JP4582271B2 - Roller bearing - Google Patents

Roller bearing Download PDF

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Publication number
JP4582271B2
JP4582271B2 JP2000269851A JP2000269851A JP4582271B2 JP 4582271 B2 JP4582271 B2 JP 4582271B2 JP 2000269851 A JP2000269851 A JP 2000269851A JP 2000269851 A JP2000269851 A JP 2000269851A JP 4582271 B2 JP4582271 B2 JP 4582271B2
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Prior art keywords
cage
assembly
outer ring
inner ring
roller
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JP2002081441A (en
Inventor
清 荻野
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JTEKT Corp
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JTEKT Corp
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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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • 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
    • F16C23/02—Sliding-contact bearings
    • 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
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

Description

【０００１】
【発明の属する技術分野】
本発明は針状ころ軸受等をはじめとするころ軸受に関し、更に詳しくは、無負荷状態における保持器およびころの自励振動に起因する異音の発生しにくいころ軸受に関する。
【０００２】
【従来の技術】
例えば自動車のミッションに用いられる針状ころ軸受においては、一般に、図３（Ａ）に要部軸平行断面図を、同図（Ｂ）に要部軸直交断面図をそれぞれ示すように、複数のポケット３１ａが周方向に一定のピッチで形成された保持器３１を用いて、その各ポケット３１ａにころ３２を保持して相互に一体化した状態で組み込まれる。この保持器３１と複数のころ３２からなる組立体３３は、内輪３４と外輪３５の間に形成される環状空間３６、あるいは内輪および外輪を有さないケージアンドローラタイプと称されるものにあっては、軸３７と当該軸に対して相対回転自在の部材３８に形成された孔の間に形成される環状空間内に、各ポケット３１ａ内のころ３２が転動自在の状態で配置される。
【０００３】
内輪３４と外輪３５の間の環状空間３６内、あるいは軸３７とその軸に対して回動自在の部材３８に形成された孔との間に形成される環状空間内において、保持器３１ところ３２の組立体３３の軸方向位置は、図３（Ａ）に示されるように、内輪３４とともに軸３７に固定された側板３７ａもしくは軸３７に形成された段部等によって規制されるようになっている。
【０００４】
【発明が解決しようとする課題】
ところで、以上のような針状ころ軸受を前記した自動車のミッション等に用いる場合のように、外部からの荷重がかからない状態、つまり無負荷状態で回転する可能性のある箇所に使用される場合、保持器の回転速度、換言すればころの公転速度が使用中に急激に変化するときがあり、その際、保持器やころが自励振動して大きな振動や耳障りな音を発することがある。
【０００５】
