JPS5830420A - Bearing device of turbosupercharger - Google Patents
Bearing device of turbosuperchargerInfo
- Publication number
- JPS5830420A JPS5830420A JP56126665A JP12666581A JPS5830420A JP S5830420 A JPS5830420 A JP S5830420A JP 56126665 A JP56126665 A JP 56126665A JP 12666581 A JP12666581 A JP 12666581A JP S5830420 A JPS5830420 A JP S5830420A
- Authority
- JP
- Japan
- Prior art keywords
- floating
- ring
- float ring
- casing
- intermediate float
- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
- F01D25/162—Bearing supports
- F01D25/164—Flexible supports; Vibration damping means associated with the bearing
-
- 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/02—Sliding-contact bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
-
- 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
- F16C17/26—Systems consisting of a plurality of sliding-contact bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- 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)
- Supercharger (AREA)
Abstract
Description
【発明の詳細な説明】
本発明はケーシング内に収納されたタービンとブロアを
回転軸の両端にそれぞれ取付け、その回転軸を一対の浮
動ブツシュによシ支持してなるターボ過給機の軸受装置
に関するものである。Detailed Description of the Invention The present invention provides a bearing device for a turbocharger, in which a turbine and a blower housed in a casing are respectively attached to both ends of a rotating shaft, and the rotating shaft is supported by a pair of floating bushes. It is related to.
従来のターボ過給機の典型例を第１図および第２図につ
いて説明するに、ケーシング５内に収納されたタービン
２とブロア３は回転軸１０両端にそれぞれ取付けられ、
その回転軸１は一対の浮動ブツシュ４ａ、４ｂによυ制
振的に支持されている。しかもその浮動ブツシュ４ａ、
４ｂは回転軸１とケーシング５の内周面との間に、適当
な間隙を保持しながら半径方向に浮動自在に設けられて
いる。A typical example of a conventional turbocharger will be described with reference to FIGS. 1 and 2. A turbine 2 and a blower 3 housed in a casing 5 are respectively attached to both ends of a rotating shaft 10.
The rotating shaft 1 is supported by a pair of floating bushes 4a and 4b in a damping manner. Moreover, that floating bush 4a,
4b is provided between the rotating shaft 1 and the inner circumferential surface of the casing 5 so as to be freely floating in the radial direction while maintaining an appropriate gap.
上記ケーシング５に設けられた給油路６を流通した油は
浮動ブツシュ４ａ、４ｂの外周面に給油され、この油は
浮動ブツシュ４ａ、４ｂに設けられた半径方向の給油孔
７を流通し、回転軸１と浮動ブツシュ４ａ、４ｂとの間
の隙間に供給される。The oil flowing through the oil supply passage 6 provided in the casing 5 is supplied to the outer peripheral surfaces of the floating bushes 4a and 4b, and this oil flows through the radial oil supply hole 7 provided in the floating bushes 4a and 4b, and rotates. It is supplied to the gap between the shaft 1 and the floating bushes 4a, 4b.
また浮動ブツシュ４ａ、４ｂが軸方向へ太幅に移動する
のを防止するため、ケーシング５の内周面に設けられた
溝内に止め輪８が固定されている。Further, in order to prevent the floating bushes 4a, 4b from moving widely in the axial direction, a retaining ring 8 is fixed in a groove provided on the inner peripheral surface of the casing 5.
上記のような構造では、回転軸１が高速回転すると、回
転軸１の自励または不釣合によシ回転軸１は半径方向に
振動する。この振動の振幅によジタービン２およびブロ
ア３の外周面がケーシング５に接触して損傷する恐れが
あるため、浮動ブツシュ４ａ、４ｂと回転軸１およびケ
ーシング５との間の各狭い隙間に介在するスクイズ効果
によシ制振作用が行われている。しかるに回転軸１がさ
らに尚速回転すると割振効果は不十分となる。In the above structure, when the rotating shaft 1 rotates at high speed, the rotating shaft 1 vibrates in the radial direction due to self-excitation or imbalance of the rotating shaft 1. Because the amplitude of this vibration may cause the outer peripheral surfaces of the turbine 2 and the blower 3 to come into contact with the casing 5 and be damaged, Vibration damping is performed by the squeeze effect. However, if the rotary shaft 1 rotates even faster, the allocation effect will be insufficient.
