JP2002323049A - Rolling bearing - Google Patents
Rolling bearingInfo
- Publication number
- JP2002323049A JP2002323049A JP2001129787A JP2001129787A JP2002323049A JP 2002323049 A JP2002323049 A JP 2002323049A JP 2001129787 A JP2001129787 A JP 2001129787A JP 2001129787 A JP2001129787 A JP 2001129787A JP 2002323049 A JP2002323049 A JP 2002323049A
- Authority
- JP
- Japan
- Prior art keywords
- rolling
- washer
- inner ring
- rolling bearing
- ring
- 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.)
- Pending
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
- 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
- F16C19/36—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 a single row of rollers
- F16C19/364—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 a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
-
- 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
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller 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
- 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
- F16C35/063—Fixing them on the shaft
-
- 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
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/073—Fixing them on the shaft or housing with interposition of an element between shaft and inner race 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
- F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
- F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
-
- 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
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling 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
- 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、転がり軸受、特に
車両の歯車減速装置における歯車軸を回転自在に支持す
る転がり軸受に関する。The present invention relates to a rolling bearing, and more particularly to a rolling bearing for rotatably supporting a gear shaft in a gear reduction device for a vehicle.
【0002】[0002]
【従来の技術】従来、自動車や建設機械等におけるデフ
ァレンシャルやトランスミッション等の歯車減速装置の
歯車軸を回転自在に支持する転がり軸受として、ラジア
ル荷重とアキシアル荷重、およびそれらの合成荷重を負
荷することができる円すいころ軸受が多く用いられてい
る。2. Description of the Related Art Conventionally, as a rolling bearing for rotatably supporting a gear shaft of a gear reduction device such as a differential or a transmission in an automobile or a construction machine, a radial load, an axial load, and a combined load thereof are applied. Tapered roller bearings that can be used are often used.
【0003】図4は、従来の自動車のデファレンシャル
を示し、ハウジング50に一対の円すいころ軸受51、
52を介して回転自在に支持されたドライブピニオン5
3と、このドライブピニオン53に噛合するリングギア
54と、このリングギア54が取り付けられ、ハウジン
グ50に対して回転自在に支持された差動歯車ケース5
5と、この差動歯車ケース55の中に配設されたピニオ
ン(図示せず)と、このピニオンと噛合する一対のサイ
ドギア(図示せず)とで基本的に構成され、ギアオイル
の封入されたハウジング50内に収容されている。この
ギアオイルは前記円すいころ軸受51、52等の潤滑も
行っている。FIG. 4 shows a differential of a conventional automobile. A housing 50 has a pair of tapered roller bearings 51,
Drive pinion 5 rotatably supported via 52
3, a ring gear 54 meshing with the drive pinion 53, and a differential gear case 5 to which the ring gear 54 is attached and rotatably supported with respect to the housing 50.
5, a pinion (not shown) disposed in the differential gear case 55, and a pair of side gears (not shown) meshing with the pinion, and gear oil is sealed therein. It is housed in a housing 50. This gear oil also lubricates the tapered roller bearings 51, 52 and the like.
【0004】通常、ドライブピニオン53を支持する円
すいころ軸受51、52は、ドライブピニオン53とリ
ングギア54との噛み合いを良好に保つため予圧が付与
されるが、組立現場では、ドライブピニオン53に間座
56を介して一対の円すいころ軸受51、52を装着
後、ドライブシャフト(図示せず)に連結されるピニオ
ンフランジ57を介してナット58の締め付け、一対の
円すいころ軸受51、52の起動トルクまたは回転トル
クにて予圧管理を行っている。Normally, the tapered roller bearings 51 and 52 supporting the drive pinion 53 are given a preload in order to maintain good engagement between the drive pinion 53 and the ring gear 54. After mounting the pair of tapered roller bearings 51 and 52 via the seat 56, the nut 58 is tightened via a pinion flange 57 connected to a drive shaft (not shown), and the starting torque of the pair of tapered roller bearings 51 and 52 is increased. Or, the preload is controlled by the rotational torque.
【0005】建設機械や比較的車重の大きい自動車等に
は、負荷容量の大きいこうした一対の円すいころ軸受が
一般に使用されるが、これ以外に一対のアンギュラ玉軸
受や、またアンギュラ玉軸受と円すいころ軸受とのセッ
トで使用される場合もある。A pair of tapered roller bearings having a large load capacity is generally used in construction machines and automobiles having a relatively heavy vehicle weight. In addition to this, a pair of angular ball bearings or a pair of angular ball bearings and a tapered roller bearing are used. It may be used in combination with a roller bearing.
