JPH0719140A - Fuel injection device for internal combustion engine - Google Patents
Fuel injection device for internal combustion engineInfo
- Publication number
- JPH0719140A JPH0719140A JP6139058A JP13905894A JPH0719140A JP H0719140 A JPH0719140 A JP H0719140A JP 6139058 A JP6139058 A JP 6139058A JP 13905894 A JP13905894 A JP 13905894A JP H0719140 A JPH0719140 A JP H0719140A
- Authority
- JP
- Japan
- Prior art keywords
- fuel
- valve
- conduit
- pressure
- pump
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/32—Varying fuel delivery in quantity or timing fuel delivery being controlled by means of fuel-displaced auxiliary pistons, which effect injection
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/365—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages valves being actuated by the fluid pressure produced in an auxiliary pump, e.g. pumps with differential pistons; Regulated pressure of supply pump actuating a metering valve, e.g. a sleeve surrounding the pump piston
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は内燃機関の燃料噴射装置
であって、シリンダ孔内でシリンダブッシュに案内され
かつカム駆動によって軸方向に運動可能であるポンプピ
ストンを備えており、該ポンプピストンはシリンダ孔内
でポンプ作業室を制限し、該ポンプ作業室は、燃料を供
給されるべき内燃機関の燃焼室内に突入している噴射弁
に高圧導管を介して接続されており、かつ制御された燃
料導管を介して燃料を充填及び放出することができ、更
にポンプ作業室に対する、高圧吐出を制御する燃料導管
の閉鎖が、燃料導管内に配置されかつ戻しばねの力に抗
して液圧式に作動する弁によって行われており、該弁は
軸方向で閉鎖方向に向いている圧力面を有し、該圧力
面、搬送ポンプによって貯蔵容器から供給される圧力媒
体導管を介し圧力媒体によって負荷されており、かつそ
の圧力媒体負荷は、圧力媒体導管から分岐した放圧導管
を電磁弁を用いて制御することによって行われている形
式のものに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fuel injection device for an internal combustion engine, which includes a pump piston guided in a cylinder bush in a cylinder hole and movable in the axial direction by a cam drive. Restricts the pump working chamber in the cylinder bore, which is connected via a high-pressure conduit to the injection valve projecting into the combustion chamber of the internal combustion engine to be fueled and is controlled. Fuel can be filled and discharged via the fuel conduit, and the closure of the fuel conduit controlling the high pressure discharge to the pump working chamber is hydraulically arranged against the force of the return spring arranged in the fuel conduit. Actuated by means of a valve, which has an axially directed pressure direction in the closing direction, said pressure surface being a pressure medium via a pressure medium conduit supplied from a storage container by a conveying pump. Are loaded by, and the pressure medium load is related of the type that is performed by controlling an electromagnetic valve relief line which branches off from the pressure medium conduit.
【０００２】[0002]
【従来の技術】この種の米国特許第４３８７６８６号明
細書によって公知の燃料噴射装置にあっては、シリンダ
ブッシュのシリンダ孔内を軸方向に案内されているポン
プピストンが、カム駆動により戻しばねの力に抗して軸
方向に往復運動を行っている。ポンプピストンはその端
面によってシリンダ孔内のポンプ作業室を制御し、該ポ
ンプ作業室は、供給されるべき内燃機関の燃焼室に突入
している噴射弁に接続されていて、燃料導管を介して燃
料を、燃料貯蔵タンクから充填し又は放圧することがで
きる。燃料導管内には液圧式に作動可能な滑り弁が配置
されており、該滑り弁を介してポンプ作業室内の高圧吐
出を制御する目的で、燃料導管へのポンプ作業室の接続
部を制御することができる。2. Description of the Related Art In a fuel injection system known from U.S. Pat. No. 4,387,686 of this type, a pump piston axially guided in a cylinder bore of a cylinder bush is driven by a cam to act as a return spring. It reciprocates in the axial direction against the force. The pump piston controls by its end face a pump working chamber in the cylinder bore, which pump working chamber is connected to an injection valve projecting into the combustion chamber of the internal combustion engine to be supplied, via a fuel conduit. Fuel can be filled or depressurized from a fuel storage tank. A hydraulically operable slide valve is arranged in the fuel conduit and controls the connection of the pump work chamber to the fuel conduit for the purpose of controlling the high pressure discharge in the pump work chamber via the slide valve. be able to.
【０００３】滑り弁はケーシング内を軸方向にスライド
可能なシリンダ状の弁部材を有し、その一方の端面は戻
しばねによって負荷されており、、かつその他方の端面
は、圧力媒体導管に接続されている作業室を制限してい
る。開放された滑り弁を貫く燃料の流れは弁部材の切欠
きによって行われ、該弁部材は、ばね側で常時燃料導管
に接続されている端面から出発して、弁部材のリング溝
を介してポンプ作業室への接続通路の領域に開口してい
る。開放された状態で戻しばねは、弁部材をストッパに
当接して保持し、その際この位置で弁部材のリング溝は
ポンプ作業室への接続通路によって覆われており、その
ために燃料はポンプ作業室に流入及び流出することがで
きる。滑り弁がポンプ作業室と燃料導管との間の接続部
を閉ぢた場合には、端面側の作業室が圧力媒体導管を介
し圧力媒体によって充填され、かつ弁部材は戻しばねの
力に抗して閉鎖位置にスライドせしめられ、その位置で
円筒形弁部材の套面がポンプ作業室への接続通路を閉鎖
している。The slide valve comprises a cylindrical valve member which is axially slidable in a casing, one end of which is loaded by a return spring and the other end of which is connected to a pressure medium conduit. The working room is restricted. The flow of fuel through the open slide valve is carried out by means of a notch in the valve member, which starts from the end face which is always connected to the fuel conduit on the spring side and through the ring groove of the valve member. It opens in the area of the connection passage to the pump work chamber. In the open state, the return spring holds the valve member against the stopper, in which position the ring groove of the valve member is covered by the connecting passage to the pump working chamber, so that the fuel is pumped. It can flow in and out of the chamber. When the sliding valve closes the connection between the pump working chamber and the fuel conduit, the working chamber on the end face side is filled with the pressure medium via the pressure medium conduit and the valve member resists the force of the return spring. And is slid into the closed position, in which position the sleeve of the cylindrical valve member closes the connection passage to the pump working chamber.