本発明はこのような実情に鑑みてなされたもので、無負荷状態での回転中に生じる自励振動に伴う振動や騒音の発生を抑制することのできるころ軸受の提供を目的としている。
【０００６】
上記の目的を達成するため、本発明のころ軸受は、複数のころと、その各ころを周方向に一定のピッチで保持する複数のポケットが形成されてなる保持器を備えたころ軸受において、
上記保持器の軸方向端面が、内輪に対して相対回転不能に設けられている側板もしくは軸の段部に当接して当該保持器と上記複数のころからなる組立体の軸方向位置を規制するよう構成されているとともに、上記組立体の外輪に対する連れ回り力が、内輪に対する連れ回り力に比して十分に大きくなるように、上記保持器の軸方向端面の面積が、ころの転動空間の軸直交断面積の４０％以下とされていることによって特徴づけられる。
【０００７】
本発明は、針状ころ軸受等のころ軸受の無負荷状態での回転時における保持器およびころの組立体の挙動を鋭意研究した結果としてなされたものであり、以下に、その組立体の自励振動発生のメカニズム、換言すれば異音発生のメカニズムについて説明する。
【０００８】
保持器ところの組立体の自励振動は、組立体の内輪に対する連れ回り力と、外輪に対する連れ回り力とのバランスが崩れることにより、その回転数が急激に変動したときに発生する。
【０００９】
図２に隙間を誇張した軸直交断面図を示すように、保持器３１とその各ポケット３１ａ内に保持された複数のころ３２からなる組立体３３が、内輪３４と外輪３５の間に形成されている環状空間３６内に配置されており、内輪３４が固定されて外輪３５が回転するものとして、無負荷状態において組立体３３には、外輪３５に連れ回ろうとする力Ｑと、内輪３４に連れ回ろうとする力Ｆ（この場合は内輪３４の回転数＝０）とが働く。これらのＱとＦは下記のように表すことができる。
【００１０】
Ｑ＝ころ３２に発生する遠心力による影響＋保持器３１と外輪３５との間の摩擦力＋ころ３２の慣性力＋保持器３１の慣性力 ・・・・（１）
で表される。ここで、保持器３１と外輪３５との間の摩擦力とは、保持器３１の外周面と外輪３５の内周面の間に介在する潤滑剤の粘性抵抗である。
【００１１】
Ｆ＝ころ３２と内輪３４との接触抵抗＋保持器３１と側板３７との摩擦力＋保持器３１と内輪３４との摩擦力 ・・・・（２）
で表される。ここで、保持器３１と側板３７との摩擦力とは、保持器３１の端面（軸方向端面）と側板３７との間に介在する潤滑剤の粘性抵抗であり、保持器３１と内輪３４との摩擦力とは、保持器３１の内周面と内輪３４の外周面との間に介在する潤滑剤の粘性抵抗である。
【００１２】
（１）式において、
ころ３２に発生する遠心力による影響＝Ｚ・μ1 ・ｆ
保持器３１と外輪３５の摩擦力＝η・Ａ1 ・ν1 ・／ｈ1
また、（２）式において、
保持器３１と側板３７との摩擦力＝η・Ａ2 ・ν2 ・／ｈ2
保持器３１と内輪３４との摩擦力＝η・Ａ3 ・ν3 ・／ｈ3
である。ここで、
【００１３】
Ｚ ：ころ３２の数
μ1 ：ころ３２と外輪３５の摩擦係数
ｆ ：ころ３２の１本当たりの遠心力
η ：潤滑剤の粘性係数
Ａ1 ：保持器３１の外周面と外輪３５との接触面積
ν1 ：外輪３５の内周面の周速
ｈ1 ：保持器３１の外周面と外輪３５の内周面間の潤滑剤油膜厚さ
Ａ2 ：保持器３１の端面と側板３７との接触面積
ν2 ：保持器３１の端面の周速
ｈ2 ：保持器３１の端面と側板３７間の潤滑剤油膜厚さ
Ａ3 ：保持器３１の内周面と内輪３４の外周面との接触面積
ν3 ：保持器３１の内周面の周速
ｈ3 ：保持器３１の内周面と内輪３４の外周面間の潤滑剤油膜厚さ
である。
【００１４】
以上のことから、（１）式は
Ｑ＝Ｚ・μ1 ・ｆ＋η・Ａ1 ・ν1 ／ｈ1 ＋ころ３２の慣性力＋保持器３１の慣性力 ・・・・（３）
Ｆ＝ころ３２と内輪３４との接触抵抗＋η・Ａ2 ・ν2 ／ｈ2
＋η・Ａ3 ・ν3 ／ｈ 3 ・・・・（４）
となる。
【００１５】
ここで、（３）式におけるころ３２の慣性力＋保持器３１の慣性力は、急加減速時に影響される因子と考えられる。また、（４）式におけるころ３２と内輪３４の接触抵抗は、いずれの場合も一定と考えられる。
【００１６】
