JP2010133559A - Inner ring of roller bearing - Google Patents

Inner ring of roller bearing Download PDF

Info

Publication number
JP2010133559A
JP2010133559A JP2009267970A JP2009267970A JP2010133559A JP 2010133559 A JP2010133559 A JP 2010133559A JP 2009267970 A JP2009267970 A JP 2009267970A JP 2009267970 A JP2009267970 A JP 2009267970A JP 2010133559 A JP2010133559 A JP 2010133559A
Authority
JP
Japan
Prior art keywords
inner ring
roller bearing
rolling element
contact surfaces
subsidence
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP2009267970A
Other languages
Japanese (ja)
Inventor
Horst Masuch
マッシュ ホルスト
Volker Kestler
ケスラー フォルカー
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler KG filed Critical Schaeffler KG
Publication of JP2010133559A publication Critical patent/JP2010133559A/en
Pending legal-status Critical Current

Links

Images

Classifications

    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C33/6607—Retaining the grease in or near the bearing
    • F16C33/6614—Retaining the grease in or near the bearing in recesses or cavities provided in retainers, races or 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
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • 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
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/50—Crowning, e.g. crowning height or crowning radius

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide an inner ring capable of lengthening the service life of a roller bearing, and manufacturing in a cost effective manner. <P>SOLUTION: The inner ring 1 has a rolling body raceway surface 2 present in the axial direction of the rotary shaft 12 of the inner ring 1 between two edge ends 5, 6 of the inner ring 1. The inner ring 1 has sunken parts 7, 8 between at least one edge end 5, 6 and the rolling body raceway surface 2. More specifically, the roller bearing which rotates at a high speed is lengthened in the service life by improving a lubricating state, can be simply manufactured in a cost-effective manner, and can be used in place of a conventional inner ring without additionally changing the roller bearing. The widths a, b of part between both contact surfaces 3, 4 in the sunken parts 5, 6 are set to 15 to 30% of the interval c of both contact surfaces 3, 4. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

この発明は、転動体端面と接する接触面を有する二つの内輪側縁部の間に、内輪の回転軸に関して、軸方向に存在する転動体走行面を有するローラー軸受の内輪に関する。このような内輪は、側縁部の接触面によって、転動体を軸方向に案内することができる。開放型の外輪との組合せにより、このような内輪は開放型軸受、例えば円筒ローラー軸受に利用できる。そのような開放型軸受の利用分野は、例えば工作機械の主軸の軸受である。   The present invention relates to an inner ring of a roller bearing having a rolling element traveling surface that exists in an axial direction with respect to a rotation axis of the inner ring between two inner ring side edges having contact surfaces in contact with rolling element end faces. Such an inner ring can guide the rolling element in the axial direction by the contact surface of the side edge portion. By combining with an open type outer ring, such an inner ring can be used for an open type bearing, for example, a cylindrical roller bearing. The field of application of such an open type bearing is, for example, a bearing for a spindle of a machine tool.

このような高速回転主軸は、モーター叉は外部から駆動され、固定軸受および開放型軸受により軸支されている。主軸は、固定軸受叉は開放軸受の内輪に回転不能に連結され、これらの軸受の外輪はハウジングに回転不能に連結されている。   Such a high-speed rotation main shaft is driven from a motor or the outside, and is supported by a fixed bearing and an open type bearing. The main shaft is non-rotatably connected to the inner ring of the fixed bearing or the open bearing, and the outer ring of these bearings is non-rotatably connected to the housing.

工作機械におけるそのような主軸の高い回転数は、所望の耐用年数を達成するために、潤滑性能に対する高い要求を突きつける。これらのローラー軸受は、通常グリースにより潤滑される。二つの側縁部を有する内輪をもつ上述の開放型軸受の場合には、特に内輪の潤滑状態がその耐用年数を決定する。ひとつは、転動体と内輪の転動体走行面との接触面は、潤滑材を供給しなければならない。その上、磨耗に対する好ましくない作用を低減するために、転動体側面と側縁部の接触面との十分な潤滑がなされねばならない。   Such high spindle speeds in machine tools impose high demands on lubrication performance in order to achieve the desired service life. These roller bearings are usually lubricated with grease. In the case of the above-mentioned open type bearing with an inner ring having two side edges, the lubrication state of the inner ring determines its useful life. One is that the contact surface between the rolling element and the rolling surface of the inner ring must be supplied with a lubricant. Moreover, sufficient lubrication between the rolling element side surfaces and the contact surfaces of the side edges must be provided in order to reduce undesirable effects on wear.

