JPS5893932A - Lubricating oil leakage preventer for turbo supercharger - Google Patents
Lubricating oil leakage preventer for turbo superchargerInfo
- Publication number
- JPS5893932A JPS5893932A JP19195981A JP19195981A JPS5893932A JP S5893932 A JPS5893932 A JP S5893932A JP 19195981 A JP19195981 A JP 19195981A JP 19195981 A JP19195981 A JP 19195981A JP S5893932 A JPS5893932 A JP S5893932A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- lubricating oil
- exhaust
- shaft seal
- turbine
- 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
- 239000010687 lubricating oil Substances 0.000 title claims abstract description 27
- 230000002265 prevention Effects 0.000 claims description 5
- 238000013016 damping Methods 0.000 abstract description 6
- 230000010349 pulsation Effects 0.000 description 18
- 239000003921 oil Substances 0.000 description 6
- 230000000694 effects Effects 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
Classifications
-
- 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
- F01D25/18—Lubricating arrangements
- F01D25/183—Sealing means
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
Description
【発明の詳細な説明】
この発明は内燃機関の排気エネルギで駆動される排気タ
ーが過給機において、軸受部潤滑油の漏れ防止装置の改
良に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a bearing lubricating oil leak prevention device in a supercharger whose exhaust gas is driven by the exhaust energy of an internal combustion engine.
機関排気ガスのエネルギにより排気タービンを回わし、
これと同軸上の吸気コンプレッサを駆動することによシ
、吸気を過給して機関出方や燃費の改善をはかるように
したターが過給機が広く知られている。The exhaust turbine is rotated by the energy of the engine exhaust gas,
A well-known turbocharger is a turbocharger that drives an intake compressor on the same axis to supercharge intake air to improve engine output and fuel efficiency.
このターボ過給機は自動車用の場合毎分致方回転あるい
はそれ以上に高回転するため、回転軸の摩擦損失を可及
的に小さくする必要があり、通常は７０−ティング軸受
を用い、かつ大量の潤滑油を供給して回転効率を高める
ようにしている。Since this turbocharger for automobiles rotates at a high speed of 100 rpm or more, it is necessary to minimize the friction loss of the rotating shaft, and usually a 70-ring bearing is used. A large amount of lubricating oil is supplied to increase rotational efficiency.
ところが、このように潤滑油を大量に循環させると、軸
シール部から排気タービンあるいは吸気コンプレッサ側
が負圧化したときなどに漏洩する油の消＊量が、長時間
の無補給潤滑いいかえれば、メインテナンスフリー化に
とって大きな支障となっていた。However, when a large amount of lubricating oil is circulated in this way, the amount of oil that leaks from the shaft seal when the exhaust turbine or intake compressor side becomes negative pressure is reduced, resulting in long-term lubrication or maintenance. This was a major hindrance to freeing.
そこで、従来、第１図に示すような潤滑油漏れ防止装置
が提案された（実開昭４８−５１ｔＪＢ号）。Therefore, a lubricating oil leakage prevention device as shown in FIG. 1 has been proposed (Utility Model Application No. 1983-51tJB).
図中１は排気ガスによシ回わる排気タービン、２は回転
軸３を介して排気タービン１と同軸上に連結された吸気
コンプレッサ、４はタービンハウジンク５に形成した排
気通路（スクロール）、６はコンプレッサハウジング７
に形成した吸気通路（スクロール）である。In the figure, 1 is an exhaust turbine that is rotated by exhaust gas, 2 is an intake compressor coaxially connected to the exhaust turbine 1 via a rotating shaft 3, 4 is an exhaust passage (scroll) formed in the turbine housing 5, 6 is compressor housing 7
This is an intake passage (scroll) formed in the
そして回転軸３はセンタハウジング８の内部で軸受９を
介して回転自由に支持され、軸受９の周囲には潤滑油が
供給される＠滑油室１ｏが形成される。The rotating shaft 3 is rotatably supported inside the center housing 8 via a bearing 9, and a lubricating oil chamber 1o is formed around the bearing 9 to which lubricating oil is supplied.
