JPS58152125A - Controller for supercharging pressure of supercharged engine - Google Patents
Controller for supercharging pressure of supercharged engineInfo
- Publication number
- JPS58152125A JPS58152125A JP57034006A JP3400682A JPS58152125A JP S58152125 A JPS58152125 A JP S58152125A JP 57034006 A JP57034006 A JP 57034006A JP 3400682 A JP3400682 A JP 3400682A JP S58152125 A JPS58152125 A JP S58152125A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- valve
- bypass
- supercharging pressure
- passage
- 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
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
- F02B37/183—Arrangements of bypass valves or actuators therefor
- F02B37/186—Arrangements of actuators or linkage for bypass valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は過給機付内燃機関において過給圧の過昇を防止
する過給圧制御装置に関し、詳しくは排気通路にもうけ
たバイパスパルプの制御装置の改良である。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a supercharging pressure control device for preventing an excessive rise in supercharging pressure in a supercharged internal combustion engine, and more specifically, to an improvement of a bypass pulp control device provided in an exhaust passage.
第1図に示す従来の過給圧11Ji!装置は特開昭50
−65712号公報に開示されたものであって、内燃機
関1の排気通路2に介装されたタービン3を排気エネル
ギーによって回し、これと軸4を介して連結されたコン
プレッサ5を回転駆動することによシ、吸気通路6を介
して吸気を内燃機関1に過給する過給機付内燃機関にお
いて、タービン3をバイパスするバイパス通路Tにバイ
パスパルプ10を介装してなる。Conventional supercharging pressure 11Ji shown in Fig. 1! The device is Japanese Patent Application Publication No. 1973.
- Disclosed in Japanese Patent No. 65712, in which a turbine 3 installed in an exhaust passage 2 of an internal combustion engine 1 is rotated by exhaust energy, and a compressor 5 connected to the turbine 3 via a shaft 4 is rotationally driven. In a supercharged internal combustion engine that supercharges intake air to the internal combustion engine 1 via the intake passage 6, a bypass pulp 10 is interposed in a bypass passage T that bypasses the turbine 3.
バイパスパルプ10ti、バイパス通路70入口11を
開閉する弁体11をロンドを介してダイヤフラム12に
連結し、骸ダイヤフ2ム12の07ト@呈である圧力作
動室13に、コンプレッサ5下流の吸気通路6内圧力(
過給圧)を導いたものであって、スプリング14は弁体
11を閉弁方向に弾性付勢する。尚図中15絋スロツト
ルイ(ルプである。The bypass pulp 10ti is connected to the diaphragm 12 via the valve body 11 which opens and closes the bypass passage 70 inlet 11, and the intake passage downstream of the compressor 5 is connected to the pressure working chamber 13 which is the part of the skeleton diaphragm 12. 6 Internal pressure (
The spring 14 elastically biases the valve body 11 in the valve closing direction. In the figure, there are 15 slots.
従ってかかる構成によると、圧力作動室13に作用する
過給圧がスプリング14で定められた開弁設定圧以上の
時轄、スプリング14の弾性力とダイヤフラム12に作
用する過給圧とのバランスによシ、過給圧に比例した一
度たけ弁体11が開いて、ターヒフ3回転にあずからず
にバイパス通路Tを流通する排気を増量し、ターヒフ3
回転に使用される排気エネルギを低減する。これによっ
てコンプレッ?5が過回転し設定圧以上の過給圧となる
ことを予防して、過給機、吸気系、ひいて紘内燃機関そ
のものの破損から保験している。Therefore, according to this configuration, when the supercharging pressure acting on the pressure operating chamber 13 exceeds the valve opening setting pressure determined by the spring 14, the elastic force of the spring 14 and the supercharging pressure acting on the diaphragm 12 are balanced. Okay, the one-time valve body 11 proportional to the boost pressure opens and increases the amount of exhaust gas flowing through the bypass passage T without participating in the three rotations of Tahif.
Reduce exhaust energy used for rotation. Does this compile? 5 is prevented from over-revving and the supercharging pressure exceeds the set pressure, thereby protecting the supercharger, intake system, and even the internal combustion engine itself from damage.
