WO2016112888A1 - Assemblage vissé annulaire - Google Patents

Assemblage vissé annulaire Download PDF

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Publication number
WO2016112888A1
WO2016112888A1 PCT/DE2015/200517 DE2015200517W WO2016112888A1 WO 2016112888 A1 WO2016112888 A1 WO 2016112888A1 DE 2015200517 W DE2015200517 W DE 2015200517W WO 2016112888 A1 WO2016112888 A1 WO 2016112888A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
ring
fastening arrangement
arrangement according
spacer
Prior art date
Application number
PCT/DE2015/200517
Other languages
German (de)
English (en)
Inventor
Jörg-Oliver Hestermann
Original Assignee
Schaeffler Technologies AG & Co. 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 Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2016112888A1 publication Critical patent/WO2016112888A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16B—DEVICES FOR FASTENING OR SECURING CONSTRUCTIONAL ELEMENTS OR MACHINE PARTS TOGETHER, e.g. NAILS, BOLTS, CIRCLIPS, CLAMPS, CLIPS OR WEDGES; JOINTS OR JOINTING
    • F16B31/00—Screwed connections specially modified in view of tensile load; Break-bolts
    • F16B31/02—Screwed connections specially modified in view of tensile load; Break-bolts for indicating the attainment of a particular tensile load or limiting tensile load
    • 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
    • F16C19/34—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 both radial and axial load
    • F16C19/38—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 both radial and axial load with two or more rows of rollers
    • F16C19/381—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 both radial and axial load with two or more rows of rollers with at least one row for radial load in combination with at least one row for axial load
    • 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
    • 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
    • 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
    • F16C19/34—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 both radial and axial load
    • F16C19/38—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 both radial and axial load with two or more rows 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
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections
    • 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 mounting arrangement of a rolling bearing with a rotatable and a stationary component.
  • the roller bearing comprises a bearing inner ring and a bearing outer ring as well as a multiplicity of rolling elements arranged between the bearing inner ring and the bearing outer ring for radial and axial bearing.
  • a plurality of axially extending through holes are present in both bearing rings.
  • a bearing which comprises an outer ring, an inner ring and arranged therebetween rows of Wälzkörpem. Holes with countersinks in which short screws are inserted are present in the inner ring and in the outer ring. Through the use of short and far sunk screws while the bearing rings may be less compressed during screwing compared to the prior art, but this can lead to a low bias especially after subsidence in the screw.
  • the object of the present invention is therefore to specify an improved fastening arrangement of a roller bearing, which represents a more advantageous relation between helical prestressing and deformation of the bearing rings.
  • the fastening arrangement according to the invention is characterized in that a spacer ring is arranged in at least one countersink.
  • the spacer ring preferably has a spacer ring length which is greater than the wall thickness of the spacer ring.
  • the spacer ring may be formed in particular as a sleeve, a pipe or a socket. This is to achieve the goal that the deformation of the bearing rings due to the screw force does not affect the preload in the rolling contact and the screws have a sufficient length, so that the screw retains the required preload force in subsidence phenomena.
  • the bores in each bearing ring each have at most one countersink with a spacer ring arranged therein. This means that either a lowering is present either in both bearing rings, in each of which a spacer ring is arranged or that a spacer ring is present only in a bearing ring.
  • the bores in one of the bearing rings each have two counterbores with a spacer ring arranged in each countersink. It is useful if the other bearing ring has a different number of spacers in all holes. There are thus several possibilities of arranging spacer rings.
  • the bearing outer ring could have two countersinks, each with a spacer ring and the bearing inner ring no spacers. Another possibility is when the bearing inner ring as well as the bearing outer ring has two countersinks, each with a spacer ring.
  • it would be possible Lich if the bearing inner ring two and the bearing outer ring has no spacers in the respective intended reductions.
  • the bores in each of the bearing rings each have a countersink and in the other bearing ring in each case two counterbores with a spacer ring arranged in each countersink.
  • the bearing inner ring has two and the bearing outer ring on a countersink with the spacers contained therein. Conversely, this is also possible, so that the bearing inner ring has only one and the bearing outer ring two spacers.
  • the clamping length in the bearing ring is shorter than the sum of the dis- dance ring lengths in the respective bearing ring.
  • a spacer ring and / or a screw head in the countersink flush with the bearing ring.
