EP2126386A1 - Ensemble palier - Google Patents

Ensemble palier

Info

Publication number
EP2126386A1
EP2126386A1 EP07846346A EP07846346A EP2126386A1 EP 2126386 A1 EP2126386 A1 EP 2126386A1 EP 07846346 A EP07846346 A EP 07846346A EP 07846346 A EP07846346 A EP 07846346A EP 2126386 A1 EP2126386 A1 EP 2126386A1
Authority
EP
European Patent Office
Prior art keywords
bearing
ring
axial
angular contact
contact ball
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Withdrawn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
EP07846346A
Other languages
German (de)
English (en)
Inventor
Timur Dizlek
Josef Zylla
Arnd Heeg
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler KG
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 Schaeffler KG filed Critical Schaeffler KG
Publication of EP2126386A1 publication Critical patent/EP2126386A1/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Withdrawn legal-status Critical Current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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/49—Bearings with both balls and 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing

Definitions

  • the invention relates to a bearing arrangement for an axially exactly in a component to be guided shaft or the like, the conditions in the two Axialrichtun- different loads and / or long, comprising a substantially designed for receiving axial forces angular contact ball bearing assembly and a substantially for the inclusion of radial forces designed cylindrical roller bearing assembly.
  • a bearing arrangement is already known from DE 103 57 109 A1, in which an angular contact ball bearing arrangement is provided for receiving axial forces and a cylindrical roller bearing arrangement is provided for receiving radial forces.
  • the angular contact ball bearing assembly is designed as a so-called four-point bearing, which can and should absorb axial forces in both axial directions.
  • the angular ball bearing arrangement on the one hand and the cylindrical roller bearing arrangement on the other hand are structurally separated from one another in such a way that the former absorbs only axial forces and the latter only radial forces.
  • a general disadvantage of four-point bearings is seen in the fact that they are available by default only with a pressure angle of about 35 °, so that when acting on the bearing axial force a relatively large radial force component occurs only the rolling friction of the bearing and thus its wear increased, without bringing a benefit.
  • four-point bearings are relatively expensive.
  • the invention has for its object to provide a bearing assembly of the type mentioned in the O-term of claim 1, which is inexpensive to manufacture, has a relatively small length and which is better adapted than the known bearing assemblies to the particular operating conditions, in which in addition to acting in an axial direction main operating force generally occurs in terms of the duration and the size of lower opposing axial force.
  • the invention is based on the finding that the property of cylindrical roller bearings, even to a certain extent to be able to absorb axial forces, can be used to accommodate the lower in terms of time and size back pressure forces, so that the angular contact ball bearing assembly relieved of this task or can be released.
  • the invention is therefore based on a bearing arrangement for an axially exactly in a component to be guided shaft or the like, which is loaded in different degrees in the two axial directions, comprising a substantially designed for the absorption of axial forces Schrägkugellageran- order and a substantially for the Recording of radial forces designed cylindrical roller bearing assembly.
  • the angular contact ball bearing assembly as a single row, for recording designed the stronger axial main operating force designed angular contact ball bearings
  • the cylindrical roller bearing assembly is designed as a single row, designed for receiving the weaker axial back pressure force and the radial force designed as a support bearing cylindrical roller bearing.
  • a single-row angular contact ball bearing is sufficient for receiving the main operating force.
  • Such angular contact ball bearings represent commercially available, inexpensive machine elements that are available in different configurations.
  • the lower in terms of their duration and size back pressure forces can be easily absorbed by a correspondingly modified cylindrical roller bearing, which means a slight increase in construction costs for the cylindrical roller bearing, but this is more than compensated by the simplification of the angular contact ball bearing assembly.
  • one, namely the radially outer or the radially inner of the two bearing rings is formed in one piece and fixed in both axial directions relative to the associated component. It can thus transmit both the axial main operating force introduced via the angular contact ball bearing and the axial return pressure force introduced via the cylindrical roller bearing to the associated component.
  • the respective other bearing ring is preferably formed from two individual rings, each of which is fixed in one of the axial force to be transmitted corresponding axial direction relative to the associated component (shaft).
  • a further preferred variant of the invention includes a unilaterally defined axial ring projection between the inner and outer ring, preferably on the angular contact ball bearing, which allows a defined axial shaft position relative to the housing relative.
