JP2017032123A - Double-row self-aligning roller bearing - Google Patents

Double-row self-aligning roller bearing Download PDF

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JP2017032123A
JP2017032123A JP2015155722A JP2015155722A JP2017032123A JP 2017032123 A JP2017032123 A JP 2017032123A JP 2015155722 A JP2015155722 A JP 2015155722A JP 2015155722 A JP2015155722 A JP 2015155722A JP 2017032123 A JP2017032123 A JP 2017032123A
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rollers
row
roller
rows
double
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津森　幸久
Yukihisa Tsumori
幸久 津森
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2015155722A priority Critical patent/JP2017032123A/en
Priority to PCT/JP2016/072525 priority patent/WO2017022718A1/en
Publication of JP2017032123A publication Critical patent/JP2017032123A/en
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    • 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
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • Wind Motors (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a double-row self-aligning roller bearing which can secure a large load capacity, and can elongate a life with a standard width dimension.SOLUTION: In a double-row self-aligning roller bearing 1, rollers 4, 5 are interposed between an inner ring 2 and an outer ring 3 in left and right two rows. A raceway surface 3a of the outer ring 3 is spherical, and the rollers 4, 5 in the left and right two rows are formed into cross section shapes which progress along the raceway surface 3a of the outer ring 3 at external peripheral faces. The rollers 4, 5 in the left and right two rows differ from each other in lengths L1, L2 of the left-row roller 4 and the right-row roller 5, and also either of the rollers 4, 5 in either of the left and right rows is a symmetric roller whose position of a maximum diameter is located in a center of the roller length. A center rib does not exist in a portion between the left-row roller 4 and the right-row roller 5 at an external peripheral face of the inner ring 2.SELECTED DRAWING: Figure 1

Description

この発明は、左右２列のころに不均等な荷重が負荷される用途、例えば風力発電装置や産業機械の主軸を支持する軸受等に適用される複列自動調心ころ軸受に関する。   The present invention relates to a double-row self-aligning roller bearing applied to an application in which uneven loads are applied to the left and right two-row rollers, for example, a bearing that supports a main shaft of a wind power generator or an industrial machine.

風力発電装置の主軸を支持する軸受には、ブレードやロータヘッドの自重によるラジアル荷重の他に、風力によるアキシアル荷重が作用する。軸受が複列自動調心ころ軸受である場合、左右２列のころのうち、主に一方の列のころだけがアキシアル荷重を受ける。つまり、一方の列のころがラジアル荷重とアキシアル荷重の両方を受けるのに対し、他方の列のころはほぼラジアル荷重だけを受ける。ラジアル荷重に比べて一方向のアキシアル荷重が大きいため、アキシアル荷重を受ける列のころは、アキシアル荷重を殆ど受けない列のころと比べて、摩耗や表面損傷が生じやすく、転がり寿命が短い。このアキシアル荷重を受ける列のころの転がり寿命により、軸受全体の実質寿命が決定される。   In addition to the radial load caused by the weight of the blade and the rotor head, an axial load caused by wind force acts on the bearing that supports the main shaft of the wind power generator. When the bearing is a double-row self-aligning roller bearing, only one of the two rows of left and right rollers mainly receives an axial load. That is, one row of rollers receives both a radial load and an axial load, while the other row of rollers receives only a radial load. Since the axial load in one direction is larger than the radial load, the roller in the row subjected to the axial load is more likely to be worn or damaged, and the rolling life is shorter than the roller in the row not subjected to the axial load. The actual life of the entire bearing is determined by the rolling life of the rollers in the row subjected to this axial load.

そこで、例えば図５に示すように、内輪２と外輪３との間に介在する左右各列のころ４，５の長さＬ１，Ｌ２を互いに異ならせることで、アキシアル荷重を受ける列のころ５の負荷容量を、アキシアル荷重を殆ど受けない列のころ４の負荷容量よりも大きくすることが提案されている（特許文献１）。左右各列のころ４，５の負荷容量を適正に定めることにより、左右各列のころ４，５の転がり寿命がほぼ同じになり、軸受全体の実質寿命を向上させることができる。   Therefore, for example, as shown in FIG. 5, the lengths L1 and L2 of the left and right rows of rollers 4 and 5 interposed between the inner ring 2 and the outer ring 3 are made different from each other, whereby the row of rollers 5 receiving the axial load. It has been proposed to make the load capacity of the roller 4 larger than the load capacity of the rollers 4 in a row that hardly receives an axial load (Patent Document 1). By appropriately determining the load capacity of the rollers 4 and 5 in the left and right rows, the rolling life of the rollers 4 and 5 in the left and right rows is almost the same, and the substantial life of the entire bearing can be improved.

