[go: up one dir, main page]

WO2009079997A2 - Corps de roulement comprenant un rouleau creux et un corps de surcharge - Google Patents

Corps de roulement comprenant un rouleau creux et un corps de surcharge Download PDF

Info

Publication number
WO2009079997A2
WO2009079997A2 PCT/DE2008/002101 DE2008002101W WO2009079997A2 WO 2009079997 A2 WO2009079997 A2 WO 2009079997A2 DE 2008002101 W DE2008002101 W DE 2008002101W WO 2009079997 A2 WO2009079997 A2 WO 2009079997A2
Authority
WO
WIPO (PCT)
Prior art keywords
hollow
roller
rolling element
rolling
overload
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.)
Ceased
Application number
PCT/DE2008/002101
Other languages
German (de)
English (en)
Other versions
WO2009079997A3 (fr
Inventor
Andreas Ens
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
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 WO2009079997A2 publication Critical patent/WO2009079997A2/fr
Publication of WO2009079997A3 publication Critical patent/WO2009079997A3/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16C33/34—Rollers; Needles
    • 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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/522—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to load on the bearing, e.g. bearings with load sensors or means to protect the bearing against overload
    • 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
    • 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
    • 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
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors

Definitions

  • Rolling element comprising a hollow roller and an overload body
  • the invention relates to a rolling element for a roller bearing comprising a hollow roller with a through hole extending along a rotation axis of the hollow roller and a coaxially arranged in the through hole cylindrical inner body.
  • the invention further relates to a rolling bearing with at least one rolling element according to the invention.
  • a hollow roller according to the invention may be, for example, a hollow cylinder for a cylindrical roller bearing, a hollow taper roller for a tapered roller bearing, a hollow barrel roller for a spherical roller bearing or roller bearing or a hollow ball roller for a ball roller bearing.
  • Rolling elements which have a through bore extending along their axis of rotation are used, for example, in rolling bearings for use when the mass moment of inertia of the bearing set (rolling element and cage) should be reduced.
  • the hollow cylinder as an example of such a rolling element consisting of an open circular cylinder with a central bore, is also used in low-loaded bearings to reduce the risk of slipping.
  • individual conventional, massive rolling elements are replaced by hollow cylinders with a slightly larger outer diameter.
  • the outer diameter of the hollow cylinder is chosen so that they ensure a constant contact with the raceways in the load-free state of the bearing.
  • the hollow cylinder springs with increasing load of the bearing, so that carry the massive rolling elements from a certain load.
  • Such a rolling bearing for reducing the risk of slipping is e.g. from FR 2479 369 A1.
  • hollow rollers Due to the running along its axis of rotation bore, hollow rollers can be easily deform elastically under the action of a radial load. Their radial stiffness, which describes the ratio of radial load and radial, elastic compression, is therefore lower. This property is advantageous when used in roller bearings for slip reduction, since even at a relatively low radial load, the outer diameter of the hollow rollers corresponds to the outer diameter of the solid rollers and thus bear all rolling elements.
  • the reduced radial stiffness can also lead to problems.
  • the hollow rollers subject to constant bending cycle stress under radial load due to their permanent deformation represent potential weak points of the rolling bearing with respect to their load capacity and fatigue strength.
  • the hollow rollers are the cause of a reduced load capacity and a shortened life of the rolling bearing.
  • the damage to the hollow rollers does not occur directly through the radially acting load. So there is no failure due to excessive, radially acting compressive stress in the region of the force application point. Rather, the damage occurs due to the stresses resulting from the deformation of the hollow roller to form an elliptical hollow body.
  • the deformation of the hollow roller generated as in a bending beam tensile and compressive stresses, which in this case run in the tangential direction of the hollow roller.
  • compressive stresses on the inner circumferential surface and tensile stresses on the outer circumferential surface result at the secondary vertices. It was found that the failure of the hollow roller is caused by the tensile stresses on the inner circumferential surfaces, which can lead to cracks during continuous operation of the rolling bearing and finally to the break of the hollow rollers.
  • Overstressing of the hollow rollers arise in particular when the hollow rollers enter the load range of the rolling bearing. Decisive are the high loads distributed on only a few rolling elements and the smaller by the deformation of the raceways distance between the raceways. In contrast to solid rolling elements, which can at least partially press into the raceways in this situation, the hollow rollers are deformed almost exclusively by itself elastically. Less problematic, however, is the deformation of the hollow rollers, which results from the rolling of the hollow rollers between the raceways outside the load zone, since this deformation is less.
  • cylindrical rollers for a roller bearing consist of a core and one or more cladding layers.