Ｔｈｌ’ｔｉｉ油案１０とタ油上１０ウジング５及びコ
ンプレッサハウジング７との間に扛、回転軸３の外周に
位置して軸シール部１２と１３が設けられるとともに、
潤滑油室１０の両側に位置しで環状の空気導入室１４．
１５が形成され、この空気導入室１４．１５と排気ター
ビン１及び吸気コンプレッサ２の背面との連通部に環状
の弁体１５，１７がその外周部を固定された状態で設け
られる。Shaft seals 12 and 13 are provided between the Thl'tii oil draft 10, the oil top 10 housing 5, and the compressor housing 7, and are located on the outer periphery of the rotating shaft 3.
An annular air introduction chamber 14 located on both sides of the lubricating oil chamber 10.
15 is formed, and annular valve bodies 15 and 17 are provided in a communicating portion between the air introduction chamber 14.15 and the back surface of the exhaust turbine 1 and the intake compressor 2, with their outer peripheries fixed.
空気導入室１４．１５には吸気コンプレッサ２の吐出空
気が、バイア’１８Ａ、１８Ｂ及びセンタハウジング８
の通Ｔｈ１９Ａ、１９Ｂを介してそれぞれ導入される。The discharge air of the intake compressor 2 enters the air introduction chamber 14.15 through the vias 18A, 18B and the center housing 8.
are introduced through Th19A and Th19B, respectively.
上記環状弁体１６と１７は常態ではその弾性力によυ空
気導入室１４．１５と排気タービン１及び吸気コンプレ
ッサ２との連通を邂断するように、センタハウジング８
の両側からそれぞれ内側に向けて圧着しているが、例え
ば排気タービン１の背面の圧力が排気脈動により低圧化
して、弁体１６の前後差圧が一定値を越えたときに排気
タービン１側に弾性変形し、空気導入室１４がらの高圧
空気を、回転軸３の周囲から排気タービン１の背面に供
給し、これによシこの付近の圧力を相対的に高め、軸シ
ール部１２を境にして潤滑油室ｌＯよシも排気タービン
１の背面の圧力が極端に下がるのを防いで、潤滑油の排
気タービン１側への漏洩を減小させるようにしている。The annular valve bodies 16 and 17 are arranged in the center housing 8 so that under normal conditions, their elastic force causes communication between the air introduction chamber 14.15 and the exhaust turbine 1 and the intake compressor 2 to be interrupted.
For example, when the pressure at the back of the exhaust turbine 1 decreases due to exhaust pulsation and the differential pressure across the valve body 16 exceeds a certain value, pressure is applied to the exhaust turbine 1 side from both sides. It deforms elastically and supplies high-pressure air from the air introduction chamber 14 to the back of the exhaust turbine 1 from around the rotating shaft 3, thereby relatively increasing the pressure in this area, and increasing the pressure around the shaft seal part 12. The lubricating oil chamber 1O and the lubricating oil chamber 10 are also designed to prevent the pressure on the back side of the exhaust turbine 1 from dropping excessively, thereby reducing leakage of lubricating oil to the exhaust turbine 1 side.
しかしながら、この場合にはタービンハウジング５の内
部の排気通路（スクロール）４の排気脈動が、排気ター
ビン１の背面の隙間から、回転軸３の軸シール部１２に
直接的に作用するため、とくに排気脈動の高周波域（機
関高回転域）で、弁体１６がこの脈動に追従しきれなく
なって高圧空気の導入が不十分になると、排気タービン
ｌの背面圧力の脈動を緩和できず、脈動負圧によシ潤滑
油室ｌＯの潤滑油が回転軸３と軸シール部１２０環状微
小隙間から排気タービン１側へと漏洩しやすくなる傾向
があった。However, in this case, the exhaust pulsation in the exhaust passage (scroll) 4 inside the turbine housing 5 directly acts on the shaft seal portion 12 of the rotating shaft 3 through the gap on the back surface of the exhaust turbine 1. If the valve body 16 is unable to follow the pulsation in the high frequency range of pulsation (high engine speed range) and the introduction of high pressure air becomes insufficient, the pulsation of the back pressure of the exhaust turbine l cannot be alleviated, resulting in pulsating negative pressure. There was a tendency for the lubricating oil in the lubricating oil chamber lO to easily leak from the annular minute gap between the rotating shaft 3 and the shaft seal portion 120 to the exhaust turbine 1 side.
