JP2000230559A - Bearing assembly - Google Patents
Bearing assemblyInfo
- Publication number
- JP2000230559A JP2000230559A JP3077999A JP3077999A JP2000230559A JP 2000230559 A JP2000230559 A JP 2000230559A JP 3077999 A JP3077999 A JP 3077999A JP 3077999 A JP3077999 A JP 3077999A JP 2000230559 A JP2000230559 A JP 2000230559A
- Authority
- JP
- Japan
- Prior art keywords
- inner ring
- flange
- bearing assembly
- oil groove
- flange portion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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
- F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
- F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
- F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
-
- 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
-
- 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
- F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
-
- 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
- F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、軸受組立体に関
し、例えば自動車のトランスミッションなどに使用され
る軸受組立体に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing assembly, and more particularly, to a bearing assembly used for an automobile transmission.
【0002】[0002]
【従来の技術】内輪外周に鍔部を設けた軸受組立体が知
られている。かかる鍔部は、例えばころなどの転動体が
軸線方向に移動しないように機能するものである。とこ
ろで、このような軸受組立体を複列にして用いる場合、
鍔部同士が直接もしくは間座等を介して突き合わされる
ことが多い。かかる場合、突き合わされた状態でも転動
体や軌道面の潤滑を確保できるよう、鍔部の一部を切り
欠いて内輪の内外周を連通させ、それにより潤滑油を通
過可能とする油溝を形成することが通常行われている。2. Description of the Related Art A bearing assembly having a flange on the outer periphery of an inner ring is known. Such a flange portion functions to prevent a rolling element such as a roller from moving in the axial direction. By the way, when using such a bearing assembly in a double row,
The flanges are often butted directly or via a spacer. In such a case, a part of the flange is cut off to communicate the inner and outer peripheries of the inner ring so that the lubrication of the rolling elements and the raceway surface can be ensured even in the abutted state, thereby forming an oil groove through which lubricating oil can pass. That is usually done.
【0003】[0003]
【発明が解決しようとする課題】ところで、このような
油溝は、鍔部の一部を切り欠いて形成されるものである
から、油溝の軸線方向深さ分だけ、鍔部の厚さが薄くな
ることとなる。一方、軸受の長寿命化を図るため、所定
の硬度を得るべく内輪は熱処理が施されており、よって
衝撃に対し脆いという特性を有する。Since such an oil groove is formed by cutting a part of the flange, the thickness of the flange is increased by the axial depth of the oil groove. Becomes thinner. On the other hand, in order to extend the life of the bearing, the inner ring is heat-treated to obtain a predetermined hardness, and thus has the property of being brittle against impact.
【0004】ところが、軸受の組立作業は自動化がすす
み、内輪などの構成要素は自動搬送されることが多くな
っているので、搬送中における内輪同士の衝接や、内輪
受け渡し時における衝撃などが生じやすい状態となって
いる。しかるに、油溝が形成されているため一部が薄く
なっている内輪の鍔部には、搬送時の衝撃により応力が
過大となり割れ・欠けなどが生じる恐れがある。割れ・
欠けなどが生じた内輪は、製品として使用できないもの
であるため、検査段階で排除され、それにより歩留まり
が悪化するという不具合が生じる。However, assembling of the bearings has been automated, and components such as the inner ring are often transported automatically, so that the inner rings come into contact with each other during the transport and an impact occurs when the inner ring is delivered. It is in an easy state. However, there is a possibility that the stress at the time of conveyance causes excessive stress at the flange portion of the inner ring, which is partially thinned due to the formation of the oil groove, causing cracks or chipping. Crack
Since the inner ring in which chipping or the like has occurred cannot be used as a product, it is removed at the inspection stage, thereby causing a problem that the yield is deteriorated.
【0005】このような不具合を防止するためには、内
輪をより丁寧に搬送できるよう自動搬送システムを改良
することが考えられるが、かかる改良には多額の費用が
かかると共に、搬送中の衝接を完全になくすことは困難
であるといえる。一方、油穴の深さを浅くすることによ
って、鍔部の十分な厚さを確保することも考えられる
が、それにより潤滑油の通路面積が縮小し、十分な潤滑
効果を得られない恐れがあるという新たな問題を生じさ
せる。In order to prevent such a problem, it is conceivable to improve the automatic transport system so that the inner ring can be transported more carefully. However, such an improvement requires a large amount of cost and a collision during transport. It can be said that it is difficult to completely eliminate. On the other hand, it is conceivable to secure a sufficient thickness of the flange portion by reducing the depth of the oil hole, but this may reduce the passage area of the lubricating oil and may not obtain a sufficient lubricating effect. Raises a new problem.