加工技術上の理由から、現在使用されている内輪は、典型的には、側縁部と転動体走行面との間に円周状に沈下部が設けられている。これは、転動体走行面の加工のために用いられる研削円盤が、転動体走行面を転動体と後で接触する領域を完全に加工できるのに役立つ。このような内輪は独国特許第１０２１６５７号明細書により公知である。   For reasons of processing technology, currently used inner rings typically have a sunken portion in a circumferential shape between the side edge and the rolling element running surface. This is useful for the grinding disk used for machining the rolling element running surface to be able to completely machine the area where the rolling element running surface will later contact the rolling element. Such an inner ring is known from DE 1021657.

独国特許第１０２１６５７号明細書German patent No. 1021657

そのような沈下部の一部が両側の側縁部の間の領域内で延在している。沈下部の長さが大きいほど転動体走行面の有効幅が小さくなる。転動体走行面の有効幅の減少に伴い、ローラー軸受の支持能力も減少するので、現在の技術では、沈下部をできるだけ小さくすることが試みられている。   A portion of such a sinking portion extends in the region between the side edges on both sides. The effective width of the rolling element traveling surface decreases as the length of the sinking portion increases. As the effective width of the rolling element running surface decreases, the support capacity of the roller bearing also decreases, so the current technology attempts to make the subsidence as small as possible.

この発明は、ローラー軸受の耐用寿命を長くでき、コスト上有利に製造できる冒頭に述べた種類の内輪を提案することを課題としている。   An object of the present invention is to propose an inner ring of the type described at the beginning, which can extend the service life of a roller bearing and can be manufactured advantageously in terms of cost.

この課題は、独立請求項の特徴により解決される。この特徴によれば、転動体端面と接触する内輪の二つの側縁部の間で、内輪の回転軸の軸方向に延在する転動体走行面を有する内輪が、少なくとも一つの側縁部と転動体走行面との間に、内輪回転軸回りの沈下部を有しており、該少なくとも一つの沈下部の、両接触面間の領域に存在する部分の幅が、両接触面間の距離の１５％−３０％に相当することを特徴としている。即ち、沈下部は、両接触面内において、その間隔の１５％−３０％の長さにわたり延びている。沈下部の幅および両接触面の距離は、内輪の回転軸を含む断面内において、走行面に平行に計測する。そのような断面においては、両接触面は、常に平行である。円筒ローラー軸受の内輪においては、沈下部の幅は、沈下部の軸方向の長さに相当する。内輪は、一般的な内輪用の材料例えば、軸受鋼により作られる。   This problem is solved by the features of the independent claims. According to this feature, the inner ring having the rolling element running surface extending in the axial direction of the rotation axis of the inner ring is between at least one side edge part between the two side edge parts of the inner ring in contact with the rolling element end surface. Between the rolling element traveling surfaces, there is a depressed portion around the rotation axis of the inner ring, and the width of the portion of the at least one depressed portion existing in the region between the two contact surfaces is the distance between the two contact surfaces. It is characterized by being equivalent to 15% -30%. That is, the subsidence extends over a length of 15% to 30% of the interval in both contact surfaces. The width of the sinking portion and the distance between both contact surfaces are measured in parallel to the running surface in the cross section including the rotation axis of the inner ring. In such a cross section, both contact surfaces are always parallel. In the inner ring of the cylindrical roller bearing, the width of the depressed portion corresponds to the axial length of the depressed portion. The inner ring is made of a general inner ring material such as bearing steel.

この課題の発明に従う解決法は、従来の先行技術が教える方向と全く異なる方向を目指している。この発明は、発明に従う沈下部により転動体走行面の幅が減少し、それによりその内輪を有するローラー軸受の支持能力が小さくなると言う知見に基づいている。従来の見解に反して、大きくされた沈下部は、ある用途においては、沈下部によりもたらされる利点がこれらの不利を補うので有利である。   The solution according to the invention of this problem aims at a completely different direction from the direction taught by the prior art. The present invention is based on the finding that the width of the rolling element running surface is reduced by the subsidence according to the invention, thereby reducing the support capacity of the roller bearing having its inner ring. Contrary to the conventional view, enlarged subsidence is advantageous in some applications because the advantages provided by subsidence compensate for these disadvantages.