また浮動ブツシュ４ａ、４ｂは回転軸１の周囲を自転す
るが、止め輪８は第３図に示すように馬蹄形に形成され
ているため、その切欠き部が浮動ブツシュ４ａ、４ｂの
自転と軸方向の移動を阻害するので浮動ブツシュ４ａ、
４ｂは尚速回転軸１の制振作用の効果を十分に発揮しな
くなる恐れがある。Furthermore, the floating bushes 4a and 4b rotate around the rotating shaft 1, but since the retaining ring 8 is formed in a horseshoe shape as shown in FIG. Floating bushing 4a, since it obstructs movement in the direction.
4b, there is a risk that the vibration damping effect of the rotating shaft 1 will not be sufficiently exerted.
本発明は上記欠点を解消することを目的とするもので、
ゲージング−と回転軸との間に中間フロートリングを浮
動的に介設すると共に、この中間フロートリングにより
回転軸を支持する浮動ブツシュを覆うように構成したこ
とを特徴とするものである。The present invention aims to eliminate the above-mentioned drawbacks.
The present invention is characterized in that an intermediate float ring is floatingly interposed between the gauging and the rotation shaft, and the intermediate float ring is configured to cover a floating bush that supports the rotation shaft.
以下本発明の実施例を図面について説明する。Embodiments of the present invention will be described below with reference to the drawings.
第４図において、１は段部１ａを有し、かつ半径方向に
設けられ７’Ｃ胎油孔７ａ、７ｂをそれぞれ有する浮動
ブツシュ４ａ、４ｂにより支持された回転軸で、この回
転軸１の一端にタービン、他端にブロア（図示せず）が
それぞれ取付けられている。そのタービンとブロアを収
納するケーシング５の内周面には、回転軸ｌの段部１ａ
に対向して環状突起５ａが設けられると共に、後述する
中間フロー） ＩＪソングの外周面に給油する給油路６
ａ。In FIG. 4, reference numeral 1 denotes a rotating shaft having a stepped portion 1a and supported by floating bushes 4a and 4b provided in the radial direction and having 7'C oil holes 7a and 7b, respectively. A turbine is attached to one end and a blower (not shown) is attached to the other end. On the inner peripheral surface of the casing 5 that houses the turbine and the blower, there is a stepped portion 1a of the rotating shaft l.
An annular protrusion 5a is provided facing the IJ song, and an oil supply path 6 is provided to supply oil to the outer peripheral surface of the IJ song (intermediate flow (to be described later)).
a.
６ｂが設けられている。6b is provided.
上記ケーシング５の内周面と浮動ブツシュ４ａ。The inner peripheral surface of the casing 5 and the floating bush 4a.
４ｂとの間には、中間フロートリング９が浮動自在に介
設されている。この中間フロートリング９はその両端部
にケーシング５の給油路５ａ、５ｂを経て供給された油
を浮動ブツシュ４ａ、４ｂの外周面へ供給する任意数の
給油孔１０ａ、１０ｂがそれぞれ設けられている。また
中間フロートリング９はその中央部に浮動ブツシュ４ａ
、４ｂからの排油を排出する任意数の排油孔１１が設け
られると共に、中央部の内゛周゛笥に浮動ブツシュ４ａ
。4b, an intermediate floating ring 9 is provided so as to be freely floating. This intermediate floating ring 9 is provided with an arbitrary number of oil supply holes 10a and 10b at both ends thereof, respectively, for supplying oil supplied through the oil supply passages 5a and 5b of the casing 5 to the outer peripheral surfaces of the floating bushes 4a and 4b. . In addition, the intermediate floating ring 9 has a floating bush 4a in its center.
, 4b are provided with an arbitrary number of oil drain holes 11 for discharging waste oil from the holes 4b, and a floating bush 4a is provided on the inner periphery of the central part.
.
４ｂ間に突出する一対の環状突起１３ａ、１３ｂが設け
られている。しかも前記浮動ブツシュ４ａ。A pair of annular protrusions 13a and 13b are provided that protrude between 4b. Moreover, the floating bush 4a.
