JP2007085520A - Ball bearing - Google Patents

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Publication number
JP2007085520A
JP2007085520A JP2005278326A JP2005278326A JP2007085520A JP 2007085520 A JP2007085520 A JP 2007085520A JP 2005278326 A JP2005278326 A JP 2005278326A JP 2005278326 A JP2005278326 A JP 2005278326A JP 2007085520 A JP2007085520 A JP 2007085520A
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Prior art keywords
bearing
ball
seal
thickness
diameter
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Japanese (ja)
Inventor
Akitoshi Maeda
明年 前田
Toru Shoda
亨 正田
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NSK Ltd
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NSK Ltd
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Priority to JP2005278326A priority Critical patent/JP2007085520A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—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
    • F16C33/7893—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a cage or integral therewith
    • 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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a ball bearing, improving the load capacity of a thin bearing, and further giving a sealing function. <P>SOLUTION: In this thin ball bearing, a bearing thickness/bearing outside diameter is set to 0.15 or less to increase the load capacity. The bearing thickness is set to (bearing outside diameter-bearing inside diameter)/2, the ball diameter/bearing thickness is set to 0.5 or more, the bearing thickness/bearing width is set to exceed 0.5, and (ball diameter × number of balls)/(3.14×PCD) is set to 0.5 or more. Further, the bottom of a cage 4 is formed at a folded part 6. Thus, the case bottom of a press iron cage is formed as a folded structure to increase the strength, whereby although it is thin, a small seal member 5 not taking space can be used. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、薄肉軸受に於ける耐荷重性能を向上した玉軸受に関する。   The present invention relates to a ball bearing with improved load bearing performance in a thin bearing.

断面幅／軸受外径が０．１５以下の薄肉の玉軸受では、玉径／軸受厚さの比率を０．５未満と小さな玉を用い、保持器も小さくすることで、シールと保持器の干渉を抑える設計がなされていた。この場合の軸受厚さ／軸受幅の比率は、０．５以下が一般に用いられており、玉径が小さいため、負荷容量が小さい問題点がある。   For thin ball bearings with a cross-sectional width / bearing outer diameter of 0.15 or less, the ratio of the ball diameter / bearing thickness is less than 0.5 and small balls are used. It was designed to reduce interference. In this case, the ratio of the bearing thickness / bearing width is generally 0.5 or less, and since the ball diameter is small, there is a problem that the load capacity is small.

また、軸受厚さ／軸受幅の比率が０．５を超えるサイズでは、保持器装着が困難でオープンタイプの軸受となり、グリースの密封性、外部異物の防塵性が問題となる。   Further, when the ratio of the bearing thickness / bearing width exceeds 0.5, it is difficult to mount the cage and the bearing becomes an open type bearing, which causes a problem of grease sealing and dust-proofing of external foreign matter.

図５（ａ）（ｂ）は、それぞれ、従来例に係る玉軸受の部分断面図である。図５（ａ）の従来例では、両シールタイプであり、外輪１と内輪２との間に、玉３が転動自在に介装してあり、保持器４及びシール部材５，５を備えている。しかし、薄い保持器４であり、強度確保のため、幅方向が長くなり、その結果、玉３の径は、小さく、軸受幅が広くなる。図５（ｂ）の従来例では、玉３の径を大きく、軸受幅を狭くした場合、シール部材５の装着が困難で、オープンタイプの軸受となる。   5A and 5B are partial cross-sectional views of ball bearings according to conventional examples. In the conventional example of FIG. 5 (a), both seal types are used, and a ball 3 is interposed between an outer ring 1 and an inner ring 2 so as to be freely rotatable, and includes a cage 4 and seal members 5 and 5. ing. However, it is a thin cage 4 and the width direction is long in order to secure the strength. As a result, the diameter of the ball 3 is small and the bearing width is wide. In the conventional example of FIG. 5B, when the diameter of the ball 3 is increased and the bearing width is decreased, it is difficult to mount the seal member 5 and an open type bearing is obtained.