国際公開第２００５／０５００３８号パンフレットInternational Publication No. 2005/050038 Pamphlet 米国特許第２０１４／０１１２６０７号明細書US 2014/0112607

図５に示す特許文献１に記載の複列自動調心ころ軸受１は、内輪２の外周面の中間部に、左右各列のころ４，５を案内する中つば８が設置されている。中つば８は、ころ４，５の誘起スラスト荷重に耐えうる強度を確保するために、ある程度の幅方向の肉厚が必要である。そのため、軸受の限られた幅寸法内では、アキシアル荷重を受ける列のころ５の長さをあまり長くすることができず、軸受全体の負荷容量を思うように高められないという課題がある。   In the double-row self-aligning roller bearing 1 described in Patent Document 1 shown in FIG. 5, an intermediate collar 8 that guides the rollers 4 and 5 in the left and right rows is installed in the middle portion of the outer peripheral surface of the inner ring 2. The middle collar 8 needs to have a certain thickness in the width direction in order to ensure strength that can withstand the induced thrust load of the rollers 4 and 5. Therefore, within the limited width dimension of the bearing, there is a problem that the length of the roller 5 in the row receiving the axial load cannot be increased so much that the load capacity of the entire bearing cannot be increased as expected.

なお、前記中つば８は、左右各列のころ４，５が非対称ころである場合に、ころ４，５が幅方向にずれないように設けられる。「非対称ころ」とは、図６に誇張して示すように、最大径の位置がころ長さの中央から外れたころのことである。左右各列のころ４，５が対称ころである場合、図７に示すように、中つばを設けずに、自由回転する案内輪１３で左右各列のころ４，５を案内することもある（特許文献２）。「対称ころ」とは、最大径の位置がころ長さの中央に位置するころのことである。但し、特許文献２の例は、左列のころ４と右列のころ５の長さが同じである。   The middle collar 8 is provided so that the rollers 4 and 5 do not shift in the width direction when the rollers 4 and 5 in the left and right rows are asymmetric rollers. The “asymmetric roller” is a roller in which the position of the maximum diameter deviates from the center of the roller length, as exaggeratedly shown in FIG. When the left and right rows of rollers 4 and 5 are symmetrical rollers, as shown in FIG. 7, the left and right rows of rollers 4 and 5 may be guided by the freely rotating guide wheels 13 without providing a middle collar. (Patent Document 2). “Symmetric rollers” are rollers whose maximum diameter is located at the center of the roller length. However, in the example of Patent Document 2, the lengths of the left row roller 4 and the right row roller 5 are the same.

この発明の目的は、規格の幅寸法のままで、大きな負荷容量の確保および長寿命化を図ることができる複列自動調心ころ軸受を提供することである。   An object of the present invention is to provide a double-row self-aligning roller bearing capable of ensuring a large load capacity and extending the life while maintaining the standard width dimension.

この発明の複列自動調心ころ軸受は、内輪と外輪との間に左右２列にころが介在し、前記外輪の軌道面が球面状であり、前記左右２列のころは外周面が前記外輪の軌道面に沿う断面形状である複列自動調心ころ軸受であって、前記左右２列のころは、左列のころと右列のころの長さが互いに異なり、かつ左右いずれの列のころも最大径の位置がころ長さの中央に位置する対称ころであり、前記内輪の外周面における前記左列のころと前記右列のころ間の部分に中つばが存在しないことを特徴とする。   In the double-row self-aligning roller bearing according to the present invention, rollers are interposed in two right and left rows between the inner ring and the outer ring, the raceway surface of the outer ring is spherical, and the outer circumferential surface of the left and right two-row rollers is the outer surface. A double-row self-aligning roller bearing having a cross-sectional shape along the raceway surface of the outer ring, wherein the left and right two-row rollers have different lengths of the left and right rows of rollers, and either left or right row The roller is also a symmetric roller whose maximum diameter is located at the center of the roller length, and there is no middle collar in the portion between the left row roller and the right row roller on the outer peripheral surface of the inner ring. And

この構成によると、左右の列のころを対称ころとしたことにより、ころの誘起スラスト荷重の発生がなくなり、内輪の中つばを無くすことが可能となった。中つばが存在しないと、中つばが存在する場合と比較して、ころ長さを長くすることができる。そのため、同じ幅寸法の軸受であっても、軸受全体の負荷容量が向上する。   According to this configuration, since the left and right rows of rollers are symmetric rollers, no induced thrust load is generated on the rollers, and the inner collar of the inner ring can be eliminated. When the middle collar is not present, the roller length can be increased as compared with the case where the middle collar is present. Therefore, even if the bearings have the same width, the load capacity of the entire bearing is improved.

