JPH0255646B2 - - Google Patents
Info
- Publication number
- JPH0255646B2 JPH0255646B2 JP57201762A JP20176282A JPH0255646B2 JP H0255646 B2 JPH0255646 B2 JP H0255646B2 JP 57201762 A JP57201762 A JP 57201762A JP 20176282 A JP20176282 A JP 20176282A JP H0255646 B2 JPH0255646 B2 JP H0255646B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- rotating shaft
- shaft hole
- bearing
- cylindrical
- 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.)
- Expired - Lifetime
Links
- 230000000694 effects Effects 0.000 description 12
- 239000011888 foil Substances 0.000 description 12
- 238000010586 diagram Methods 0.000 description 3
- 238000013016 damping Methods 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/024—Sliding-contact bearings for exclusively rotary movement for radial load only with flexible leaves to create hydrodynamic wedge, e.g. radial foil 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
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
- F16C2360/24—Turbochargers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Supercharger (AREA)
- Support Of The Bearing (AREA)
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、ターボチヤージヤにおいて用いられ
る軸受装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a bearing device used in a turbocharger.
（従来の技術）
従来から、ターボ機械における軸受装置は、軸
と軸受との間にオイルを介在せしめるオイル軸受
や同じく気体を介在せしめる気体軸受が用いられ
ているが、本願は後者の気体軸受に係わり、その
なかでも複数の薄い金属板を介在せしめた構造で
あるフオイル軸受の改良に係わる。すなわち、フ
オイルタイプの気体軸受は他の形式のものに比べ
構造が簡単で低価格であることから、小型ガスタ
ービンやターボ機械に実用化されているが、自動
車用ターボチヤージヤにおいては特に高回転が要
求される（ちなみに、ガスタービンでは毎分
60000〜70000回転であるが自動車用ターボチヤー
ジヤでは毎分1000000回転以上である）。(Prior Art) Conventionally, oil bearings in which oil is interposed between the shaft and the bearing, and gas bearings in which gas is interposed between the shaft and the bearing have been used as bearing devices in turbo machines. In particular, the present invention relates to the improvement of a foil bearing, which has a structure in which a plurality of thin metal plates are interposed. In other words, foil type gas bearings have a simpler structure and are cheaper than other types, so they are put into practical use in small gas turbines and turbomachinery, but they are used in automotive turbochargers, especially at high rotation speeds. required (by the way, for gas turbines every minute
(60,000 to 70,000 revolutions per minute, but in automotive turbochargers it is more than 1,000,000 revolutions per minute).
かかるフオイルタイプの気体軸受としては特開
昭52−144555号公報に記載されたもの、特開昭56
−141021号公報に記載されたものが知られてい
る。前者の気体軸受は、軸孔の内周面に所定の間
隔で突部をもつ長い帯状のフオイルを２重に巻き
付けたものである。また後者の気体軸受は軸孔の
内周面に等間隔にフオイルの一端を固定した複数
のフオイルを植付け他端部を軸受面とするもので
ある。 Such foil type gas bearings include those described in JP-A-52-144555, and those described in JP-A-56-1989.
The one described in Publication No.-141021 is known. The former type of gas bearing is made by doubly wrapping a long strip-shaped foil having protrusions at predetermined intervals around the inner peripheral surface of a shaft hole. The latter gas bearing has a plurality of foils fixed at equal intervals on the inner circumferential surface of a shaft hole, with one end of the foil fixed, and the other end serving as a bearing surface.
（本発明によつて解決される課題）
従来のフオイルタイプの気体軸受では高回転時
に十分な制振効果が発揮されず、振れ回りにより
フオイルと軸とが直接接触し焼き付きが生じると
いう欠点があつた。なお一般に回転軸が高速回転
した場合回転軸とトツプフオイルとの間に十分に
空気を巻込むことにより軸受として負荷容量を高
め得るためのくさび効果は、トツプフオイルの曲
率半径と回転軸の外径とが差が大きくなる程顕著
である。すなわち、くさび効果を十分に発揮させ
るためには、くさびの先端角はある程度大きいこ
とが必要となる。従来のトツプフオイルと回転軸
との間で形成されるくさびの先角は０度に近いた
めくさび効果は小さい。この先端角大きくするこ
とにより、負荷容量が大きくなる。この反面、ト
ツプフオイルの曲率半径と回転軸の外径との差す
なわちトツプフオイルと回転軸との間のクリアラ
ンスの大きさに比例して回転軸が振れ前記焼き付
きを発生させる。(Problems to be Solved by the Present Invention) Conventional foil-type gas bearings do not exhibit sufficient vibration damping effects at high speeds, and have the disadvantage that the foil and shaft come into direct contact with each other due to whirling, resulting in seizure. It was hot. In general, when the rotating shaft rotates at high speed, the wedge effect, which increases the load capacity of the bearing by sufficiently entraining air between the rotating shaft and the Topf oil, occurs when the radius of curvature of the Topf oil and the outer diameter of the rotating shaft are The larger the difference, the more noticeable it is. That is, in order to fully exhibit the wedge effect, the tip angle of the wedge needs to be large to some extent. Since the tip angle of the wedge formed between the conventional top oil and the rotating shaft is close to 0 degrees, the wedge effect is small. By increasing this tip angle, the load capacity increases. On the other hand, the rotation shaft swings out in proportion to the difference between the radius of curvature of the top oil and the outer diameter of the rotation shaft, that is, the size of the clearance between the top oil and the rotation shaft, causing the seizure.
