JP2005207264A - Bearing for small wind power generator main spindle - Google Patents

Bearing for small wind power generator main spindle Download PDF

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Publication number
JP2005207264A
JP2005207264A JP2004012820A JP2004012820A JP2005207264A JP 2005207264 A JP2005207264 A JP 2005207264A JP 2004012820 A JP2004012820 A JP 2004012820A JP 2004012820 A JP2004012820 A JP 2004012820A JP 2005207264 A JP2005207264 A JP 2005207264A
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Prior art keywords
bearing
wind power
power generator
small wind
grease
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Japanese (ja)
Inventor
Naoki Nakagawa
直樹 中川
Soichi Yagi
壮一 八木
Seiji Hori
政治 堀
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2004012820A priority Critical patent/JP2005207264A/en
Publication of JP2005207264A publication Critical patent/JP2005207264A/en
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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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6622—Details of supply and/or removal of the grease, e.g. purging grease
    • 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/94—Volume
    • 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)
  • Wind Motors (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing for a small wind power generator main spindle, rotating a blade by even weak wind, reducing torque, and ensuring durability. <P>SOLUTION: The bearing 7 rotatively supports the main spindle 6 with the blade 4 of the small wind power generator 1 attached, and comprises a deep groove ball bearing lubricated with grease. An amount of grease filled into the bearing is set to 5 to 20% of the internal space S of the bearing. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

この発明は駐車場や公園の照明、企業の看板のライト、各種公共施設の照明など、種々の用途に用いられる小型風力発電機における主軸用軸受に関する。   The present invention relates to a bearing for a main shaft in a small wind power generator used for various applications such as lighting for parking lots and parks, lighting for corporate signs, and lighting for various public facilities.

近年、小型風力発電機は、環境への配慮や、商用電源を用いるには配線が長くなる場合などの対策として、種々のものが開発、実用化され、使用が増えつつある。
このような小型風力発電機では、風の強い場所や高所を選んで設置される大型の発電機と異なり、設置場所が制限される場合が多く、弱い風でもブレードが回るように支持されることが望まれる。小型風力発電機においてブレードを取付けた主軸を支持する軸受には、グリース潤滑の深溝玉軸受が用いられることが多い。深溝玉軸受は、ラジアル軸受であるが、スラスト負荷の支持が可能であり、また価格面でも有利であり、小型風力発電機における主軸の支持に好適なものとなる。また、グリース潤滑であると、メンテナンスフリー化にも優れている。
ＮＴＮ株式会社カタログ「転がり軸受総合カタログ」Ａ６３ＣＡＴ．ＮＯ．２２０２−ＶＩ／Ｊ ２００１年１２月６日発行（Ａ−７３頁） In recent years, various types of small wind power generators have been developed and put into practical use as a countermeasure for environmental considerations or when the wiring becomes long for using a commercial power supply.
In such a small wind power generator, unlike a large power generator that is installed by selecting a windy place or high place, the installation place is often limited, and it is supported so that the blade can rotate even in a weak wind It is desirable. Grease-lubricated deep groove ball bearings are often used as bearings for supporting the main shaft on which blades are mounted in a small wind power generator. Although the deep groove ball bearing is a radial bearing, it can support a thrust load and is advantageous in terms of price, and is suitable for supporting a main shaft in a small wind power generator. Grease lubrication is also excellent for maintenance-free.
NTN catalog “Rolling Bearing General Catalog” A63CAT. NO. 2202-VI / J Published on December 6, 2001 (A-73)

一般的なグリース潤滑の深溝玉軸受は、軸受空間内に封入される初期充填のグリース量が、軸受内部空間の４０％前後（３６〜５０％）とされることが多い（非特許文献１）。しかし、グリース量が４０％程度であると、グリースの粘性によるトルクが大きく、小型風力発電機の主軸の支持に用いた場合、弱い風ではブレードが回転しないことがある。   In general grease-lubricated deep groove ball bearings, the amount of initially filled grease filled in the bearing space is often about 40% (36 to 50%) of the bearing internal space (Non-patent Document 1). . However, when the amount of grease is about 40%, the torque due to the viscosity of the grease is large, and when used for supporting the main shaft of a small wind power generator, the blade may not rotate with a weak wind.

