JP2007024294A - Tapered roller bearing and spindle supporting structure of wind power generator - Google Patents

Tapered roller bearing and spindle supporting structure of wind power generator Download PDF

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JP2007024294A
JP2007024294A JP2005211708A JP2005211708A JP2007024294A JP 2007024294 A JP2007024294 A JP 2007024294A JP 2005211708 A JP2005211708 A JP 2005211708A JP 2005211708 A JP2005211708 A JP 2005211708A JP 2007024294 A JP2007024294 A JP 2007024294A
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tapered roller
roller bearing
inner ring
tapered
large collar
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JP4699827B2 (en
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Tatsuya Omoto
達也 大本
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • 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
    • F16C19/383—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—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 tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
    • 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
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the 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
    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Motor Or Generator Frames (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered roller bearing wherein the cracks and chipping of a large flange of an inner ring can be prevented, and a spindle supporting structure of a wind power generator using the bearing. <P>SOLUTION: The inner ring 12b is provided with a tilt part 28b extended to the peripheral direction between a large flange face 27b abutted to a large end face of a tapered roller and guiding the large end face and a large flange outside diameter face 26b which is the outside diameter face of the inner ring 12b on the large flange side. The tilt part 28b is the tilt provided between the large flange face 27b and the large flange outside diameter face, and is the region obtained by increasing a thickness of the large flange 21b to an arrow Y direction which is the load applying direction. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は、円錐ころ軸受および風力発電機の主軸支持構造に関し、特に、大きなラジアル荷重やスラスト荷重、モーメント荷重を受けることができる円錐ころ軸受およびこのような軸受を使用した風力発電機の主軸支持構造に関する。   The present invention relates to a tapered roller bearing and a main shaft support structure of a wind power generator, and more particularly, a tapered roller bearing capable of receiving a large radial load, thrust load, and moment load, and a main shaft support of a wind power generator using such a bearing. Concerning structure.

風力発電機の主軸に使用される軸受は、ブレードの自重等に対するラジアル荷重、風力に対するスラスト荷重およびモーメント荷重を受ける必要がある。さらには、風力発電機の主軸は片持ちの梁構造であるため、主軸の撓みに対する自動調心性を備えた軸受が求められるため、自動調心ころ軸受および円筒ころ軸受を組み合わせた軸受が使用されていた。図５は、自動調心ころ軸受１０１を風力発電機の主軸に使用した場合の概略図である。図５を参照して、自動調心ころ軸受１０１は、内輪１０２と、左右の列に配置された複数の調心ころ１０３ａ、１０３ｂと、複数の調心ころ１０３ａ、１０３ｂの間隔を保持する保持器１０４と、外輪１０５とを有する。自動調心ころ軸受１０１は、風を受けるブレード１１１が一方端に設けられた主軸１１２に取り付けられ、ハウジング１１３に組み込まれる。このように取り付けられた自動調心ころ軸受１０１と円筒ころ軸受とを組み合わせて、風力発電機の主軸に使用していた。   The bearing used for the main shaft of the wind power generator needs to receive a radial load against the weight of the blade, a thrust load against the wind force, and a moment load. Furthermore, since the main shaft of a wind power generator has a cantilever beam structure, a bearing having self-alignment with respect to the deflection of the main shaft is required, and therefore, a combination of a self-aligning roller bearing and a cylindrical roller bearing is used. It was. FIG. 5 is a schematic view when the self-aligning roller bearing 101 is used as a main shaft of a wind power generator. Referring to FIG. 5, the self-aligning roller bearing 101 holds an inner ring 102, a plurality of aligning rollers 103 a and 103 b arranged in the left and right rows, and a plurality of aligning rollers 103 a and 103 b. A container 104 and an outer ring 105. The self-aligning roller bearing 101 is mounted on a main shaft 112 provided with a blade 111 for receiving wind at one end, and is incorporated in a housing 113. The self-aligning roller bearing 101 and the cylindrical roller bearing thus mounted are combined and used for the main shaft of the wind power generator.

しかし、上記の二つの転がり軸受を組み合わせた軸受については、部品点数が多く、その削減が求められている。また、軸受の小型化についても要求される。   However, a bearing that combines the above-mentioned two rolling bearings has a large number of parts and is required to be reduced. Moreover, it is requested | required also about size reduction of a bearing.

そのような要求に応じて、自動調心ころ軸受と比較して調心性は劣るものの、一つの軸受で大きなスラスト荷重及びラジアル荷重を受けることができる複列円錐ころ軸受が、風力発電機の主軸に使用されている。図６は、複列円錐ころ軸受１２１の断面図の一例である。図６を参照して、複列円錐ころ軸受１２１は、小径側端面が向き合うように配置された左右の内輪１２２ａ、１２２ｂと、内輪１２２ａ、１２２ｂの間に配置された内輪間座１２８と、外輪１２４と、内輪１２２ａ、１２２ｂと外輪１２４との間に配置された複数の円錐ころ１２３ａ、１２３ｂと、左右の列において複数の円錐ころ１２３ａ、１２３ｂの間隔を保持する左右の保持器とを有する。   In response to such demands, a double-row tapered roller bearing that can receive a large thrust load and radial load with a single bearing is inferior in alignment to a self-aligning roller bearing. Is used. FIG. 6 is an example of a cross-sectional view of the double row tapered roller bearing 121. Referring to FIG. 6, double-row tapered roller bearing 121 includes left and right inner rings 122a and 122b arranged so that the end surfaces on the small diameter side face each other, inner ring spacers 128 arranged between inner rings 122a and 122b, and outer rings. 124, a plurality of tapered rollers 123a, 123b disposed between the inner rings 122a, 122b and the outer ring 124, and left and right cages for holding the intervals between the plurality of tapered rollers 123a, 123b in the left and right rows.

各保持器については、大きなラジアル荷重に対する負荷容量を実現するために、円錐ころ１２３ａ、１２３ｂをより多く保持することができるピンタイプ保持器が用いられる。ピンタイプ保持器は、各円錐ころ１２３ａ、１２３ｂを貫通するピン１２５ａ、１２５ｂと、各円錐ころ１２３ａ、１２３ｂの大端面側に突出する複数のピン１２５ａ、１２５ｂの一方端を保持して環状に延びる大径側側板１２６ａ、１２６ｂと、各円錐ころ１２３ａ、１２３ｂの小端面側に突出する複数のピン１２５ａ、１２５ｂの他方端を保持して環状に延びる小径側側板１２７ａ、１２７ｂとを有する。   For each cage, a pin type cage that can hold more tapered rollers 123a and 123b is used in order to realize a load capacity against a large radial load. The pin type cage holds the ends of the pins 125a and 125b penetrating the tapered rollers 123a and 123b and the plurality of pins 125a and 125b protruding from the large end surfaces of the tapered rollers 123a and 123b, and extends in an annular shape. Large-diameter side plates 126a and 126b, and small-diameter side plates 127a and 127b that hold the other ends of the plurality of pins 125a and 125b protruding toward the small end surfaces of the tapered rollers 123a and 123b and extend annularly.

