JP5237038B2 - Anti-creep rolling bearing - Google Patents
Anti-creep rolling bearing Download PDFInfo
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- JP5237038B2 JP5237038B2 JP2008261327A JP2008261327A JP5237038B2 JP 5237038 B2 JP5237038 B2 JP 5237038B2 JP 2008261327 A JP2008261327 A JP 2008261327A JP 2008261327 A JP2008261327 A JP 2008261327A JP 5237038 B2 JP5237038 B2 JP 5237038B2
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- 238000005096 rolling process Methods 0.000 title claims description 14
- 229920005989 resin Polymers 0.000 claims description 24
- 239000011347 resin Substances 0.000 claims description 24
- 229910052751 metal Inorganic materials 0.000 claims description 14
- 239000002184 metal Substances 0.000 claims description 14
- 229910000831 Steel Inorganic materials 0.000 claims description 12
- 239000010959 steel Substances 0.000 claims description 12
- 238000000034 method Methods 0.000 claims 2
- 229910000838 Al alloy Inorganic materials 0.000 description 4
- 230000007423 decrease Effects 0.000 description 4
- 230000014509 gene expression Effects 0.000 description 4
- FYYHWMGAXLPEAU-UHFFFAOYSA-N Magnesium Chemical compound [Mg] FYYHWMGAXLPEAU-UHFFFAOYSA-N 0.000 description 3
- 229910052782 aluminium Inorganic materials 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 3
- 230000000052 comparative effect Effects 0.000 description 3
- 229910052749 magnesium Inorganic materials 0.000 description 3
- 239000011777 magnesium Substances 0.000 description 3
- 229910000861 Mg alloy Inorganic materials 0.000 description 2
- 229920000571 Nylon 11 Polymers 0.000 description 2
- 229920002302 Nylon 6,6 Polymers 0.000 description 2
- 229910045601 alloy Inorganic materials 0.000 description 2
- 239000000956 alloy Substances 0.000 description 2
- 229920006128 poly(nonamethylene terephthalamide) Polymers 0.000 description 2
- 229920001707 polybutylene terephthalate Polymers 0.000 description 2
- 229920012310 Polyamide 9T (PA9T) Polymers 0.000 description 1
- SNAAJJQQZSMGQD-UHFFFAOYSA-N aluminum magnesium Chemical compound [Mg].[Al] SNAAJJQQZSMGQD-UHFFFAOYSA-N 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- FXNGWBDIVIGISM-UHFFFAOYSA-N methylidynechromium Chemical group [Cr]#[C] FXNGWBDIVIGISM-UHFFFAOYSA-N 0.000 description 1
- -1 polybutylene terephthalate Polymers 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/067—Fixing them in a housing
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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
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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
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/10—Force connections, e.g. clamping
-
- 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
- F16C2240/70—Diameters; Radii
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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
- 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
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mounting Of Bearings Or Others (AREA)
- Rolling Contact Bearings (AREA)
Description
本発明は、ハウジングに内嵌される外輪のクリープを防止するクリープ防止転がり軸受に関する。 The present invention relates to an anti-creep rolling bearing that prevents creep of an outer ring fitted in a housing.
オルタネータ等の自動車用補機のハウジングには、軽量化のためにアルミニウム、マグネシウム、またはこれらの一方もしくは両方の合金等の比重が軽い軽金属で形成されたものがある。これらの軽金属は、いずれも鋼よりも線膨張係数が大きい。 2. Description of the Related Art Some auxiliary housings for automobiles such as alternators are made of a light metal having a low specific gravity such as aluminum, magnesium, or one or both of these alloys for weight reduction. All of these light metals have a larger linear expansion coefficient than steel.
このような鋼よりも線膨張係数が大きい金属で形成されたハウジングに、鋼で形成された外輪が内嵌される転がり軸受には、ハウジングと外輪の熱膨張差に伴う締め代の低下による外輪のクリープを防止するために、外輪の外径面に円周方向へ延びる環状溝を設け、この環状溝にハウジングよりも線膨張係数が大きい樹脂で形成されたバンドを外輪の外径面から突出するように装着したクリープ防止転がり軸受が用いられている（例えば、特許文献１参照）。 In a rolling bearing in which an outer ring formed of steel is fitted in a housing formed of a metal having a larger linear expansion coefficient than that of steel, the outer ring is caused by a decrease in tightening allowance due to a difference in thermal expansion between the housing and the outer ring. In order to prevent creep, an annular groove extending in the circumferential direction is provided on the outer diameter surface of the outer ring, and a band formed of a resin having a linear expansion coefficient larger than that of the housing protrudes from the outer diameter surface of the outer ring. An anti-creep rolling bearing that is mounted as described above is used (see, for example, Patent Document 1).