この発明の目的は、弱い風でもブレードの回転が可能な低トルクのものとでき、かつ耐久性が確保できる小型風力発電機主軸用軸受を提供することである。   An object of the present invention is to provide a bearing for a small wind power generator main shaft that has a low torque capable of rotating a blade even in a weak wind and can ensure durability.

この発明における第１の発明の小型風力発電機主軸用軸受は、小型風力発電機のブレードを取付けた主軸を回転自在に支持する軸受であって、グリース潤滑の深溝玉軸受からなり、軸受内部空間に封入されるグリース量を、軸受内部空間の５〜２０％としたことを特徴とする。ここで言うグリース量は、使用初期の封入グリース量である。軸受内部空間は、内外輪間の両端にシールを有する軸受の場合、内外輪間の両側のシールで仕切られた空間における転動体や保持器等の軸受構成部品が占める残りの空間のことである。   A bearing for a main shaft of a small wind generator according to a first aspect of the present invention is a bearing that rotatably supports a main shaft to which a blade of a small wind power generator is attached, and is constituted by a grease-lubricated deep groove ball bearing. The amount of grease enclosed in the bearing is 5 to 20% of the bearing internal space. The amount of grease referred to here is the amount of grease charged in the initial stage of use. In the case of a bearing having seals at both ends between the inner and outer rings, the bearing inner space is the remaining space occupied by bearing components such as rolling elements and cages in a space partitioned by seals on both sides between the inner and outer rings. .

小型風力発電機に用いられる程度の大きさのグリース潤滑の深溝玉軸受においては、試験によると、図２に見られるように、封入グリース量が２０％を超えた程度から、回転抵抗となるトルクが急激に大きくなる傾向が見られた。したがって、グリース封入量の最大量は２０％とすることが好ましい。グリース量が２０％以下の場合は、グリース量によるトルクの差は小さいが、封入グリース量が５％未満であると、使用に伴うグリースの劣化のため、耐久性の面で望ましくない。   In grease-lubricated deep groove ball bearings of a size that can be used for small wind power generators, as shown in FIG. 2, the torque that causes rotational resistance from the extent that the amount of enclosed grease exceeds 20%, as shown in FIG. Tended to increase rapidly. Therefore, the maximum amount of grease filled is preferably 20%. When the amount of grease is 20% or less, the difference in torque due to the amount of grease is small, but when the amount of enclosed grease is less than 5%, it is not desirable in terms of durability because the grease deteriorates with use.

この発明における第２の発明の小型風力発電機主軸用軸受は、小型風力発電機のブレードを取付けた主軸を回転自在に支持する軸受であって、油潤滑の転がり軸受からなり、前記小型風力発電機の発電電力で駆動されるポンプにより、潤滑油を前記転がり軸受に供給しかつこの転がり軸受から漏れ出た潤滑油を再度供給に用いる潤滑油循環装置を設けたことを特徴とする。
この構成の場合、油潤滑のため、グリース潤滑に比べて回転抵抗となるトルクが小さいものとできる。油潤滑であると、耐久性確保のために補給を行う必要があるが、潤滑油を転がり軸受に供給しかつこの転がり軸受から漏れ出た潤滑油を再度供給に用いる潤滑油循環装置を設けたため、優れた耐久性が得られる。ポンプの駆動に電力が必要であるが、風力発電機の軸受であり、その発電電力を用いてポンプを駆動するようにしたため、別途に電源を設ける必要がない。 A small wind power generator main shaft bearing according to a second aspect of the present invention is a bearing that rotatably supports a main shaft to which a blade of a small wind power generator is attached, and is composed of an oil-lubricated rolling bearing. According to another aspect of the present invention, there is provided a lubricating oil circulation device that supplies lubricating oil to the rolling bearing by a pump driven by power generated by the machine and uses the lubricating oil leaked from the rolling bearing for supply again.
In the case of this configuration, because of oil lubrication, it is possible to reduce torque that becomes rotational resistance compared to grease lubrication. In the case of oil lubrication, it is necessary to replenish in order to ensure durability. However, a lubricating oil circulation device is provided that supplies lubricating oil to the rolling bearing and uses again the lubricating oil leaked from the rolling bearing. Excellent durability can be obtained. Electric power is required to drive the pump, but since it is a bearing of a wind power generator and the pump is driven using the generated electric power, it is not necessary to provide a separate power source.

