EP2016300A2 - Joint tournant à palier à roulement - Google Patents

Joint tournant à palier à roulement

Info

Publication number
EP2016300A2
EP2016300A2 EP07727787A EP07727787A EP2016300A2 EP 2016300 A2 EP2016300 A2 EP 2016300A2 EP 07727787 A EP07727787 A EP 07727787A EP 07727787 A EP07727787 A EP 07727787A EP 2016300 A2 EP2016300 A2 EP 2016300A2
Authority
EP
European Patent Office
Prior art keywords
raceway
rolling bearing
rolling
slewing ring
bearing
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Withdrawn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
EP07727787A
Other languages
German (de)
English (en)
Inventor
Peter Meier
Frank Neubert
Jürgen Stölzle
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 EP2016300A2 publication Critical patent/EP2016300A2/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Withdrawn legal-status Critical Current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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • 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
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F16C19/166—Four-point-contact ball bearings
    • 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
    • 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

Definitions

  • the invention relates to a rolling bearing rotary joint, consisting of two concentric nested races between which rolling on associated raceways rolling elements, wherein at least one of the races is designed to be resilient.
  • Rolling bearing slewing rings have been known for a long time. According to the textbook “Die Wälzlagerpraxis", suverlage GmbH, Mainz, 1995, such bearings rotary joints are used as a pivot bearing for the support of excavators, cranes or in vehicle for articulated buses or trams, ie, in applications in which in a limited space high loads The main fields of application of such rotary joints are therefore characterized by a low peripheral speed but with very high tilting moments and high axial and radial forces
  • Such rolling bearing slewing rings are known for example from DE 37 25 972 A1, DE 195 10 182 A1, DE 196 34 877 A1 and DE 197 28 606 A1.
  • rolling bearing rotary joints are used, for example in computer tomography.
  • the rolling bearing slewing connection can be found in similar X-ray machines for Checking luggage in the security area, eg at airports.
  • completely different demands are made on the slewing connection in the medical field and also in luggage scanners:
  • the loads to be absorbed are very small compared to the bearing diameter, i. low tilting moments, low radial and axial forces.
  • peripheral speeds are very high, for example, speeds of 150 rev / min at a Wälzlger pitch of 1 meter are not uncommon.
  • a measurable running noise with the running noise to be measured as airborne sound, to have a total sound pressure level of not more than 65 dB (A) measured at a distance of 1 meter relative to the rolling bearing axle.
  • the raceway associated with the superstructure and connected to the superstructure is secured so that the attachment permits radial deformation of the raceway in its entirety.
  • this is achieved by the fact that, for the race assigned to the superstructure, centering strips on the inside and outside are present on the uppercarriage, whose arrangement permits the deformation of the race, but limits the extent of its deformation.
  • a second possibility is given by the fact that the race assigned to the uppercarriage has horizontal, groove-like milled cuts which penetrate deeper into the raceway than the ball raceway.
  • the invention is therefore an object of the invention to provide a rolling bearing slewing connection, which meets the aforementioned requirements.
  • the weakening of the race in the manner according to the invention causes it in the raceway area receives a resilient effect that absorbs a portion of the bias. This ensures that in addition to the particularly low noise at high revolutions and a long life of the rolling bearing slewing connection is possible.
  • the race when the race consists of a connected to a connecting structure first base part and a second branching from this in the axial direction, the raceway-bearing part, wherein the radial thickness of the base part is greater than the radial thickness of is the track-carrying part.
  • the part bearing the raceway can have a constant radial thickness or a decreasing radial thickness in the direction of the raceway when viewed in the axial direction.
  • the ratio B1: B2> 1, 5: 1 ensures that a uniform distribution of the stress is present within the race-bearing part. It is realized in an approximately uniform spring characteristic, so that the raceway-carrying part of the race is elastically deformed over its entire axial length and not only in the area where it branches off from the base part.