前記した従来のフオイルを２重に巻きつけた気
体軸受は、フオイルの突部の部分が軸受面では凹
部となり気体だまりを形成し、軸受面への気体の
供給がすぐれている。しかしくさび効果について
は従来のフオイル軸受と何らかわることがない。
また後者の気体軸受はくさび効果にはすぐれてい
るが、フオイルがカンチレバー式であるためくさ
び効果によつて生じた高圧の気体を持続する回転
軸とフオイルとが近接して平走する部分がない。
このため高い圧力の気体を維持する周方向距離が
短かくなり高い圧力の気体を生じさせることが困
難であるとともに、気体軸受の組付けが難しい。 In the above-mentioned conventional gas bearing in which the foil is wound twice, the protruding portion of the foil becomes a recess on the bearing surface, forming a gas reservoir, and is excellent in supplying gas to the bearing surface. However, the wedge effect is no different from conventional foil bearings.
The latter type of gas bearing has an excellent wedge effect, but since the foil is a cantilever type, there is no part where the foil runs close to the rotating shaft that sustains the high pressure gas generated by the wedge effect. .
For this reason, the circumferential distance for maintaining high pressure gas becomes short, making it difficult to generate high pressure gas and also making it difficult to assemble the gas bearing.
（課題を達成するための手段）
本発明のターボチヤージヤ用軸受装置は、軸孔
をもつ軸受ハウジングと、該軸孔内に配置された
筒状のダンプフオイルと、該ダンプフオイルの内
側に配置された筒状のトツプフオイルと、該トツ
プフオイルの内側に配置された回転軸とで構成さ
れ、該トツプフオイルは、複数の突部で分割され
た複数の弧状部をもち、各弧状部の曲率中心が軸
孔の中心よりも遠い方にそれぞれ偏心され該弧状
部と該突部とを交互に一体的に連結されて筒状と
なつていることを特徴とする。(Means for Achieving the Object) A bearing device for a turbocharger according to the present invention includes a bearing housing having a shaft hole, a cylindrical dump oil arranged in the shaft hole, and a cylindrical dump oil arranged inside the dump oil. The topfoil is composed of a topfoil and a rotating shaft placed inside the topfoil, and the topfoil has a plurality of arcuate parts divided by a plurality of protrusions, and the center of curvature of each arcuate part is closer to the center of the shaft hole. The arcuate portions and the protrusions are alternately and integrally connected to each other so as to form a cylindrical shape.