この発明の小型風力発電機主軸用軸受は、小型風力発電機のブレードを取付けた主軸を回転自在に支持する軸受であって、グリース潤滑の深溝玉軸受からなり、軸受空間内に封入されるグリース量を、軸受内部空間の５〜２０％としたため、弱い風でもブレードの回転が可能な低トルクのものとでき、かつ耐久性も確保できる。
この発明の他の小型風力発電機主軸用軸受は、油潤滑として、前記小型風力発電機の発電電力で駆動されるポンプにより、潤滑油を前記転がり軸受に供給しかつこの転がり軸受から漏れ出た潤滑油を再度供給に用いる潤滑油循環装置を設けたため、弱い風でもブレードの回転が可能な低トルクのものとでき、かつ耐久性も確保できる。 A bearing for a main shaft of a small wind power generator according to the present invention is a bearing that rotatably supports a main shaft on which a blade of a small wind power generator is mounted, and is a grease-lubricated deep groove ball bearing that is sealed in a bearing space. Since the amount is 5 to 20% of the internal space of the bearing, it is possible to achieve a low torque capable of rotating the blade even in a weak wind and to ensure durability.
Another small wind power generator main shaft bearing of the present invention supplies lubricating oil to the rolling bearing and leaks out from the rolling bearing by a pump driven by power generated by the small wind power generator as oil lubrication. Since the lubricating oil circulating device for supplying the lubricating oil again is provided, it is possible to achieve a low torque that can rotate the blade even in a weak wind and to ensure durability.

この発明の第１の実施形態を図１，図２と共に説明する。図１（Ａ）は小型風力発電機１の側面図であり、支持台２上にナセル３が水平旋回方向に方向転換自在に設置されている。ナセル３の前端に回転翼となるブレード４が設けられ、後部に、風向きに応じた方向にナセル３を方向転換させるための尾翼５が設けられている。このブレード４は、主軸６に取付けられている。主軸６は、ナセル３に設置された軸受７により、回転自在に支持されている。軸受７は、この実施形態にかかる小型風力発電機主軸用軸受であり、主軸６の支持に１個または複数個が用いられる。ナセル３内には、この他に主軸６の回転より発電を行う発電機８が設けられる。主軸６と発電機８の間には主軸６の回転を発電機の効率化のために増速する増速機（図示せず）を設けても良い。なお、ここで言う小型風力発電機は、発電電力が５〜６ｋｗ以下のもの、特に１ｋｗ以下のものである。   A first embodiment of the present invention will be described with reference to FIGS. FIG. 1A is a side view of a small wind power generator 1, and a nacelle 3 is installed on a support base 2 so as to be capable of changing its direction in a horizontal turning direction. A blade 4 serving as a rotating blade is provided at the front end of the nacelle 3, and a tail blade 5 for changing the direction of the nacelle 3 in a direction corresponding to the wind direction is provided at the rear part. The blade 4 is attached to the main shaft 6. The main shaft 6 is rotatably supported by a bearing 7 installed in the nacelle 3. The bearing 7 is a bearing for a small wind power generator main shaft according to this embodiment, and one or more bearings are used for supporting the main shaft 6. In addition to this, a generator 8 is provided in the nacelle 3 to generate power from the rotation of the main shaft 6. Between the main shaft 6 and the generator 8, you may provide the gearbox (not shown) which speeds up rotation of the main shaft 6 for efficiency improvement of a generator. In addition, the small wind generator said here is a thing with generated electric power of 5-6 kw or less, especially 1 kw or less.