この沈下部により、大きな潤滑剤溜めが形成される。これにより、明らかに潤滑性能が改良された。特に、両接触面間の距離の１５％−３０％、好ましくは２０％−２５％の長さの発明に従う沈下部により、非常に良い潤滑剤供給が可能と成った。さらに、潤滑剤溜めを側縁部の位置に設けたので、潤滑剤が転動体の側面から側縁部の接触面へ供給され、側縁部の接触面の最適な潤滑が得られる。   This sinking portion forms a large lubricant reservoir. This clearly improved the lubrication performance. In particular, the subsidence according to the invention of a length of 15% -30%, preferably 20% -25% of the distance between the two contact surfaces has enabled a very good lubricant supply. Further, since the lubricant reservoir is provided at the position of the side edge portion, the lubricant is supplied from the side surface of the rolling element to the contact surface of the side edge portion, and optimum lubrication of the contact surface of the side edge portion is obtained.

内輪の転動体走行面が小さくされることにより、転動体と内輪との摩擦が減少し、稼動中の摩擦熱の発生が少ない。特に高速回転のローラー軸受において利点が発揮される。   By reducing the rolling element running surface of the inner ring, the friction between the rolling element and the inner ring is reduced, and the generation of frictional heat during operation is reduced. The advantage is exhibited particularly in a high-speed roller bearing.

この発明は、高速回転においては、転動体が遠心力により外方に押されるので、高速回転の場合に有用である。沈下部は、先ず転動体走行面の幅の減少につながり、これが担持能力の低減につながることになる。しかし、遠心力により、転動体と内輪の転動体走行面との接触力は低減されるので、担持能力の低減は実質上僅かとなる。内輪の転動体走行面と転動体との接触形態の本発明に従う変更に起因する担持能力の低減は、回転数が大きいほど小さくなる。   The present invention is useful for high-speed rotation because the rolling element is pushed outward by centrifugal force at high-speed rotation. The sinking portion first leads to a reduction in the width of the rolling element running surface, which leads to a reduction in carrying capacity. However, since the contact force between the rolling element and the rolling surface of the inner ring is reduced by the centrifugal force, the reduction in the carrying capacity is substantially small. The reduction in the carrying capacity due to the change according to the present invention of the contact form between the rolling element running surface of the inner ring and the rolling element becomes smaller as the rotational speed increases.

この発明の別の実施形態は、従属請求項に記載されている。これらの特徴は、任意に組合せができる。   Further embodiments of the invention are described in the dependent claims. These features can be combined arbitrarily.

一つの実施形態によれば、内輪が、側縁部と転動体走行面との間に内輪の回転軸回りに沈下部を有している。この沈下部の両接触面の間に存在する部分の幅は両接触面間の距離の１５％−３０％に相当する。好ましくは、沈下部の両接触面の間に存在する部分の幅は両接触面間の距離の２０％−２５％に相当する。さらに、接触面間にある両沈下部の幅が等しい大きさであるのが好ましい。   According to one embodiment, the inner ring has a depressed portion around the rotation axis of the inner ring between the side edge and the rolling element traveling surface. The width of the portion existing between the two contact surfaces of the subsidence corresponds to 15% -30% of the distance between the two contact surfaces. Preferably, the width of the portion existing between the contact surfaces of the sinking portion corresponds to 20% -25% of the distance between the contact surfaces. Furthermore, it is preferable that the widths of the two subsidence portions between the contact surfaces are equal.

さらに別の実施形態によれば、沈下部（単数叉は複数）は、アンダーカット、溝叉は転動体走行面の後退部により形成される。勿論、沈下部は、他の形態や、上述の形態の組合せにより形成することができる。転動体走行面や両接触面と同様に、沈下部も内輪の回転軸に関して回転対称に形成するのが好ましい。一つの沈下部が隣接する接触面から他方の沈下部、即ち対向する沈下部に向かって一方にのみ延在させることができる。沈下部の全体は、これにより、両接触面の間にある沈下部の幅に相当する。沈下部がこれとは反対の方向に延びていることも考えられる。これにより、隣接する接触面に関してアンダーカットが形成される。沈下部の深さは、基本的には、任意の大きさにできる。沈下部の深さを大きくしても利用面は大きくならないが、潤滑剤溜まりを大きくすることは有利である。   According to yet another embodiment, the subsidence (single or plural) is formed by an undercut, a groove or a receding portion of the rolling element running surface. Of course, the subsidence can be formed by other forms or combinations of the above forms. Similarly to the rolling element running surface and the two contact surfaces, the sinking portion is preferably formed to be rotationally symmetric with respect to the rotation axis of the inner ring. One subsidence can extend only from one adjacent contact surface to the other subsidence, i.e., the opposing subsidence. The entirety of the squat is thereby corresponding to the width of the squat between the contact surfaces. It is also conceivable that the subsidence extends in the opposite direction. Thereby, an undercut is formed with respect to the adjacent contact surface. The depth of the subsidence can be basically set to an arbitrary size. Increasing the depth of the subsidence does not increase the use surface, but it is advantageous to increase the lubricant pool.