  • the countersinkings introduced into the bearing rings need not only be used for the spacers, but that the head of the screw can also be arranged in the countersink.
  • a spacer ring and a screw head are arranged in a countersink, so that the screw head terminates flush in the countersink with the bearing ring. Otherwise, the screw head can lie flush on the bearing ring and the spacer ring inserted in the recess can be flush with the bearing ring.
  • the spacer ring is preferably made of a metallic material with an E-modulus of at most 210 kN / mm 2 at 20 ° C. in any embodiments.
  • the E-modulus of the spacer ring is preferably in the range of 1 10 kN / mm 2 up to 210 kN / mm 2 .
  • the spacers consist of an elastic material, in particular a metallic material. Furthermore, the spacers could also consist of plastic.
  • the screw connection according to the invention is used for rolling bearings which are designed with two rows of rolling elements serving for axial bearing and with a row of rolling elements serving for the radial bearing. An example of this is a rotary table bearing, which is offered by the applicant under the name "axial radial bearing YRT".
  • the rolling bearing is designed as a double-row oblique roller or angular contact ball bearings.
  • Angular contact ball bearings and tapered roller bearings are available in innumerable varieties in the prior art.
  • the Applicant offers these in her catalog in a large variety. They can be found, for example, under the designations "angular contact ball bearings 30 to 38" and "axial tapered roller bearings AXS".
  • bearings which come into question by constructive configurations for the fastening arrangement, as for example in DE 10 201 1 005 725 A1 or in DE 10 201 1 002 898 A1.
  • FIG. 1 shows an embodiment of a fastening arrangement of a rotary table bearing with three spacer rings
  • Figure 2 shows another embodiment of a fastening arrangement of a
  • Figure 3 shows an embodiment of a mounting arrangement of a
  • the roller bearing 1 shows an exemplary embodiment of the Befest onlysanord- tion of a rolling bearing 1 with a fixed 2 and with a rotatable member 3 is shown in cross section.
  • the roller bearing 1, a so-called round table bearing, comprises a bearing inner ring 4 and a bearing outer ring 5, and two rows of rolling elements for axial bearing 6, which are arranged axially above and below the bearing outer ring 5, and a series of rolling elements for Radalla- tion 7, the between bearing outer 5 and bearing inner ring 4 is arranged centrally on the inner circumference of the bearing outer ring 5.
  • the bearing outer ring 5 has a continuous bore 8 ending in the stationary component 2.
  • the spacers 10, 11 in the bearing outer ring 5 here have the same length spacer ring lengths L10, L11 and the same wall thicknesses b.
  • the inserted screw 12 has a clamping length L in the bearing outer ring 5, which is shorter than the sum of the spacer ring lengths L10, L11.
  • the bearing inner ring 4 has, parallel to the bore 8 in the bearing outer ring 5, a bore 15 passing through the bearing ring 5 and through an intermediate piece 14, also called wave washer, and ending in the rotatable component 3.
  • the intermediate piece 14 is a part of the bearing inner ring 4 and has raceways for the rolling elements for axial bearing 6.
  • a countersink 9 is arranged in the bore 15 on the opposite side of the intermediate piece 14 and the rotatable component 3.
  • the screw head 13 includes in the present embodiment in the reduction 9 flush with the bearing inner ring 4.
  • the clamping length L of the screw 12 is shorter in the bearing inner ring 4 than the spacer ring length L16. It is advantageous that the compressed material of the bearing rings 4, 5 is not in the plane of the rolling elements 6, 7. The geometrical changes of the bearing rings 4, 5 as a result of the screw thus lie in the region of the screw connection and not in the region of the rolling elements 6, 7.
  • the intermediate piece 14 can also be omitted by constructive embodiments of the other components.
  • FIG. 2 differs from FIG. 1 only with respect to the bores 8, 15 and the spacer rings 10, 11, 16 arranged therein.
  • the bore 8 of the bearing outer ring 5 has two countersinks 9. In the countersink 9 to the stationary component 2 towards a spacer ring 10 is arranged.
  • the screw head 13 of the screw 12 is inserted in the other countersink 9 of the bearing outer ring 5, so that this screw head 13 is flush in the countersink 9 with the bearing outer ring 5.
  • the screw head 13 could also be sunk further in the countersink 9.
  • the clamping length L of the screw 12 in the bearing outer ring 5 is shorter than the spacer ring length L10.
  • FIG. 3 shows a further fastening arrangement according to the invention of a roller bearing 1 with a stationary 2 and with a rotatable component 3 in cross section.
  • the rolling bearing 1, comprising a bearing outer ring 5, a bearing inner ring 4 and arranged therebetween two rows of roller-shaped Whisker 18, is designed as a double row tapered roller bearing.
  • the bearing outer ring 5 is fastened to the stationary component 2 by means of a screw 12.
  • the screw 12 is inserted in a bore 8 passing through the bearing outer ring 5 and ending in the stationary component 2.
  • the bore 8 in the bearing outer ring 5 has a countersink 9 from both sides.
  • a spacer ring 10 is arranged in the countersink 9, which bears against the stationary component 2, a spacer ring 10 is arranged.
  • the clamping length L of the screw 12 is also shorter here than the sum of the spacer ring lengths L10, L1 1.
  • the bearing inner ring 4 has a continuous bore 15 ending in the rotatable component 3.