軸受７は、グリース潤滑の深溝玉軸受からなり、内輪１１と外輪１２の間に、保持器１４に保持された玉１３が介在させている。内外輪１１，１２間の軸受内部空間Ｓの両端は、外輪１２に取付けられたシール１５により密封されている。シール１５は芯金にゴム材等の弾性体を設けた接触シールからなる。シール１５の内径側の先端は内輪１１の外径面に摺接する。なお、シール１５は非接触シールでも良く、例えば非接触の鉄板シールであっても良い。内輪１１および外輪１２の玉１３が転走する軌道溝１１ａ，１２ａは、断面形状が半円状に形成されている。軌道溝１１ａ，１２ａの曲率半径は、一般的な深溝玉軸受では、玉１３の直径の１．０２〜１．０４倍の範囲とされるが、例えば１．０８〜１．２５倍の範囲としても良い。   The bearing 7 is a grease-lubricated deep groove ball bearing, and a ball 13 held by a cage 14 is interposed between an inner ring 11 and an outer ring 12. Both ends of the bearing internal space S between the inner and outer rings 11 and 12 are sealed by seals 15 attached to the outer ring 12. The seal 15 is formed of a contact seal in which an elastic body such as a rubber material is provided on a core metal. The tip on the inner diameter side of the seal 15 is in sliding contact with the outer diameter surface of the inner ring 11. The seal 15 may be a non-contact seal, for example, a non-contact iron plate seal. The raceway grooves 11a and 12a in which the balls 13 of the inner ring 11 and the outer ring 12 roll are formed in a semicircular cross section. The radius of curvature of the raceway grooves 11a and 12a is 1.02 to 1.04 times as large as the diameter of the ball 13 in a general deep groove ball bearing, for example, as a range of 1.08 to 1.25 times. Also good.

軸受６の軸受内部空間ＳにはグリースＧを充填する。グリースＧの初期封入量は、軸受内部空間Ｓの容積の５〜２０％とする。このグリース封入量は、好ましくは、５〜１５％であり、より好ましくは５〜１０％である。
なお、軸受内部空間Ｓは、同図のようなシール付き軸受の場合は、内外輪１１，１２間の両側のシール１５で仕切られた空間における玉１３や保持器１４等の軸受構成部品が占める残りの空間のことである。 The bearing internal space S of the bearing 6 is filled with grease G. The initial amount of grease G filled is 5 to 20% of the volume of the bearing internal space S. The amount of grease filled is preferably 5 to 15%, more preferably 5 to 10%.
In the case of a bearing with a seal as shown in the figure, the bearing internal space S is occupied by bearing components such as balls 13 and cages 14 in a space partitioned by seals 15 on both sides between the inner and outer rings 11 and 12. It is the remaining space.

シール無しの軸受の場合は、軸受内部空間Ｓは、厳密には内外輪１１，１２間の空間から玉１３や保持器１４等の軸受構成部品が占める残りの空間のことになるが、シール付き軸受に対応する空間容積、つまりシールがあると仮定した場合の空間容積を、上記軸受内部空間Ｓの容積として扱うこととしている。
軸受内部空間についての一般的な厳密な定義はないが、上記非特許文献１では、軸受内部空間の容積の概略値を次式で求めることができるとされている。
Ｖ＝Ｋ・Ｗ …(1)
ここで、Ｖ：開放型軸受の空間容積（概略値）（ｃｍ3 ）、
Ｋ：軸受空間係数（軸受形式によって定められている係数）、
Ｗ：軸受の質量（ｋｇ）、
である。
Ｋの値は、深溝玉軸受であって保持器形式が打抜き保持器の場合は、例えばＫ＝６１とされる。
例えば、上記の(1) 式で定められる容積Ｖを、シール無し軸受の場合の軸受内部空間Ｓの容積と定めてもよい。 In the case of a bearing without a seal, the bearing inner space S is strictly the remaining space occupied by bearing components such as the balls 13 and the cage 14 from the space between the inner and outer rings 11, 12. The space volume corresponding to the bearing, that is, the space volume when it is assumed that there is a seal, is treated as the volume of the bearing internal space S.
Although there is no general strict definition for the bearing internal space, the non-patent document 1 states that an approximate value of the volume of the bearing internal space can be obtained by the following equation.
V = K · W (1)
Where V: space volume of open type bearing (approximate value) (cm 3 ),
K: Bearing space coefficient (coefficient determined by bearing type),
W: Mass of bearing (kg),
It is.
When the value of K is a deep groove ball bearing and the cage type is a punched cage, for example, K = 61.
For example, the volume V defined by the above equation (1) may be determined as the volume of the bearing internal space S in the case of a bearing without a seal.