  • the radially outer bearing ring is integrally formed, while the inner bearing ring consists of two individual rings.
  • the inner bearing ring is in one piece and the outer bearing ring consists of two individual rings.
  • the outer or the inner bearing ring consists of two individual rings fixedly connected to one another, wherein these two individual rings may each have an annular groove in the region of the mutually facing end faces into which the two individual rings are fixed and flush with the surface without axial play connecting clip is inserted.
  • Another embodiment provides a one-piece inner ring with a separate flanged wheel.
  • the two other bearing rings are also formed as individual rings and axially adjacent to the joint B.
  • the angular contact ball bearing is not loaded by radial forces is provided according to a further embodiment of the invention that the bearing bore diameter of the angular contact ball bearing associated with individual inner ring defined larger than the diameter of the associated shaft portion.
  • the outer diameter of the individual outer ring assigned to the angular contact ball bearing is a defined distance A forming smaller than the diameter of the associated section of the housing.
  • the difference or the distance A between the bearing bore diameter and the outside diameter the individual ring of the angular contact ball bearing and the associated portion of the shaft or the hollow shaft is greater than or equal to twice the value of the radial clearance of the cylindrical roller bearing.
  • a precise axial positioning of the second single ring relative to the first single ring is achieved in that it is measured after a first preliminary assembly of the second single ring, and that optionally an axial oversize or undersize of the second single ring is compensated by material removal or Beilegen a spacer ring ,
  • the rolling elements of the angular contact ball bearing and / or the cylindrical roller bearing are preferably guided in a cage to exclude a friction of the rolling elements to each other.
  • a bearing assembly may be provided in a bearing assembly according to the invention that is formed on the side facing away from the angular contact ball end of the one-piece inner ring radially outwardly an annular groove into which a locking ring is inserted.
  • This securing ring preferably acts as a disassembly safeguard so that the bearing arrangement can be manufactured by a bearing manufacturer as a ready-to-install bearing unit and can be disposed of as such.
  • the retaining ring preferably holds such a distance C to the adjacent cylindrical rollers of the cylindrical roller bearing, that the locking ring and the cylindrical rollers do not touch.
  • the one-piece inner ring or outer ring of the cylindrical roller bearing may be provided at its end facing away from the angular contact ball bearing with a flange, which prevents loss of this one-piece bearing ring from the bearing assembly.
  • the two individual rings of the two-part inner ring as already described after assembly of the cylindrical rolling elements by means of the clamp are firmly connected. Further, it is considered advantageous if it is provided that the two individual rings in the region of the mutually facing end faces radially outwardly each have an axial groove into which a two individual rings against relative rotation is used protecting each other locking element.
  • the locking element may be formed as a feather key which is glued into the axial groove of one of the two individual rings and protrudes axially for engagement in the associated axial groove of the other single ring from the first-mentioned axial groove.
  • the individual ring of the angular contact ball bearing and / or the single ring of the cylindrical roller bearing has at least one radial groove on its end face facing the respective other individual ring, in which lubricant can be taken up and forwarded.
  • FIG. 1 shows a longitudinal section through a bearing arrangement with an angular contact ball bearing and a cylindrical roller bearing in O arrangement, which supports a central shaft in a housing
  • Fig. 2 is a longitudinal section through a bearing assembly similar to FIG. 1, but in an X-arrangement, which supports a central shaft in a housing, and
  • Fig. 3 shows a bearing assembly in O arrangement similar to that in Fig. 1, but with an inner ring consisting of two firmly connected individual rings or of a ring and an axially flanged flange. Detailed description of the drawing
  • the two bearings have a common one-piece outer ring 8, on the inner surface of the raceways for the rolling elements of these two bearings, ie the balls 10 of the angular contact ball bearing 4 and Cylindrical rollers 12 of the cylindrical roller bearing 6, are formed.
  • the inner bearing ring of the bearing assembly 2 is divided into a first single ring 14 for the angular contact ball bearing 4 and a second single ring 16 for the cylindrical roller bearing. 6
  • the bearing assembly 2 serves, for example, to radially and axially very precisely in a housing 22 a shaft 18, which must receive a larger axial force in the direction of the arrow 20 and occasionally and for a shorter period of time a smaller back pressure force in the opposite direction respectively.
  • the main force occurring during operation is transmitted from the shaft 18 via the first single ring 14, the balls 10 and the outer ring 8 to the housing 22.