さて、無負荷状態における保持器３１ところ３２の組立体３３の挙動は、組立体３３が外輪３５に連れ回ろうとする力Ｑと、内輪３４に連れ回ろうとする力（ここでは内輪３４の回転数０）Ｆの大小関係によって決まる。すなわち、Ｑ≫Ｆならば、保持器３１ところ３２の組立体３３の回転数≒外輪３５の回転数となり、組立体３３の回転変動は少なくなる。また、Ｑ≪Ｆならば、保持器３１の回転数≒外輪３５の回転数／２（ころ３２に滑りが生じない場合のころ３２の公転回転数）となる。これらの場合には、いずれも、異音の発生頻度は極めて少なくなると推定される。更に、Ｑ≒Ｆならば、この場合においても保持器３１の回転数≒外輪３５の回転数／２となるが、ＱとＦとの大小関係が逆転しやすいが故に保持器３１の回転変動は大きく、異音の発生頻度が多くなると推定される。
【００１７】
従って、前記した目的を達成するためには、Ｑ≫ＦもしくはＱ≪Ｆとすればよいのであるが、（３），（４）式の右辺各項に鑑み、（４）式右辺の各項のいずれかを小さくしてＦを小さくすることによりＱ≫Ｆとして、保持器３１ところ３２の組立体３３を外輪３５に連れ回りさせることが実用的である。より具体的には、請求項１に係る発明のように、保持器の軸方向両端面の面積を、ころの転動空間（環状空間３６）の軸直交断面面積の４０％以下と小さくして、保持器３１の端面と側板３７との接触面積Ａ2 を小さくし、（４）式右辺第２項を小さくすることにより、Ｆを小さくする構成を好適に採用することができる。
【００１８】
【発明の実施の形態】
以下、図面を参照しつつ本発明の好適な実施の形態について説明する。
図１は本発明の実施の形態の説明図であり、（Ａ）は要部軸平行断面図で、（Ｂ）は要部拡大軸直交断面図である。
【００１９】
保持器１は、ころ２を収容するための複数のポケット１ａを有し、その各ポケット１ａにころ２を回動自在に保持することによって、各ころ２は周方向に一定のピッチのもとに保持された状態となる。この保持器１と複数のころ２からなる組立体３は、図１（Ｂ）に示すように、軸７に圧入された内輪４と外輪５の間、もしくは、内輪４および外輪５を有さないものにあっては、軸７とギア等の回転部材８の中心部に形成された孔との間に形成される環状空間６内に収容される。
【００２０】
また、組立体３の軸方向への位置は、内輪４が圧入される軸に固定された側板７ａ（もしくは軸に形成される段部等）に保持器１の両端部が当接することによって規制される。
【００２１】
この実施の形態の特徴は、図１（Ａ）に示すように、保持器１の両端部に比較的大きな面取り部１１を形成することによって、その両端部の面積を、ころ２の転動空間である環状空間６の軸直交断面積の４０％以下としている点と、図１（Ｂ）に示すように、各ポケット１ａの空間形状が、保持器１の外周側ほど周方向への寸法が大きくなっており、その最外周部における周方向への寸法Ｌが、ころ２の直径Ｄの１０５％以上、より詳しくは１０５〜１１５％の範囲、となっている点である。
【００２２】
以上の実施の形態の構成によれば、保持器１の両端面の面積を環状空間６の軸直交断面積の４０％以下にしているため、保持器１の両端と側板７ａ（または軸７に形成される段部）との接触面積が小さくなり、前記した（４）式右辺第２項が小さくなる。また、各ポケット１ａを、保持器１の外周側ほど広くしているので、無負荷状態で外輪５が回転しているとき、各ころ２は外輪５側に移動しやすくなり、つまり内輪４から離脱しやすくなり、（４）式右辺第１項のころ２と内輪４との接触抵抗が小さくなる。
【００２３】
以上の結果、保持器１ところ２の組立体３は、保持器１の両端部に形成された面取り部１１と、ポケット１ａの空間形状により、無負荷状態で外輪５が回転しているとき、組立体３の内輪４に対する連れ回り力（内輪４に対するドラッグ力）Ｆが小さくなり、外輪５に対する連れ回り力（外輪５に対するドラッグ力）Ｑとの関係が、Ｑ≫Ｆとなる。従って、無負荷状態で外輪５が回転しているとき、保持器１ところ２の組立体３は主として外輪５に連れ回り、その回転数は安定して外輪４の回転数と略等しくなる。従って、組立体３は回転変動に起因する自励振動を生じることがなく、異音や振動を発生することがない。
【００２４】
なお、以上の実施の形態では、請求項１に係る発明の特徴的構成である保持器１の両端面の面積を環状空間６の軸直交断面積の４０％以下とする構成と、保持器１の各ポケット１ａの空間形状を保持器１の外周側ほど広くしてその最大の周方向寸法Ｌをころ２の直径Ｄの１０５％以上とする構成の双方を採用したが、保持器１の両端面の面積を環状空間６の軸直交断面積の４０％以下とする構成のみを採用しても、組立体３の内輪４に対する連れ回り力Ｆを小さくすることができ、従って無負荷状態における組立体３の自励振動を抑制する効果を奏することができる。
