JP2005127493A - Cylindrical roller bearing - Google Patents
Cylindrical roller bearing Download PDFInfo
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- JP2005127493A JP2005127493A JP2003394275A JP2003394275A JP2005127493A JP 2005127493 A JP2005127493 A JP 2005127493A JP 2003394275 A JP2003394275 A JP 2003394275A JP 2003394275 A JP2003394275 A JP 2003394275A JP 2005127493 A JP2005127493 A JP 2005127493A
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- cylindrical roller
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- column
- cage
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- 238000005096 rolling process Methods 0.000 claims abstract description 32
- 230000002093 peripheral effect Effects 0.000 claims description 25
- 229920003002 synthetic resin Polymers 0.000 claims description 10
- 239000000057 synthetic resin Substances 0.000 claims description 10
- 230000004323 axial length Effects 0.000 claims description 4
- 230000002159 abnormal effect Effects 0.000 abstract description 14
- 230000003252 repetitive effect Effects 0.000 abstract description 10
- 230000005489 elastic deformation Effects 0.000 description 7
- 238000005461 lubrication Methods 0.000 description 6
- 238000005315 distribution function Methods 0.000 description 5
- 239000003921 oil Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 229920000049 Carbon (fiber) Polymers 0.000 description 3
- 239000004696 Poly ether ether ketone Substances 0.000 description 3
- 239000004917 carbon fiber Substances 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 3
- 229920002530 polyetherether ketone Polymers 0.000 description 3
- 229920005989 resin Polymers 0.000 description 3
- 239000011347 resin Substances 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 239000004734 Polyphenylene sulfide Substances 0.000 description 2
- 239000003365 glass fiber Substances 0.000 description 2
- 239000004519 grease Substances 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 229920000069 polyphenylene sulfide Polymers 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000000945 filler Substances 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 235000013372 meat Nutrition 0.000 description 1
- 238000003801 milling Methods 0.000 description 1
- 229920006122 polyamide resin Polymers 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000002250 progressing effect Effects 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Classifications
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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
- F16C33/46—Cages for rollers or needles
- F16C33/49—Cages for rollers or needles comb-shaped
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
本発明は、合成樹脂製の保持器を備えた円筒ころ軸受に関し、例えば、工作機械主軸等の高速で回転する回転部材の支持用軸受として好適である。 The present invention relates to a cylindrical roller bearing provided with a cage made of synthetic resin, and is suitable, for example, as a bearing for supporting a rotating member that rotates at a high speed such as a machine tool main shaft.
マシニングセンタ、ＣＮＣ旋盤、フライス盤等の工作機械において、主軸はハウジングに対して軸受で回転自在に支持される。主軸の向きは、機械形式によって、縦軸（軸線が鉛直方向に向いたもの）と横軸（軸線が水平方向に向いたもの）がある。また、軸受の潤滑方式は、使用条件等に応じてグリース潤滑やエアオイル潤滑等の油潤滑が採用される。
軸受形式としては、組合せアンギュラ玉軸受や円筒ころ軸受が使用される場合が多い。
In machine tools such as machining centers, CNC lathes, and milling machines, the main shaft is rotatably supported by a bearing with respect to a housing. Depending on the machine type, the orientation of the main axis includes a vertical axis (the axis is oriented in the vertical direction) and a horizontal axis (the axis is oriented in the horizontal direction). Further, as a bearing lubrication system, oil lubrication such as grease lubrication or air-oil lubrication is employed depending on the use conditions and the like.
As a bearing type, a combination angular contact ball bearing or a cylindrical roller bearing is often used.
工作機械主軸支持用の円筒ころ軸受では、これまで高力黄銅鋳物のもみ抜き（削り出し）保持器が主に使用されてきたが、運転時の保持器の摩耗粉による潤滑剤劣化の問題や軽量化の点から、近時は合成樹脂製保持器への切り換えが進んでいる。 For cylindrical roller bearings for machine tool spindle support, high-strength brass cast machined (machined) cages have been mainly used so far. From the point of weight reduction, switching to a synthetic resin cage has been progressing recently.
現在使用されている円筒ころ軸受の合成樹脂製保持器として、例えば下記の特許文献１、２に記載されているように、環状部と、環状部の内側面から軸方向の一方に延びた複数の柱部と、円周方向に隣接する柱部の円周方向側面間に形成され、円筒ころを回転自在に保持する複数のポケットとを備えた、所謂くし形と呼ばれる形態の保持器が知られている。しかしながら、この形態の合成樹脂製保持器は、柱部の先端が自由端であるため、特に高速回転時では、回転時の遠心力の作用で柱部が外径側に比較的大きく弾性変形して、その円周方向側面の先端側内周部が円筒ころの転動面と強く接触（異常接触）することにより、該接触部分に油膜切れが生じて異常摩耗が発生したり、軸受温度上昇の増大要因になったりする場合がある。そこで、特許文献１、２では、この問題に対応するため、図８に示すように、保持器１４の柱部１４ｂの円周方向側面１４ｂ１を、ポケット１４ｃのポケット中心Ｏを通るころＰＣＤを境にして、外径側領域と内径側領域に区分し、外径側領域を円筒ころ１３の転動面に沿う円弧面（円筒面）１４ｂ１１に形成すると共に、内径側領域をその軸方向全長さに亘ってポケット中心Ｏを通る半径線ｒ１と平行なストレート面１４ｂ１２に形成することにより、回転時の遠心力の作用で柱部１４ｂが外径側に弾性変形したときに、柱部１４ｂの円周方向側面１４ｂ１の内径側領域１４ｂ１２が円筒ころ３の転動面と半径方向の接触圧を生じないようにしている。
工作機械の主軸に要求される主要な特性として、高速回転｛通常、ｄｍｎ値（＝転動体のピッチ円径ｍｍ×回転数ｒｐｍ）で１００万以上｝が可能であることと、非繰り返し振れ（ＮＲＲＯ）が小さいことが挙げられ、この特性は主に主軸を支持する軸受の軸支持機能によって決まる。しかしながら、特許文献１、２に記載された円筒ころ軸受は、次の理由により、工作機械の主軸に要求される非繰り返し振れ（ＮＲＲＯ）を満足することが難しい。 The main characteristics required for the main spindle of a machine tool are that high-speed rotation {usually, dmn value (= 1 million or more of rolling element pitch circle diameter mm × rotational speed rpm) and non-repetitive runout ( NRRO) is small, and this characteristic is mainly determined by the shaft support function of the bearing that supports the main shaft. However, it is difficult for the cylindrical roller bearings described in Patent Documents 1 and 2 to satisfy non-repetitive runout (NRRO) required for the spindle of a machine tool for the following reason.