また、このようなピンタイプ保持器を使用した複列円錐ころ軸受が特開２００３−４９８４３号公報（特許文献１）に開示されており、複列円錐ころ軸受を主軸に使用した風力発電用風車が特開２００５−１０５９１７号公報（特許文献２）に開示されている。
特開２００３−４９８４３号公報（段落番号０００８〜０００９、図１） 特開２００５−１０５９１７号公報（段落番号００２０〜００３９、図２） Further, a double row tapered roller bearing using such a pin type cage is disclosed in Japanese Patent Laid-Open No. 2003-49843 (Patent Document 1), and a wind turbine for wind power generation using the double row tapered roller bearing as a main shaft. Is disclosed in Japanese Patent Laying-Open No. 2005-105917 (Patent Document 2).
JP 2003-49843 A (paragraph numbers 0008 to 0009, FIG. 1) Japanese Patent Laying-Open No. 2005-105917 (paragraph numbers 0020 to 0039, FIG. 2)

より大きな発電量を得るためには、ブレード１１１がより大きな風を受ける必要があり、そのような環境下においては、主軸を支持する軸受は、より大きなラジアル荷重やスラスト荷重、モーメント荷重を受ける。より大きなラジアル荷重を受けるためには、上記した複列円錐ころ軸受１２１の円錐ころ１２３ａ、１２３ｂのころ長さをできるだけ大きくする必要がある。また、より大きなスラスト荷重、モーメント荷重を受けるためには、外輪軌道面と複列円錐ころ軸受１２１の回転軸線とのなす角度である接触角を大きくする必要がある。   In order to obtain a larger amount of power generation, the blade 111 needs to receive a larger wind. Under such circumstances, the bearing that supports the main shaft receives a larger radial load, thrust load, and moment load. In order to receive a larger radial load, it is necessary to make the roller lengths of the tapered rollers 123a and 123b of the double-row tapered roller bearing 121 as large as possible. Further, in order to receive a larger thrust load and moment load, it is necessary to increase a contact angle that is an angle formed by the outer ring raceway surface and the rotation axis of the double row tapered roller bearing 121.

図７は、接触角を大きくした場合の複列円錐ころ軸受１２１の断面図である。図７を参照して、外輪軌道面１３１と複列円錐ころ軸受１２１の回転軸線（図示せず）とのなす角度である接触角αを大きくすると、内輪１２２ｂの大鍔１３３ｂのうち、矢印Ｙの方向の肉厚が薄くなることになる。内輪１２２ａの大鍔１３３ａについても同様である。   FIG. 7 is a sectional view of the double-row tapered roller bearing 121 when the contact angle is increased. Referring to FIG. 7, when the contact angle α, which is the angle formed between the outer ring raceway surface 131 and the rotation axis (not shown) of the double row tapered roller bearing 121, is increased, the arrow Y of the large collar 133b of the inner ring 122b The thickness in the direction of will be reduced. The same applies to the large collar 133a of the inner ring 122a.

ここで、円錐ころ１２３ｂの大端面に接する内輪１２２ｂの大鍔面１３４ｂには、円錐ころ１２３ｂを大端面で案内するため、図７中、矢印Ｙの方向に荷重がかかることになる。具体的には、たとえば、外輪１２４に、ラジアル荷重やスラスト荷重、モーメント荷重等の外力が加わった場合、その分力が円錐ころ１２３ｂを経由して、内輪１２２ｂの大鍔面１３４ｂに伝わることになる。このような場合、大鍔１３３ｂには、大鍔面１３４ｂと軌道面との交わる部分に設けられたぬすみ溝１３５ｂを中心に、矢印Ｚの方向に大きな曲げ応力がかかることになり、肉厚が薄くなり剛性が低下した大鍔１３３ｂが、割れたり、欠けたりするおそれがある。   Here, since the tapered roller 123b is guided by the large end surface to the large collar surface 134b of the inner ring 122b in contact with the large end surface of the tapered roller 123b, a load is applied in the direction of arrow Y in FIG. Specifically, for example, when an external force such as a radial load, a thrust load, or a moment load is applied to the outer ring 124, the component force is transmitted to the large collar surface 134b of the inner ring 122b via the tapered roller 123b. Become. In such a case, a large bending stress is applied to the large collar 133b in the direction of the arrow Z around the thin groove 135b provided at the intersection of the large collar surface 134b and the raceway surface. There is a risk that the large spear 133b, which has become thin and has reduced rigidity, may crack or chip.

ここで、ころ長さを短くして、荷重作用方向である矢印Ｙの方向の大鍔１３３ｂの肉厚を確保することも可能であるが、上記したようにラジアル荷重に対する剛性を維持する観点から、円錐ころ１２３ａ、１２３ｂのころ長さを短くすることもできない。   Here, it is possible to shorten the roller length to secure the wall thickness of the large flange 133b in the direction of the arrow Y that is the load acting direction, but from the viewpoint of maintaining the rigidity against the radial load as described above. The roller lengths of the tapered rollers 123a and 123b cannot be shortened.

この発明は、内輪の大鍔が割れたり、欠けたりするおそれがない円錐ころ軸受およびこのような軸受を使用した風力発電機の主軸支持構造を提供することを目的とする。   An object of the present invention is to provide a tapered roller bearing that does not cause the inner ring to be cracked or chipped, and a main shaft support structure for a wind power generator using such a bearing.

この発明に係る円錐ころ軸受は、外輪と、内輪と、外輪と内輪との間に配置された複数の円錐ころと、複数の円錐ころの間隔を保持する保持器とを備える。ここで、上記した内輪は、円錐ころの大端面に接する大鍔面と、大鍔外径面との間に斜面部を設ける。   A tapered roller bearing according to the present invention includes an outer ring, an inner ring, a plurality of tapered rollers disposed between the outer ring and the inner ring, and a cage that holds a space between the plurality of tapered rollers. Here, the above-described inner ring is provided with a slope portion between a large collar surface in contact with the large end face of the tapered roller and a large collar outer diameter surface.

このような斜面部を設けることにより、荷重作用方向の大鍔の肉厚が増すことになり、荷重作用方向における大鍔の剛性をあげることができる。   By providing such a slope portion, the thickness of the large bowl in the load acting direction is increased, and the rigidity of the large bowl in the load acting direction can be increased.

好ましくは、斜面部は、円錐台形状の面を形成し、その母線は円錐ころの中心軸線方向に沿って延びている。このように構成することにより、簡単な構成で、荷重作用方向に対して荷重を受け易い方向の肉厚を増すことができる。   Preferably, the slope portion forms a truncated cone-shaped surface, and the generatrix thereof extends along the direction of the central axis of the tapered roller. By comprising in this way, the thickness of the direction which is easy to receive a load with respect to a load action direction can be increased with a simple structure.

より好ましくは、内輪の内径面から大鍔面の最大外径位置に至るまでの厚み寸法をＡとし、内輪の内径面から大鍔外径面に至るまでの厚み寸法をＢとしたときに、Ｂ≧１．０５Ａの関係が成立し、さらに好ましくは、Ｂ≦１．２０Ａの関係が成立する。   More preferably, when the thickness dimension from the inner diameter surface of the inner ring to the maximum outer diameter position of the large collar surface is A and the thickness dimension from the inner diameter surface of the inner ring to the outer diameter surface of the large collar is B, The relationship of B ≧ 1.05A is established, and more preferably, the relationship of B ≦ 1.20A is established.