【００２５】
また、以上の実施の形態においては、保持器１ところ２の組立体３を内輪４と外輪５の間に配置したころ軸受に本発明を適用した例を示したが、組立体３を、軸７とその周囲で回転するギア等の回転部材８との間に挿入して内輪および外輪を省略した、いわゆるケージアンドローラタイプのころ軸受に対しても等しく適用し得ることは勿論である。
【００２６】
【発明の効果】
以上のように、本発明によれば、保持器の軸方向両端面の面積をころの転動空間（環状空間）の軸直交断面積の４０％以下とすることにより、保持器ところの組立体の内輪（または軸）に対する連れ回り力（ドラッグ力）Ｆを小さくして、組立体の外輪に対する連れ回り力Ｑとの関係をＱ≫Ｆとしているので、無負荷状態において外輪が回転しているとき、保持器ところの組立体に主として外輪に対して連れ回り、その回転数は安定して外輪の回転数に略等しくなって、内輪に対する連れ回り力と外輪に対する連れ回り力とのバランスの崩れによる急激な回転数変動が生じず、従って自励振動が発生して異音や振動が発生することを防止することができる。
【図面の簡単な説明】
【図１】 本発明の実施の形態の説明図で、（Ａ）は要部軸平行断面図で、（Ｂ）は要部拡大軸直交断面図である。
【図２】 本発明の原理説明図で、隙間を誇張して示すころ軸受の要部軸直交断面図である。
【図３】 自動車のミッション等に用いられる針状ころ軸受の構成例の説明図で、（Ａ）は要部軸平行断面図であり、（Ｂ）は要部軸直交断面図である。
【符号の説明】
１ 保持器
１ａ ポケット
１１ 面取り部
２ ころ
３ 組立体
４ 内輪
５ 外輪
６ 環状空間
７ 軸
７ａ 側板
８ 回転部材[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a roller bearing such as a needle roller bearing, and more particularly to a cage and a roller bearing in which abnormal noise due to self-excited vibration of the roller is hardly generated in a no-load state.
[0002]
[Prior art]
For example, in a needle roller bearing used in an automobile mission, in general, as shown in FIG. 3 (A), a main part axis parallel sectional view and in FIG. Using the cages 31 in which the pockets 31a are formed at a constant pitch in the circumferential direction, the rollers 31 are held in the respective pockets 31a so as to be integrated with each other. The assembly 33 including the cage 31 and the plurality of rollers 32 is an annular space 36 formed between the inner ring 34 and the outer ring 35, or a so-called cage and roller type having no inner ring and outer ring. Thus, the rollers 32 in the pockets 31a are arranged in a freely rollable state in an annular space formed between the shaft 37 and a hole formed in the member 38 rotatable relative to the shaft. .