すなわち、特許文献１、２に記載された円筒ころ軸受の保持器１４において、柱部１４ｂの円周方向側面１４ｂ１は、上述のように、ころＰＣＤよりも内径側領域がその軸方向全長さに亘ってストレート面１４ｂ１２に形成されており、回転時の遠心力の作用で柱部１４ｂが外径側に弾性変形したときに、円周方向側面１４ｂ１の内径側領域１４ｂ１２が円筒ころ１３の転動面と半径方向の接触圧を生じないようになっている。しかしながら、この構成は、柱部１４ｂの円周方向側面１４ｂ１と円筒ころ１３の転動面との異常接触を防止する点では効果的であるものの、その反面、柱部１４ｂの円周方向側面１４ｂ１の内径側領域を上記のストレート面１４ｂ１２に形成したことにより、柱部１４ｂの外径側への弾性変形を助長する結果ともなっている。すなわち、柱部１４ｂの円周方向側面１４ｂ１の内径側領域を上記のストレート面１４ｂ１２に形成したことにより、通常のポケット形態（柱部の円周方向側面の全領域を円筒ころの転動面に沿う円弧面に形成したポケット形態）に比較して、柱部１４ｂの外径側への弾性変形を規制する部位がなくなり、また、柱部１４ｂの内径側領域の円周方向肉厚が小さくなって柱部１４ｂの剛性が低下する結果、柱部１４ｂの外径側への弾性変形が助長されている。 In other words, in the cylindrical roller bearing retainer 14 described in Patent Documents 1 and 2, the circumferential side surface 14b1 of the column portion 14b has an axial inner side area that is the entire axial length of the roller PCD as described above. It is formed on the straight surface 14b12, and when the column portion 14b is elastically deformed to the outer diameter side by the action of centrifugal force during rotation, the inner diameter side region 14b12 of the circumferential side surface 14b1 rolls the cylindrical roller 13. No contact pressure in the radial direction with the surface is generated. However, this configuration is effective in preventing abnormal contact between the circumferential side surface 14b1 of the column portion 14b and the rolling surface of the cylindrical roller 13, but on the other hand, the circumferential side surface 14b1 of the column portion 14b. As a result of forming the inner diameter side region of the cylindrical portion on the straight surface 14b12, the result is that the elastic deformation of the column portion 14b toward the outer diameter side is promoted. That is, by forming the inner diameter side region of the circumferential side surface 14b1 of the column part 14b on the straight surface 14b12, the normal pocket configuration (the entire region of the circumferential side surface of the column part is used as the rolling surface of the cylindrical roller). Compared to the pocket shape formed on the arcuate surface, the portion that restricts elastic deformation of the column portion 14b toward the outer diameter side is eliminated, and the circumferential thickness of the inner diameter side region of the column portion 14b is reduced. As a result, the rigidity of the column portion 14b is reduced, and the elastic deformation of the column portion 14b toward the outer diameter side is promoted.
図９は、特許文献１、２に記載された円筒ころ軸受の保持器１４の柱部１４ｂが高速回転時の遠心力の作用で外径側に弾性変形した状態（実線）と、変形前の状態（点線）とを模式的にしている。同図に示すように、特許文献１、２に記載された円筒ころ軸受の保持器１４では、柱部１４ｂが外径側に弾性変形すると、柱部１４ｂの円周方向側面１４ｂ１と円筒ころ１３の転動面との間のポケット隙間ｇが初期隙間（変形前の隙間）よりも増大する。しかも、上述のように、柱部１４ｂの外径側への弾性変形が助長される結果、ポケット隙間ｇの増大も助長される。そして、このポケット隙間ｇの増大により、円筒ころの等配機能が低下し、円筒ころの公転中心が振れて、内輪が不安定に振れる非繰り返し振れが発生する。特に、ころ案内形式の保持器では、保持器の半径方向の自由度が増大することにより、ポケット隙間ｇが増大する箇所と縮小する箇所とができ、しかもこれらの箇所の発生位置が一定しないために、非繰り返し振れの程度が大きくなる。この非繰り返し振れ（ＮＲＲＯ）は、回転数の上昇に比例して増大し、工作機械の主軸に取付けられた工具による加工精度を悪化させる等の原因となる。 FIG. 9 shows a state (solid line) in which the column portion 14b of the retainer 14 of the cylindrical roller bearing described in Patent Documents 1 and 2 is elastically deformed to the outer diameter side by the action of centrifugal force during high-speed rotation (solid line). The state (dotted line) is schematically shown. As shown in the figure, in the cage 14 of the cylindrical roller bearing described in Patent Documents 1 and 2, when the column portion 14b is elastically deformed to the outer diameter side, the circumferential side surface 14b1 of the column portion 14b and the cylindrical roller 13 are shown. The pocket gap g between the first and second rolling surfaces is larger than the initial gap (gap before deformation). Moreover, as described above, the elastic deformation of the column part 14b toward the outer diameter side is promoted, and as a result, the pocket gap g is also increased. Then, due to the increase in the pocket gap g, the equal distribution function of the cylindrical roller is lowered, the revolution center of the cylindrical roller is shaken, and non-repetitive shake is generated in which the inner ring is shaken in an unstable manner. In particular, in a roller guide type cage, the degree of freedom in the radial direction of the cage is increased, so that a portion where the pocket gap g is increased and a portion where the pocket gap g is reduced can be formed, and the occurrence positions of these portions are not constant. In addition, the degree of non-repetitive shake increases. This non-repetitive run-out (NRRO) increases in proportion to the increase in the number of revolutions, and causes a reduction in machining accuracy by a tool attached to the main spindle of the machine tool.
本発明の課題は、所謂くし形の合成樹脂製保持器を備えた円筒ころ軸受において、高速回転時における柱部の先端側内周部と円筒ころの転動面との異常接触を防止して、保持器の異常摩耗の防止と軸受温度上昇の抑制を図ると同時に、非繰り返し振れ（ＮＲＲＯ）を低減することである。 An object of the present invention is to prevent abnormal contact between the inner peripheral portion on the tip side of the column portion and the rolling surface of the cylindrical roller during high-speed rotation in a cylindrical roller bearing provided with a so-called comb-shaped synthetic resin cage. It is intended to prevent non-repetitive runout (NRRO) at the same time as preventing abnormal wear of the cage and suppressing an increase in bearing temperature.