４ｂは中間フロートリング９の両端部によりそれぞれ覆
われている。4b are respectively covered by both ends of the intermediate float ring 9.
上記突起１３ａ、１３ｂおよび回転軸１によ）油だまヤ
１４が形成され、この油だまシ１４にたまった油は排油
孔１１から排出される。前記回転軸１のブロア側（図で
は右側）にはカラー１５が嵌合され、このカラー１５に
ケーシング５の端面に取付けられたスラスト軸受１２が
係合されている。An oil reservoir 14 is formed by the projections 13a, 13b and the rotating shaft 1, and the oil accumulated in the oil reservoir 14 is discharged from the oil drain hole 11. A collar 15 is fitted on the blower side (right side in the figure) of the rotary shaft 1, and a thrust bearing 12 attached to the end face of the casing 5 is engaged with this collar 15.
次に上記のような構成からなる本実施例の作用について
説明する。Next, the operation of this embodiment configured as described above will be explained.
ケーシング５の給油路６ａ、５ｂを流通した油は、ケー
シング５と中間フロートリング９との間の狭い隙間Ｙに
給油された後、中間フロートリング９の給油孔１０ａ、
ｌＯｂを経て中間フロートリング９と浮動ブツシュ４ａ
、４ｂとの間の狭い隙間Ｘａ、）（ｂへ給油され、さら
に浮動ブツシュ４ａ、４ｂの給油孔７ａ、７ｂを経て回
転軸１の外周面に給油される。この際、前記隙間Ｙは回
転軸１の振動に対しスクイズ効果を有して制振作用を行
う。The oil flowing through the oil supply passages 6a and 5b of the casing 5 is supplied to the narrow gap Y between the casing 5 and the intermediate float ring 9, and then to the oil supply hole 10a of the intermediate float ring 9.
Intermediate floating ring 9 and floating bush 4a via lOb
, 4b, and is further oiled to the outer peripheral surface of the rotating shaft 1 through the oiling holes 7a, 7b of the floating bushes 4a, 4b. At this time, the gap Y is It has a squeezing effect on the vibration of the shaft 1 and performs a damping action.
中間フロートリング９の軸方向への移動は、り−ビン側
ではケーシング５に設けられた環状突起５ａにより、ブ
ロア側ではスラスト軸受１２の端部によシそれぞれ阻止
される。ま友浮動ブツシュ４ａ、４ｂの内側への移動は
中間フロートリング９に設けられた環状突起１３ａ、１
３ｂによシそれぞれ阻止される。さらに浮動ブツシュ４
ａのタービン側（図では左側）への移動は回転軸の段部
１ａにより、浮動ブツシュ４ｂのブロア側への移動はカ
ラー１５によシそれぞれ阻止される。The intermediate float ring 9 is prevented from moving in the axial direction by an annular protrusion 5a provided on the casing 5 on the bin side and by the end of the thrust bearing 12 on the blower side. The inward movement of the guide floating bushes 4a, 4b is performed using annular protrusions 13a, 1 provided on the intermediate floating ring 9.
3b, respectively. More floating bushes 4
The movement of the floating bush 4b toward the turbine side (left side in the figure) is prevented by the stepped portion 1a of the rotating shaft, and the movement of the floating bush 4b toward the blower side is prevented by the collar 15.
上記のように回転軸１０軸受部に中間フロートリング９
を設けることによシ、浮動ブツシュ４ａ。As mentioned above, the intermediate float ring 9 is attached to the rotating shaft 10 bearing part.
By providing a floating bush 4a.
４ｂを同期化し、さらに浮動ブツシュ４ａ、４ｂで不足
したスクイズ効果を中間フロートリング９とケーシング
５との間の隙間Ｙのスクイズ効果で補充することにより
、回転軸１の高速回転における制振作用を増大させるこ
とができる。4b and further supplement the squeeze effect lacking in the floating bushes 4a and 4b with the squeeze effect of the gap Y between the intermediate floating ring 9 and the casing 5, the vibration damping effect during high-speed rotation of the rotating shaft 1 can be improved. can be increased.