この構成の小型風力発電機主軸用軸受７によると、封入グリースを軸受内部空間Ｓの２０％以下としたため、後の試験例に示すように、通常の４０％前後の封入量とする場合に比べて、回転抵抗となるトルクが大幅に小さくなる。そのため、弱い風でもブレード４の回転が可能になる。また、封入グリース量を５％以上としたため、使用に伴うグリースの劣化に対して、必要な耐久性も確保できる。
この実施形態において、内外輪１１，１２の軌道面１１ａ，１２ａの曲率半径を、玉径（玉の半径）に対して、従来の１．０２〜１．０４倍から１．０８〜１．２５倍の範囲と大きくした場合は、回転トルクがさらに低減される。軌道面１１ａ，１２ａの玉径に対する曲率半径を大きくすると、トルクが低減する反面、支持精度が低下するが、小型風力発電機１の主軸６の支持では、あまり高い精度は要求されない。そのため、曲率半径が１．２５倍まであれば、精度面の支障を生じることなく、トルク低減の効果が得られる。また曲率半径が１．０８倍以上であれば、従来の一般的な曲率半径の割合である１．０２〜１．０４倍の場合に比べて明らかなトルク低減の効果が得られる。 According to the small-sized wind power generator main shaft bearing 7 having this configuration, since the sealed grease is 20% or less of the bearing internal space S, as shown in a later test example, compared with a case where the sealed amount is about 40% as usual. Thus, the torque that becomes the rotational resistance is significantly reduced. Therefore, the blade 4 can be rotated even in a weak wind. Further, since the amount of the enclosed grease is 5% or more, necessary durability can be ensured against the deterioration of the grease due to use.
In this embodiment, the radius of curvature of the raceway surfaces 11a and 12a of the inner and outer rings 11 and 12 is 1.02 to 1.04 times 1.08 to 1.25 compared with the conventional ball diameter (ball radius). When the range is doubled, the rotational torque is further reduced. Increasing the radius of curvature of the raceway surfaces 11a and 12a with respect to the ball diameter reduces the torque, but lowers the support accuracy. However, the support of the main shaft 6 of the small wind power generator 1 does not require a very high accuracy. Therefore, if the radius of curvature is up to 1.25 times, the effect of torque reduction can be obtained without causing any problem in accuracy. In addition, when the radius of curvature is 1.08 times or more, a clear torque reduction effect can be obtained as compared with the case of 1.02 to 1.04 times that is a ratio of a conventional general radius of curvature.