このように構成することにより、大鍔が割れたり、欠けたりするおそれがない最低限の剛性を維持する肉厚を確保することができる。また、内輪の最大外径等その他の寸法も考慮して、肉厚を増す量を適当にすることができる。   By comprising in this way, the thickness which maintains the minimum rigidity which does not have a possibility that a big crack may be cracked or chipped can be ensured. In addition, the amount of increase in wall thickness can be made appropriate in consideration of other dimensions such as the maximum outer diameter of the inner ring.

さらに好ましくは、円錐ころの大端面側のピッチ円の直径と、大鍔外径面の直径とが等しい。こうすることにより、円錐ころをより安定して転動させることができる。ここで、「等しい」とは、円錐ころの大端面側のピッチ円の直径の値と、大鍔外径面の直径の値とが、ほぼ近似していることをいう。   More preferably, the diameter of the pitch circle on the large end face side of the tapered roller is equal to the diameter of the outer diameter surface of the large collar. By carrying out like this, a tapered roller can be rolled more stably. Here, “equal” means that the value of the diameter of the pitch circle on the large end face side of the tapered roller is approximately approximate to the value of the diameter of the outer diameter surface of the large collar.

この発明の他の局面においては、風力発電機の主軸支持構造は、風力を受けるブレードと、その一端がブレードに固定され、ブレードとともに回転する主軸と、固定部材に組み込まれ、主軸を回転自在に支持する円錐ころ軸受とを有する風力発電機の主軸支持構造である。上記した円錐ころ軸受は、外輪と、内輪と、外輪と内輪との間に配置された複数の円錐ころと、複数の円錐ころの間隔を保持する保持器とを備える。ここで、上記した内輪は、円錐ころの大端面に接する大鍔面と、大鍔外径面との間に斜面部を設ける。   In another aspect of the present invention, the main shaft support structure of the wind power generator includes a blade that receives wind power, one end of which is fixed to the blade, the main shaft that rotates together with the blade, and a fixed member that can rotate the main shaft. A main shaft support structure of a wind power generator having a tapered roller bearing to be supported. The above-mentioned tapered roller bearing includes an outer ring, an inner ring, a plurality of tapered rollers disposed between the outer ring and the inner ring, and a cage that holds the intervals between the plurality of tapered rollers. Here, the above-described inner ring is provided with a slope portion between a large collar surface in contact with the large end face of the tapered roller and a large collar outer diameter surface.

このように構成することにより、荷重作用方向における大鍔の剛性が増すことになり、内輪の大鍔が割れたり、欠けたりするおそれがなく接触角を大きくすることができ、より大きなスラスト荷重およびモーメント荷重を受けることができる。   By configuring in this way, the rigidity of the large cage in the load acting direction is increased, and the contact angle can be increased without the possibility of cracking or chipping of the inner race, so that a larger thrust load and Can receive moment load.

この発明によれば、内輪の大鍔面と大鍔外径面との間に斜面部を設けたので、荷重作用方向に対する大鍔の肉厚が増すことになることになり、大鍔の剛性をあげることができる。その結果、内輪の大鍔が割れたり、欠けたりするおそれがなく接触角を大きくすることができ、より大きなスラスト荷重を受けることができる。   According to the present invention, since the slope portion is provided between the large collar surface and the large collar outer diameter surface of the inner ring, the thickness of the large collar relative to the load acting direction is increased, and the rigidity of the large collar is increased. Can give. As a result, there is no fear that the inner ring is cracked or chipped, the contact angle can be increased, and a larger thrust load can be received.

また、このような円錐ころ軸受を風力発電機の主軸に使用すれば、内輪の大鍔が割れたり、欠けたりするおそれがなく接触角を大きくすることができるので、より大きなスラスト荷重およびモーメント荷重を受けることができる。   In addition, if such a tapered roller bearing is used for the main shaft of a wind power generator, the contact angle can be increased without the possibility of cracking or chipping the inner ring, so a larger thrust load and moment load. Can receive.

以下、この発明の実施の形態を図面を参照して説明する。図１は、この発明の一実施形態に係る円錐ころ軸受を複列で使用した場合の複列円錐ころ軸受１１に含まれる内輪１２ｂを示した断面図である。図１を参照して、内輪１２ｂは円錐ころの大端面を案内する大鍔２１ｂと、円錐ころの小端面を案内する小鍔２２ｂと、円錐ころを転動させる軌道面２３ｂとを有する。   Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional view showing an inner ring 12b included in a double row tapered roller bearing 11 when the tapered roller bearing according to an embodiment of the present invention is used in a double row. Referring to FIG. 1, inner ring 12b has a large flange 21b for guiding the large end face of the tapered roller, a small flange 22b for guiding the small end face of the tapered roller, and a raceway surface 23b for rolling the tapered roller.

内輪１２ｂには、円錐ころの大端面に接し、大端面を案内する面である大鍔面２７ｂと、内輪１２ｂの大鍔２１ｂ側の外径面である大鍔外径面２６ｂとの間に、円周方向に連なった斜面部２８ｂが設けられている。ここで、斜面部２８ｂとは、大鍔面２７ｂと大鍔外径面２６ｂとの間に設けられた傾斜のことをいい、矢印Ｙの方向に大鍔２１ｂの肉厚を増すことによって現れる領域をいう。この場合、斜面部２８ｂは、一つの面でなく、多数の面で構成されていてもよく、また、緩やかな曲面等で構成されていてもよい。なお、大鍔面２７ｂと斜面部２８ｂとの境界部分Ｘには、Ｃ面やＲ面等の面取りがなされている。   The inner ring 12b is in contact with the large end surface of the tapered roller and between the large collar surface 27b that guides the large end surface and the large collar outer diameter surface 26b that is the outer diameter surface on the large collar 21b side of the inner ring 12b. In addition, a slope portion 28b that is continuous in the circumferential direction is provided. Here, the slope portion 28b refers to an inclination provided between the large collar surface 27b and the large collar outer diameter surface 26b, and is an area that appears by increasing the thickness of the large collar 21b in the direction of arrow Y. Say. In this case, the slope portion 28b may be configured by a number of surfaces instead of a single surface, or may be configured by a gently curved surface. A chamfer such as a C surface or an R surface is chamfered at the boundary portion X between the large collar surface 27b and the slope portion 28b.

