JPH08261230A - Tilt contact type ball bearing - Google Patents
Tilt contact type ball bearingInfo
- Publication number
- JPH08261230A JPH08261230A JP7062478A JP6247895A JPH08261230A JP H08261230 A JPH08261230 A JP H08261230A JP 7062478 A JP7062478 A JP 7062478A JP 6247895 A JP6247895 A JP 6247895A JP H08261230 A JPH08261230 A JP H08261230A
- Authority
- JP
- Japan
- Prior art keywords
- ball bearing
- impeller shaft
- contact type
- type ball
- balls
- 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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
- F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
- F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
- F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles 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
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
- F16C2360/24—Turbochargers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、過給機におけるインペ
ラ軸や工作機械の軸を支持するのに用いる斜接型玉軸受
に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oblique contact ball bearing used for supporting an impeller shaft in a supercharger and a shaft of a machine tool.
【０００２】[0002]
【従来の技術】例えばスーパーチャージャーなどの機械
式遠心過給機におけるインペラ軸支持用の玉軸受は、ギ
ヤからの振動およびインペラのアンバランスによるイン
ペラ軸のふれ回りなどを避けるために、剛性を高くする
必要がある。そのためには、一般的に、複列の斜接型玉
軸受が用いられ、予圧の付与形態としても定位置予圧と
されている。2. Description of the Related Art For example, a ball bearing for supporting an impeller shaft in a mechanical centrifugal supercharger such as a supercharger has a high rigidity in order to avoid vibration of a gear and whirling of the impeller shaft due to imbalance of the impeller. There is a need to. For that purpose, generally, a double-row oblique contact type ball bearing is used, and a fixed position preload is also used as a preload application mode.
【０００３】そして、玉軸受の外輪には、複数の周溝が
形成されており、この周溝と過給機のハウジング内周面
との間にオイルが供給され、このオイルによって制振効
果つまりダンパ作用を得るようにしている。A plurality of peripheral grooves are formed on the outer ring of the ball bearing, and oil is supplied between the peripheral grooves and the inner peripheral surface of the housing of the supercharger. The oil suppresses vibration. I try to get a damper effect.
【０００４】[0004]
【発明が解決しようとする課題】ところで、玉軸受の外
輪側は、ダンパ作用を担うオイルにより冷却されるよう
になっているが、玉軸受の内輪側は、冷却作用が一切な
く、インペラ軸からの熱伝導を受け高温になる。このよ
うに内・外輪の温度差が大きくなるため、定位置予圧と
される玉軸受の場合、内部隙間が小さくなる傾向とな
る。しかも、過給機のインペラ軸のように１０万ｒｐｍ
を超える超高速回転で使用されるものでは、回転遠心力
によっても内輪の外径寸法が数μｍと膨張する。このよ
うな内部隙間の変化により、玉軸受の焼き付きが発生し
やすくなる。さらには軸受内部の温度上昇に伴って潤滑
油の劣化が進み早期寿命に至る。By the way, the outer ring side of the ball bearing is designed to be cooled by the oil having a damper action, but the inner ring side of the ball bearing has no cooling action and is not affected by the impeller shaft. It becomes high temperature due to heat conduction. Since the temperature difference between the inner and outer rings becomes large in this way, in the case of a ball bearing in which a fixed position preload is applied, the internal clearance tends to become smaller. Moreover, it is 100,000 rpm like the impeller shaft of a supercharger.
In the case of ultra-high speed rotation exceeding 100 rpm, the outer diameter of the inner ring expands to several μm due to centrifugal force. Due to such a change in the internal clearance, seizure of the ball bearing is likely to occur. Further, the temperature of the inside of the bearing rises and the lubricating oil deteriorates, leading to an early life.
【０００５】したがって、本発明は、斜接型玉軸受にお
いて、温度上昇に伴う内部隙間の変化を抑制し、軸受の
焼き付きを回避できるようにすることを目的としてい
る。Therefore, it is an object of the present invention to prevent the seizure of the bearing by suppressing the change in the internal clearance due to the temperature rise in the oblique contact type ball bearing.