  • the outer ring 8 must therefore be fixed against displacement in the direction of the arrow 20 in the housing 22, while the first single ring 14 is fixed against relative displacement on the shaft 18 against the direction of the arrow, so that the main force from the shaft 18 to the first Single ring 14 can be transferred.
  • the back pressure force acting in the direction opposite to the arrow 20 is correspondingly transmitted from the shaft 18 via the second individual ring 16 equipped with a radially outwardly directed rim 24, the cylindrical rollers 12 and the outer ring 8 with a radially inward-pointing rim 26 transferred to the housing 22, so that the outer ring 8 must be fixed in the direction opposite to the arrow 20 in the housing 22.
  • the diameter of the shaft 18 is smaller than the bore diameter of the individual ring 14, at least in the region receiving the first individual ring 14.
  • the axial fixation of the first individual ring 14 is therefore achieved, for example, by a securing ring 32 inserted into a shaft groove guaranteed.
  • the axial position of its outer end face is measured after a first preliminary mounting of the second individual ring 16 and an optionally present axial over- or undersize ⁇ X by a corresponding Material removal or Beilegen a spacer compensated.
  • the reference numerals 28 and 30 cages for the balls 10 and the cylindrical rollers 12 are referred to, which guide these rolling elements and prevent friction of the same to each other.
  • Fig. 2 shows a second embodiment of a bearing assembly 2 'according to the invention, in which the angular contact ball bearing 4 has an X-arrangement and in which the bearing assembly 2 ' supports a shaft 22 ' in a housing 18'.
  • a one-piece inner ring 34 is used for the rolling elements 10 and 12 of the angular contact ball bearing 4 and the cylindrical roller bearing 6, while the outer rings 36 and 38 are formed as individual rings.
  • the outer peripheral surface of the individual ring 36 of the angular contact ball bearing 4 has a distance A from the inner circumferential surface of the housing 18 ' , while the single ring 38 of the cylindrical roller bearing 6 with the inner circumferential surface of the housing 18 ' non-positively connected is.
  • Fig. 2 also shows that the single ring 38 of the cylindrical roller bearing 6 has radially inwardly facing ribs 46 and 48, between which the cylindrical rolling elements 12 are arranged.
  • a retaining ring 52 is inserted, which serves as a dismantling safeguard for the finished bearing assembly 2 ' .
  • the distance C of the securing ring 52 to the adjacent cylindrical rollers 12 is preferably selected so that they do not touch each other.
  • FIG. 3 shows a bearing assembly 2 " with an O-arrangement of the angular contact ball bearing 4.
  • the bearing assembly 2 " as in Fig. 1 the storage of a central shaft 18 in one rotatably fixed housing 22.
  • the outer rings of the angular contact ball bearing 4 and the cylindrical roller bearing 6 lie against each other at the joint B and are formed as individual rings 36, 38, of which the single ring 38 of the cylindrical roller bearing 6 is positively and non-positively received in the housing 22, while the single ring 36 of the angular contact ball bearing 4 has such an outer diameter that a distance A between the outer circumferential surface of this single ring 36 and the inner circumferential surface of the housing 22 is determined. This distance A is so great that, taking into account the radial clearance of the cylindrical roller bearing 6, there is no radial transfer of force from the shaft 18 via the angular contact ball bearing 4 into the housing 22.
  • FIG. 3 is also in the bearing assembly 2 "provides that the two outer rings 36 and 38 against each other against rotation. For this purpose, this in the region of its opposite end faces of axial grooves 40 and 42, respectively, in the as a locking means such as a key 44 is inserted.
  • a provided with the reference numeral 54 radial groove in the inner end face of the individual ring 36 of the angular contact ball bearing 4 is formed, which can be used for grease relubrication.
  • the bearing assembly 2 " according to FIG. 3 is characterized in that the radially inner bearing ring 56 consists of two firmly interconnected individual rings 56 ' and 56 " , each having an annular groove 62, 64 in the region of their facing end faces, in the one the two individual rings 56 ' , 56 " fixed without axial play and radially flush inside binding clip 60 is inserted.
  • both inner rings 56 ' and 56 " can be produced and assembled individually so that they are firmly connected to each other only in a subsequent manufacturing step by means of the clamp 60.
  • FIG. 3 shows that the two-part inner ring 56 (56 ' , 56 " ) is firmly connected at its cylindrical roller side free end with a flanged wheel 58.
  • This flanged wheel 58 serves on the one hand as captive and on the other hand forwards axial forces, which counter to the main load direction 20 of the shaft 18 are carried in the bearing assembly 2 " .
  • These comparatively small axial forces are then conducted via the cylindrical rollers 12 and the rim 46 of the radially outer individual ring 38 of the cylindrical roller bearing 6 into the housing 22.
  • the one-piece inner ring 56 (without grooves 62, 64 and without clip 60) can be realized with a loose flange 58.
  • an axial clamping of one-piece inner ring 56 plus loose flanged wheel 58 when mounted on the shaft is required

