JPH02173323A - Lubrication device for supercharger - Google Patents
Lubrication device for superchargerInfo
- Publication number
- JPH02173323A JPH02173323A JP32585588A JP32585588A JPH02173323A JP H02173323 A JPH02173323 A JP H02173323A JP 32585588 A JP32585588 A JP 32585588A JP 32585588 A JP32585588 A JP 32585588A JP H02173323 A JPH02173323 A JP H02173323A
- Authority
- JP
- Japan
- Prior art keywords
- supercharger
- engine
- oil
- amount
- exhaust 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
- 238000005461 lubrication Methods 0.000 title claims 6
- 238000001514 detection method Methods 0.000 claims abstract description 8
- 239000003921 oil Substances 0.000 claims description 76
- 239000010687 lubricating oil Substances 0.000 claims description 4
- 239000000314 lubricant Substances 0.000 claims 3
- 230000001050 lubricating effect Effects 0.000 claims 2
- 238000011144 upstream manufacturing Methods 0.000 claims 1
- 230000006835 compression Effects 0.000 abstract 1
- 238000007906 compression Methods 0.000 abstract 1
- 230000008844 regulatory mechanism Effects 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
Landscapes
- Supercharger (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は排気タービン式過給機の給油量をエンジン運転
条件に応して変化させることに関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to varying the amount of oil supplied to an exhaust turbine supercharger in response to engine operating conditions.
排気タービン式過給機の給油圧力を変化させる例として
は実開昭61−1.692]、3号、実開昭62117
238等かあり、特に実開昭62− ]、、1.723
8ではエンジン回転数等のエンジン運転条件を検出し給
油量を変化させている。しかし、これらの構造は給油温
度の−I−Aを防く、また給油温度の変化による給油量
の変化製補正することが「目的であった。つまり排気タ
ービン式過給機の軸受を保護すること、及び油量の過多
によるオイル洩れの防止が目的であり、エンジンが高速
高負荷運転時の給油量制御か主で、低速低負荷時の給油
量については制御されていなかった。Examples of changing the oil supply pressure of an exhaust turbine supercharger are Utility Model Application No. 61-1.692], No. 3, and Utility Model Application No. 62117.
238 etc., especially 1.723
8, engine operating conditions such as engine speed are detected and the amount of oil supplied is changed. However, the purpose of these structures was to prevent -I-A of the oil supply temperature and to compensate for changes in the oil supply amount due to changes in the oil supply temperature. The purpose was to prevent oil leakage due to excessive oil volume, and the amount of oil supplied was mainly controlled when the engine was operating at high speeds and high loads, and the amount of oil supplied at low speeds and low loads was not controlled.
1−記従来技術では給油ポンプによって消費されるエン
ジン動力については配慮されておらず、エンジンが低速
低負荷運転時には排気タービン式過給機が必要とする油
量共」二の給油か行なわれ、過給機を用いないエンジン
に比ベオイルボンブによって消費される動力か多く低速
低負荷時のエンジン効率を悪化されていた。1- In the prior art, no consideration is given to the engine power consumed by the oil supply pump, and when the engine is operating at low speed and low load, the amount of oil required by the exhaust turbine supercharger is refueled. Compared to an engine that does not use a supercharger, the oil bomb consumes more power, which deteriorates engine efficiency at low speeds and low loads.
特に機械式過給機と排気ター ヒン式過給機を組み合わ
せて用いる場合、排気タービン式過給機は高速高負荷用
に設定されているため、低速低負荷時にはほとんど給/
ll+は必要無いにもかかわらず、従来技術では通常の
給油を行ない、エンジン効率を悪化さセていた。Especially when a mechanical turbocharger and an exhaust turbine turbocharger are used in combination, the exhaust turbine turbocharger is designed for high speed and high load, so at low speed and low load there is almost no supply or
Even though ll+ is not necessary, the conventional technology performs normal refueling, which deteriorates engine efficiency.
本発明は低速低負荷時エンジンのオイルポンプの負荷を
低減しエンジン効率を向」ニさせることを目的とする。An object of the present invention is to reduce the load on the oil pump of an engine at low speeds and low loads, thereby improving engine efficiency.
3− 、 l記[」的を達成するために、エンジンの運
転条件を検出する検出装置を設け、該検出装置からの伯
−じ−によりJJI気タービン式過給機の必要油量を算
出し、該必要油量を最低でも確保する様に給油装置の吐
出油量を制御し、給油装置が余分な仕事をしない様にし
たものである。3-, In order to achieve the objective described in [1], a detection device is installed to detect the operating conditions of the engine, and the required amount of oil for the JJI air turbine supercharger is calculated based on the calculation from the detection device. The amount of oil discharged from the oil supply device is controlled so as to secure at least the required amount of oil, so that the oil supply device does not perform unnecessary work.