【０００４】作業室を充たしている圧力媒体導管の制御
は、公知の燃料噴射装置の場合にあっては、ポンプピス
トンの制御エッジと、互いに平行に配置された２つの電
磁弁とによって行われており、該電磁弁は、圧力媒体導
管を高圧回路に、又は低圧で作動する燃料導管の燃料回
路に接続しており、その際低圧回路内の圧力と高圧回路
内の圧力とは夫々１つの圧力弁を介して制御されてい
る。The control of the pressure medium conduit filling the working chamber is effected in the known fuel injection system by the control edge of the pump piston and two solenoid valves arranged parallel to one another. The solenoid valve connects the pressure medium conduit to the high-pressure circuit or to the fuel circuit of the fuel conduit operating at low pressure, the pressure in the low-pressure circuit and the pressure in the high-pressure circuit being one pressure each. It is controlled via a valve.
【０００５】公知の燃料噴射装置にあっては、高圧回路
に接続された圧力媒体導管における圧力の増圧が制御の
開始に対し遅延して行われるため、圧力媒体導管の制御
時点が滑り弁の制御時点に一致しないようになり、この
ことから回転数が高くて制御時間が短い場合には制御の
不正確さが発生するという欠点を有している。更に公知
の装置にあっては、極めて短い切換時間が平行な２つの
電磁弁の交差によってだけ達成可能であるため、組立及
び制御のコストが極めて高価である。In the known fuel injection system, the pressure in the pressure medium conduit connected to the high-pressure circuit is increased with a delay relative to the start of control, so that the control point of the pressure medium conduit is controlled by the slip valve. Since the control time does not coincide with the control time point, there is a disadvantage that the control becomes inaccurate when the rotation speed is high and the control time is short. Moreover, in the known device, the assembly and control costs are very high, since a very short switching time can only be achieved by the intersection of two solenoid valves in parallel.
【０００６】[0006]
【発明が解決しようとする課題】本発明の課題は燃料噴
射装置に関する上述の欠点を除去することにある。The object of the present invention is to eliminate the above-mentioned drawbacks associated with fuel injection systems.
【０００７】[0007]
【課題を解決するための手段】本発明では電磁弁が放圧
導管内に配置されており、かつ圧力媒体導管からの放圧
導管の分岐部と搬送ポンプとの間に、弁の方向に開放す
る逆止弁が配置されていることによって、上記課題を解
決することができた。SUMMARY OF THE INVENTION According to the invention, a solenoid valve is arranged in the pressure relief conduit and is opened in the direction of the valve between the branch of the pressure relief conduit from the pressure medium conduit and the transfer pump. The above-mentioned problem was able to be solved by arranging the check valve.
【０００８】[0008]
【発明の効果】請求項１に記載の特徴を備えた本発明の
燃料噴射装置は、滑り弁に対し常時貫流している圧力媒
体導管内に逆止弁を配置することによって、搬送ポンプ
と圧力媒体導管と放圧導管とを接続している電磁弁との
間で、電磁弁による閉鎖の後に、電磁弁と逆止弁との間
に反動管乃至揺動管（ハンマパイプｈａｍｍｅｒ ｐｉ
ｐｅ）が形成されうるという利点を有している。その際
逆止弁は逆行する圧力波によって電磁弁の閉鎖後に同じ
様に閉ぢられるので、閉ぢられた容積内で圧力媒体の流
れエネルギが急激な圧力上昇に変換せしめられる。この
圧力上昇によって滑り弁は、戻しばねの力に抗してその
ポンプ作業室と燃料導管との間の接続部を閉ぢるように
なる。このような形式で搬送ポンプの吐出量が少ない場
合でも、そのように形成される圧力上昇によって搬送ポ
ンプの静的な吐出圧力に対し極めて急激なかつ滑り弁の
閉鎖のために十分な圧力上昇が、電磁弁を利用するだけ
で圧力導管内で達成される。このためコスト的に有利な
製作が可能になるばかりでなく、制御技術的なコストも
廉値になる。更に本発明の燃料噴射装置にあっては、必
要な高い制御動力を保証するために、１０バールを超え
るような圧力レベルの付加的な液圧装置が全く必要でな
い。これによって同じ様に、装置の構成に対する諸要求
を減らすことができる。The fuel injection device of the invention with the features of claim 1 arranges a check valve in the pressure medium conduit which is constantly flowing through the slide valve, so that the delivery pump and pressure Between the solenoid valve connecting the medium conduit and the pressure relief conduit, after closing by the solenoid valve, a reaction tube or rocker tube (hammer pipe hammer pi) between the solenoid valve and the check valve.
pe) can be formed. In that case, the check valve is likewise closed after the closing of the solenoid valve by the reverse pressure wave, so that in the closed volume the flow energy of the pressure medium is converted into a sharp pressure rise. This increase in pressure causes the slide valve to close the connection between its pump chamber and the fuel conduit against the force of the return spring. Even when the delivery amount of the delivery pump is small in this manner, the pressure rise thus formed causes a very rapid increase in the static delivery pressure of the delivery pump and a sufficient pressure increase for closing the slide valve. This is accomplished in the pressure conduit simply by using a solenoid valve. For this reason, not only cost-effective production is possible, but also control technology costs are low. Furthermore, in the fuel injection device according to the invention, no additional hydraulic device with a pressure level above 10 bar is required in order to ensure the required high control power. This likewise reduces the requirements on the construction of the device.
