JP2018035944A - Method for manufacturing ball bearing - Google Patents

Method for manufacturing ball bearing Download PDF

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JP2018035944A
JP2018035944A JP2017230850A JP2017230850A JP2018035944A JP 2018035944 A JP2018035944 A JP 2018035944A JP 2017230850 A JP2017230850 A JP 2017230850A JP 2017230850 A JP2017230850 A JP 2017230850A JP 2018035944 A JP2018035944 A JP 2018035944A
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Prior art keywords
grease
ball bearing
shield plate
ring
outer ring
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泰成 高鶴
Yasunari Takatsuru
泰成 高鶴
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—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
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
    • 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
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7846—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with a gap between the annular disc and the inner race
    • F16C33/785—Bearing shields made of sheet metal

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  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a method for manufacturing a ball bearing that can provide low torque even while preload is applied for such use as supporting a rotary part of a small-sized motor.SOLUTION: A method for manufacturing a ball bearing includes applying grease 6 in the vicinity of a shield plate 50 of an inner peripheral surface 21 of an outer ring (non-rotary ring) 2 of mainly a retainer 4 of a space (bearing space) surrounded by an inner ring 1, the outer ring 2, a ball 3 and the shield plate 50 using a nozzle pierced with a plurality of holes.SELECTED DRAWING: Figure 1

Description

この発明は、内輪と外輪との間を軸方向両端で塞ぐシールド板を備えた玉軸受に関する。特に、ファンモータ等の小型モータの回転部を支持する用途に好適なシールド板付き玉軸受に関する。   The present invention relates to a ball bearing including a shield plate that closes between an inner ring and an outer ring at both axial ends. In particular, the present invention relates to a ball bearing with a shield plate suitable for use in supporting a rotating part of a small motor such as a fan motor.

玉軸受は、いずれか一方が回転輪となり他方が非回転輪となる内輪および外輪と、内輪と外輪の間に転動自在に配置された複数の玉とを有する。グリースが封入されて使用される玉軸受として、内輪と外輪との間を軸方向両端で塞ぐシールド板を有するものがある。シールド板を有する玉軸受においては、内輪、外輪、玉、およびシールド板で囲まれた空間にグリースが封入されている。   The ball bearing has an inner ring and an outer ring, one of which is a rotating wheel and the other is a non-rotating ring, and a plurality of balls that are arranged so as to roll between the inner ring and the outer ring. Some ball bearings used with grease sealed include a shield plate that closes the inner ring and the outer ring at both ends in the axial direction. In a ball bearing having a shield plate, grease is sealed in a space surrounded by the inner ring, the outer ring, the ball, and the shield plate.

シールド板は、円板の中心に円穴を有するドーナツ板状であり、シールド板の内周縁部が内輪の外周面と係合し、シールド板の外周縁部が外輪の内周面と係合する。シールド板が外輪に固定されている場合は、シールド板の内周縁部が内輪の外周面と所定隙間で近接する近接部となり、シールド板が内輪に固定されている場合は、シールド板の外周縁部が外輪の内周面と所定隙間で近接する近接部となる。   The shield plate has a donut plate shape with a circular hole in the center of the disc, and the inner peripheral edge of the shield plate engages with the outer peripheral surface of the inner ring, and the outer peripheral edge of the shield plate engages with the inner peripheral surface of the outer ring. To do. When the shield plate is fixed to the outer ring, the inner peripheral edge of the shield plate is close to the outer peripheral surface of the inner ring with a predetermined gap, and when the shield plate is fixed to the inner ring, the outer peripheral edge of the shield plate The portion is a proximity portion that is close to the inner peripheral surface of the outer ring with a predetermined gap.

グリースで潤滑されている玉軸受は、軸受空間が狭い場合、封入されたグリースが潰され易い。これに伴って、グリースの基油だけでなく増ちょう剤が内外輪の軌道溝や保持器のポケットに入り、攪拌抵抗が増大して、回転トルクが上昇する恐れがある。
特許文献１には、必要グリース量を封入して耐久性を満足しつつ、低トルクを実現するために、グリースを保持器の軸方向一側の端面だけでなく軸方向反対側の端面にも配置することが記載されている。
特許文献２には、小型モータの回転部を支持する玉軸受の低トルク化や個体毎のバラツキの低減を図ることを目的として、内輪および外輪のうちの非回転輪（固定輪）の溝肩部（軌道面が設けられた周面）に潤滑剤を塗布することが記載されている。 Ball bearings lubricated with grease tend to crush the enclosed grease when the bearing space is narrow. Along with this, not only the grease base oil but also the thickener enters the raceway grooves of the inner and outer rings and the pockets of the cage, and the agitation resistance increases and the rotational torque may increase.
In Patent Document 1, in order to achieve low torque while filling the required amount of grease and satisfying the durability, grease is applied not only to the end surface on one side in the axial direction but also to the end surface on the opposite side in the axial direction. It is described to arrange.
Patent Document 2 discloses a groove shoulder of a non-rotating ring (fixed ring) of an inner ring and an outer ring for the purpose of reducing the torque of a ball bearing that supports a rotating part of a small motor and reducing variation among individual rings. It describes that a lubricant is applied to a portion (a peripheral surface provided with a raceway surface).

特開平９−７９２６６号公報JP-A-9-79266 特開２００８−２２３８５４号公報JP 2008-223854 A

特許文献１に記載された方法は、グリースを保持器の両側に均等に配置することで、保持器の回転によりグリースにかかる遠心力を小さくする方法であるが、保持器が回転体である以上、根本的な解決方法とはならない。
小型軸受の軸受空間は元々狭いが、予圧を付与すると、内外輪に軸方向のずれが生じるためさらに狭くなり、封入されたグリースがさらに潰されやすくなる。特許文献２に記載されているように、単に非回転輪の溝肩部に潤滑剤を塗布すると、軸受に予圧を付与した後に軸受の内部空間が狭くなるため、グリースが潰されやすい。
この発明の課題は、小型モータの回転部を支持する用途等で軸受の内部空間が狭い場合でも、低トルク化が実現できる玉軸受の製造方法を提供することである。 The method described in Patent Document 1 is a method in which the grease is evenly arranged on both sides of the cage to reduce the centrifugal force applied to the grease by the rotation of the cage. This is not a fundamental solution.
The bearing space of the small bearing is originally narrow, but if preload is applied, the inner and outer rings are displaced in the axial direction, so that it is further narrowed and the enclosed grease is more easily crushed. As described in Patent Document 2, when a lubricant is simply applied to the groove shoulder portion of the non-rotating wheel, the internal space of the bearing becomes narrow after preload is applied to the bearing, so that the grease is easily crushed.
The subject of this invention is providing the manufacturing method of the ball bearing which can implement | achieve a reduction in torque, even when the internal space of a bearing is narrow for the use etc. which support the rotation part of a small motor.