【0006】そこで本発明は、十分なる潤滑作用を確保
しながらも、信頼性の向上した軸受組立体を提供するこ
とを目的とする。Accordingly, an object of the present invention is to provide a bearing assembly with improved reliability while ensuring a sufficient lubricating action.
【0007】[0007]
【課題を解決するための手段】本発明の軸受組立体は、
内輪と、外輪と、前記内輪と前記外輪との間に配置され
た転動体とからなり、前記内輪の端部に鍔部が形成され
た軸受組立体において、前記鍔部には、前記内輪の内周
と外周とを連通する切欠が形成されており、前記鍔部の
外周面には、少なくとも前記切欠の一部を含んでなる逃
げ部が形成されている。SUMMARY OF THE INVENTION A bearing assembly according to the present invention comprises:
In a bearing assembly comprising an inner ring, an outer ring, and a rolling element disposed between the inner ring and the outer ring, wherein a flange portion is formed at an end of the inner ring, the flange portion includes A notch communicating the inner periphery and the outer periphery is formed, and a relief portion including at least a part of the notch is formed on the outer peripheral surface of the flange.
【0008】更に、本発明の軸受組立体は、内輪と、外
輪と、前記内輪と前記外輪との間に配置された転動体と
からなり、前記内輪の端部に鍔部が形成された軸受組立
体において、前記鍔部には、前記内輪の内周と外周とを
連通する切欠が形成されており、前記切欠の内輪軸線方
向深さは、前記鍔部の内輪軸線方向厚さ以上に設定され
ている。Further, a bearing assembly according to the present invention comprises an inner race, an outer race, and a rolling element disposed between the inner race and the outer race, wherein a flange is formed at an end of the inner race. In the assembly, a notch communicating with the inner and outer circumferences of the inner ring is formed in the flange, and the inner ring axial direction depth of the notch is set to be equal to or greater than the inner ring axial direction thickness of the flange. Have been.
【0009】[0009]
【作用】本発明にかかる軸受組立体によれば、前記鍔部
には、前記内輪の内周と外周とを連通する切欠が形成さ
れており、前記鍔部の外周面には、少なくとも前記切欠
の一部を含んでなる逃げ部が形成されているので、例え
ば前記内輪の搬送時に、前記鍔部同士が衝接したとして
も、前記切欠が形成されたことによって薄厚となった前
記鍔部の部分は、前記逃げ部が形成されたことによって
相手側から強い力を受ける恐れが少なくなり、それによ
り前記鍔部の割れや欠けを抑止することができる。尚、
逃げ部を大きく形成すれば、鍔部における薄厚の部分を
排除することも可能である。According to the bearing assembly of the present invention, the flange is formed with a notch communicating the inner circumference and the outer circumference of the inner ring, and the outer circumference of the flange is formed with at least the notch. Is formed, so that, for example, when the inner ring is conveyed, even if the flanges come into contact with each other, the notch is formed so that the thickness of the flange is reduced. The portion is less likely to receive a strong force from the counterpart due to the formation of the escape portion, and thereby it is possible to prevent the flange portion from being cracked or chipped. still,
If the relief portion is formed to be large, it is possible to eliminate a thin portion in the flange portion.
【0010】更に、本発明にかかる軸受組立体によれ
ば、前記鍔部には、前記内輪の内周と外周とを連通する
切欠が形成されており、前記切欠の内輪軸線方向深さ
は、前記鍔部の内輪軸線方向厚さ以上に設定されている
ので、前記切欠の形成により前記鍔部は厚さ方向にわた
って削除され、結果として薄厚の部分が存在しなくなる
ので、例えば前記内輪の搬送時に、前記鍔部同士が衝接
したとしても、前記鍔部の割れや欠けを抑止することが
できる。Further, according to the bearing assembly of the present invention, the flange is formed with a notch communicating the inner circumference and the outer circumference of the inner ring, and the notch has a depth in the axial direction of the inner ring. Since the thickness of the flange portion is set to be equal to or greater than the thickness of the inner ring in the axial direction, the formation of the notch removes the flange portion in the thickness direction, and as a result, a thin portion does not exist. Even if the flanges come into contact with each other, cracking and chipping of the flanges can be suppressed.