2、また給油量の制御を節11iに行なうために、通常
の給油量が排気タービン式過給機の必要油量に比較して
はるかに多い、低速低負荷時のめに給油量制御を行なう
様にしたものである。2. Also, in order to control the amount of oil supplied at node 11i, the amount of oil supplied is controlled at low speeds and low loads, when the normal amount of oil supplied is much larger than the amount of oil required by the exhaust turbine supercharger. It was made in a similar manner.
3、給油装置の消費する動力を効率良く低減するため、
給油油量の低減を給油装置の負荷低減(例えば回転数低
減等)によって達成する様にしたものである。3. In order to efficiently reduce the power consumed by the oil supply system,
The reduction in the amount of oil to be supplied is achieved by reducing the load on the oil supply device (for example, by reducing the number of revolutions).
4、給油量の制御を簡単に行なうために、給油装置から
排気タービン式過給機に潤滑油を供給する給油管に給油
量調節機構を設けたものである。4. In order to easily control the amount of oil supplied, an oil supply amount adjusting mechanism is provided in the oil supply pipe that supplies lubricating oil from the oil supply device to the exhaust turbine supercharger.
5、給油油量の低減による給油装置の消費動力の低減効
果を高めるため、エンジンが低速低負荷運転時に排気タ
ービン式過給機の必要油量が少ない、機械駆動式過給機
と排気タービン式過給機を絹み合わせて使用するシステ
11に採用したものである。5. In order to increase the effect of reducing the power consumption of the refueling system by reducing the amount of oil supplied, the exhaust turbine type supercharger requires less oil when the engine is operating at low speed and low load. This system was adopted in system 11, which uses a supercharger in combination.
6、給油油量の低減による給油装置の消費動力の低減効
果を高めるため、排気タービン式過給機用の潤滑油量の
多い2つの排気タービン式過給機を用いるシステムに採
用したものである。6. In order to increase the effect of reducing the power consumption of the oil supply system by reducing the amount of lubricating oil, this system was adopted for a system that uses two exhaust turbine superchargers with a large amount of lubricating oil for the exhaust turbine supercharger. .
エンジンの運転状態を検出する検出手段からの信号によ
り、排気タービン式過給機の必要油量を泪算し、その必
要油量を最低確保する油量を供給する様に給油装置の吐
出油量を制御する。The amount of oil required for the exhaust turbine supercharger is calculated based on the signal from the detection means that detects the operating state of the engine, and the amount of oil discharged from the oil supply device is adjusted to supply the amount of oil that ensures the minimum amount of oil required. control.
それによって給油装置の動力を最小に押えることができ
るためエンジン効率か向上する。This allows the power of the refueling system to be kept to a minimum, thereby improving engine efficiency.
以下本発明の実施例を添付図面により説明する。 Embodiments of the present invention will be described below with reference to the accompanying drawings.
エンジン1より排出された排気ガスはタービン2に導入
され、タービンインペラ3を回転駆動した後マフラーを
通り大気に放出される。タービンインペラ3はタービン
シャフト4の一端に形成され、タービンシャツ1〜4は
軸受けにより軸受部5に回転自在に支持される。一方エ
アクリーナ6を通り吸入された空気は空気流量817を
通りコンプレッサ8に導入される。コンプレッサ8内に
はタービンシャフト4の他端に形成されタービンインペ
ラ3と一体に回転するコンプレッサインペラ9が配設さ
れ、導入された空気を圧縮してエンジン1へ供給する。Exhaust gas discharged from the engine 1 is introduced into a turbine 2, rotates a turbine impeller 3, and then passes through a muffler and is released into the atmosphere. The turbine impeller 3 is formed at one end of a turbine shaft 4, and the turbine shirts 1 to 4 are rotatably supported by a bearing portion 5 by bearings. On the other hand, the air sucked through the air cleaner 6 is introduced into the compressor 8 through an air flow rate 817. A compressor impeller 9 that is formed at the other end of the turbine shaft 4 and rotates together with the turbine impeller 3 is disposed within the compressor 8, compresses the introduced air, and supplies the compressed air to the engine 1.