さらに別の実施形態によれば、転動体走行面は、曲面に形成される。内輪は、これにより転動体走行面の領域において、凸面形状を有する。好ましくは、転動体走行面は円周曲面に形成される。即ち、内輪の回転軸を含む平面による断面図において、転動体走行面は一定の曲率を有している。平らな転動体走行面に対して、この転動体走行面の両端部における直径は減少している。更に別の実施形態においては、転動体走行面の軸方向端部において該走行面の後退部は、転動体走行面の軸方向中央における直径の０．００２５％から０．０１５％、好ましくは、０．００５％から０．０１２５％、さらに好ましくは、０．０１％の大きさを有する。軸方向中央において８０ｍｍである転動体走行面の直径を有する円筒ローラー軸受の内輪の場合、転動体走行面の軸方向端部の直径は例えば８μ、即ち８０ｍｍの０．０１％だけ減少している。曲面の転動体走行面の利点は、稼動時において、角部走行の現象が低減されることである。   According to still another embodiment, the rolling element traveling surface is formed in a curved surface. Accordingly, the inner ring has a convex shape in the region of the rolling element traveling surface. Preferably, the rolling element traveling surface is formed in a circumferential curved surface. That is, in the cross-sectional view of the plane including the rotation axis of the inner ring, the rolling element traveling surface has a certain curvature. With respect to a flat rolling element traveling surface, the diameters at both ends of the rolling element traveling surface are reduced. In yet another embodiment, the retracted portion of the running surface at the axial end of the rolling element running surface is 0.0025% to 0.015% of the diameter at the axial center of the rolling element running surface, preferably It has a size of 0.005% to 0.0125%, more preferably 0.01%. In the case of an inner ring of a cylindrical roller bearing having a diameter of the rolling element running surface of 80 mm at the center in the axial direction, the diameter of the axial end of the rolling element running surface is reduced by, for example, 8 μ, ie 0.01% of 80 mm. . The advantage of the curved rolling element traveling surface is that the corner traveling phenomenon is reduced during operation.

さらに別の実施形態によれば、内輪は、円筒ローラー軸受の内輪である。転動体走行面は円筒状の外表面、場合により曲面を有する外表面に相当する。   According to yet another embodiment, the inner ring is an inner ring of a cylindrical roller bearing. The rolling element running surface corresponds to a cylindrical outer surface, and in some cases, an outer surface having a curved surface.

この発明の利点は、発明に従う内輪を有するローラー軸受の回転数が高ければ高いほど発揮される。それ故、内輪は、好ましくは高速回転用のローラー軸受の内輪である。例えば、この内輪は、工作機械の主軸用のローラー軸受に使用される。   The advantages of the present invention are exhibited as the number of rotations of the roller bearing having the inner ring according to the invention increases. Therefore, the inner ring is preferably an inner ring of a roller bearing for high-speed rotation. For example, the inner ring is used as a roller bearing for a main shaft of a machine tool.

発明に従う内輪を有するローラー軸受は、転動体走行面の上を転がり、その側面が側縁部の接触面と接触できる回転対称のローラーをさらに有する。このようなローラー軸受は、さらに外輪を含むことができる。その代わり、転動体は直接にハウジング内でまたは連結構造の中で転がることができる。好ましくは、ローラー軸受は、円筒ローラー軸受である。アンギュラーローラー軸受叉は円錐ローラー軸受である場合も考えられる。   The roller bearing having an inner ring according to the invention further has a rotationally symmetric roller that rolls on the rolling element running surface and whose side surface can contact the contact surface of the side edge. Such a roller bearing can further include an outer ring. Instead, the rolling elements can roll directly in the housing or in the connecting structure. Preferably, the roller bearing is a cylindrical roller bearing. An angular roller bearing or a conical roller bearing is also conceivable.