上記課題を解決するために、この発明の一態様は、いずれか一方が回転輪となり他方が非回転輪となる内輪および外輪と、前記内輪と前記外輪の間に転動自在に配置された複数の玉と、前記玉を保持するポケットに開口部を有する保持器と、前記内輪と前記外輪との間を軸方向両端で塞ぐシールド板と、前記内輪、前記外輪、前記玉、および前記シールド板で囲まれた空間に配置されたグリースと、を有する玉軸受の製造方法であって、前記グリースを、前記保持器の、前記空間を構成する非回転輪の面の前記シールド板近傍に、複数の穴の開いたノズルを使用して塗布することを特徴とする玉軸受の製造方法である。   In order to solve the above-described problems, one aspect of the present invention includes an inner ring and an outer ring, one of which is a rotating wheel and the other is a non-rotating ring, and a plurality of rollers disposed between the inner ring and the outer ring so as to be freely rollable Ball, a cage having an opening in a pocket for holding the ball, a shield plate that closes between the inner ring and the outer ring at both axial ends, the inner ring, the outer ring, the ball, and the shield plate A ball bearing having a grease disposed in a space surrounded by a plurality of the grease in the vicinity of the shield plate on the surface of the non-rotating ring constituting the space of the cage. The ball bearing is manufactured by using a nozzle having a plurality of holes.

また、この発明の別の態様は、いずれか一方が回転輪となり他方が非回転輪となる内輪および外輪と、前記内輪と前記外輪の間に転動自在に配置された複数の玉と、前記玉を保持するポケットの軸方向一端に開口部を有する保持器と、前記内輪と前記外輪との間を軸方向両端で塞ぐシールド板と、前記内輪、前記外輪、前記玉、および前記シールド板で囲まれた空間に配置されたグリースと、を有する玉軸受の製造方法であって、前記グリースの塗布体積は前記空間の１７体積％以上３０体積％以下であり、前記グリースの混和ちょう度は２５０以下であり、前記グリースを、前記保持器の前記開口部側の、前記空間を構成する非回転輪の面の前記シールド板近傍に、複数の穴の開いたノズルを使用して塗布することを特徴とする玉軸受の製造方法である。   Further, another aspect of the present invention includes an inner ring and an outer ring, one of which is a rotating wheel and the other is a non-rotating wheel, a plurality of balls that are rotatably arranged between the inner ring and the outer ring, A cage having an opening at one axial end of a pocket for holding a ball, a shield plate that closes between the inner ring and the outer ring at both axial ends, the inner ring, the outer ring, the ball, and the shield plate And a grease disposed in an enclosed space, wherein the grease application volume is not less than 17% by volume and not more than 30% by volume of the space, and the grease penetration is 250. The grease is applied by using a nozzle having a plurality of holes in the vicinity of the shield plate on the surface of the non-rotating ring constituting the space on the opening side of the cage. Made of featured ball bearings It is a method.

また、この発明の別の態様の玉軸受は、いずれか一方が回転輪となり他方が非回転輪となる内輪および外輪と、前記内輪と前記外輪の間に転動自在に配置された複数の玉と、前記玉を保持するポケットの軸方向一端に開口部を有する保持器と、前記内輪と前記外輪との間を軸方向両端で塞ぐシールド板と、前記内輪、前記外輪、前記玉、および前記シールド板で囲まれた空間に配置されたグリースと、を有し、下記構成(a) または(a')と(b) および(c) を満たすことを特徴とする。   Further, a ball bearing according to another aspect of the present invention includes an inner ring and an outer ring, one of which is a rotating wheel and the other is a non-rotating ring, and a plurality of balls that are rotatably arranged between the inner ring and the outer ring. A cage having an opening at one axial end of a pocket for holding the ball, a shield plate for closing between the inner ring and the outer ring at both axial ends, the inner ring, the outer ring, the ball, and the And a grease disposed in a space surrounded by a shield plate, and satisfying the following configurations (a) or (a ′) and (b) and (c).

(a) 前記グリースは、前記保持器の前記開口部側の、前記空間を構成する非回転輪の面の前記シールド板近傍に塗布されている。回転輪の面には前記グリースが塗布されていないか、僅かに塗布されている。すなわち、前記グリースは、内輪回転の場合は、前記外輪の内周面に塗布され、前記内輪の外周面には塗布されていないか、僅かに塗布されている。外輪回転の場合は、前記内輪の外周面に塗布され、前記外輪の内周面には塗布されていないか、僅かに塗布されている。 (a) The grease is applied to the vicinity of the shield plate on the surface of the non-rotating wheel constituting the space on the opening side of the cage. The grease is not applied or slightly applied to the surface of the rotating wheel. That is, in the case of inner ring rotation, the grease is applied to the inner peripheral surface of the outer ring, and is not applied or slightly applied to the outer peripheral surface of the inner ring. In the case of outer ring rotation, it is applied to the outer peripheral surface of the inner ring and is not applied or slightly applied to the inner peripheral surface of the outer ring.

(a')前記グリースは、主に前記保持器の前記開口部側の、前記空間を構成する非回転輪の面の前記シールド板近傍に塗布され、回転輪の面には塗布されていない。すなわち、前記グリースは、内輪回転の場合は、前記外輪の内周面に塗布され、前記内輪の外周面には塗布されていない。外輪回転の場合は、前記内輪の外周面に塗布され、前記外輪の内周面には塗布されていない。
(b) 前記グリースの塗布体積は前記空間の１７体積％以上３０体積％以下である。
(c) 前記グリースの混和ちょう度は２５０以下である。 (a ′) The grease is applied mainly to the vicinity of the shield plate on the surface of the non-rotating wheel constituting the space on the opening side of the cage, and is not applied to the surface of the rotating wheel. That is, in the case of inner ring rotation, the grease is applied to the inner peripheral surface of the outer ring and is not applied to the outer peripheral surface of the inner ring. In the case of outer ring rotation, it is applied to the outer peripheral surface of the inner ring and not applied to the inner peripheral surface of the outer ring.
(b) The application volume of the grease is 17 volume% or more and 30 volume% or less of the space.
(c) The grease has a penetration of 250 or less.

前記構成(a) および(a')のうち、グリースが前記空間を構成する非回転輪の面に塗布され、回転輪の面には塗布されていないか、その塗布量が僅かであることで、グリースが回転輪の面にも所定量（僅かな量ではなく、例えば非回転輪と同等程度の量）塗布されている玉軸受と比較して、軸受空間が狭い場合でもグリースが潰されにくい。
前記構成(a) および(a')のうち、グリースが前記シールド板近傍に塗布されていることで、前記シールド板から離れた位置に塗布されているものと比較して、グリースが玉からより離れた位置に存在するため、玉軸受に予圧を付与して内外輪に軸方向のずれが生じた場合でも、グリースが玉に接触しにくい状態となる。よって、玉軸受に予圧を付与した状態でもグリースが潰されにくい。 Of the configurations (a) and (a ′), the grease is applied to the surface of the non-rotating wheel constituting the space, and is not applied to the surface of the rotating wheel, or the amount applied is small. Compared with ball bearings where a predetermined amount of grease is applied to the surface of the rotating wheel (not the slight amount, for example, an amount equivalent to that of the non-rotating wheel), the grease is less likely to be crushed even in a narrow bearing space. .
Of the configurations (a) and (a ′), the grease is applied in the vicinity of the shield plate. Since it exists in a distant position, even if a preload is applied to the ball bearing and an axial displacement occurs in the inner and outer rings, the grease is difficult to contact the ball. Therefore, the grease is not easily crushed even when a preload is applied to the ball bearing.