図２は、グリース封入割合とトルクとの関係の試験結果を示す。供試軸受には、ＪＩＳ規格の６２０５番の深溝玉軸受を用いた。この軸受は内径が２５mmのものである。回転速度は８００ｒｐｍとした。
同図からわかるように、グリース封入割合（グリース封入量）が５％から２０％の範囲では、封入量が増えるに従ってトルクが増大する傾向は見られるが、その増大割合は僅かであり、トルク値は２０ｍＮ・ｍ程度と略一定となっている。グリース封入割合が２０％を超え、３０％程度となると、トルク値が４０Ｎ・ｍ程度と略２倍になっており、この間ではグリース封入割合が増えるに従ってトルク価は急激に増大する。４０％を超えると、６０％程度までは、略一定のトルク価となっている。
同図の結果から、トルクを低減させるには、グリース封入量（封入割合）を２０％以下とすることが好ましいことが判る。 FIG. 2 shows a test result of the relationship between the grease filling ratio and the torque. A JIS standard 6205 deep groove ball bearing was used as the test bearing. This bearing has an inner diameter of 25 mm. The rotation speed was 800 rpm.
As can be seen from the figure, when the grease filling ratio (grease filling amount) is in the range of 5% to 20%, the torque tends to increase as the filling amount increases, but the increase ratio is slight and the torque value is small. Is approximately constant at about 20 mN · m. When the grease filling ratio exceeds 20% and is about 30%, the torque value is approximately doubled to about 40 N · m. During this period, the torque value increases rapidly as the grease filling ratio increases. If it exceeds 40%, the torque value is substantially constant up to about 60%.
From the results shown in FIG. 6, it can be seen that the amount of grease (encapsulation ratio) is preferably 20% or less in order to reduce the torque.

図３は、この発明の他の実施形態を示す。この実施形態は、図１（Ａ）に示した小型風力発電機１において、その軸受７を油潤滑の深溝玉軸受とし、次の構成の潤滑油循環装置２０を設けたものである。   FIG. 3 shows another embodiment of the present invention. In this embodiment, in the small wind power generator 1 shown in FIG. 1A, the bearing 7 is an oil-lubricated deep groove ball bearing, and a lubricating oil circulation device 20 having the following configuration is provided.

この潤滑油循環装置２０は、小型風力発電機１（図１）における上記発電機８の発電電力で駆動されるポンプ２１により、潤滑油を軸受７に供給し、かつこの軸受７から漏れ出た潤滑油を再度供給に用いるものである。潤滑油循環装置２０は、油溜め２２に溜めた潤滑油を供給路２３によって軸受７内に供給するものであり、軸受７から漏れた潤滑油を受ける潤滑油受け２４を有している。潤滑油受け２４の潤滑油が、上記ポンプ２１により、循環路２５を介して油溜め２２に送られる。循環路２５の油溜め２２に対向する出口にはフィルタ２６が設けられている。油溜め２２には潤滑油の油面を検出するレベルセンサ２７が設けられ、レベルセンサ２７の検出値によってポンプ２１を駆動するモータ２８のオンオフ制御が行われる。   The lubricating oil circulation device 20 supplies lubricating oil to the bearing 7 by the pump 21 driven by the generated power of the generator 8 in the small wind power generator 1 (FIG. 1), and leaks from the bearing 7. Lubricating oil is used again for supply. The lubricating oil circulation device 20 supplies the lubricating oil stored in the oil reservoir 22 into the bearing 7 through the supply passage 23, and has a lubricating oil receiver 24 that receives the lubricating oil leaking from the bearing 7. Lubricating oil in the lubricating oil receiver 24 is sent to the oil sump 22 through the circulation path 25 by the pump 21. A filter 26 is provided at the outlet of the circulation path 25 facing the oil sump 22. The oil sump 22 is provided with a level sensor 27 for detecting the oil level of the lubricating oil, and on / off control of the motor 28 that drives the pump 21 is performed based on the detection value of the level sensor 27.

ポンプ２１のモータ２８は、発電機８の発電電力を直接用いるものであっても良いが、この例では、発電機８の発電電力を充電回路２９によって二次電池３０に充電し、二次電池３０の電力をモータ２８の駆動に用いるようにしている。   The motor 28 of the pump 21 may directly use the generated power of the generator 8, but in this example, the secondary battery 30 is charged by the charging circuit 29 with the generated power of the generator 8, and the secondary battery is charged. 30 electric power is used to drive the motor 28.