  • the cladding layers are firmly joined together with the core and are intended to limit crack propagation starting from centering bores of the core.
  • the invention has for its object to provide a rolling element, which allows in operation a partially elastic deformation, for. can be used in a rolling bearing for slip reduction, but which prevents deformation that can lead to damage.
  • a rolling element according to the preamble of claim 1, with the proviso that the inner body is arranged with a radial clearance fit in the hollow roller, wherein the clearance is selected such that the inner body acts as an overload body by acting at radi- aler load of the rolling element, the hollow roller is supported, before a predetermined material stress of the hollow roller is exceeded.
  • the entry of a predetermined material stress, which is to be avoided, can be shifted to a greater radial load by the inner body supporting the hollow cylinder as an overload body.
  • This inventive support by the overload body starts when the hollow cylinder begins to abut due to its radial compression of the overload body, ie, when viewed in cross-sectional profile of the smallest inner diameter of ellipti- see hollow roller corresponds to the outer diameter of the overload body.
  • the support according to the invention by the overload body causes the radial rigidity of the entire rolling body is increased, as for a agreed radial compression of the rolling element now a load is required, which must overcome both the restoring force of the hollow roller and the restoring force of the overload body.
  • This greater radial rigidity of the rolling element causes a further deformation of the hollow roller occurs with increasing radial load, as would be the case without support and thus lower material stresses due to the bending of the hollow roll occur.
  • the clearance between hollow and overload body is necessary. This clearance ensures that the hollow cylinder can be compressed by a relatively small radial load until it is supported by the overload body, since only the - relatively low - radial rigidity of the hollow roller has an influence.
  • the game In order to allow the inventive support by the overload body before the predetermined material stress is reached, the game must not exceed a maximum throw. This maximum value depends on the size of the specified material stress, the type of material stress selected, the dimensions of the hollow roll and the material of the hollow roll, in particular the elasticity modulus.
  • a radial stiffness of the overload body is selected such that a radial stiffness of the rolling element in the support of the hollow roller by results in the overload body, which excludes a predetermined material stress of the hollow roller at a given radial load of the rolling element.
  • its radial stiffness must not be increased.
  • the radial stiffness of the overload body can be selected accordingly become.
  • the necessary radial rigidity of the rolling element can now be determined taking into account the given load. With knowledge of the radial stiffness of the hollow roller thus results in the required radial stiffness of the overload body.
  • This rigidity can now be achieved by selecting a corresponding material, in particular a corresponding modulus of elasticity, or a corresponding shape, eg a solid cylinder or a hollow cylinder.
  • the material stress is a maximum of the tangential stress.
  • the type of material stress used to select the clearance fit or to determine the radial stiffness of the overload body must reflect the stress critical to the failure of the hollow roll. Although in principle also e.g. the radial compressive stress directly occurring in the force application point due to the radial load is taken into account. However, since the failure of the hollow roller is usually done by the tangential stresses caused by the bending, they are usually to be selected. These should always be lower than the applicable value for the respective material for the bending alternating strength.
  • the material of the overload body and the material of the hollow roller essentially the same modulus of elasticity.
  • the materials can be the same.
  • This solution makes sense on the one hand for economic reasons.
  • the radial stiffness of the entire rolling element according to the invention corresponds to the radial stiffness of the entire rolling element according to the invention, as soon as the support is made by the overload body, substantially the radial stiffness of solid rolling elements of the same material.
  • all rolling elements can have a substantially equal radial stiffness with a corresponding load. This results in a, for example, with respect to the rest quiet advantageous, uniform load distribution over the rolling elements.
  • the hollow roller and the overload body consist of different materials.
  • the hollow roller can be made of conventional rolling steel and the overload body to reduce the mass moment of inertia of the bearing set made of a lighter material.
  • the axial extent of the overload body may be shorter, longer or as long as the axial extent of the through hole of the hollow roller. It is only crucial that the overload body can support the hollow roller in the axial direction over a sufficient distance to prevent overloading damaging deformation of the hollow roller over its entire axial extent. According to a preferred embodiment of the present invention, therefore, the overload body extends substantially over the entire axial extent of the fürgangsboh- tion, since this the function of the overload body is met without the mass moment of inertia of the rolling body unnecessarily increased.
  • the hollow roller is a hollow cylinder, a hollow cone roller, a hollow barrel roller or a hollow ball roller.