（作用）
本発明のターボチヤージヤ用軸受装置は、高速
回転しうる回転軸と該回転軸を支持するための軸
受ハウジングとの間に、複数の突部で分割された
複数の弧状部をもち、各弧状部の曲率中心が軸孔
の中心よりも遠い方にそれぞれ偏心され弧状部と
突部とを交互に一体的に連結されて筒状となつて
いるトツプフオイルをもつ。この複数の突部で分
割された複数の弧状部の円周面と、回転軸の外周
面との間で、くさび状の間隙が形成される。この
ため回転軸が高速回転したときの気体の巻込み作
用（くさび膜作用）を促進させ高圧の気体が発生
する。そしてこの高圧の気体は形成されたくさび
状の隙間に続く、回転軸と弧状部の近接して平走
する部分に形成される周方向に長い間隙に送られ
回転軸を軸芯方向に強く付勢することができる。
これにより回転軸は複数箇所で広い面積にわたつ
て高圧の気体で支持されることになり回転軸表面
の固体接触が回避される。なお、この作用は、回
転軸の外周面にトツプフオイルの複数の弧状部が
対向しており、しかも各弧状部の曲率中心が軸孔
の中心よりも遠い方にそれぞれ偏心された特異な
形状であるため、トツプフオイルの曲率半径と回
転軸の外径との差が大きく気体の巻込作用が効果
的なものとなり、かつ前記差が大きなものであつ
てもトツプフオイルと回転軸とのクリアランスは
小さなものとなり、回転軸はその軸芯を大きく振
られることなく、所定の軸芯を中心としてスムー
スに回転します。(Function) The turbocharger bearing device of the present invention has a plurality of arcuate parts divided by a plurality of protrusions between a rotating shaft that can rotate at high speed and a bearing housing for supporting the rotating shaft. The top oil has a cylindrical shape in which the centers of curvature of the arcuate portions are eccentrically located farther from the center of the shaft hole, and the arcuate portions and protrusions are alternately and integrally connected. A wedge-shaped gap is formed between the circumferential surfaces of the plurality of arcuate parts divided by the plurality of protrusions and the outer circumferential surface of the rotating shaft. Therefore, when the rotating shaft rotates at high speed, gas entrainment action (wedge film action) is promoted and high pressure gas is generated. This high-pressure gas is then sent to a circumferentially long gap formed between the rotating shaft and the arc-shaped portion that runs parallel to each other, following the formed wedge-shaped gap, and strongly attaches the rotating shaft in the axial direction. can be strengthened.
As a result, the rotating shaft is supported by high-pressure gas at a plurality of locations over a wide area, and solid contact on the surface of the rotating shaft is avoided. This effect is due to the unique shape in which multiple arcuate portions of Topfu oil face the outer circumferential surface of the rotating shaft, and the center of curvature of each arcuate portion is eccentrically located further away from the center of the shaft hole. Therefore, the difference between the radius of curvature of the Topf oil and the outer diameter of the rotating shaft is large, making the gas entrainment effect effective, and even if the difference is large, the clearance between the Topf oil and the rotating shaft is small. , the rotating shaft rotates smoothly around a predetermined axis without being shaken significantly.
（実施例）
以下、本発明の実施例を添付図面に基づき詳細
に説明する。(Example) Hereinafter, an example of the present invention will be described in detail based on the accompanying drawings.
図は本発明の一実施例を示す断面図で、図中、
符号１はａ矢印方向に高速回転する回転軸であ
り、Ｏは該軸１の中心である。一方、符号２は前
記軸１を支持するための軸受ハウジングであり、
該ハウジング２には断面円形の軸孔２ａが穿設さ
れ、その軸孔２ａ内にクリアランス調整シム３、
ダンプフオイル４、トツプフオイル５、回転軸１
の順に配置されている。すなわち、まず薄板状の
クリアランス調整シム３が打込まれる。このクリ
アランス調整シム３はあくまでクリアランス調整
用のもので厳密な工作をすれば不要となる部分で
ある。クリアランス調整シム３の開口部３ａには
筒状のダンプフオイル４の一端部４ａ及び筒状の
トツプフオイル５の一端部５ａがそれぞれ係合せ
しめられ、トツプフオイル５が最内周部に位置し
て前記回転軸１を支える構成となつている。前記
ダンプフオイル４は略波形状であり、前記調整シ
ム３の内周面に接触する複数個の第１突部４ｂ
と、前記トツプフオイル５の外周面に接触する複
数個の第２突部４ｃとが連続する形状となつてい
る。そしてダンプフオイル４の他端部４ｄと前記
トツプフオイル５の一端部５ａとの間には小間隙
６が設けてある。この間隙６は、軸１からの圧力
がダンプフオイル４に加わつた場合に前記第２突
部４ｃがたわみ得るようにすべく設けてあるもの
である。 The figure is a sectional view showing one embodiment of the present invention, and in the figure,
Reference numeral 1 is a rotating shaft that rotates at high speed in the direction of the arrow a, and O is the center of the shaft 1. On the other hand, numeral 2 is a bearing housing for supporting the shaft 1,
A shaft hole 2a having a circular cross section is bored in the housing 2, and a clearance adjustment shim 3,
Dump oil 4, top oil 5, rotating shaft 1
are arranged in this order. That is, first, a thin plate-shaped clearance adjustment shim 3 is driven. This clearance adjustment shim 3 is only for clearance adjustment and is unnecessary if the work is done precisely. One end 4a of a cylindrical dump oil 4 and one end 5a of a cylindrical top oil 5 are respectively engaged with the opening 3a of the clearance adjustment shim 3, and the top oil 5 is located at the innermost circumference and is connected to the rotating shaft. It is structured to support 1. The dump oil 4 has a substantially wave shape and includes a plurality of first protrusions 4b that contact the inner circumferential surface of the adjustment shim 3.
and a plurality of second protrusions 4c that contact the outer circumferential surface of the top oil 5 are continuous. A small gap 6 is provided between the other end 4d of the dump oil 4 and the one end 5a of the top oil 5. This gap 6 is provided so that when pressure from the shaft 1 is applied to the dump oil 4, the second protrusion 4c can bend.