この実施形態の場合、軸受７は油潤滑のため、グリース潤滑に比べて回転抵抗となるトルクが小さいものとできる。油潤滑であると、耐久性確保のために補給を行う必要があるが、ポンプ２１によって潤滑油を軸受７に供給し、この軸受７から漏れ出た潤滑油を、潤滑油循環装置２０により再度供給に用いるようにしたため、優れた耐久性が得られる。ポンプ２８の駆動に電力が必要であるが、風力発電機１の軸受７であり、その発電電力を用いてポンプ２８を駆動するようにしたため、別途に電源を設ける必要がない。   In the case of this embodiment, since the bearing 7 is oil-lubricated, it can have a smaller torque that becomes a rotational resistance than grease lubrication. In the case of oil lubrication, it is necessary to replenish in order to ensure durability. However, the lubricating oil is supplied to the bearing 7 by the pump 21, and the lubricating oil leaked from the bearing 7 is again supplied by the lubricating oil circulation device 20. Since it was used for supply, excellent durability was obtained. Electric power is required to drive the pump 28, but the bearing 7 of the wind power generator 1 is used to drive the pump 28 using the generated electric power, so there is no need to provide a separate power source.

なお、図３に示すような油潤滑とする場合は、軸受７は、深溝玉軸受に限らず、種々の形式の転がり軸受を用いることができる。   In the case of oil lubrication as shown in FIG. 3, the bearing 7 is not limited to a deep groove ball bearing, and various types of rolling bearings can be used.

（Ａ）はこの発明の第１の実施形態にかかる軸受を用いた小型風力発電機の概略側面図、（Ｂ）はその軸受の部分断面図である。(A) is a schematic side view of the small wind power generator using the bearing concerning 1st Embodiment of this invention, (B) is a fragmentary sectional view of the bearing. 深溝玉軸受におけるグリース封入割合とトルクの関係を示すグラフである。It is a graph which shows the relationship between the grease enclosure ratio and torque in a deep groove ball bearing. この発明の他の実施形態にかかる小型風力発電機主軸用軸受、およびその潤滑油循環装置の構成を示す説明図である。It is explanatory drawing which shows the structure of the bearing for small wind power generator main shafts concerning other embodiment of this invention, and its lubricating oil circulation apparatus.

符号の説明Explanation of symbols

１…小型風力発電機
４…ブレード
６…主軸
７…小型風力発電機主軸用軸受
１１…内輪
１２…外輪
１１ａ，１２ａ…軌道溝
１３…玉
１５…シール
２０…潤滑油循環装置
２１…ボンプ
２８…モータ
Ｇ…グリース
Ｓ…軸受内部空間
DESCRIPTION OF SYMBOLS 1 ... Small wind power generator 4 ... Blade 6 ... Main shaft 7 ... Bearing for small wind power generator main shaft 11 ... Inner ring 12 ... Outer ring 11a, 12a ... Track groove 13 ... Ball 15 ... Seal 20 ... Lubricating oil circulation device 21 ... Pump 28 ... Motor G ... Grease S ... Bearing internal space

Claims (2)

小型風力発電機のブレードを取付けた主軸を回転自在に支持する軸受であって、グリース潤滑の深溝玉軸受からなり、軸受内部空間に封入されるグリース量を、軸受内部空間の５〜２０％としたことを特徴とする小型風力発電機主軸用軸受。   A bearing that rotatably supports a main shaft to which a blade of a small wind power generator is attached. The bearing comprises a grease-lubricated deep groove ball bearing, and the amount of grease enclosed in the bearing inner space is 5 to 20% of the bearing inner space. A small wind power generator main shaft bearing characterized by the above. 小型風力発電機のブレードを取付けた主軸を回転自在に支持する軸受であって、油潤滑の転がり軸受からなり、前記小型風力発電機の発電電力で駆動されるポンプにより、潤滑油を前記転がり軸受に供給しかつこの転がり軸受から漏れ出た潤滑油を再度供給に用いる潤滑油循環装置を設けたことを特徴とする小型風力発電機主軸用軸受。   A bearing for rotatably supporting a main shaft on which a blade of a small wind power generator is mounted, comprising a rolling bearing of oil lubrication, and lubricating oil is supplied to the rolling bearing by a pump driven by power generated by the small wind power generator. A small wind power generator main shaft bearing provided with a lubricating oil circulating device that supplies the lubricating oil that is supplied to the rolling bearing and leaked from the rolling bearing to supply again.
JP2004012820A 2004-01-21 2004-01-21 Bearing for small wind power generator main spindle Pending JP2005207264A (en)