しかし、このような従来構造によると、過給圧のバイパ
スバルブの開弁設定圧以上の値に比例してバイパスバル
ブ10を開くものであるから、排気熱によるバイパスバ
ルブ10の熱変形、及び排気不純物(カーボン等)の付
着による弁体11駆動系(pラド、スプリング等)の摺
動摩擦抵抗増大が発生したシ、或いはスプリングや組付
WA差のバラツキ勢があると、過給圧に対しバイパスバ
ルブ10が所望開度開かないという応答不良が発生し易
い。その結果、所望最適の排気バイパス通路量ることが
できなくなシ、過給圧の最大値を設定圧に一定にしにく
くなシ過大となシ過少となったシしてノッキング現象或
いはピストン焼損勢の不都合を発生するおそれがあった
。However, according to such a conventional structure, the bypass valve 10 is opened in proportion to the value of boost pressure that is equal to or higher than the valve opening set pressure of the bypass valve, so thermal deformation of the bypass valve 10 due to exhaust heat and exhaust gas If the sliding frictional resistance of the valve body 11 drive system (Prad, spring, etc.) increases due to the adhesion of impurities (carbon, etc.), or if there is a variation in the spring or assembly WA difference, bypass will occur due to boost pressure. Poor response, in which the valve 10 does not open to the desired degree, is likely to occur. As a result, it becomes impossible to maintain the desired optimum amount of exhaust bypass passage, and it becomes difficult to maintain the maximum value of boost pressure at the set pressure. There was a risk that this would cause inconvenience.
本発明は上記従来装置の不都合に鎌み、過給圧が設定圧
以上になったときのみバイパスバルブに過給圧信号を導
ひく圧力調整手段を設け、圧力調整手段を作動させる設
定圧をバイパスパルプO開弁設定圧よシ大とすることに
よってバイパスバルブを、過給圧比例型ではなく、オン
オフ的に繰ル返し開閉制御することによシ、過給圧を設
定圧以下に常に保持するようにし九過給圧調整装置を提
供するものである。The present invention addresses the above-mentioned disadvantages of the conventional device and provides a pressure regulating means that guides a boost pressure signal to the bypass valve only when the boost pressure exceeds the set pressure, thereby bypassing the set pressure that activates the pressure regulating means. By setting the pulp O valve opening pressure higher than the set pressure, the bypass valve is not proportional to the boost pressure, but is controlled to open and close repeatedly in an on-off manner, thereby constantly maintaining the boost pressure below the set pressure. The present invention provides nine supercharging pressure adjustment devices.
以下に本発明の実施例を図面に基づいて説明する。Embodiments of the present invention will be described below based on the drawings.
第2図及び第3図に示す内燃機関1絋電子制御燃料噴射
式であつそ、噴射弁21は一次側スロットルバルブ15
Aの直下流の吸気通路6に臨設されたいわゆるシングル
ポイントインジェクションタイプである。15Bti二
次側スpットルパルブである。コンプレッサ5上流の吸
気通路6にはエアフローメータ22が装備されている一
方、ター−ビン3下流の排気通路2には排気中のo2.
co。The internal combustion engine 1 shown in FIGS. 2 and 3 is an electronically controlled fuel injection type, and the injection valve 21 is the primary throttle valve 15.
This is a so-called single point injection type installed directly in the intake passage 6 immediately downstream of A. This is a 15Bti secondary throttle valve. An air flow meter 22 is installed in the intake passage 6 upstream of the compressor 5, while an air flow meter 22 is installed in the exhaust passage 2 downstream of the turbine 3.
co.
co2等成分を検出する排気センサ23が介装され、こ
れらエアフローメータ22による吸気量、排気センサ2
3による吸入混合気空燃比並びにスロットルセンサ24
による一次側スロットルバルブ15ムのスロットル一度
等機関の運転諸状態が検出されて図示しないコントロー
ラに入力され、とζで所定燃料量が演算されて噴射弁2
1から吸気通路6へ向けて間欠的に燃料が噴射され、吸
入空気と混合して適正空炉比の混合気が形成される。An exhaust sensor 23 that detects components such as CO2 is interposed, and the intake air amount and exhaust sensor 2 are measured by the air flow meter 22.