  • the rolling element according to the invention can thus be used wherever advantages arise from a rolling element having a bore, ie, for example, in cylindrical roller bearings, in tapered roller bearings. in spherical roller bearings, in roller bearings or in ball roller bearings.
  • the overload body forms a solid cylinder or a solid truncated cone.
  • the advantage here is the great radial stiffness.
  • a solid cylinder is also easy to manufacture.
  • standard rolling bodies e.g. for cylindrical roller bearings.
  • a solid truncated cone can e.g. into a corresponding conical through-hole, for example a hollow cone roller. If the truncated cone has only a small cone angle, it can also be inserted into a cylindrical through-hole, for example in order to obtain a cylindrical through-hole. to support different degrees of tilting of the rolling bearing along the axial extent of the through hole.
  • the overload body forms a hollow cylinder or a hollow cone roller. Due to the lower weight, thus the mass moment of inertia of the complete bearing set can be reduced.
  • At least one further hollow cylinder or a further hollow cone roller and / or a solid cylinder or solid truncated cone is located within the hollow cylinder or the hollow cone roller forming the overload body. It is not necessary for the further elements to be positively connected to the hollow cylinder or the hollow cone roller forming the overload body. Rather, here also a game are present, so that when applying a radial load first, the hollow roller to the overload body forming hollow cylinder or the Hohlkegelrolle applies, and with further increasing radial load of the overload body forming hollow cylinder or the hollow cone roller creates the further elements. According to a preferred embodiment of the present invention, there is a filling material between the hollow roller and the overload body.
  • the filling material may consist of an adhesive which ensures that the overload body is held in the bore of the hollow roller. At the same time, the penetration of contaminants into the gap can be prevented.
  • the filling material can also consist of lubricant for minimizing the friction between the hollow roller and the overload body.
  • a protective layer can be applied to the lateral surface of the bore and / or the outer surface of the overload body lying in the radial direction. This may be, for example, a thin chromium layer or a layer resulting from burnishing.
  • the filler may also consist of plastic.
  • the overload body has means for its axial and / or radial fixation in the hollow roller.
  • Axial fixation of the overload body within the through-bore of the hollow roller allows e.g. a simple mounting of the rolling elements in a rolling bearing, since the overload body can not slip out, or ensures that the overload body does not move axially during operation, but supports the hollow roller in the axial direction as intended.
  • Radial fixation is desirable to prevent the overload body in the hollow roller from striking the inner circumferential surface during operation.
  • the means for axial and / or radial fixation may e.g. consist of located at the two axial end portions of the overload body, circumferential notches for receiving an O-ring and an O-ring fitted therein itself.
  • the overload body is guided through a cage.
  • the supervisor load body for this purpose a greater axial extent than the hollow roller, ie it protrudes in the axial direction and can be absorbed by the cage.
  • the overload body can also have a reduced diameter at its two ends over partial areas in the axial direction, the resulting pin being guided through a cage.
  • the overload body has a profiling.
  • This can e.g. consist in a hollow cylinder of a circular, cylindrical or elliptical elliptical profile, as is known for rolling elements for cylindrical roller bearings.
  • a better support of the axially central region of the hollow roller can be achieved.
  • the ratio of the largest outer diameter of the hollow roller to the smallest inner diameter of the hollow roller between 2: 1 to 1, 1: 1, preferably between 1, 8: 1 to 1, 25: 1, more preferably between 1 , 6: 1 to 1, 4: 1.
  • the largest outer diameter corresponds to the diameter of an enveloping, coaxial cylinder.
  • the smallest inner diameter of the hollow roller corresponds to the maximum possible diameter of a coaxially arranged in the hollow cylinder.
  • the diameter ratios given in accordance with this embodiment correspond to typical dimensions of hollow rollers according to the invention. On the one hand, these have a correspondingly low radial rigidity in order to be used in rolling bearings for slip reduction.
  • An inventive rolling bearing has a plurality of massive rolling bodies, wherein at least one solid rolling element is replaced by a rolling element according to one of claims 1-14.
  • a bearing can be used, for example, to reduce the moment of inertia of the rolling bearing.
  • massive rolling elements are replaced by rolling elements according to the invention.
  • the hollow roller has a slightly larger outer diameter than the solid rolling elements. To avoid slippage, it is generally not necessary to use more than three rolling elements distributed over the circumference according to the invention.
  • the rolling bearing according to the invention may be a radial roller bearing, axial roller bearing, or a radial / axial roller bearing.
  • the game between the hollow body and overload body is chosen such - under certain circumstances by appropriate choice of the radial stiffness of the overload body - that the Ab support by the overload body then occurs when all rolling elements begin to wear. This ensures that, if the solid rolling elements and the at least one overload body made of a same material, a uniform load distribution occurs.
  • the overload body is a bolt of a bolt cage.