【0011】[0011]
【発明の実施の形態】以下、図面を参照して本発明の実
施の形態について詳細に説明する。図1は、本発明にか
かる第1の実施の形態による軸受組立体10の軸線方向
断面図である。固定部Fの内周に外輪11が嵌合的に取
り付けられている。外輪11の内周面11aは、軸線方
向中央において最小径となり、両端に行くに従い拡径す
る二重テーパ形状を有している。外輪11の内方には、
一対の内輪12,13が同軸に配置的されている。回転
軸Rの外周に嵌合的に取り付けられた内輪12,13
は、同一形状を有しているが、図1においては互いに鏡
像の関係となるように配置されている。Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is an axial sectional view of a bearing assembly 10 according to a first embodiment of the present invention. An outer ring 11 is fitted on the inner periphery of the fixed portion F in a fitting manner. The inner peripheral surface 11a of the outer race 11 has a double tapered shape that has a minimum diameter at the center in the axial direction and increases in diameter toward both ends. Inside the outer ring 11,
A pair of inner rings 12, 13 are arranged coaxially. Inner rings 12, 13 fitted to the outer periphery of the rotation shaft R
Have the same shape, but are arranged in a mirror image relationship with each other in FIG.
【0012】内輪12,13は、図1においてはそれぞ
れ軸線方向外側端に配置され、かつ半径方向に突出する
大鍔部12a、13aと、それぞれ軸線方向内側端に配
置され、かつ半径方向にわずかに突出する小鍔部12
b、13bと、大鍔部12a、13aと小鍔部12b、
13bとの間にそれぞれ形成されたテーパ面12c、1
3cとを有している。In FIG. 1, the inner rings 12 and 13 are respectively disposed at axially outer ends and are protruded in the radial direction and large flanges 12a and 13a, respectively, and are disposed at axially inner ends and slightly radially. Small flange 12 protruding from
b, 13b, large collar portions 12a, 13a and small collar portion 12b,
13b and tapered surfaces 12c, 1
3c.
【0013】外輪11の内周面11aと、内輪12,1
3のテーパ面12c、13cとの間には、複数(本実施
の形態においては25個)の円錐ころ14,15が転動
自在に配置されている。円錐ころ14,15をそれぞれ
周方向に等間隔に支持すべく、保持器16,17がそれ
ぞれ外輪11と内輪12,13との間に配置されてい
る。The inner peripheral surface 11a of the outer race 11 and the inner races 12, 1
Between the three tapered surfaces 12c and 13c, a plurality (25 in the present embodiment) of tapered rollers 14 and 15 are arranged so as to roll freely. In order to support the tapered rollers 14 and 15 at equal intervals in the circumferential direction, retainers 16 and 17 are arranged between the outer ring 11 and the inner rings 12 and 13, respectively.
【0014】図2は、図1に示す軸受組立体10の内輪
13と、円錐ころ15と、一部のみ示す保持器17とを
組み付けた状態で、矢印II方向に見た図である。図3
は、図2に示す内輪13を矢印III方向に見た図であ
る。図4は、図2に示す内輪13のIV部を拡大して示す
図である。尚、上述したように、内輪12、13は同一
形状を有するため、主として内輪13の構成のみを説明
し、内輪12については説明を省略する。FIG. 2 is a view of the bearing assembly 10 shown in FIG. 1 in a state where the inner ring 13, the tapered rollers 15, and the retainer 17, which is shown only partially, are assembled and viewed in the direction of arrow II. FIG.
FIG. 3 is a view of the inner ring 13 shown in FIG. FIG. 4 is an enlarged view showing an IV portion of the inner ring 13 shown in FIG. As described above, since the inner rings 12 and 13 have the same shape, only the configuration of the inner ring 13 will be mainly described, and the description of the inner ring 12 will be omitted.