3 and throttle sensor 24
The operating conditions of the engine such as the throttle of the primary throttle valve 15 are detected and input to a controller (not shown), and a predetermined fuel amount is calculated by ζ and the injection valve 2 is
Fuel is intermittently injected from 1 toward the intake passage 6 and mixed with intake air to form an air-fuel mixture with an appropriate air-to-air ratio.
尚過給機の構成、バイパス通路T等は先の従来例と略同
−であシ、25は点火栓である。The configuration of the supercharger, the bypass passage T, etc. are substantially the same as in the prior art example, and 25 is a spark plug.
バイパス通路Tを開閉するバイパスバルブ31は、バイ
パス入ロアat−開閉する弁体32にリンク35で連結
した圧力応動型アクチュエータ33を有する。該アクチ
ュエータ33は弁体32にリンク結合したダイヤフラム
34のm個に圧力作動室36を有すると共に他側に弁体
32を閉弁方向に付勢し、−弁設定圧を決定するスプリ
ング37を備える。圧力作動室36には、圧力調整弁4
0によシ設定圧でオンオフ的に制御されたコンプレッサ
5下流の過給圧力が通路39を介して導入される。尚、
該通路39はオリフィス38を介して大気に開口してい
る。The bypass valve 31 that opens and closes the bypass passage T has a pressure-responsive actuator 33 connected by a link 35 to a valve body 32 that opens and closes the bypass entry lower at. The actuator 33 has m diaphragms 34 linked to the valve body 32 and has pressure operating chambers 36, and has a spring 37 on the other side that biases the valve body 32 in the valve closing direction and determines the valve setting pressure. . A pressure regulating valve 4 is provided in the pressure operating chamber 36.
A supercharging pressure downstream of the compressor 5, which is controlled on and off at a set pressure of 0, is introduced through a passage 39. still,
The passage 39 opens to the atmosphere through an orifice 38.
圧力調整弁40は前記通路39の開口端3saが臨む圧
力作動室41と大気型42とを仕切シ、かつスプリング
430弾性力を受けて前記開口端39aを弁体44が閉
鎖する方向に付勢されるダイヤフラム45を備える。こ
のときスプリング43による開口端39m開弁圧Pa(
例えは約350−HP)即ち、設定圧は前記バイパスバ
ルブ31のスプリング3Tによる弁体32開弁圧pb(
例えは約150mHf)即ち、開弁設定圧よシも大とな
るように設定する。そして前記圧力作動室41に通路4
7を介して過i圧を導いている。The pressure regulating valve 40 partitions a pressure operating chamber 41 facing the open end 3sa of the passage 39 from an atmospheric type 42, and receives the elastic force of a spring 430 to bias the open end 39a in the direction in which the valve body 44 closes. A diaphragm 45 is provided. At this time, the valve opening pressure Pa (
For example, about 350-HP), that is, the set pressure is the valve body 32 opening pressure pb (by the spring 3T of the bypass valve 31).
For example, about 150 mHf), that is, the valve opening setting pressure is also set to be higher. A passage 4 is connected to the pressure working chamber 41.
7 leads to an overpressure.
従ってかかる構成によると、圧力調整弁40の圧力作動
室41に導かれた過給圧が設定圧Pa以上になろうとす
ると、ダイヤフラム45がスプリング430弾性力に抗
して図で上動し開口端39aを開く。このため、過給圧
が通路39を介してバイパスバルブ31の圧力作動室3
6内に導入される。ここで開弁設定圧よシ設定圧が上述
のように大となっているのでスプリング370弾性力に
抗してダイヤフラム34を図で右行させ、リンク35を
介し弁体32を開いて排気をバイパス通路7に導く。こ
れによってタービン3を回転fる排気エネルギを低減し
、コンプレッサ5の過回転を防止して過給圧の設定圧P
a以上の上昇を防止する。Therefore, according to this configuration, when the supercharging pressure introduced into the pressure working chamber 41 of the pressure regulating valve 40 is about to exceed the set pressure Pa, the diaphragm 45 moves upward in the figure against the elastic force of the spring 430 and ends at the open end. Open 39a. Therefore, the supercharging pressure passes through the passage 39 to the pressure operating chamber 3 of the bypass valve 31.