  • the bearing set can be driven via the cage, wherein the cage in turn only has to be driven by a single rolling element according to the invention.
  • the remaining rolling elements must therefore not have holes to receive corresponding pin of the cage.
  • the rolling element according to the invention can be used for example in rolling bearings of a gearbox storage of a wind turbine.
  • FIG. 1 is a schematic sectional view of a first embodiment of a rolling element according to the invention
  • FIG. 2 is a schematic sectional view of a loaded rolling element according to the invention
  • Fig. 3 is a schematic sectional view of a second and third
  • Fig. 4 is a schematic sectional view of inventive hollow rollers
  • FIG. 5 shows a relationship between radial compression and radial load of a rolling body according to the invention.
  • Fig. 1 shows a schematic sectional view of a first embodiment of a rolling element according to the invention.
  • the hollow roller 1 is a hollow cylinder which can be used, for example, in an axial or radial cylindrical roller bearing.
  • Fig. 1 a) shows a sectional view along an axially extending sectional plane
  • Fig. 1 b) shows a sectional view with a viewing direction in the axial direction.
  • the overload body 2 is spaced by the game 3 of the hollow roller 1.
  • the play is for example in rolling bearings to slip reduction in the range of a few microns up to 1 millimeter, the game is greater, the larger the Wälz stresses- diameter or the rolling bearing diameter.
  • the game may for example be between 50 microns and 0.8 millimeters.
  • the game is for example 0.132 millimeters.
  • the material used is, for example, 100CrMnSi6-4, both for the hollow roller and for the overload body.
  • Fig. 2 shows a schematic sectional view of a loaded rolling element according to the invention. Shown here is again a sectional view with a viewing direction in the axial direction corresponding to FIG. 1 b).
  • the hollow roller 1 is in each case between two raceways 4 and is loaded in the radial direction by the forces shown symbolically as arrows. This creates an elliptical deformation of the hollow roller. In Fig. 2 a), this deformation does not lead to a concern of the hollow roller to the overload body. Such a deformation of the hollow roller - until shortly before contact with the overload body - corresponds to a normal operation of the rolling element. In the event of a very large radial load in the load range, however, the deformation of the hollow roller 1 can lead to a concern to the overload body 2. This prevents further deformation of the hollow roller 1, so that it is ensured that no damage occurs.
  • FIG. 3 shows a schematic sectional view of a second and third embodiment of a rolling element according to the invention. Shown again is a sectional view with a viewing direction in the axial direction corresponding to FIG. 1 b).
  • the embodiment of FIG. 3 a) shows a hollow roller 1, for example a hollow cylinder. Distanced from this by the game 3 is an overload body forming hollow cylinder 2. This is in turn supported by a solid cylinder 5. The massive cylinder 5 is located directly on the overload body forming hollow cylinder 2.
  • cylinder 2 supported by a further hollow cylinder 6. As a result, the hollow cylinder 2 is supported sufficiently radially, without the weight of the rolling element increases significantly.
  • Fig. 4 shows a schematic sectional view of inventive hollow rollers with massive overload bodies. Shown are respective sectional views along an axially extending sectional plane corresponding to FIG. 1 a).
  • Fig. 4 a) shows a hollow cylinder for a cylindrical roller bearing
  • Fig. 4 b) shows a hollow tapered roller for a tapered roller bearing with cylindrical fürgangsboh- tion
  • Fig. 4 c) shows a hollow tapered roller for a tapered roller bearing with a tapered through hole
  • Fig. 4 d) shows a hollow barrel roller for a spherical roller bearing or spherical roller bearing
  • Fig. 4 e) shows a hollow ball roller for a ball roller bearing.
  • Fig. 5 shows a relationship between radial compression and radial load of a rolling element according to the invention. Shown in Fig. 5 a) is the cross-sectional profile and a radially acting force F, which causes a radial compression x.
  • the curve A in Fig. 5 b) corresponds to the compression of the hollow roller with increasing force, without being supported by the overload body. This results in a stiffness which remains constant over the load, namely the rigidity of the hollow roller.
  • the maximum permissible or predetermined radial compression xmax which corresponds to a corresponding maximum permissible material stress due to the bending stress of the hollow roller, is exceeded with a force F1.
  • the exceeding of xmax can be shifted to a higher force.
  • Such support of the hollow roller is represented by the curve B.
  • the stiffness corresponds from the support by the overload body substantially the sum of the individual stiffness of hollow roller and Overload body, neglecting the influence of the contact stiffness in the area of the force application point.
  • the rigidity of the entire rolling element thus has a kink.
  • the value of the radial compression at which the change in rigidity occurs, namely x ⁇ corresponds to twice the value of the clearance s which existed between the hollow roller and the overload body in the unloaded state.
  • the overload body according to the course of the curve C has a greater rigidity, as the overload body according to the course of the curve B. D.h.
  • the curve D finally shows the influence of the size of the game between hollow and overload body. This clearance has been chosen to be lower in the case of the curve D than in the case of the curves B and C. The supporting effect of the overload body thus already occurs earlier.