【０００６】[0006]
【課題を解決するための手段】本発明の斜接型玉軸受
は、鋼製の内・外輪間に複数の玉を配設し、内・外輪に
対して玉が斜接するもので、内輪とそれが嵌合される軸
との少なくとも一方の嵌合面に、凹部および段部もしく
はそれらのいずれか一方が設けられており、定位置予圧
が付与される形態で取付対象部位に装着される。なお、
前述の玉は、セラミックスで形成するのが好ましい。The oblique contact type ball bearing of the present invention is one in which a plurality of balls are arranged between steel inner and outer rings, and the balls are obliquely contacted with the inner and outer rings. At least one fitting surface with the shaft to which it is fitted is provided with a concave portion and a step portion or any one of them, and the concave portion and the step portion are attached to the attachment target portion in a form in which a fixed position preload is applied. In addition,
The balls described above are preferably made of ceramics.
【０００７】[0007]
【作用】凹部または段部を内輪またはそれが嵌合される
軸のいずれに設けても、内輪と軸との接触面積を減少さ
せ、熱伝導を抑制するとともに、軸の熱膨張に伴い内輪
に作用する応力を緩和することで内輪軌道径の膨張を抑
制する。したがって、玉軸受の内部隙間の変化が抑制さ
れる。これは、特に定位置予圧が付与される形態で利用
される斜接型玉軸受において、より有効となる。[Effect] Regardless of whether the concave portion or the stepped portion is provided on the inner ring or the shaft to which it is fitted, the contact area between the inner ring and the shaft is reduced, heat conduction is suppressed, and the inner ring becomes The expansion of the inner ring raceway diameter is suppressed by relaxing the acting stress. Therefore, changes in the internal clearance of the ball bearing are suppressed. This is particularly effective in the oblique contact type ball bearing used in the form in which the fixed position preload is applied.
【０００８】しかも、玉をセラミックスとすれば、高速
回転を有利とする上、さらに斜接型玉軸受の内部の発熱
を抑制するとともに、潤滑油の寿命も延びる。Moreover, if the balls are made of ceramics, high-speed rotation is advantageous, heat generation inside the oblique contact type ball bearing is suppressed, and the life of the lubricating oil is extended.
【０００９】[0009]
【実施例】以下、本発明の詳細を図１に示す実施例に基
づいて説明する。図１は本発明の一実施例にかかり、遠
心式スーパーチャージャーのインペラ周辺構造を示す縦
断面図である。DESCRIPTION OF THE PREFERRED EMBODIMENTS The details of the present invention will be described below based on the embodiment shown in FIG. 1 is a longitudinal sectional view showing an impeller peripheral structure of a centrifugal supercharger according to an embodiment of the present invention.
【００１０】図中、１は過給機のハウジング、２は過給
機における圧縮機のインペラ、３はインペラ軸、４はイ
ンペラ軸３をハウジング１の挿通孔１１に回転自在に支
持する複列外向きアンギュラ玉軸受、５は増速歯車機構
である。In the figure, 1 is a housing of a supercharger, 2 is an impeller of a compressor in the supercharger, 3 is an impeller shaft, and 4 is a double row which rotatably supports the impeller shaft 3 in an insertion hole 11 of the housing 1. Outward angular contact ball bearings 5 are speed increasing gear mechanisms.
【００１１】複列外向きアンギュラ玉軸受４は、２つの
内輪４１，４１と、共通の外輪４２と、内・外輪４１，
４２で形成する２列の軌道溝に介装される複数の玉４３
と、各列の玉群を保持する２つの保持器４４，４４とを
備えている。内輪４１，４１の内周面の玉の接触線ｌの
延長上には、それぞれ１つずつ周溝４６が形成されてお
り、さらに、軸受中心に対し軸方向で接触線ｌの延長線
と反対側の内周面にインペラ軸３とは非接触となる段部
４７が形成されている。外輪４２の外周面には、互いに
連通する複数列（４列）のダンパ用の周溝４５が形成さ
れている。ダンパ用の周溝４５は、断面ほぼ矩形状に、
また、応力緩和用の周溝４６は、断面ほぼ半円形状にそ
れぞれ形成されている。The double-row outward angular ball bearing 4 has two inner rings 41, 41, a common outer ring 42, an inner / outer ring 41,
A plurality of balls 43 that are inserted in two rows of raceway grooves formed by 42
And two cages 44, 44 for holding the balls in each row. One circumferential groove 46 is formed on each extension of the contact lines 1 of the balls on the inner peripheral surfaces of the inner rings 41, 41. Further, the circumferential groove 46 is opposite to the extension line of the contact line 1 in the axial direction with respect to the bearing center. A step portion 47 that is not in contact with the impeller shaft 3 is formed on the inner peripheral surface on the side. A plurality of rows (four rows) of damper circumferential grooves 45 communicating with each other are formed on the outer peripheral surface of the outer ring 42. The peripheral groove 45 for the damper has a substantially rectangular cross section,
Further, the peripheral grooves 46 for stress relaxation are each formed in a substantially semicircular cross section.