この複列自動調心ころ軸受は、左右の列に互いに大きさが異なる荷重が作用する用途、例えば片方の列はアキシアル荷重とラジアル荷重の両方を受け、もう片方の列は殆どラジアル荷重のみを受けるような用途に用いられる。その場合、アキシアル荷重を受ける列のころは、長さが長いころとし、かつアキシアル荷重を殆ど受けない列のころは、長さが短いころとする。また、アキシアル荷重を受ける列のころは、アキシアル荷重を殆ど受けない列のころよりも、接触角を大きくする。これにより、負荷容量の大きな長さが長いころが、アキシアル荷重とラジアル荷重の両方を受け、負荷容量の小さな長さが短いころがラジアル荷重のみを受けることとなる。このように、負荷に応じた適正な支持が左右のころ列で行われることにより、左右各列のころの転がり寿命がほぼ同じになり、軸受全体の実質寿命を向上させることができる。   This double-row spherical roller bearing is used in applications where loads of different magnitudes are applied to the left and right rows, for example, one row receives both axial and radial loads, and the other row receives almost only radial loads. Used for receiving applications. In this case, the roller in the row receiving the axial load is a long roller, and the roller in the row receiving almost no axial load is the roller having a short length. In addition, the roller of the row that receives the axial load has a larger contact angle than the roller of the row that receives almost no axial load. Accordingly, a roller having a large load capacity and a long length receives both an axial load and a radial load, and a roller having a small load capacity and a short length receives only a radial load. As described above, when the right and left roller trains support appropriately according to the load, the rolling life of the left and right roller rows becomes substantially the same, and the substantial life of the entire bearing can be improved.

この発明において、前記左右２列のころを保持する保持器と前記内輪との間に、これら保持器および前輪に対して自由回転し前記左右２列のころを案内する案内輪が設けられていても良い。
案内輪が設けられていると、前記中つばが無くても、ころのスキューを抑えることができる。 In the present invention, a guide wheel that freely rotates with respect to the cage and the front wheel and guides the left and right two rows of rollers is provided between the cage that holds the two rows of left and right rollers and the inner ring. Also good.
If the guide ring is provided, the skew of the rollers can be suppressed even without the middle collar.

この複列自動調心ころ軸受は、風力発電装置の主軸の支持に適する。
この複列自動調心ころ軸受は、中つばを有しないことにより、ころの長さを長くして大きな負荷容量を持たせることができる反面、ころの支持が内輪と外輪だけとなり高速回転には適さない。しかし、風力発電装置の主軸は低速回転しかしないので、高速回転に適さないという特性はあまり問題にならない。むしろ、負荷容量が増加することのメリットの方が大きい。従って、この複列自動調心ころ軸受は、風力発電装置の主軸の支持に適した軸受と言える。 This double row self-aligning roller bearing is suitable for supporting the main shaft of the wind power generator.
This double-row spherical roller bearing does not have a middle collar, so the roller length can be lengthened to give a large load capacity, but the roller supports only the inner ring and outer ring for high-speed rotation. Not suitable. However, since the main shaft of the wind power generator has only low speed rotation, the characteristic that it is not suitable for high speed rotation is not a problem. Rather, the merit of increasing the load capacity is greater. Therefore, this double row spherical roller bearing can be said to be a bearing suitable for supporting the main shaft of the wind power generator.