Landscapes

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

Abstract

L'invention concerne un corps de roulement pour palier à roulement, comprenant un rouleau creux présentant un alésage traversant s'étendant le long d'un axe de rotation du rouleau creux, et un corps de surcharge cylindrique disposé coaxialement dans l'alésage traversant. L'invention concerne en outre un palier à roulement présentant un corps de roulement conforme à l'invention. Un rouleau creux selon l'invention peut être, par exemple, un cylindre creux pour un palier à rouleaux cylindriques, un rouleau conique creux pour un palier à rouleaux coniques, un rouleau articulé creux pour un palier à rouleaux articulés, un galet sphérique pour un palier à galets sphériques. L'invention a pour but d'obtenir un corps de roulement autorisant, en fonctionnement, une déformation élastique partielle, de manière à pouvoir être utilisé, par exemple, dans un palier à roulement en vue de réduire le glissement, tout en empêchant toutefois une déformation élastique susceptible d'entraîner une détérioration. A cet effet, le corps de roulement est caractérisé en ce qu'il est prévu de ménager, entre l'alésage traversant et le corps de surcharge, un jeu radial dont la grandeur est sélectionnée de façon que le rouleau creux s'applique sur le corps de surcharge, par suite d'une surcharge radiale du corps de roulement se trouvant, dans un palier de roulement, entre deux pistes de roulement, avant qu'une sollicitation prédéterminée admissible du matériau du rouleau creux soit dépassée.
PCT/DE2008/002101 2007-12-22 2008-12-16 Corps de roulement comprenant un rouleau creux et un corps de surcharge Ceased WO2009079997A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007062391.9 2007-12-22
DE102007062391A DE102007062391A1 (de) 2007-12-22 2007-12-22 Wälzkörper umfassend eine Hohlrolle und einen Überlastkörper