【0006】[0006]
【発明が解決しようとする課題】前述したデファレンシ
ャルにおいて、高入力トルク負荷時に、ドライブピニオ
ン53にねじれが発生し、円すいころ軸受52の端面と
ドライブピニオン53の肩部53a間、また、円すいこ
ろ軸受51の端面51aとピニオンフランジ57間で滑
り(スティックスリップ)が発生することがある。この
時、カッキン等の金属音、所謂スティックスリップノイ
ズが発生することがあり、これを防止する手段として、
円すいころ軸受52の端面とドライブピニオン53の肩
部53a間、あるいは、円すいころ軸受51の端面51
aとピニオンフランジ57間にワッシャ59を挿入する
こともなされているが、組立性が低下するだけでなく、
このワッシャ59が摩耗して軸受予圧が減少し、ドライ
ブピニオン53とリングギア54との噛み合いを良好に
保つことができないといった問題があった。In the above-mentioned differential, when a high input torque load is applied, the drive pinion 53 is twisted, and between the end face of the tapered roller bearing 52 and the shoulder 53a of the drive pinion 53, as well as the tapered roller bearing. Sliding (stick-slip) may occur between the end face 51a of the pin 51 and the pinion flange 57. At this time, a metal sound such as a cockle, so-called stick-slip noise may be generated, and as a means for preventing this,
Between the end face of the tapered roller bearing 52 and the shoulder 53a of the drive pinion 53, or the end face 51 of the tapered roller bearing 51
Although a washer 59 is inserted between a and the pinion flange 57, not only does the assemblability deteriorate, but also
There was a problem that the washer 59 was worn to reduce the bearing preload, and the meshing between the drive pinion 53 and the ring gear 54 could not be maintained well.
【0007】本発明は、このような事情に鑑みてなされ
たもので、組立性を向上させ、ドライブピニオンとリン
グギア等、歯車減速装置における歯車の噛み合いを良好
に保つことができるように、初期の軸受予圧を維持でき
る転がり軸受を提供することを目的としている。SUMMARY OF THE INVENTION The present invention has been made in view of such circumstances, and has been developed in order to improve assemblability and maintain good meshing of gears in a gear reduction device such as a drive pinion and a ring gear. An object of the present invention is to provide a rolling bearing capable of maintaining the preload of the bearing.
【0008】[0008]
【課題を解決するための手段】係る目的を達成すべく、
本発明のうち請求項1記載の発明は、内輪、外輪、およ
びそれらの環状空間内に収容された複数の転動体とから
なる転がり軸受において、内輪の端部に耐摩耗性を有す
る鋼板製ワッシャを嵌合した。こうした構成により、ス
ティックスリップノイズ発生を防止し、従来のような別
体のワッシャを介在させた構成に比べ、組立性を向上さ
せると共に、ワッシャの摩耗を軽減させることができ
る。In order to achieve the above object,
An invention according to claim 1 of the present invention provides a rolling bearing comprising an inner ring, an outer ring, and a plurality of rolling elements housed in an annular space thereof, wherein a washer made of a steel plate having wear resistance at an end of the inner ring. Was fitted. With such a configuration, it is possible to prevent the occurrence of stick-slip noise, to improve the assemblability, and to reduce the wear of the washer as compared with a conventional configuration in which a separate washer is interposed.
【0009】また、請求項2に記載の発明は、ワッシャ
が、断面L字状をなし、内輪の外径に圧入嵌合する円筒
部と、内輪の端面に接合する円板部とからなる構成とし
たため、ワッシャ取付のために内輪、あるいはワッシャ
自体に特別な加工を施すことはなく、簡単な構成で低コ
ストな転がり軸受を提供することができる。According to a second aspect of the present invention, the washer has an L-shaped cross section, and has a cylindrical portion press-fitted to the outer diameter of the inner ring and a disk portion joined to the end face of the inner ring. Therefore, no special processing is performed on the inner ring or the washer itself for mounting the washer, and a low-cost rolling bearing with a simple configuration can be provided.
【0010】また、請求項3に記載の発明は、ワッシャ
の表面に、軟窒化処理による窒化層を形成することによ
り、ワッシャの耐摩耗性を確保すると共に、表面処理に
よる変形を可及的に抑制することができる。According to a third aspect of the present invention, by forming a nitrided layer on the surface of the washer by soft nitriding, the wear resistance of the washer is ensured and deformation by the surface treatment is minimized. Can be suppressed.
【0011】また、請求項4に記載の発明のように、さ
らに、ワッシャの表面硬さを400Hv以上とし、か
つ、その窒化層深さを20μm以上とすることにより、
長期間にわたってワッシャの摩耗を抑制することができ
る。Further, as in the invention according to claim 4, by further setting the surface hardness of the washer to 400 Hv or more and the depth of the nitride layer to 20 μm or more,
Wear of the washer can be suppressed for a long period of time.
