WO2015057127A1 - Éolienne comportant un palier multirangée - Google Patents

Éolienne comportant un palier multirangée Download PDF

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Publication number
WO2015057127A1
WO2015057127A1 PCT/SE2014/051051 SE2014051051W WO2015057127A1 WO 2015057127 A1 WO2015057127 A1 WO 2015057127A1 SE 2014051051 W SE2014051051 W SE 2014051051W WO 2015057127 A1 WO2015057127 A1 WO 2015057127A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
rolling elements
wind turbine
row
shaft
Prior art date
Application number
PCT/SE2014/051051
Other languages
English (en)
Inventor
Hans Wendeberg
Jonas Kullin
Original Assignee
Aktiebolaget Skf
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 Aktiebolaget Skf filed Critical Aktiebolaget Skf
Publication of WO2015057127A1 publication Critical patent/WO2015057127A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • 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
    • F16C19/30—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 axial load mainly
    • 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
    • F16C19/50—Other types of ball or roller bearings
    • F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2240/00—Components
    • F05B2240/50—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
    • 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
    • F16C2360/00—Engines or pumps
    • F16C2360/31—Wind motors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

  • the present invention concerns a wind turbine comprising at least one bearing, namely a rolling element bearing.
  • a wind turbine is a device that converts kinetic energy from the wind into mechanical energy.
  • the mechanical energy may be used to produce electricity, or to drive machinery, such as for pumping water.
  • Bearings support the shaft of the wind turbine to permit its free motion about an axis of rotation.
  • Load can be applied to bearings in either of two basic directions. Radial load acts at right angles to the shaft. Axial load (thrust) acts parallel to the axis of rotation. When these loads are offset from either the bearing axis or radial plane of the bearing, a resulting moment load will be created.
  • a wind turbine may have rotor blades of about 40 meters in length, a rotor hub height of up to 100 meters and a total weight of up to 200 tons or more.
  • the bearings used in wind turbines can therefore be very large, with bore diameters of 100 mm up to 2 meters or more, and may need to withstand substantial combined loads, i.e. radial and axial loads, or radial, axial and moment loads, or large axial loads in one or two directions.
  • An object of the invention is to provide an improved wind turbine containing at least one bearing that is suitable for withstanding combined loads, i.e. radial and axial loads, or to large axial loads in one or two directions.
  • a "large axial load” is intended to mean application in which the axial load constitutes a substantial part of the radial load, for example application in which the axial load is 0.2-1000 times as large as the radial load.
  • a wind turbine containing at least one bearing having a bearing axis and comprising a first row of rolling elements having a first pressure centre and a first contact angle, a second row of rolling elements having a second pressure centre and a second contact angle, whereby the first pressure centre is arranged to coincide with the second pressure centre, i.e. whereby the first row of rolling elements and the second row of rolling elements are arranged to have a common pressure centre, and whereby the first contact angle and the second contact angle are on the same side of a plane perpendicular to the bearing axis, i.e. the first contact angle and the second contact angle have the same sign, i.e. ++ or - - .
  • a contact angle is formed by a straight line drawn between the points of contact of the rolling elements with the raceways and a plane perpendicular to the bearing axis. Contact angles having the same sign are on the same side of said plane perpendicular to the bearing axis.
  • Such a bearing can accommodate radial loads in addition to axial loads, which makes the bearing suitable for use in applications where there are combined loads.
  • This ability to accommodate combined loads enables economical, space saving compact bearing designs that can provide a high degree of axial and radial stiffness under heavy load conditions.
  • Such a bearing may for example be used to accommodate a radial load up to 55% of a simultaneously acting axial load.
  • Such a self-aligning bearing can also accommodate misalignment and shaft deflections, and low as well as high speeds.
  • the wind bearing design according to the present invention enables a user to adapt a bearing to a particular application depending on the loads to which the bearing will be subjected during its use.
  • the contact angles for the first and second rows of rolling elements may be optimized depending on the magnitudes of the axial load and the radial load in one or two directions.
  • a first row of rolling elements may for example be subjected to a large axial load in one direction and the second row of rolling elements may be subjected to a smaller axial load in the opposite direction and contact angles may be chosen accordingly.