【0015】図2に示すように、小鍔部13bには、円
周方向に沿って等間隔に3つの油溝13d(内輪12に
は油溝12d)が設けられている。油溝13dは、小鍔
部13bの端面の一部を部分円筒面状に切り欠いて形成
されている(図1参照)。かかる油溝13dは、小鍔部
13bを内輪12の小鍔部12bに突き合わせたとき
に、内輪13(内輪12)の外周側と内周側とを連通し
て、潤滑油の通過を許容する潤滑油路を確保するという
機能を有する。尚、図3に示すように、本実施の形態に
おいては、油溝13dの(内輪)軸線方向深さdpは、
小鍔部13bの(内輪)軸線方向厚さtより小さく設定
されている。As shown in FIG. 2, the small flange portion 13b is provided with three oil grooves 13d (oil grooves 12d on the inner ring 12) at equal intervals along the circumferential direction. The oil groove 13d is formed by cutting a part of the end face of the small flange 13b into a partially cylindrical shape (see FIG. 1). When the small flange portion 13b abuts against the small collar portion 12b of the inner ring 12, the oil groove 13d communicates the outer peripheral side and the inner peripheral side of the inner ring 13 (the inner ring 12) to allow the passage of lubricating oil. It has the function of securing a lubricating oil passage. As shown in FIG. 3, in the present embodiment, the (deep) axial depth dp of the oil groove 13d is:
The thickness is set smaller than the thickness t of the small flange portion 13b in the axial direction (inner ring).
【0016】図4において、従来技術による小鍔部の形
状を点線で示しており、一方、本実施の形態による小鍔
部13bの形状を実線で示している。図3,4から明ら
かなように、本実施の形態においては、小鍔部13bの
外周面を油溝13dの部分でそぎ落とし、それにより逃
げ部13eを形成している。In FIG. 4, the shape of the small collar portion according to the prior art is shown by a dotted line, while the shape of the small collar portion 13b according to the present embodiment is shown by a solid line. As is clear from FIGS. 3 and 4, in the present embodiment, the outer peripheral surface of the small flange portion 13b is cut off at the oil groove 13d, thereby forming a relief portion 13e.
【0017】図3を参照して説明したように、小鍔部1
3bの軸線方向厚さtと、油溝13dの深さdpとの関
係から、小鍔部13bの油溝13dにおける軸線方向最
小厚さは(t−dp)となる。ここで、油溝13dを通
過する潤滑油の量をある程度確保しようとすると、その
深さdpを大きくする必要がある。しかしながら、それ
により小鍔部13bの油溝13dにおける軸線方向最小
厚さ(t−dp)が薄くなって、搬送時等において割れ
や欠け生じる恐れがある。As described with reference to FIG.
From the relationship between the axial thickness t of 3b and the depth dp of the oil groove 13d, the minimum axial thickness of the small flange portion 13b in the oil groove 13d is (t-dp). Here, in order to secure a certain amount of the lubricating oil passing through the oil groove 13d, it is necessary to increase the depth dp. However, the axial minimum thickness (t-dp) in the oil groove 13d of the small flange portion 13b is thereby reduced, and there is a possibility that cracks or chips may occur during transportation or the like.
【0018】そこで、本実施の形態においては、逃げ部
13eを形成することによって、小鍔部13bの外周面
を油溝13dの部分で、値Eだけ内方にへこませてい
る。従って、例えば搬送時において、小鍔部13bが他
の部材や搬送ガイド等に衝接するようなことがあったと
しても、油溝13dの部分が直接衝接する恐れは低く、
それにより小鍔部13bの割れや欠けを抑止することが
できる。Therefore, in the present embodiment, by forming the escape portion 13e, the outer peripheral surface of the small flange portion 13b is depressed inward by the value E at the oil groove 13d. Therefore, for example, at the time of conveyance, even if the small flange portion 13b may come into contact with another member, a conveyance guide, or the like, the possibility that the oil groove 13d directly abuts is low,
Thereby, cracking and chipping of the small flange 13b can be suppressed.
【0019】図5は、第1の実施の形態の変形例を示す
図1と同様な断面図である。本変形例が、第1の実施の
形態と異なるのは、外輪が2つ(外輪11A、11B)
に分割されている点である。従って、外輪11A11B
と、第1の実施の形態と同様な構成を有する内輪12,
13等とで、2つの軸受組立体20,21が形成されて
なる。FIG. 5 is a sectional view similar to FIG. 1 showing a modification of the first embodiment. This modification is different from the first embodiment in that there are two outer rings (outer rings 11A and 11B).
This is the point that is divided into Therefore, the outer ring 11A11B
And an inner ring 12 having a configuration similar to that of the first embodiment.
13 and the like form two bearing assemblies 20, 21.