【0012】また、請求項5に記載の発明のように、ワ
ッシャの表面に固体潤滑剤からなる表面層を形成すれ
ば、転がり軸受と相手部材との間に発生するスティック
スリップノイズ発生をより防止でき、また、ワッシャだ
けでなく、さらにワッシャに当接する転がり軸受、ある
いは相手部材の摩耗も抑制することができる。Further, when a surface layer made of a solid lubricant is formed on the surface of the washer as in the invention described in claim 5, generation of stick-slip noise generated between the rolling bearing and the mating member is further prevented. In addition, the wear of not only the washer but also a rolling bearing or a mating member that comes into contact with the washer can be suppressed.
【0013】また、請求項6に記載の発明では、車両用
歯車減速装置における歯車軸を回転自在に支持する転が
り軸受に適用することにより、転がり軸受と歯車等の相
手部材との間に発生するスティックスリップノイズ発生
を防止でき、また、ワッシャだけでなく、さらにワッシ
ャに当接する転がり軸受、あるいは相手部材の摩耗も抑
制することができる。したがって、転がり軸受の初期予
圧を維持でき、長期間にわたって良好な歯車の噛み合い
を保持することができる。In the invention according to claim 6, the invention is applied to a rolling bearing for rotatably supporting a gear shaft in a vehicle gear reduction device, so that a gear is generated between the rolling bearing and a mating member such as a gear. The occurrence of stick-slip noise can be prevented, and the wear of not only the washer but also a rolling bearing that contacts the washer or a mating member can be suppressed. Therefore, the initial preload of the rolling bearing can be maintained, and good gear engagement can be maintained for a long period of time.
【0014】また、請求項7に記載の発明のように、転
がり軸受が、内周に円すい状の転走面を有する外輪と、
この転走面に対向する円すい状の転走面と、この転走面
の大径側に大鍔とを外周に有する内輪と、外輪の転走面
と内輪の転走面との環状空間内に転動自在に収容された
複数の円すいころと、この円すいころを保持する保持器
とを備えた円すいころ軸受とすれば、軸受の負荷容量が
増大し、トラック等、車重の大きい自動車や建設機械に
おいても、長期間にわたりスティックスリップノイズ発
生を防止でき、また、ワッシャだけでなく、さらにワッ
シャに当接する転がり軸受、あるいは相手部材の摩耗も
抑制することができ、メンテナンスフリー化が可能とな
る。According to a seventh aspect of the present invention, the rolling bearing comprises an outer ring having a conical rolling surface on an inner periphery;
A conical rolling surface facing the rolling surface, an inner ring having a large flange on the outer periphery of the rolling surface on the large diameter side, and an annular space between the rolling surface of the outer ring and the rolling surface of the inner ring. If the tapered roller bearing is provided with a plurality of tapered rollers rotatably accommodated in the tapered roller and a retainer for holding the tapered roller, the load capacity of the bearing is increased, such as trucks and other heavy vehicles. In construction machinery, it is possible to prevent the occurrence of stick-slip noise for a long period of time, and it is also possible to suppress the wear of not only the washer, but also the rolling bearing that comes into contact with the washer, or the mating member, thereby enabling maintenance-free operation. .
【0015】[0015]
【発明の実施の形態】以下、本発明の実施の形態を図面
に基づいて詳細に説明する。図1は、本発明に係る転が
り軸受の縦断面図を示す。Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 shows a longitudinal sectional view of a rolling bearing according to the present invention.
【0016】図1において、転がり軸受1は、外輪2、
内輪3、複数の転動体4、保持器5、および、内輪3の
端部に圧入嵌合された断面L字状のワッシャ6とからな
る。外輪2の内周には円すい状の転走面2aが形成さ
れ、一方、内輪3には、この転走面2aに対向する円す
い状の転走面3aと、この転走面3aの大径側に大鍔3
bとがその外周に形成されている。外輪2の転走面2a
と内輪3の転走面3aとの環状空間内には複数の転動体
4と、この転動体4を転動自在に、かつ、円周方向等配
に保持する保持器5とを備えている。In FIG. 1, a rolling bearing 1 includes an outer ring 2,
It comprises an inner ring 3, a plurality of rolling elements 4, a retainer 5, and a washer 6 having an L-shaped cross section which is press-fitted to an end of the inner ring 3. A conical rolling surface 2a is formed on the inner circumference of the outer ring 2, while a conical rolling surface 3a facing the rolling surface 2a and a large diameter of the rolling surface 3a are formed on the inner ring 3. Otsuba 3 on the side
b is formed on the outer periphery thereof. Rolling surface 2a of outer ring 2
A plurality of rolling elements 4 are provided in an annular space between the rolling element 3 and the rolling surface 3 a of the inner ring 3, and a retainer 5 for holding the rolling elements 4 so as to be able to roll freely and in a circumferential direction. .