6 will be introduced. Here, since the valve opening setting pressure is higher than the opening setting pressure as described above, the diaphragm 34 is moved to the right in the figure against the elastic force of the spring 370, and the valve body 32 is opened via the link 35 to exhaust the air. It leads to the bypass passage 7. This reduces the exhaust energy that rotates the turbine 3, prevents over-rotation of the compressor 5, and sets the boost pressure P.
Prevent the temperature from rising above a.
過給圧が設定圧Paよシも小さくなると、圧力調整弁4
0においてはスプリング430弾性力によシ、ダイヤフ
ラム43が図で下降し、弁体44が通j139の開口f
i39mを塞ぐ。従ってオリフィス38の存在のため、
通路39、バイパスバルブ31の圧力作動室36内の圧
力が大気稀釈され、開弁設定圧pbよシも小さくなシス
プリング3Tの設定荷重が勝ってダイヤフラム34を左
行させる。これに伴ってリンク35を介して弁体32を
右行しバイパス通路1のバイパス人口1aを閉じる。こ
のためバイパス通路7を通る排気流がなくて過給圧の低
下を防止する。When the boost pressure becomes smaller than the set pressure Pa, the pressure regulating valve 4
At 0, the diaphragm 43 moves down due to the elastic force of the spring 430, and the valve body 44 opens into the opening f of the passage j139.
Block i39m. Therefore, due to the presence of orifice 38,
The pressure in the passage 39 and the pressure operating chamber 36 of the bypass valve 31 is diluted to the atmosphere, and the set load of the spring 3T, which is smaller than the valve opening set pressure pb, overcomes and moves the diaphragm 34 to the left. Along with this, the valve body 32 moves to the right via the link 35 and the bypass port 1a of the bypass passage 1 is closed. Therefore, there is no exhaust flow passing through the bypass passage 7, thereby preventing a drop in supercharging pressure.
このような作用を繰シ返して、コンプレッサ下流の過給
圧が設定圧Paに一定圧制御される。By repeating such actions, the supercharging pressure downstream of the compressor is controlled to be constant at the set pressure Pa.
勿論過給圧が設定圧Pa以下であるならばバイパスバル
ブ31は閉状態を維持してそのときの値よりも過給圧を
低下するように紘作用しない。Of course, if the supercharging pressure is below the set pressure Pa, the bypass valve 31 remains closed and does not act to lower the supercharging pressure below the current value.
上記実施例において、オリフィス38の開口径によシ、
圧力調整弁40の開口端39mの閉弁作用に対するバイ
パスバルブ31の閉弁応答遅れを任意に設定できること
は言うまでもない。またバイパスバルブ31の開弁設定
圧Pbを圧力調整弁40の開弁設定圧Paから離れて小
さくなるように、バイパスバルブ31のスプリング37
の設定荷重を選定すれは、′過給圧が設定圧Paよル上
昇しようとしたとき、圧力調整弁40が開弁することに
よるバイパスバルブ31、圧力作動室36内の圧力立上
がシに応答性良くバイパスバルブ31を開弁するように
構成できる。In the above embodiment, depending on the opening diameter of the orifice 38,
It goes without saying that the delay in closing response of the bypass valve 31 to the closing action of the opening end 39m of the pressure regulating valve 40 can be set arbitrarily. In addition, the spring 37 of the bypass valve 31 is arranged so that the valve opening setting pressure Pb of the bypass valve 31 becomes smaller and away from the valve opening setting pressure Pa of the pressure regulating valve 40.
When selecting the set load for ', when the supercharging pressure is about to rise above the set pressure Pa, the pressure rise in the bypass valve 31 and the pressure operating chamber 36 due to the opening of the pressure regulating valve 40 is prevented. The bypass valve 31 can be configured to open with good response.