前記構成(b) を満たすことで、玉軸受の回転トルクを低く抑えながら、潤滑に必要なグリース量を確保できる。前記グリースの塗布体積が前記空間の１７体積％未満であると、グリースによる潤滑状態が不良になる恐れがある。３０体積％を超えると、玉軸受の回転時にグリースに含まれる増ちょう剤が内外輪の軌道溝に入る量が極端に多くなる。
前記構成(c) を満たすことで、混和ちょう度が２５０を超えるグリースを使用した場合と比較して、玉軸受の回転トルクを低く抑えることができる。混和ちょう度が２５０を超えるグリースは柔らかいため、玉軸受の回転時にグリースに含まれる増ちょう剤が内外輪の軌道溝に入り易くなる。 By satisfying the configuration (b), it is possible to secure the amount of grease necessary for lubrication while keeping the rotational torque of the ball bearing low. If the grease application volume is less than 17% by volume of the space, the lubrication state by the grease may be poor. When it exceeds 30% by volume, the amount of the thickener contained in the grease entering the raceway grooves of the inner and outer rings becomes extremely large when the ball bearing rotates.
By satisfying the configuration (c), the rotational torque of the ball bearing can be kept low as compared with the case where grease having a blending consistency exceeding 250 is used. Since grease having a blending degree exceeding 250 is soft, the thickener contained in the grease easily enters the raceway grooves of the inner and outer rings when the ball bearing rotates.

上述のように、この態様の玉軸受は、前記構成(a) または(a')と(b) および(c) を満たすことで、いずれかを満たさない玉軸受と比較して、小型モータの回転部を支持する用途で予圧をかけた状態であっても、グリースが潰されにくく、グリースに含まれる増ちょう剤が内外輪の軌道溝に入る量が低減されることで、回転トルクの上昇が抑制される。
この態様の玉軸受は、下記の構成(d) を満たすシールド板を有することが好ましい。
(d) 前記内輪の外周面または前記外輪の内周面と所定隙間で近接する近接部を有し、前記近接部は軸方向内側に折り曲げられた折り曲げ部を有し、前記折り曲げ部の折り曲げ角度（θ）は、板面に沿った基準線に対して９０°未満である。 As described above, the ball bearing of this aspect satisfies the configuration (a) or (a ′) and (b) and (c), so that it is smaller than a ball bearing that does not satisfy any of the above. Even when preload is applied to support rotating parts, the grease is hard to be crushed, and the amount of thickener contained in the grease enters the raceway grooves of the inner and outer rings is reduced, resulting in an increase in rotational torque. Is suppressed.
The ball bearing of this aspect preferably has a shield plate that satisfies the following configuration (d).
(d) a proximity portion that is close to the outer peripheral surface of the inner ring or the inner peripheral surface of the outer ring with a predetermined gap, the proximity portion has a bent portion that is bent inward in the axial direction, and a bending angle of the bent portion (Θ) is less than 90 ° with respect to a reference line along the plate surface.

この態様の玉軸受は、前記構成(d) と下記の構成(e) を満たすシールド板を有することがより好ましい。
(e) 前記シールド板の近接部は、前記折り曲げ部である第１の折り曲げ部の先端に、軸方向内側に折り曲げられた第２の折り曲げ部を有し、前記第２の折り曲げ部の前記基準線に対する折り曲げ角度（θ２）は、前記第１の折り曲げ部の折り曲げ角度（θ１）より大きい。 It is more preferable that the ball bearing of this aspect has a shield plate that satisfies the configuration (d) and the following configuration (e).
(e) The proximity portion of the shield plate has a second bent portion that is bent inward in the axial direction at the tip of the first bent portion that is the bent portion, and the reference of the second bent portion. The bending angle (θ2) with respect to the line is larger than the bending angle (θ1) of the first bent portion.

前記シールド板の前記第２の折り曲げ部の前記折り曲げ角度（θ２）は９０°以上であことが好ましい。
前記構成(d) を満たすシールド板によれば、前記折り曲げ部を有さないシールド板や、前記折り曲げ部を有するシールド板であっても、その折り曲げ角度θが９０°未満の範囲から外れるものと比較して、玉軸受に取り付けて玉軸受を回転した場合のグリース漏れ量が低減できる。 The bending angle (θ2) of the second bent portion of the shield plate is preferably 90 ° or more.
According to the shield plate satisfying the configuration (d), even if the shield plate does not have the bent portion or the shield plate having the bent portion, the bending angle θ is out of the range of less than 90 °. In comparison, the amount of grease leakage when the ball bearing is rotated by being attached to the ball bearing can be reduced.

この態様の玉軸受が前記構成(d) を満たすシールド板を有することにより、前記折り曲げ部を有さないシールド板を有する場合や、前記折り曲げ部を有するシールド板を有していても、その折り曲げ角度θが９０°未満の範囲から外れる場合と比較して、高速回転時のグリース漏れ量が低減できる。   When the ball bearing of this aspect has a shield plate that satisfies the configuration (d), even if it has a shield plate that does not have the bent portion, or has a shield plate that has the bent portion, the bent Compared with the case where the angle θ is out of the range of less than 90 °, the amount of grease leakage during high-speed rotation can be reduced.

この発明によれば、小型モータの回転部を支持する用途等で予圧を付与した状態でも、トルクを低減できる玉軸受の製造方法が提供できる。   According to the present invention, it is possible to provide a ball bearing manufacturing method capable of reducing torque even in a state in which a preload is applied in an application for supporting a rotating portion of a small motor.

第１実施形態の玉軸受を示す断面図である。It is sectional drawing which shows the ball bearing of 1st Embodiment. 図１、図５〜８、図１１のＡ−Ａ断面に対応する図である。It is a figure corresponding to the AA section of Drawing 1, Drawing 5-8, and Drawing 11. 第２実施形態の玉軸受を示す断面図である。It is sectional drawing which shows the ball bearing of 2nd Embodiment. 図３のＡ−Ａ断面に対応する図である。It is a figure corresponding to the AA cross section of FIG. 第３実施形態の玉軸受を示す断面図である。It is sectional drawing which shows the ball bearing of 3rd Embodiment. 第４実施形態の玉軸受を示す断面図である。It is sectional drawing which shows the ball bearing of 4th Embodiment. 第５実施形態の玉軸受を示す断面図である。It is sectional drawing which shows the ball bearing of 5th Embodiment. 第６実施形態の玉軸受を示す断面図である。It is sectional drawing which shows the ball bearing of 6th Embodiment. 図８の部分拡大図である。It is the elements on larger scale of FIG. 第７実施形態の玉軸受を示す部分拡大断面図である。It is a partial expanded sectional view which shows the ball bearing of 7th Embodiment. 第１実施形態の変形例に相当する玉軸受を示す部分拡大断面図である。It is a partial expanded sectional view which shows the ball bearing corresponded to the modification of 1st Embodiment. 従来のシールド板を使用した場合のグリースの流れを説明する図（玉軸受の部分拡大断面図）である。It is a figure (partial expanded sectional view of a ball bearing) explaining the flow of grease at the time of using the conventional shield board. 接触シールが取り付けられた玉軸受の部分拡大断面図である。It is a partial expanded sectional view of the ball bearing to which the contact seal was attached.