Publications (2)

Publication Number Publication Date
WO2009079997A2 true WO2009079997A2 (fr) 2009-07-02
WO2009079997A3 WO2009079997A3 (fr) 2009-12-17

Family

ID=40627645

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2008/002101 Ceased WO2009079997A2 (fr) 2007-12-22 2008-12-16 Corps de roulement comprenant un rouleau creux et un corps de surcharge

Country Status (2)

Country Link
DE (1) DE102007062391A1 (fr)
WO (1) WO2009079997A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017054409A1 (fr) * 2015-09-30 2017-04-06 昆山光腾智能机械有限公司 Rouleau élastique, réducteur cycloïdal à engrenage à broche et palier
CN108980286A (zh) * 2018-09-29 2018-12-11 昆山光腾智能机械有限公司 针齿摆线减速器、传动滚柱和轴承
WO2020062122A1 (fr) * 2018-09-29 2020-04-02 昆山光腾智能机械有限公司 Réducteur de vitesse cycloïdal à engrenage à broche, rouleaux de broche de transmission et palier

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008044799A1 (de) 2008-08-28 2010-03-04 Schaeffler Kg Wälzkörper für ein Wälzlager sowie Wälzlager
DE102010034618A1 (de) 2010-08-18 2012-02-23 Schaeffler Technologies Gmbh & Co. Kg Wälzlager, Wälzkörper und Herstellungsverfahren für die Wälzkörper
DE102011006330A1 (de) 2011-03-29 2012-10-04 Schaeffler Technologies Gmbh & Co. Kg Wälzlager mit hohlen Wälzkörpern
DE102012214419A1 (de) * 2012-08-14 2014-02-20 Aktiebolaget Skf Brüniertes Wälzlager und Verfahren zur Herstellung eines brünierten Wälzlagers
DE102013201326A1 (de) * 2013-01-28 2014-07-31 Aktiebolaget Skf Wälzlager mit verbesserten Lasteigenschaften
DE102013215128A1 (de) 2013-08-01 2015-02-05 Schaeffler Technologies Gmbh & Co. Kg Wälzkörper
DE102013215837A1 (de) 2013-08-12 2015-02-12 Schaeffler Technologies Gmbh & Co. Kg Wälzlager
DE102013218620A1 (de) * 2013-09-17 2015-03-19 Schaeffler Technologies Gmbh & Co. Kg Wälzlagerung
CN114357846B (zh) * 2022-03-16 2022-06-24 中国华能集团清洁能源技术研究院有限公司 一种风电齿轮箱轴承故障识别方法及系统

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1005473A (en) * 1907-02-04 1911-10-10 Gustaf Rennerfelt Elastic-wheel bearing.
DE507577C (de) * 1927-07-02 1930-09-22 Robert Richard Gobereau Rollkoerperlager
DE566062C (de) 1929-07-11 1932-12-10 Skf Svenska Kullagerfab Ab Rolle fuer Rollenlager
FR946559A (fr) * 1946-06-27 1949-06-08 Coussinet à roulement avec organes roulants à élasticité radiale ou diamétrale
DE1261709B (de) * 1962-07-02 1968-02-22 Oskar E Peter Aus einem Kaefig und zylindrischen Rollen zusammengesetztes Lagerelement
DE1946966A1 (de) * 1969-09-17 1971-03-25 Peter Oskar E Aus einem Kaefig und zylindrischen Rollen zusammengesetztes Lagerelement
DE2152125A1 (de) * 1971-01-20 1972-07-27 Rollway Bearing Co Inc Rolle fuer ein Waelzlager
JPS52156254A (en) * 1976-06-21 1977-12-26 Suehiro Seikou Kk Multiplex bearing
SU681249A1 (ru) * 1977-06-13 1979-08-25 Предприятие П/Я А-1665 Упругий роликоподшипник
FR2479369A1 (fr) 1980-04-01 1981-10-02 Torrington France Dispositif de roulement pour palier radial
DE102005033355A1 (de) * 2005-07-16 2007-01-18 Schaeffler Kg Radialwälzlager, insbesondere zur Lagerung gering belasteter Wellen in Schwermaschinen