またエンジン1によって駆動されるオイルポンプ10は
オイルパン11内のオイルを吸入し、オイル通路16を
分し軸受部5に供給する。軸受部5を潤滑したオイルは
オイルドレンパイプ12を通りオイルパン11内へ自然
落下する。またエンジン回転センサ13と空気流量貫1
7からの信号はコントロールユニツ1〜14に入力され
、該コン1〜ロールユニツ1〜14からの出力によりオ
イルポンプ10の吐出量を制御する第一の制御手配置5
を作動させる。Further, an oil pump 10 driven by the engine 1 sucks oil in an oil pan 11, divides the oil passage 16, and supplies the oil to the bearing portion 5. The oil that has lubricated the bearing portion 5 passes through the oil drain pipe 12 and naturally falls into the oil pan 11. In addition, the engine rotation sensor 13 and the air flow rate sensor 1
The signal from 7 is input to the control units 1 to 14, and the first control arrangement 5 controls the discharge amount of the oil pump 10 based on the output from the control units 1 to 14.
Activate.
本構造において第2図に示す如くエンジン回転数Nが低
く、空気流量のとエンジン回転数から計算される負荷(
Q/N)が小さい減滅21ではタービンの回転数が低く
、軸受部5が必要とする油量は通常の運転をしているオ
イルポンプ10から軸受部5へ供給される油量に比べ十
分小さい。この場合、コントロールユニツ1−14は第
一の制御手段15を作動させオイルポンプ10の吐出量
を下げる。これによりオイルポンプ10が消費している
エンジン出力が減小する。エンジンが低速低負荷で運転
中はエンジン出力も小さく、エンジン出力の内オイルポ
ンプ10が消費する割合が高いため、この様にオイルポ
ンプの出力を下げるとエンジン効率の向」二に有効であ
る。In this structure, as shown in Fig. 2, the engine speed N is low, and the load calculated from the air flow rate and engine speed (
In the attenuation 21 where Q/N) is small, the rotational speed of the turbine is low, and the amount of oil required by the bearing portion 5 is sufficient compared to the amount of oil supplied to the bearing portion 5 from the oil pump 10 in normal operation. small. In this case, the control unit 1-14 operates the first control means 15 to reduce the discharge amount of the oil pump 10. This reduces the engine power consumed by the oil pump 10. When the engine is operating at low speed and low load, the engine output is small, and a high proportion of the engine output is consumed by the oil pump 10. Therefore, reducing the output of the oil pump in this way is effective in improving engine efficiency.
第3図はオイル流量を調節する別の実施例である。FIG. 3 shows another embodiment for adjusting the oil flow rate.
オイルポンプ10から軸受部5ヘオイルを供給するオイ
ル通路16内しこオイル流量制御機構を設けてあり、こ
の例によるとオイルポンプ白身は通常の仕様の物を使用
でき、採用が簡単である。An oil flow rate control mechanism is provided in the oil passage 16 for supplying oil from the oil pump 10 to the bearing portion 5, and in this example, the oil pump white can be of normal specifications and is easy to adopt.
第4図に別の実施例を示す。FIG. 4 shows another embodiment.
エンジン1によって駆動される機械駆動式過給機17を
コンプレッサ8の下流に備えており、該機械駆動式過給
機]−7はコントロールユニツ1〜14からの信号によ
り運転、停止する。また機械駆動式過給機17を迂回す
るバイパス通路19、該バイパス通路をコントロールユ
ニツI〜14からの信号により開閉制御する第2の制御
手段18も同時に設けられている。本構造において、機
械駆動式過給機17はエンジン回転数が低い領域から過
給を開始し、コンプレッサ8から吸入した空気を圧縮し
エンジン1へ供給する。また機械駆動式過給機17は所
定のエンジン回転数以上ではコン1−ロールユニット1
4からの信号により運転を停止する。一方、排気タービ
ン式過給機は高速タイプに設定され、エンジン回転数が
低い状態では過給圧力は低いが、エンジン回転数の上昇
に伴い過給圧力が上昇し、機械駆動式過給機が運転を停
止する高速運転時に最も優れた過給効果を表わす。A mechanically driven supercharger 17 driven by the engine 1 is provided downstream of the compressor 8, and the mechanically driven supercharger]-7 is operated and stopped by signals from the control units 1 to 14. Also provided are a bypass passage 19 that detours around the mechanically driven supercharger 17, and a second control means 18 that controls opening and closing of the bypass passage by signals from the control units I to 14. In this structure, the mechanically driven supercharger 17 starts supercharging from a region where the engine speed is low, compresses air taken in from the compressor 8, and supplies the compressed air to the engine 1. In addition, the mechanically driven supercharger 17 is activated when the engine speed exceeds a predetermined engine speed.