[0003]
In the annular space 36 between the inner ring 34 and the outer ring 35, or in the annular space formed between the shaft 37 and the hole formed in the member 38 rotatable relative to the shaft, the cage 31 and 32 are provided. As shown in FIG. 3A, the position of the assembly 33 in the axial direction is regulated by a side plate 37a fixed to the shaft 37 together with the inner ring 34 or a step portion formed on the shaft 37. Yes.
[0004]
[Problems to be solved by the invention]
By the way, when the needle roller bearing as described above is used in the above-mentioned automobile mission, etc., when it is used in a state where there is a possibility that the load is not applied from the outside, that is, in a no-load state, The rotational speed of the cage, in other words, the revolution speed of the roller may change abruptly during use. At that time, the cage or the roller may self-excited to generate a large vibration or annoying sound.
[0005]
The present invention has been made in view of such circumstances, and an object of the present invention is to provide a roller bearing capable of suppressing the generation of vibration and noise associated with self-excited vibration that occurs during rotation in a no-load state.
[0006]
In order to achieve the above object, a roller bearing of the present invention is a roller bearing comprising a plurality of rollers and a cage formed with a plurality of pockets for holding the rollers at a constant pitch in the circumferential direction.
The axial end surface of the cage is in contact with a side plate or a shaft step provided so as not to rotate relative to the inner ring, thereby restricting the axial position of the assembly including the cage and the plurality of rollers. And the area of the axial end face of the cage is such that the rolling force of the roller is such that the rotating force of the assembly with respect to the outer ring is sufficiently larger than the rotating force of the assembly with respect to the inner ring. It is characterized by being 40% or less of the cross-sectional area perpendicular to the axis.
[0007]
The present invention has been made as a result of earnestly studying the behavior of a cage and roller assembly when a roller bearing such as a needle roller bearing rotates in an unloaded state. A mechanism for generating excitation vibration, in other words, a mechanism for generating abnormal noise will be described.
[0008]
The self-excited vibration of the assembly at the cage is generated when the rotational speed of the assembly is abruptly changed due to a loss of balance between the accompanying force of the assembly with respect to the inner ring and the accompanying force with respect to the outer ring.
[0009]
As shown in the cross-sectional view perpendicular to the axis in FIG. 2, an assembly 33 including a cage 31 and a plurality of rollers 32 held in each pocket 31 a is formed between an inner ring 34 and an outer ring 35. The inner ring 34 is fixed and the outer ring 35 rotates, and the assembly 33 has a force Q to rotate around the outer ring 35 and an inner ring 34. A force F (in this case, the number of rotations of the inner ring 34) to try to rotate is exerted. These Q and F can be expressed as follows.
[0010]
Q = Effect of centrifugal force generated on the roller 32 + friction force between the retainer 31 and the outer ring 35 + inertial force of the roller 32 + inertial force of the retainer 31 (1)
It is represented by Here, the frictional force between the cage 31 and the outer ring 35 is a viscous resistance of a lubricant interposed between the outer circumferential surface of the cage 31 and the inner circumferential surface of the outer ring 35.
[0011]
F = Contact resistance between the roller 32 and the inner ring + Friction force between the cage 31 and the side plate 37 + Friction force between the cage 31 and the inner ring 34 (2)
It is represented by Here, the frictional force between the cage 31 and the side plate 37 is a viscous resistance of a lubricant interposed between the end surface (axial end surface) of the cage 31 and the side plate 37, and the cage 31, the inner ring 34, The frictional force is the viscous resistance of the lubricant interposed between the inner peripheral surface of the cage 31 and the outer peripheral surface of the inner ring 34.