高周波排気脈動に対応しての追従性を高めるために、環
状弁体１６の板厚を薄くすると、排気熱による影響で変
形を生じて高回転する排気タービン１と干渉する恐れが
あシ、実用的には解決しなければならない問題が多過ぎ
るという欠点があった。If the plate thickness of the annular valve body 16 is made thinner in order to improve followability in response to high-frequency exhaust pulsations, there is a risk of deformation due to the influence of exhaust heat and interference with the high-speed exhaust turbine 1. The downside was that there were too many problems to solve.
そこで本発明は、回転軸の周囲において軸シール部と排
気タービン背面との間で形成される環状通路の途中に、
回転軸の外周との間で絞り部を設け、かつこの絞シ部と
軸シール部との間に十分な容積の圧力緩衝室を形成し、
この圧力緩衝室に吸気コンプレッサの吐出圧をチェック
弁を介して導入するようにして、排気タービン背面の隙
間からの排気脈動を低周波域から高周波域まで、絞ル部
と圧力緩衝室とで十分に減衰し、潤滑油の漏洩の減小を
はかったターボ過給機の潤滑油漏れ防止装置を提供する
ことを目的とするものである。Therefore, the present invention provides an annular passage formed between the shaft seal portion and the back surface of the exhaust turbine around the rotating shaft.
A constriction part is provided between the outer periphery of the rotating shaft, and a pressure buffer chamber of sufficient volume is formed between the constriction part and the shaft seal part,
By introducing the discharge pressure of the intake compressor into this pressure buffer chamber through a check valve, the exhaust pulsation from the gap at the back of the exhaust turbine can be suppressed from the low frequency range to the high frequency range by the throttle part and the pressure buffer chamber. It is an object of the present invention to provide a lubricating oil leakage prevention device for a turbo supercharger that reduces lubricating oil leakage.
以下、本発明の実施例を図面にもとづいて説明するが、
第２図の実施例において実質的に第１図と同一部分には
、同一符号を用いることにする。Examples of the present invention will be described below based on the drawings.
In the embodiment of FIG. 2, parts that are substantially the same as those in FIG. 1 are designated by the same reference numerals.
センタハウジング８とタービンハウジング５との間に挾
持された状態で、排気タービン１の背面に近接して環状
の遮熱板２０が設けられる。遮熱板２０の外周フランジ
部２１はセンタハウジング８とともにタービンハウジン
グ５にポルト２２で共線めされる一方、中心の開口部２
３は回転軸３′の外周に近接し、これらの間に微小環状
間隙からなる絞シ部２４を゛形成している。An annular heat shield plate 20 is provided close to the back surface of the exhaust turbine 1 while being sandwiched between the center housing 8 and the turbine housing 5 . The outer peripheral flange portion 21 of the heat shield plate 20 is collinear with the center housing 8 and the turbine housing 5 at a port 22, while the center opening 2
3 is close to the outer periphery of the rotating shaft 3', and a constriction part 24 consisting of a minute annular gap is formed therebetween.
そして、遮熱板２０の内壁とセンターハウジング８の外
側壁及び回転軸３の外周との間で、十分な容積空間をも
つ圧力緩衝室２５を区画形成する３圧力緩衝室２５には
チェック弁２６を介して、通路２７及びパイプ２８を経
由して導く吸気コンプレッサ２の吐出圧を作用させる。A check valve 26 is installed in the three pressure buffer chambers 25 that partition and form a pressure buffer chamber 25 having a sufficient volume space between the inner wall of the heat shield plate 20, the outer wall of the center housing 8, and the outer periphery of the rotating shaft 3. The discharge pressure of the intake compressor 2 is applied via the passage 27 and the pipe 28.