第４図に示す実施例では、ケーシング５の内周面に環状
突起５ａを設けたが、これに代シ第５図に示す実施例は
、ケーシング５のタービン側（左側）内周面に環状４１
５ｂを設け、この環状溝５ｂに中空円板例えば口Ｈング
、止め輪１８を挿入して固着したものである。その他の
構造は同一であるから説明を省略する。In the embodiment shown in FIG. 4, an annular protrusion 5a is provided on the inner peripheral surface of the casing 5, but in place of this, in the embodiment shown in FIG. 41
5b, and a hollow disc, such as a mouth H ring, and a retaining ring 18 are inserted and fixed into this annular groove 5b. Since the other structures are the same, their explanation will be omitted.
このように構成すれば、中間フロートリング９がタービ
ン側へ移動するのを阻止することができる。また隙間Ｙ
にた筐った油の円周方向の剪断抵抗が大きいため、中間
フロートリング９はほとんど回転しないので、割リング
または止め輪１８の割れ目は中間フロートリング９０回
転に悪影響を及ぼす恐れはない。With this configuration, it is possible to prevent the intermediate float ring 9 from moving toward the turbine. Also gap Y
Since the intermediate float ring 9 hardly rotates due to the large circumferential shearing resistance of the oil contained in the casing, there is no possibility that a crack in the split ring or retaining ring 18 will adversely affect the rotation of the intermediate float ring 90.
第５図に示す実施例では、ケーシング５のタービン側内
周面に中空円板１８を取付けたが、第６図に示す実施例
はケーシング５のブロア側（右側）にもタービン側（左
側）と同様に中空円板１８２を設け、かつ第５図のスラ
スト軸受１２を廃止したものである。その他の構造は同
一であるから説明を省略する。In the embodiment shown in FIG. 5, the hollow disk 18 is attached to the inner peripheral surface of the casing 5 on the turbine side, but in the embodiment shown in FIG. Similarly, a hollow disk 182 is provided, and the thrust bearing 12 shown in FIG. 5 is omitted. Since the other structures are the same, their explanation will be omitted.
このように構成すれば、中間フロートリング９が軸方向
（左右方向）へ移動するのを阻止することができ、かつ
スラスト軸受が不要となる。ずなわち回転軸１の右方向
への移動に対し、浮動ブツシュ４ａの端面と軸設付部１
４の端面によシ、回転軸１の左方向へ移動に対し、浮動
ブツシュ４ｂの端面とカラー１５の端面によシそれぞれ
阻止作用すなわちスラスト軸受作用を行う。したがって
中間フロートリング９のスクイズ効果によるダンピング
はなんら阻害とならない。With this configuration, it is possible to prevent the intermediate float ring 9 from moving in the axial direction (horizontal direction), and a thrust bearing is not required. That is, when the rotating shaft 1 moves to the right, the end face of the floating bush 4a and the shaft mounting portion 1
The end face of the floating bush 4b and the end face of the collar 15 respectively perform a blocking action, that is, a thrust bearing action against the leftward movement of the rotating shaft 1. Therefore, damping due to the squeeze effect of the intermediate floating ring 9 is not hindered in any way.
第７図に示す他の実施例は中間フロートリング９に設け
た給油孔１０ａ、１０ｂの外周部に円周溝２１ａ、２１
ｂをそれぞれ設けた点が第６図に示す実施例と異なる。Another embodiment shown in FIG.
This embodiment differs from the embodiment shown in FIG. 6 in that b is provided respectively.
これは、隙間Ｙが狭く、かつ中間フロートリング９の給
油孔１０は円周に複数個設けられているため、隙間Ｙ、
よシ十分に広くするためである。This is because the gap Y is narrow and a plurality of oil supply holes 10 of the intermediate float ring 9 are provided around the circumference.
This is to make it sufficiently wide.
この場合、中間フロートリング９によ多形成される隙間
Ｙの円周面積は浮動ブツシュ４ａ、４ｂによυ形成され
る隙間Ｘの円周面積よシ広くする。In this case, the circumferential area of the gap Y formed by the intermediate floating ring 9 is made larger than the circumferential area of the gap X formed by the floating bushes 4a and 4b.