【0017】外輪2および内輪3の各転走面2a、3a
と、転動体4の外径にはそれぞれクラウニングを形成
し、エッジロードによる接触面圧増大を抑制している
が、特に内輪3の転走面3aの両端部にはその転走面幅
の20%以下の幅で、ドロップ量20μm程度からなる
クラウニングを形成すれば、メンテナンス周期を著しく
延長できる。このクラウニングは単一円弧からなるクラ
ウニングでも、また、両端部を所定の角度でカットし
た、所謂カットクラウニングでも良い。ここでは転動体
4に円すいころを使用した円すいころ軸受を例示した
が、内外輪に円弧状の転走面が形成され、転動体に鋼球
を使用したアンギュラ玉軸受等の玉軸受でも良い。The rolling surfaces 2a, 3a of the outer ring 2 and the inner ring 3
And the outer diameter of the rolling element 4 is formed with a crowning to suppress an increase in the contact surface pressure due to the edge load. In particular, both ends of the rolling surface 3a of the inner race 3 have a rolling surface width of 20 mm. %, A maintenance cycle can be significantly extended by forming a crowning having a drop amount of about 20 μm. This crowning may be a crowning composed of a single arc or a so-called cut crowning in which both ends are cut at a predetermined angle. Here, a tapered roller bearing using a tapered roller for the rolling element 4 has been illustrated, but a ball bearing such as an angular ball bearing using steel balls for the rolling element with an arcuate rolling surface formed on the inner and outer rings may be used.
【0018】内輪3の大鍔3bに圧入嵌合されたワッシ
ャ6は、SPCC等の冷間圧延鋼やS10C〜S60C
等の炭素鋼からなる鋼板製で、プレス加工により、大鍔
3bの外径に圧入嵌合される円筒部6aと、内輪3の端
面3cに接合する円板部6bとからなる断面L字状に形
成されている(図2)。ワッシャ6を内輪3に一体にす
る手段として、例えば、内輪3の大鍔3bの外径に環状
溝を形成し、ワッシャ6を嵌合後、円筒部6aを加締め
ても良いが、内輪3の加工、および加締工程に工数を要
し、転がり軸受1のコストアップは否めない。The washer 6 press-fitted into the large collar 3b of the inner ring 3 is made of cold-rolled steel such as SPCC or S10C to S60C.
L-shaped section formed of a cylindrical portion 6a press-fitted to the outer diameter of the large flange 3b by press working and a disk portion 6b joined to the end surface 3c of the inner ring 3 by press working. (FIG. 2). As a means for integrating the washer 6 with the inner ring 3, for example, an annular groove may be formed in the outer diameter of the large flange 3 b of the inner ring 3, and after fitting the washer 6, the cylindrical portion 6 a may be swaged. The process and the caulking process require man-hours, and the cost of the rolling bearing 1 cannot be denied.
【0019】このワッシャ6は、耐摩耗性を向上させる
手段として一般に浸炭処理や窒化処理を施されるが、板
厚が0.5mm程度の薄いものであるため、ガス軟窒化
処理が施されている。通常、軟窒化処理は、540〜5
70℃アンモニアガス等の雰囲気中に1〜3時間保持し
ているが、こうした処理では、表面に400Hv程度の
窒化層は得られるも、窒化層深さ(白層の深さ)がせい
ぜい10〜20μm程度しか得られず、実使用で15μ
mを超える摩耗量を呈する条件下では、充分な窒化層深
さとは言えない。逆に、摩耗がこの窒化層を越えた場合
は、急速に摩耗が促進する恐れがある。The washer 6 is generally subjected to a carburizing treatment or a nitriding treatment as a means for improving the wear resistance. However, since the plate thickness is as thin as about 0.5 mm, it is subjected to a gas nitrocarburizing treatment. I have. Usually, the nitrocarburizing treatment is performed at 540 to 5
The substrate is kept in an atmosphere such as 70 ° C. ammonia gas for 1 to 3 hours. In such a treatment, a nitride layer of about 400 Hv can be obtained on the surface, but the nitride layer depth (white layer depth) is at most 10 to 10. Only about 20μm can be obtained.
Under conditions where the wear amount exceeds m, the nitrided layer depth cannot be said to be sufficient. Conversely, if the wear exceeds this nitrided layer, the wear may be accelerated rapidly.