上記課題を解決するため、本発明は、内輪と、外輪と、内輪と外輪との間に転動自在に配された複数の円筒ころと、合成樹脂製の保持器とを備え、保持器は、環状部と、環状部の内側面から軸方向の一方に延びた複数の柱部と、円周方向に隣接する柱部の円周方向側面間に形成され、円筒ころを回転自在に保持する複数のポケットとを備えている円筒ころ軸受において、保持器の柱部の円周方向側面は、その基端側内周部に、円筒ころの転動面に沿う円弧面に形成され、柱部が回転時の遠心力により外径側に弾性変形したときに、円筒ころの転動面を案内するころ案内部を有すると共に、その先端側内周部に、ころ案内部よりも柱部の円周方向中心側に退避し、柱部が回転時の遠心力により外径側に弾性変形したときに、円筒ころの転動面と半径方向の接触圧を生じない逃げ部を有する構成を提供する。 In order to solve the above-described problems, the present invention includes an inner ring, an outer ring, a plurality of cylindrical rollers that are rotatably arranged between the inner ring and the outer ring, and a cage made of synthetic resin. The cylindrical roller is formed between the annular portion, the plurality of column portions extending in the axial direction from the inner side surface of the annular portion, and the circumferential side surface of the column portion adjacent in the circumferential direction, and rotatably holds the cylindrical roller. In the cylindrical roller bearing provided with a plurality of pockets, the circumferential side surface of the column portion of the cage is formed in an arc surface along the rolling surface of the cylindrical roller at the proximal end side inner peripheral portion, and the column portion Has a roller guide portion that guides the rolling surface of the cylindrical roller when it is elastically deformed to the outer diameter side due to centrifugal force during rotation, and a circular portion of the column portion at the tip end side inner periphery thereof rather than the roller guide portion. When the column is retracted to the center side in the circumferential direction and elastically deformed to the outer diameter side by the centrifugal force during rotation, the rolling surface of the cylindrical roller Providing a structure having a relief portion that does not cause the contact pressure of the radial direction.
柱部が回転時の遠心力により外径側に弾性変形すると、柱部の円周方向側面の基端側内周部に円筒ころの転動面に沿う円弧面として形成されたころ案内部が、円筒ころの転動面との間のポケット隙間が減少する方向（外径側）に変位して、円筒ころの転動面を案内する。そのため、円筒ころの良好な等配機能が確保され、高速回転時における非繰り返し振れ（ＮＲＲＯ）が問題のない程度まで低減される。尚、柱部の弾性変形量は基端側が先端側よりも小さくなるため、基端側内周部のころ案内部で円筒ころを案内する構成としても、両者の異常接触は発生しない。一方、柱部の円周方向側面の先端側内周部には、ころ案内部よりも柱部の円周方向中心側に退避した逃げ部が設けられているので、円周方向側面の先端側内周部は円筒ころの転動面と非接触になるか、あるいは、接触する場合でも半径方向の接触圧を生じない程度の軽い接触となる。そのため、高速回転時における円周方向側面の先端側内周部と円筒ころの転動面との異常接触が回避され、先端側内周部の異常摩耗が防止されると共に、軸受温度上昇が抑制される。 When the column portion is elastically deformed to the outer diameter side due to centrifugal force during rotation, a roller guide portion formed as an arc surface along the rolling surface of the cylindrical roller is provided on the inner peripheral portion on the proximal side of the circumferential side surface of the column portion. The pocket roller is displaced in the direction (outer diameter side) in which the pocket clearance between the cylindrical roller and the rolling surface decreases, and the rolling surface of the cylindrical roller is guided. Therefore, a good even distribution function of the cylindrical roller is ensured, and non-repetitive runout (NRRO) during high-speed rotation is reduced to a level where there is no problem. In addition, since the amount of elastic deformation of the column portion is smaller on the proximal end side than on the distal end side, even if the cylindrical roller is guided by the roller guide portion on the inner circumferential portion on the proximal end side, neither abnormal contact occurs. On the other hand, the inner circumferential portion on the distal end side of the circumferential side surface of the column portion is provided with a relief portion that is retracted closer to the circumferential center side of the column portion than the roller guide portion, so the distal end side of the circumferential side surface The inner peripheral portion is not in contact with the rolling surface of the cylindrical roller, or is light enough to cause no contact pressure in the radial direction even when contacting. As a result, abnormal contact between the inner circumferential portion on the circumferential side surface and the rolling surface of the cylindrical roller during high-speed rotation is avoided, abnormal wear on the inner circumferential portion on the distal end is prevented, and a rise in bearing temperature is suppressed. Is done.
さらに、円周方向側面の基端側内周部に上記のようなころ案内部を設けることにより、柱部の基端側内周部の円周方向肉厚が増大して、柱部の剛性が向上する。そのため、回転時の遠心力や円筒ころからの荷重による柱部の外径方向及び円周方向への弾性変形量が小さくなる。これにより、円筒ころの良好な等配機能が維持される。 Furthermore, by providing the roller guide portion as described above at the proximal side inner peripheral portion of the circumferential side surface, the circumferential thickness of the proximal end side inner peripheral portion of the column portion is increased, and the rigidity of the column portion is increased. Will improve. Therefore, the amount of elastic deformation in the outer diameter direction and the circumferential direction of the column portion due to the centrifugal force during rotation and the load from the cylindrical roller is reduced. Thereby, the favorable equal distribution function of a cylindrical roller is maintained.
上記構成において、逃げ部の軸方向長さは円筒ころの長さの１０％〜３５％であることが好ましい。また、逃げ部の半径方向の開始位置とポケットのポケット中心とを結ぶ線が、ポケットのポケット中心におけるポケットＰＣＤの接線に対して、内径側に２０度以下の角度をなすように、逃げ部の半径方向の開始位置を設定することが好ましい。これらの基準に基づいて逃げ部を形成することにより、工作機械主軸で要求される高速回転域において、上記の効果を発揮することができる。 In the above configuration, the axial length of the relief portion is preferably 10% to 35% of the length of the cylindrical roller. In addition, the line connecting the radial start position of the relief portion and the pocket center of the pocket forms an angle of 20 degrees or less on the inner diameter side with respect to the tangent to the pocket PCD at the pocket center of the pocket. It is preferable to set a starting position in the radial direction. By forming the relief portion based on these standards, the above-described effects can be exhibited in the high-speed rotation range required for the machine tool spindle.