【0020】外輪11A、11Bは、固定部Fに設置さ
れたスナップリング22を介して対向配置されている。
また内輪12,13は、円管状の間座23を介して小鍔
部同士を対向させている。内輪12,13の内方端面が
間座23に当接した状態でも、潤滑油路を確保すべく、
本変形例においても油溝12d、13dが形成されてい
る。かかる油溝12d、13dには、第1の実施の形態
と同様に逃げ部(図4参照)が形成されているので、例
えば搬送時において、小鍔部が他の部材や搬送ガイド等
に衝接するようなことがあったとしても、小鍔部の割れ
や欠けを抑止することができる。The outer races 11A and 11B are opposed to each other via a snap ring 22 installed on the fixing portion F.
The inner rings 12 and 13 have their small flanges facing each other via a circular spacer 23. Even in a state where the inner end faces of the inner rings 12 and 13 are in contact with the spacer 23, in order to secure a lubricating oil passage,
Also in this modified example, oil grooves 12d and 13d are formed. In the oil grooves 12d and 13d, a relief portion (see FIG. 4) is formed as in the first embodiment, so that, for example, at the time of transport, the small flange portion comes into contact with another member or a transport guide. Even if it touches, cracking or chipping of the small flange can be suppressed.
【0021】図6は、第2の実施の形態の変形例を示す
図1と同様な断面図である。図7は、図6に示す内輪を
上方から見た図である。図8は、図7に示す内輪のVIII
部を拡大して示す図である。FIG. 6 is a sectional view similar to FIG. 1 showing a modification of the second embodiment. FIG. 7 is a view of the inner race shown in FIG. 6 as viewed from above. FIG. 8 shows the inner ring VIII shown in FIG.
It is a figure which expands and shows a part.
【0022】第2の実施の形態が、第1の実施の形態と
異なるのは、油溝33dの形状である。第1の実施の形
態における油溝13d(図3)の深さは、従来技術の油
溝の深さに等しく設定されているが、第2の実施の形態
においては、かかる深さを値Sだけ増大させている。The second embodiment differs from the first embodiment in the shape of the oil groove 33d. The depth of the oil groove 13d (FIG. 3) in the first embodiment is set to be equal to the depth of the oil groove of the related art, but in the second embodiment, the depth is set to a value S. Only increase.
【0023】より具体的には、図8において、従来技術
による油溝の形状を点線で示しており、一方、本実施の
形態による油溝33dの形状を実線で示している。図8
に示すように、小鍔部33bの軸線方向厚さをTとし、
油溝33dの深さをDpとすると、T<Dpとなってお
り、すなわち小鍔部33bは、油溝33dにより分断さ
れ、結果として油溝33dの範囲内では小鍔部33bが
除去されている。More specifically, in FIG. 8, the shape of the oil groove according to the prior art is shown by a dotted line, while the shape of the oil groove 33d according to the present embodiment is shown by a solid line. FIG.
As shown in the figure, the thickness in the axial direction of the small collar portion 33b is T,
Assuming that the depth of the oil groove 33d is Dp, T <Dp, that is, the small flange 33b is divided by the oil groove 33d. As a result, the small flange 33b is removed within the range of the oil groove 33d. I have.
【0024】従って、従来技術によれば、油溝を形成す
ることによって薄厚となった小鍔部に割れや欠けの恐れ
があるが、本実施の形態によれば、割れや欠けが生じや
すい小鍔部の薄厚の部分を予め除去しているので、例え
ば搬送時における衝接などに起因する内輪の破損を極力
抑止することができる。Therefore, according to the prior art, there is a possibility that the small flange portion which is thinned by forming the oil groove may be cracked or chipped. However, according to the present embodiment, the small flange portion is liable to be cracked or chipped. Since the thin portion of the flange is removed in advance, damage to the inner ring due to, for example, abutment during transport can be suppressed as much as possible.
【0025】以上、本発明を実施の形態を参照して説明
してきたが、本発明は上記実施の形態に限定して解釈さ
れるべきではなく、適宜変更・改良が可能であることは
もちろんである。たとえば、本実施の形態では、油溝は
等間隔に3箇所設けられているが、2箇所以下あるいは
4箇所以上設けることも可能である。As described above, the present invention has been described with reference to the embodiments. However, the present invention should not be construed as being limited to the above embodiments, and it is needless to say that modifications and improvements can be made as appropriate. is there. For example, in the present embodiment, three oil grooves are provided at equal intervals, but two or less oil grooves may be provided or four or more oil grooves may be provided.