以下、この発明の実施形態について説明するが、この発明はこの実施形態に限定されるものではない。この実施形態では、内輪回転の玉軸受を例に挙げて説明する。
［第１実施形態］
図１は、この発明の第１実施形態に相当する玉軸受を示す断面図である。図２は図１のＡ−Ａ断面に対応する図である。この玉軸受は、内輪１と、外輪２と、玉３と、保持器４と、シールド板５０と、グリース６で構成されている。この玉軸受の寸法は、外径８ｍｍ、内径３ｍｍ、幅４ｍｍ、玉の直径１．５８８ｍｍである。 Embodiments of the present invention will be described below, but the present invention is not limited to these embodiments. In this embodiment, an inner ring rotating ball bearing will be described as an example.
[First Embodiment]
FIG. 1 is a sectional view showing a ball bearing corresponding to the first embodiment of the present invention. FIG. 2 is a view corresponding to the AA cross section of FIG. The ball bearing includes an inner ring 1, an outer ring 2, a ball 3, a cage 4, a shield plate 50, and grease 6. The dimensions of this ball bearing are an outer diameter of 8 mm, an inner diameter of 3 mm, a width of 4 mm, and a ball diameter of 1.588 mm.

内輪１の外周面１１の軸方向中央部に、玉３の軌道溝１２が形成されている。外輪２の内周面２１の軸方向中央部に、玉３の軌道溝２２が形成されている。外輪２の内周面２１の軸方向両端部に、シールド板５０の取り付け溝２３が形成されている。保持器４は合成樹脂製の冠形保持器で、軸方向片側が開口されたポケット４１を有する。
シールド板５０は金属製で、シールド板５０の内周縁部が、内輪１の外周面１１と所定隙間で近接する近接部５０１となっている。この近接部５０１は軸方向内側に折り曲げられていない。シールド板５０の外周縁部が、外輪２の内周面２１に形成された取り付け溝２３に固定される固定部５２となっている。 A raceway groove 12 for the ball 3 is formed in the central portion in the axial direction of the outer peripheral surface 11 of the inner ring 1. A raceway groove 22 for the ball 3 is formed in the central portion in the axial direction of the inner peripheral surface 21 of the outer ring 2. Mounting grooves 23 for the shield plate 50 are formed at both axial ends of the inner peripheral surface 21 of the outer ring 2. The cage 4 is a crown-shaped cage made of a synthetic resin, and has a pocket 41 opened on one side in the axial direction.
The shield plate 50 is made of metal, and the inner peripheral edge portion of the shield plate 50 is a proximity portion 501 that is close to the outer peripheral surface 11 of the inner ring 1 with a predetermined gap. The proximity portion 501 is not bent inward in the axial direction. The outer peripheral edge portion of the shield plate 50 is a fixing portion 52 that is fixed to the attachment groove 23 formed on the inner peripheral surface 21 of the outer ring 2.

図１に示すように、グリース６は、内輪１と外輪２と玉３とシールド板５０で囲まれた空間（軸受空間）のうち、保持器４の開口側であって、外輪（非回転輪）２の内周面２１のシールド板５０近傍に塗布されている。保持器４の開口部とは反対側の空間には塗布されていない。
図２に示すように、グリース６は、外輪２の内周面２１に塗布され、内輪１の外周面１１には塗布されていない。グリース６の塗布は、シールド板５０を取り付ける前に、保持器４の開口側から、例えば複数の穴の開いたノズルを使用して、外輪２の内周面２１の周方向全体に渡って、複数の球状のグリース６が隙間なく配置されるように行う。この塗布方法では、従来のグリース封入装置が利用できるため、新たな設備が不要であり、生産コストの上昇を招かない。 As shown in FIG. 1, the grease 6 is located on the opening side of the cage 4 in the space (bearing space) surrounded by the inner ring 1, the outer ring 2, the balls 3 and the shield plate 50, and the outer ring (non-rotating ring). ) It is applied in the vicinity of the shield plate 50 on the inner peripheral surface 21 of 2. It is not applied to the space opposite to the opening of the cage 4.
As shown in FIG. 2, the grease 6 is applied to the inner peripheral surface 21 of the outer ring 2 and is not applied to the outer peripheral surface 11 of the inner ring 1. Before applying the shield plate 50, the grease 6 is applied from the opening side of the cage 4 over the entire circumferential direction of the inner peripheral surface 21 of the outer ring 2 using, for example, a nozzle having a plurality of holes. The plurality of spherical greases 6 are arranged without gaps. In this application method, since a conventional grease filling device can be used, new equipment is not required, and production costs are not increased.

グリース６の混和ちょう度は２３２であり、グリース６の塗布体積は軸受空間の２５〜２９体積％である。
この実施形態の玉軸受は、軸受空間が狭いミニアチュア玉軸受であるが、グリース６が外輪（非回転輪）２の内周面２１に塗布され、内輪（回転輪）１の外周面１１には塗布されていないため、グリースが潰されにくい。また、グリース６がシールド板５０の近傍に塗布されていることで、予圧を付与して内外輪に軸方向のずれが生じた場合でも、グリース６が玉３に接触しにくい状態となる。よって、玉軸受に予圧を付与した状態でもグリース６が潰されにくい。
したがって、この実施形態の玉軸受によれば、予圧を付与した状態でも、グリース６に含まれる増ちょう剤が内外輪の軌道溝１２，２２に入る量が低減されるため、回転トルクの上昇が抑制される。 The blending degree of the grease 6 is 232, and the application volume of the grease 6 is 25 to 29% by volume of the bearing space.
The ball bearing of this embodiment is a miniature ball bearing with a narrow bearing space, but grease 6 is applied to the inner peripheral surface 21 of the outer ring (non-rotating ring) 2, and the outer peripheral surface 11 of the inner ring (rotating ring) 1 is applied to the outer ring 11. Since it is not applied, grease is not easily crushed. Further, since the grease 6 is applied in the vicinity of the shield plate 50, even when a preload is applied and an axial displacement occurs in the inner and outer rings, the grease 6 is difficult to contact the ball 3. Therefore, the grease 6 is not easily crushed even when a preload is applied to the ball bearing.
Therefore, according to the ball bearing of this embodiment, even when a preload is applied, the amount of the thickener contained in the grease 6 enters the raceway grooves 12 and 22 of the inner and outer rings is reduced, so that the rotational torque is increased. It is suppressed.