トツプフオイル５は、遠心方向に突出する２個
の突部５ｂ，５ｂで分割された、３個の弧状部分
５c1，５c2，５c3からなる弧状部５ｃをもち、各
弧状部分５c1，５c2，５c3の曲率中心O1，O2，
O3が軸孔２ａの中心O′よりも遠い方にそれぞれ
偏心され各弧状部分５c1，５c2，５c3と、２個の
突部５ｂ，５ｂとを交互に一体的に連結された筒
状の円形部分と、該円形部分の一端より曲折して
遠心方向に突出する一端部５ａとからなる。トツ
プフオイル５の一端部５ａと他端５ｄとの間には
小間隙７が設けてある。小間隙７は該トツプフオ
イル５がたわんだ場合の余裕をもたせるために設
けてある。また前記軸孔２ａ及びクリアランス調
整用シム３の共通中心O′とした場合、図上では
前記３箇所の弧状部５ｃの中心O′であるように
見えるが実際はそうでなく、各弧状部分５c1，５
c2，５c3の各曲率半径がR1，R2，R3であり（R1
＝R2＝R3）、その中心は軸孔２ａの中心O′よりも
遠い方にそれぞれ偏心されたO1，O2，O3である。 Topfu oil 5 has an arcuate portion 5c consisting of three arcuate portions 5c 1 , 5c 2 , 5c 3 divided by two protrusions 5b, 5b protruding in the centrifugal direction, and each arcuate portion 5c 1 , 5c. 2 , 5c 3 center of curvature O 1 , O 2 ,
A cylinder in which each arcuate portion 5c 1 , 5c 2 , 5c 3 and two protrusions 5b, 5b are alternately and integrally connected, with O 3 being eccentric to the side farther from the center O' of the shaft hole 2a . It consists of a circular portion having a shape, and one end portion 5a that is bent from one end of the circular portion and protrudes in the centrifugal direction. A small gap 7 is provided between one end 5a and the other end 5d of the top oil 5. The small gap 7 is provided to provide a margin in case the top oil 5 is bent. Further, when the common center O' of the shaft hole 2a and the clearance adjustment shim 3 is assumed to be the center O' of the three arcuate portions 5c in the diagram, this is actually not the case, and each arcuate portion 5c 1 ,5
The radii of curvature of c 2 and 5c 3 are R 1 , R 2 , and R 3 (R 1
= R 2 = R 3 ), the centers of which are O 1 , O 2 , and O 3 which are eccentrically located farther from the center O' of the shaft hole 2a.
尚、符号Ａは回転軸１とトツプフオイル５との
間に形成される空間であり、同じくB1，B2はダ
ンプフオイル４の第１突部４ｂとトツプフオイル
５との間及び同フオイル４の第２突部４ｃとクリ
アランス調整用シム３との間にそれぞれ形成され
る空間であつて、これらの空間Ａ，B1，B2は図
示してない通路を介して外気と連通している。な
お前記空間B1にはトツプフオイル５の突部５ｂ
が配置されている。 The symbol A is a space formed between the rotating shaft 1 and the top oil 5, and B 1 and B 2 are the spaces between the first protrusion 4b of the dump oil 4 and the top oil 5 and the second space of the top oil 5. These spaces A, B 1 and B 2 are respectively formed between the protrusion 4c and the clearance adjustment shim 3, and communicate with the outside air via passages not shown. Note that in the space B1 there is a protrusion 5b of the topfoil 5.
is located.