[0012]
In the formula (1),
Influence of centrifugal force generated on roller 32 = Z · μ 1 · f
Friction force between cage 31 and outer ring 35 = η · A 1 · ν 1 · / h 1
Further, in the equation (2),
Frictional force between cage 31 and side plate 37 = η · A 2 · ν 2 · / h 2
Frictional force between cage 31 and inner ring 34 = η · A 3 · ν 3 · / h 3
It is. here,
[0013]
Z: Number of rollers 32 μ 1 : Friction coefficient between rollers 32 and outer ring 35 f: Centrifugal force per roller 32 η: Viscosity coefficient of lubricant A 1 : Contact between outer peripheral surface of cage 31 and outer ring 35 Area ν 1 : Peripheral speed of inner peripheral surface of outer ring 35 h 1 : Lubricant oil film thickness between outer peripheral surface of retainer 31 and inner peripheral surface of outer ring 35 A 2 : Contact between end surface of retainer 31 and side plate 37 Area ν 2 : Peripheral speed of end surface of cage 31 h 2 : Lubricant oil film thickness between end surface of cage 31 and side plate 37 A 3 : Contact area between inner circumferential surface of cage 31 and outer circumferential surface of inner ring 34 ν 3 : Peripheral speed of the inner peripheral surface of the cage 31 h 3 : Lubricant oil film thickness between the inner peripheral surface of the cage 31 and the outer peripheral surface of the inner ring 34.
[0014]
From the above, the equation (1) is expressed as follows: Q = Z · μ 1 · f + η · A 1 · ν 1 / h 1 + Inertial force of roller 32 + Inertial force of cage 31 (3)
F = contact resistance between the roller 32 and the inner ring 34 + η · A 2 · ν 2 / h 2
+ Η ・ A 3・ ν 3 / h 3・ ・ ・ ・ （4）
It becomes.
[0015]
Here, the inertial force of the roller 32 and the inertial force of the cage 31 in the expression (3) are considered to be factors that are influenced during rapid acceleration / deceleration. Further, the contact resistance between the roller 32 and the inner ring 34 in the equation (4) is considered to be constant in any case.
[0016]
Now, the behavior of the assembly 33 of the cage 31 and 32 in the no-load state is based on the force Q that the assembly 33 tries to rotate with the outer ring 35 and the force that the assembly 33 tries to rotate with the inner ring 34 (here, the rotational speed of the inner ring 34). 0) Determined by the magnitude relationship of F. That is, if Q >> F, the rotational speed of the assembly 33 of the cage 31 and 32 is approximately equal to the rotational speed of the outer ring 35, and the rotational fluctuation of the assembly 33 is reduced. Further, if Q << F, the rotational speed of the cage 31 ≈ the rotational speed of the outer ring 35/2 (the revolution speed of the roller 32 when the roller 32 does not slip). In any of these cases, it is estimated that the occurrence frequency of abnormal noise is extremely low. Further, if Q≈F, the rotational speed of the retainer 31 is approximately equal to the rotational speed / 2 of the outer ring 35 even in this case. However, since the magnitude relationship between Q and F is easily reversed, the rotational fluctuation of the retainer 31 is It is large and the frequency of occurrence of abnormal noise is estimated to increase.
[0017]
Accordingly, in order to achieve the above-described purpose, Q >> F or Q << F may be used. In view of the terms on the right side of equations (3) and (4), each term on the right side of equation (4) It is practical to rotate the assembly 33 of the cage 31 and 32 around the outer ring 35 by reducing any of the above and reducing F so that Q >> F. More specifically, as in the invention according to claim 1, the area of both axial end faces of the cage is reduced to 40% or less of the axial orthogonal cross-sectional area of the roller rolling space (annular space 36). A configuration in which F is reduced can be suitably employed by reducing the contact area A 2 between the end surface of the cage 31 and the side plate 37 and reducing the second term on the right side of the equation (4).
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
1A and 1B are explanatory views of an embodiment of the present invention, in which FIG. 1A is a cross-sectional view of a principal part axis, and FIG.