したがって、軸シール部１２の外側には、排気タービン
１側の排気圧力が直接にかからずに、回転軸外周に環状
通路２９を経て圧力緩衝室２５の略一定の正圧（これに
ついては後述する。）が作用する。なお、軸シール部１
２の内側には、給油路３ｏからフローティング軸受９（
この実施例では２つの軸受９，９で回転軸３を支持して
いる）に通口３１を介して導かれる潤滑油の一部が流れ
る。Therefore, the exhaust pressure on the exhaust turbine 1 side is not directly applied to the outside of the shaft seal portion 12, but is passed through the annular passage 29 to the outer periphery of the rotating shaft to maintain a substantially constant positive pressure in the pressure buffer chamber 25 (this will be described later). ) is in effect. In addition, the shaft seal part 1
2, a floating bearing 9 (
In this embodiment, a portion of the lubricating oil introduced through the opening 31 flows into the rotary shaft 3 supported by two bearings 9, 9.
潤滑油室１０からは図示しないリデーバ（オイル・平ン
）へと潤滑及び冷却を行った油が排出口３２を経て流出
する。The lubricating and cooling oil flows out from the lubricating oil chamber 10 to a redevater (oil flat) not shown through a discharge port 32.
次に作用を説明すると、排気タービン１の排気通路（ス
クロール）４には、機関排気圧力脈動が直接的に伝達さ
れ、さらに排気タービン１の背面と遮熱板２０との間隙
３３にも作用する。Next, to explain the operation, engine exhaust pressure pulsations are directly transmitted to the exhaust passage (scroll) 4 of the exhaust turbine 1, and also act on the gap 33 between the back surface of the exhaust turbine 1 and the heat shield plate 20. .
そして、この圧力脈動は既熱板２０の開口部２３と回転
軸３の間の絞シ部２４を経て、圧力緩衝室２５にて拡張
されてから軸シール部１２の外側へも伝達される。This pressure pulsation passes through the constriction part 24 between the opening 23 of the heated plate 20 and the rotary shaft 3, is expanded in the pressure buffer chamber 25, and is also transmitted to the outside of the shaft seal part 12.
しかしこの圧力脈動は絞９部２４と圧力緩衝室２５のダ
ンピング作用で減衰され、とくに高周波域の脈動に対す
るほどそのダンピング効果は大きく、これにより軸シー
ル部】２の外側の圧力（圧力緩衝室２５の圧力）をほぼ
一定に保ちすなわち排気脈動による負圧化を防ぎ、軸シ
ール部１２と回転軸３との微小間隙を経ての潤滑油の漏
洩を確実に防止するのである。However, this pressure pulsation is attenuated by the damping effect of the throttle 9 part 24 and the pressure buffer chamber 25, and the damping effect is particularly large for pulsations in the high frequency range. In other words, negative pressure caused by exhaust pulsation is prevented, and leakage of lubricating oil through the minute gap between the shaft seal portion 12 and the rotating shaft 3 is reliably prevented.
ところで、このような高周波の圧力脈動に対しては十分
な働きを発揮することができても、機関低回転域での低
周波の脈動に対しては、圧力緩衝室２５の空間容積に限
りがあるため、十分に圧力脈動を抑えることができなく
なる。By the way, even if the pressure buffer chamber 25 has a sufficient effect against such high-frequency pressure pulsations, the space volume of the pressure buffer chamber 25 is limited against low-frequency pulsations in the low engine speed range. Therefore, pressure pulsation cannot be suppressed sufficiently.