特許文献１に記載されたものでは、軸受外径に対する樹脂製のバンドの径方向厚さを、室温よりも高い軸受の想定使用温度と室温との温度差をパラメータとした、ハウジング、外輪およびバンドの各線膨張係数の関数で規定している。
In the one described in
前記バンドを形成する樹脂には、ポリアミド９Ｔ（ＰＡ９Ｔ）、ポリアミド１１（ＰＡ１１）、ポリアミド６６（ＰＡ６６）、ポリブチレンテレフタレート（ＰＢＴ）等が用いられている。 As the resin forming the band, polyamide 9T (PA9T), polyamide 11 (PA11), polyamide 66 (PA66), polybutylene terephthalate (PBT) or the like is used.
特許文献１に記載されたクリープ防止転がり軸受は、想定使用温度と室温との温度差をパラメータとして、軸受外径に対する樹脂製バンドの径方向厚さを規定しているので、軸受の使用温度に応じて樹脂製バンドのサイズを設計する必要があり、汎用性に欠ける問題がある。
The anti-creep rolling bearing described in
そこで、本発明の課題は、軸受の使用温度と関係なく、広い温度範囲で使用できるように、樹脂製バンドのサイズを設計することである。 Therefore, an object of the present invention is to design the size of the resin band so that it can be used in a wide temperature range regardless of the operating temperature of the bearing.
上記の課題を解決するために、本発明は、鋼よりも線膨張係数が大きい金属で形成されたハウジングに内嵌され、鋼で形成された外輪の外径面に円周方向へ延びる環状溝を設け、この環状溝に前記ハウジングを形成する金属よりも線膨張係数が大きい樹脂で形成されたバンドを、前記外輪の外径面から突出するように装着したクリープ防止転がり軸受において、前記バンドが前記環状溝を充満するように装着されるようにし、前記ハウジングを形成する金属の線膨張係数をαＨ（／Ｋ）、前記外輪を形成する鋼の線膨張係数をαＲ（／Ｋ）、前記バンドを形成する樹脂の線膨張係数をαＢ（／Ｋ）としたときに、前記バンドの内径ｄと外径Ｄとの比ｄ／Ｄが、（１）式を満足するように規定した構成を採用した。
ｄ／Ｄ≦√〔（２αＨ−３αＢ＋αＲ）／｛３（αＲ−αＢ）｝〕 （１）
In order to solve the above problems, the present invention is an annular groove that is fitted in a housing formed of a metal having a larger linear expansion coefficient than steel and extends in the circumferential direction on the outer diameter surface of the outer ring formed of steel. In the anti-creep rolling bearing in which a band formed of a resin having a larger linear expansion coefficient than the metal forming the housing is mounted in the annular groove so as to protrude from the outer diameter surface of the outer ring, the band is The metal is formed so as to fill the annular groove, the coefficient of linear expansion of the metal forming the housing is α H (/ K), the coefficient of linear expansion of the steel forming the outer ring is α R (/ K), When the linear expansion coefficient of the resin forming the band is α B (/ K), the ratio d / D between the inner diameter d and the outer diameter D of the band is defined to satisfy the expression (1). Adopted the configuration.
d / D ≦ √ [(2α H −3α B + α R ) / {3 (α R −α B )}] (1)
すなわち、環状溝を充満するように装着されたバンドの単位温度上昇当たりの体膨張量ΔＶは、バンドの外径膨張率をβ（／Ｋ）、環状溝の幅寸法すなわちバンドの初期幅をＷとすると、環状溝による拘束条件によって（２）式で表される。
ΔＶ＝π〔｛Ｄ（１＋β）｝２−｛ｄ（１＋αＲ）｝２〕・（１＋αＲ）・Ｗ
−π（Ｄ２−ｄ２）・Ｗ （２）
一方、バンドの体膨張率は線膨張係数αＢの３倍となるので、バンドの単位温度上昇当たりの体膨張量ΔＶは、（３）式で表すこともできる。
ΔＶ＝３αＢπ（Ｄ２−ｄ２）・Ｗ （３）
（２）式と（３）式を等置して整理し、線膨張係数αＲや外径膨張率βの２次以上の微小項を省略すると、バンドの外径膨張率βは（４）式で表される。
β＝｛３αＢ−αＲ＋３（ｄ／Ｄ）２・（αＲ−αＢ）｝／２ （４）
That is, the body expansion amount ΔV per unit temperature increase of the band mounted so as to fill the annular groove is expressed by β (/ K) as the outer diameter expansion coefficient of the band, and the width dimension of the annular groove, that is, the initial width of the band as W. Then, it is expressed by equation (2) depending on the constraint condition by the annular groove.