  • the first row of rolling elements constitutes an inner row of rolling elements and the second row of rolling elements constitutes an outer row of rolling elements, and any of the outer or inner row of rolling elements is arranged to carry a radial load when the bearing is in use.
  • the outer and inner row of rolling elements are also arranged to carry axial loads in opposite directions when the bearing is in use.
  • the first row of rolling elements constitutes an inner row of rolling elements and the second row of rolling elements constitutes an outer row of rolling elements, wherein the inner row and the outer row are relatively displaced in a radial direction of the bearing.
  • the first row and the second row of rolling elements are also located such that the outer row and the inner row of rolling elements are at least partly overlapping each other in an axial direction of the bearing. The radial displacement is thus such that the outer row and the inner row will not interfere with each other.
  • the outer and inner row of rolling elements are overlapping each other in an axial direction by at least 10 %, 20 %, 30 %, 40 %, 50 %, 60 %, 70 %, 80 %, 90 % or 100 %.
  • the extent of the axial overlap may depend on the current requirements of the bearing in its intended application, i.e. expected radial and axial forces exerted on the bearing, the amount of space available in the application etc.
  • the rolling elements are symmetrical. Alternatively, the rolling elements are asymmetrical.
  • the at least one bearing is at least one of the following: a spherical roller bearing, a toroidal roller bearing, a ball bearing or a combination thereof.
  • the at least one bearing is at least one self-aligning bearing. It may for example have spherical rolling elements and a common sphered raceway in its outer ring.
  • the at least one bearing comprises at least two rows of rolling elements (i.e. including the first row of rolling elements and the second row of rolling elements) and a plurality of bearing rings, such as two or three bearing rings. Any of the bearing rings may be arranged to rotate or to remain stationary when the bearing is in us, i.e. any of the rings, i.e. an inner ring, a central ring or intermediate ring or an outer ring, may be arranged to be mounted on a rotatable shaft when the bearing is in use.
  • the bearing comprises a first ring, a second ring and an intermediate ring, wherein the outer row of rolling elements is interposed in between an outer raceway of the first ring and an outer raceway of the intermediate ring and wherein the inner row of rolling elements is interposed in between an inner raceway of the intermediate ring and an inner raceway of the second ring.
  • the rolling elements of the outer row of rolling elements and the rolling elements of the inner row of rolling elements will rotate in opposite directions.
  • this will allow the bearing to be able to accommodate radial loads, but also axial loads in both directions.
  • the first and second rings are connected or integrated, i.e. the first and second rings may be seen as one unified ring.
  • the at least one bearing comprises more than two rows of rolling elements, whereby each row of rolling elements has a pressure centre and all the pressure centres are arranged to coincide, i.e. all of the rows of rolling elements are arranged to have a common pressure centre.
  • the at least one bearing is separable, whereby the mounting and dismounting procedure is facilitated.
  • a shaft washer with cage and roller assembly and a housing washer of the bearing may for example be arranged to be mounted/dismounted separately.
  • the at least one bearing constitutes at least one of the following types of bearing: SRB (Spherical Roller Bearing), SAT (Self-Aligning Torus bearing), SRTB (Spherical Roller Thrust Bearing), ACBB (Angular Contact Ball Bearing).
  • the wind turbine comprises a shaft having a rotor end and the at least one bearing is mounted at the rotor end of the shaft.
  • the wind turbine comprises a gearbox and the at least one bearing is mounted in the vicinity of said gearbox, i.e. the outermost edge of at least one bearing is mounted within 10-100 mm from the outermost edge of the gearbox, as close as possible to the gearbox.
  • Figures 1 -4 show cross sections of bearings of wind turbines according to embodiments of the present invention
  • Figure 5 shows cross sections of a self-aligning bearing of a wind turbine according to an embodiment of the present invention
  • Figure 6 shows a cross section of a bearing of a wind turbine according to an embodiment of the invention mounted on a shaft
  • Figure 7 shows a wind turbine according to an embodiment of the invention.
  • Figure 8 shows a cross section of a bearing of a wind turbine according to an embodiment of the invention.
  • Figures 1 -4 schematically show a cross section (defined as a plane coinciding with the axial direction of the bearing 8) of a bearing 8 of a wind turbine according to the present invention comprising a first inner row of rolling elements 10 having a first pressure centre, and a second outer row of rolling elements 12 having a second pressure centre, whereby the first pressure centre is arranged to coincide with the second pressure centre at a common pressure centre 14 and said first contact angle and said second contact angle are on the same side of a plane perpendicular to said bearing axis.