しかし、このような場合には、圧力緩衝室２５の圧力が
低下して吸気コンプレッサ吐出圧との差圧が一定値を越
えると、チェック弁２６が一升してパイｆ２７、通路２
６を経て圧力緩衝室２５に吸気コングレツサ出口圧力を
導入し、軸シール部１２の外側圧力を高く保つのである
。However, in such a case, if the pressure in the pressure buffer chamber 25 decreases and the differential pressure with the intake compressor discharge pressure exceeds a certain value, the check valve 26 will be closed to the pi f27 and the passage 2.
6, the intake congressor outlet pressure is introduced into the pressure buffer chamber 25, and the pressure outside the shaft seal portion 12 is kept high.
チェック弁２６は低周波の圧力脈動には応答よく追従で
きるため、この領域での圧力緩衝室２５の負圧化を確実
に阻止し、上記と同様潤滑油の漏洩を防止するのである
。Since the check valve 26 can respond well to low-frequency pressure pulsations, it reliably prevents the pressure buffer chamber 25 from becoming negative pressure in this region, thereby preventing leakage of lubricating oil as described above.
第３図に圧力緩衝室２５の圧力特性を示すが、機関低回
転域から高回転域まで、排気圧力脈動の上限と下限（曲
線＆ ＋ ）ｉｒ２で示す）に大きな差異があるにもか
かわらず、はぼ一定の正圧Ｐｘに保持できることを示し
ている。Figure 3 shows the pressure characteristics of the pressure buffer chamber 25, and although there is a large difference in the upper and lower limits (indicated by the curve &+)ir2 of the exhaust pressure pulsation from the low engine speed range to the high engine speed range, , indicates that it is possible to maintain an approximately constant positive pressure Px.
なお、潤滑油室１０を機関ブローバイガス通路に接続す
ることにより、大気圧よシも若干低い負圧Ｐｏに設定す
ると、軸シール部１２の内側圧力を外側圧力よシも確実
に下げて、潤滑油漏れの防止機能を高められる。By connecting the lubricating oil chamber 10 to the engine blow-by gas passage, the negative pressure Po, which is slightly lower than the atmospheric pressure, can be set to ensure that the inner pressure of the shaft seal portion 12 is lowered as well as the outer pressure, thereby improving the lubrication. Improves oil leak prevention function.
次に、第４図の第２実施例を説明すると、チェック弁２
６として、皿バネのような環状弁体３５を、遮熱板２０
の内壁に外周部３５Ａを固定し、内周部３５ＢＫ−セン
タハウジング８の外壁に弾性圧着させたもので、これに
より受圧面積を拡大して微小差圧でも確実に開弁させら
れるようにした。Next, to explain the second embodiment shown in FIG. 4, the check valve 2
6, an annular valve body 35 like a disc spring is connected to the heat shield plate 20.
The outer peripheral part 35A is fixed to the inner wall of the center housing 8, and the inner peripheral part 35BK is elastically crimped to the outer wall of the center housing 8, thereby expanding the pressure receiving area and ensuring that the valve can be opened even with a small differential pressure.
そして、環状弁体３５で仕切られた圧力緩衝室２５の外
周の空気溜３６が大きくとれるので、予めこの空気溜３
６に導かれているコンプレッサ吐出圧を開弁時に応答よ
く瞬時に導入でき、圧力緩衝室２５の圧力脈動幅を非常
に小さくできる。Since the air reservoir 36 on the outer periphery of the pressure buffer chamber 25 partitioned by the annular valve body 35 can be made large, this air reservoir 36 can be prepared in advance.
The compressor discharge pressure introduced into the pressure buffer chamber 25 can be introduced instantaneously with good response when the valve is opened, and the width of pressure pulsation in the pressure buffer chamber 25 can be made very small.
なお、環状弁体３５は遮熱板２ｏの内側にあるため熱的
に保護され、したがって板厚は開弁応答性が高まるよう
に十分に薄肉化できる。Since the annular valve body 35 is located inside the heat shield plate 2o, it is thermally protected, and therefore, the plate thickness can be made sufficiently thin so as to improve the valve opening response.