また、逃げ部の円周方向側面は柱部の円周方向中心線と平行なストレート面とすることが好ましい。逃げ部の円周方向側面をポケット中心を通る半径線と平行なストレート面とする場合に比べて、同様の効果を得つつ、柱部の先端側内周部の円周方向肉厚を厚くして、柱部の剛性を高めることができる。 Moreover, it is preferable that the circumferential side surface of the relief portion is a straight surface parallel to the circumferential center line of the column portion. Compared to the case where the circumferential side surface of the relief portion is a straight surface parallel to the radial line passing through the center of the pocket, the circumferential thickness of the inner peripheral portion on the tip side of the column portion is increased while obtaining the same effect. Thus, the rigidity of the column portion can be increased.
あるいは、逃げ部の円周方向側面を柱部の円周方向中心線に近づく方向に傾斜した傾斜面としても良い。これにより、高速回転時における柱部の円周方向側面の先端側内周部と円筒ころの転動面との異常接触をより確実に回避することできる。 Alternatively, the circumferential side surface of the relief portion may be an inclined surface that is inclined in a direction approaching the circumferential center line of the column portion. Thereby, the abnormal contact with the front end side inner peripheral part of the circumferential direction side surface of a pillar part at the time of high speed rotation and the rolling surface of a cylindrical roller can be avoided more reliably.
本発明は、保持器に形成された複数の柱部の全て、特にその全ての円周方向両側面に逃げ部を形成することが好適であるが、それらの複数の柱部における一つおき又は二つ以上おきに逃げ部を形成するようにしても良く、或いは、それらの複数の柱部における二つ以上おきに逃げ部を形成せず、その他の柱部に逃げ部を形成するようにしても良い。 In the present invention, it is preferable to form relief portions on all of the plurality of pillar portions formed on the cage, in particular, on both circumferential sides thereof, but every other one of the plurality of pillar portions or The escape portions may be formed every two or more, or the escape portions are not formed every two or more of the plurality of pillar portions, and the escape portions are formed in the other pillar portions. Also good.
さらに、本発明は、円筒ころが複数列で配列されている複列円筒ころ軸受に特に好適である。この場合、円筒ころの各列をそれぞれ上記の保持器によって個別的に保持する構成とするのが好ましい。より好ましくは、円筒ころの各列を保持する上記の保持器の環状部同士を軸受中央側で相互に付き合わせた状態で配置する。 Furthermore, the present invention is particularly suitable for a double row cylindrical roller bearing in which cylindrical rollers are arranged in a plurality of rows. In this case, it is preferable that each row of cylindrical rollers is individually held by the above cage. More preferably, it arrange | positions in the state which mutually attached the cyclic | annular parts of said holder | retainer holding each row | line | column of a cylindrical roller on the bearing center side.
本発明によれば、所謂くし形の合成樹脂製保持器を備えた円筒ころ軸受において、高速回転時における柱部の先端側内周部と円筒ころの転動面との異常接触を防止して、保持器の異常摩耗の防止と軸受温度上昇の抑制を図ることができると同時に、非繰り返し振れ（ＮＲＲＯ）を低減することができる。 According to the present invention, in a cylindrical roller bearing provided with a so-called comb-shaped synthetic resin cage, abnormal contact between the inner peripheral portion of the column portion and the rolling surface of the cylindrical roller during high-speed rotation is prevented. In addition, it is possible to prevent abnormal wear of the cage and suppress an increase in bearing temperature, and at the same time, it is possible to reduce non-repetitive runout (NRRO).
以下、本発明の実施形態について図面を参照しながら説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
図１は、第１の実施形態に係る複列円筒ころ軸受を示している。この複列円筒ころ軸受は、工作機械の主軸装置において、高速で回転駆動される主軸をハウジングに対して回転自在に支持するもので、複列の軌道面１ａを有する内輪１と、複列の軌道面２ａを有する外輪２と、内輪１の軌道面１ａと外輪２の軌道面２ａとの間に転動自在に配された複列の円筒ころ３と、各列の円筒ころ３をそれぞれ保持する一対の合成樹脂製の保持器４とで構成される。内輪１の軸方向中央部には中鍔１ｂが設けられ、両端部には外鍔１ｃが設けられている。内輪１は主軸の外周に嵌合され、外輪２はハウジングの内周に嵌合される。この複列円筒ころ軸受は、例えば、エアオイルやグリース等の微量の潤滑剤で潤滑され、ラジアル内部隙間が負、すなわちラジアル方向の予圧を付与した状態で運転される場合が多々ある。尚、内輪１の内径面はテーパ形状であっても良い（この内輪は、テーパ形状に形成した主軸の外周面、あるいは、主軸の外周に嵌合したテーパ状スリーブの外周面に嵌合される）。 FIG. 1 shows a double-row cylindrical roller bearing according to the first embodiment. This double-row cylindrical roller bearing is a spindle device of a machine tool that supports a main shaft that is driven to rotate at a high speed with respect to a housing. The double-row cylindrical roller bearing includes an inner ring 1 having a double-row raceway surface 1a, An outer ring 2 having a raceway surface 2a, a double-row cylindrical roller 3 disposed between the raceway surface 1a of the inner ring 1 and the raceway surface 2a of the outer ring 2, and a cylindrical roller 3 in each row are held. And a pair of synthetic resin cages 4. An inner collar 1b is provided at the axial center of the inner ring 1, and outer collars 1c are provided at both ends. The inner ring 1 is fitted to the outer circumference of the main shaft, and the outer ring 2 is fitted to the inner circumference of the housing. This double-row cylindrical roller bearing is often operated in a state where the radial internal gap is negative, that is, a radial preload is applied, for example, by being lubricated with a small amount of lubricant such as air oil or grease. The inner ring 1 may have a tapered inner diameter surface (this inner ring is fitted to the outer circumferential surface of the main shaft formed in a tapered shape or the outer circumferential surface of the tapered sleeve fitted to the outer circumference of the main shaft. ).