好ましい実施形態によれば、ローラー軸受が、開放型軸受として主軸の軸受に利用されている円筒ローラー軸受である。ローラー軸受の外輪はこのために側縁部無しのものである。   According to a preferred embodiment, the roller bearing is a cylindrical roller bearing that is used as a main shaft bearing as an open type bearing. The outer ring of the roller bearing is therefore free from side edges.

上述の発明の実施例が、添付の図面を参照して以下に詳述される。
この発明の第一の実施例の断面図 この発明の第二の実施例の断面図 この発明による内輪を有するローラー軸受の断面図 この発明による内輪を有するローラー軸受の断面図 この発明による軸受を用いて支持されたスピンドルの断面図 Embodiments of the above-described invention are described in detail below with reference to the accompanying drawings.
Sectional view of the first embodiment of the present invention Sectional drawing of 2nd Example of this invention Sectional view of a roller bearing having an inner ring according to the present invention Sectional view of a roller bearing having an inner ring according to the present invention Sectional view of a spindle supported using a bearing according to the invention

図１は、第一の実施例によるこの発明の内輪１を示す。内輪１の回転軸１２を含む切断面で切断した内輪１の断面図が示されている。回転軸１２と平行な転動体走行面２が示されている。側縁部５，６の両接触面３，４は、転動体走行面２の軸方向終端部を成している。両接触面３，４は互いに平行で、転動体走行面２および回転軸１２に直交している。内輪１は、円筒ローラー軸受用である。   FIG. 1 shows an inner ring 1 of the present invention according to a first embodiment. A cross-sectional view of the inner ring 1 cut along a cutting plane including the rotation shaft 12 of the inner ring 1 is shown. A rolling element traveling surface 2 parallel to the rotating shaft 12 is shown. Both contact surfaces 3, 4 of the side edge portions 5, 6 form an axial end portion of the rolling element traveling surface 2. Both contact surfaces 3 and 4 are parallel to each other and are orthogonal to the rolling element traveling surface 2 and the rotating shaft 12. The inner ring 1 is for a cylindrical roller bearing.

各側縁部５，６と転動体走行面２との間に沈下部７、８が存在する。沈下部７，８の幅は、ａ叉はｂで示され、両接触面３，４の間における沈下部の軸方向の大きさを表している。両沈下部７，８は、両接触面３，４の間の領域においてのみ、軸方向に延びている。幅ａ叉はｂは符号ｃで示された接触面３，４間の距離の約２０％に相当する。両沈下部７，８は、夫々の接触面３，４に直接接続されている。接触面３，４の沈下部７，８への遷移部および沈下部７，８と転動体走行面２との遷移部はＲ部により丸められている。   Sinks 7 and 8 exist between the side edges 5 and 6 and the rolling element traveling surface 2. The width of the sunk portions 7 and 8 is indicated by a or b, and represents the size of the sunk portion between the contact surfaces 3 and 4 in the axial direction. The two subsidence parts 7 and 8 extend in the axial direction only in the region between the contact surfaces 3 and 4. The width a or b corresponds to about 20% of the distance between the contact surfaces 3 and 4 indicated by the symbol c. Both subsidence parts 7 and 8 are directly connected to the respective contact surfaces 3 and 4. Transition portions of the contact surfaces 3 and 4 to the subsidence portions 7 and 8 and a transition portion between the subsidence portions 7 and 8 and the rolling element traveling surface 2 are rounded by the R portion.

内輪１の内側穴は円錐状の内側装着面１０を有している。   The inner hole of the inner ring 1 has a conical inner mounting surface 10.

図２は、第２の実施例によるこの発明の内輪１を示す。この実施例も、実質的には、図１に示された実施例に対応している。しかしこの例においては、転動体走行面２が曲面にされ、凸形状を有する。   FIG. 2 shows an inner ring 1 of the present invention according to a second embodiment. This embodiment also substantially corresponds to the embodiment shown in FIG. However, in this example, the rolling element running surface 2 is curved and has a convex shape.