この発明の複列自動調心ころ軸受は、内輪と外輪との間に左右２列にころが介在し、前記外輪の軌道面が球面状であり、前記左右２列のころは外周面が前記外輪の軌道面に沿う断面形状である複列自動調心ころ軸受であって、前記左右２列のころは、左列のころと右列のころの長さが互いに異なり、かつ左右いずれの列のころも最大径の位置がころ長さの中央に位置する対称ころであり、前記内輪の外周面における前記左列のころと前記右列のころ間の部分に中つばが存在しないため、規格の幅寸法のままで、大きな負荷容量の確保および長寿命化を図ることができる。   In the double-row self-aligning roller bearing according to the present invention, rollers are interposed in two right and left rows between the inner ring and the outer ring, the raceway surface of the outer ring is spherical, and the outer circumferential surface of the left and right two-row rollers is the outer surface. A double-row self-aligning roller bearing having a cross-sectional shape along the raceway surface of the outer ring, wherein the left and right two-row rollers have different lengths of the left and right rows of rollers, and either left or right row The roller is also a symmetric roller whose maximum diameter is located in the center of the roller length, and there is no middle brim in the portion between the left row roller and the right row roller on the outer peripheral surface of the inner ring. With this width dimension, a large load capacity can be secured and the life can be extended.

この発明の一実施形態にかかる複列自動調心ころ軸受の断面図である。It is sectional drawing of the double row self-aligning roller bearing concerning one Embodiment of this invention. この発明の異なる実施形態にかかる複列自動調心ころ軸受の断面図である。It is sectional drawing of the double row self-aligning roller bearing concerning different embodiment of this invention. 風力発電装置の主軸支持装置の一例の一部を切り欠いて表した斜視図である。It is the perspective view which notched and represented a part of example of the spindle support apparatus of the wind power generator. 同主軸支持装置の破断側面図である。It is a fracture side view of the spindle support device. 提案例の複列自動調心ころ軸受の断面図である。It is sectional drawing of the double row self-aligning roller bearing of a proposal example. 非対称ころの説明図である。It is explanatory drawing of an asymmetrical roller. 異なる提案例の複列自動調心ころ軸受の断面図である。It is sectional drawing of the double row self-aligning roller bearing of a different proposal example.

この発明の一実施形態を図１と共に説明する。
この複列自動調心ころ軸受１は、内輪２と外輪３との間に幅方向に並ぶ左右２列にころ４，５を介在させてある。外輪３の軌道面３ａは球面状であり、左右各列のころ４，５は外周面が外輪３の軌道面３ａに沿う断面形状である。言い換えると、ころ４，５の外周面は、外輪３の軌道面３ａに沿った円弧を中心線Ｃ１，Ｃ２回りに回転させた回転曲面である。内輪２には、左右各列のころ４，５の外周面に沿う断面形状の複列の軌道面２ａ，２ｂが形成されている。内輪２の外周面の両端には、つば６，７がそれぞれ設けられている。内輪２の外周面の中央部、すなわち左列のころ４と右列のころ５間の部分に中つばが存在しない。 An embodiment of the present invention will be described with reference to FIG.
In this double-row self-aligning roller bearing 1, rollers 4 and 5 are interposed in two right and left rows arranged in the width direction between an inner ring 2 and an outer ring 3. The raceway surface 3 a of the outer ring 3 has a spherical shape, and the rollers 4 and 5 in each of the left and right rows have a cross-sectional shape along the raceway surface 3 a of the outer ring 3. In other words, the outer peripheral surfaces of the rollers 4 and 5 are rotating curved surfaces obtained by rotating an arc along the raceway surface 3a of the outer ring 3 around the center lines C1 and C2. The inner ring 2 is formed with double-row raceway surfaces 2a and 2b having a cross-sectional shape along the outer peripheral surfaces of the rollers 4 and 5 in the left and right rows. At both ends of the outer peripheral surface of the inner ring 2, collars 6 and 7 are provided, respectively. There is no middle collar at the center of the outer peripheral surface of the inner ring 2, that is, the portion between the left row roller 4 and the right row roller 5.

左右各列のころ４，５は、いずれも最大径Ｄ１ｍａｘ，Ｄ２ｍａｘの位置がころ長さの中央Ａ１，Ａ２に位置する対称ころである。対称ころからなるころ４，５は、誘起スラスト荷重が発生しない。このため、前記中つばでころ４，５を支える必要がなく、中つばを無くすことができる。 The rollers 4 and 5 in each of the left and right rows are symmetrical rollers in which the positions of the maximum diameters D1 max and D2 max are located at the center A1 and A2 of the roller length. The rollers 4 and 5 made of symmetrical rollers do not generate an induced thrust load. For this reason, it is not necessary to support the rollers 4 and 5 with the middle collar, and the middle collar can be eliminated.