しかしながら、薄肉の玉軸受は、コピー機、プリンター等の定着部の支持用途も多く、そのような用途では、比較的大きなラジアル荷重が負荷される。玉径が小さいため、玉軸受の定格容量も少なく、短期で玉軸受が焼き付いて、寿命にいたる問題があった。また、グリース漏れを嫌い、外部環境もクリーンではないため、軸受シール機能は不可欠である。   However, thin ball bearings are often used for supporting fixing units of copying machines, printers, etc., and in such applications, a relatively large radial load is applied. Since the ball diameter is small, the rated capacity of the ball bearing is small, and the ball bearing is burned out in a short period of time, leading to a problem in life. In addition, bearing seal function is indispensable because it dislikes grease leakage and the external environment is not clean.

本発明は、上述したような事情に鑑みてなされたものであって、薄肉軸受の負荷容量を向上させ、更に、シール機能も付与させることができる、玉軸受を提供することを目的とする。   The present invention has been made in view of the above-described circumstances, and an object of the present invention is to provide a ball bearing capable of improving the load capacity of a thin-walled bearing and further providing a sealing function.

上記の目的を達成するため、本発明に係る玉軸受は、軸受厚さ／軸受外径を、０．１５以下とした薄肉の玉軸受に於いて、
軸受厚さは、（軸受外径−軸受内径）／２であり、
玉径／軸受厚さを、０．５以上とし、
軸受厚さ／軸受幅を、０．５を超えるものとし、かつ
（玉径×玉数）／（３．１４×ＰＣＤ）を、０．５以上として設定したことを特徴とする。 In order to achieve the above object, a ball bearing according to the present invention is a thin ball bearing in which the bearing thickness / outer diameter is 0.15 or less.
The bearing thickness is (bearing outer diameter−bearing inner diameter) / 2.
The ball diameter / bearing thickness is 0.5 or more,
The bearing thickness / bearing width exceeds 0.5, and (ball diameter × number of balls) / (3.14 × PCD) is set to 0.5 or more.

好適には、反シール側に、シール機能を兼用した保持器を設定し、軸受幅を縮小してある。   Preferably, a cage having a sealing function is set on the side opposite to the seal, and the bearing width is reduced.

また、好適には、止め輪を、シール兼用として設定してある。   Preferably, the retaining ring is set as a seal.

さらに、好適には、内輪に装着する断熱ブッシュを、シール兼用として設定してある。   Further, preferably, a heat insulating bush to be mounted on the inner ring is set as a seal.

本発明によれば、薄肉軸受の負荷容量を向上させることができ、更に、シール機能も付与させることができる。   According to the present invention, it is possible to improve the load capacity of the thin bearing, and to provide a sealing function.

以下、本発明の実施の形態に係る玉軸受を図面を参照しつつ説明する。   Hereinafter, ball bearings according to embodiments of the present invention will be described with reference to the drawings.

（第１実施の形態）
図１は、本発明の第１実施の形態に係る玉軸受の部分断面図である。玉軸受は、両シールタイプであり、外輪１と内輪２との間に、玉３が転動自在に介装してあり、保持器４及びシール部材５，５を備えている。 (First embodiment)
FIG. 1 is a partial cross-sectional view of a ball bearing according to a first embodiment of the present invention. The ball bearing is of a double seal type, a ball 3 is interposed between the outer ring 1 and the inner ring 2 so as to be freely rotatable, and includes a cage 4 and seal members 5 and 5.

負荷容量を上げるため、軸受厚さ／軸受外径を、０．１５以下とした薄肉の玉軸受に於いて、軸受厚さは、（軸受外径−軸受内径）／２であり、玉径／軸受厚さを、０．５以上とし、軸受厚さ／軸受幅を、０．５を超えるものとし、かつ（玉径×玉数）／（３．１４×ＰＣＤ）を、０．５以上として設定している。このように、玉径は、大きく、玉数の多い設計としてある。従って、玉径、玉数を最大限にすることで、高負荷容量化ができ、特に事務機定着部等負荷の大きな部位で長寿命が可能である。   In a thin ball bearing in which the bearing thickness / bearing outer diameter is 0.15 or less to increase the load capacity, the bearing thickness is (bearing outer diameter−bearing inner diameter) / 2, The bearing thickness is 0.5 or more, the bearing thickness / bearing width is more than 0.5, and (ball diameter × number of balls) / (3.14 × PCD) is 0.5 or more. It is set. Thus, the ball diameter is large and has a large number of balls. Therefore, by maximizing the ball diameter and the number of balls, a high load capacity can be achieved, and in particular, a long life can be achieved at a heavy load portion such as an office machine fixing portion.