【００１２】そして、内輪４１，４１は、インペラ軸３
に対して所要のしめしろを介して軸方向に位置決めされ
た状態で外嵌されており、内輪４１，４１に周溝４６お
よび段部４７を設けているから、内輪４１，４１とイン
ペラ軸３との接触面積は、周溝４６無しのものに比べて
減少する。この段部４７の軸方向での始点は、内輪４
１，４１の嵌合状態に支障がないように軌道最深部に対
応する位置を越えないように適宜設定される。The inner rings 41, 41 are connected to the impeller shaft 3
With respect to the inner races 41 and 41, the inner races 41 and 41 are provided with the peripheral groove 46 and the stepped portion 47, so that the inner races 41 and 41 and the impeller shaft 3 are fitted to each other. The contact area with is smaller than that without the circumferential groove 46. The starting point of this step portion 47 in the axial direction is the inner ring 4
It is appropriately set so as not to exceed the position corresponding to the deepest portion of the track so as not to hinder the fitted state of 1, 41.
【００１３】また、外輪４２は、ハウジング１の挿通孔
１１の内周面に対して所要の微小間隙を介して軸方向に
位置決めされた状態で内嵌されている。この微小間隙お
よび外輪４２の外周側の周溝４５には、ダンパ作用を担
うオイルが供給されるようになっており、このオイル
は、中央の周溝４５から内・外輪４１，４２の間に潤滑
用オイルとしても供給されるようになっている。前述の
微小間隙のオイルが圧縮室側へ漏れるのを防止するため
に、外輪４２において圧縮室側（図では右側）の端部の
外周面にはＯリング６が装着されており、さらに、複列
外向きアンギュラ玉軸受４の内部のオイルが圧縮室側へ
漏れるのを防止するために、外輪４２において圧縮室側
（図では右側）の端部の内周面とインペラ軸３の外周面
との間には、シール７が装着されている。The outer ring 42 is fitted in the inner peripheral surface of the insertion hole 11 of the housing 1 while being axially positioned with a required minute gap. Oil having a damper action is supplied to the minute gap and the peripheral groove 45 on the outer peripheral side of the outer ring 42, and the oil flows from the central peripheral groove 45 to the inner / outer rings 41, 42. It is also supplied as lubricating oil. In order to prevent the oil in the minute gap from leaking to the compression chamber side, an O-ring 6 is attached to the outer peripheral surface of the end portion of the outer ring 42 on the compression chamber side (right side in the figure). In order to prevent oil inside the row outward angular contact ball bearings 4 from leaking to the compression chamber side, the outer ring 42 has an inner peripheral surface at the end on the compression chamber side (right side in the figure) and an outer peripheral surface of the impeller shaft 3. A seal 7 is attached between them.
【００１４】このように、内輪４１，４１および外輪４
２をそれぞれ軸方向に位置決めした状態で取り付けるこ
とにより、結局、複列外向きアンギュラ玉軸受４には定
位置予圧が付与される形態としている。In this way, the inner rings 41, 41 and the outer ring 4 are
By mounting the two in a state of being respectively positioned in the axial direction, a fixed position preload is eventually applied to the double-row outward angular ball bearing 4.
【００１５】ところで、複列外向きアンギュラ玉軸受４
において、内・外輪４１，４２は、高炭素クロム軸受鋼
（ＪＩＳ規格ＳＵＪ２など）や耐熱・耐食合金（ＡＩＳ
Ｉ規格Ｍ−５０、ＪＩＳ規格高速度工具鋼ＳＫＨなど）
で形成され、適宜焼入れ、焼戻し処理が施されている。
また、玉４３は、セラミックス材料で形成され、保持器
４４は、耐熱性合成樹脂（例えばポリイミド樹脂など）
で形成されている。前述のセラミックス材料としては、
焼結助剤として、イットリア（Ｙ2Ｏ3）およびアルミナ
（Ａｌ2Ｏ3）、その他、適宜、窒化アルミ（ＡｌＮ）、
酸化チタン（ＴｉＯ2）を用いた窒化けい素（Ｓｉ
3Ｎ4）を主体とするものの他、アルミナ（Ａｌ2Ｏ3）や
炭化けい素（ＳｉＣ）、ジルコニア（ＺｒＯ2）、窒化
アルミ（ＡｌＮ）などがある。By the way, the double-row outward angular ball bearing 4
In, the inner and outer rings 41, 42 are made of high carbon chrome bearing steel (JIS standard SUJ2 etc.) or heat resistant / corrosion resistant alloy (AIS
I standard M-50, JIS standard high speed tool steel SKH, etc.)