Abstract

L'invention concerne un système de fixation d'un palier à roulement (1) comprenant un élément structural rotatif (3) et un fixe (2). Le palier à roulement (1) comprend une bague intérieure de palier (4) et une bague extérieure de palier (5) ainsi qu'une pluralité d'organes roulants (6, 7, 18) disposés entre la bague intérieure de palier (4) et la bague extérieure de palier (5) pour le support radial et axial. Selon l'invention, il existe dans les deux bagues de palier (4, 5) une pluralité de trous traversants (8, 15) qui s'étendent dans le sens, et sur au moins une bague de palier (4, 5), sur au moins un côté des trous traversants (8, 15), se trouve un enfoncement (9). Une bague d'espacement (10, 11, 16, 17) est disposée dans ledit enfoncement (9).
PCT/DE2015/200517 2015-01-13 2015-11-24 Assemblage vissé annulaire WO2016112888A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015200294.2 2015-01-13
DE102015200294.2A DE102015200294A1 (de) 2015-01-13 2015-01-13 Ringverschraubung

Publications (1)

Publication Number Publication Date
WO2016112888A1 true WO2016112888A1 (fr) 2016-07-21

Family

ID=55272201

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2015/200517 WO2016112888A1 (fr) 2015-01-13 2015-11-24 Assemblage vissé annulaire

Country Status (2)

Country Link
DE (1) DE102015200294A1 (fr)
WO (1) WO2016112888A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11619211B2 (en) * 2020-10-30 2023-04-04 General Electric Renovables Espana, S.L. Wind turbine pitch bearing with friction enhancing insert layer

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010018141A1 (de) * 2010-04-24 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Mehrreihiges Wälzlager, insbesondere mehrreihiges Großwälzlager einer Windkraftanlage
DE102011002898A1 (de) 2011-01-20 2012-07-26 Schaeffler Technologies Gmbh & Co. Kg Doppelreihiges Schrägrollenlager
DE102011005725A1 (de) 2011-03-17 2012-09-20 Schaeffler Technologies Gmbh & Co. Kg Wälzlager
JP2012193859A (ja) 2012-07-10 2012-10-11 Thk Co Ltd ベアリング

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE7208997U (de) * 1972-06-15 Hoesch Ag Axial vorgespanntes Großwälzlager
US1433528A (en) * 1919-03-01 1922-10-31 Taft Peirce Mfg Co Ring thread gauge
DE1201128B (de) * 1957-08-20 1965-09-16 Schwermaschb Verlade Und Trans Mittenfreier, vertikalachsiger Grossdrehkranz fuer Krane, Bagger, Arbeitsbuehnen und aehnliche Rotations- und Schwenkgeraete
FR2296787A1 (fr) * 1975-01-06 1976-07-30 Hoesch Werke Ag Palier
DE3020522A1 (de) * 1980-05-30 1981-12-10 Emuge-Werk Richard Glimpel Fabrik für Präzisionswerkzeuge vormals Moschkau & Glimpel, 8560 Lauf Federelement fuer eine spannvorrichtung
DE8437821U1 (de) * 1984-12-22 1986-09-18 Jacob, Werner, 6000 Frankfurt Ringförmiges Drahtlager

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010018141A1 (de) * 2010-04-24 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Mehrreihiges Wälzlager, insbesondere mehrreihiges Großwälzlager einer Windkraftanlage
DE102011002898A1 (de) 2011-01-20 2012-07-26 Schaeffler Technologies Gmbh & Co. Kg Doppelreihiges Schrägrollenlager
DE102011005725A1 (de) 2011-03-17 2012-09-20 Schaeffler Technologies Gmbh & Co. Kg Wälzlager
JP2012193859A (ja) 2012-07-10 2012-10-11 Thk Co Ltd ベアリング

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