  • the magnitude of the applied bias voltage is also set via the ratio B1: H ⁇ 1: 2, whereby the bias voltage decreases with an increasing axial length H of the race-bearing part.
  • a further possibility for influencing the pretensioning of the flexible race is its hardening treatment according to claim 7. Under the same geometric conditions, a hardened race will have a larger elastic range than an unhardened race. It is obvious that by improving the hardness values of both races a long life, up to the fatigue strength is achieved.
  • the rolling bearing rotary connection is designed as a four-point ball bearing.
  • Four-point ball bearings have two circular arc-shaped raceways on the inner and on the outer race, whose centers of curvature are offset from one another in such a way that the balls touch the races at four points under radial load.
  • the advantage of the four-point bearing is that it can absorb axial forces in both directions and tilting moments due to mutually acting pressure angle.
  • the ratio of a pitch circle diameter to a diameter of each individual rolling element is greater than 30: 1.
  • the imaginary circle which is arranged concentrically to the axis of rotation of the rotary joint and the aligned parallel to the axis of rotation center axes of the Rolling element cuts.
  • the central axes are in cylindrical rolling elements, the axes of rotation and symmetry and imaginary spheres, by the spherical center and parallel to the axis of rotation of the rotary connection requiring axes.
  • Such a bearing is known to those skilled in the art as so-called.
  • the rolling elements are made of ceramic.
  • hot-pressed silicon nitride which has low dry friction coefficients compared to metallic materials, is suitable, so that the rotary joint can also be operated with lubricant.
  • rolling elements made of ceramic also give a lower centrifugal force.
  • ceramic rolling elements make the raceways free of minor impurities that they grind thanks to their hardness.
  • Raceway bearing part of the raceway and
  • FIG. 3 shows the force acting on the bearing balls as a function of
  • the rolling bearing rotary joint 1 shown in Figure 1 consists of the outer race 2, which is provided with mounting holes 3, 4 for connection to a connecting structure, not shown.
  • the seal 5 is arranged, which is formed in the embodiment as a sliding seal whose unspecified sealing lip on the inner race 6 rests.
  • This is formed in one piece and consists of the base part 7, which has at least one mounting hole 8 for connection to a connecting structure, also not shown. From the base part 7 branches off parallel to the bearing axis 9 of the raceway 10 bearing part 11 of the inner race.
  • the associated second raceway 12 is provided by the outer race 2.
  • On the raceways 10, 12 roll bearing balls 13, which are guided in a cage 14.
  • the bearing balls 13 have both on the outer race 2 and on the inner race 6 each two non-designated points of contact, ie, the rolling bearing rotary joint 1 is formed as a four-point ball bearing.
  • the rolling bearing rotary joint 1 is formed as a four-point ball bearing.
  • the outer race 2 has at its left-hand end on the radially inwardly directed projection 16 which covers the inner race 6 partially. In this way, a radially extending gap 17 is formed between the two running rings 2, 6, which seals the roller bearing rotary joint 1, ie acts as a gap seal.
  • the part 11 of the inner bearing ring 6 carrying the raceway 10 has a radial thickness in the branch region from the base part 7, which is denoted by B1. This steadily decreases in the axial direction until, in the region of the raceway 10, it assumes the value indicated by B2.
  • the geometrically measured ratio B1: B2 is approximately 2.15: 1. It can be assumed that with an increasing ratio between B1 and B2 with constant axial length H, the bias voltage increases. As can also be seen, the ratio of the axial length H of the raceway 10-carrying part 11 to its radial thickness B1 in the exemplary embodiment is approximately 1: 2.35. From this it is derived that due to the leverage effect with increasing axial length H, the bias acting on the bearing balls 13 becomes lower.
  • the lower curve which represents a roller bearing slewing compound, which is biased at 10 microns, shows that the bearing balls are biased in a complete revolution only in an angular range between 90 ° and 270 °. In the other half of the revolution there is no bias, so that the bearing balls are subject to a slip during a load change, which leads to bearing noise.
  • the upper curve which realizes a preload of 30 ⁇ m for the same antifriction bearing, reveals that in this case the bearing balls are preloaded from 0 ° to 360 ° in the entire angular range and thus no slippage in the load change region can occur.