内輪１２ｂの大鍔面２７ｂには、円錐ころ（図示せず）を介して、ラジアル荷重やスラスト荷重、モーメント荷重等の外力の作用した場合、また、内部アキシアルすき間が負の場合等において、矢印Ｙの方向に荷重がかかる。また、矢印Ｙの方向の荷重に対して、ぬすみ溝２４ｂを中心に、大鍔２１ｂに対して矢印Ｚの方向に大きな曲げ応力もかかる。しかし、大鍔２１ｂは、斜面部２８ｂを設けることにより、荷重作用方向である矢印Ｙの方向に肉厚を増しているため、大鍔２１ｂの剛性をあげることができ、矢印Ｙの方向の荷重や、矢印Ｚの方向の大きな曲げ応力に対し、割れたり、欠けたりすることはない。   An arrow is applied to the large collar surface 27b of the inner ring 12b when an external force such as a radial load, a thrust load, or a moment load is applied via a tapered roller (not shown), or when the internal axial clearance is negative. A load is applied in the Y direction. Further, with respect to the load in the direction of the arrow Y, a large bending stress is also applied in the direction of the arrow Z with respect to the large collar 21b, centering on the fillet groove 24b. However, since the large collar 21b is provided with the inclined surface portion 28b, the thickness of the large collar 21b is increased in the direction of the arrow Y, which is the direction of the load, so that the rigidity of the large collar 21b can be increased and the load in the direction of the arrow Y can be increased. Moreover, it does not crack or chip with respect to a large bending stress in the direction of arrow Z.

このように構成することにより、ラジアル荷重やスラスト荷重、モーメント荷重等の外力の作用時等における大鍔２１ｂへの荷重や、曲げ応力に対する剛性を維持する肉厚を十分に確保しているため、大鍔２１ｂが割れたり、欠けたりすることがない。したがって、大鍔２１ｂが割れたり、欠けたりするおそれなく内輪１２ｂを含んだ複列円錐ころ軸受の接触角を大きくすることができ、より大きなスラスト荷重を受けることができる。   By configuring in this way, a sufficient thickness is maintained to maintain the rigidity against the load and bending stress on the large collar 21b when an external force such as a radial load, a thrust load, and a moment load is applied. The large bowl 21b is not cracked or chipped. Therefore, the contact angle of the double-row tapered roller bearing including the inner ring 12b can be increased without fear of the large flange 21b being cracked or chipped, and a larger thrust load can be received.

なお、斜面部２８ｂの寸法については、回転軸（図示せず）と当接する面である内輪１２ｂの内径面２５ｂから大鍔面２７ｂの最大外径位置に至るまでの厚み寸法をＡとし、内径面２５ｂから大鍔外径面２６ｂに至るまでの厚み寸法をＢとしたときに、Ｂ≧１．０５Ａの関係が成立し、さらに好ましくは、Ｂ≦１．２０Ａの関係が成立する。   In addition, about the dimension of the slope part 28b, let A be the thickness dimension from the inner diameter surface 25b of the inner ring 12b, which is a surface in contact with the rotating shaft (not shown), to the maximum outer diameter position of the large collar surface 27b, and the inner diameter. When the thickness dimension from the surface 25b to the large outer diameter surface 26b is B, the relationship of B ≧ 1.05A is established, and more preferably, the relationship of B ≦ 1.20A is established.

Ｂが１．０５Ａ以下であると、ラジアル荷重やスラスト荷重、モーメント荷重等の外力の作用時における大鍔２１ｂへの荷重や、曲げ応力に対して、大鍔２１ｂの剛性を維持する肉厚を十分に確保することができず、大鍔２１ｂが割れたり、欠けたりするおそれがある。また、Ｂが１．２０Ａ以上であると、内輪１２ｂの寸法関係において、大鍔外径面２６ｂが許容できる最大外径よりも大きくなるおそれがある。   When B is 1.05 A or less, the thickness to maintain the rigidity of the large flange 21b against the load on the large flange 21b or the bending stress when an external force such as a radial load, a thrust load, or a moment load is applied. It cannot be secured sufficiently, and there is a possibility that the large bowl 21b may be cracked or chipped. Further, if B is 1.20 A or more, there is a possibility that the large outer diameter surface 26b is larger than the allowable maximum outer diameter in the dimensional relationship of the inner ring 12b.

さらに好ましくは、内輪１２ｂを組み込んだ円錐ころ軸受において、後述する円錐ころの大端面側のピッチ円の直径と、内輪１２ｂの大鍔外径面２６ｂの直径とを等しくする。こうすることにより、より最適な肉厚量とすることができる。ここで、ピッチ円とは、軸方向からみて、円錐ころの大端面の中心が、回転軸を中心に回転する際に描く円をいう。   More preferably, in the tapered roller bearing incorporating the inner ring 12b, the diameter of the pitch circle on the large end face side of the tapered roller, which will be described later, is made equal to the diameter of the large flange outer diameter surface 26b of the inner ring 12b. By carrying out like this, it can be set as more optimal wall thickness. Here, the pitch circle refers to a circle drawn when the center of the large end face of the tapered roller rotates around the rotation axis when viewed from the axial direction.

図２は、図１に示した内輪１２ｂを含む円錐ころ軸受を複列で使用した場合の複列円錐ころ軸受１１を表した断面図である。図２を参照して、複列円錐ころ軸受１１は、小径側端面が互いに向き合うよう配置された左右の内輪１２ａ、１２ｂと、左右の内輪１２ａ、１２ｂの間に配置された内輪間座１８と、左右の内輪１２ａ、１２ｂに対応する軌道面を有する外輪１４と、内輪１２ａ、１２ｂと外輪１４の間に配置された複数の円錐ころ１３ａ、１３ｂと、左右の列において複数の円錐ころ１３ａ、１３ｂの間隔を保持する左右の保持器とを有する。ここで、内輪１２ｂに向き合うよう配置された内輪１２ａは、内輪１２ｂと同じ構成であり、内輪１２ａの大鍔面２７ａと大鍔外径面２６ａとの間には、斜面部２８ａが設けられている。   FIG. 2 is a sectional view showing the double row tapered roller bearing 11 when the tapered roller bearing including the inner ring 12b shown in FIG. 1 is used in a double row. Referring to FIG. 2, double-row tapered roller bearing 11 includes left and right inner rings 12 a and 12 b arranged so that the end surfaces on the small diameter side face each other, and an inner ring spacer 18 arranged between left and right inner rings 12 a and 12 b. The outer ring 14 having a raceway corresponding to the left and right inner rings 12a, 12b, the plurality of tapered rollers 13a, 13b disposed between the inner rings 12a, 12b and the outer ring 14, and the plurality of tapered rollers 13a in the left and right rows, And left and right cages that hold a distance of 13b. Here, the inner ring 12a disposed so as to face the inner ring 12b has the same configuration as the inner ring 12b, and a slope portion 28a is provided between the large collar surface 27a and the large collar outer diameter surface 26a of the inner ring 12a. Yes.

内輪１２ａ、１２ｂは、大きなスラスト荷重およびモーメント荷重を受けるため、外輪軌道面と複列円錐ころ軸受１１の回転軸線（図示せず）とのなす角度である接触角が大きく構成されている。好ましくは、接触角は４０°〜４７°の範囲内に設定されている。   Since the inner rings 12a and 12b receive a large thrust load and moment load, a contact angle that is an angle formed between the outer ring raceway surface and the rotation axis (not shown) of the double row tapered roller bearing 11 is configured to be large. Preferably, the contact angle is set within a range of 40 ° to 47 °.