【０００９】その際揺動導管は有利な形式で次の様に設
計される。つまり滑り弁内で導管に接続された作業室の
容積が拡大する際、導管内に残っている静止圧力は、閉
鎖時の滑り弁部材のストローク運動によってポンプ作業
室と燃料導管との間の接続部内で滑り弁を閉ぢた状態に
確実に保持するのに充分な大きさであり、更に閉鎖位置
の弁部材は、燃料噴射ポンプの吐出圧力に晒されること
のない、閉鎖部材の調節方向に向いたシール面を有して
いる。滑り弁は有利な形式で円錐形のシール面を備えた
シート弁として形成されていて、仕上げ精度に対する要
求が厳しくないようになっている。更に円錐形の弁座の
ために、弁部材の高い閉鎖圧力が滑り弁の制御に対して
だけ必要であるようになる。その理由は、スライド弁が
閉ぢている場合吐出ストローク中ポンプ作業室内に増圧
される高圧が、滑り弁部材の調節方向にもはや作用しな
いで、圧力媒体導管内の静止圧力がばね力と加圧ポンプ
の吐出圧力だけによって克服されなければならないから
である。これに対しシート弁は極めて急激な高圧吐出の
終了を実現することができる。その理由は、電磁弁によ
る圧力媒体導管の放圧の際滑り弁の戻り運動が、僅かの
開放の際既に、弁シール面に作用する燃料の高圧によっ
て支持されるからである。更に滑り弁の開放の際には、
圧力によって開放方向に負荷される面が弁部材の閉鎖方
向に向いている面よりも大きい。The oscillating conduit is then designed in an advantageous manner as follows. That is, as the volume of the working chamber connected to the conduit in the slide valve increases, the rest pressure remaining in the conduit causes the stroke motion of the slide valve member to close to establish a connection between the pump working chamber and the fuel conduit. The valve member in the closed position is large enough to securely hold the slide valve closed in the section, and the valve member in the closed position is in the adjusting direction of the closing member without being exposed to the discharge pressure of the fuel injection pump. It has a facing sealing surface. The slide valve is expediently designed as a seat valve with a conical sealing surface so that the demands on the finishing accuracy are not so demanding. Furthermore, the conical valve seat makes high closing pressure of the valve member only necessary for control of the slide valve. The reason for this is that the high pressure that is built up in the pump working chamber during the discharge stroke when the slide valve is closed no longer acts in the adjusting direction of the slide valve member, and the static pressure in the pressure medium conduit exerts a spring force on it. This is because it must be overcome only by the discharge pressure of the pressure pump. On the other hand, the seat valve can realize the extremely rapid end of high-pressure discharge. The reason for this is that the return movement of the sliding valve during the pressure relief of the pressure medium conduit by the solenoid valve is already supported by the high pressure of the fuel acting on the valve sealing surface during a slight opening. Furthermore, when opening the slide valve,
The surface loaded in the opening direction by the pressure is larger than the surface facing the closing direction of the valve member.
【００１０】別の利点は、円筒状の滑り弁部材をケーシ
ングの案内孔内に外方から挿入することによって、また
案内孔内に突入した閉鎖ねじの端面が滑り弁の戻しばね
のための当接面として利用されうるような形式での、閉
鎖ねじを用いた案内孔の閉鎖によって、夫々達成されて
いる。従って閉鎖ねじの螺入深さを介して簡単な形式
で、ばねの予張力ひいては滑り弁の開放方向における戻
し力を調節することができる。Another advantage is that the cylindrical slide valve member is inserted into the guide hole of the casing from the outside, and the end face of the closing screw projecting into the guide hole is used for the return spring of the slide valve. This is achieved in each case by closing the guide hole with a closing screw in such a way that it can be used as a contact surface. The pretension of the spring and thus the return force in the opening direction of the slide valve can thus be adjusted in a simple manner via the screw-in depth of the closing screw.
【００１１】制御回路として役立っている圧力媒体回路
を噴射弁のための燃料回路から分離することによって、
更に有利な形式で燃料として重油を使用することも可能
であり、その際装置の運転中１８０℃までに加熱された
重油と電磁弁との接触は阻止されている。By separating the pressure medium circuit, which serves as a control circuit, from the fuel circuit for the injection valve,
It is also possible to use heavy oil as fuel in a more advantageous manner, whereby contact between the heavy oil heated to 180 ° C. and the solenoid valve is prevented during operation of the device.
【００１２】本発明の対象の別の利点及び別の有利な構
成は、次の説明、図面及び請求項に述べられている。Further advantages and further advantageous configurations of the subject matter of the invention are set forth in the following description, drawings and claims.
【００１３】[0013]
【実施例】本発明の燃料噴射装置の２つの実施例を図面
に図示し、次にこれを詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Two embodiments of the fuel injection device of the present invention are shown in the drawings and will now be described in detail.
【００１４】図１に概略図示の燃料噴射装置にあっては
シリンダ孔１がポンプケーシング３内に装着されてお
り、該孔１内にポンプピストン５が案内され、該ピスト
ン５は、詳細には図示なしのカム駆動部によって軸方向
に往復状に駆動されている。ポンプピストン５はその端
面７によってシリンダ孔１内のポンプ作業室９を制限
し、該作業室９は接続通路１１を介して制御室１３に常
時接続されており、該制御室１３から定圧弁１５を含む
高圧導管１７が、燃料を供給されるべき内燃機関の燃焼
室内に突入している噴射弁１９に通じている。その際定
圧弁１５は、反対方向に開放された２つの逆止弁によっ
て形成されていて、該逆止弁を介して高圧導管１７内の
所定の静止圧力を調節することができるようになってい
る。In the fuel injection device schematically shown in FIG. 1, a cylinder hole 1 is mounted in a pump casing 3, a pump piston 5 is guided in the hole 1, and the piston 5 is described in detail. It is reciprocally driven in the axial direction by a cam drive unit (not shown). The pump piston 5 limits the pump working chamber 9 in the cylinder hole 1 by the end face 7, and the working chamber 9 is constantly connected to the control chamber 13 via the connection passage 11, and the constant pressure valve 15 is connected to the control chamber 13 from the control chamber 13. A high-pressure conduit 17, which contains a fuel cell, leads to an injection valve 19 which projects into the combustion chamber of the internal combustion engine to be supplied with fuel. The constant-pressure valve 15 is in this case formed by two check valves which are opened in opposite directions and through which the predetermined rest pressure in the high-pressure conduit 17 can be adjusted. There is.
【００１５】更に制御室１３から滑り弁２１を介して閉
鎖可能な燃料導管２３が分岐し、該燃料導管２３は供給
導管２５に開口し、該供給導管２５は一方で、搬送ポン
プ２７を含む吐出導管２９を介して燃料貯蔵タンク３１
からの燃料によって充たされている。Furthermore, a closable fuel conduit 23 branches off from the control chamber 13 via a slide valve 21, which opens into a supply conduit 25, which on the one hand comprises a delivery pump 27. Fuel storage tank 31 via conduit 29
Filled with fuel from.
【００１６】ポンプ作業室９に接続された制御室１３と
燃料導管２３との間の接続部を閉鎖している滑り弁２１
が、ピストン状の滑り弁部材３３から形成されており、
該部材３３は、制御室１３を横切っているポンプケーシ
ングの案内孔３５内で軸方向にスライド可能に案内され
ていて、その套面に円錐形の横断面縮小部を有してお
り、該縮小部によって弁シール面３７が形成されてい
る。その際この弁シール面３７は、制御室から出発して
いる円錐形の弁座面３９と協働し、該弁座面３９は、案
内孔３５の横断面縮小部を貫通してより小さな直径を備
えた領域に向って形成されており、その際燃料導管２３
は、案内孔３５の直径の減少した部分に開口していて、
滑り弁部材３３の弁シール面３７に隣接するリング溝６
７によって覆われており、該リング溝６７によって、よ
り小さな直径を備えた案内孔部分において、案内孔３５
と滑り弁部材３３との間にリング室４１が形成されてい
る。このリング室４１は、弁座とは反対の側で滑り弁部
材３３の新たな横断面拡大部によって制限されていて、
スライド弁部材３３が弁座３９から持ち上げられた場
合、燃料導管２３による制御室１３への燃料の貫流を可
能にしている。A slide valve 21 closing the connection between the control chamber 13 connected to the pump working chamber 9 and the fuel conduit 23.