The operation is stopped by the signal from 4. On the other hand, the exhaust turbine type supercharger is set to a high-speed type, and the boost pressure is low when the engine speed is low, but as the engine speed increases, the boost pressure increases, and the mechanically driven supercharger It exhibits the best supercharging effect during high-speed operation when the operation is stopped.
この時機械駆動式過給機17が運転後停止すると同時に
第2の制御手段18が作動しバイパス通路19を開き、
コンプレッサ8からの過給空気をバイパス通路19を介
してエンジン1へ供給する。At this time, the mechanically driven supercharger 17 stops after operation, and at the same time, the second control means 18 operates to open the bypass passage 19.
Supercharged air from the compressor 8 is supplied to the engine 1 via a bypass passage 19.
この構造ではエンジンが特に高回転高負荷で運転されて
いる時以外はタービンの回転数は低く、第2図に示す領
域22において給油量を減小させることが可能となり、
通常のターボ付エンジンの場合(領域21)に比べより
広い運転領域でオイルポンプの出力を低下させエンジン
効率を向上させることができる。With this structure, the rotational speed of the turbine is low except when the engine is being operated at particularly high rotations and high loads, making it possible to reduce the amount of oil supplied in the region 22 shown in FIG.
It is possible to reduce the output of the oil pump and improve engine efficiency in a wider operating range than in the case of a normal turbo engine (region 21).
本発明しこよればオイルポンプによって消費されるエン
ジン出力を、エンジンが低速低負荷運転時に排気タービ
ン式過給機に供給されるオイル流量を減小させることに
より低減することができるためエンジン効率が向上する
効果がある。According to the present invention, the engine power consumed by the oil pump can be reduced by reducing the oil flow rate supplied to the exhaust turbine supercharger when the engine is operating at low speed and low load, thereby improving engine efficiency. It has an improving effect.
また機械駆動式過給機と組み合わせて用いられる排気タ
ービン式過給機では、その作動特性が高速高負荷運転用
に設定されているため、給油量を低減させ得る領域が通
常の排気タービン式過給機を用いる場合に比へ広く、本
発明を適用した場合効果が大きい。In addition, the operating characteristics of exhaust turbine turbochargers used in combination with mechanically driven turbochargers are set for high-speed, high-load operation, so the range in which the amount of oil supply can be reduced is different from that of ordinary exhaust turbine turbochargers. When a feeder is used, the effect is much wider than that when the present invention is applied.
第1図は本発明の一実施例を示すシステム図、第2図は
本発明の一実施例を示す動作図、第3図。
第4図は本発明の別の実施例を示すシステム図である。
1 エンジン、3・・タービンインペラ、5・軸受部、
7 空気流量計、9・・コンプレッサインペラ、10・
・・オイルポンプ、13・エンジン回転数検出装置、
コンIへロールユニット、15
第一
の制御手段、
機械駆動式過給機、
・第
二の制御手段。
第4図FIG. 1 is a system diagram showing an embodiment of the invention, FIG. 2 is an operation diagram showing an embodiment of the invention, and FIG. 3 is a system diagram showing an embodiment of the invention. FIG. 4 is a system diagram showing another embodiment of the present invention. 1. Engine, 3. Turbine impeller, 5. Bearing section,
7 Air flow meter, 9... Compressor impeller, 10...
... Oil pump, 13. Engine rotation speed detection device, Con I roll unit, 15. First control means, mechanically driven supercharger, - Second control means. Figure 4
Claims (1)
する給油装置に給油流量を調節可能な給油流量調節機構
を設け、またエンジン回転数、吸入空気量を検出する検
出手段を設け、該検出手段からの検出信号により前記給
油流量調節機構を作動させることを特徴とする過給機の
潤滑装置。 2、エンジンが低速、低負荷で運転中は排気タービン式
過給機に供給される油量を減少させる様に作動すること
を特徴とする請求項1記載の過給機の潤滑装置。 3、給油量の調節をエンジンのオイルポンプの駆動負荷
を変化させることを特徴とする請求項1記載の過給機の
潤滑装置。 4、給油量の調節をエンジンのオイルポンプと排気ター
ビン式過給機とを連通する給油通路の途中に流量調節機
構を設けたことを特徴とする請求項1記載の過給機の潤
滑装置。 5、エンジンの吸気通路の上流側に排気タービン式過給
機、下流側に機械駆動式過給機を直列に設け所定のエン
ジン回転数以上の高速運転時に機械駆動式過給機を停止
させる過給装置において、排気タービン式過給機の給油
装置に請求項1、2記載の給油量調節機構を設けたこと
を特徴とする過給機の潤滑装置。 6、エンジンに第1、第2の2つの排気タービン式過給
機を設け、第2の過給機の排気ガス通路に開閉装置を設
け、該開閉装置の作動によりエンジンが低速低負荷運転
時には第1の過給機のみが運転され、エンジンが高速高
負荷運転時には第1、第2の過給機が運転される過給装
置において、第1、第2の過給機の給油装置に請求項1
、2記載の給油量調整機構を設けたことを特徴とする過