［第２実施形態］
図３は、この発明の第２実施形態の玉軸受を示す断面図である。図４は図３のＡ−Ａ断面に対応する図である。この玉軸受は、以下の点で第１実施形態の玉軸受と異なるが、それ以外の点は第１実施形態の玉軸受と同じである。
第１実施形態では、外輪２の内周面２１の周方向全体に渡って、複数の球状のグリース６が隙間なく配置されているが、第２実施形態では、外輪２の内周面２１に円環状のグリース６が配置されている。そして、円環状のグリース６の外周面が外輪２の内周面２１に接触している。グリース６の塗布体積は軸受空間の２５〜２９体積％である。 [Second Embodiment]
FIG. 3 is a cross-sectional view showing a ball bearing according to a second embodiment of the present invention. FIG. 4 is a view corresponding to the AA cross section of FIG. This ball bearing is different from the ball bearing of the first embodiment in the following points, but the other points are the same as the ball bearing of the first embodiment.
In the first embodiment, the plurality of spherical greases 6 are arranged without gaps over the entire circumferential direction of the inner circumferential surface 21 of the outer ring 2. However, in the second embodiment, the inner circumferential surface 21 of the outer ring 2 is disposed on the inner circumferential surface 21. An annular grease 6 is arranged. The outer peripheral surface of the annular grease 6 is in contact with the inner peripheral surface 21 of the outer ring 2. The application volume of the grease 6 is 25 to 29% by volume of the bearing space.

グリース６の塗布は、シールド板５０を取り付ける前に、保持器４の開口側から、例えば１個の穴の開いたノズルを使用し、ノズルまたは玉軸受の外輪２を回転させながら外輪２の内周面２１の周方向全体に渡って、ノズルからグリースを吐出させることで行う。これにより、グリース６を、外輪２の内周面２１の周方向全体に渡って切れ目なく円環状に塗布する。   Before the shield plate 50 is attached, the grease 6 is applied by using, for example, a nozzle having one hole from the opening side of the cage 4 and rotating the outer ring 2 of the nozzle or ball bearing while rotating the inner ring 2. It is performed by discharging grease from the nozzle over the entire circumferential direction of the peripheral surface 21. As a result, the grease 6 is applied in an annular shape without a break across the entire circumferential direction of the inner peripheral surface 21 of the outer ring 2.

したがって、この実施形態の玉軸受によれば、第１実施形態の玉軸受と同様に、予圧を付与した状態でも、グリース６に含まれる増ちょう剤が内外輪の軌道溝１２，２２に入る量が低減されるため、回転トルクの上昇が抑制される。また、第１実施形態の玉軸受と比較してグリース６と外輪２との接触面積が大きいため、グリース６の封入形態が安定しやすいという効果を有する。   Therefore, according to the ball bearing of this embodiment, similarly to the ball bearing of the first embodiment, the amount of the thickener contained in the grease 6 enters the raceway grooves 12 and 22 of the inner and outer rings even in a state where a preload is applied. Therefore, an increase in rotational torque is suppressed. Further, since the contact area between the grease 6 and the outer ring 2 is larger than that of the ball bearing of the first embodiment, there is an effect that the sealing form of the grease 6 is easily stabilized.

［第３実施形態］
図５は、この発明の第３実施形態の玉軸受を示す断面図である。図５のＡ−Ａ断面に対応する図は図２と同じである。この玉軸受は、以下の点で第１実施形態の玉軸受と異なるが、それ以外の点は第１実施形態の玉軸受と同じである。
図５に示すように、この実施形態の玉軸受には、第１実施形態と同様に配置されたグリース６に加えて、保持器４の開口部とは反対側の空間にも、シールド板５０近傍にグリース６１が塗布されている。グリース６とグリース６１の合計塗布体積は軸受空間の１７〜３０体積％である。グリース６１の塗布体積はグリース６よりも多い。 [Third Embodiment]
FIG. 5 is a cross-sectional view showing a ball bearing according to a third embodiment of the present invention. The figure corresponding to the AA cross section of FIG. 5 is the same as FIG. This ball bearing is different from the ball bearing of the first embodiment in the following points, but the other points are the same as the ball bearing of the first embodiment.
As shown in FIG. 5, the ball bearing of this embodiment includes a shield plate 50 in a space opposite to the opening of the cage 4 in addition to the grease 6 disposed in the same manner as in the first embodiment. Grease 61 is applied in the vicinity. The total application volume of grease 6 and grease 61 is 17 to 30% by volume of the bearing space. The application volume of the grease 61 is larger than that of the grease 6.

グリース６１の塗布は、シールド板５０を取り付ける前に、保持器４の開口部とは反対側から、例えば複数の穴の開いたノズルを使用して、外輪２の内周面２１の周方向全体に渡って、複数の球状のグリース６１が隙間なく配置されるように行う。
したがって、この実施形態の玉軸受によれば、第１実施形態の玉軸受と同様に、予圧を付与した状態でも、グリース６に含まれる増ちょう剤が内外輪の軌道溝１２，２２に入る量が低減されるため、回転トルクの上昇が抑制される。また、保持器４の両側（開口部側とその反対側の両方の空間）に分けてグリース６１を塗布することで、グリース漏れの低減と更なる低トルク化が実現できるという効果を有する。 The grease 61 is applied to the entire circumferential direction of the inner peripheral surface 21 of the outer ring 2 from the side opposite to the opening of the retainer 4 by using, for example, a nozzle having a plurality of holes before attaching the shield plate 50. Then, the plurality of spherical greases 61 are arranged without gaps.
Therefore, according to the ball bearing of this embodiment, similarly to the ball bearing of the first embodiment, the amount of the thickener contained in the grease 6 enters the raceway grooves 12 and 22 of the inner and outer rings even in a state where a preload is applied. Therefore, an increase in rotational torque is suppressed. Further, by applying the grease 61 separately on both sides of the cage 4 (both spaces on the opening side and the opposite side), there is an effect that reduction of grease leakage and further reduction in torque can be realized.

［第４実施形態］
図６は、この発明の第４実施形態の玉軸受を示す断面図である。図６のＡ−Ａ断面に対応する図は図２と同じである。この玉軸受は、以下の点で第１実施形態の玉軸受と異なるが、それ以外の点は第１実施形態の玉軸受と同じである。
図６に示すように、この実施形態の玉軸受には、第１実施形態と同様に配置されたグリース６に加えて、外輪２の軌道溝２２の角部に少量のグリース６２が周方向全体に渡って塗布されている。グリース６とグリース６２の合計塗布体積は軸受空間の１７〜３０体積％である。 [Fourth Embodiment]
FIG. 6 is a cross-sectional view showing a ball bearing according to a fourth embodiment of the present invention. The figure corresponding to the AA cross section of FIG. 6 is the same as FIG. This ball bearing is different from the ball bearing of the first embodiment in the following points, but the other points are the same as the ball bearing of the first embodiment.
As shown in FIG. 6, in the ball bearing of this embodiment, in addition to the grease 6 arranged in the same manner as in the first embodiment, a small amount of grease 62 is provided at the corner of the raceway groove 22 of the outer ring 2 in the entire circumferential direction. Has been applied over. The total application volume of grease 6 and grease 62 is 17 to 30% by volume of the bearing space.