【0026】[0026]
【発明の効果】本発明にかかる軸受組立体によれば、前
記鍔部には、前記内輪の内周と外周とを連通する切欠が
形成されており、前記鍔部の外周面には、少なくとも前
記切欠の一部を含んでなる逃げ部が形成されているの
で、例えば前記内輪の搬送時に、前記鍔部同士が衝接し
たとしても、前記切欠が形成されたことによって薄厚と
なった前記鍔部の部分は、前記逃げ部が形成されたこと
によって相手側から強い力を受ける恐れが少なくなり、
それにより前記鍔部の割れや欠けを抑止することができ
る。尚、逃げ部を大きく形成すれば、鍔部における薄厚
の部分を排除することも可能である。According to the bearing assembly of the present invention, the flange is formed with a notch communicating the inner circumference and the outer circumference of the inner ring, and the outer circumference of the flange is provided with at least a notch. Since the relief portion including a part of the notch is formed, for example, even when the inner ring is conveyed, even if the flange portions abut each other, the thickness of the flange is reduced by the formation of the notch. The portion of the portion is less likely to receive a strong force from the other side due to the formation of the escape portion,
Thereby, cracking and chipping of the flange can be suppressed. In addition, if the relief portion is formed to be large, it is possible to eliminate a thin portion in the flange portion.
【0027】更に、本発明にかかる軸受組立体によれ
ば、前記鍔部には、前記内輪の内周と外周とを連通する
切欠が形成されており、前記切欠の内輪軸線方向深さ
は、前記鍔部の内輪軸線方向厚さ以上に設定されている
ので、前記切欠の形成により前記鍔部は厚さ方向にわた
って削除され、結果として薄厚の部分が存在しなくなる
ので、例えば前記内輪の搬送時に、前記鍔部同士が衝接
したとしても、前記鍔部の割れや欠けを抑止することが
できる。Further, according to the bearing assembly of the present invention, the flange portion is formed with a notch communicating the inner circumference and the outer circumference of the inner ring, and the notch has a depth in the axial direction of the inner ring. Since the thickness of the flange portion is set to be equal to or greater than the thickness of the inner ring in the axial direction, the formation of the notch removes the flange portion in the thickness direction, and as a result, a thin portion does not exist. Even if the flanges come into contact with each other, cracking and chipping of the flanges can be suppressed.
【図1】本発明にかかる第1の実施の形態による軸受組
立体10の軸線方向断面図である。FIG. 1 is an axial sectional view of a bearing assembly 10 according to a first embodiment of the present invention.
【図2】図1に示す軸受組立体10の内輪13と、円錐
ころ15と、一部のみ示す保持器17とを組み付けた状
態で、矢印II方向に見た図である。FIG. 2 is a view of the bearing assembly 10 shown in FIG. 1 in a state where an inner ring 13, a tapered roller 15, and a retainer 17, which is shown only in part, are assembled and viewed in the direction of arrow II.
【図3】図2に示す内輪13を矢印III方向に見た図で
ある。FIG. 3 is a view of the inner race 13 shown in FIG. 2 as viewed in the direction of arrow III.
【図4】図2に示す内輪13のIV部を拡大して示す図で
ある。FIG. 4 is an enlarged view showing an IV section of the inner ring 13 shown in FIG. 2;
【図5】第1の実施の形態の変形例を示す図1と同様な
断面図である。FIG. 5 is a sectional view similar to FIG. 1, showing a modification of the first embodiment.
【図6】第2の実施の形態の変形例を示す図1と同様な
断面図である。FIG. 6 is a sectional view similar to FIG. 1, showing a modification of the second embodiment.
【図7】図6に示す内輪を上方から見た図である。7 is a view of the inner race shown in FIG. 6 as viewed from above.