内輪１２ａと１２ｂの間には、小径側側板１７ａ、１７ｂとの干渉を避け得る形状を有する内輪間座１８が配置されている。内輪間座１８は、その両端面がそれぞれ左右の内輪１２ａ、１２ｂの小径側端面に接しており、軸受の組み込み時や、ラジアル荷重やスラスト荷重、モーメント荷重等の外力の作用時等に互いの内輪１２ａ、１２ｂから圧力がかかる。したがって、内輪間座１８には、その圧力に耐えるだけの剛性が必要である。剛性を確保するためには、たとえば、内輪間座１８の中央部の径方向の断面積を大きくする等、内輪間座１８の径方向の厚みを増すことが必要である。   An inner ring spacer 18 having a shape capable of avoiding interference with the small-diameter side plates 17a and 17b is disposed between the inner rings 12a and 12b. Both end surfaces of the inner ring spacer 18 are in contact with the small-diameter side end surfaces of the left and right inner rings 12a and 12b, respectively. When the bearing is assembled or when an external force such as a radial load, a thrust load, or a moment load is applied, the inner ring spacer 18 Pressure is applied from the inner rings 12a, 12b. Therefore, the inner ring spacer 18 needs to be rigid enough to withstand the pressure. In order to ensure rigidity, it is necessary to increase the radial thickness of the inner ring spacer 18, for example, by increasing the radial sectional area of the central portion of the inner ring spacer 18.

外輪１４は、中央部が径方向に凸状の断面形状をしており、内輪１２ａ、１２ｂとの間に複数の円錐ころ１３ａ、１３ｂを保持している。本実施形態では、外輪１４は一つで構成されているが、内輪１２ａ、１２ｂに対してそれぞれ別個の外輪が設けられていてもよい。   The outer ring 14 has a cross-sectional shape whose central portion is convex in the radial direction, and holds a plurality of tapered rollers 13a and 13b between the inner rings 12a and 12b. In the present embodiment, one outer ring 14 is configured, but separate outer rings may be provided for the inner rings 12a and 12b, respectively.

円錐ころ１３ａ、１３ｂは、外輪１４と内輪１２ａ、１２ｂとの間に配置されている。また、後述するピンタイプ保持器による保持を可能にするため、円錐ころ１３ａ、１３ｂには、小端面から大端面にかけてピンを挿通するための貫通穴が設けられている。   The tapered rollers 13a and 13b are disposed between the outer ring 14 and the inner rings 12a and 12b. Further, in order to enable holding by a pin type cage described later, the tapered rollers 13a and 13b are provided with through holes for inserting pins from the small end surface to the large end surface.

保持器は、円錐ころ１３ａ、１３ｂをより多く保持することができるピンタイプ保持器を使用している。左右の各保持器は、各円錐ころ１３ａ、１３ｂを貫通するピン１５ａ、１５ｂと、各円錐ころ１３ａ、１３ｂの小端面側に突出する複数のピン１５ａ、１５ｂの一方端を保持する小径側側板１７ａ、１７ｂと、各円錐ころ１３ａ、１３ｂの大端面側に突出する複数のピン１５ａ、１５ｂの他方端を保持する大径側側板１６ａ、１６ｂとを有する。   As the cage, a pin type cage that can hold more tapered rollers 13a and 13b is used. Each of the left and right cages includes a pin 15a, 15b that passes through each of the tapered rollers 13a, 13b, and a small-diameter side plate that holds one end of the plurality of pins 15a, 15b protruding toward the small end surface of each of the tapered rollers 13a, 13b. 17a, 17b and large-diameter side plates 16a, 16b that hold the other ends of the plurality of pins 15a, 15b protruding to the large end face side of the tapered rollers 13a, 13b.

ここで、斜面部２８ａ、２８ｂは、円錐台形状の面を形成し、その母線は円錐ころ１３ａ、１３ｂの中心軸線１９ａ、１９ｂの方向に沿って延びていることにしてもよい。こうすることにより、荷重を受け易い方向に大鍔２１ａ、２１ｂの肉厚を増すことができる。また、内輪１２ａ、１２ｂを含んだ複列円錐ころ軸受１１の組み立てにおいて、大鍔２１ａ、２１ｂと近接する大径側側板１６ａ、１６ｂとの干渉を避けることができる。この場合、中心軸線１９ａ、１９ｂと母線とが平行であってもよいし、互いの線が若干の角度を有する関係であってもよい。   Here, the slope portions 28a and 28b may form a truncated cone shape, and the generatrix thereof may extend along the direction of the central axes 19a and 19b of the tapered rollers 13a and 13b. By doing so, the thickness of the large bowls 21a and 21b can be increased in the direction in which the load is easily received. Further, in assembling the double row tapered roller bearing 11 including the inner rings 12a and 12b, it is possible to avoid interference between the large flanges 21a and 21b and the large-diameter side plates 16a and 16b. In this case, the central axis lines 19a and 19b and the bus line may be parallel, or the mutual lines may have a slight angle.

小径側側板１７ａ、１７ｂおよび大径側側板１６ａ、１６ｂのいずれも複列円錐ころ軸受１１の回転軸線を中心に環状に延びており、リング状である。小径側側板１７ａ、１７ｂは内輪１２ａ、１２ｂの小鍔側に配置されており、大鍔側に配置された大径側側板１６ａ、１６ｂよりも内径が小さい。また、小径側側板１７ａ、１７ｂおよび大径側側板１６ａ、１６ｂは、いずれも多量のピン１５ａ、１５ｂを保持するため、一定の剛性が必要である。剛性や生産性等の観点から、小径側側板１７ａ、１７ｂおよび大径側側板１６ａ、１６ｂの断面形状は四角形状であることが好適である。ここで、剛性等を確保することができれば、断面形状が円状や楕円状等、他の形状の小径側側板１７ａ、１７ｂおよび大径側側板１６ａ、１６ｂであっても、特に問題はない。   Each of the small-diameter side plates 17a and 17b and the large-diameter side plates 16a and 16b extends annularly around the rotation axis of the double row tapered roller bearing 11, and has a ring shape. The small-diameter side plates 17a and 17b are disposed on the small flange side of the inner rings 12a and 12b, and the inner diameter is smaller than the large-diameter side plates 16a and 16b disposed on the large collar side. In addition, the small-diameter side plates 17a and 17b and the large-diameter side plates 16a and 16b both hold a large amount of pins 15a and 15b, and therefore need a certain rigidity. From the viewpoint of rigidity, productivity, and the like, it is preferable that the cross-sectional shapes of the small-diameter side plates 17a and 17b and the large-diameter side plates 16a and 16b are rectangular. Here, there is no particular problem even if the small-diameter side plates 17a and 17b and the large-diameter side plates 16a and 16b have other shapes such as a circular shape and an elliptical shape as long as rigidity can be ensured.