グリース６２の塗布は、グリース６を塗布する前に、ノズルまたは玉軸受の外輪２を回転させながら外輪２の軌道溝２２の角部の周方向全体に渡って、ノズルからグリースを吐出させることで行う。
したがって、この実施形態の玉軸受によれば、第１実施形態の玉軸受と同様に、予圧を付与した状態でも、グリース６に含まれる増ちょう剤が内外輪の軌道溝１２，２２に入る量が低減されるため、回転トルクの上昇が抑制される。また、外輪２の軌道溝２２の角部に少量のグリース６２を塗布したことにより、第１実施形態の玉軸受よりも潤滑性能が高くなる。 The grease 62 is applied by discharging the grease from the nozzle over the entire circumferential direction of the corner portion of the raceway groove 22 of the outer ring 2 while rotating the outer ring 2 of the nozzle or ball bearing before applying the grease 6. Do.
Therefore, according to the ball bearing of this embodiment, similarly to the ball bearing of the first embodiment, the amount of the thickener contained in the grease 6 enters the raceway grooves 12 and 22 of the inner and outer rings even in a state where a preload is applied. Therefore, an increase in rotational torque is suppressed. Further, since a small amount of grease 62 is applied to the corner portion of the raceway groove 22 of the outer ring 2, the lubricating performance becomes higher than that of the ball bearing of the first embodiment.

［第５実施形態］
図７は、この発明の第５実施形態の玉軸受を示す断面図である。図７のＡ−Ａ断面に対応する図は図２と同じである。この玉軸受は、以下の点で第１実施形態の玉軸受と異なるが、それ以外の点は第１実施形態の玉軸受と同じである。
図７に示すように、この実施形態の玉軸受には、第１実施形態と同様に配置されたグリース６に加えて、保持器４の開口部とは反対側の軸方向端面４２に、少量のグリース６３が塗布されている。グリース６とグリース６３の合計塗布体積は軸受空間の１７〜３０体積％である。 [Fifth Embodiment]
FIG. 7 is a cross-sectional view showing a ball bearing according to a fifth embodiment of the present invention. The figure corresponding to the AA cross section of FIG. 7 is the same as FIG. This ball bearing is different from the ball bearing of the first embodiment in the following points, but the other points are the same as the ball bearing of the first embodiment.
As shown in FIG. 7, the ball bearing of this embodiment has a small amount on the axial end surface 42 opposite to the opening of the cage 4 in addition to the grease 6 arranged in the same manner as in the first embodiment. The grease 63 is applied. The total application volume of grease 6 and grease 63 is 17-30% by volume of the bearing space.

グリース６３の塗布は、シールド板５０を取り付ける前に、保持器４の開口部とは反対側から、ノズルまたは玉軸受の保持器４を回転させながら、保持器４の軸方向端面４２の周方向全体に渡ってノズルからグリースを吐出させることで行う。
したがって、この実施形態の玉軸受によれば、第１実施形態の玉軸受と同様に、予圧を付与した状態でも、グリース６に含まれる増ちょう剤が内外輪の軌道溝１２，２２に入る量が低減されるため、回転トルクの上昇が抑制される。また、保持器４の開口部とは反対側の軸方向端面４２にもグリース６３を塗布したことにより、基油が少しずつしみ出し、長時間に渡って継続的に基油を供給できるという効果を有する。 The grease 63 is applied in the circumferential direction of the axial end surface 42 of the cage 4 while rotating the cage 4 of the nozzle or ball bearing from the side opposite to the opening of the cage 4 before attaching the shield plate 50. This is done by discharging grease from the nozzle throughout.
Therefore, according to the ball bearing of this embodiment, similarly to the ball bearing of the first embodiment, the amount of the thickener contained in the grease 6 enters the raceway grooves 12 and 22 of the inner and outer rings even in a state where a preload is applied. Therefore, an increase in rotational torque is suppressed. Further, the grease 63 is also applied to the axial end surface 42 opposite to the opening of the cage 4, so that the base oil oozes out little by little and the base oil can be continuously supplied over a long period of time. Have

［第６実施形態］
図８は、この発明の第６実施形態に相当する玉軸受を示す断面図である。図８のＡ−Ａ断面に対応する図は図２と同じである。図９は図８の部分拡大図である。この玉軸受は、内輪１と、外輪２と、玉３と、保持器４と、シールド板５と、グリース６で構成されている。この玉軸受の寸法は、外径８ｍｍ、内径３ｍｍ、幅４ｍｍ、玉の直径１．５８８ｍｍである。 [Sixth Embodiment]
FIG. 8 is a sectional view showing a ball bearing corresponding to the sixth embodiment of the present invention. The figure corresponding to the AA cross section of FIG. 8 is the same as FIG. FIG. 9 is a partially enlarged view of FIG. This ball bearing includes an inner ring 1, an outer ring 2, a ball 3, a cage 4, a shield plate 5, and grease 6. The dimensions of this ball bearing are an outer diameter of 8 mm, an inner diameter of 3 mm, a width of 4 mm, and a ball diameter of 1.588 mm.

内輪１の外周面１１の軸方向中央部に、玉３の軌道溝１２が形成されている。外輪２の内周面２１の軸方向中央部に、玉３の軌道溝２２が形成されている。外輪２の内周面２１の軸方向両端部に、シールド板５の取り付け溝２３が形成されている。保持器４は合成樹脂製の冠形保持器で、軸方向片側が開口されたポケット４１を有する。
シールド板５は金属製で、シールド板５の内周縁部が、内輪１の外周面１１と所定隙間で近接する近接部５１となっている。シールド板５の外周縁部が、外輪２の内周面２１に形成された取り付け溝２３に固定される固定部５２となっている。 A raceway groove 12 for the ball 3 is formed in the central portion in the axial direction of the outer peripheral surface 11 of the inner ring 1. A raceway groove 22 for the ball 3 is formed in the central portion in the axial direction of the inner peripheral surface 21 of the outer ring 2. Mounting grooves 23 for the shield plate 5 are formed at both axial ends of the inner peripheral surface 21 of the outer ring 2. The cage 4 is a crown-shaped cage made of a synthetic resin, and has a pocket 41 opened on one side in the axial direction.
The shield plate 5 is made of metal, and the inner peripheral edge portion of the shield plate 5 is a proximity portion 51 that is close to the outer peripheral surface 11 of the inner ring 1 with a predetermined gap. The outer peripheral edge portion of the shield plate 5 serves as a fixing portion 52 that is fixed to the mounting groove 23 formed on the inner peripheral surface 21 of the outer ring 2.

図９に示すように、シールド板５の近接部５１は、軸方向に沿った板面部５３から軸方向内側に折り曲げられた折り曲げ部５１ａと、その先端からさらに軸方向内側に折り曲げられた第２折り曲げ部５１ｂを有する。折り曲げ部５１ａの折り曲げ角度θ１は、板面（板面部５３の面）に沿った基準線Ｌに対して４５°である。第２折り曲げ部５１ｂの折り曲げ角度θ２は、基準線Ｌに対して９０°である。   As shown in FIG. 9, the proximity portion 51 of the shield plate 5 includes a bent portion 51a that is bent inward in the axial direction from a plate surface portion 53 along the axial direction, and a second portion that is further bent inward in the axial direction from the tip. It has a bent part 51b. The bending angle θ1 of the bent portion 51a is 45 ° with respect to the reference line L along the plate surface (the surface of the plate surface portion 53). The bending angle θ2 of the second bent portion 51b is 90 ° with respect to the reference line L.