さらに、保持器４の底部が折り返し部６に形成してある。プレス鉄ケージのケージ底部を折り返し構造とし強度を上げることで、薄肉でも、スペースを取らない小型のシール部材５を使用することができる。また、保持器４の底部を折り返し部６としたことで、薄い鉄板の保持器４でも、十分な強度が得られる。   Further, the bottom of the cage 4 is formed in the folded portion 6. By making the bottom of the pressed iron cage a folded structure and increasing the strength, it is possible to use a small seal member 5 that does not take up space even if it is thin. In addition, since the bottom portion of the cage 4 is the folded portion 6, sufficient strength can be obtained even with the cage 4 made of a thin iron plate.

保持器４の底部の形状を折り返し部６に構成し、シール機能を兼用することで、シール取り付けに必要な軸受スペースを省略でき、幅の小さな設計ができ、コストダウンも可能となる。   By forming the shape of the bottom portion of the cage 4 in the folded portion 6 and also serving as a sealing function, it is possible to omit a bearing space necessary for attaching the seal, to design a small width, and to reduce the cost.

（第２実施の形態）
図２（ａ）は、本発明の第２実施の形態に係る玉軸受の部分断面図であり、（ｂ）は、保持器の折り返し部の拡大断面図であり、（ｃ）は、第２実施の形態の変形例に係る玉軸受の部分断面図である。 (Second Embodiment)
FIG. 2A is a partial cross-sectional view of a ball bearing according to a second embodiment of the present invention, FIG. 2B is an enlarged cross-sectional view of a folded portion of a cage, and FIG. It is a fragmentary sectional view of the ball bearing which concerns on the modification of embodiment.

図２（ａ）の本実施の形態では、シール背面側のシール部材を除去し、保持器４の背面形状を、折り返し部６に構成し、シール機能を兼用する形状としてある。なお、反対側は、シール部材５が装着してある。   In the present embodiment of FIG. 2A, the seal member on the back side of the seal is removed, and the back shape of the cage 4 is formed in the folded portion 6 so that it also serves as a seal function. A seal member 5 is mounted on the opposite side.

これら形状により、軸受厚さ／軸受幅の比率が０．５を超える幅の小さい軸受でも、保持器４とシール部材５が干渉しない。   With these shapes, the cage 4 and the seal member 5 do not interfere with each other even in a small bearing having a bearing thickness / bearing width ratio exceeding 0.5.

この場合、玉３の中心を軸方向にずらし、非対称とすことも可能である。軸方向に対し玉３の中心をずらす(シール機能を兼用した保持器４の背面方向に玉３の中心をずらす)ことで、更に幅の薄い玉軸受を設計することができる。   In this case, the center of the ball 3 can be shifted in the axial direction to be asymmetric. By shifting the center of the ball 3 with respect to the axial direction (shifting the center of the ball 3 in the back direction of the cage 4 also serving as a sealing function), a ball bearing having a thinner width can be designed.

なお、図２（ｃ）の変形例では、外輪１の外径側に、止め輪７が設定してある。   In the modification of FIG. 2C, a retaining ring 7 is set on the outer diameter side of the outer ring 1.

（第３実施の形態）
図３（ａ）は、本発明の第３実施の形態に係る玉軸受の部分断面図であり、（ｂ）は、シール兼用止め輪の側面図である。 (Third embodiment)
FIG. 3A is a partial cross-sectional view of a ball bearing according to a third embodiment of the present invention, and FIG. 3B is a side view of a seal and retaining ring.

本実施の形態に係る止め輪付き軸受では、止め輪８でシール機能を兼用させている。   In the bearing with a retaining ring according to the present embodiment, the retaining ring 8 also serves as a sealing function.