Landscapes

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

Abstract

Ensemble palier (2, 2', 2") pour un arbre (18, 18') ou analogue à monter de manière axiale précise dans une pièce structurale, par exemple dans un carter (22), ledit arbre étant sollicité différemment dans les deux sens axiaux pour ce qui est de l'intensité et / ou de la durée. Ledit ensemble palier (2) comporte un roulement à billes à portée oblique (4) à une seule rangée et un roulement à rouleaux cylindriques (6) à une seule rangée. Le roulement à billes à portée oblique (4) est conçu pour absorber la charge axiale principale (20) la plus élevée se produisant lors de l'utilisation, tandis que la force de retour plus faible agissant dans le sens opposé et les forces radiales sont absorbées par le roulement à rouleaux cylindriques (6). De cette manière, la complexité technique requise pour l'absorption de la force de retour faible et se produisant en général sur une courte durée peut être maintenue à un minimum. En outre, il est possible de régler préalablement un jeu axial défini dans l'unité ainsi que de régler une projection latérale définie de bague entre la bague externe et la bague interne.
EP07846346A 2007-02-01 2007-11-17 Ensemble palier Withdrawn EP2126386A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007004998A DE102007004998A1 (de) 2007-02-01 2007-02-01 Drehlageranordnung
PCT/DE2007/001685 WO2008092415A1 (fr) 2007-02-01 2007-09-18 Ensemble palier de pivotement
PCT/DE2007/002083 WO2008092416A1 (fr) 2007-02-01 2007-11-17 Ensemble palier

Publications (1)

Publication Number Publication Date
EP2126386A1 true EP2126386A1 (fr) 2009-12-02

Family

ID=39496024

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07846346A Withdrawn EP2126386A1 (fr) 2007-02-01 2007-11-17 Ensemble palier

Country Status (6)

Country Link
US (1) US20100061672A1 (fr)
EP (1) EP2126386A1 (fr)
JP (1) JP2010518324A (fr)
KR (1) KR20090104132A (fr)
DE (1) DE102007004998A1 (fr)
WO (2) WO2008092415A1 (fr)

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JP6171444B2 (ja) * 2013-03-21 2017-08-02 株式会社ジェイテクト 転がり軸受装置及び車両用ピニオン軸支持装置
CN103352916B (zh) * 2013-06-28 2015-07-01 沈阳罕王精密轴承有限公司 一种圆柱与钢球滚动体交叉分布的交叉滚子轴承
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CN106595427A (zh) * 2016-12-15 2017-04-26 中航工业哈尔滨轴承有限公司 双内圈双列角接触球轴承的内圈组配凸出量检测方法
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Also Published As

Publication number Publication date
DE102007004998A1 (de) 2008-08-07
JP2010518324A (ja) 2010-05-27
KR20090104132A (ko) 2009-10-05
WO2008092415A1 (fr) 2008-08-07
WO2008092416A1 (fr) 2008-08-07
US20100061672A1 (en) 2010-03-11

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