図８に示すように、グリース６は、内輪１と外輪２と玉３とシールド板５で囲まれた空間（軸受空間）のうち、保持器４の開口側であって、外輪（非回転輪）２の内周面２１のシールド板５近傍に塗布されている。保持器４の開口部とは反対側の空間には塗布されていない。
図２に示すように、グリース６は、外輪２の内周面２１に塗布され、内輪１の外周面１１には塗布されていない。グリース６の塗布は、シールド板５を取り付ける前に、保持器４の開口側から、例えば複数の穴の開いたノズルを使用して、外輪２の内周面２１の周方向全体に渡って、複数の球状のグリース６が隙間なく配置されるように行う。 As shown in FIG. 8, the grease 6 is on the opening side of the cage 4 in the space (bearing space) surrounded by the inner ring 1, the outer ring 2, the balls 3, and the shield plate 5, and the outer ring (non-rotating ring). ) 2 is applied in the vicinity of the shield plate 5 on the inner peripheral surface 21. It is not applied to the space opposite to the opening of the cage 4.
As shown in FIG. 2, the grease 6 is applied to the inner peripheral surface 21 of the outer ring 2 and is not applied to the outer peripheral surface 11 of the inner ring 1. The grease 6 is applied to the entire circumferential direction of the inner peripheral surface 21 of the outer ring 2 from the opening side of the retainer 4 by using, for example, a nozzle having a plurality of holes, before attaching the shield plate 5. The plurality of spherical greases 6 are arranged without gaps.

グリース６の混和ちょう度は２３２であり、グリース６の塗布体積は軸受空間の１７〜３０体積％である。
この実施形態の玉軸受は、軸受空間が狭いミニアチュア玉軸受であるが、グリース６が外輪（非回転輪）２の内周面２１に塗布され、内輪（回転輪）１の外周面１１には塗布されていないため、グリースが潰されにくい。また、グリース６がシールド板５の近傍に塗布されていることで、予圧を付与して内外輪に軸方向のずれが生じた場合でも、グリース６が玉３に接触しにくい状態となる。よって、玉軸受に予圧を付与した状態でもグリース６が潰されにくい。 The blending degree of the grease 6 is 232, and the application volume of the grease 6 is 17 to 30% by volume of the bearing space.
The ball bearing of this embodiment is a miniature ball bearing with a narrow bearing space, but grease 6 is applied to the inner peripheral surface 21 of the outer ring (non-rotating ring) 2, and the outer peripheral surface 11 of the inner ring (rotating ring) 1 is applied to the outer ring 11. Since it is not applied, grease is not easily crushed. Further, since the grease 6 is applied in the vicinity of the shield plate 5, even when a preload is applied and an axial shift occurs in the inner and outer rings, the grease 6 is difficult to contact the ball 3. Therefore, the grease 6 is not easily crushed even when a preload is applied to the ball bearing.

したがって、この実施形態の玉軸受によれば、予圧を付与した状態でも、グリース６に含まれる増ちょう剤が内外輪の軌道溝１２，２２に入る量が低減されるため、回転トルクの上昇が抑制される。
また、使用するシールド板５が、折り曲げ角度θ１が４５°である折り曲げ部５１ａと、折り曲げ角度θ２が９０°である第２折り曲げ部５１ｂとからなる近接部５１を有するため、玉軸受の回転時にグリース６が図９の矢印のように移動する。 Therefore, according to the ball bearing of this embodiment, even when a preload is applied, the amount of the thickener contained in the grease 6 enters the raceway grooves 12 and 22 of the inner and outer rings is reduced, so that the rotational torque is increased. It is suppressed.
Further, since the shield plate 5 to be used has a proximity portion 51 including a bent portion 51a having a bending angle θ1 of 45 ° and a second bent portion 51b having a bending angle θ2 of 90 °, the ball bearing is rotated. The grease 6 moves as shown by the arrow in FIG.

ここで、図１２に示すように、グリースの配置は同じでも、従来のシールド板５０を使用した玉軸受（つまり、第１実施形態の玉軸受）では、近接部５０１と内輪１の外周面１１との隙間からグリース６が漏れだし易くなる。
すなわち、この実施形態の玉軸受によれば、第１実施形態の玉軸受と比較して、シールド板５の近接部５１と内輪１の外周面１１との隙間から外部に漏れだすグリース６の量が抑制される。 Here, as shown in FIG. 12, in the ball bearing using the conventional shield plate 50 (that is, the ball bearing of the first embodiment) even if the grease is arranged in the same manner, the outer peripheral surface 11 of the proximity portion 501 and the inner ring 1 is used. Grease 6 is likely to leak from the gap.
That is, according to the ball bearing of this embodiment, compared with the ball bearing of the first embodiment, the amount of grease 6 that leaks to the outside from the gap between the proximity portion 51 of the shield plate 5 and the outer peripheral surface 11 of the inner ring 1. Is suppressed.

また、高速回転条件で使用される玉軸受に、図１３に示すように、芯金７１とゴム成形体７２とからなる接触シール７０を取り付けると、グリース漏れを防止できるが、接触シール７０のリップ部７２ａと内輪１の外周面１１との摩擦が大きくなるため、軸受トルクが過大になる恐れがある。
したがって、この実施形態の玉軸受は、回転トルクの上昇とグリース漏れの両方が抑制されたものとなる。 Further, as shown in FIG. 13, when a contact seal 70 made of a core metal 71 and a rubber molded body 72 is attached to a ball bearing used under high-speed rotation conditions, grease leakage can be prevented, but the lip of the contact seal 70 Since the friction between the portion 72a and the outer peripheral surface 11 of the inner ring 1 is increased, the bearing torque may be excessive.
Therefore, the ball bearing of this embodiment is one in which both an increase in rotational torque and grease leakage are suppressed.

［第７実施形態］
図１０は、第７実施形態の玉軸受を示す部分拡大断面図である。この玉軸受は、以下の点で第６実施形態の玉軸受と異なるが、それ以外の点は第６実施形態の玉軸受と同じである。
図１０に示すように、この実施形態の玉軸受において、シールド板５Ａの近接部５１は、軸方向に沿った板面部５３から軸方向内側に折り曲げられた折り曲げ部５１ａのみからなる。折り曲げ部５１ａの折り曲げ角度θは、板面（板面部５３の面）に沿った基準線Ｌに対して４５°である。グリース６の塗布体積は軸受空間の１７〜３０体積％である。 [Seventh Embodiment]
FIG. 10 is a partially enlarged sectional view showing the ball bearing of the seventh embodiment. This ball bearing is different from the ball bearing of the sixth embodiment in the following points, but the other points are the same as the ball bearing of the sixth embodiment.
As shown in FIG. 10, in the ball bearing of this embodiment, the proximity portion 51 of the shield plate 5A is composed of only a bent portion 51a bent inward in the axial direction from the plate surface portion 53 along the axial direction. The bending angle θ of the bent portion 51a is 45 ° with respect to the reference line L along the plate surface (the surface of the plate surface portion 53). The application volume of the grease 6 is 17 to 30% by volume of the bearing space.