左列のころ４と右列のころ５は、中心線Ｃ１，Ｃ２に沿った長さＬ１，Ｌ２が互いに異なり、かつ左列のころ４の接触角θ１と右列のころ５の接触角θ２は、互いに異なっている。この場合、長さＬ２の長いころ５の接触角θ２の方が、長さＬ１の短いころ４の接触角θ１よりも大きく設定されている。   The left row roller 4 and the right row roller 5 have different lengths L1 and L2 along the center lines C1 and C2, and the contact angle θ1 of the left row roller 4 and the contact angle θ2 of the right row roller 5 are different. Are different from each other. In this case, the contact angle θ2 of the long roller 5 with the length L2 is set larger than the contact angle θ1 of the short roller 4 with the length L1.

この実施形態では、左右各列のころ４，５の最小径が同じとされている。よって、長さＬ２の長いころ５の最大径Ｄ２ｍａｘの方が、長さＬ１の短いころ４の最大径Ｄ１ｍａｘよりも大きい。左右各列のころ４，５の最大径Ｄ１ｍａｘ，Ｄ２ｍａｘが同じであっても良く、またこの実施形態とは逆に、長さＬ１の短いころ４の最大径Ｄ１ｍａｘの方が、長さＬ１の長いころ５の最大径Ｄ２ｍａｘよりも大きくても良い。 In this embodiment, the minimum diameters of the rollers 4 and 5 in the left and right rows are the same. Therefore, the maximum diameter D2 max of the long roller 5 with the length L2 is larger than the maximum diameter D1 max of the short roller 4 with the length L1. The maximum diameters D1 max and D2 max of the rollers 4 and 5 in the left and right rows may be the same. Contrary to this embodiment, the maximum diameter D1 max of the short roller 4 having the length L1 is longer. It may be larger than the maximum diameter D2 max of the roller 5 having a long length L1.

左右各列のころ４，５は、それぞれ保持器１０により保持されている。この実施形態の保持器１０は、左右各列のころ４，５間に位置する円環部１１から左右両側に複数の柱部１２ａ，１２ｂが延びた櫛状であって、左側の柱部１２ａ間のポケットに左列のころ４が保持され、右側の柱部１２ｂ間のポケットに右列のころ５が保持される。つまり、この保持器１０は、左右の列のころ４，５を保持する一体型の保持器である。このような一体型の保持器１０は、２つの保持器で左右の列のころ４，５をそれぞれ個別に保持する場合よりも、円環部１１の幅を広くできるため強度が高いという利点がある。   The rollers 4 and 5 in each of the left and right rows are held by a cage 10. The cage 10 of this embodiment has a comb shape in which a plurality of column portions 12a and 12b extend on both left and right sides from an annular portion 11 located between the rollers 4 and 5 in the left and right rows, and the left column portion 12a. The left row rollers 4 are held in the pockets between them, and the right row rollers 5 are held in the pockets between the right column portions 12b. That is, the cage 10 is an integrated cage that holds the rollers 4 and 5 in the left and right rows. Such an integrated cage 10 has an advantage that the strength of the annular portion 11 can be increased because the width of the annular portion 11 can be made wider than when the rollers 4 and 5 in the left and right rows are individually held by two cages. is there.

また、左右の列間における内輪２と保持器１０との間に、左右各列のころ４，５の端面に当接してこれらのころ４，５を案内する案内輪１３が設けられている。案内輪１３は、ころ４，５、内輪２、および保持器１０のいずれに対しても自由回転するように設けられている。このような案内輪１３を設けることで、内輪２の外周面の中央部に中つばが無くても、ころ４，５のスキューを抑えることができる。   A guide wheel 13 is provided between the inner ring 2 and the cage 10 between the left and right rows so as to contact the end surfaces of the rollers 4 and 5 in the left and right rows and guide these rollers 4 and 5. The guide wheel 13 is provided so as to freely rotate with respect to any of the rollers 4 and 5, the inner ring 2, and the cage 10. By providing such a guide wheel 13, the skew of the rollers 4 and 5 can be suppressed even if there is no middle collar at the center of the outer peripheral surface of the inner ring 2.