Is formed from a piston-shaped slide valve member 33,
The member 33 is slidably guided in the axial direction in a guide hole 35 of the pump casing that traverses the control chamber 13, and has a conical cross-section reduction portion on its sleeve surface. A valve seal surface 37 is formed by the portion. This valve sealing surface 37 then cooperates with a conical valve seat surface 39 starting from the control chamber, which valve seat surface 39 penetrates through the cross-sectional reduction of the guide hole 35 and has a smaller diameter. Formed towards the region with the fuel conduit 23
Has an opening in a portion where the diameter of the guide hole 35 is reduced,
Ring groove 6 adjacent to valve sealing surface 37 of slide valve member 33
7 by means of the ring groove 67, in the part of the guide hole with a smaller diameter, the guide hole 35
A ring chamber 41 is formed between the slide valve member 33 and the slide valve member 33. This ring chamber 41 is bounded on the side facing away from the valve seat by a new cross section enlargement of the slide valve member 33,
When the slide valve member 33 is lifted from the valve seat 39, it allows fuel to flow through the fuel conduit 23 into the control chamber 13.
【００１７】滑り弁部材３３は、ポンプケーシング３の
案内孔３５の出口側のその端面において戻しばね４３に
よって負荷されており、該戻しばね４３は他方では、案
内孔３５を外方に向って閉ぢている閉鎖ねじ４５の、案
内孔３５内に突入した端面に支えられており、かつ出発
状態つまり滑り弁２１の開放状態において滑り弁部材３
３を弁座から持ち揚げて保持している。戻しばね４３と
は反対側の、ばね側端部に対して直径の拡径された弁部
材３３の部分が、案内孔３５内の作業室４７を制限して
おり、該作業室４７は他方では、段部４８を有する案内
孔３５の端部によって制限されていて、圧力媒体導管４
９に接続されている。この圧力媒体導管４９は、第１実
施例においては同じ様に供給導管２５に接続されてい
て、作業室４７の方向に開放された逆止弁５１を有して
いる。更に放圧導管５３が逆止弁５１と作業室４７との
間で圧力媒体導管４９から分岐しており、該放圧導管５
３は、燃料貯蔵タンク３１に開口し、かつ圧力媒体管４
９と共に制御回路を形成している。The slide valve member 33 is loaded by a return spring 43 at its end face on the outlet side of the guide hole 35 of the pump casing 3, which on the other hand closes the guide hole 35 outward. The slide valve member 3 is supported by the end face of the closing screw 45 protruding into the guide hole 35 and is in the starting state, that is, the slide valve 21 is open.
3 is lifted from the valve seat and held. The part of the valve member 33 on the side opposite to the return spring 43, whose diameter is increased with respect to the spring side end, limits the working chamber 47 in the guide hole 35, which on the other hand Restricted by the end of a guide hole 35 with a step 48, the pressure medium conduit 4
9 is connected. This pressure medium conduit 49 is likewise connected in the first embodiment to the supply conduit 25 and has a check valve 51 which is open in the direction of the working chamber 47. Further, a pressure release conduit 53 branches from the pressure medium conduit 49 between the check valve 51 and the working chamber 47, and the pressure release conduit 5
3 opens into the fuel storage tank 31 and the pressure medium pipe 4
9 together with 9 form a control circuit.
【００１８】その際放圧導管５３は、圧力媒体導管４９
に対し放圧導管５３内に配置された電磁弁５５を介して
閉鎖可能であり、該電磁弁５５は、内燃機関の運転パラ
メータによって処理された電気的な制御装置によって制
御されている。その際逆止弁５１に関連して放圧導管５
３を閉鎖することにより、圧力媒体の圧力媒体導管４９
からの放圧流出が衝撃的に阻止され、その結果閉鎖され
た圧力媒体導管４９が反動管乃至揺動管のように作用し
て、その内方に閉ぢ込められた媒体の流れエネルギが圧
力上昇に変換せしめられ、その到達する圧力は、搬送ポ
ンプ２７の吐出能力によって利用可能な圧力よりも更に
大きい。In this case, the pressure relief conduit 53 is a pressure medium conduit 49.
Can be closed via a solenoid valve 55 arranged in the pressure relief conduit 53, which solenoid valve 55 is controlled by an electrical control device which is processed by operating parameters of the internal combustion engine. In that case, the pressure relief conduit 5 in relation to the check valve 51
3 by closing the pressure medium pressure medium conduit 49
The release of pressure from the chamber is shockedly blocked, so that the closed pressure medium conduit 49 acts like a reaction tube or oscillating tube, so that the flow energy of the medium confined inwardly is compressed. It is converted to a rise and the pressure reached is even higher than the pressure available due to the delivery capacity of the transport pump 27.
【００１９】更に燃料導管２３内で一定の圧力を保持す
るため、圧力弁５９を含む戻り導管６１が燃料貯蔵タン
ク３１に分岐しており、その際圧力弁５９は、燃料導管
２３内の一定の供給圧力の外に燃料装置内の所定の静圧
も維持している。Furthermore, in order to maintain a constant pressure in the fuel conduit 23, a return conduit 61 containing a pressure valve 59 branches into the fuel storage tank 31, the pressure valve 59 being a constant pressure in the fuel conduit 23. In addition to the supply pressure, a predetermined static pressure inside the fuel system is also maintained.
【００２０】ポンプピストン５及び弁部材３３における
漏洩燃料は、リング溝を介しリング溝によって捕えられ
て、漏洩油導管６３を介し燃料貯蔵タンク３１に戻され
る。Leakage fuel in the pump piston 5 and the valve member 33 is caught by the ring groove via the ring groove and returned to the fuel storage tank 31 via the leak oil conduit 63.
【００２１】本発明の燃料噴射装置は次のような形式で
作業する。The fuel injector of the present invention operates in the following manner.