ΔV = π [{D (1 + β)} 2 − {d (1 + α R )} 2 ] · (1 + α R ) · W
−π (D 2 −d 2 ) · W (2)
On the other hand, since the volume expansion rate of the band is three times the linear expansion coefficient alpha B, volume expansion amount ΔV per unit temperature rise of the band can also be expressed by equation (3).
ΔV = 3α B π (D 2 −d 2 ) · W (3)
If the expressions (2) and (3) are arranged and arranged, and the second and higher terms of the linear expansion coefficient α R and the outer diameter expansion coefficient β are omitted, the outer diameter expansion coefficient β of the band is (4) It is expressed by a formula.
β = {3α B −α R +3 (d / D) 2 · (α R −α B )} / 2 (4)
前記ハウジングに対するバンドの締め代が低下しないようにするためには、バンドの外径膨張率βが、ハウジングの内径膨張率すなわち線膨張係数αＨ以上となることが必要であるので、（５）式が得られる。
β＝｛３αＢ−αＲ＋３（ｄ／Ｄ）２・（αＲ−αＢ）｝／２≧αＨ （５）
ここに、αＲ−αＢ＜０であることを考慮して、（５）式をバンドの内外径比ｄ／Ｄについて整理すると、上記の（１）式が求められる。（１）式は、温度のパラメータを含まず、各線膨張係数αＨ、αＲ、αＢのみの関数となっているので、軸受を広い温度範囲で使用できるように、樹脂製バンドのサイズを設計することができる。
In order not to lower the band tightening margin with respect to the housing, it is necessary that the outer diameter expansion coefficient β of the band is equal to or larger than the inner diameter expansion coefficient of the housing, that is, the linear expansion coefficient α H. (5) The formula is obtained.
β = {3α B −α R +3 (d / D) 2 · (α R −α B )} / 2 ≧ α H (5)
Considering that α R −α B <0, the above equation (1) is obtained by arranging the equation (5) with respect to the inner / outer diameter ratio d / D of the band. Since the equation (1) does not include a temperature parameter and is a function of only the linear expansion coefficients α H , α R , and α B , the size of the resin band is set so that the bearing can be used in a wide temperature range. Can be designed.
前記環状溝の少なくとも一方の溝底コーナ部に隅肉部を設けることにより、樹脂製バンドが環状溝を充満するように装着しやすくすることができる。 By providing a fillet portion at at least one groove bottom corner portion of the annular groove, the resin band can be easily mounted so as to fill the annular groove.
前記環状溝の隅肉部を設けた溝底コーナ部に嵌め込まれる前記バンドの内径側コーナ部に面取り部を設けることにより、樹脂製バンドを環状溝に嵌め込みやすくすることができる。 By providing a chamfered portion at the inner diameter side corner portion of the band that is fitted into the groove bottom corner portion provided with the fillet portion of the annular groove, the resin band can be easily fitted into the annular groove.
前記環状溝を軸受中心の両側の２箇所に設け、前記隅肉部を軸受中心側の溝底コーナ部に設けることにより、外輪をバランスよくハウジングに支持することができ、樹脂製バンドの嵌め込み先端側に面取り部を設ける場合は、樹脂製バンドを環状溝により嵌め込みやすくすることができる。 By providing the annular groove at two locations on both sides of the bearing center and providing the fillet portion at the groove bottom corner portion on the bearing center side, the outer ring can be supported in a well-balanced manner by the resin band fitting tip When the chamfered portion is provided on the side, the resin band can be easily fitted by the annular groove.
前記転がり軸受を前記外輪の内径面に円弧状の軌道溝が形成された玉軸受とし、前記２箇所の環状溝を前記円弧状の軌道溝中心の両側に設けることにより、外輪をバランスよくハウジングに支持することができる。 The rolling bearing is a ball bearing in which an arc-shaped raceway groove is formed on the inner diameter surface of the outer ring, and the two annular grooves are provided on both sides of the center of the arc-shaped raceway groove, so that the outer ring is balanced in the housing. Can be supported.
前記外輪の軸受中心側の溝底コーナ部と前記軌道溝間の最小肉厚を１ｍｍ以上とすることにより、外輪の強度を確保することができる。 By setting the minimum thickness between the groove bottom corner portion on the bearing center side of the outer ring and the raceway groove to be 1 mm or more, the strength of the outer ring can be ensured.