最大直径の点Ｄａｍは、転動体走行面２の軸方向中央に存在する。その点から軸方向に離れるにつれて、直径は減少する。即ち転動体走行面２は半径方向に後退する。この定常的な後退は転動体走行面２の各軸方向端部に僅かに減少した直径Ｄａｅを有している。   The point Dam with the maximum diameter exists at the center in the axial direction of the rolling element traveling surface 2. The diameter decreases with increasing axial distance from that point. That is, the rolling element running surface 2 moves backward in the radial direction. This steady retraction has a slightly reduced diameter Dae at each axial end of the rolling element running surface 2.

この例においては、Ｄａｍ＝８０ｍｍであり、Ｄａｅ＝７９．９９２ｍｍである。   In this example, Dam = 80 mm and Dae = 79.992 mm.

図３は、発明に従う内輪１を有するローラー軸受を示している。ここでも、内輪１の回転軸１２を含む断面図の半分を示している。内輪１は、図２の実施例の内輪１に相当する。   FIG. 3 shows a roller bearing with an inner ring 1 according to the invention. Here, half of the sectional view including the rotation shaft 12 of the inner ring 1 is shown. The inner ring 1 corresponds to the inner ring 1 in the embodiment of FIG.

このローラー軸受は、内輪の転動体走行面２と外輪１５の転動体走行面１４の間で転がる円筒状転動体１３を有する円筒ローラー軸受を示している。外輪１５は、開放型となるように、側縁部がない。   This roller bearing is a cylindrical roller bearing having a cylindrical rolling element 13 that rolls between the rolling element running surface 2 of the inner ring and the rolling element running surface 14 of the outer ring 15. The outer ring 15 does not have a side edge so as to be an open type.

図４は、発明に従う内輪１１を含むローラー軸受を示す。内輪は、アンダーカットとされた二つの沈下部７，８を有している。それ故、沈下部７，８は、二つの接触面の間の領域に軸方向に延びる部分ａ叉はｂを有しているが、この部分は、沈下部の幅の一部にすぎない。この沈下部７，８は接触面の軸方向外側に軸方向延長部ｘを有している。   FIG. 4 shows a roller bearing comprising an inner ring 11 according to the invention. The inner ring has two subsidence parts 7 and 8 which are undercut. Therefore, the sinking parts 7 and 8 have a part a or b extending in the axial direction in the region between the two contact surfaces, but this part is only a part of the width of the sinking part. The subsidence parts 7 and 8 have an axial extension x on the outside of the contact surface in the axial direction.

図５は、工作機械の主軸１６を示し、その主軸は、一方がアンギュラボール軸受１７により支持され、他方が、例えば図３に示された円筒ローラー軸受により支持されている。   FIG. 5 shows a main shaft 16 of a machine tool, one of which is supported by an angular ball bearing 17 and the other is supported by, for example, a cylindrical roller bearing shown in FIG.

１ 内輪
２ 転動体走行面
３ 接触面
４ 接触面
５ 側縁部
６ 側縁部
７ 沈下部
８ 沈下部
９ Ｒ部
１０ 内側装着面
１１ ローラー軸受
１２ 回転軸
１３ 転動体
１４ 転動体走行面
１５ 外輪
１６ 主軸
１７ ラジアルボール軸受
１８ 円筒ローラー軸受 DESCRIPTION OF SYMBOLS 1 Inner ring 2 Rolling body running surface 3 Contact surface 4 Contact surface 5 Side edge 6 Side edge 7 Sinking part 8 Sinking part 9 R part 10 Inner mounting surface 11 Roller bearing 12 Rotating shaft 13 Rolling body 14 Rolling body running surface 15 Outer ring 16 Spindle 17 Radial ball bearing 18 Cylindrical roller bearing

Claims (11)