図２及び図３に拡大して示すように、保持器４は、例えば、ポリエーテルエーテルケトン樹脂（ＰＥＥＫ）、ポリアミド樹脂（ＰＡ：ＰＡ６６、ＰＡ４６）、ポリフェニレンサルファイド樹脂（ＰＰＳ）等の自己潤滑性を有する合成樹脂（必要に応じてカーボンファイバ（ＣＦ）、グラスファイバ（ＧＦ）等の充填材を所要量配合する。）を射出成形して形成され、環状部４ａと、環状部４ａの内側面４ａ１から軸方向の一方に一体に連続して延びた複数の柱部４ｂと、円周方向に隣接する柱部４ｂの円周方向側面４ｂ１間に形成され、円筒ころ３を回転自在に保持する複数のポケット４ｃとを備えている。複数の柱部４ｂは円周等配位置に配列されている。各ポケット４ｃは円周方向に隣接する柱部４ｂの円周方向側面４ｂ１と環状部４ａの内側面４ａ１とで三方から囲まれ、軸方向の一方に向かって開口している。 As shown in FIGS. 2 and 3 in an enlarged manner, the cage 4 has a self-lubricating property such as polyether ether ketone resin (PEEK), polyamide resin (PA: PA66, PA46), polyphenylene sulfide resin (PPS), and the like. A synthetic resin (if necessary, a required amount of filler such as carbon fiber (CF) and glass fiber (GF) is blended) is formed by injection molding, and the annular portion 4a and the inner surface of the annular portion 4a 4a1 is formed between a plurality of pillars 4b extending continuously in one axial direction from 4a1 and a circumferential side surface 4b1 of pillars 4b adjacent in the circumferential direction, and holds cylindrical roller 3 rotatably. And a plurality of pockets 4c. The plurality of column portions 4b are arranged at circumferentially equidistant positions. Each pocket 4c is surrounded from three sides by the circumferential side surface 4b1 of the column part 4b adjacent in the circumferential direction and the inner side surface 4a1 of the annular part 4a, and is open toward one side in the axial direction.
図３に示すように、柱部４ｂの円周方向両側面４ｂ１は、ポケット４ｃのポケット中心Ｏを通るポケットＰＣＤ（同図に示す例では、ポケットＰＣＤは円筒ころ３の中心を通るころＰＣＤと等しい。）から内径側及び外径側に亘って形成された円弧面（円筒面）４ｂ１１と、先端側内周部に設けられた逃げ部４ｂ１２とを備えている。 As shown in FIG. 3, both side surfaces 4b1 in the circumferential direction of the column 4b are pocket PCDs passing through the pocket center O of the pocket 4c (in the example shown in the figure, the pocket PCD is a roller PCD passing through the center of the cylindrical roller 3). Equal to the inner diameter side and the outer diameter side, and an arc surface (cylindrical surface) 4b11 formed on the inner diameter side and the outer diameter side, and a relief portion 4b12 provided on the inner peripheral portion on the front end side.
円弧面４ｂ１１は、例えば、ポケット中心Ｏを中心とし、円筒ころ３の半径（Ｄ／２）の１．００５〜１．１倍の半径の円弧で描かれており、その外径端は、ポケット中心Ｏを通る半径線ｒ１と平行なストレート面４ｂ１３と連続している。円周方向に相対向するストレート面４ｂ１３間の離間距離Ｗ１は円筒ころ３の直径Ｄよりも小さく、これにより、ポケット４ｃに対する円筒ころ３の外径側への抜けが規制される。円弧面４ｂ１１の内径端は、基端側においては柱部４ｂの内径端まで延び、先端側においては内周部の逃げ部４ｂ１２に連続している。円周方向に相対向する円弧面４ｂ１１の基端側内周部４ｂ１４間の最小離間距離Ｗ２は円筒ころ３の直径Ｄよりも小さい。この基端側内周部４ｂ１４は、柱部４ｂが回転時の遠心力によって外径側に弾性変形したときに、円筒ころ３の転動面を案内するころ案内部となる。 For example, the arc surface 4b11 is drawn with an arc having a radius of 1.005 to 1.1 times the radius (D / 2) of the cylindrical roller 3 with the pocket center O as the center. It is continuous with the straight surface 4b13 parallel to the radial line r1 passing through the center O. The separation distance W1 between the straight surfaces 4b13 opposed to each other in the circumferential direction is smaller than the diameter D of the cylindrical roller 3, thereby restricting the cylindrical roller 3 from slipping out of the pocket 4c to the outer diameter side. The inner diameter end of the arcuate surface 4b11 extends to the inner diameter end of the column portion 4b on the base end side, and is continuous with the escape portion 4b12 on the inner peripheral portion on the distal end side. The minimum separation distance W2 between the base end side inner peripheral portions 4b14 of the circular arc surfaces 4b11 facing each other in the circumferential direction is smaller than the diameter D of the cylindrical roller 3. The base end side inner peripheral portion 4b14 serves as a roller guide portion that guides the rolling surface of the cylindrical roller 3 when the column portion 4b is elastically deformed to the outer diameter side by centrifugal force during rotation.