このようにすれば円周溝２１ａ、２１ｂを設けても、隙
間Ｙのスクイズ効果による中間フロートリング９のスク
イズ作用は阻害されることはない。In this way, even if the circumferential grooves 21a and 21b are provided, the squeezing effect of the intermediate float ring 9 due to the squeezing effect of the gap Y will not be inhibited.
（９）
第８図に示す他の実施例は中間フロートリング９の環状
突起１３ａ、１３ｂ部に円周溝２１ａ１２１ｂから浮動
ブツシュ４ａ、４ｂの端面に向う給油路２２ａ、２２ｂ
をそれぞれ設けた点が第７図に示す実施例と異なり、そ
の他の構造は同一であるから説明を省略する。このよう
に構成すれば、円周溝２１ａ、２１ｂ内の油を給油路２
２ａ。(9) In another embodiment shown in FIG. 8, oil supply passages 22a and 22b are formed in the annular projections 13a and 13b of the intermediate float ring 9 from the circumferential grooves 21a and 121b toward the end surfaces of the floating bushes 4a and 4b.
This embodiment differs from the embodiment shown in FIG. 7 in that . With this configuration, the oil in the circumferential grooves 21a and 21b is transferred to the oil supply path 2.
2a.
２２ｂを経てスラスト軸受作用部へ給油することによシ
、浮動ブツシュ４ ａ”、、 ４ ｂの周囲は油で完全
に潤滑されると共に、隙間Ｘ、Ｙにも十分に油が充満さ
れる。By supplying oil to the thrust bearing acting portion through 22b, the surroundings of the floating bushes 4a'', 4b are completely lubricated with oil, and gaps X and Y are also sufficiently filled with oil.
以上説明したように本発明によれば、従来の浮動ブツシ
ュ外周部の隙間Ｘによるスクイズ効果に、さらに中間フ
ロートリング外周部の隙間Ｙによるスクイズ効果を重ね
合せることにより割振作用をよ如一層増大させることが
できる。As explained above, according to the present invention, the allocation effect is further increased by superimposing the squeezing effect due to the gap X on the outer periphery of the floating bush with the squeezing effect due to the gap Y on the outer periphery of the intermediate floating ring. be able to.
また本発明によれば、中間フロートリングを介して一対
の浮動ブツシュの移動を同期化させることによυ、割振
効果をよシ一層に向上させることができる。さらに従来
のスラスト軸受を廃止する（１０）
ことによシ、構造の簡略化および信頼性の向上をはかる
ことが可能である。Further, according to the present invention, by synchronizing the movement of the pair of floating bushes via the intermediate floating ring, the allocation effect can be further improved. Furthermore, by eliminating the conventional thrust bearing (10), it is possible to simplify the structure and improve reliability.
第１図および第２因は従来のターボ過給材の軸受装置の
正面断面図およびその浮動ブツシュ部の拡大断面図、第
３図は第２図における止め輪の側面図、第４図は本発明
のターボ過給機の軸受装置の一実施例を示す断面図、第
５図ないし第８図は本発明に係わる他の実施例の要部断
面図である。
１・・・回転軸、１ ａ、５ａ、１３ａ、１３ｋ）”・
阻止体、４ａ、４ｂ・・・浮動ブツシュ、９・・・中間
フロートリング、１０ａ、ｌｏｂ、２２ａ、２２ｂ・・
・給（１１）
箔り図
１へ 乙 図
第 ７ 図Figures 1 and 2 are a front cross-sectional view of a conventional turbocharger bearing device and an enlarged cross-sectional view of its floating bushing, Figure 3 is a side view of the retaining ring in Figure 2, and Figure 4 is the main A sectional view showing one embodiment of a bearing device for a turbocharger according to the invention, and FIGS. 5 to 8 are sectional views of essential parts of other embodiments according to the invention. 1...Rotating axis, 1a, 5a, 13a, 13k)"・
Blocker, 4a, 4b... Floating bush, 9... Intermediate floating ring, 10a, lob, 22a, 22b...