Landscapes

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

Abstract

L'invention concerne un joint tournant à palier à roulement (1) constitué de deux bagues de roulement (2, 6) disposées concentriquement l'une à l'intérieur de l'autre, bagues entre lesquelles des corps roulants (13) roulent sur des chemins de roulement associés (12, 10), une des deux bagues de roulement (2, 6) étant flexible. L'invention se caractérise en ce que, vue en coupe longitudinale, la bague de roulement flexible (6) est conçue en dimension réduite, de façon à permettre une déformation élastique radiale d'une ampleur telle que les corps roulants (13) sont précontraints dans toute la zone périphérique à l'état chargé.
EP07727787A 2006-04-29 2007-04-04 Joint tournant à palier à roulement Withdrawn EP2016300A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006019982A DE102006019982A1 (de) 2006-04-29 2006-04-29 Wälzlager-Drehverbindung
PCT/EP2007/053318 WO2007125007A2 (fr) 2006-04-29 2007-04-04 Joint tournant à palier à roulement

Publications (1)

Publication Number Publication Date
EP2016300A2 true EP2016300A2 (fr) 2009-01-21

Family

ID=38330000

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07727787A Withdrawn EP2016300A2 (fr) 2006-04-29 2007-04-04 Joint tournant à palier à roulement

Country Status (4)

Country Link
US (1) US8092094B2 (fr)
EP (1) EP2016300A2 (fr)
DE (1) DE102006019982A1 (fr)
WO (1) WO2007125007A2 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008035357A1 (de) 2008-07-29 2010-02-04 Schaeffler Kg Wälzgelagerte Drehverbindung
DE102009049557A1 (de) 2009-10-16 2011-04-21 Schaeffler Technologies Gmbh & Co. Kg Kreuzrollenlager
WO2013093691A1 (fr) * 2011-12-20 2013-06-27 Koninklijke Philips Electronics N.V. Portique de système d'imagerie
DE102014205097A1 (de) 2014-03-19 2015-09-24 Schaeffler Technologies AG & Co. KG Rundtischlageranordnung
US11515883B2 (en) 2020-11-20 2022-11-29 AyDeeKay LLC Configuration of ADC data rates across multiple physical channels
CN113700734B (zh) * 2021-08-25 2023-02-03 常熟得美零部件有限公司 农业大棚覆盖物收放机的轮毂式移动导向装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3605812A1 (de) * 1986-02-22 1987-08-27 Kugelfischer G Schaefer & Co Mit hilfe zweier axialschieber herstellbarer kaefig fuer kegelrollenlager

Family Cites Families (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7317997U (de) * 1974-01-24 Schaefer G & Co Wälzlager
US3097898A (en) * 1960-07-29 1963-07-16 George F Mcmurray Anti-friction bearing
DE1228465B (de) * 1962-10-25 1966-11-10 Erwin Bargmann Zwischen dem Oberwagen und dem Unterteil von Kranen und Baggern angeordnete einreihige, mit senkrechten Trennfugen versehene Kugeldrehverbindung
US3504955A (en) * 1966-05-12 1970-04-07 Trw Inc Bearing with hollow rings
US3513480A (en) * 1967-04-26 1970-05-19 North American Rockwell Low stress bearing
CH529938A (de) * 1968-09-03 1972-10-31 North American Rockwell Kugellager
FR1589720A (fr) * 1968-09-05 1970-04-06
FR2224014A5 (fr) * 1973-03-26 1974-10-25 Roulements Soc Nouvelle
US3940200A (en) * 1975-03-04 1976-02-24 Schreffler Robert Z Electrical conductor arrangement including flexible race construction
DE2511120A1 (de) * 1975-03-14 1976-09-30 Teldix Gmbh Praezisions-waelzlager
JPS5740117A (en) * 1980-08-19 1982-03-05 Ntn Toyo Bearing Co Ltd Rotary ring
US4362344A (en) * 1981-08-03 1982-12-07 General Motors Corporation Sealed ball bearing with stamped races
DE3225979A1 (de) * 1982-07-10 1984-01-12 Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt Rollenlager mit korrigierter lastverteilung
US4530609A (en) * 1983-08-03 1985-07-23 Frocemco, Inc. Conveyor roll bearing
JPS60208626A (ja) * 1984-03-30 1985-10-21 Koyo Seiko Co Ltd 腐食環境下で使用する回転部材支持装置
US5211273A (en) * 1986-01-22 1993-05-18 Hybo Science, Inc. Axial thrust clutch/bearing/freewheel
EP0258845A3 (fr) * 1986-08-29 1988-08-17 Kabushiki Kaisha Nagano Keiki Seisakusho Palier céramique
DE3725972C2 (de) * 1987-08-05 1998-09-10 Schaeffler Waelzlager Ohg Wälzlager-Drehverbindung
JP2681182B2 (ja) * 1987-12-15 1997-11-26 光洋精工株式会社 玉軸受
DE3926577A1 (de) * 1989-08-11 1991-02-14 Leybold Ag Vakuumpumpe mit einem rotor und mit unter vakuum betriebenen rotorlagerungen
JP2913061B2 (ja) * 1990-03-05 1999-06-28 光洋精工株式会社 真空用玉軸受およびそれを用いたターボ分子ポンプ
DE9411375U1 (de) * 1994-07-14 1994-09-08 INA Wälzlager Schaeffler KG, 91074 Herzogenaurach Wälzlager-Drehverbindung
JPH09209102A (ja) * 1996-02-01 1997-08-12 Koyo Seiko Co Ltd 溶融めっき槽用ラジアルころ軸受
SE514372C2 (sv) * 1996-03-07 2001-02-19 Skf Nova Ab Smord rullningskontaktanordning, sätt och komposition för smörjning av en rullningskontaktanordning samt en keramisk rullkropp
DE19612571A1 (de) * 1996-03-29 1997-10-02 Fag Aircraft Gmbh Käfigloses Wälzlager
DE19634877A1 (de) * 1996-08-29 1998-03-05 Schaeffler Waelzlager Kg Wälzlager-Drehverbindung
DE19728606A1 (de) * 1997-07-04 1999-01-07 Schaeffler Waelzlager Ohg Schmiereinrichtung für eine Wälzlagerdrehverbindung
DE19729450C2 (de) * 1997-07-10 1999-12-09 Fag Aircraft Gmbh Wälzlager, insbesondere Notlager für magnetisch gelagerte Vakuumpumpen
JPH11141544A (ja) * 1997-11-06 1999-05-25 Okuma Corp アンギュラ玉軸受
JP2000120811A (ja) * 1998-08-12 2000-04-28 Teijin Seiki Co Ltd 撓み噛み合い式減速機
JP2001074053A (ja) * 1999-04-01 2001-03-23 Nsk Ltd 転がり軸受
JP2002188646A (ja) * 2000-12-20 2002-07-05 Nsk Ltd 転がり軸受及び軸受装置
JP4834921B2 (ja) * 2001-01-30 2011-12-14 日本精工株式会社 コンプレッサ用プーリの回転支持装置
GB0107616D0 (en) * 2001-03-27 2001-05-16 Hansen Transmissions Int Profiled roller bearing
JP2003070398A (ja) * 2001-08-31 2003-03-11 Daiwa Seiko Inc 魚釣用スピニングリ−ル
JP2005180636A (ja) * 2003-12-22 2005-07-07 Nsk Ltd 遊星歯車用軸受
DE102004035387B4 (de) * 2004-07-21 2006-11-09 Ab Skf Zylinderrollenlager