先端側内周部の逃げ部４ｂ１２は、柱部４ｂの先端から軸線方向に沿って基端部に至る途中部分まで形成され、基端側内周部４ｂ１４よりも柱部４ｂの円周方向中心線ｒ２の側に退避するように肉取りされている。逃げ部４ｂ１２の軸方向長さＬ１は円筒ころ３の長さＬの１０％〜３５％であり、逃げ部４ｂ１２の半径方向の開始位置はポケット中心ＯにおけるポケットＰＣＤの接線ｍ１を基準として内径側にθ≦２０°となるように設定される。角度θは、逃げ部４ｂ１２の半径方向の開始位置とポケット中心Ｏとを結ぶ線ｍ２が接線ｍ１となす角度である。また、逃げ部４ｂ１２の円周方向側面は、柱部４ｂの円周方向中心線ｒ２と平行なストレート面に形成されている。このような態様で形成された逃げ部４ｂ１２は、柱部４ｂが高速回転時の遠心力の作用で円周方向中心線ｒ２に沿って外径側に弾性変形したときにおいても、円筒ころ３の転動面とは接触しなくなる。尚、円周方向に相対向する逃げ部４ｂ１２の円周方向側面間の最小離間距離は円筒ころ３の直径Ｄよりも若干小さいが、逃げ部４ｂ１２は円周方向中心線ｒ２に沿って外径側に変位するため、円筒ころ３の転動面とは接触しない。このように、逃げ部４ｂ１２の円周方向側面を円周方向中心線ｒ２と平行なストレート面に形成することにより、半径線ｒ１と平行なストレート面に形成する場合に比べ、柱部４ｂの先端側内周部の円周方向肉厚を厚くして、柱部４ｂの剛性を高めることができる。 The clearance part 4b12 of the distal end side inner peripheral part is formed from the distal end of the column part 4b to the middle part from the distal end along the axial direction to the proximal end part, and the circumferential center of the column part 4b is more than the proximal end inner peripheral part 4b14. The meat is cut so as to retract to the line r2. The axial length L1 of the escape portion 4b12 is 10% to 35% of the length L of the cylindrical roller 3, and the radial start position of the escape portion 4b12 is on the inner diameter side with respect to the tangent m1 of the pocket PCD at the pocket center O. Is set to satisfy θ ≦ 20 °. The angle θ is an angle formed by a line m2 connecting the starting position in the radial direction of the relief portion 4b12 and the pocket center O with the tangent line m1. Further, the circumferential side surface of the relief portion 4b12 is formed on a straight surface parallel to the circumferential center line r2 of the column portion 4b. The relief portion 4b12 formed in such a manner can be used for the cylindrical roller 3 even when the column portion 4b is elastically deformed to the outer diameter side along the circumferential center line r2 by the action of centrifugal force during high-speed rotation. No contact with the rolling surface. In addition, although the minimum separation distance between the circumferential direction side surfaces of the relief portion 4b12 opposed to each other in the circumferential direction is slightly smaller than the diameter D of the cylindrical roller 3, the relief portion 4b12 has an outer diameter along the circumferential center line r2. Since it is displaced to the side, it does not contact the rolling surface of the cylindrical roller 3. In this way, by forming the circumferential side surface of the relief portion 4b12 on a straight surface parallel to the circumferential center line r2, the tip of the column portion 4b is formed compared to the case where it is formed on a straight surface parallel to the radial line r1. The rigidity of the column part 4b can be increased by increasing the circumferential thickness of the side inner peripheral part.
図１に示すように、この実施形態において、保持器４は転動体案内形式のものであり、軸受回転時、保持器４は柱部４ｂの円周方向側面４ｂ１を円筒ころ３の転動面に接触案内されながら回転する。そして、軸受の回転が所定の高速回転域に達し、柱部４ｂが高速回転時の遠心力により外径側に弾性変形すると、柱部４ｂの円周方向側面４ｂ１の基端側内周部（ころ案内部）４ｂ１４が円筒ころ３の転動面との間のポケット隙間が減少する方向（円周方向中心線ｒ２に沿って外径側）に変位して、円筒ころ３の転動面を案内する。これにより、円筒ころ３の良好な等配機能が確保され、高速回転時における非繰り返し振れ（ＮＲＲＯ）が問題のない程度まで低減される。このとき、柱部４ｂの円周方向側面４ｂ１の先端側内周部は逃げ部４ｂ１２が設けられていることにより、円筒ころ３の転動面との接触が回避される。そのため、高速回転時における円周方向側面４ｂ１の先端側内周部の異常摩耗が防止されると共に、軸受温度上昇が抑制される。 As shown in FIG. 1, in this embodiment, the retainer 4 is of a rolling element guide type, and when the bearing rotates, the retainer 4 moves the circumferential side surface 4 b 1 of the column portion 4 b on the rolling surface of the cylindrical roller 3. Rotates while being guided by contact. Then, when the rotation of the bearing reaches a predetermined high-speed rotation region and the column portion 4b is elastically deformed to the outer diameter side by the centrifugal force at the time of high-speed rotation, the proximal end side inner peripheral portion of the circumferential side surface 4b1 of the column portion 4b ( The roller guide portion) 4b14 is displaced in the direction in which the pocket gap between the rolling contact surface of the cylindrical roller 3 is reduced (on the outer diameter side along the circumferential center line r2) and the rolling contact surface of the cylindrical roller 3 is changed. invite. As a result, a good even distribution function of the cylindrical rollers 3 is ensured, and non-repetitive runout (NRRO) during high-speed rotation is reduced to a level where there is no problem. At this time, the tip side inner peripheral portion of the circumferential side surface 4b1 of the column portion 4b is provided with the relief portion 4b12, thereby avoiding contact with the rolling surface of the cylindrical roller 3. Therefore, abnormal wear of the inner peripheral portion on the distal end side of the circumferential side surface 4b1 during high-speed rotation is prevented, and an increase in bearing temperature is suppressed.
さらに、円周方向側面４ｂ１の基端側内周部（ころ案内部）４ｂ１４を円筒ころ３の転動面に沿う円弧面とすることにより、柱部４ｂの基端側内周部４ｂ１４の円周方向肉厚が増大して、柱部４ｂの剛性が向上する。そのため、高速回転時の遠心力や円筒ころ３からの荷重による柱部４ｂの外径方向及び円周方向への弾性変形量が小さくなり、これにより、円筒ころ３の良好な等配機能が維持される。 Furthermore, the base end side inner peripheral portion (roller guide portion) 4b14 of the circumferential side surface 4b1 is an arc surface along the rolling surface of the cylindrical roller 3, so that the base end side inner peripheral portion 4b14 of the column portion 4b has a circle. The circumferential thickness is increased, and the rigidity of the column portion 4b is improved. Therefore, the amount of elastic deformation in the outer diameter direction and the circumferential direction of the column portion 4b due to the centrifugal force at the time of high-speed rotation and the load from the cylindrical roller 3 is reduced, thereby maintaining a good even distribution function of the cylindrical roller 3. Is done.
図４に示す第２の実施形態に係る保持器４は、上記のような逃げ部４ｂ１２を、その外径端が柱部４ｂの先端から基端部に向かって内径側に傾斜するように形成したものである。その他の事項は、第１の実施形態に準じるので、重複する説明を省略する。 The retainer 4 according to the second embodiment shown in FIG. 4 is formed with the relief portion 4b12 as described above so that the outer diameter end thereof is inclined toward the inner diameter side from the distal end of the column portion 4b toward the base end portion. It is a thing. Since other matters are the same as those in the first embodiment, a duplicate description is omitted.