And is appropriately quenched and tempered.
The balls 43 are made of a ceramic material, and the cage 44 is made of heat-resistant synthetic resin (for example, polyimide resin).
It is formed with. As the aforementioned ceramic material,
As a sintering aid, yttria (Y 2 O 3 ), alumina (Al 2 O 3 ), and optionally aluminum nitride (AlN),
Silicon nitride (Si 2 ) using titanium oxide (TiO 2 ).
Other than those mainly containing 3 N 4 ), there are alumina (Al 2 O 3 ), silicon carbide (SiC), zirconia (ZrO 2 ), aluminum nitride (AlN) and the like.
【００１６】このように、複列外向きアンギュラ玉軸受
４の内輪４１，４１に周溝４６，４６および段部４７，
４７を設けることにより内輪４１，４１とインペラ軸３
との接触面積を小さくしているから、インペラ軸３から
内輪４１，４１への熱伝導を減少するとともに、玉の接
触線ｌの延長上に設けているので、インペラ軸３の熱膨
張に伴い内輪４１，４１の軌道溝に作用する応力を緩和
できて、内輪４１，４１の軌道径の変化を抑制できるよ
うになる。しかも、複列外向きアンギュラ玉軸受４の玉
４３をセラミックス材としているから、当該玉軸受４の
内部発熱を抑制できて、内部隙間の変化を抑制できる。
したがって、このような複列外向きアンギュラ玉軸受４
を遠心式スーパーチャージャーのインペラ軸３の支持に
用いていれば、インペラ軸３の熱膨張の影響をうけにく
くなるから、定位置予圧の形態をとりながらも、複列外
向きアンギュラ玉軸受４の内部隙間の変化を抑制できる
ようになり、焼き付き寿命を延ばせるようになる。As described above, the inner races 41, 41 of the double-row outward angular ball bearing 4 have circumferential grooves 46, 46 and step portions 47,
By providing 47, the inner rings 41, 41 and the impeller shaft 3
Since the contact area with the impeller shaft 3 is reduced, the heat conduction from the impeller shaft 3 to the inner rings 41, 41 is reduced, and since it is provided on the extension of the contact line 1 of the ball, the thermal expansion of the impeller shaft 3 is accompanied. The stress acting on the raceway grooves of the inner rings 41, 41 can be relaxed, and the change in the raceway diameter of the inner rings 41, 41 can be suppressed. Moreover, since the balls 43 of the double-row outward angular ball bearing 4 are made of a ceramic material, the internal heat generation of the ball bearing 4 can be suppressed, and the change of the internal clearance can be suppressed.
Therefore, such a double row outward angular contact ball bearing 4
If it is used to support the impeller shaft 3 of the centrifugal supercharger, it will be less susceptible to the thermal expansion of the impeller shaft 3. The change in the internal clearance can be suppressed, and the seizure life can be extended.
【００１７】なお、本発明は上記実施例のみに限定され
るものでなく、種々な応用や変形が考えられる。例え
ば、内輪４１，４１の周溝４６は、断面ほぼ矩形状とす
ることができる他、セレーション溝、ローレット溝、歯
形溝、螺旋溝、格子溝など、種々な凹部とすることがで
きる。また、凹部のみ、段部のみでもよい。また、内輪
の内周面に前述のような種々な凹部を設けるものに限ら
ず、内輪が装着されるインペラ軸などの軸の外周面に前
述のような凹部を設けるものも本発明に含む。さらに、
本発明は、内輪一体型の複列アンギュラ玉軸受などにも
適用することができる。この他、本発明の玉軸受は、工
作機械の軸の支持にも利用できる。The present invention is not limited to the above embodiment, and various applications and modifications can be considered. For example, the circumferential groove 46 of the inner rings 41, 41 can be formed into a substantially rectangular cross section, or can be formed into various recesses such as a serration groove, a knurled groove, a toothed groove, a spiral groove, and a lattice groove. Further, only the concave portion or only the step portion may be used. Further, the present invention is not limited to the above-described various concave portions provided on the inner peripheral surface of the inner ring, and includes the present invention including the above-described concave portions provided on the outer peripheral surface of a shaft such as an impeller shaft on which the inner ring is mounted. further,
The present invention can also be applied to a double-row angular contact ball bearing with an inner ring integrated. In addition, the ball bearing of the present invention can be used for supporting a shaft of a machine tool.