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JP2007078113A (en) * 2005-09-15 2007-03-29 Ntn Corp Roller bearing, ball bearing, and bearing structure
DE102007036891A1 (en) * 2007-08-04 2009-02-19 Ab Skf Storage of a main shaft of a wind turbine
WO2010044171A1 (en) * 2008-10-17 2010-04-22 三菱重工業株式会社 Wind-driven electricity generator
KR100999715B1 (en) 2008-09-01 2010-12-08 두산중공업 주식회사 Cooling Lubrication System of Wind Generating Gearbox
JP2011027188A (en) * 2009-07-27 2011-02-10 Ntn Corp Rotating bearing and rotating section support device for wind turbine
JPWO2010018630A1 (en) * 2008-08-14 2012-01-26 三菱重工業株式会社 Wind power generator
WO2012038327A1 (en) * 2010-09-21 2012-03-29 Xemc Darwind B.V. Wind turbine with oil lubrication
US8227950B2 (en) 2005-09-15 2012-07-24 Ntn Corporation Rolling bearing, spindle support structure of main motor for railway vehicle, and bearing structure
WO2013136056A1 (en) * 2012-03-10 2013-09-19 Romax Technology Limited Overhead tank
CN103791037A (en) * 2012-10-30 2014-05-14 吴小杰 Wind power generation variable-pitch speed reducing device with bearings lubricated by grease
EP3018375A1 (en) * 2014-11-07 2016-05-11 Senvion GmbH Roller bearing lubrication of a wind power facility

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007078113A (en) * 2005-09-15 2007-03-29 Ntn Corp Roller bearing, ball bearing, and bearing structure
US8227950B2 (en) 2005-09-15 2012-07-24 Ntn Corporation Rolling bearing, spindle support structure of main motor for railway vehicle, and bearing structure
DE102007036891A1 (en) * 2007-08-04 2009-02-19 Ab Skf Storage of a main shaft of a wind turbine
JPWO2010018630A1 (en) * 2008-08-14 2012-01-26 三菱重工業株式会社 Wind power generator
KR100999715B1 (en) 2008-09-01 2010-12-08 두산중공업 주식회사 Cooling Lubrication System of Wind Generating Gearbox
US8672093B2 (en) 2008-10-17 2014-03-18 Mitsubishi Heavy Industries, Ltd. Wind turbine generator
KR101087518B1 (en) * 2008-10-17 2011-11-28 미츠비시 쥬고교 가부시키가이샤 Wind turbine generator
JP5031031B2 (en) * 2008-10-17 2012-09-19 三菱重工業株式会社 Wind power generator
WO2010044171A1 (en) * 2008-10-17 2010-04-22 三菱重工業株式会社 Wind-driven electricity generator
JP2011027188A (en) * 2009-07-27 2011-02-10 Ntn Corp Rotating bearing and rotating section support device for wind turbine
US8944692B2 (en) 2009-07-27 2015-02-03 Ntn Corporation Slewing bearing and rotating section support device for wind turbine
WO2012038327A1 (en) * 2010-09-21 2012-03-29 Xemc Darwind B.V. Wind turbine with oil lubrication
CN103189643A (en) * 2010-09-21 2013-07-03 湘电达尔文有限责任公司 Wind turbine with oil lubrication
US9903345B2 (en) 2010-09-21 2018-02-27 Xemc Darwind B.V. Wind turbine with oil lubrication
WO2013136056A1 (en) * 2012-03-10 2013-09-19 Romax Technology Limited Overhead tank
CN103791037A (en) * 2012-10-30 2014-05-14 吴小杰 Wind power generation variable-pitch speed reducing device with bearings lubricated by grease
EP3018375A1 (en) * 2014-11-07 2016-05-11 Senvion GmbH Roller bearing lubrication of a wind power facility

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