給機の潤滑装置。[Claims] 1. A lubricant supply device that supplies lubricating oil from the engine to the exhaust turbine supercharger is provided with a lubricant flow rate adjustment mechanism that can adjust the lubricant flow rate, and a detection system that detects the engine rotation speed and intake air amount. A lubrication device for a supercharger, characterized in that a means is provided, and the oil supply flow rate adjustment mechanism is actuated by a detection signal from the detection means. 2. The supercharger lubrication system according to claim 1, which operates to reduce the amount of oil supplied to the exhaust turbine supercharger when the engine is operating at low speed and low load. 3. The supercharger lubrication system according to claim 1, wherein the oil supply amount is adjusted by changing the driving load of an oil pump of the engine. 4. The supercharger lubrication system according to claim 1, further comprising a flow rate adjustment mechanism provided in the middle of an oil supply passage that communicates the oil pump of the engine with the exhaust turbine type supercharger to adjust the amount of oil supplied. 5. An exhaust turbine supercharger is installed in series on the upstream side of the engine intake passage, and a mechanically driven supercharger is placed on the downstream side. A lubricating device for a supercharger, characterized in that the lubricating device for an exhaust turbine type supercharger is provided with the oil supply amount adjusting mechanism according to claim 1 or 2. 6. The engine is provided with two exhaust turbine superchargers, a first and a second, and an opening/closing device is provided in the exhaust gas passage of the second supercharger, and when the engine is operated at low speed and under low load, the opening/closing device is operated. In a supercharging system in which only the first supercharger is operated and the first and second superchargers are operated when the engine is operated at high speed and high load, the oil supply system for the first and second superchargers is charged. Item 1
A lubrication device for a supercharger, characterized in that it is provided with the oil supply amount adjustment mechanism according to 2.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32585588A JPH02173323A (en) | 1988-12-26 | 1988-12-26 | Lubrication device for supercharger |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32585588A JPH02173323A (en) | 1988-12-26 | 1988-12-26 | Lubrication device for supercharger |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH02173323A true JPH02173323A (en) | 1990-07-04 |
Family
ID=18181372
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP32585588A Pending JPH02173323A (en) | 1988-12-26 | 1988-12-26 | Lubrication device for supercharger |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH02173323A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8015810B2 (en) * | 2007-05-14 | 2011-09-13 | GM Global Technology Operations LLC | Control of turbocharger lubrication for hybrid electric vehicle |
US20120003075A1 (en) * | 2010-06-30 | 2012-01-05 | Mazda Motor Corporation | Lubrication device of turbocharger of engine for vehicle |
US20130269340A1 (en) * | 2012-04-17 | 2013-10-17 | Ford Global Technologies, Llc | Turbocharger for an internal combustion engine and method for operating a turbocharged internal combustion engine |
WO2016067955A1 (en) * | 2014-10-29 | 2016-05-06 | 大豊工業株式会社 | Lubricating oil supply mechanism for turbocharger |
-
1988
- 1988-12-26 JP JP32585588A patent/JPH02173323A/en active Pending
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8015810B2 (en) * | 2007-05-14 | 2011-09-13 | GM Global Technology Operations LLC | Control of turbocharger lubrication for hybrid electric vehicle |
US20120003075A1 (en) * | 2010-06-30 | 2012-01-05 | Mazda Motor Corporation | Lubrication device of turbocharger of engine for vehicle |
US8615998B2 (en) * | 2010-06-30 | 2013-12-31 | Mazda Motor Corporation | Lubrication device of turbocharger of engine for vehicle |
US20130269340A1 (en) * | 2012-04-17 | 2013-10-17 | Ford Global Technologies, Llc | Turbocharger for an internal combustion engine and method for operating a turbocharged internal combustion engine |
US9476350B2 (en) * | 2012-04-17 | 2016-10-25 | Ford Global Technologies, Llc | Turbocharger for an internal combustion engine and method for operating a turbocharged internal combustion engine |
WO2016067955A1 (en) * | 2014-10-29 | 2016-05-06 | 大豊工業株式会社 | Lubricating oil supply mechanism for turbocharger |
JP2016089632A (en) * | 2014-10-29 | 2016-05-23 | 大豊工業株式会社 | Lubricating oil supply mechanism for turbocharger |
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