【００１８】[0018]
【発明の効果】本発明では、内輪に嵌合される軸からの
熱伝導および軸の熱膨張の影響を受けにくくなるから、
内輪の熱膨張を抑制することができて、玉軸受の内部隙
間の変化を抑制できるようになる。したがって、玉軸受
の焼き付き寿命の向上に貢献できる。As described above, according to the present invention, the heat conduction from the shaft fitted to the inner ring and the thermal expansion of the shaft are less likely to influence,
The thermal expansion of the inner ring can be suppressed, and the change in the internal clearance of the ball bearing can be suppressed. Therefore, the seizure life of the ball bearing can be improved.
【００１９】この効果は、特に、定位置予圧が付与され
る形態で利用される斜接型玉軸受において、より有効に
発揮する。This effect is more effectively exerted particularly in the oblique contact type ball bearing used in the form in which the fixed position preload is applied.
【００２０】しかも、玉をセラミックスとする場合に
は、高速回転を有利とする上、玉軸受内部の発熱を抑制
するので、玉軸受の内部隙間の寸法安定化の効果をさら
に有効に発揮する。Moreover, when the balls are made of ceramics, high-speed rotation is advantageous, and heat generation inside the ball bearings is suppressed, so that the effect of stabilizing the dimension of the internal clearance of the ball bearings is more effectively exhibited.
【図１】本発明の一実施例にかかり、スーパーチャージ
ャーのインペラ周辺構造を示す縦断面図。FIG. 1 is a vertical cross-sectional view showing an impeller peripheral structure of a supercharger according to an embodiment of the present invention.
３ インペラ軸 ４ 複列外向きアンギュラ玉軸受 ４１ 内輪 ４２ 外輪 ４３ 玉 ４６ 内輪の周溝 3 Impeller shaft 4 Double row outward angular contact ball bearing 41 Inner ring 42 Outer ring 43 Ball 46 Inner ring circumferential groove
Claims (2)
内・外輪に対して玉が斜接する斜接型玉軸受であって、 内輪とそれが嵌合される軸との少なくとも一方の嵌合面
に、凹部および段部もしくはそれらのいずれか一方が設
けられており、定位置予圧が付与される形態で取付対象
部位に装着される、ことを特徴とする斜接型玉軸受。1. A plurality of balls are arranged between steel inner and outer rings,
An oblique contact type ball bearing in which balls are obliquely contacted with the inner and outer rings, and at least one fitting surface of the inner ring and the shaft to which it is fitted is provided with a concave portion and / or a stepped portion. The oblique contact type ball bearing is characterized in that the oblique contact type ball bearing is mounted in a mounting target portion in a form in which a fixed position preload is applied.
る、請求項１の斜接型玉軸受。2. The oblique contact type ball bearing according to claim 1, wherein the ball is made of ceramics.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7062478A JPH08261230A (en) | 1995-03-22 | 1995-03-22 | Tilt contact type ball bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7062478A JPH08261230A (en) | 1995-03-22 | 1995-03-22 | Tilt contact type ball bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08261230A true JPH08261230A (en) | 1996-10-08 |
Family
ID=13201343
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7062478A Pending JPH08261230A (en) | 1995-03-22 | 1995-03-22 | Tilt contact type ball bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08261230A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1705393A1 (en) * | 2003-12-10 | 2006-09-27 | Jtekt Corporation | Bearing device for turbocharger |
| WO2008136481A1 (en) | 2007-05-01 | 2008-11-13 | Jtekt Corporation | Bearing device for turbocharger |
| US11339794B2 (en) | 2018-01-04 | 2022-05-24 | Ihi Corporation | Turbocharger |
-
1995
- 1995-03-22 JP JP7062478A patent/JPH08261230A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1705393A1 (en) * | 2003-12-10 | 2006-09-27 | Jtekt Corporation | Bearing device for turbocharger |
| EP1705393A4 (en) * | 2003-12-10 | 2010-01-13 | Jtekt Corp | Bearing device for turbocharger |
| WO2008136481A1 (en) | 2007-05-01 | 2008-11-13 | Jtekt Corporation | Bearing device for turbocharger |
| US11339794B2 (en) | 2018-01-04 | 2022-05-24 | Ihi Corporation | Turbocharger |
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