・Supply (11) Go to Foil Figure 1 Figure 7
Claims (1)
軸の両端にそれぞれ取付け、その回転軸を一対の浮動フ
ッシュによシ支持してなるターボ過給機において、前記
ケーシングと浮動ブツシュとの間に中間フロートリング
を浮動自在に設け、この中間フロートリングにより前記
浮動ブツシュを覆うように構成したことを特徴とするタ
ーボ過給機の軸受装置。 ２、中間フロートリングの両端部に浮動ブツシュへ給油
する任意数の給油孔をそれぞれ設けると共に、中央部に
浮動ブツシュからの排油を排出する排油孔を設けたこと
を特徴とする特許請求の範囲第１項記載のターボ過給機
の軸受装置。 ３３．ケーシングの内周面に中間フロートリングが軸方
向へ移動するのを抑制する阻止体を設けたことを特徴と
する特許請求の範囲第１項または第２項記載のターボ過
給機の軸受装置。 ４、中間フロートリングの内周面および回転軸に、浮動
ブツシュが軸方向へ移動するのを抑制する阻止体をそれ
ぞれ設けたことを特徴とする第１項ないし第３項のいず
れかに記載のターボ過給機の軸受装置。 ５、中間フロートリングに設けた内側突起の外周面と浮
動ブツシュの内側面との間の隙間に給油する給油路を中
間フロートリングに設けたことを特徴とする特許請求の
範囲第１項ないし第４項のいずれかに記載のターボ過給
戦の軸受装置。[Claims] 1. In a turbocharger in which a turbine and a blower housed in a casing are respectively attached to both ends of a rotating shaft, and the rotating shaft is supported by a pair of floating fishes, the casing and 1. A bearing device for a turbocharger, characterized in that an intermediate float ring is freely floating between the floating bush and the floating bush is covered by the intermediate float ring. 2. A patent claim characterized in that an arbitrary number of oil supply holes for supplying oil to the floating bushings are provided at both ends of the intermediate floating ring, and an oil drain hole for discharging waste oil from the floating bushings is provided in the center part. A bearing device for a turbocharger according to scope 1. 33. 3. A bearing device for a turbocharger according to claim 1, further comprising a blocking body provided on the inner circumferential surface of the casing to prevent the intermediate float ring from moving in the axial direction. 4. The device according to any one of items 1 to 3, wherein a blocking body for suppressing movement of the floating bush in the axial direction is provided on the inner circumferential surface of the intermediate float ring and on the rotating shaft, respectively. Bearing device for turbocharger. 5. Claims 1 to 5, characterized in that the intermediate float ring is provided with an oil supply path for supplying oil to the gap between the outer peripheral surface of the inner protrusion provided on the intermediate float ring and the inner surface of the floating bush. 4. The bearing device for turbocharging according to any one of Item 4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56126665A JPS5830420A (en) | 1981-08-14 | 1981-08-14 | Bearing device of turbosupercharger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56126665A JPS5830420A (en) | 1981-08-14 | 1981-08-14 | Bearing device of turbosupercharger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5830420A true JPS5830420A (en) | 1983-02-22 |
Family
ID=14940834
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56126665A Pending JPS5830420A (en) | 1981-08-14 | 1981-08-14 | Bearing device of turbosupercharger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5830420A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60215821A (en) * | 1984-04-05 | 1985-10-29 | Murata Mach Ltd | Preparation of spun yarn |
| US5137286A (en) * | 1991-08-23 | 1992-08-11 | General Electric Company | Permanent magnet floating shaft seal |
| DE4230037A1 (en) * | 1991-09-09 | 1993-03-11 | Aisin Seiki | CENTRIFUGAL RECHARGE BLOWER |
-
1981
- 1981-08-14 JP JP56126665A patent/JPS5830420A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60215821A (en) * | 1984-04-05 | 1985-10-29 | Murata Mach Ltd | Preparation of spun yarn |
| US5137286A (en) * | 1991-08-23 | 1992-08-11 | General Electric Company | Permanent magnet floating shaft seal |
| DE4230037A1 (en) * | 1991-09-09 | 1993-03-11 | Aisin Seiki | CENTRIFUGAL RECHARGE BLOWER |
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