特に、大径側側板１６ａ、１６ｂは、複列円錐ころ軸受１１の組み立てる際に、斜面部２８ａ、２８ｂと近接する位置にある。そのため、斜面部２８ａ、２８ｂが大径側側板１６ａ、１６ｂの存する方向に角度を有する場合、大径側側板１６ａ、１６ｂと斜面部２８ａ、２８ｂとが干渉するおそれがある。このような場合、斜面部２８ａ、２８ｂと干渉しないよう、大径側側板１６ａ、１６ｂの干渉部分に逃げ部を設ける等、大径側側板１６ａ、１６ｂの形状について、多少の変形を行ってもよい。   In particular, the large-diameter side plates 16a and 16b are located close to the inclined surface portions 28a and 28b when the double row tapered roller bearing 11 is assembled. Therefore, when the slope portions 28a and 28b have an angle in the direction in which the large-diameter side plates 16a and 16b exist, the large-diameter side plates 16a and 16b and the slope portions 28a and 28b may interfere with each other. In such a case, even if the large-diameter side plates 16a and 16b are slightly deformed, for example, a relief portion is provided at the interference portion of the large-diameter side plates 16a and 16b so as not to interfere with the slope portions 28a and 28b. Good.

なお、先の実施の形態においては、円錐ころ１３ａ、１３ｂを保持する保持器としてピンタイプ保持器を使用したが、これに限らず、プレス保持器、成型保持器、揉みぬき保持器等を使用してもよい。このように構成することにより、用途等に応じて最適な保持器を選択して、複列円錐ころ軸受１１を構成することができる。   In the previous embodiment, the pin type cage is used as the cage for holding the tapered rollers 13a and 13b. However, the present invention is not limited to this, and a press cage, a molded cage, a kneading cage, etc. are used. May be. By configuring in this way, it is possible to configure the double-row tapered roller bearing 11 by selecting an optimal cage according to the application.

また、先の実施の形態においては、複列円錐ころ軸受１１が内輪間座１８を含むこととしたが、これに限らず、内輪間座１８を設けず、内輪の小鍔から軸方向に延びて内輪の小径側端面とが当接する内輪突合せ部を内輪１２ａ、１２ｂに設けてもよい。このように構成することにより、複列円錐ころ軸受１１を構成する部材を削減することができる。   In the previous embodiment, the double row tapered roller bearing 11 includes the inner ring spacer 18. However, the present invention is not limited to this, and the inner ring spacer 18 is not provided, and extends in the axial direction from the inner ring of the inner ring. The inner rings 12a and 12b may be provided with inner ring butting portions that come into contact with the small-diameter side end surface of the inner ring. By comprising in this way, the member which comprises the double row tapered roller bearing 11 can be reduced.

なお、先の実施の形態においては、この発明の実施の形態にかかる円錐ころ軸受として複列円錐ころ軸受を用いて説明したが、これに限らず、単列の円錐ころ軸受を複数使用し、各円錐ころ軸受を組み合わせて用いる場合、さらには、単列の円錐ころ軸受を単独で用いた場合についても同様に適用される。具体的には、単列の円錐ころ軸受は、外輪と、内輪と、外輪と内輪との間に配置された複数の円錐ころと、複数の円錐ころの間隔を保持する保持器とを備え、内輪は、円錐ころの大端面に接する大鍔面と、大鍔外径面との間に斜面部が設けられている。   In the previous embodiment, the double-row tapered roller bearing has been described as the tapered roller bearing according to the embodiment of the present invention, but not limited thereto, a plurality of single-row tapered roller bearings are used, In the case where the tapered roller bearings are used in combination, the same applies to the case where a single row tapered roller bearing is used alone. Specifically, the single-row tapered roller bearing includes an outer ring, an inner ring, a plurality of tapered rollers disposed between the outer ring and the inner ring, and a cage that holds a space between the plurality of tapered rollers, The inner ring is provided with a slope portion between a large collar surface in contact with the large end surface of the tapered roller and a large collar outer diameter surface.

図３および図４は、上記した円錐ころ軸受を主軸支持軸受３５として適用した、風力発電機の主軸支持構造の一例を示している。主軸支持構造の主要部品を支持するナセル３２のケーシング３３は、高い位置で、旋回座軸受３１を介して支持台３０上に水平旋回自在に設置されている。風力を受けるブレード３７を一端に固定する主軸３６は、ナセル３２のケーシング３３内で、軸受ハウジング３４に組み込まれた主軸支持軸受３５を介して、回転自在に支持されている、主軸３６の他端は増速機３８に接続され、この増速機３８の出力軸が発電機３９のロータ軸に結合されている。ナセル３２は、旋回用モータ４０により、減速機４１を介して任意の角度に旋回させられる。   3 and 4 show an example of a main shaft support structure of a wind power generator in which the above-described tapered roller bearing is applied as a main shaft support bearing 35. FIG. The casing 33 of the nacelle 32 that supports the main components of the spindle support structure is installed on the support base 30 via a swivel bearing 31 at a high position so as to be able to turn horizontally. A main shaft 36 that fixes a blade 37 that receives wind power to one end is rotatably supported in a casing 33 of the nacelle 32 via a main shaft support bearing 35 incorporated in a bearing housing 34. Is connected to the speed increaser 38, and the output shaft of the speed increaser 38 is coupled to the rotor shaft of the generator 39. The nacelle 32 is turned at an arbitrary angle by the turning motor 40 via the speed reducer 41.

軸受ハウジング３４に組み込まれた主軸支持軸受３５は、この発明の一実施形態に係る円錐ころ軸受を複列で使用した場合の複列円錐ころ軸受であって、外輪と、小径側端面を向き合わせるよう配置された左右の内輪と、左右の内輪の間に配置された内輪間座と、外輪と左右の内輪との間に配置された複数の円錐ころと、左右の列において複数の円錐ころの間隔を保持する左右の保持器とを備える。上記した各保持器は、各円錐ころを貫通するピンと、各円錐ころの小端面側に突出する複数のピンの一方端を保持して環状に延びる小径側側板と、各円錐ころの大端面側に突出する複数のピンの他方端を保持して環状に延びる大径側側板とを有する。ここで、上記した各内輪は、円錐ころの大端面に接する大鍔面と、大鍔外径面との間に斜面部を設ける。   The main shaft support bearing 35 incorporated in the bearing housing 34 is a double row tapered roller bearing when the tapered roller bearing according to one embodiment of the present invention is used in a double row, and the outer ring faces the end surface on the small diameter side. Left and right inner rings, inner ring spacers arranged between the left and right inner rings, a plurality of tapered rollers arranged between the outer ring and the left and right inner rings, and a plurality of tapered rollers in the left and right rows And left and right cages for holding the gap. Each of the cages described above includes a pin that passes through each tapered roller, a small-diameter side plate that extends annularly while holding one end of a plurality of pins protruding to the small end surface side of each tapered roller, and a large end surface side of each tapered roller And a large-diameter side plate extending annularly while holding the other ends of the plurality of pins projecting. Here, each of the inner rings described above is provided with a slope portion between the large collar surface in contact with the large end face of the tapered roller and the large collar outer diameter surface.

主軸支持軸受３５を、このような構成の複列円錐ころ軸受にすることにより、大鍔の肉厚を増すことができるので、内輪の大鍔が割れたり、欠けたりすることがなく接触角を大きくすることができ、より大きなスラスト荷重およびモーメント荷重を受けることができる。その結果、より大きなスラスト荷重およびモーメント荷重を受けることができる風力発電機の主軸支持構造を提供することができる。   By making the main shaft support bearing 35 into a double-row tapered roller bearing having such a configuration, the thickness of the large collar can be increased, so that the large diameter of the inner ring is not cracked or chipped, and the contact angle is increased. It can be increased and can receive larger thrust loads and moment loads. As a result, it is possible to provide a main shaft support structure for a wind power generator that can receive larger thrust loads and moment loads.