【００２２】電磁弁５５が開放されると作業室４７内の
圧力が低下して、滑り弁部材３３が作動位置に持ってこ
られる。ポンプピストン５の吸込みストローク中のポン
プ作業室９への充填は、そのように開放された滑り弁２
１によって行われ、その際滑り弁部材３３は戻しばね４
３によって段部４８に当接して保持されており、その結
果燃料は、搬送ポンプ２７によて燃料貯蔵タンク３１か
ら吐出導管２９、供給導管２５、燃料導管２３、制御室
１３及び接続通路１１を介しポンプ作業室９へと搬送せ
しめられる。When the solenoid valve 55 is opened, the pressure in the working chamber 47 drops, and the slide valve member 33 is brought to the operating position. The filling of the pump working chamber 9 during the suction stroke of the pump piston 5 is accomplished by the sliding valve 2 thus opened.
1 by means of which the slide valve member 33 engages the return spring 4
3 is held in contact with the step portion 48 by means of 3, so that the fuel flows from the fuel storage tank 31 to the discharge conduit 29, the supply conduit 25, the fuel conduit 23, the control chamber 13 and the connection passage 11 by the transport pump 27. It is conveyed to the pump working chamber 9 via the.
【００２３】続くポンプピストン５の吐出ストロークの
際には、夫々噴射パラメータに応じて先づ燃料の１部分
が、再びポンプ作業室９から燃料導管２３、供給導管２
５及び戻り導管６１を介して燃料貯蔵タンク３１へと逆
に押し除けられる。During the subsequent discharge stroke of the pump piston 5, a portion of the fuel is fed again from the pump working chamber 9 to the fuel conduit 23 and the supply conduit 2 according to the respective injection parameters.
5 and via the return conduit 61 back into the fuel storage tank 31.
【００２４】同時に燃料導管２３に対し併行的に圧力媒
体導管４９内に吐出された燃料は、開放された電磁弁５
５を貫流し、放圧導管５３を介して燃料貯蔵タンク３１
内へ逆送され、その結果滑り弁２１の作業室４７は、戻
しばね４３の力を充分に克服しえないような僅かな圧力
だけで負荷されるようになる。ポンプ作業室９内の高圧
吐出は、制御装置５７によて制御される電磁弁５５の通
電によって開始されるので、２ポート２位置切換弁とし
て形成された電磁弁５５が放圧導管５３を閉鎖するよう
になる。At the same time, the fuel discharged into the pressure medium conduit 49 in parallel with the fuel conduit 23 is released by the opened solenoid valve 5.
5 through the pressure release conduit 53, the fuel storage tank 31
It is fed back in, so that the working chamber 47 of the slide valve 21 is loaded with only a slight pressure which is not sufficient to overcome the force of the return spring 43. High-pressure discharge in the pump working chamber 9 is started by energizing the solenoid valve 55 controlled by the controller 57, so that the solenoid valve 55 formed as a 2-port 2-position switching valve closes the pressure release conduit 53. Come to do.
【００２５】圧力媒体導管４９内に位置して流れている
媒体は、電磁弁５５において反射せしめられ、それによ
って逆流する圧力波が発生し、該圧力波は圧力媒体導管
４９内の逆止弁５１も閉鎖せしめる。その際圧力媒体導
管４９の閉ぢられた容積内の流れエネルギが圧力上昇に
変換せしめられ、該圧力上昇は滑り弁２１の作業室４７
内に引き継がれ、その位置で滑り弁部材３３は、圧力衝
撃により戻しばね４３の力に抗してその弁シール面３７
が弁座３９に当接するようになり、その結果ポンプ作業
室９と燃料導管２３との間の接続が閉鎖される。その際
圧力媒体導管４９内に閉ぢ込められた容積によって形成
される反動管乃至揺動管の大きさは、作業室４７の容積
が増大するのにかかわらず、揺動管内に残留する静圧
が、滑り弁部材３３を戻しばね４３の力に抗して弁座３
９に当接して保持するのに十分であるような大きさに寸
法化されている。その際弁座３９は、弁部材３３の作業
室側のより大きな直径によって弁部材３３のばね室側部
分のより小さな直径に対して支持されるので、閉鎖位置
における作業面はより大きくなる。The medium flowing in the pressure medium conduit 49 is reflected in the solenoid valve 55, which produces a backflowing pressure wave, which is a check valve 51 in the pressure medium conduit 49. Also close it. In that case, the flow energy in the closed volume of the pressure medium conduit 49 is converted into a pressure rise, which rises in the working chamber 47 of the slide valve 21.
And in that position the sliding valve member 33 resists the force of the return spring 43 due to the pressure shock and its valve sealing surface 37.
Abut the valve seat 39, so that the connection between the pump working chamber 9 and the fuel conduit 23 is closed. At this time, the size of the reaction tube or the rocking tube formed by the volume enclosed in the pressure medium conduit 49 depends on the static pressure remaining in the rocking tube despite the increase in the volume of the working chamber 47. The slide valve member 33 against the force of the return spring 43 and the valve seat 3
9 is sized to be sufficient to abut and hold 9. The valve seat 39 is then supported by the larger diameter of the valve member 33 on the working chamber side against the smaller diameter of the portion of the valve member 33 on the spring chamber side, so that the working surface in the closed position is larger.
【００２６】燃料導管２３の閉鎖制御の結果ポンプピス
トン５の更なる吐出運動中ポンプ作業室９内に高圧が増
大され、該高圧は、定圧弁１５の開放後高圧導管１７を
介して噴射弁１９に伝達され、その位置において公知の
形式で、燃料を供給されるべき内燃機関の燃焼室内の燃
料噴射装置へ案内される。As a result of the closing control of the fuel line 23, the high pressure is increased in the pump working chamber 9 during the further discharge movement of the pump piston 5, which after opening the constant pressure valve 15 is passed through the high pressure line 17 to the injection valve 19. And is guided in a known manner in its position to the fuel injectors in the combustion chamber of the internal combustion engine to be supplied with fuel.
【００２７】高圧吐出及び燃料噴射の終了は電磁弁５５
の制御によって開始され、その結果揺動管内の圧力が放
圧導管５３に急激に放圧せしめられる。その際作業室４
７も放圧せしめられ、かつ戻しばね４３が滑り弁２１を
新たに開放し、そのためにポンプ作業室９内の圧力も燃
料導管２３内に放圧せしめられ、その際高圧導管１７内
の圧力降下によって噴射弁１９が閉鎖せしめられる。そ
の際弁部材３３の開ストロークは、開放方向で弁部材３
３上に作用する燃料高圧によって支えられている。The solenoid valve 55 is used to terminate the high pressure discharge and the fuel injection.