  • the outer row of rolling elements 12 and the inner row of rolling elements 10 are displaced in a radial direction of the bearing 8.
  • the outer row 12 and the inner row 10 are overlapping each other at least partly in the axial direction of the bearing 8, which leads to a more compact bearing 8.
  • the rows do not necessarily need to overlap in the axial direction, depending e.g. on the level of compactness that is wanted in the specific application.
  • the contact angles can be modified depending on the load situation in the bearing's 8 intended application.
  • the rolling elements 10 and 12 are arranged in between a stationary component 16 and a rotatable component 18 that is to be mounted on a shaft of the wind turbine, but the components 12, 18 may also be mounted so that the component 16 is rotating and the component 18 is stationary.
  • the second outer row of rolling elements 12 may be arranged to carry a radial load when the bearing 8 is in use, and optionally also an axial load in one direction.
  • the inner row 10 may then be able to carry an axial load in the other axial direction.
  • the component 18 (or intermediate ring 18) presents an outer raceway 21 and an inner raceway 22.
  • the component 16 presents an outer raceway 23 and an inner raceway 24.
  • the component 16 is split into two rings, comprising a first ring and a second ring (not shown in this figure).
  • the rolling elements of the outer row of rolling elements 12 and the rolling elements of the inner row 10 of rolling elements will rotate in opposite directions when the bearing 8 is in operation. Furthermore, this will allow the bearing 8 of the wind turbine to be able to accommodate radial loads, but also axial loads in both directions.
  • the bearing 8 has asymmetrical rolling elements 10, 12, a flange on the rings, sphered raceways, and rolling elements 10, 12 with different contact angles.
  • the bearing 8 has asymmetrical rolling elements 10, 12, a flange on the rings, sphered raceways, and rolling elements 10, 12 with the same contact angle.
  • the bearing 8 has symmetrical rolling elements 10, 12, no flange on the rings, sphered raceways, and rolling elements 10, 12 with the same contact angle.
  • the bearing 8 has symmetrical rolling elements 10, 12, no flange on the rings, toroidal raceways, and rolling elements 10, 12 with the same contact angle (i.e. figure 4 shows a toroidal roller bearing).
  • a bearing 8 according to the present invention need not necessarily comprise a flange on a bearing ring. Furthermore, a bearing 8 according to the present invention may have contact angles of 90° to 0°.
  • Figure 5 shows a cross section of a self-aligning bearing 8 according to an embodiment of the invention.
  • the bearing 8 comprises four rows of rolling elements 10a, 10b, 12a, 12b whereby the pressure centre of all of the rows of rolling elements 10a, 10b, 12a, 12b is arranged to coincide at a common pressure centre 14.
  • the bearing 8 comprises a common sphered raceway 20 for two of the adjacent inner rows of rolling elements 10a and 10b and a common sphered raceway 20 for the other two adjacent rows of outer rolling elements 12a and 12b.
  • Such a self-aligning bearing 8 provides smooth, friction-free adjustment over a broad range of operating conditions.
  • the inner row of rolling elements 10a and 10b are overlapping the outer row of rolling elements 12a and 12b in the axial direction of the bearing 8.
  • the axial overlap in this specific embodiment is relatively large, up to at least 80 % of the axial width of the outer row of rolling elements 12a and 12b.
  • the contact angles of the outer rows 12 a, b and the inner rows 10a, b may be adjusted within the scope of the invention depending on the current load situation in the application in which the bearing 8 shall operate. Due to the configuration of the bearing 8, the rolling elements of the outer rows of rolling elements 12a, b will rotate in one direction and the rolling elements of the inner rows of rolling elements 10a, b will rotate in the opposite direction.
  • a bearing of a wind turbine according to the present invention may comprise any number of rows of rolling elements, i.e. 2, 3, 4 or more. Furthermore, any number of rows may be located adjacently. For example two adjacent outer rows of rolling elements may be located above a single inner row of rolling elements, whereby these rows of rolling elements are arranged to have a common pressure centre.
  • the bearing 8 comprises at least two rows of rolling elements and three bearing 8 rings, whereby an outer ring may be arranged to comprise a common sphered raceway 20 for a plurality of rows of rolling elements.
  • the three bearing rings can comprise an inner ring, a central ring (intermediate ring) and an outer ring, and the central ring may be arranged to be mounted on a rotatable shaft of the wind turbine when the bearing 8 is in use.
  • Figure 6 shows a bearing 8 of a wind turbine according to an embodiment of the invention mounted on a shaft 30 of a wind turbine.