このようにバイパスバルブをオンオフ的に開閉制御する
ので、弁体32、リンク35に排気不純物(大−ボン等
)が付着して作動不良、応答性悪化を招き易い状態にな
っても、ステップ的な差圧のある圧力でバイパスバルブ
を開若しくは閉にすれd足シ、かかるおそれがなくなる
こと明らかである。Since the bypass valve is controlled to open and close in an on-off manner in this way, even if exhaust impurities (such as large particles) adhere to the valve body 32 and link 35 and are likely to cause malfunction or poor responsiveness, the bypass valve can be opened and closed in a stepwise manner. It is clear that this risk can be eliminated by opening or closing the bypass valve with a certain pressure difference.
尚、第4図は上記実施例における通路3Sを大略省略し
圧力調整弁40/とバイパスバルブのアクチュエータ3
3とを、これらの圧力作動室41゜36相互を通路39
1′で短絡すると共に両者一体形成した亀のである。図
中51.52はダイヤ72ム34に固定したストッパで
ある。In addition, in FIG. 4, the passage 3S in the above embodiment is largely omitted, and the pressure regulating valve 40/and the actuator 3 of the bypass valve are shown.
3 and these pressure working chambers 41゜36 mutually through a passage 39.
1' is short-circuited and both are integrally formed. In the figure, reference numerals 51 and 52 indicate stoppers fixed to the diamond 72 rim 34.
ま九第5図に示す実施例は、通路39の開口端39aを
圧力調整弁40のダイヤフラム45に関し圧力作動室4
10反対個に対向して開口させると共に通路47と通路
39とを通路55によって接続し喪ものである。前記開
口端39mの開口した室は大気圧室である。9. In the embodiment shown in FIG.
The passage 47 and the passage 39 are connected by a passage 55, which is opened to face 10 opposite passages. The open chamber at the open end 39m is an atmospheric pressure chamber.
従って過給圧が設定圧Pa以上になろうとすると、ダイ
ヤフラム45が図で上動し、開口端39aを閉じるから
、過給圧設定圧Paがそのtま通路47.55.39を
介してアクチェエータ33に導かれバイパスバルブを開
く一方、過給圧が設定圧Paよシ小さくなると、ダイヤ
フラム45が図で下降して、−口端39mを開き、過給
圧信号を大気稀釈してバイパスバルブに導かれ該バルブ
を閉じる。その作用効果は先の2つの実施例と同様であ
る。Therefore, when the supercharging pressure is about to exceed the set pressure Pa, the diaphragm 45 moves upward in the figure and closes the opening end 39a, so that the supercharging pressure set pressure Pa passes through the passage 47, 55, 39 to the actuator. 33 to open the bypass valve. On the other hand, when the boost pressure becomes smaller than the set pressure Pa, the diaphragm 45 lowers in the figure, opens the negative end 39m, dilutes the boost pressure signal to the atmosphere, and opens the bypass valve. and close the valve. Its operation and effect are similar to those of the previous two embodiments.
以上述べたように、本発明によると、バイパスバルブへ
送る過給圧信号を過給圧が設定圧以上になったときのみ
バイパスバルブの圧力作動室に導入する圧力調整手段を
設けたので、バイパスバルブを、過給圧比例型ではなく
、オンオフ的に繰シ返して開閉制御することによシ、過
給圧を設定圧以下に保持することができる。従ってバイ
パスバルブが熱変形及びカーボン岬の付着による弁体態
動系の摺動j11捺抵抗増大が発生した〕、スプリング
や組付誤差のバラツキ等があっても、バイパスバルブは
開と閉の2位置のみをとればよいから、応答精度が極め
て良く、バルブ構造も簡単になる。As described above, according to the present invention, the pressure regulating means is provided to introduce the boost pressure signal sent to the bypass valve into the pressure operating chamber of the bypass valve only when the boost pressure exceeds the set pressure. By repeatedly controlling the valve to open and close in an on-off manner instead of using a valve proportional to the boost pressure, the boost pressure can be maintained below the set pressure. Therefore, the bypass valve is thermally deformed and the sliding resistance of the valve body dynamic system increases due to the adhesion of carbon capes], and even if there are variations in springs and assembly errors, the bypass valve can only open and close in two directions. Since only the position needs to be determined, the response accuracy is extremely high and the valve structure is simple.