この実施形態の玉軸受によれば、第６実施形態の玉軸受と同様に、予圧を付与した状態でも、グリース６に含まれる増ちょう剤が内外輪の軌道溝１２，２２に入る量が低減されるため、回転トルクの上昇が抑制される。
また、使用するシールド板５Ａが、折り曲げ角度θが４５°である折り曲げ部５１ａからなる近接部５１を有するため、玉軸受の回転時にグリース６が図１０の矢印のように移動する。よって、図１２に示す従来のシールド板５０を使用した場合と比較して、シールド板５Ａの近接部５１と内輪１の外周面１１との隙間から外部に漏れだすグリース６の量が抑制される。 According to the ball bearing of this embodiment, similarly to the ball bearing of the sixth embodiment, the amount of the thickener contained in the grease 6 enters the raceway grooves 12 and 22 of the inner and outer rings is reduced even when a preload is applied. Therefore, an increase in rotational torque is suppressed.
Further, since the shield plate 5A to be used has the proximity portion 51 including the bent portion 51a having a bending angle θ of 45 °, the grease 6 moves as indicated by an arrow in FIG. Therefore, as compared with the case where the conventional shield plate 50 shown in FIG. 12 is used, the amount of grease 6 leaking outside through the gap between the proximity portion 51 of the shield plate 5A and the outer peripheral surface 11 of the inner ring 1 is suppressed. .

したがって、この実施形態の玉軸受は、回転トルクの上昇とグリース漏れの両方が抑制されたものとなる。
さらに、この実施形態のシールド板５Ａは、第６実施形態のシールド板５と比較して、第２折り曲げ部５１ｂがない分、形状が単純になるため量産性の点で有利である。
なお、上記各実施形態では、グリース６が外輪（非回転輪）２の内周面２１に塗布され、内輪（回転輪）１の外周面１１には塗布されていない玉軸受について説明しているが、内輪（回転輪）１の外周面１１にも僅かな量のグリース６が塗布されていてもよい。 Therefore, the ball bearing of this embodiment is one in which both an increase in rotational torque and grease leakage are suppressed.
Further, the shield plate 5A of this embodiment is advantageous in terms of mass productivity because the shape is simplified as compared with the shield plate 5 of the sixth embodiment because the second bent portion 51b is not provided.
In each of the above embodiments, the ball bearing is described in which the grease 6 is applied to the inner peripheral surface 21 of the outer ring (non-rotating ring) 2 and not applied to the outer peripheral surface 11 of the inner ring (rotating ring) 1. However, a slight amount of grease 6 may be applied to the outer peripheral surface 11 of the inner ring (rotating ring) 1.

すなわち、グリースの大部分が非回転輪の前記空間を構成する面（主に前記保持器の前記開口部側のシールド板近傍）に塗布され、グリースの全塗布量のうちの僅かな量のグリースが回転輪の面に塗布されている玉軸受も、この発明の権利範囲に含まれる。
例えば、図１１に示す玉軸受は、第１実施形態の玉軸受の内輪（回転輪）１の外周面１１に僅かな量のグリース６Ａが塗布されている例であり、この例もこの発明の権利範囲に含まれる。また、第２〜第７実施形態の玉軸受において内輪（回転輪）１の外周面１１に僅かな量のグリースが塗布されている例も、この発明の権利範囲に含まれる。 That is, most of the grease is applied to the surface of the non-rotating wheel that constitutes the space (mainly near the shield plate on the opening side of the cage), and only a small amount of the grease is applied. A ball bearing in which is applied to the surface of the rotating wheel is also included in the scope of the present invention.
For example, the ball bearing shown in FIG. 11 is an example in which a small amount of grease 6A is applied to the outer peripheral surface 11 of the inner ring (rotating ring) 1 of the ball bearing of the first embodiment. Included in the scope of rights. In addition, an example in which a slight amount of grease is applied to the outer peripheral surface 11 of the inner ring (rotating ring) 1 in the ball bearings of the second to seventh embodiments is also included in the scope of the right of the present invention.

１ 内輪（回転輪）
１１ 内輪の外周面
１２ 軌道溝
２ 外輪（非回転輪）
２１ 外輪の内周面
２２ 軌道溝
２３ シールド板の取り付け溝
３ 玉
４ 保持器
４１ ポケット
４２ 保持器の開口部とは反対側の軸方向端面
５ シールド板
５Ａ シールド板
５１ 近接部
５１ａ 折り曲げ部（第１の折り曲げ部）
５１ｂ 第２の折り曲げ部
５２ 固定部
５３ 板面部
５０ シールド板
５０１ 近接部
６ グリース
６Ａ グリース
６１ グリース
６２ グリース
６３ グリース
７０ 接触シール
７１ 芯金
７２ ゴム成形体
７２ａ リップ部 1 Inner ring (rotating wheel)
11 Outer surface of inner ring 12 Track groove 2 Outer ring (non-rotating ring)
21 Inner circumferential surface of outer ring 22 Track groove 23 Mounting groove of shield plate 3 Ball 4 Cage 41 Pocket 42 Axial end surface opposite to cage opening 5 Shield plate 5A Shield plate 51 Proximity portion 51a Bending portion 1 bent part)
51b Second bent portion 52 Fixed portion 53 Plate surface portion 50 Shield plate 501 Proximity portion 6 Grease 6A Grease 61 Grease 62 Grease 63 Grease 70 Contact seal 71 Core metal 72 Rubber molded body 72a Lip portion

Claims (2)

いずれか一方が回転輪となり他方が非回転輪となる内輪および外輪と、
前記内輪と前記外輪の間に転動自在に配置された複数の玉と、
前記玉を保持するポケットに開口部を有する保持器と、
前記内輪と前記外輪との間を軸方向両端で塞ぐシールド板と、
前記内輪、前記外輪、前記玉、および前記シールド板で囲まれた空間に配置されたグリースと、
を有する玉軸受の製造方法であって、
前記グリースを、前記保持器の、前記空間を構成する非回転輪の面の前記シールド板近傍に、複数の穴の開いたノズルを使用して塗布することを特徴とする玉軸受の製造方法。 An inner ring and an outer ring, one of which is a rotating wheel and the other is a non-rotating wheel;
A plurality of balls arranged to roll freely between the inner ring and the outer ring;
A cage having an opening in a pocket for holding the ball;
A shield plate that closes between the inner ring and the outer ring at both axial ends;
Grease disposed in a space surrounded by the inner ring, the outer ring, the ball, and the shield plate;
A ball bearing manufacturing method comprising:
A method of manufacturing a ball bearing, wherein the grease is applied to the vicinity of the shield plate on the surface of the non-rotating ring constituting the space of the cage using a nozzle having a plurality of holes. 前記グリースの塗布体積は前記空間の１７体積％以上３０体積％以下であり、
前記グリースの混和ちょう度は２５０以下である請求項１記載の玉軸受の製造方法。 The application volume of the grease is 17 volume% or more and 30 volume% or less of the space,
The ball bearing manufacturing method according to claim 1, wherein the grease has a penetration degree of 250 or less.
JP2017230850A 2012-08-27 2017-11-30 Method for manufacturing ball bearing Pending JP2018035944A (en)

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