[0019]
The cage 1 has a plurality of pockets 1a for accommodating the rollers 2, and the rollers 2 are rotatably held in the pockets 1a, so that the rollers 2 have a constant pitch in the circumferential direction. It will be in the state held by. The assembly 3 composed of the cage 1 and the plurality of rollers 2 has an inner ring 4 and an outer ring 5 that are press-fitted into the shaft 7 or an inner ring 4 and an outer ring 5 as shown in FIG. If not, it is accommodated in an annular space 6 formed between the shaft 7 and a hole formed in the center of the rotating member 8 such as a gear.
[0020]
Further, the position of the assembly 3 in the axial direction is restricted by the both ends of the cage 1 coming into contact with the side plate 7a (or a step formed on the shaft) fixed to the shaft into which the inner ring 4 is press-fitted. Is done.
[0021]
The feature of this embodiment is that, as shown in FIG. 1 (A), by forming relatively large chamfered portions 11 at both ends of the cage 1, the area of both ends can be reduced to the rolling space of the rollers 2. As shown in FIG. 1B, the space shape of each pocket 1a is such that the outer circumferential side of the cage 1 has a dimension in the circumferential direction that is less than 40% of the axial cross-sectional area of the annular space 6 that is The dimension L in the outer peripheral portion in the circumferential direction is 105% or more of the diameter D of the roller 2, more specifically, a range of 105 to 115%.
[0022]
According to the configuration of the above embodiment, since the area of both end faces of the cage 1 is 40% or less of the axial orthogonal cross-sectional area of the annular space 6, both ends of the cage 1 and the side plate 7a (or the shaft 7) The contact area with the step portion to be formed is reduced, and the second term on the right side of the above-described equation (4) is reduced. Further, since each pocket 1a is made wider toward the outer peripheral side of the cage 1, when the outer ring 5 is rotated in a no-load state, each roller 2 is easily moved to the outer ring 5 side. The contact resistance between the roller 2 and the inner ring 4 in the first term on the right side of the equation (4) becomes small.
[0023]
As a result of the above, the assembly 3 of the cage 1 has a chamfered portion 11 formed at both ends of the cage 1 and the space shape of the pocket 1a. The accompanying force F of the assembly 3 with respect to the inner ring 4 (dragging force with respect to the inner ring 4) F decreases, and the relationship with the accompanying force Q with respect to the outer ring 5 (drag force with respect to the outer ring 5) Q becomes Q >> F. Therefore, when the outer ring 5 is rotating in a no-load state, the assembly 3 of the cage 1 and 2 is mainly rotated along with the outer ring 5, and the rotation speed is stable and substantially equal to the rotation speed of the outer ring 4. Therefore, the assembly 3 does not generate self-excited vibration due to rotational fluctuation, and does not generate abnormal noise or vibration.
[0024]
Incidentally, in the above embodiment, configuration and hold device for the area of the end faces of the retainer 1, which is a characteristic configuration of the invention according to claim 1 or less 40% of the axial orthogonal cross-sectional area of the annular space 6 Although the space shape of each pocket 1a is made wider toward the outer peripheral side of the cage 1 and the maximum circumferential dimension L is set to 105% or more of the diameter D of the roller 2, both of the configurations of the cage 1 are adopted . Even if only the configuration in which the area of both end faces is 40% or less of the axial cross-sectional area of the annular space 6 can be reduced, the follower force F against the inner ring 4 of the assembly 3 can be reduced, and therefore in the no-load state. The effect which suppresses the self-excited vibration of the assembly 3 can be show | played.
[0025]
Moreover, in the above embodiment, although the example which applied this invention to the roller bearing which has arrange | positioned the assembly 3 of the holder | retainer 1 and 2 between the inner ring | wheel 4 and the outer ring | wheel 5 was shown, Of course, the present invention can be equally applied to a so-called cage-and-roller type roller bearing in which the inner ring and the outer ring are omitted by being inserted between the rotary member 7 and a rotating member 8 such as a gear rotating therearound.