このためバイパスバルブによるタービンバイパス排気量
の計量精度が向上し、過給圧を正確に設定圧附近に抑え
ることができ、ノッキング現象、ピストン焼損等の不都
合を回避できる。Therefore, the accuracy of measuring the turbine bypass displacement amount by the bypass valve is improved, the boost pressure can be accurately suppressed to around the set pressure, and problems such as knocking phenomenon and piston burnout can be avoided.
第1図は従来装置の概略系統図、第2図は本発明の一実
施例を示す縦断面図、第3図は同上要部の断面図、第4
図及び第5図線夫々本発明の他の実施例の断面図である
。
1・・・内燃機関 2・・・排気通路 3・・・タ
ービン 5・・・コンプレッサ T・・・バイパス
通路31.31’・・・バイパスパルプ 32・・・
弁体33−−・アクチュエータ 39・・・通路
39色・・・開口端 40 、40’・・・圧力調整
弁 47・・・通路 55・・・通路
特許 出願人 日産自動車株式脅社
代理人 弁理士 笹 島 富二雄Fig. 1 is a schematic system diagram of a conventional device, Fig. 2 is a vertical sectional view showing an embodiment of the present invention, Fig. 3 is a sectional view of the main parts of the same, and Fig. 4 is a schematic diagram of a conventional device.
FIG. 5 is a sectional view of another embodiment of the present invention, respectively. 1... Internal combustion engine 2... Exhaust passage 3... Turbine 5... Compressor T... Bypass passage 31.31'... Bypass pulp 32...
Valve body 33--Actuator 39...Passage
39 colors...Opening end 40, 40'...Pressure regulating valve 47...Passage 55...Passage patent Applicant: Nissan Motor Co., Ltd. Patent attorney Fujio Sasashima
Claims (1)
回転駆動されるコンプレッサによシ吸気を過給する過給
機付内燃機関において、タービンをバイパスする排気通
路に圧力応動娶のバイパスパルプを介装し、前記コンプ
レッサ下流の過給圧信号を該過給圧が設定圧以上になっ
たとき前記バイパスパルプの圧力作動室に導入する圧力
調整手段を設け、該設定圧をバイパスパルプの開弁設定
圧よシ大とすることによシ、バイパスパルプをオンオフ
的に開閉制御するように構成したことを%像とする過給
機付内炉機−の過給圧制御装置。In an internal combustion engine with a supercharger that uses exhaust gas to drive a turbine and supercharge intake air by a compressor that is rotatably connected to the turbine, a pressure-responsive bypass pulp is installed in the exhaust passage that bypasses the turbine. A pressure adjusting means is provided to introduce a boost pressure signal downstream of the compressor into the pressure operating chamber of the bypass pulp when the boost pressure becomes equal to or higher than a set pressure, and the set pressure is used to control the valve opening of the bypass pulp. A supercharging pressure control device for an inner furnace equipped with a supercharger, which is configured to control the opening and closing of bypass pulp in an on-off manner by increasing the set pressure.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP57034006A JPS58152125A (en) | 1982-03-05 | 1982-03-05 | Controller for supercharging pressure of supercharged engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP57034006A JPS58152125A (en) | 1982-03-05 | 1982-03-05 | Controller for supercharging pressure of supercharged engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS58152125A true JPS58152125A (en) | 1983-09-09 |
Family
ID=12402344
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP57034006A Pending JPS58152125A (en) | 1982-03-05 | 1982-03-05 | Controller for supercharging pressure of supercharged engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS58152125A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63164524U (en) * | 1987-04-17 | 1988-10-26 | ||
US5487273A (en) * | 1993-09-13 | 1996-01-30 | Alliedsignal Inc. | Turbocharger having pneumatic actuator with pilot valve |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5593923A (en) * | 1979-01-10 | 1980-07-16 | Hitachi Ltd | Exhaust bypass type turbo-charger |
-
1982
- 1982-03-05 JP JP57034006A patent/JPS58152125A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5593923A (en) * | 1979-01-10 | 1980-07-16 | Hitachi Ltd | Exhaust bypass type turbo-charger |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63164524U (en) * | 1987-04-17 | 1988-10-26 | ||
US5487273A (en) * | 1993-09-13 | 1996-01-30 | Alliedsignal Inc. | Turbocharger having pneumatic actuator with pilot valve |
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