このように、止め輪８の鍔面を軸受シールと兼用することで、シール取り付けのスペースが不要となるため、軸受幅を小さくできる。シール不要によるコストダウンが可能となる。   Thus, by using the collar surface of the retaining ring 8 also as a bearing seal, a space for attaching the seal becomes unnecessary, so that the bearing width can be reduced. Cost can be reduced by eliminating the need for a seal.

なお、シール兼用の止め輪８には、図３（ｂ）に示すように、切欠き部９が設けてある。
（第４実施の形態）
図４（ａ）は、本発明の第４実施の形態に係る玉軸受の部分断面図であり、（ｂ）は、シール兼用断熱ブッシュの側面図である。 The retaining ring 8 also serving as a seal is provided with a notch 9 as shown in FIG.
(Fourth embodiment)
FIG. 4A is a partial cross-sectional view of a ball bearing according to a fourth embodiment of the present invention, and FIG. 4B is a side view of a heat-insulating bush for sealing.

本実施の形態では、断熱ブッシュ付き軸受に於いて、断熱ブッシュ１０でシール機能を兼用させている。これにより、軸受厚さ／軸受幅の比率が０．５を超える幅の小さい軸受でも、シール機能が得られる。   In the present embodiment, the heat insulating bush 10 also serves as a sealing function in the bearing with the heat insulating bush. As a result, a sealing function can be obtained even for a bearing having a small bearing width / bearing width ratio exceeding 0.5.

断熱ブッシュ１０の鍔面を軸受シールと兼用することで、シール取り付けのスペースが不要となるため、軸受幅を小さくできる。シール不要によるコストダウンが可能となる。   By using the flange surface of the heat-insulating bush 10 also as a bearing seal, a space for attaching the seal becomes unnecessary, so that the bearing width can be reduced. Cost can be reduced by eliminating the need for a seal.

なお、シール兼用の断熱ブッシュ１０には、図４（ｂ）に示すように、切欠き部１１が設けてある。   Note that the heat insulating bush 10 also serving as a seal is provided with a notch 11 as shown in FIG.

なお、本発明は、上述した実施の形態に限定されず、種々変形可能である。   In addition, this invention is not limited to embodiment mentioned above, A various deformation | transformation is possible.

比較例１〜３及び実施例１〜７の寸法一覧を表１に示す。なお、止め輪８や断熱ブッシュ１０は、図面形態に関わらず適応可能である。   Table 1 shows a list of dimensions of Comparative Examples 1 to 3 and Examples 1 to 7. Note that the retaining ring 8 and the heat insulating bush 10 are applicable regardless of the form of the drawing.

Figure 2007085520
Figure 2007085520

本発明の第１実施の形態に係る玉軸受の部分断面図であるIt is a fragmentary sectional view of the ball bearing concerning a 1st embodiment of the present invention. （ａ）は、本発明の第２実施の形態に係る玉軸受の部分断面図であり、（ｂ）は、保持器の折り返し部の拡大断面図であり、（ｃ）は、第２実施の形態の変形例に係る玉軸受の部分断面図である。(A) is a fragmentary sectional view of the ball bearing which concerns on 2nd Embodiment of this invention, (b) is an expanded sectional view of the folding | returning part of a holder | retainer, (c) is 2nd Embodiment. It is a fragmentary sectional view of the ball bearing which concerns on the modification of a form. （ａ）は、本発明の第３実施の形態に係る玉軸受の部分断面図であり、（ｂ）は、シール兼用止め輪の側面図である。(A) is a fragmentary sectional view of the ball bearing which concerns on 3rd Embodiment of this invention, (b) is a side view of a retaining ring for a seal. （ａ）は、本発明の第４実施の形態に係る玉軸受の部分断面図であり、（ｂ）は、シール兼用断熱ブッシュの側面図である。(A) is a fragmentary sectional view of the ball bearing concerning a 4th embodiment of the present invention, and (b) is a side view of a heat insulating bush for seal. （ａ）（ｂ）は、それぞれ、従来例に係る玉軸受の部分断面図である。(A) (b) is a fragmentary sectional view of the ball bearing which concerns on a prior art example, respectively.