【0020】本出願人は、こうした厳しい条件下におい
ても、長期間にわたり耐摩耗性を保持できるように、表
面硬さが400Hv以上で、かつ、窒化層深さが少なく
とも20μmを安定して確保できる軟窒化処理を見出し
た。すなわち、処理時間を従来の約2倍の4時間程度に
延長し、さらに、処理温度を550〜580℃の範囲で
経時的に変化させた。また、処理炉内のワッシャの配置
についても、アンモニアガス等が行き渡り難い処理炉の
隅を避け、雰囲気ガスが同一条件で均一化されるよう
に、ワッシャの投入個数を限定し、最適条件を見極め
た。The present applicant can stably secure a surface hardness of 400 Hv or more and a nitride layer depth of at least 20 μm so that wear resistance can be maintained for a long time even under such severe conditions. A soft nitriding treatment was found. That is, the processing time was extended to about 4 hours, which is about twice the conventional value, and the processing temperature was changed over time in the range of 550 to 580 ° C. Also, regarding the arrangement of washers in the processing furnace, limit the number of washers to be introduced and determine the optimum conditions so that the corners of the processing furnace where ammonia gas and the like are difficult to spread can be avoided and the atmospheric gas can be uniform under the same conditions. Was.
【0021】さらに、ワッシャ6の表面、特に円板部6
bの表面に二硫化モリブデンやグラファイト等の固体潤
滑剤を含有する無機系樹脂(商品名:デフリックコー
ト、モリコート、ゾルベスト処理)を被覆することによ
って耐摩耗性を向上すると共に、スティックスリップノ
イズ発生も抑制することができる。この被膜は、内輪3
の端面3cと接触する内表面、相手部材と接触する外表
面のどちらか一方、あるいは両方に形成すると良い。被
膜は、これに限らず、四フッ化エチレンを含有する有機
系樹脂、マトリクス樹脂内に、低分子量潤滑成分を含有
する潤滑性被膜のようなものでも良い。Further, the surface of the washer 6, in particular, the disk 6
The surface of b is coated with an inorganic resin containing a solid lubricant such as molybdenum disulfide or graphite (trade name: defric coat, moly coat, sol vest treatment) to improve wear resistance and generate stick-slip noise. Can also be suppressed. This coating is inner ring 3
It may be formed on one or both of the inner surface contacting the end surface 3c and the outer surface contacting the mating member. The coating is not limited to this, and may be a lubricating coating containing a low molecular weight lubricating component in an organic resin containing tetrafluoroethylene or a matrix resin.
【0022】また、こうした転がり軸受をデファレンシ
ャルのドライブピニオン支持等に使用する場合、多くの
歯車の噛み合い部や回転部材の摺動部を有しているた
め、これらの部位で発生する金属摩耗粉等の異物が、ハ
ウジングに封入されたギアオイルに混入する。これらの
摩耗粉は、高負荷で回転する歯車を支持する転がり軸
受、特に円すいころ軸受に中に入り込み、転がり軸受の
摩耗を促進させ、予圧抜けによる歯車の噛み合いに影響
を与えるだけでなく、軸受の耐久寿命面で問題となるこ
とがある。When such a rolling bearing is used for supporting a drive pinion of a differential, etc., since it has many meshing portions of gears and sliding portions of rotating members, metal abrasion powder or the like generated at these portions is required. Foreign matter enters the gear oil enclosed in the housing. These abrasion powders penetrate into rolling bearings, especially tapered roller bearings, which support gears rotating under high load, and promote the wear of rolling bearings, not only affecting gear meshing due to preload loss, but also bearings. May be problematic in terms of durability life.
【0023】したがって、こうした転がり軸受の内輪、
外輪、および転動体は肌焼き鋼SCr435からなり、
この各表面に、炭素含有量0.80重量%以上で、か
つ、58HRc以上の浸炭窒化層を形成することが有効
である。さらに、浸炭窒化層の残留オーステナイト量を
25〜35体積%の範囲に設定することにより、浸炭層
の表面硬さを確保した上で、亀裂の発生や進展を抑制す
ることができる。さらに、通常の浸炭層に比べ、大きな
圧縮残留応力が形成されるため、軸受の疲労強度を高め
ることもできる。Therefore, the inner ring of such a rolling bearing,
The outer ring and rolling elements are made of case hardened steel SCr435,
It is effective to form a carbonitrided layer having a carbon content of 0.80% by weight or more and 58HRc or more on each surface. Furthermore, by setting the amount of retained austenite of the carbonitrided layer in the range of 25 to 35% by volume, it is possible to secure the surface hardness of the carburized layer and suppress the generation and propagation of cracks. Furthermore, since a larger compressive residual stress is formed than in a normal carburized layer, the fatigue strength of the bearing can be increased.