ローラー軸受（１１）の内輪であって、転動体端面と接触する接触面（３，４）を有する内輪（１）の二つの側縁部（５，６）の間に、該内輪（１）の回転軸（１２）の軸方向に延在する転動体走行面（２）を有しており、該内輪（１）は、少なくとも一つの側縁部（５，６）と転動体走行面（２）との間に、内輪回転軸（１２）の回りの沈下部（７，８）を有しており、該少なくとも一つの沈下部（７，８）の、両接触面（３，４）間の領域に存在する部分の幅が、両接触面間の距離の１５％−３０％に相当することを特徴とするローラー軸受の内輪。   An inner ring (1) between two side edges (5, 6) of the inner ring (1), which is an inner ring of the roller bearing (11) and has a contact surface (3, 4) in contact with the end face of the rolling element. The rotating body running surface (2) extends in the axial direction of the rotating shaft (12) of the rotating shaft (12), and the inner ring (1) has at least one side edge (5, 6) and a rolling body running surface ( 2) between the contact surfaces (3, 4) of the at least one subsidence (7, 8). An inner ring of a roller bearing, characterized in that the width of the portion existing in the area between them corresponds to 15% -30% of the distance between both contact surfaces. 該少なくとも一つの沈下部（７，８）の、両接触面（３，４）間の領域に存在する部分の幅が、両接触面間の距離の２０％−２５％に相当する請求項１に記載の内輪。   2. The width of the portion of the at least one subsidence (7, 8) existing in the region between the contact surfaces (3, 4) corresponds to 20% -25% of the distance between the contact surfaces. The inner ring described in. 内輪（２）が、該側縁部（５，６）の各々と該転動体走行面（２）との間において、該回転軸（１２）の回りの沈下部（７，８）を有しており、該各沈下部（７，８）の、両接触面（３，４）の間の領域に存在する部分の幅が、該両接触面（３，４）の間の距離の１５％−３０％、好ましくは２０％−２５％に相当することを特徴とする請求項１叉は請求項２に記載の内輪。   The inner ring (2) has a depressed portion (7, 8) around the rotating shaft (12) between each of the side edges (5, 6) and the rolling element running surface (2). The width of the portion of each subsidence (7, 8) in the region between the two contact surfaces (3, 4) is 15% of the distance between the two contact surfaces (3, 4). The inner ring according to claim 1 or 2, characterized in that it corresponds to -30%, preferably 20% -25%. 前記一つ叉は複数の沈下部（７，８）が、アンダーカット、溝叉は転動体走行面（２）の後退部により形成されていることを特徴とする請求項１ないし３に記載の内輪。   The one or more subsidence parts (7, 8) are formed by undercuts, grooves or receding parts of rolling element running surfaces (2). Inner ring. 前記転動体走行面（２）が曲面に形成されている請求項１ないし４に記載の内輪。   The inner ring according to any one of claims 1 to 4, wherein the rolling element running surface (2) is formed in a curved surface. 前記転動体走行面（２）が、該転動体走行面（２）の軸方向端において、転動体走行面（２）の軸方向中央における該転動体走行面の直径の０．００２５％から０．０１５％、好ましくは０．００５％から０．０１２５％、さらに好ましくは０．０１％だけ後退していることを特徴とする請求項１ないし５に記載の内輪。   The rolling element traveling surface (2) has an axial end of the rolling element traveling surface (2) of 0.0025% to 0 of the diameter of the rolling element traveling surface at the axial center of the rolling element traveling surface (2). 6. Inner ring according to claims 1 to 5, characterized in that it is retracted by .015%, preferably 0.005% to 0.0125%, more preferably 0.01%. 内輪（１）が円筒ローラー軸受（１８）の内輪である請求項１ないし６に記載の内輪。   The inner ring (1) according to claim 1, wherein the inner ring (1) is an inner ring of a cylindrical roller bearing (18). 内輪（１）が、高速回転用ローラー軸受の内輪である請求項１ないし７に記載の内輪。   The inner ring according to any one of claims 1 to 7, wherein the inner ring (1) is an inner ring of a roller bearing for high-speed rotation. 請求項１ないし８の一つに記載の内輪（１）及び、転動体走行面（２）上を転がることができ、その端面が側縁部の接触面（３，４）と接触できる回転対称のローラー（１３）を含むローラー軸受。   Rotational symmetry that can roll on the inner ring (1) according to one of claims 1 to 8 and the rolling element running surface (2), and whose end surface can contact the contact surface (3, 4) of the side edge. Roller bearing comprising a roller (13). ローラー軸受が円筒ローラー軸受（１８）であることを特徴とする請求項９に記載のローラー軸受。   10. Roller bearing according to claim 9, characterized in that the roller bearing is a cylindrical roller bearing (18). 該円筒ローラー軸受（１８）が開放型軸受として主軸支持軸受とされている請求項９叉は１０に記載のローラー軸受。   The roller bearing according to claim 9 or 10, wherein the cylindrical roller bearing (18) is a main shaft support bearing as an open type bearing.
JP2009267970A 2008-12-05 2009-11-25 Inner ring of roller bearing Pending JP2010133559A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200810060479 DE102008060479A1 (en) 2008-12-05 2008-12-05 Inner ring of a roller bearing