Control is performed, and as a result, the pressure in the rocking tube is suddenly released to the pressure release conduit 53. At that time, work room 4
7 is also depressurized and the return spring 43 reopens the slide valve 21 so that the pressure in the pump working chamber 9 is also depressurized in the fuel line 23, the pressure drop in the high-pressure line 17 being reduced. The injection valve 19 is closed by this. At that time, the opening stroke of the valve member 33 is set in the opening direction.
3 is supported by the high pressure of the fuel acting on it.
【００２８】図２に図示の第２実施例は、圧力媒体導管
４９と放圧導管５３とによって形成された制御回路が、
燃料導管２３によって形成された燃料回路から分離され
ているという点で、第１実施例と異なっている。In the second embodiment shown in FIG. 2, the control circuit formed by the pressure medium conduit 49 and the pressure relief conduit 53 is
It differs from the first embodiment in that it is separated from the fuel circuit formed by the fuel conduit 23.
【００２９】その際燃料回路は、図１に類似して、搬送
ポンプ２７によって燃料貯蔵タンク３１から供給される
燃料導管２３から成っており、その圧力は、この場合も
圧力弁５９を介し燃料導管２３から分岐した戻し導管６
１において調節可能である。The fuel circuit then consists, similar to FIG. 1, of a fuel line 23 which is supplied from a fuel storage tank 31 by a transfer pump 27, the pressure of which is again via the pressure valve 59. Return conduit 6 branched from 23
It is adjustable in 1.
【００３０】圧力媒体導管４９は図２では、別個の圧力
媒体貯蔵タンク７１から圧力媒体搬送ポンプ７３及び供
給通路７５を介して供給されており、その際逆止弁５１
及び電磁弁５５を備えた放圧導管５３が図２同様に配置
されており、更に放圧導管５３は圧力媒体貯蔵タンク７
１に開口している。The pressure-medium conduit 49 is supplied in FIG. 2 from a separate pressure-medium storage tank 71 via a pressure-medium transport pump 73 and a supply passage 75, with check valve 51.
And a pressure relief conduit 53 equipped with a solenoid valve 55 is arranged in the same way as in FIG.
It is open to 1.
【００３１】第２実施例にあっては供給通路７５内の供
給圧力が、制御可能な戻し回路内の絞り７７によって圧
力媒体貯蔵タンク７１において制御されている。In the second embodiment, the supply pressure in the supply passage 75 is controlled in the pressure medium storage tank 71 by the throttle 77 in the controllable return circuit.
【００３２】図２に図示の第２実施例の作業形式は、ポ
ンプ作業室９を充している燃料回路と、滑り弁部材３３
を負荷している制御回路とが別個の貯蔵タンク３１，７
１から夫々供給されているという点で、第１実施例の作
用形式と異なっている。The work type of the second embodiment shown in FIG. 2 is that the fuel circuit filling the pump work chamber 9 and the slide valve member 33 are used.
Storage tanks 31, 7 separate from the control circuit loading
It is different from the operation mode of the first embodiment in that it is supplied from each.
【００３３】回路をこのように分離することによって燃
料として重油を使用することが可能となる。その理由
は、燃料噴射装置の運転中１８０℃までに加熱された重
油が制御回路を制御している電磁弁５５とは接触しない
からである。This separation of the circuit makes it possible to use heavy oil as fuel. The reason is that the heavy oil heated to 180 ° C. during the operation of the fuel injection device does not come into contact with the solenoid valve 55 controlling the control circuit.
【図１】本発明の燃料噴射装置の第１実施例の図であっ
て、燃料噴射装置の燃料回路と制御回路とが共通の燃料
貯蔵タンクから共に供給されている。FIG. 1 is a diagram of a first embodiment of a fuel injection device of the present invention, in which a fuel circuit and a control circuit of the fuel injection device are both supplied from a common fuel storage tank.
【図２】本発明の燃料噴射装置の第２実施例の図であっ
て、燃料噴射装置の燃料回路と制御回路とが分離されて
いる。FIG. 2 is a diagram of a second embodiment of the fuel injection device of the present invention, in which the fuel circuit and the control circuit of the fuel injection device are separated.
１ シリンダ孔 ３ ポンプケーシング ５ ポンプピストン ７ 端面 ９ ポンプ作業室 １１ 接続通路 １３ 制御室 １５ 室圧弁 １７ 高圧導管 １９ 噴射弁 ２１ 滑り弁 ２３ 燃料導管 ２５ 供給導管 ２７ 搬送ポンプ ２９ 吐出導管 ３１ 燃料貯蔵タンク ３３ スライダ弁部材 ３５ 案内孔 ３７ 弁シール面 ３９ 弁座面 ４１ リング室 ４３ 戻しばね ４５ 閉鎖ばね ４７ 作業室 ４８ 段部 ４９ 圧力媒体導管 ５１ 逆止弁 ５３ 放圧導管 ５５ 電磁弁 ５７ 制御装置 ５９ 圧力弁 ６１ 戻し導管 ６３ 漏洩油導管 ６７ リング溝 ７１ 圧力媒体貯蔵タンク ７３ 圧力媒体搬送ポンプ ７５ 供給通路 ７７ 絞り 1 Cylinder Hole 3 Pump Casing 5 Pump Piston 7 End Face 9 Pump Working Chamber 11 Connection Passage 13 Control Room 15 Chamber Pressure Valve 17 High Pressure Pipeline 19 Injection Valve 21 Slide Valve 23 Fuel Pipeline 25 Supply Pipeline 27 Transport Pump 29 Discharge Pipeline 31 Fuel Storage Tank 33 Slider valve member 35 Guide hole 37 Valve sealing surface 39 Valve seat surface 41 Ring chamber 43 Return spring 45 Closing spring 47 Working chamber 48 Step 49 Pressure medium conduit 51 Check valve 53 Pressure release conduit 55 Solenoid valve 57 Control device 59 Pressure valve 61 Return Conduit 63 Leaked Oil Conduit 67 Ring Groove 71 Pressure Medium Storage Tank 73 Pressure Medium Transfer Pump 75 Supply Passage 77 Throttle
Claims (9)
ンダ孔（１）内でシリンダブッシュに案内されかつカム
駆動によって軸方向に運動可能であるポンプピストン
（５）を備えており、該ポンプピストン（５）はシリン
ダ孔（１）内でポンプ作業室（９）を制限し、該ポンプ
作業室（９）は、燃料を供給されるべき内燃機関の燃焼
室内に突入している噴射弁（１９）に高圧導管（１７）
を介して接続されており、かつ制御された燃料導管（２
３）を介して燃料を充填及び放出することができ、更に
ポンプ作業室（９）に対する、高圧吐出を制御する燃料
導管（２３）の閉鎖が、燃料導管内に配置されかつ戻し
ばね（４３）の力に抗して液圧式に作動する弁（２１）
によって行われており、該弁（２１）は軸方向で閉鎖方
向に向いている圧力面を有し、該圧力面は、搬送ポンプ
（２７）によって貯蔵容器（３１）から供給される圧力
媒体導管を介し圧力媒体によって負荷されており、かつ
その圧力媒体負荷は、圧力媒体導管（４９）から分岐し
た放圧導管（５３）を電磁弁（５５）を用いて制御する
ことによって行われている形式のものにおいて、 電磁弁（５５）が放圧導管（５３）内に配置されてお
り、かつ圧力媒体導管（４９）からの放圧導管（５３）
の分岐部と搬送ポンプ（２７）との間に、弁（２１）の