図５に示す第３の実施形態に係る保持器４は、上記のような逃げ部４ｂ１２を、その円周方向側面が柱部４ｂの円周方向中心線ｒ２に近づく方向に傾斜した傾斜面となるように形成したものである。この実施形態は、第２の実施形態と組み合わせても良い。その他の事項は、第１の実施形態に準じるので、重複する説明を省略する。 The retainer 4 according to the third embodiment shown in FIG. 5 is configured such that the relief portion 4b12 as described above has an inclined surface inclined in a direction in which the circumferential side surface approaches the circumferential center line r2 of the column portion 4b. It is formed as follows. This embodiment may be combined with the second embodiment. Since other matters are the same as those in the first embodiment, a duplicate description is omitted.
図６に示す第４の実施形態に係る保持器４は、複数の柱部４ｂの一つおき又は二つ以上おき（この実施形態では一つおき）における円周方向両側面４ｂ１に、逃げ部４ｂ１２を形成したものである。この実施形態は、第２の実施形態又は第３の実施形態と組み合わせても良い。その他の事項は、第１の実施形態に準じるので、重複する説明を省略する。この場合、本発明は、複数の柱部４ｂの全てについて円周方向両側面４ｂ１に逃げ部４ｂ１２を形成することを排除するものでないことは言うまでもない。 The retainer 4 according to the fourth embodiment shown in FIG. 6 is provided with relief portions on both circumferential side surfaces 4b1 of every other pillar portion 4b or every other two or more (every other in this embodiment). 4b12 is formed. This embodiment may be combined with the second embodiment or the third embodiment. Since other matters are the same as those in the first embodiment, a duplicate description is omitted. In this case, it goes without saying that the present invention does not exclude the formation of the relief portions 4b12 on the circumferential side surfaces 4b1 for all of the plurality of column portions 4b.
尚、保持器の案内形式は、転動体案内に限らず、外輪案内や内輪案内でも良い。すなわち、本発明は保持器の案内形式の如何を問わない。また、図１にはＮＮ形の複列円筒ころ軸受を例示しているが、本発明はＮＮＵ形、その他の軸受形式の複列円筒ころ軸受にも同様に適用可能である。さらに、本発明は複列円筒ころ軸受に限らず、単列円筒ころ軸受や多列円筒ころ軸受にも同様に適用可能である。 Note that the guide type of the cage is not limited to the rolling element guide, but may be an outer ring guide or an inner ring guide. That is, this invention does not ask | require the any guide form of a holder | retainer. Although FIG. 1 illustrates an NN type double row cylindrical roller bearing, the present invention can be similarly applied to an NNU type and other bearing type double row cylindrical roller bearings. Furthermore, the present invention is not limited to double-row cylindrical roller bearings but can be similarly applied to single-row cylindrical roller bearings and multi-row cylindrical roller bearings.
図１に示す構成の複列円筒ころ軸受において、複数の柱部４ｂの全てにおける円周方向両側面４ｂ１に逃げ部４ｂ１２を形成した保持器４を使用したもの（実施例１）と、図１に示す構成の複列円筒ころ軸受において、複数の柱部４ｂの一つおきにおける円周方向両側面４ｂ１に逃げ部４ｂ１２を形成した保持器４を使用したもの（実施例２）と、図１に示す構成の複列円筒ころ軸受において、保持器４の逃げ部４ｂ１２をなくし、柱部４ｂの先端側内周部を他の領域と同じ円弧面４ｂ１１とした複列円筒ころ軸受（比較例）とを作製し、エアオイル潤滑下で運転して外輪の温度上昇を比較した。試験結果を図７に示す。 In the double-row cylindrical roller bearing having the configuration shown in FIG. 1, one using a cage 4 in which relief portions 4 b 12 are formed on both circumferential side surfaces 4 b 1 in all of the plurality of column portions 4 b (Example 1), and FIG. In the double-row cylindrical roller bearing having the configuration shown in FIG. 1, a cage 4 in which escape portions 4b12 are formed on both circumferential side surfaces 4b1 of every other column 4b is used (Example 2), and FIG. In the double-row cylindrical roller bearing having the configuration shown in FIG. 2, the double-row cylindrical roller bearing (comparative example) in which the escape portion 4b12 of the cage 4 is eliminated and the inner peripheral portion on the front end side of the column portion 4b is the same arc surface 4b11 as other regions. And were operated under air oil lubrication to compare the temperature rise of the outer ring. The test results are shown in FIG.
試験条件は下記のとおりである。
軸受品番：ＮＮ３０２０Ｋ
保持器の材質：樹脂［ＰＥＥＫ材＋ＣＦ材］
組み込み後のラジアル内部隙間：−５μｍ
円筒ころ：ころ径φ１１ｍｍ、ころ長さ１１ｍｍ、ころＰＣＤφ１２６ｍｍ
潤滑条件：エア量３０ＮＬ／ｍｉｎ、潤滑量０．０２ｍｌ／２０ｍｉｎ、潤滑油粘度ＶＧ３２、ハウジング冷却有り
The test conditions are as follows.