【図8】図8は、図7に示す内輪のVIII部を拡大して示
す図である。FIG. 8 is an enlarged view of a portion VIII of the inner race shown in FIG. 7;
10,20,21,30 軸受組立体 11、31 外輪 12、13,32、33 内輪 13b、33b 小鍔部 12d、13d、33d 油溝 13e 逃げ部 10, 20, 21, 30 Bearing assembly 11, 31 Outer ring 12, 13, 32, 33 Inner ring 13b, 33b Small flange portion 12d, 13d, 33d Oil groove 13e Escape portion
Claims (2)
の間に配置された転動体とからなり、前記内輪の端部に
鍔部が形成された軸受組立体において、 前記鍔部には、前記内輪の内周と外周とを連通する切欠
が形成されており、 前記鍔部の外周面には、少なくとも前記切欠の一部を含
んでなる逃げ部が形成されている軸受組立体。1. A bearing assembly comprising an inner race, an outer race, and a rolling element disposed between the inner race and the outer race, wherein a flange is formed at an end of the inner race. In the bearing assembly, a notch communicating the inner periphery and the outer periphery of the inner ring is formed, and a relief portion including at least a part of the notch is formed on an outer peripheral surface of the flange portion.
の間に配置された転動体とからなり、前記内輪の端部に
鍔部が形成された軸受組立体において、 前記鍔部には、前記内輪の内周と外周とを連通する切欠
が形成されており、 前記切欠の内輪軸線方向深さは、前記鍔部の内輪軸線方
向厚さ以上に設定されている軸受組立体。2. A bearing assembly comprising an inner race, an outer race, and a rolling element disposed between the inner race and the outer race, wherein a flange is formed at an end of the inner race. In the bearing assembly, a notch communicating the inner circumference and the outer circumference of the inner ring is formed, and the depth of the notch in the axial direction of the inner ring is set to be equal to or greater than the thickness of the flange in the axial direction of the inner ring.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3077999A JP2000230559A (en) | 1999-02-09 | 1999-02-09 | Bearing assembly |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3077999A JP2000230559A (en) | 1999-02-09 | 1999-02-09 | Bearing assembly |
Publications (2)
Publication Number | Publication Date |
---|---|
JP2000230559A true JP2000230559A (en) | 2000-08-22 |
JP2000230559A5 JP2000230559A5 (en) | 2005-08-25 |
Family
ID=12313180
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP3077999A Withdrawn JP2000230559A (en) | 1999-02-09 | 1999-02-09 | Bearing assembly |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2000230559A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7036989B2 (en) | 2002-03-29 | 2006-05-02 | Isuzu Motors Limited | Roller bearing oil feed device |
-
1999
- 1999-02-09 JP JP3077999A patent/JP2000230559A/en not_active Withdrawn
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7036989B2 (en) | 2002-03-29 | 2006-05-02 | Isuzu Motors Limited | Roller bearing oil feed device |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP4790341B2 (en) | Needle roller bearing and bearing structure | |
EP1961981B1 (en) | Bearing device for wheel | |
JPWO2006137468A1 (en) | Thrust roller bearing | |
JP2007002914A (en) | Bearing ring split type rolling bearing | |
WO2019026358A1 (en) | Hub unit bearing, method for manufacturing same, motor vehicle, and method for manufacturing same | |
JP2003083339A (en) | Thrust bearing | |
JP2000230559A (en) | Bearing assembly | |
JP2007120591A (en) | Cam follower and roller follower | |
JP3510726B2 (en) | Roller bearing | |
JP2004019731A (en) | Self-aligning roller bearing | |
US10584742B2 (en) | Rolling bearing | |
JPH09236131A (en) | Roller bearing | |
JP2005214330A (en) | Four-point contact ball bearing and manufacturing method thereof | |
US10941811B1 (en) | High-speed bearing | |
JP2009019701A (en) | Split type needle roller bearing | |
US20060222280A1 (en) | Shaft assembly | |
US20090046973A1 (en) | Bearing retention method and apparatus | |
JP2011185364A (en) | Bearing ring for roller bearing, roller bearing, and roller bearing device | |
JP2005069350A (en) | Tapered roller bearing | |
JP2008051161A (en) | Thrust roller bearing | |
JP2008175371A (en) | Sliding tripod type constant velocity joint | |
JP4731198B2 (en) | Roller bearing | |
US11965546B2 (en) | Bearing module for coaxial shaft ends | |
JP2007177800A (en) | Bearing device | |
JP2003322156A (en) | Roller bearing |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
A521 | Written amendment |
Effective date: 20050215 Free format text: JAPANESE INTERMEDIATE CODE: A523 |
|
A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20050215 |
|
A761 | Written withdrawal of application |
Free format text: JAPANESE INTERMEDIATE CODE: A761 Effective date: 20070604 |