なお、この場合についても、この発明の実施の形態に係る主軸支持構造に用いる主軸支持軸受として複列円錐ころ軸受を使用したが、これに限らず、単列の円錐ころ軸受を複数使用し、各円錐ころ軸受を組み合わせて用いてもよいし、さらには、単列の円錐ころ軸受を単独で用いてもよい。   In this case as well, a double row tapered roller bearing was used as the main shaft support bearing used in the main shaft support structure according to the embodiment of the present invention, but not limited to this, a plurality of single row tapered roller bearings were used, The tapered roller bearings may be used in combination, or a single row tapered roller bearing may be used alone.

以上、図面を参照してこの発明の実施形態を説明したが、この発明は、図示した実施形態のものに限定されない。図示した実施形態に対して、この発明と同一の範囲内において、あるいは均等の範囲内において、種々の修正や変形を加えることが可能である。   As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

この発明に係る円錐ころ軸受および風力発電機の主軸支持構造は、内輪の大鍔が割れたり、欠けたりすることなく接触角を大きくすることができるため、特に、大きなラジアル荷重やスラスト荷重、モーメント荷重を受ける円錐ころ軸受および風力発電機の主軸支持構造に有効に利用できる。   The main shaft support structure of the tapered roller bearing and the wind power generator according to the present invention can increase the contact angle without cracking or chipping the inner ring, so that particularly large radial load, thrust load, moment It can be effectively used for a tapered roller bearing and a main shaft support structure of a wind power generator.

この発明の一実施形態に係る円錐ころ軸受を複列円錐ころ軸受として使用した場合の複列円錐ころ軸受１１に含まれる内輪１２ｂを示す断面図である。It is sectional drawing which shows the inner ring | wheel 12b contained in the double row tapered roller bearing 11 at the time of using the tapered roller bearing which concerns on one Embodiment of this invention as a double row tapered roller bearing. 図１に示す内輪１２ｂを含む複列円錐ころ軸受１１の断面図である。It is sectional drawing of the double row tapered roller bearing 11 containing the inner ring | wheel 12b shown in FIG. この発明の一実施形態に係る風力発電機の主軸支持構造の一例を示す図である。It is a figure which shows an example of the spindle support structure of the wind power generator concerning one Embodiment of this invention. 図３に示した風力発電機の主軸支持構造の図解的側面図である。FIG. 4 is a schematic side view of the main shaft support structure of the wind power generator shown in FIG. 3. 自動調心ころ軸受１０１を風力発電機の主軸に使用した場合の概略図である。It is the schematic at the time of using the self-aligning roller bearing 101 for the main axis | shaft of a wind power generator. 従来における複列円錐ころ軸受１２１の一例を示す断面図である。It is sectional drawing which shows an example of the conventional double row tapered roller bearing 121. 従来における接触角が大きい場合の複列円錐ころ軸受１２１を示す断面図である。It is sectional drawing which shows the double row tapered roller bearing 121 in the case of the conventional large contact angle.

符号の説明Explanation of symbols

１１ 複列円錐ころ軸受、１２ａ，１２ｂ 内輪、１３ａ，１３ｂ 円錐ころ、１４ 外輪、１５ａ，１５ｂ ピン、１６ａ，１６ｂ 大径側側板、１７ａ，１７ｂ 小径側側板、１８ 内輪間座、１９ａ，１９ｂ 中心軸線、２１ａ，２１ｂ 大鍔、２２ｂ 小鍔、２３ｂ 軌道面、２４ｂ ぬすみ溝、２５ｂ 内径面、２６ａ，２６ｂ 大鍔外径面、２７ａ，２７ｂ 大鍔面、２８ａ，２８ｂ 斜面部、３０ 支持台、３１ 旋回座軸受、３２ ナセル、３３ ケーシング、３４ 軸受ハウジング、３５ 主軸支持軸受、３６ 主軸、３７ ブレード、３８ 増速機、３９ 発電機、４０ 旋回用モータ、４１ 減速機。   11 Double row tapered roller bearing, 12a, 12b Inner ring, 13a, 13b Tapered roller, 14 Outer ring, 15a, 15b Pin, 16a, 16b Large diameter side plate, 17a, 17b Small diameter side plate, 18 Inner ring spacer, 19a, 19b Center Axis line, 21a, 21b, large surface, 22b, small surface, 23b raceway surface, 24b fillet groove, 25b inner surface, 26a, 26b large surface, 27a, 27b large surface, 28a, 28b slope, 30 support base 31 bearing seat, 32 nacelle, 33 casing, 34 bearing housing, 35 spindle support bearing, 36 spindle, 37 blade, 38 speed increaser, 39 generator, 40 motor for turning, 41 speed reducer.

Claims (6)