以上説明したように本発明は、回転軸の軸シール部と排
気タービン背面との通路中に絞シ部を設け、この絞９部
と軸シール部との間に十分な容積空間をもつ圧力緩衝室
を形成し、この圧力緩衝室にチェック弁を介して吸気コ
ンプレッサ吐出圧を導入するようにしたため、排気脈動
圧力の低周波域から高周波域まで軸シール部に排気ター
ビン側から作用する圧力を、常時はぼ一定の正圧に保持
でき、センタハウジング内の潤滑油室から排気ターヒン
側への潤滑油の漏洩を確実に防止することができる。As explained above, the present invention provides a pressure buffer in which a restriction part is provided in the passage between the shaft seal part of the rotating shaft and the back surface of the exhaust turbine, and a sufficient volume space is provided between the restriction part and the shaft seal part. By forming a chamber and introducing the intake compressor discharge pressure into this pressure buffer chamber via a check valve, the pressure acting on the shaft seal from the exhaust turbine side from the low frequency range to the high frequency range of exhaust pulsating pressure can be reduced. A substantially constant positive pressure can be maintained at all times, and leakage of lubricating oil from the lubricating oil chamber in the center housing to the exhaust engine side can be reliably prevented.
第１図は従来装置の断面図である。
第２図は本発明の第１実施例の断面図、第３図は圧力緩
衝室の圧力特性図、第４図は第２実施例の断面図である
。
ｌ・・・排気タービン、２・・・吸気コンプレッサ、３
・・・回転軸、４・・・排気通路（スクロール）、６・
・・吸気通ｕ（スクロール）、５・・・タービンハウジ
ング、７・・・コングレツサハウジング、８・・・セン
タハウジング、９・・・フローティング軸受、１０・・
・潤滑油室、１２・・・軸シール部、２０遮熱板、２３
・・・開口部、２４・・・絞９部、２５・・・圧力緩衝
室、２６・・・チェック弁、３５・・・環状弁体、３６
・・・空気溜。
特許出願人 日産自動車株式会社
第１図FIG. 1 is a sectional view of a conventional device. FIG. 2 is a sectional view of the first embodiment of the present invention, FIG. 3 is a pressure characteristic diagram of the pressure buffer chamber, and FIG. 4 is a sectional view of the second embodiment. l...exhaust turbine, 2...intake compressor, 3
... Rotating shaft, 4... Exhaust passage (scroll), 6.
...Intake air u (scroll), 5...Turbine housing, 7...Congressor housing, 8...Center housing, 9...Floating bearing, 10...
・Lubricating oil chamber, 12...Shaft seal section, 20 Heat shield plate, 23
... Opening part, 24 ... Throttle 9 part, 25 ... Pressure buffer chamber, 26 ... Check valve, 35 ... Annular valve body, 36
...Air pocket. Patent applicant Nissan Motor Co., Ltd. Figure 1
Claims (1)
付け、センタノ・ウジングに軸受を介して回転軸を回転
自由に支持するとともに、軸受の外側に位置して潤滑油
の軸シール部を配設したターボ過給機において、上記軸
シール部と排気タービン背面との間に位置する回転軸の
外周項隙通路に、絞シ部とその内側に十分な容積空間を
もつ圧力緩衝室とを形成し、圧力緩衝室に吸気コンプレ
ッサ吐出圧をチェック弁を介して導入するようにしたこ
とを特徴とするターボ過給機の潤滑油漏れ防止装置。The exhaust turbine and intake compressor are mounted on a coaxial rotating shaft, and the rotating shaft is freely supported through a bearing in the centano housing, and a shaft seal for lubricating oil is located outside of the bearing. In a turbocharger, a pressure buffer chamber with a throttle part and a sufficient volume space inside the throttle part is formed in the outer circumferential clearance passage of the rotating shaft located between the shaft seal part and the back surface of the exhaust turbine. A lubricating oil leak prevention device for a turbo supercharger, characterized in that an intake compressor discharge pressure is introduced into a buffer chamber via a check valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19195981A JPS5893932A (en) | 1981-11-30 | 1981-11-30 | Lubricating oil leakage preventer for turbo supercharger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19195981A JPS5893932A (en) | 1981-11-30 | 1981-11-30 | Lubricating oil leakage preventer for turbo supercharger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5893932A true JPS5893932A (en) | 1983-06-03 |