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3605812A1 (de) * 1986-02-22 1987-08-27 Kugelfischer G Schaefer & Co Mit hilfe zweier axialschieber herstellbarer kaefig fuer kegelrollenlager

Also Published As

Publication number Publication date
US20090103845A1 (en) 2009-04-23
WO2007125007A2 (fr) 2007-11-08
WO2007125007A3 (fr) 2008-01-10
DE102006019982A1 (de) 2007-10-31
US8092094B2 (en) 2012-01-10

Similar Documents

Publication Publication Date Title
EP2715162B1 (fr) Couronne d'orientation
DE102008049813A1 (de) Drehverbindung, zum Beispiel für eine Windenergieanlage sowie Windenergieanlage mit der Drehverbindung
EP2126387A1 (fr) Palier à rouleaux avec limiteur d'angle de rotation
WO2008055747A1 (fr) Disposition de palier d'un arbre
EP2016300A2 (fr) Joint tournant à palier à roulement
EP3759367A1 (fr) Palier à roulement de grande dimension
DE102010013741A1 (de) Kugellager
EP1972802B1 (fr) Roulement à rouleaux oblique
WO2007000150A1 (fr) Palier a roulement radial, notamment palier a roulement oblique ou cannele a une seule rangee
DE102008046237A1 (de) Reibungsarmes Rollenlager
WO2010037373A1 (fr) Palier à roulement pour rotor destiné à une éolienne, comprenant un palier à rouleaux doté d'au moins deux rangées de rouleaux et de trois bagues de roulement concentriques
DE102008049812A1 (de) Hochbelastbare Drehverbindung
WO2015021983A2 (fr) Palier à roulement sans glissement
DE10311851B4 (de) Schwenklagerung
DE102020105751A1 (de) Wälzlageranordnung
DE102010011462A1 (de) Kegelrollenlager mit profilierter Laufbahn
DE102019124683A1 (de) Wälzlageranordnung
EP3004674B1 (fr) Ensemble palier comportant un palier de retenue
DE102015203414A1 (de) Lageranordnung für einen Abgasturbolader
DE102017202330A1 (de) Radiallageranordnung, insbesondere für eine Ausgleichswelle
DE102020101681A1 (de) Wälzlageranordnung
DE102010007257A1 (de) Drehverbindung für eine Windkraftanlage sowie Windkraftanlage mit der Drehverbindung
DE102020112732A1 (de) Wälzlageranordnung
DE102020117715A1 (de) Wälzlageranordnung
DE102019117888A1 (de) Wälzlageranordnung

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20081201

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR IT NL

17Q First examination report despatched

Effective date: 20091106

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20141101

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230524