符号の説明Explanation of symbols

１ 外輪
２ 内輪
３ 玉
４ 保持器
５ シール部材
６ 折り返し部
７ 止め輪
８ シール兼用の止め輪
９ 切欠き部
１０ シール兼用の断熱ブッシュ
１１ 切欠き部 DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner ring 3 Ball 4 Cage 5 Seal member 6 Folding part 7 Retaining ring 8 Retaining ring for sealing 9 Notch part 10 Insulating bush for sealing 11 Notch part

Claims (4)

軸受厚さ／軸受外径を、０．１５以下とした薄肉の玉軸受に於いて、
軸受厚さは、（軸受外径−軸受内径）／２であり、
玉径／軸受厚さを、０．５以上とし、
軸受厚さ／軸受幅を、０．５を超えるものとし、かつ
（玉径×玉数）／（３．１４×ＰＣＤ）を、０．５以上として設定したことを特徴とする玉軸受。 In a thin ball bearing having a bearing thickness / outer diameter of 0.15 or less,
The bearing thickness is (bearing outer diameter−bearing inner diameter) / 2.
The ball diameter / bearing thickness is 0.5 or more,
A ball bearing characterized in that the bearing thickness / bearing width exceeds 0.5, and (ball diameter × number of balls) / (3.14 × PCD) is set to 0.5 or more. 反シール側に、シール機能を兼用した保持器を設定し、軸受幅を縮小したことを特徴とする請求項１に記載の玉軸受。   The ball bearing according to claim 1, wherein a cage having a sealing function is set on the side opposite to the seal, and the bearing width is reduced. 止め輪を、シール兼用として設定したことを特徴とする請求項１又は２に記載の玉軸受。   The ball bearing according to claim 1, wherein the retaining ring is set as a seal. 内輪に装着する断熱ブッシュを、シール兼用として設定したことを特徴とする請求項１乃至３の何れか１項に記載の玉軸受。   The ball bearing according to any one of claims 1 to 3, wherein the heat insulating bush mounted on the inner ring is set as a seal.
JP2005278326A 2005-09-26 2005-09-26 Ball bearing Pending JP2007085520A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008117618A1 (en) 2007-03-28 2008-10-02 Nissan Motor Co., Ltd. Magnetostrictive stress sensor
JP2010090944A (en) * 2008-10-06 2010-04-22 Nsk Ltd Bearing device
CN102084144A (en) * 2008-06-20 2011-06-01 谢夫勒科技有限两合公司 Roller bearing for underwater applications
JP2013142444A (en) * 2012-01-11 2013-07-22 Nsk Ltd Seal ring for ball bearing, and the ball bearing with the same

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001012486A (en) * 1999-06-28 2001-01-16 Skf Gmbh Axial direction fixing structure of bearing ring
JP2002235751A (en) * 2001-02-13 2002-08-23 Nsk Ltd Rolling bearing
JP2003130068A (en) * 2001-10-23 2003-05-08 Ntn Corp Insulating sleeve integrated bearing
JP2004313466A (en) * 2003-04-16 2004-11-11 Nsk Ltd Ct scanner apparatus and rolling bearing installed in the same

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001012486A (en) * 1999-06-28 2001-01-16 Skf Gmbh Axial direction fixing structure of bearing ring
JP2002235751A (en) * 2001-02-13 2002-08-23 Nsk Ltd Rolling bearing
JP2003130068A (en) * 2001-10-23 2003-05-08 Ntn Corp Insulating sleeve integrated bearing
JP2004313466A (en) * 2003-04-16 2004-11-11 Nsk Ltd Ct scanner apparatus and rolling bearing installed in the same

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008117618A1 (en) 2007-03-28 2008-10-02 Nissan Motor Co., Ltd. Magnetostrictive stress sensor
CN102084144A (en) * 2008-06-20 2011-06-01 谢夫勒科技有限两合公司 Roller bearing for underwater applications
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JP2013142444A (en) * 2012-01-11 2013-07-22 Nsk Ltd Seal ring for ball bearing, and the ball bearing with the same

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