  • the bearing 8 comprises a first inner row of rolling elements 10 having a first pressure centre, and a second row of rolling elements 12 having a second pressure centre, whereby the first pressure centre is arranged to coincide with the second pressure centre at a common pressure centre 14.
  • the shaft 30 may comprise a rotor at a rotor end thereof and the bearing 8 in the illustrated embodiment is mounted at the non-rotor end of the shaft 2.
  • a bearing 8 of a wind turbine according to the present invention may however be alternatively or additionally mounted at the rotor end of the shaft 30.
  • Figure 6 shows that a bearing 8 of a wind turbine according to the present invention may be used with another bearing at the opposite end of a shaft 30.
  • a bearing 8 may alternatively or additionally be mounted in the vicinity of a gearbox of a wind turbine.
  • the bearing 8 may be separable into any number of individual components so as to facilitate mounting and dismounting of the bearing 8.
  • a shaft washer with cage, a rolling element assembly and a housing washer of the bearing 8 may for example be arranged to be mounted/dismounted separately.
  • the bearing 8 of a wind turbine according to the invention may constitute one of the following types of bearing 8: SAT, SRTB, ACBB.
  • a bearing 8 of a wind turbine according to the present invention may be of any size and have any load-carrying capacity.
  • An inner ring and/or an outer ring of the bearing 8 may for example have a diameter up to a few metres and a load-carrying capacity up to many thousands of tonnes.
  • the bearing 8 may have an open design, or a sealed design with contact seals on one or both sides of the bearing 8, and/or it may have an extended inner ring.
  • Figure 7 shows a wind turbine 50 according to an embodiment of the present invention.
  • the dashed circle 51 shows an axially free-moving position (i.e. an "axially non-locating position")
  • the dotted circle 52 (the "axially locating position") shows a suitable position for a bearing 8 according to the present invention.
  • a toroidal bearing should therefore preferably be located in the position indicated by the dotted circle 51 . It can be advantageous to have a bearing in an axially locating position (within the area indicated by the dotted circle 52) located as close as possible to a gearbox so as to avoid large axial displacements in the gearbox.
  • Figure 8 shows a cross section of another embodiment of a bearing 8 of a wind turbine according to the invention, which is mounted onto a rotor shaft 30. Further, the bearing 8 is mounted into a housing structure 40 allowing the rotor shaft 30 to rotate relative the housing structure 40.
  • the bearing 8 comprises an outer row of rolling elements 12 and an inner row of rolling elements 10.
  • the roller elements in the rolling rows 12 and 10 are asymmetrical spherical rollers and further the bearing 8 comprises flanges 181 and 161 for the outer and inner row 12 and 10 respectively.
  • the bearing comprises an outer ring 162, an inner ring 163 and an intermediate ring 18.
  • the outer row of rolling elements 12 and the inner row of rolling elements 10 present a common pressure center 14 but with different contact angles as can be seen from the illustration.
  • the contact angles are on the same side of a plane perpendicular to said bearing axis.
  • the outer ring 162 presents a spherical outer raceway 23 and the inner ring 163 presents a spherical inner raceway 24, and the intermediate ring 18 presents a spherical outer raceway 21 and a spherical inner raceway 22.
  • the bearing 8 may be able to accommodate radial loads, but also axial loads in both directions.
  • the rotor shaft 30 may preferably be arranged with two bearings, i.e. the bearing 8 and a further radial bearing mounted onto the rotor shaft 30 (not shown), such as a toroidal roller bearing or any other suitable radial bearing.
  • the intermediate ring 18 When in operation, i.e. when the rotor shaft 30 is rotating relative the housing structure 40, the intermediate ring 18 will rotate with the shaft 30 and the outer ring 162 and the inner ring 163 will be stationary with the housing structure 40.
  • the bearing 8 will be able to accommodate relatively large axial forces in both axial directions of the shaft.
  • the bearing 8 can be optimized for different specific load situations (radial forces, axial forces and especially combinations thereof). A person skilled in the art will be able to make such modifications for optimizing the bearing 8 for its specific intended use.
  • the bearing 8 will be able to accommodate misalignments of the shaft 30 relative the housing structure 40.
  • the curved raceway profiles are spherical, but the curved profiles may for instance also be in a torus form.
  • a wind turbine according to the present invention may comprise a bearing comprising at least one coated component, such as a component comprising a corrosion protection layer and/or at least one separable component.
  • the bearing may comprise at least one sensor, such as a load and/or temperature sensor to monitor the status of the bearing, it may have any suitable row configuration adapted for a particular application and/or comprise any suitable material or materials.