方向に開放する逆止弁（５１）が配置されていることを
特徴とする、内燃機関の燃料噴射装置。1. A fuel injection device for an internal combustion engine, comprising a pump piston (5) guided in a cylinder bush in a cylinder hole (1) and movable axially by a cam drive. The piston (5) limits a pump working chamber (9) in the cylinder bore (1), which pump working chamber (9) projects into the combustion chamber of the internal combustion engine to which fuel is to be supplied (injection valve (9)). 19) high pressure conduit (17)
And a controlled fuel conduit (2
The closure of the fuel conduit (23), which can be charged and discharged via 3) and which controls the high-pressure discharge to the pump working chamber (9), is arranged in the fuel conduit and the return spring (43). Operated hydraulically against the force of the valve (21)
And the valve (21) has a pressure surface oriented axially in the closing direction, the pressure surface being supplied by a transfer pump (27) from a storage container (31) to a pressure medium conduit. Via a solenoid valve (55) which controls the pressure relief conduit (53) branched from the pressure medium conduit (49) by means of a solenoid valve (55). A solenoid valve (55) is arranged in the pressure relief conduit (53) and the pressure relief conduit (53) from the pressure medium conduit (49)
A fuel injector for an internal combustion engine, characterized in that a check valve (51) that opens in the direction of the valve (21) is arranged between the branch portion of the valve and the transfer pump (27).
の外周面に横断面縮小部を備えた弁部材（３３）を有
し、横断面縮小部は、弁シール面（３７）のより小さな
横断面への円錐形の移行部を形成し、該弁シール面（３
７）は、弁部材（３３）を案内している案内孔（３５）
の直径縮小部によって形成された円錐形の弁座（３９）
と協働し、かつ案内孔（３５）は弁座（３９）の一方の
側で直径の拡大された制御室（１３）に拡大されてお
り、該制御室（１３）は、ポンプ作業室（９）と噴射弁
（１９）との間の高圧導管（１７）の構成部分であり、
また弁座（３９）の他方の側は、より小さな直径を備え
た案内孔（３５）の孔区分に移行し、その位置で弁部材
（３３）のリング溝（６７）と協働して、より小さな直
径を備えた案内孔（３５）の孔区分内に、燃料導管（２
３）に接続された別のリング溝（４１）を形成してお
り、その内方で直径の減少した部分を備えた弁部材（３
３）が滑動していることを特徴とする、請求項１記載の
燃料噴射装置。2. A valve (21) formed as a sliding valve has on its outer peripheral surface a valve member (33) with a cross-section reduction part, which cross-section reduction part is provided with a valve sealing surface (37). Forming a conical transition to a small cross section, the valve sealing surface (3
7) is a guide hole (35) for guiding the valve member (33)
Conical valve seat formed by the reduced diameter portion (39)
And a guide hole (35) is enlarged on one side of the valve seat (39) into a control chamber (13) of increased diameter, which control chamber (13) comprises a pump working chamber (13). 9) and the injection valve (19), a component of the high pressure conduit (17),
The other side of the valve seat (39) also transitions into a hole section of the guide hole (35) with a smaller diameter, in which position in cooperation with the ring groove (67) of the valve member (33), Within the bore section of the guide bore (35) with the smaller diameter, the fuel conduit (2
(3) forming another ring groove (41) connected to the valve member (3) with a portion of reduced inner diameter.
Fuel injector according to claim 1, characterized in that 3) is sliding.
材（３３）の端面に戻しばね（４３）が当接しており、
該戻しばね（４３）は他方では案内孔（３５）の、外方
から調節可能な閉鎖ねじ（４５）によって支えられてい
ることを特徴とする、請求項２記載の燃料噴射装置。3. A return spring (43) is in contact with the end face of the valve member (33) opposite the pressure medium conduit (49),
3. The fuel injection device according to claim 2, characterized in that the return spring (43) is supported on the other hand by an externally adjustable closing screw (45) in the guide hole (35).
（４１）を制限している部分が、弁部材（３３）の、圧
力媒体導管（４９）の側の横断面よりも更に小さな横断
面を有していることを特徴とする、請求項２又は３記載
の燃料噴射装置。4. The part of the valve member (33) that limits the ring groove (41) on the spring side is smaller than the cross section of the valve member (33) on the pressure medium conduit (49) side. The fuel injection device according to claim 2 or 3, wherein the fuel injection device has a cross section.
３）とが共通の供給導管（２５）に開口し、該供給導管
（２５）は、搬送ポンプ（２７）による燃料貯蔵タンク
（３１）からの燃料で充満されており、かつ該燃料の圧
力は、供給導管（２５）から燃料貯蔵タンク（３１）へ
の戻り導管（６１）内の圧力弁（５９）を介して制御可
能であることを特徴とする、請求項１記載の燃料噴射装
置。5. A pressure medium conduit (49) and a fuel conduit (2).
3) opens into a common supply conduit (25) with which the supply conduit (25) is filled with fuel from the fuel storage tank (31) by the transfer pump (27) and the pressure of the fuel is 2. The fuel injection device according to claim 1, characterized in that it is controllable via a pressure valve (59) in a return conduit (61) from the supply conduit (25) to the fuel storage tank (31).
回路と、ポンプ作業室（９）を充填している燃料回路と
が互いに分離されており、かつ夫々１つの搬送ポンプ
（７３，２７）と圧力制御装置（７７，５９）とを有し
ていることを特徴とする、請求項１記載の燃料噴射装
置。6. The pressure medium circuit for controlling the slide valve (21) and the fuel circuit for filling the pump working chamber (9) are separated from each other, and each has one transfer pump (73, 27) Fuel injection device according to claim 1, characterized in that it comprises a pressure control device (77, 59).