上述した各クリープ防止転がり軸受は、前記ハウジングを形成する金属が、アルミニウム、マグネシウム、またはこれらの一方もしくは両方の合金のいずれかであるものに好適である。 Each of the anti-creep rolling bearings described above is suitable for a case where the metal forming the housing is aluminum, magnesium, or one or both of these alloys.
本発明のクリープ防止転がり軸受は、樹脂で形成されたバンドが環状溝を充満するように装着されるようにし、ハウジングを形成する金属の線膨張係数をαＨ（／Ｋ）、外輪を形成する鋼の線膨張係数をαＲ（／Ｋ）、バンドを形成する樹脂の線膨張係数をαＢ（／Ｋ）としたときに、バンドの内径ｄと外径Ｄとの比ｄ／Ｄが、前記（１）式を満足するように規定したので、軸受の使用温度と関係なく、広い温度範囲で使用できるように、樹脂製バンドのサイズを設計することができる。 The anti-creep rolling bearing of the present invention is mounted so that the band formed of resin fills the annular groove, the linear expansion coefficient of the metal forming the housing is α H (/ K), and the outer ring is formed. When the linear expansion coefficient of the steel is α R (/ K) and the linear expansion coefficient of the resin forming the band is α B (/ K), the ratio d / D between the inner diameter d and the outer diameter D of the band is Since it has been defined so as to satisfy the expression (1), the size of the resin band can be designed so that it can be used in a wide temperature range regardless of the operating temperature of the bearing.
以下、図面に基づき、本発明の実施形態を説明する。 このクリープ防止転がり軸受は、図１（ａ）に示すように、内輪１と外輪２が高炭素クロム軸受鋼ＳＵＪ２（線膨張係数αＲ＝１．２５×１０−５／Ｋ）で形成されて、これらの円弧状の軌道溝１ａ、２ａ間に複数のボール３が保持器４に保持され、両端部がシール部材５でシールされた深溝玉軸受であり、アルミニウム合金（線膨張係数αＨ＝２．１８×１０−５／Ｋ）で形成されたハウジング１０の内径面に内嵌される外輪２の外径面に、軸受中心に設けられた軌道溝２ａの両側の２箇所で円周方向へ延びる環状溝６が設けられ、各環状溝６に、ハウジング１０を形成するアルミニウム合金の線膨張係数αＨよりも大きい線膨張係数αＢの樹脂で形成されたバンド７が装着されている。
Hereinafter, embodiments of the present invention will be described with reference to the drawings. In this creep-proof rolling bearing, as shown in FIG. 1 (a), an
前記バンド７は、図１（ｂ）に拡大して示すように、外輪２の外径面から突出し、環状溝６を充満するように装着されている。環状溝６の軸受中心側の溝底コーナ部にはＲ形状の隅肉部６ａが設けられ、この隅肉部６ａが設けられた溝底コーナ部と軌道溝２ａ間の最小肉厚は１ｍｍ以上とされている。隅肉部６ａは、両側の溝底コーナ部に設けてもよく、その断面形状はＲ形状に限定されることはない。また、隅肉部６ａが設けられた溝底コーナ部に嵌め込まれたバンド７の内径側コーナ部には、隅肉部６ａと等しいか少し小さいＲ形状の面取り部７ａが設けられている。
The
前記バンド７の内径ｄと外径Ｄとの比ｄ／Ｄは、使用中に温度上昇したときに、ハウジング１０に対する締め代が低下しないように、各部材の線膨張係数αＨ、αＲ、αＢのみの関数である（１）式を満足するように規定されている。
ｄ／Ｄ≦√〔（２αＨ−３αＢ＋αＲ）／｛３（αＲ−αＢ）｝〕 （１）
The ratio d / D between the inner diameter d and the outer diameter D of the
d / D ≦ √ [(2α H −3α B + α R ) / {3 (α R −α B )}] (1)
表１に示すように、前記バンド７を形成した樹脂を、それぞれＰＡ９Ｔ、ＰＡ１１、ＰＡ６６とし、内外径比ｄ／Ｄが（１）式を満足するように規定した深溝玉軸受を用意した（実施例１〜３）。また、比較例として、バンド７を形成した樹脂をＰＡ９Ｔとし、内外径比ｄ／Ｄが（１）式を満足しない深溝玉軸受も用意した。なお、表１中には、（５）式で算出されるバンド７の外径膨張率βと、（１）式の右辺の値も参考値として付記しているが、各実施例の外径膨張率βは、いずれもハウジングの線膨張係数αＨよりも大きくなっている。
As shown in Table 1, deep groove ball bearings were prepared in which the resin on which the
上記各実施例と比較例の深溝玉軸受を、回転試験機のアルミニウム合金で形成したハウジングに、バンドとハウジング間に締め代を付与して圧入したのち、内輪を回転させる軸受回転試験を行い、運転中の温度上昇に伴う締め代の低下を、クリープ発生の有無で調査した。この軸受回転試験の結果を表１に併せて示すが、内外径比ｄ／Ｄが（１）式を満足するように規定した各実施例のものは、広い温度範囲でクリープが発生せず、温度上昇に伴う締め代の低下がないことが確認された。これに対して、内外径比ｄ／Ｄが（１）式を満足しない比較例のものはクリープが発生し、温度上昇に伴って締め代が低下することが分かった。 The deep groove ball bearings of the above examples and comparative examples were subjected to a bearing rotation test for rotating the inner ring after press-fitting with a tightening margin between the band and the housing to the housing formed of the aluminum alloy of the rotation tester, The decrease in the tightening allowance due to the temperature rise during operation was investigated based on the occurrence of creep. The results of this bearing rotation test are also shown in Table 1. In the examples in which the inner / outer diameter ratio d / D is defined so as to satisfy the formula (1), creep does not occur in a wide temperature range. It was confirmed that there was no decrease in the tightening allowance associated with the temperature rise. On the other hand, it was found that the comparative example in which the inner / outer diameter ratio d / D does not satisfy the formula (1) generates creep, and the tightening margin decreases as the temperature rises.