外輪と、内輪と、外輪と内輪との間に配置された複数の円錐ころと、複数の円錐ころの間隔を保持する保持器とを備えた円錐ころ軸受であって、
前記内輪は、前記円錐ころの大端面に接する大鍔面と、大鍔外径面との間に斜面部を設けた、円錐ころ軸受。 A tapered roller bearing comprising an outer ring, an inner ring, a plurality of tapered rollers disposed between the outer ring and the inner ring, and a retainer for maintaining a spacing between the plurality of tapered rollers,
The inner ring is a tapered roller bearing in which a slope portion is provided between a large collar surface in contact with a large end surface of the tapered roller and an outer diameter surface of the large collar. 前記斜面部は、円錐台形状の面を形成し、その母線は前記円錐ころの中心軸線方向に沿って延びている、請求項１に記載の円錐ころ軸受。 The tapered roller bearing according to claim 1, wherein the inclined surface portion forms a truncated cone-shaped surface, and a generatrix thereof extends along a central axis direction of the tapered roller. 前記内輪の内径面から前記大鍔面の最大外径位置に至るまでの厚み寸法をＡとし、前記内輪の内径面から前記大鍔外径面に至るまでの厚み寸法をＢとしたときに、
Ｂ≧１．０５Ａの関係が成立する、請求項１または２に記載の円錐ころ軸受。 When the thickness dimension from the inner diameter surface of the inner ring to the maximum outer diameter position of the large collar surface is A, and the thickness dimension from the inner diameter surface of the inner ring to the outer diameter surface of the large collar is B,
The tapered roller bearing according to claim 1, wherein a relationship of B ≧ 1.05 A is established. 前記寸法関係において、
Ｂ≦１．２０Ａの関係が成立する、請求項１〜３のいずれかに記載の円錐ころ軸受。 In the dimensional relationship,
The tapered roller bearing according to claim 1, wherein a relationship of B ≦ 1.20 A is established. 前記円錐ころの大端面側のピッチ円の直径と、前記大鍔外径面の直径とが等しい、請求項１〜４のいずれかに記載の円錐ころ軸受。 The tapered roller bearing according to any one of claims 1 to 4, wherein a diameter of a pitch circle on a large end surface side of the tapered roller is equal to a diameter of the outer diameter surface of the large collar. 風力を受けるブレードと、
その一端が前記ブレードに固定され、ブレードとともに回転する主軸と、
固定部材に組み込まれ、前記主軸を回転自在に支持する円錐ころ軸受とを有する風力発電機の主軸支持構造であって、
前記円錐ころ軸受は、外輪と、内輪と、外輪と内輪との間に配置された複数の円錐ころと、複数の円錐ころの間隔を保持する保持器とを備え、
前記内輪は、前記円錐ころの大端面に接する大鍔面と、大鍔外径面との間に斜面部を設けた、風力発電機の主軸支持構造。 A blade that receives wind,
One end of which is fixed to the blade and rotates with the blade;
A main shaft support structure for a wind power generator, which is incorporated in a fixed member and has a tapered roller bearing that rotatably supports the main shaft,
The tapered roller bearing includes an outer ring, an inner ring, a plurality of tapered rollers disposed between the outer ring and the inner ring, and a cage that holds a space between the plurality of tapered rollers,
The inner ring is a main shaft support structure of a wind power generator in which a slope portion is provided between a large collar surface in contact with the large end surface of the tapered roller and an outer diameter surface of the large collar.
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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008298283A (en) * 2008-03-28 2008-12-11 Ntn Corp Wind-power plant spindle supporting roller bearing, and spindle supporting structure of wind-power plant
US8476781B2 (en) 2010-08-10 2013-07-02 Kabushiki Kaisha Yaskawa Denki Rotating electric machine, wind power generation system and method of manufacturing rotating electric machine
US8764304B2 (en) 2006-09-08 2014-07-01 Ntn Corporation Roller bearing, retainer segment of roller bearing for supporting main shaft of wind-power generator, and main shaft support structure of wind-power generator
WO2017073325A1 (en) * 2015-10-29 2017-05-04 Ntn株式会社 Method for manufacturing bearing ring, and multi-row tapered roller bearing and manufacturing method therefor
WO2017073327A1 (en) * 2015-10-29 2017-05-04 Ntn株式会社 Multi-row tapered roller bearing, and method for manufacturing bearing ring and multi-row tapered roller bearing
CN113958620A (en) * 2021-10-14 2022-01-21 三一重能股份有限公司 Wind turbine generator and transmission system thereof
US20220356901A1 (en) * 2019-06-25 2022-11-10 Schaeffler Technologies AG & Co. KG Roller bearing assembly for determining loads
WO2024111363A1 (en) * 2022-11-21 2024-05-30 Ntn株式会社 Roller bearing

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54150535A (en) * 1978-05-16 1979-11-26 Koyo Seiko Co Ltd Roller bearing
JPH0632747U (en) * 1992-09-30 1994-04-28 三菱自動車工業株式会社 Tapered roller bearing device
JPH11236920A (en) * 1998-02-24 1999-08-31 Nippon Seiko Kk Rolling bearing
JP2000130443A (en) * 1998-10-26 2000-05-12 Ntn Corp Tapered roller bearing and holder for tapered roller bearing
JP2000170775A (en) * 1998-12-03 2000-06-20 Ntn Corp Conical roller bearing and gear shaft support device for vehicle
JP2001317551A (en) * 2000-05-10 2001-11-16 Ntn Corp Tapered roller bearing
JP2005105917A (en) * 2003-09-30 2005-04-21 Mitsubishi Heavy Ind Ltd Wind power generating windmill
JP2005147331A (en) * 2003-11-18 2005-06-09 Ntn Corp Double row rolling bearing

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54150535A (en) * 1978-05-16 1979-11-26 Koyo Seiko Co Ltd Roller bearing
JPH0632747U (en) * 1992-09-30 1994-04-28 三菱自動車工業株式会社 Tapered roller bearing device
JPH11236920A (en) * 1998-02-24 1999-08-31 Nippon Seiko Kk Rolling bearing
JP2000130443A (en) * 1998-10-26 2000-05-12 Ntn Corp Tapered roller bearing and holder for tapered roller bearing
JP2000170775A (en) * 1998-12-03 2000-06-20 Ntn Corp Conical roller bearing and gear shaft support device for vehicle
JP2001317551A (en) * 2000-05-10 2001-11-16 Ntn Corp Tapered roller bearing
JP2005105917A (en) * 2003-09-30 2005-04-21 Mitsubishi Heavy Ind Ltd Wind power generating windmill
JP2005147331A (en) * 2003-11-18 2005-06-09 Ntn Corp Double row rolling bearing

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* Cited by examiner, † Cited by third party
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US9664231B2 (en) 2006-09-08 2017-05-30 Ntn Corporation Roller bearing, retainer segment of roller bearing for supporting main shaft of wind-power generator
US8764304B2 (en) 2006-09-08 2014-07-01 Ntn Corporation Roller bearing, retainer segment of roller bearing for supporting main shaft of wind-power generator, and main shaft support structure of wind-power generator
US10408267B2 (en) 2006-09-08 2019-09-10 Ntn Corporation Tapered roller bearing and main shaft support structure of wind-power generator using same
US9810263B2 (en) 2006-09-08 2017-11-07 Ntn Corporation Retainer segment for a roller bearing for supporting a main shaft of a wind-power generator
JP2008298283A (en) * 2008-03-28 2008-12-11 Ntn Corp Wind-power plant spindle supporting roller bearing, and spindle supporting structure of wind-power plant
US8476781B2 (en) 2010-08-10 2013-07-02 Kabushiki Kaisha Yaskawa Denki Rotating electric machine, wind power generation system and method of manufacturing rotating electric machine
EP3369953A4 (en) * 2015-10-29 2019-06-19 NTN Corporation Method for manufacturing bearing ring, and multi-row tapered roller bearing and manufacturing method therefor
JP2017082945A (en) * 2015-10-29 2017-05-18 Ntn株式会社 Double row tapered roller bearing, race ring and method of manufacturing double row tapered roller bearing
WO2017073327A1 (en) * 2015-10-29 2017-05-04 Ntn株式会社 Multi-row tapered roller bearing, and method for manufacturing bearing ring and multi-row tapered roller bearing
US10378076B2 (en) 2015-10-29 2019-08-13 Ntn Corporation Double row tapered roller bearing, bearing ring, and method for producing double row tapered roller bearing
WO2017073325A1 (en) * 2015-10-29 2017-05-04 Ntn株式会社 Method for manufacturing bearing ring, and multi-row tapered roller bearing and manufacturing method therefor
US10718377B2 (en) 2015-10-29 2020-07-21 Ntn Corporation Method for producing bearing ring, double row tapered roller bearing, and method for producing double row tapered roller bearing
US20220356901A1 (en) * 2019-06-25 2022-11-10 Schaeffler Technologies AG & Co. KG Roller bearing assembly for determining loads
US12049920B2 (en) * 2019-06-25 2024-07-30 Schaeffler Technologies AG & Co. KG Roller bearing assembly for determining loads
CN113958620A (en) * 2021-10-14 2022-01-21 三一重能股份有限公司 Wind turbine generator and transmission system thereof
WO2024111363A1 (en) * 2022-11-21 2024-05-30 Ntn株式会社 Roller bearing

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