • Recesses in the shape of a circular arc can be seen with a constant radius of curvature rs. Rs> ⁇ and d ⁇ bN ensure that the rolling elements 4 rotate as smoothly as possible with respect to the cage 5.
  • the circumference 25 of a recess 9 extends over an arc of more than 180 °, for example between 200 ° and 230 °, in particular from 210 ° to 220 °, so that the end regions 26 of the Recess circumference 25 converge towards one another in the viewing direction from the inner circumference 10 of the cage 5 to its outer circumference 8.
  • the minimum distance between the end regions 26 is smaller than the diameter (2 * ⁇ N) of the rolling elements 4 in the area of the groove base 13, so that the rolling elements 4 are encompassed in a form-fitting manner.
  • the former would therefore have to be pulled outwards with a large force in order (temporarily) to push the end regions 26 of the recess periphery 25 apart.
  • the end regions 26 thus form snap noses for snapping the rolling elements 4.
  • the modified disc cage 27 from FIG. 9 has a similar effect. It differs from the cage 5 according to FIG. 8 only in that the recess circumference 28, which has the radius of curvature rs in its area 29 facing the inside 10 of the cage 27, approximately has areas 30 which are flattened (approximately parallel to one another) at the level of its radial course (With a length I of, for example, rs / 3), to which the actual snap noses 31, which are in turn curved and converge towards one another, then follow, the radius of curvature of which can be selected to match r s .
  • This embodiment tolerates larger radial displacements of the cage 27 with respect to the rolling elements 4, which can occur, for example, as a result of strong temperature fluctuations, but without the rolling elements 4 being able to come loose when the outer ring 2 is tilted strongly.
  • the edges of the circumference of the recess are also rounded 32 in cross section.

Landscapes

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

Abstract

L'invention concerne un roulement à galets-tonneaux qui comprend une bague extérieure et une bague intérieure entre lesquelles se trouve au moins une rangée de corps de roulement en forme de tonneaux. Le roulement selon l'invention comprend également au moins une cage en forme de disque qui tourne avec les corps de roulement, qui s'engrène dans une rainure périphérique des corps de roulement d'une rangée et qui présente, sur sa périphérie extérieure, un nombre d'évidements correspondant au nombre des corps de roulement d'une rangée. La surface de roulement totale de la bague intérieure a une section concave sur toute la longueur axiale d'un corps de roulement et la plus petite distance entre les deux côtés d'un évidement de la cage en forme de disque, dans la zone de la périphérie extérieure de cette dernière, est inférieure au diamètre d'un corps de roulement dans la zone de la rainure périphérique de ce corps de roulement.
EP03812127A 2002-11-30 2003-11-21 Roulement a galets-tonneaux Withdrawn EP1565664A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10255992A DE10255992A1 (de) 2002-11-30 2002-11-30 Tonnenlager
DE10255992 2002-11-30
PCT/DE2003/003868 WO2004051099A2 (fr) 2002-11-30 2003-11-21 Roulement a galets-tonneaux

Publications (1)

Publication Number Publication Date
EP1565664A2 true EP1565664A2 (fr) 2005-08-24

Family

ID=32308875

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03812127A Withdrawn EP1565664A2 (fr) 2002-11-30 2003-11-21 Roulement a galets-tonneaux

Country Status (5)

Country Link
US (1) US7338213B2 (fr)
EP (1) EP1565664A2 (fr)
JP (1) JP2006508312A (fr)
DE (1) DE10255992A1 (fr)
WO (1) WO2004051099A2 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006044271A1 (de) 2006-09-20 2008-04-03 Schaeffler Kg Scheibenkäfig sowie Tonnenlager mit Scheibenkäfig
DE202009018813U1 (de) * 2009-11-06 2013-08-26 Neo-Plastic Dr. Doetsch Diespeck Gmbh Wälzkörper-Käfigring
CN103047279A (zh) * 2012-10-25 2013-04-17 王守彬 一种静音模糊调心滚子轴承
CN103047274A (zh) * 2012-10-25 2013-04-17 王守彬 一种静音顶锥滚子轴承
CN103671507A (zh) * 2013-12-31 2014-03-26 李岚 一种高承载调心滚子轴承
EP3314135B1 (fr) * 2015-06-26 2019-08-28 Forum US, Inc. Cage pour roulement à rotule à double rangée de rouleaux
DE102016201776B4 (de) * 2016-02-05 2017-10-05 Schaeffler Technologies AG & Co. KG Laufrolle für ein Podegelenk
CN105976017A (zh) * 2016-04-29 2016-09-28 新昌县羽林街道宏博机械厂 一种轴承检测计数装置
JP7369330B2 (ja) * 2022-03-11 2023-10-26 泰一 岡田 軸受の製造方法

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US574988A (en) * 1897-01-12 Roller-bearing
US1454057A (en) * 1923-05-08 Julius kuttnee
US137415A (en) * 1873-04-01 Improvement in anti-frictional bushings
US1018324A (en) * 1908-09-10 1912-02-20 Daniel E Kempster Antifriction-bearing.
DE391950C (de) * 1922-06-24 1924-03-17 Philipp Mutter Waelzlager
US1806279A (en) * 1928-09-17 1931-05-19 Augustus D Booth Roller bearing
US2016526A (en) * 1934-05-22 1935-10-08 Miller S Tyson Roller bearing
DE663179C (de) * 1936-08-25 1938-07-30 Gustav Siegener Selbst einstellendes Pendelrollenlager
US4010527A (en) * 1976-05-06 1977-03-08 Swanson Kenneth P Textile drafting roll assembly
CA2149107A1 (fr) * 1994-05-27 1995-11-28 Charles J. Lob Rea a roulements a rouleaux
US6247847B1 (en) * 1999-01-30 2001-06-19 Harken, Inc. Flexible bearing cage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004051099A2 *

Also Published As

Publication number Publication date
US7338213B2 (en) 2008-03-04
WO2004051099A3 (fr) 2004-09-16
DE10255992A1 (de) 2004-06-09
WO2004051099A2 (fr) 2004-06-17
JP2006508312A (ja) 2006-03-09
US20060165333A1 (en) 2006-07-27

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