Abstract

L'invention concerne une éolienne (24) contenant au moins un palier (8) comportant une première rangée de corps roulants (10, 10a, 10b, 12, 12a, 12b) ayant un premier centre de pression (14), et une deuxième rangée de corps roulants (10, 10a, 10b, 12, 12a, 12b) ayant un deuxième centre de pression (14), caractérisée en ce que le premier centre de pression (14) est conçu pour coïncider avec le deuxième centre de pression (14).
PCT/SE2014/051051 2013-10-17 2014-09-11 Éolienne comportant un palier multirangée WO2015057127A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE1300661-4 2013-10-17
SE1300661 2013-10-17

Publications (1)

Publication Number Publication Date
WO2015057127A1 true WO2015057127A1 (fr) 2015-04-23

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PCT/SE2014/051051 WO2015057127A1 (fr) 2013-10-17 2014-09-11 Éolienne comportant un palier multirangée

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WO (1) WO2015057127A1 (fr)

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191501133A (en) * 1915-01-23 1915-06-17 Harold Wade Improvements in or relating to Ball-bearings.
US1645345A (en) * 1926-12-09 1927-10-11 Okner Bernard Ball bearing
US20020085677A1 (en) * 2000-12-29 2002-07-04 Ratzmann Paul Michael Multiple row x-ray tube bearing assembly
JP2004308792A (ja) * 2003-04-07 2004-11-04 Ts Corporation 複列式一体アンギュラ軸受およびそれを用いた歯車装置
JP2005265094A (ja) * 2004-03-19 2005-09-29 Koyo Seiko Co Ltd 複列斜接玉軸受およびピニオン軸支持用軸受装置
EP1724478A1 (fr) * 2004-03-11 2006-11-22 JTEKT Corporation Roulement a double rangee de billes a contact en biais et dispositif pour soutenir un arbre de pignon
JP2008082506A (ja) * 2006-09-28 2008-04-10 Jtekt Corp 転がり軸受及びこれを用いた過給機
DE102006051643A1 (de) * 2006-11-02 2008-05-08 Schaeffler Kg Tandem-Schrägwälzlager
JP2008138842A (ja) * 2006-12-05 2008-06-19 Ntn Corp タンデム型複列アンギュラ玉軸受
DE102010054318A1 (de) * 2010-12-13 2012-06-14 Schaeffler Technologies Gmbh & Co. Kg Rotorlagerung einer Windkraftanlage

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191501133A (en) * 1915-01-23 1915-06-17 Harold Wade Improvements in or relating to Ball-bearings.
US1645345A (en) * 1926-12-09 1927-10-11 Okner Bernard Ball bearing
US20020085677A1 (en) * 2000-12-29 2002-07-04 Ratzmann Paul Michael Multiple row x-ray tube bearing assembly
JP2004308792A (ja) * 2003-04-07 2004-11-04 Ts Corporation 複列式一体アンギュラ軸受およびそれを用いた歯車装置
EP1724478A1 (fr) * 2004-03-11 2006-11-22 JTEKT Corporation Roulement a double rangee de billes a contact en biais et dispositif pour soutenir un arbre de pignon
JP2005265094A (ja) * 2004-03-19 2005-09-29 Koyo Seiko Co Ltd 複列斜接玉軸受およびピニオン軸支持用軸受装置
JP2008082506A (ja) * 2006-09-28 2008-04-10 Jtekt Corp 転がり軸受及びこれを用いた過給機
DE102006051643A1 (de) * 2006-11-02 2008-05-08 Schaeffler Kg Tandem-Schrägwälzlager
JP2008138842A (ja) * 2006-12-05 2008-06-19 Ntn Corp タンデム型複列アンギュラ玉軸受
DE102010054318A1 (de) * 2010-12-13 2012-06-14 Schaeffler Technologies Gmbh & Co. Kg Rotorlagerung einer Windkraftanlage

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