【0024】前述した浸炭窒化層の組織は、次のような
処理工程で形成することができる。すなわち、雰囲気中
の炭素ポテンシャルを0.8%以上にして所定時間加熱
保持した後、油中で冷却して浸炭焼入れを行い、この
後、アンモニアガス中で所定時間加熱保持して窒化処理
を行う。また、浸炭工程中に同時に窒化処理も行う方法
を採用しても良い。The structure of the carbonitrided layer described above can be formed by the following processing steps. That is, after the carbon potential in the atmosphere is kept at 0.8% or more and heated and held for a predetermined time, it is cooled in oil to perform carburizing and quenching, and then is heated and held in an ammonia gas for a predetermined time to perform a nitriding treatment. . Further, a method of performing a nitriding treatment simultaneously during the carburizing step may be adopted.
【0025】以上、本発明の実施の形態について説明を
行ったが、本発明はこうした実施の形態に何等限定され
るものではなく、あくまで例示であって、本発明の要旨
を逸脱しない範囲内において、さらに種々なる形態で実
施し得ることは勿論のことであり、本発明の範囲は、特
許請求の範囲の記載によって示され、さらに特許請求の
範囲に記載の均等の意味、および範囲内のすべての変更
を含む。Although the embodiments of the present invention have been described above, the present invention is not limited to these embodiments at all, but is merely an example and is within the scope of the present invention. Needless to say, the present invention can be embodied in various forms, and the scope of the present invention is indicated by the description of the claims, and furthermore, the equivalent meanings described in the claims, and all within the scope Including changes.
【0026】[0026]
【発明の効果】以上詳述したように、本発明に係る転が
り軸受は、以下に挙げるような格別な効果を奏する。請
求項1に記載の発明によれば、内輪、外輪、およびそれ
らの環状空間内にされた複数の転動体とからなる転がり
軸受において、内輪の端部に耐摩耗性を有する鋼板製ワ
ッシャを嵌合させたことにより、スティックスリップノ
イズ発生を防止し、従来のような別体のワッシャを介在
させた構成に比べ、組立性を向上させると共に、ワッシ
ャの摩耗を軽減させることができる。請求項2に記載の
発明によれば、ワッシャが、断面L字状をなし、内輪の
外径に圧入嵌合する円筒部と、内輪の端面に接合する円
板部とからなるため、ワッシャ取付のために内輪、ある
いはワッシャ自体に特別な加工を施すことはなく、簡単
な構成で低コストな転がり軸受を提供することができ
る。請求項3に記載の発明によれば、ワッシャの表面
に、軟窒化処理による窒化層を形成することにより、ワ
ッシャの耐摩耗性を確保すると共に、表面処理による変
形を可及的に抑制することができる。請求項4に記載の
発明によれば、ワッシャの表面硬さを400Hv以上と
し、かつ、その窒化層深さを20μm以上とすることに
より、長期間にわたってワッシャの摩耗を抑制すること
ができる。請求項5に記載の発明によれば、ワッシャの
表面に固体潤滑剤からなる表面層を形成すれば、転がり
軸受と相手部材との間に発生するスティックスリップノ
イズ発生を防止でき、また、ワッシャだけでなく、さら
にワッシャに当接する転がり軸受、あるいは相手部材の
摩耗も抑制することができる。請求項6に記載の発明に
よれば、車両用歯車減速装置における歯車軸を回転自在
に支持する転がり軸受に適用することにより、転がり軸
受と歯車等の相手部材との間に発生するスティックスリ
ップノイズ発生を防止でき、また、ワッシャだけでな
く、さらにワッシャに当接する転がり軸受、あるいは相
手部材の摩耗も抑制することができる。したがって、転
がり軸受の初期予圧を維持でき、長期間にわたって良好
な歯車の噛み合いを保持することができる。請求項7に
記載の発明によれば、転がり軸受が、内周に円すい状の
転走面を有する外輪と、この転走面に対向する円すい状
の転走面と、この転走面の大径側に大鍔とを外周に有す
る内輪と、外輪の転走面と内輪の転走面との環状空間内
に転動自在に収容された複数の円すいころと、この円す
いころを保持する保持器とを備えた円すいころ軸受とす
れば、軸受の負荷容量が増大し、トラック等、車重の大
きい自動車や建設機械においても、長期間にわたりステ
ィックスリップノイズ発生を防止でき、また、ワッシャ
だけでなく、さらにワッシャに当接する円すいころ軸
受、あるいは相手部材の摩耗も抑制することができ、メ
ンテナンスフリー化が可能となる。As described in detail above, the rolling bearing according to the present invention has the following special effects. According to the first aspect of the present invention, in a rolling bearing including an inner ring, an outer ring, and a plurality of rolling elements provided in the annular space, a washer-resistant steel plate washer is fitted to an end of the inner ring. The combination prevents the occurrence of stick-slip noise, improves the assemblability and reduces the wear of the washer as compared with the conventional configuration in which a separate washer is interposed. According to the second aspect of the present invention, the washer has an L-shaped cross section, and is composed of a cylindrical portion press-fitted to the outer diameter of the inner ring and a disk portion joined to the end surface of the inner ring. Therefore, no special processing is performed on the inner ring or the washer itself, and a low-cost rolling bearing with a simple configuration can be provided. According to the third aspect of the present invention, by forming a nitrided layer on the surface of the washer by soft nitriding, the wear resistance of the washer is ensured, and