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017054409A1 (fr) * 2015-09-30 2017-04-06 昆山光腾智能机械有限公司 Rouleau élastique, réducteur cycloïdal à engrenage à broche et palier
TWI608180B (zh) * 2015-09-30 2017-12-11 昆山光騰智能機械有限公司 彈性滾柱、針齒擺線減速器和軸承
CN108980286A (zh) * 2018-09-29 2018-12-11 昆山光腾智能机械有限公司 针齿摆线减速器、传动滚柱和轴承
WO2020062122A1 (fr) * 2018-09-29 2020-04-02 昆山光腾智能机械有限公司 Réducteur de vitesse cycloïdal à engrenage à broche, rouleaux de broche de transmission et palier

Also Published As

Publication number Publication date
DE102007062391A1 (de) 2009-06-25
WO2009079997A3 (fr) 2009-12-17

Similar Documents

Publication Publication Date Title
WO2009079997A2 (fr) Corps de roulement comprenant un rouleau creux et un corps de surcharge
DE102015201257B3 (de) Kugelgewindetrieb und zugehöriger elektromechanischer Aktuator
DE102007016591A1 (de) Mehrreihiges Schub-Kugellager mit unsymmetrischer Lastenverteilung
EP2464894B1 (fr) Vis à billes comprenant des repères pour la butée et procédé de montage pour une telle vis à billes
DE2154836A1 (de) Ring-Tonnenlager
DE102015204970A1 (de) Wälzlager, beispielsweise einer Windkraftanlage
EP2094983B1 (fr) Palier à roulement, notamment pour le logement d'arbres dans des mécanismes moteurs à vent
DE102012005123A1 (de) Wälzlagerbefestigung und Kugelgewindemutter mit einer solchen
DE102013214869B4 (de) Unsymmetrisches Kegelrollenlager zur Lagerung eines Getrieberades an einer Getriebewelle
EP2076680B1 (fr) Ancrage
EP2143835A1 (fr) Dispositif de stockage et entrait pour machine à tisser
EP2312171A2 (fr) Procédé pour réduire et éviter l'usure du matériel dans des arbres rotatifs exposés à des tensions de flexion
EP3721113A1 (fr) Structure de palier composée d'éléments de palier en élastomère pouvant être montés individuellement et pouvant être remplacés
WO2009059585A2 (fr) Montage d'une roue planétaire pour optimiser la répartition des charges
WO2006021273A1 (fr) Ensemble palier radial et palier radial, notamment pour un logement de broche
DE102010034618A1 (de) Wälzlager, Wälzkörper und Herstellungsverfahren für die Wälzkörper
DE102018129339A1 (de) Einrichtung zur drehfesten Verbindung eines Verzahnungsteils mit einer Welle, Verfahren Herstellen einer solchen Einrichtung und Winkelgetriebe
DE102011078713B4 (de) Radlageranordnung
WO2005028888A1 (fr) Palier servant a absorber des contraintes axiales
EP4214426A1 (fr) Coussinet élastomère, ensemble coussinet et palier d'éolienne pour éoliennes
DE102013222833A1 (de) Stützlageranordnung für ein Planetendifferential
DE102009048692A1 (de) Verfahren zur Bearbeitung eines Wälzlagers und Lageranordnung
DE102021208077B4 (de) Sicherungsring zur axialen Sicherung eines Wälzlagers, Lageranordnung mit dem Sicherungsring sowie Verfahren zur Montage des Sicherungsrings
EP3670948B1 (fr) Palier à roulement pourvu de bague d'arrêt radiale permettant de limiter la déformation radiale du palier à roulement
DE102010015582A1 (de) Konus zur Herstellung einer Ankerstelle an einem Betonbauteil

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: 08864923

Country of ref document: EP

Kind code of ref document: A2

122 Ep: pct application non-entry in european phase

Ref document number: 08864923

Country of ref document: EP

Kind code of ref document: A2