かかる構成においてはトツプフオイル５に突部
５ｂ，５ｂによつて分割された前記各弧状部分５
c1，５c2，５c3の曲率半径R1，R2，R3が軸受ハ
ウジング２の軸孔２ａの半径よりも大きいため、
各弧状部分５c1，５c2，５c3の各内周面と回転軸
１の外周面との間の３つのくさび状の空間Ａ（第
２図参照）が形成される。従つて回転軸１がａ方
向に高速回転した場合、回転軸１とトツプフオイ
ル５との間に前記３つの空間Ａ内の空気が前記回
転方向に巻込まれ（スクイズフイルム効果）、高
圧の気体が発生する。そしてこの高圧の気体は形
成されたくさび状の空間Ａに続く、回転軸１と各
弧状部分５ｃ１，５ｃ２，５ｃ３の近接して平走
する部分に形成される周方向に長い間隙に送られ
回転軸１を軸芯方向に強く付勢する。すなわち、
この巻込み作用によつて回転軸１は、複数箇所で
広い面積にわたつて高圧の空気で支持されて３方
より中心方向に押され、かつ回転軸１は軸振れす
ることなく回転し該軸１と弧状部５ｃとの固体接
触が避けられる。ダンプフオイル５は弾性力を有
する材料でつくられており、回転軸１が偏心した
ときに弾性変形することにより、回転軸１の回転
方向の力が受け止めて回転軸１を中心方向に戻す
作用をする。 In such a configuration, the top oil 5 has each of the arcuate portions 5 divided by the protrusions 5b, 5b.
Since the radius of curvature R 1 , R 2 , R 3 of c 1 , 5c 2 , 5c 3 is larger than the radius of the shaft hole 2a of the bearing housing 2,
Three wedge-shaped spaces A (see FIG. 2) are formed between the inner circumferential surfaces of each of the arcuate portions 5c 1 , 5c 2 , and 5c 3 and the outer circumferential surface of the rotating shaft 1 . Therefore, when the rotating shaft 1 rotates at high speed in the direction a, the air in the three spaces A is drawn in between the rotating shaft 1 and the top oil 5 in the rotating direction (squeeze film effect), and high-pressure gas is generated. do. Then, this high-pressure gas is sent to a circumferentially long gap formed between the rotary shaft 1 and the portions of the arcuate portions 5c1, 5c2, and 5c3 that run parallel to each other following the formed wedge-shaped space A, and rotates. Strongly urges the shaft 1 in the axial direction. That is,
Due to this entrainment action, the rotating shaft 1 is supported by high-pressure air over a wide area at multiple locations and is pushed toward the center from three sides, and the rotating shaft 1 rotates without axial wobbling. 1 and the arcuate portion 5c can be avoided. The dump oil 5 is made of a material with elastic force, and by elastically deforming when the rotating shaft 1 is eccentric, it absorbs the force in the rotational direction of the rotating shaft 1 and acts to return the rotating shaft 1 toward the center. .
なお、上記実施例では、トツプフオイル５の複
数の弧状部５ｃは、３個の弧状部分５c1，５c2，
５c3からなるが、これが最も良いという意味であ
つて別段２又は４個以上設けてもよい。 In the above embodiment, the plurality of arcuate portions 5c of the top oil 5 are three arcuate portions 5c 1 , 5c 2 ,
It consists of 5c3 , but this means that it is the best, and 2 or 4 or more may be provided.
このように本発明は、軸孔をもつ軸受ハウジン
グと、該軸孔内に配置された筒状のダンプフオイ
ルと、該ダンプフオイルの内側に配置された筒状
のトツプフオイルと、該トツプフオイルの内側に
配置された回転軸とで構成され、該トツプフオイ
ルは、複数の突部で分割された複数の弧状部をも
ち、各弧状部の曲率中心が軸孔の中心よりも遠い
方にそれぞれ偏心され該弧状部と該突部とを交互
に一体的に連結されて筒状となつている構成とし
たため、１つのトツプフオイルの複数位置で回転
軸との間にくさび状の空間を形成することができ
る。これにより回転軸が高速回転した場合でも該
回転軸とトツプフオイルとの間に十分に空気を巻
込むことができ、軸受として負荷容量を高め得る
とともに高い制振効果が得られるため、回転軸と
トツプフオイルとの固体接触が回避され、摩擦熱
による焼きつきが生じず安全な高速回転が保障さ
れるという効果がある。 As described above, the present invention provides a bearing housing having a shaft hole, a cylindrical dump oil placed in the shaft hole, a cylindrical top oil placed inside the dump oil, and a cylindrical top oil placed inside the top oil. The top oil has a plurality of arcuate parts divided by a plurality of protrusions, and the center of curvature of each arcuate part is eccentrically located further away from the center of the shaft hole. Since the protrusions are alternately and integrally connected to form a cylindrical shape, wedge-shaped spaces can be formed between the top oil and the rotating shaft at a plurality of positions on one top oil. As a result, even when the rotating shaft rotates at high speed, sufficient air can be drawn between the rotating shaft and the Topf oil, increasing the load capacity as a bearing and achieving a high vibration damping effect. This has the effect of avoiding solid contact with the metal and ensuring safe high-speed rotation without causing seizure due to frictional heat.