上述した実施形態では、外輪の外径面の２箇所の環状溝に２本の樹脂製バンドを装着した深溝玉軸受としたが、本発明に係るクリープ防止転がり軸受は、アンギュラ玉軸受やころ軸受等の他のタイプの転がり軸受にも適用することができ、樹脂製バンドの装着本数も１本または３本以上とすることもできる。 In the above-described embodiment, the deep groove ball bearing is provided with two resin bands in two annular grooves on the outer diameter surface of the outer ring. However, the anti-creep rolling bearing according to the present invention is an angular ball bearing or a roller bearing. The present invention can be applied to other types of rolling bearings, and the number of resin bands can be one or three or more.
また、上述した実施形態では、外輪がアルミニウム合金で形成されたハウジングに内嵌されるものとしたが、ハウジングを形成する金属は、線膨張係数が鋼よりも大きいものであればよく、アルミニウム、マグネシウム、マグネシウム合金、アルミマグネシウム合金等とすることもできる。 In the above-described embodiment, the outer ring is fitted in a housing formed of an aluminum alloy. However, the metal forming the housing may be any material that has a linear expansion coefficient larger than that of steel, aluminum, Magnesium, a magnesium alloy, an aluminum magnesium alloy, or the like can also be used.
１ 内輪
２ 外輪
１ａ、２ａ 軌道溝
３ ボール
４ 保持器
５ シール部材
６ 環状溝
６ａ 隅肉部
７ バンド
７ａ 面取り部
１０ ハウジング
Claims (1)
ｄ／Ｄ≦√〔（２αＨ−３αＢ＋αＲ）／｛３（αＲ−αＢ）｝〕 A metal that is fitted in a housing made of a metal having a linear expansion coefficient larger than that of steel, and that has an annular groove extending in the circumferential direction on the outer diameter surface of the outer ring made of steel. The metal that forms the housing in the annular groove In a design method of a creep-proof rolling bearing in which a band formed of a resin having a larger linear expansion coefficient than the outer ring is mounted so as to protrude from the outer diameter surface of the outer ring, the band is mounted so as to fill the annular groove. The linear expansion coefficient of the metal forming the housing is α H (/ K), the linear expansion coefficient of the steel forming the outer ring is α R (/ K), and the linear expansion coefficient of the resin forming the band The size of the band is designed so that the ratio d / D between the inner diameter d and the outer diameter D of the band satisfies the following equation where α B is / B (/ K) : Design method .
d / D ≦ √ [(2α H −3α B + α R ) / {3 (α R −α B )}]
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| DE102012211261B4 (en) * | 2012-06-29 | 2022-09-08 | Aktiebolaget Skf | bearing arrangement |
| DE102014103794A1 (en) * | 2014-03-20 | 2015-09-24 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Crank drive arrangement with non-rotating rod bearing, preferably for an oil-free piston compressor |
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| JP4357154B2 (en) * | 2002-05-24 | 2009-11-04 | Ｎｔｎ株式会社 | Anti-creep bearing |
| JP2007315585A (en) * | 2006-04-24 | 2007-12-06 | Ntn Corp | Rolling bearing |
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