deformation due to the surface treatment is suppressed as much as possible. Can be. According to the fourth aspect of the present invention, by setting the washer surface hardness to 400 Hv or more and the nitrided layer depth to 20 μm or more, the wear of the washer can be suppressed for a long period of time. According to the fifth aspect of the present invention, if a surface layer made of a solid lubricant is formed on the surface of the washer, stick-slip noise generated between the rolling bearing and the mating member can be prevented. In addition, the wear of the rolling bearing or the mating member that comes into contact with the washer can be suppressed. According to the invention as set forth in claim 6, stick-slip noise generated between a rolling bearing and a mating member such as a gear by applying to a rolling bearing rotatably supporting a gear shaft in a vehicle gear reduction device. Generation can be prevented, and wear of not only the washer but also a rolling bearing contacting the washer or a mating member can be suppressed. Therefore, the initial preload of the rolling bearing can be maintained, and good gear engagement can be maintained for a long period of time. According to the invention as set forth in claim 7, the rolling bearing has an outer ring having a conical rolling surface on an inner periphery, a conical rolling surface facing the rolling surface, and a large size of the rolling surface. A plurality of tapered rollers rotatably accommodated in an annular space between a rolling surface of an outer ring and a rolling surface of an inner ring having a large flange on an outer periphery on a radial side, and a holding device for holding the tapered rollers; Tapered roller bearings equipped with a container increases the load capacity of the bearings, and can prevent the occurrence of stick-slip noise over a long period of time even in heavy vehicles such as trucks and construction machinery. In addition, wear of the tapered roller bearing or the mating member that comes into contact with the washer can be suppressed, and maintenance-free operation can be achieved.
【図1】本発明に係る転がり軸受の縦断面図FIG. 1 is a longitudinal sectional view of a rolling bearing according to the present invention.
【図2】本発明に係る転がり軸受に装着されるワッシャ
の縦断面図FIG. 2 is a longitudinal sectional view of a washer mounted on the rolling bearing according to the present invention.
【図3】図2の左側面図FIG. 3 is a left side view of FIG. 2;
【図4】従来の自動車のデファレンシャルを示す破断断
面図FIG. 4 is a cutaway sectional view showing a conventional automobile differential.
1・・・・・・・転がり軸受 2・・・・・・・外輪 2a・・・・・・転走面 3・・・・・・・内輪 3a・・・・・・転走面 3b・・・・・・大鍔 3c・・・・・・端面 4・・・・・・・転動体 5・・・・・・・保持器 6・・・・・・・ワッシャ 6a・・・・・・円筒部 6b・・・・・・円板部 50・・・・・・ハウジング 51・・・・・・円すいころ軸受 51a・・・・・端面 52・・・・・・円すいころ軸受 52a・・・・・端面 53・・・・・・ドライブピニオン 53a・・・・・肩部 54・・・・・・リングギア 55・・・・・・差動歯車ケース 56・・・・・・間座 57・・・・・・ピニオンフランジ 58・・・・・・ナット 59・・・・・・ワッシャ 1 Rolling bearing 2 Outer ring 2a Rolling surface 3 Inner ring 3a Rolling surface 3b・ ・ ・ ・ ・ Large collar 3c ・ ・ ・ ・ ・ ・ End face 4 ・ ・ ・ ・ ・ ・ ・ ・ ・ Rolling element 5 ・ ・ ・ ・ ・ ・ ・ ・ ・ Cage 6 ・ ・ ・ ・ ・ ・ ・ ・ ・ Washer 6a ・ ・ ・ ・ ・ ・・ Cylindrical part 6b ・ ・ ・ ・ ・ ・ Disc part 50 ・ ・ ・ ・ ・ ・ Housing 51 ・ ・ ・ ・ ・ ・ Tapered roller bearing 51a ・ ・ ・ ・ ・ ・ End face 52 ・ ・ ・ ・ ・ ・ Tapered roller bearing 52a ・... End face 53 Drive pinion 53a Shoulder 54 Ring gear 55 Differential gear case 56 Seat 57: Pinion flange 58: Nut 59: Washer
Claims (7)
収容された複数の転動体とからなる転がり軸受におい
て、 前記内輪の端部に耐摩耗性を有する鋼板製ワッシャを嵌
合したことを特徴とする転がり軸受。In a rolling bearing comprising an inner ring, an outer ring, and a plurality of rolling elements housed in an annular space thereof, it is preferable that a wear-resistant steel washer is fitted to an end of the inner ring. Rolling bearing characterized.