Bearing product number: NN3020K
Cage material: Resin [PEEK material + CF material]
Radial internal gap after installation: -5 μm
Cylindrical roller: Roller diameter φ11mm, Roller length 11mm, Roller PCDφ126mm
Lubrication conditions: Air amount 30NL / min, Lubricating amount 0.02ml / 20min, Lubricating oil viscosity VG32, With housing cooling
図７に示すように、軸受回転数が８０００ｒｐｍ（ｄｍｎ＝１００万）以下の回転数領域では、実施例１、２と比較例とで外輪温度上昇に大きな差異は見られなかったが、軸受回転数が８０００ｒｐｍ（ｄｍｎ＝１００万）を超えると、これらの外輪温度上昇に差が現れ、特に軸受回転数が１００００ｒｐｍ（ｄｍｎ＝１２５万）以上では、これらの差が顕著に現れた。すなわち、実施例１、２は、軸受回転数が８０００ｒｐｍ（ｄｍｎ＝１００万）を超えた領域で外輪温度上昇が比較例よりも低くなっており、特に軸受回転数が１００００ｒｐｍ（ｄｍｎ＝１２５万）以上の領域では外輪温度上昇の抑制効果が顕著であった。また、実施例１と実施例２とを比較すると、実施例２は、軸受回転数が１２０００ｒｐｍ（ｄｍｎ＝１５０万）を超えた領域で外輪温度上昇が急激となったのに対して、実施例１は、そのような領域でも外輪温度上昇の抑制効果を充分に得ることができた。 As shown in FIG. 7, in the rotation speed region where the bearing rotation speed is 8000 rpm (dmn = 1 million) or less, there was no significant difference in the outer ring temperature rise between Examples 1 and 2 and the comparative example. When the number exceeded 8000 rpm (dmn = 1 million), a difference appeared in the temperature increase of these outer rings, and especially when the bearing rotational speed was 10,000 rpm (dmn = 1.25 million) or more, these differences were noticeable. That is, in Examples 1 and 2, the temperature increase of the outer ring is lower than that of the comparative example in a region where the bearing rotational speed exceeds 8000 rpm (dmn = 1 million), and in particular, the bearing rotational speed is 10,000 rpm (dmn = 1.25 million). In the above region, the effect of suppressing the increase in the outer ring temperature was significant. Further, when Example 1 and Example 2 are compared, Example 2 shows that the outer ring temperature rises rapidly in the region where the bearing rotational speed exceeds 12000 rpm (dmn = 1,500,000). No. 1 was able to sufficiently obtain the effect of suppressing the increase in the outer ring temperature even in such a region.
１ 内輪
２ 外輪
３ 円筒ころ
４ 保持器
４ａ 環状部
４ａ１ 内側面
４ｂ 柱部
４ｂ１ 円周方向側面
４ｂ１２ 逃げ部
４ｂ１４ ころ案内部
DESCRIPTION OF SYMBOLS 1 Inner ring 2 Outer ring 3 Cylindrical roller 4 Cage 4a Annular part 4a1 Inner side face 4b Column part 4b1 Circumferential side face 4b12 Escape part 4b14 Roller guide part
Claims (6)
前記保持器の柱部の円周方向側面は、その基端側内周部に、前記円筒ころの転動面に沿う円弧面に形成され、前記柱部が回転時の遠心力によって外径側に弾性変形したときに、前記円筒ころの転動面を案内するころ案内部を有すると共に、その先端側内周部に、前記ころ案内部よりも前記柱部の円周方向中心側に退避し、前記柱部が回転時の遠心力によって外径側に弾性変形したときに、前記円筒ころの転動面と半径方向の接触圧を生じない逃げ部を有することを特徴とする円筒ころ軸受。 An inner ring, an outer ring, a plurality of cylindrical rollers rotatably disposed between the inner ring and the outer ring, and a synthetic resin cage, the cage comprising: an annular portion; and an inner portion of the annular portion A plurality of column portions extending in one axial direction from the side surface, and a plurality of pockets formed between the circumferential side surfaces of the column portions adjacent in the circumferential direction and rotatably holding the cylindrical rollers. In cylindrical roller bearings,
The circumferential side surface of the column portion of the retainer is formed in an arc surface along the rolling surface of the cylindrical roller at the proximal end inner peripheral portion, and the column portion is on the outer diameter side by centrifugal force during rotation. A roller guide portion that guides the rolling surface of the cylindrical roller when elastically deformed, and retracts closer to the center in the circumferential direction of the column portion than the roller guide portion at the inner peripheral portion on the tip end side. A cylindrical roller bearing comprising: a relief portion that does not generate radial contact pressure with a rolling surface of the cylindrical roller when the column portion is elastically deformed to an outer diameter side by a centrifugal force during rotation.
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003394275A JP4322641B2 (en) | 2003-09-30 | 2003-11-25 | Cylindrical roller bearing |
| DE102004046789.7A DE102004046789B4 (en) | 2003-09-30 | 2004-09-27 | Cylindrical roller bearings |
| US10/952,714 US7101088B2 (en) | 2003-09-30 | 2004-09-28 | Cylindrical roller bearing |
| CNB2004100806245A CN100386536C (en) | 2003-09-30 | 2004-09-29 | Cylindrical roller bearing |
| CN2007101628709A CN101187399B (en) | 2003-09-30 | 2004-09-29 | Cylindrical roller bearing |
| CN2007101628728A CN101187400B (en) | 2003-09-30 | 2004-09-29 | Cylindrical roller bearing |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003340473 | 2003-09-30 | ||
| JP2003394275A JP4322641B2 (en) | 2003-09-30 | 2003-11-25 | Cylindrical roller bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2005127493A true JP2005127493A (en) | 2005-05-19 |
| JP4322641B2 JP4322641B2 (en) | 2009-09-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2003394275A Expired - Lifetime JP4322641B2 (en) | 2003-09-30 | 2003-11-25 | Cylindrical roller bearing |
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| JP (1) | JP4322641B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010095647A1 (en) | 2009-02-20 | 2010-08-26 | Ntn株式会社 | Holder, rolling bearing, method of manufacturing holder and injection molding die |
| WO2011111729A1 (en) | 2010-03-10 | 2011-09-15 | Ntn株式会社 | Cage and rolling bearing |
| JP2014231900A (en) * | 2013-05-30 | 2014-12-11 | 日本精工株式会社 | Roller bearing |
| JP2014231899A (en) * | 2013-05-30 | 2014-12-11 | 日本精工株式会社 | Tapered roller bearing |
-
2003
- 2003-11-25 JP JP2003394275A patent/JP4322641B2/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010095647A1 (en) | 2009-02-20 | 2010-08-26 | Ntn株式会社 | Holder, rolling bearing, method of manufacturing holder and injection molding die |
| US9192986B2 (en) | 2009-02-20 | 2015-11-24 | Ntn Corporation | Cage, rolling bearing, method for manufacturing cage, and injection mold |
| WO2011111729A1 (en) | 2010-03-10 | 2011-09-15 | Ntn株式会社 | Cage and rolling bearing |
| US9284982B2 (en) | 2010-03-10 | 2016-03-15 | Ntn Corporation | Cage and rolling bearing |
| JP2014231900A (en) * | 2013-05-30 | 2014-12-11 | 日本精工株式会社 | Roller bearing |
| JP2014231899A (en) * | 2013-05-30 | 2014-12-11 | 日本精工株式会社 | Tapered roller bearing |
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| Publication number | Publication date |
|---|---|
| JP4322641B2 (en) | 2009-09-02 |
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