[0026]
【The invention's effect】
As described above, according to the present invention, the area of both axial end faces of the cage is set to 40% or less of the axial orthogonal cross-sectional area of the rolling space (annular space) of the roller, whereby the assembly of the cage is assembled. Since the rotational force (drag force) F with respect to the inner ring (or shaft) is reduced, and the relationship with the rotational force Q with respect to the outer ring of the assembly is Q >> F, the outer ring rotates in a no-load state. When the cage assembly is rotated mainly with respect to the outer ring, the rotation speed is stable and substantially equal to the rotation speed of the outer ring, and the balance between the rotation force for the inner ring and the rotation force for the outer ring is lost. Therefore, it is possible to prevent the occurrence of abnormal noise and vibration due to the occurrence of self-excited vibration.
[Brief description of the drawings]
FIGS. 1A and 1B are explanatory views of an embodiment of the present invention, in which FIG. 1A is a cross-sectional view of a principal part axis, and FIG.
FIG. 2 is an explanatory diagram of the principle of the present invention, and is a cross-sectional view perpendicular to the main axis of a roller bearing in which a gap is exaggerated.
FIGS. 3A and 3B are explanatory views of a configuration example of a needle roller bearing used in an automobile mission or the like, in which FIG. 3A is a cross-sectional view of an essential part axis, and FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Cage 1a Pocket 11 Chamfer 2 Roller 3 Assembly 4 Inner ring 5 Outer ring 6 Annular space 7 Shaft 7a Side plate 8 Rotating member

Claims (1)

複数のころと、その各ころを周方向に一定のピッチで保持する複数のポケットが形成されてなる保持器を備えたころ軸受において、
上記保持器の軸方向端面が、内輪に対して相対回転不能に設けられている側板もしくは軸の段部に当接して当該保持器と上記複数のころからなる組立体の軸方向位置を規制するよう構成されているとともに、上記組立体の外輪に対する連れ回り力が、内輪に対する連れ回り力に比して十分に大きくなるように、上記保持器の軸方向端面の面積が、ころの転動空間の軸直交断面積の４０％以下とされていることを特徴とするころ軸受。In a roller bearing comprising a plurality of rollers and a cage formed with a plurality of pockets for holding the rollers at a constant pitch in the circumferential direction,
The axial end surface of the cage is in contact with a side plate or a shaft step provided so as not to rotate relative to the inner ring, thereby restricting the axial position of the assembly including the cage and the plurality of rollers. And the area of the axial end face of the cage is such that the rolling force of the roller is such that the rotating force of the assembly with respect to the outer ring is sufficiently larger than the rotating force of the assembly with respect to the inner ring. A roller bearing characterized by being 40% or less of the cross-sectional area perpendicular to the axis.
JP2000269851A 2000-09-06 2000-09-06 Roller bearing Expired - Fee Related JP4582271B2 (en)

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KR100925071B1 (en) * 2005-01-31 2009-11-04 닛본 세이고 가부시끼가이샤 Thin-wall bearing
JP2015059592A (en) * 2013-09-18 2015-03-30 Ntn株式会社 Bearing structure
JP6645378B2 (en) * 2016-08-03 2020-02-14 日本精工株式会社 Ball bearings and spindle devices for machine tools
JP6714856B2 (en) * 2016-08-03 2020-07-01 日本精工株式会社 Ball bearings and spindle devices for machine tools

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JPH053643U (en) * 1991-07-03 1993-01-19 光洋精工株式会社 Needle roller bearings for gear inner
JPH0678627U (en) * 1993-02-25 1994-11-04 日本トムソン株式会社 Roller with cage
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CN108708958A (en) * 2017-02-07 2018-10-26 通用电气公司 The gear of roller element stress with reduction and the method for manufacturing this type gear
CN108708958B (en) * 2017-02-07 2022-09-27 通用电气公司 Gear with reduced roller element stress and method of making such gear

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