Publications (1)

Publication Number Publication Date
JP2010133559A true JP2010133559A (en) 2010-06-17

Family

ID=42101331

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2009267970A Pending JP2010133559A (en) 2008-12-05 2009-11-25 Inner ring of roller bearing

Country Status (4)

Country Link
JP (1) JP2010133559A (en)
CN (1) CN102239338B (en)
DE (1) DE102008060479A1 (en)
WO (1) WO2010063282A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101398985B1 (en) 2013-03-26 2014-05-27 주식회사 일진글로벌 Taper roller wheel bearing assembly

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012204571A1 (en) 2012-03-22 2013-09-26 Schaeffler Technologies AG & Co. KG Rolling bearing has recesses that are respectively provided at boards of inner ring raceway and outer ring raceway, are filled with lubricant and are provided with different cross section areas
GB2520718A (en) * 2013-11-29 2015-06-03 Skf Ab Roller bearing
CN105114449A (en) * 2015-07-24 2015-12-02 山东凯美瑞轴承科技有限公司 Floating deflection mixing bearing for electric main shaft
DE102019113897A1 (en) * 2019-05-24 2020-11-26 Liebherr-Components Biberach Gmbh Rolling bearings and material handling and / or construction machine with such a rolling bearing
WO2022078583A1 (en) * 2020-10-14 2022-04-21 Aktiebolaget Skf Cylindrical roller bearing

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1021657B (en) 1954-06-19 1957-12-27 Skf Kugellagerfabriken Gmbh Cylindrical roller bearings
CN2242992Y (en) * 1994-09-28 1996-12-18 北京轴承厂 Hollow roller bearing set with micro windage value
CN100451368C (en) * 2003-11-07 2009-01-14 株式会社捷太格特 Oil lubrication-type rolling bearing device
US20080063331A1 (en) * 2004-06-11 2008-03-13 Ntn Corporation Lubricating Structure Of Rolling Bearing
JP2007051700A (en) * 2005-08-18 2007-03-01 Jtekt Corp Tapered roller bearing, tapered roller bearing device, and pinion shaft supporting device for vehicle using the same
JP2008039128A (en) * 2006-08-09 2008-02-21 Nsk Ltd Collared roller bearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101398985B1 (en) 2013-03-26 2014-05-27 주식회사 일진글로벌 Taper roller wheel bearing assembly
US9056522B2 (en) 2013-03-26 2015-06-16 Il Jin Global Co., Ltd. Tapered roller wheel bearing assembly

Also Published As

Publication number Publication date
CN102239338A (en) 2011-11-09
WO2010063282A1 (en) 2010-06-10
CN102239338B (en) 2013-07-31
DE102008060479A1 (en) 2010-06-10

Similar Documents

Publication Publication Date Title
JP5870563B2 (en) Roller bearing cage and rolling bearing
JP5129762B2 (en) Angular contact ball bearings
JP2010133559A (en) Inner ring of roller bearing
JP6922928B2 (en) Cage for rolling bearings and rolling bearings
JP4006836B2 (en) Ball bearing
JP2010133560A (en) Roller bearing equipped with optimized outer ring
JP2003314558A (en) Retainer of radial ball bearing
JP2004251323A (en) Cylindrical roller bearing
JP2012021581A (en) Oil-air lubrication type rolling bearing device
JP2010043680A (en) Floating bush bearing
JP5929544B2 (en) Rolling bearings and spindles for machine tools
CN105715676A (en) Double-row spherical roller bearing, manufacturing method and wind turbine bearing arrangement
JP2008175239A (en) Ball bearing crown cage and ball bearing
JP2008002495A (en) Automatic aligning roller bearing
JP2008019937A (en) Rolling bearing
CN203477063U (en) High-rotating-speed thrust cylindrical roller bearing
JP2007100775A (en) Thrust cylindrical roller bearing
JP2007232177A (en) Rolling bearing
JP2007032674A (en) Rolling bearing
JP2006214533A (en) Thrust cylindrical roller bearing
WO2018225720A1 (en) Holder for rolling bearing, and rolling bearing
JP2003254338A (en) Conical roller bearing
JP6065423B2 (en) Rolling bearings and spindles for machine tools
JP2003214438A (en) Rolling bearing
JP2011112201A (en) Ball bearing