この構成の複列自動調心ころ軸受１は、左右のころ列に互いに大きさが異なる荷重が作用する用途、例えば片方のころ列にアキシアル荷重とラジアル荷重とを受け、もう片方のころ列には殆どラジアル荷重のみを受けるような用途に用いられる。具体的には、風力発電装置の主軸支持軸受等に用いられる。その場合、アキシアル荷重を受ける列のころは、長さＬ２が長いころ５とし、かつアキシアル荷重を殆ど受けない列のころは、長さＬ１が短いころ４とする。また、アキシアル荷重を受ける列のころ５の接触角θ２を、アキシアル荷重を殆ど受けない列のころ４の接触角θ１よりも大きくする。   The double-row self-aligning roller bearing 1 having this configuration is used in applications in which loads of different sizes act on the left and right roller rows, for example, one roller row receives an axial load and a radial load, and the other roller row receives Is used for applications that receive almost only radial loads. Specifically, it is used for a spindle support bearing of a wind power generator. In this case, the roller in the row that receives the axial load is the roller 5 with the long length L2, and the roller in the row that receives almost no axial load is the roller 4 with the short length L1. Further, the contact angle θ2 of the row of rollers 5 that receives the axial load is made larger than the contact angle θ1 of the row of rollers 4 that hardly receives the axial load.

この構成によると、左右各列のころ４，５を対称ころとしたことにより、ころ４，５の誘起スラスト荷重が発生しなくなり、内輪２の中つばを無くすことが可能となっている。内輪２に中つばが存在しないと、中つばが存在する場合と比較して、ころ４，５の長さを長くすることが可能である。そのため、同じ幅寸法の軸受であっても、軸受全体の負荷容量を高めることができる。   According to this configuration, since the rollers 4 and 5 in the left and right rows are symmetric rollers, the induced thrust load of the rollers 4 and 5 is not generated, and the middle collar of the inner ring 2 can be eliminated. If there is no middle collar in the inner ring 2, it is possible to increase the length of the rollers 4, 5 as compared with the case where a middle collar is present. Therefore, even if the bearings have the same width, the load capacity of the entire bearing can be increased.

また、アキシアル荷重を受ける列のころ５の接触角θ２を、アキシアル荷重を殆ど受けない列のころ４の接触角θ１よりも大きくしてあるため、負荷容量の大きな長さＬ２の長いころ５がアキシアル荷重とラジアル荷重の両方を受け、負荷容量の小さな長さＬ１の短いころ４はほぼラジアル荷重のみを受けることとなる。このように、負荷に応じた適正な支持が左右のころ列で行われることにより、左右各列のころ４，５の転がり寿命がほぼ同じになり、軸受全体の実質寿命を向上させることができる。   In addition, since the contact angle θ2 of the row roller 5 that receives the axial load is larger than the contact angle θ1 of the row roller 4 that hardly receives the axial load, the long roller 5 having a large load capacity L2 is large. Both the axial load and the radial load are received, and the short roller 4 with a small load capacity and the length L1 receives almost only the radial load. As described above, when the right and left roller trains support properly according to the load, the rolling life of the rollers 4 and 5 in each of the left and right rows becomes substantially the same, and the substantial life of the entire bearing can be improved. .

図２は、図１のものと比べて保持器の構成が異なる実施形態を示す。この複列自動調心ころ軸受１は、左列のころ４を保持する左列用の保持器１０Ｌと、右列のころ５を保持する右列用の保持器１０Ｒとを備える。左列用の保持器１０Ｌは、円環部１１Ｌから複数の柱部１２Ｌが左側に延び、これら柱部１２Ｌ間のポケットに左列のころ４が保持される。右列用の保持器１０Ｒは、円環部１１Ｒから複数の柱部１２Ｒが右側に延び、これら柱部１２Ｒ間のポケットに右列のころ５が保持される。   FIG. 2 shows an embodiment in which the structure of the cage is different from that of FIG. This double row self-aligning roller bearing 1 includes a left row retainer 10L for retaining the left row roller 4 and a right row retainer 10R for retaining the right row roller 5. In the left row retainer 10L, a plurality of column portions 12L extend from the annular portion 11L to the left side, and the left row rollers 4 are held in pockets between the column portions 12L. In the right row retainer 10R, a plurality of column portions 12R extend from the annular portion 11R to the right, and the right row rollers 5 are held in pockets between the column portions 12R.