第１図及び第２図は本発明の一実施例の要部を
示す説明図で、第１図は回転軸の静止状態を示す
断面図、第２図は回転軸の回転状態を示し、かつ
くさび状の空間部分を明示するため、部分的に拡
大比率を変化させた図である。
１…回転軸、２…軸受ハウジング、３…クリア
ランス調整シム、４…ダンプフオイル、５…トツ
プフオイル、５ｂ…突部、５ｃ…弧状部、５c1，
５c2，５c3…弧状部分。
1 and 2 are explanatory diagrams showing essential parts of an embodiment of the present invention. FIG. 1 is a cross-sectional view showing the rotating shaft in a stationary state, and FIG. 2 is a sectional view showing the rotating shaft in a rotating state. It is a diagram in which the enlargement ratio is partially changed in order to clearly show a wedge-shaped spatial portion. DESCRIPTION OF SYMBOLS 1... Rotating shaft, 2... Bearing housing, 3... Clearance adjustment shim, 4... Dump oil, 5... Topfu oil, 5b... Protrusion, 5c... Arc-shaped part, 5c 1 ,
5c 2 , 5c 3 ... arcuate portion.
Claims (1)
置された筒状のダンプフオイルと、該ダンプフオ
イルの内側に配置された筒状のトツプフオイル
と、該トツプフオイルの内側に配置された回転軸
とで構成され、 該トツプフオイルは、複数の突部で分割された
複数の弧状部をもち、各弧状部の曲率中心が軸孔
の中心よりも遠い方にそれぞれ偏心され該弧状部
と該突部とを交互に一体的に連結されて筒状とな
つていることを特徴とするターボチヤージヤ用軸
受装置。 ２ トツプフオイルは、複数の弧状部と複数の突
部とからなる筒状の円形部分と該円形部分の一端
より遠心方向に突出する端部とからなる特許請求
の範囲第１項記載のターボチヤージヤ用軸受装
置。 ３ 軸孔にはクリアランス調整シムが装着され、
該シムの内側にダンプフオイル装着されている特
許請求の範囲第１項記載のターボチヤージヤ用軸
受装置。[Scope of Claims] 1. A bearing housing having a shaft hole, a cylindrical dump oil placed in the shaft hole, a cylindrical top oil placed inside the dump oil, and a cylindrical top oil placed inside the top oil. The top oil has a plurality of arcuate parts divided by a plurality of protrusions, and the center of curvature of each arcuate part is eccentrically located farther from the center of the shaft hole. A bearing device for a turbocharger, characterized in that the projections are alternately and integrally connected to form a cylindrical shape. 2. The turbocharger bearing according to claim 1, wherein the topfoil comprises a cylindrical circular portion including a plurality of arcuate portions and a plurality of protrusions, and an end portion protruding in the centrifugal direction from one end of the circular portion. Device. 3 A clearance adjustment shim is installed in the shaft hole,
2. A bearing device for a turbocharger according to claim 1, wherein a damp oil is installed inside said shim.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20176282A JPS5993514A (en) | 1982-11-17 | 1982-11-17 | Bearing device for turbo-charger |
| US06/552,469 US4549821A (en) | 1982-11-17 | 1983-11-16 | Foil bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP20176282A JPS5993514A (en) | 1982-11-17 | 1982-11-17 | Bearing device for turbo-charger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5993514A JPS5993514A (en) | 1984-05-30 |
| JPH0255646B2 true JPH0255646B2 (en) | 1990-11-28 |
Family
ID=16446507
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP20176282A Granted JPS5993514A (en) | 1982-11-17 | 1982-11-17 | Bearing device for turbo-charger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5993514A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105179462B (en) * | 2015-09-16 | 2017-11-03 | 中国民航大学 | A kind of ripple foil-type air hydrodynamic bearing |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52144555A (en) * | 1976-05-28 | 1977-12-01 | Hitachi Ltd | Hydrodynamical bearing |
-
1982
- 1982-11-17 JP JP20176282A patent/JPS5993514A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS52144555A (en) * | 1976-05-28 | 1977-12-01 | Hitachi Ltd | Hydrodynamical bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5993514A (en) | 1984-05-30 |
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