内輪の外径に圧入嵌合する円筒部と、前記内輪の端面に
接合する円板部とからなる請求項1に記載の転がり軸
受。2. The rolling device according to claim 1, wherein the washer has an L-shaped cross section, and comprises a cylindrical portion press-fitted to the outer diameter of the inner ring and a disk portion joined to an end surface of the inner ring. bearing.
窒化層を形成した請求項1または2に記載の転がり軸
受。3. The rolling bearing according to claim 1, wherein a nitrided layer is formed on the surface of the washer by nitrocarburizing.
とし、かつ、その窒化層深さを20μm以上とした請求
項3に記載の転がり軸受。4. The rolling bearing according to claim 3, wherein the washer has a surface hardness of 400 Hv or more and a nitrided layer depth of 20 μm or more.
からなる表面層を形成した請求項1乃至4いずれかに記
載の転がり軸受。5. The rolling bearing according to claim 1, wherein a surface layer made of a solid lubricant is further formed on the surface of said washer.
自在に支持する請求項1乃至5いずれかに記載の転がり
軸受。6. The rolling bearing according to claim 1, wherein the gear shaft in the vehicle gear reduction device is rotatably supported.
面を有する外輪と、この転走面に対向する円すい状の転
走面と、この転走面の大径側に大鍔とを外周に有する内
輪と、外輪の転走面と内輪の転走面との環状空間内に転
動自在に収容された複数の円すいころと、この円すいこ
ろを保持する保持器とを備えた円すいころ軸受である請
求項1乃至6いずれかに記載の転がり軸受。7. The rolling bearing has an outer ring having a conical rolling surface on an inner periphery, a conical rolling surface facing the rolling surface, and a large flange on a large diameter side of the rolling surface. And a plurality of tapered rollers rotatably accommodated in an annular space between the rolling surface of the outer ring and the rolling surface of the inner ring, and a retainer holding the tapered rollers. The rolling bearing according to any one of claims 1 to 6, which is a tapered roller bearing.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001129787A JP2002323049A (en) | 2001-04-26 | 2001-04-26 | Rolling bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001129787A JP2002323049A (en) | 2001-04-26 | 2001-04-26 | Rolling bearing |
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Publication Number | Publication Date |
---|---|
JP2002323049A true JP2002323049A (en) | 2002-11-08 |
Family
ID=18978267
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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JP2001129787A Pending JP2002323049A (en) | 2001-04-26 | 2001-04-26 | Rolling bearing |
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Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008144844A (en) * | 2006-12-08 | 2008-06-26 | Ntn Corp | Tandem double row angular ball bearing and differential gear |
WO2009154166A1 (en) | 2008-06-16 | 2009-12-23 | Ntn株式会社 | Tapered roller bearing |
JP2010106975A (en) * | 2008-10-30 | 2010-05-13 | Nsk Ltd | Rolling bearing |
WO2015098397A1 (en) * | 2013-12-24 | 2015-07-02 | Ntn株式会社 | Rolling bearing |
JP2015203483A (en) * | 2014-04-16 | 2015-11-16 | 株式会社ジェイテクト | Differential device for vehicle |
-
2001
- 2001-04-26 JP JP2001129787A patent/JP2002323049A/en active Pending
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008144844A (en) * | 2006-12-08 | 2008-06-26 | Ntn Corp | Tandem double row angular ball bearing and differential gear |
WO2009154166A1 (en) | 2008-06-16 | 2009-12-23 | Ntn株式会社 | Tapered roller bearing |
JP2009299845A (en) * | 2008-06-16 | 2009-12-24 | Ntn Corp | Conical roller bearing |
EP2306036A1 (en) * | 2008-06-16 | 2011-04-06 | NTN Corporation | Tapered roller bearing |
CN102066789A (en) * | 2008-06-16 | 2011-05-18 | Ntn株式会社 | Tapered roller bearing |
EP2306036A4 (en) * | 2008-06-16 | 2012-08-29 | Ntn Toyo Bearing Co Ltd | Tapered roller bearing |
JP2010106975A (en) * | 2008-10-30 | 2010-05-13 | Nsk Ltd | Rolling bearing |
WO2015098397A1 (en) * | 2013-12-24 | 2015-07-02 | Ntn株式会社 | Rolling bearing |
US9683606B2 (en) | 2013-12-24 | 2017-06-20 | Ntn Corporation | Rolling bearing |
JP2015203483A (en) * | 2014-04-16 | 2015-11-16 | 株式会社ジェイテクト | Differential device for vehicle |
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