両保持器１０Ｌ，１０Ｒを比較した場合、円環部１１Ｌ，１１Ｒの断面の径方向厚さは同じであるが、柱部１２Ｌ，１２Ｒの断面の径方向厚さについては、左列用の保持器１０Ｌの柱部１２Ｌの方が右列用の保持器１０Ｒの柱部１２Ｒよりも厚くしてある。このように、長さＬ２が長く負荷容量が大きい右列のころ５を保持する右列用の保持器１０Ｒの柱部１２Ｒの断面を大きくすることで、右列用の保持器１０Ｒが損傷するリスクを低減している。   When both the cages 10L and 10R are compared, the radial thicknesses of the cross sections of the annular portions 11L and 11R are the same, but the radial thicknesses of the cross sections of the column portions 12L and 12R are retained for the left row. The column portion 12L of the container 10L is thicker than the column portion 12R of the cage 10R for the right row. In this way, the right row retainer 10R is damaged by increasing the cross section of the column portion 12R of the right row retainer 10R that holds the right row rollers 5 having a long length L2 and a large load capacity. Risk is reduced.

図３、図４は、風力発電装置の主軸支持装置の一例を示す。支持台２１上に旋回座軸受２２（図４）を介してナセル２３のケーシング２３ａが水平旋回自在に設置されている。ナセル２３のケーシング２３ａ内には、軸受ハウジング２４に設置された主軸支持軸受２５を介して主軸２６が回転自在に設置され、主軸２６のケーシング２３ａ外に突出した部分に、旋回翼となるブレード２７が取り付けられている。主軸２６の他端は、増速機２８に接続され、増速機２８の出力軸が発電機２９のロータ軸に結合されている。ナセル２３は、旋回用モータ３０により、減速機３１を介して任意の角度に旋回させられる。   3 and 4 show an example of the spindle support device of the wind turbine generator. A casing 23a of the nacelle 23 is installed on the support base 21 via a swivel bearing 22 (FIG. 4) so as to be horizontally swivelable. In the casing 23 a of the nacelle 23, a main shaft 26 is rotatably installed via a main shaft support bearing 25 installed in the bearing housing 24, and a blade 27 serving as a swirl wing is formed on a portion protruding from the casing 23 a of the main shaft 26. Is attached. The other end of the main shaft 26 is connected to the speed increaser 28, and the output shaft of the speed increaser 28 is coupled to the rotor shaft of the generator 29. The nacelle 23 is turned at an arbitrary angle by the turning motor 30 via the speed reducer 31.

主軸支持軸受２５は、図示の例では２個並べて設置してあるが、１個であっても良い。この主軸支持軸受２５に、図１または図２に示す複列自動調心ころ軸受１が用いられる。その場合、ブレード２７から遠い方のころ列にラジアル荷重とアキシアル荷重の両方がかかるので、ブレード２７から遠い方のころ列に、接触角θ２が大きくかつ長さＬ２が長いころ５を用いる。ブレード２７に近い方のころ列には主としてラジアル荷重のみがかかるので、ブレード２７に近い方のころ列には、接触角θ１が小さくかつ長さＬ１が短いころ４を用いる。   In the illustrated example, two main shaft support bearings 25 are arranged side by side, but may be one. A double row self-aligning roller bearing 1 shown in FIG. 1 or 2 is used for the main shaft support bearing 25. In this case, since both the radial load and the axial load are applied to the roller row far from the blade 27, the roller 5 having a large contact angle θ2 and a long length L2 is used for the roller row far from the blade 27. Since only the radial load is mainly applied to the roller row closer to the blade 27, the roller 4 having a smaller contact angle θ1 and a shorter length L1 is used for the roller row closer to the blade 27.

図１または図２に示す複列自動調心ころ軸受１は、内輪２が中つばを有しないことにより、ころ４，５の長さＬ１，Ｌ２を長くして大きな負荷容量を持たせることができる反面、ころ４，５の支持が内輪２と外輪３だけとなり高速回転には適さない。しかし、風力発電装置の主軸２６は低速回転しかしないので、高速回転に適さないという特性はあまり問題にならない。むしろ、負荷容量が増加することのメリットの方が大きい。従って、この複列自動調心ころ軸受１は、風力発電装置の主軸２６の支持に適した軸受と言える。   In the double-row self-aligning roller bearing 1 shown in FIG. 1 or 2, the inner ring 2 does not have a middle collar, so that the lengths L1 and L2 of the rollers 4 and 5 can be increased to have a large load capacity. On the other hand, the rollers 4 and 5 are supported only by the inner ring 2 and the outer ring 3 and are not suitable for high-speed rotation. However, since the main shaft 26 of the wind power generator only rotates at a low speed, the characteristic that it is not suitable for high-speed rotation is not a problem. Rather, the merit of increasing the load capacity is greater. Therefore, it can be said that the double-row self-aligning roller bearing 1 is a bearing suitable for supporting the main shaft 26 of the wind power generator.