Family
ID=16283288
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19195981A Pending JPS5893932A (en) | 1981-11-30 | 1981-11-30 | Lubricating oil leakage preventer for turbo supercharger |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5893932A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2746849A1 (en) * | 1996-03-29 | 1997-10-03 | Aisin Seiki | FUEL TURBOCHARGER |
| WO2004063535A1 (en) * | 2003-01-10 | 2004-07-29 | Honeywell International Inc. | Sealing means for a lubrication system in a turbocharger |
| EP2336571A1 (en) * | 2009-12-15 | 2011-06-22 | Perkins Engines Company Limited | System for reducing compressor oil consumption |
| US8328509B2 (en) | 2007-10-13 | 2012-12-11 | Cummins Turbo Technologies Limited | Turbomachine |
| JP2017527739A (en) * | 2014-09-23 | 2017-09-21 | ボーグワーナー インコーポレーテッド | Turbocharger with integrated actuator |
| CN107407222A (en) * | 2014-11-20 | 2017-11-28 | 沃尔沃卡车集团 | The method and system for preventing machine oil from escaping |
| CN107725175A (en) * | 2017-10-18 | 2018-02-23 | 山东交通学院 | A kind of resonant pulse energy sustained release turbo charge system of spring oscillator |
| GB2569372A (en) * | 2017-12-15 | 2019-06-19 | Ford Global Tech Llc | Turbocharger heat shield |
-
1981
- 1981-11-30 JP JP19195981A patent/JPS5893932A/en active Pending
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2746849A1 (en) * | 1996-03-29 | 1997-10-03 | Aisin Seiki | FUEL TURBOCHARGER |
| WO2004063535A1 (en) * | 2003-01-10 | 2004-07-29 | Honeywell International Inc. | Sealing means for a lubrication system in a turbocharger |
| US8328509B2 (en) | 2007-10-13 | 2012-12-11 | Cummins Turbo Technologies Limited | Turbomachine |
| US8727715B2 (en) | 2007-10-13 | 2014-05-20 | Cummins Turbo Technologies Limited | Turbomachine |
| WO2011073620A3 (en) * | 2009-12-15 | 2011-09-22 | Perkins Engines Company Limited | System for reducing compressor oil consumption |
| CN102656369A (en) * | 2009-12-15 | 2012-09-05 | 珀金斯发动机有限公司 | System for reducing compressor oil consumption |
| EP2336571A1 (en) * | 2009-12-15 | 2011-06-22 | Perkins Engines Company Limited | System for reducing compressor oil consumption |
| US9261106B2 (en) | 2009-12-15 | 2016-02-16 | Perkins Engines Company Limited | System for reducing compressor oil consumption |
| JP2017527739A (en) * | 2014-09-23 | 2017-09-21 | ボーグワーナー インコーポレーテッド | Turbocharger with integrated actuator |
| CN107407222A (en) * | 2014-11-20 | 2017-11-28 | 沃尔沃卡车集团 | The method and system for preventing machine oil from escaping |
| CN107407222B (en) * | 2014-11-20 | 2020-08-25 | 沃尔沃卡车集团 | Method and system for preventing oil from escaping |
| CN107725175A (en) * | 2017-10-18 | 2018-02-23 | 山东交通学院 | A kind of resonant pulse energy sustained release turbo charge system of spring oscillator |
| CN107725175B (en) * | 2017-10-18 | 2024-03-26 | 山东交通学院 | Spring vibrator resonance type pulse energy delayed release turbocharging system |
| GB2569372A (en) * | 2017-12-15 | 2019-06-19 | Ford Global Tech Llc | Turbocharger heat shield |
| GB2569372B (en) * | 2017-12-15 | 2019-12-11 | Ford Global Tech Llc | Turbocharger heat shield |
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