以上、実施例に基づいて本発明を実施するための形態を説明したが、ここで開示した実施の形態はすべての点で例示であって制限的なものではない。本発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。   As mentioned above, although the form for implementing this invention based on the Example was demonstrated, embodiment disclosed here is an illustration and restrictive at no points. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

１…複列自動調心ころ軸受
２…内輪
３…外輪
３ａ…軌道面
４，５…ころ
１０，１０Ｌ，１０Ｒ…保持器
１３…案内輪
２６…主軸
Ａ１，Ａ２…ころ長さの中央
Ｄ１ｍａｘ，Ｄ２ｍａｘ…最大径
Ｌ１，Ｌ２…ころ長さ DESCRIPTION OF SYMBOLS 1 ... Double row self-aligning roller bearing 2 ... Inner ring 3 ... Outer ring 3a ... Raceway surface 4, 5 ... Roller 10, 10L, 10R ... Cage 13 ... Guide wheel 26 ... Spindle A1, A2 ... Roller length center D1 max , D2 max ... Maximum diameter L1, L2 ... Roller length

Claims (3)

内輪と外輪との間に左右２列にころが介在し、前記外輪の軌道面が球面状であり、前記左右２列のころは外周面が前記外輪の軌道面に沿う断面形状である複列自動調心ころ軸受であって、
前記左右２列のころは、左列のころと右列のころの長さが互いに異なり、かつ左右いずれの列のころも最大径の位置がころ長さの中央に位置する対称ころであり、前記内輪の外周面における前記左列のころと前記右列のころ間の部分に中つばが存在しないことを特徴とする複列自動調心ころ軸受。 Two rows of rollers are interposed between the inner ring and the outer ring, the outer ring raceway surface is spherical, and the left and right two rows of rollers have an outer circumferential surface having a cross-sectional shape along the outer raceway surface. Self-aligning roller bearing,
The left and right two rows of rollers are symmetrical rollers in which the lengths of the left and right rows of rollers are different from each other, and the left and right rows of rollers are positioned at the center of the maximum roller length. A double-row self-aligning roller bearing, characterized in that no intermediate collar exists in a portion between the left row roller and the right row roller on the outer peripheral surface of the inner ring. 請求項１に記載の複列自動調心ころ軸受において、前記左右２列のころを保持する保持器と前記内輪との間に、これら保持器および前輪に対して自由回転し前記左右２列のころを案内する案内輪が設けられている複列自動調心ころ軸受。   2. The double-row self-aligning roller bearing according to claim 1, wherein the double-row self-aligning roller bearing is configured to freely rotate with respect to the cage and the front wheel between the cage and the inner ring that hold the two rows of left and right rollers, and Double row self-aligning roller bearing provided with guide wheels for guiding rollers. 請求項１または請求項２に記載の複列自動調心ころ軸受において、風力発電装置の主軸の支持に用いられる複列自動調心ころ軸受。   The double row spherical roller bearing according to claim 1 or 2, wherein the double row spherical roller bearing is used for supporting a main shaft of a wind power generator.
JP2015155722A 2015-08-06 2015-08-06 Double-row self-aligning roller bearing Pending JP2017032123A (en)

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PCT/JP2016/072525 WO2017022718A1 (en) 2015-08-06 2016-08-01 Double-row self-aligning roller bearing

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001140875A (en) * 1999-11-12 2001-05-22 Ntn Corp Self-aligning roller bearing
JP2004245251A (en) * 2003-02-10 2004-09-02 Nsk Ltd Automatic centering rolling bearing
WO2005050038A1 (en) * 2003-11-18 2005-06-02 Ntn Corporation Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft
JP2009063101A (en) * 2007-09-06 2009-03-26 Ntn Corp Rolling bearing
US20140112607A1 (en) * 2012-10-18 2014-04-24 Schaeffler Technologies AG & Co. KG Roller bearing for wind turbines

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001140875A (en) * 1999-11-12 2001-05-22 Ntn Corp Self-aligning roller bearing
JP2004245251A (en) * 2003-02-10 2004-09-02 Nsk Ltd Automatic centering rolling bearing
WO2005050038A1 (en) * 2003-11-18 2005-06-02 Ntn Corporation Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft
JP2009063101A (en) * 2007-09-06 2009-03-26 Ntn Corp Rolling bearing
US20140112607A1 (en) * 2012-10-18 2014-04-24 Schaeffler Technologies AG & Co. KG Roller bearing for wind turbines

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