媒体としてジーゼル燃料が夫々使用されていることを特
徴とする、請求項６記載の燃料噴射装置。7. The fuel injection device according to claim 6, wherein heavy oil is used as the fuel to be injected and diesel fuel is used as the pressure medium, respectively.
き内燃機関の運転パラメータを処理する電気的な制御装
置（５７）によって制御されていることを特徴とする、
請求項１記載の燃料噴射装置。8. The solenoid valve (55) is controlled by an electrical control device (57) which processes operating parameters of the internal combustion engine to which fuel is to be supplied.
The fuel injection device according to claim 1.
の間の高圧導管（１７）内に定圧弁（１５）が配置され
ていることを特徴とする、請求項１記載の燃料噴射装
置。9. Fuel according to claim 1, characterized in that a constant pressure valve (15) is arranged in the high-pressure conduit (17) between the pump working chamber (9) and the injection valve (19). Injection device.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4320620.4 | 1993-06-22 | ||
| DE4320620A DE4320620B4 (en) | 1993-06-22 | 1993-06-22 | Fuel injection device for internal combustion engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0719140A true JPH0719140A (en) | 1995-01-20 |
| JP3574681B2 JP3574681B2 (en) | 2004-10-06 |
Family
ID=6490884
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13905894A Expired - Fee Related JP3574681B2 (en) | 1993-06-22 | 1994-06-21 | Fuel injection device for internal combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP3574681B2 (en) |
| KR (1) | KR100340741B1 (en) |
| DE (1) | DE4320620B4 (en) |
| GB (1) | GB2279706B (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001003838A (en) * | 1999-05-21 | 2001-01-09 | Robert Bosch Gmbh | Electronic injection mechanism |
| WO2001059292A1 (en) * | 2000-02-07 | 2001-08-16 | Bosch Automotive Systems Corporation | Fuel injection device |
| JP2003515033A (en) * | 1999-11-13 | 2003-04-22 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | Fuel injection system |
| US7066152B2 (en) | 2004-09-03 | 2006-06-27 | Ford Motor Company | Low evaporative emission fuel system depressurization via solenoid valve |
| JP2012533010A (en) * | 2009-07-08 | 2012-12-20 | デルファイ・テクノロジーズ・ホールディング・エス．アー．エール．エル． | Pump device |
| JP2013531176A (en) * | 2010-07-14 | 2013-08-01 | ボルボ ラストバグナー アーベー | Fuel injection system with pressure controlled bleed function |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DK174139B1 (en) * | 1995-03-14 | 2002-07-08 | Man B & W Diesel As | Injection system with variable setting of fuel injection time in a high-pressure diesel engine |
| FI101999B1 (en) | 1997-02-20 | 1998-09-30 | Waertsilae Nsd Oy Ab | Arrangement for an injection pump at an internal combustion engine |
| DE10054202A1 (en) * | 2000-11-02 | 2002-05-29 | Siemens Ag | Injector for injecting fuel into a combustion chamber |
| DE10138362A1 (en) * | 2001-04-06 | 2002-10-17 | Bosch Gmbh Robert | Single-punch injection pump for a common rail fuel injection system |
| DE10139055A1 (en) * | 2001-08-08 | 2003-02-27 | Bosch Gmbh Robert | Method, computer program, control and / or regulating device and fuel system for an internal combustion engine |
| DE10153189A1 (en) * | 2001-10-27 | 2003-05-15 | Bosch Gmbh Robert | Fuel pump, fuel system, method for operating a fuel system and internal combustion engine |
| DE10155718C2 (en) * | 2001-11-13 | 2003-09-18 | Hermann Golle | Injection system for diesel engines |
| DE10229395B4 (en) * | 2002-06-29 | 2006-02-16 | Robert Bosch Gmbh | Displacement machine, in particular radial piston pump in a fuel system of an internal combustion engine, and hydraulic system |
| DE102008043217A1 (en) * | 2008-10-28 | 2010-04-29 | Robert Bosch Gmbh | High-pressure fuel pump for an internal combustion engine |
| WO2015048983A1 (en) * | 2013-10-04 | 2015-04-09 | Volvo Truck Corporation | Fuel injection system for low-viscosity fuels |
| ITUB20153528A1 (en) * | 2015-09-10 | 2017-03-10 | Bosch Gmbh Robert | HIGH PRESSURE PUMP UNIT FOR FUEL SUPPLEMENT, PREFERABLY GASOIL, TO AN INTERNAL COMBUSTION ENGINE |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1153941B (en) * | 1958-08-14 | 1963-09-05 | Pierre Etienne Bessiere | Self-regulating piston pump for injecting fuel into internal combustion engines |
| DE3001051A1 (en) * | 1980-01-12 | 1981-07-16 | Robert Bosch Gmbh, 7000 Stuttgart | FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES, ESPECIALLY FOR DIESEL ENGINES |
| FR2481752A1 (en) * | 1980-04-30 | 1981-11-06 | Renault Vehicules Ind | IMPROVEMENT OF MECHANICAL FUEL INJECTION DEVICES, IN PARTICULAR FOR DIESEL ENGINES |
| DE3111837A1 (en) * | 1980-06-21 | 1982-01-14 | Robert Bosch Gmbh, 7000 Stuttgart | "FUEL INJECTION DEVICE FOR INTERNAL COMBUSTION ENGINES, ESPECIALLY FOR DIESEL ENGINES" |
| US4387686A (en) * | 1981-01-27 | 1983-06-14 | Robert Bosch Gmbh | Fuel injection apparatus for internal combustion engines, in particular for diesel engines |
| JP2636379B2 (en) * | 1988-11-07 | 1997-07-30 | トヨタ自動車株式会社 | Fuel injection device |
| DE3910793C2 (en) * | 1989-04-04 | 1996-05-23 | Kloeckner Humboldt Deutz Ag | Fuel injector |
-
1993
- 1993-06-22 DE DE4320620A patent/DE4320620B4/en not_active Expired - Lifetime
-
1994
- 1994-06-21 JP JP13905894A patent/JP3574681B2/en not_active Expired - Fee Related
- 1994-06-21 KR KR1019940013993A patent/KR100340741B1/en not_active IP Right Cessation
- 1994-06-21 GB GB9412430A patent/GB2279706B/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001003838A (en) * | 1999-05-21 | 2001-01-09 | Robert Bosch Gmbh | Electronic injection mechanism |
| JP4612149B2 (en) * | 1999-05-21 | 2011-01-12 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | Electronic injection mechanism |
| JP2003515033A (en) * | 1999-11-13 | 2003-04-22 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | Fuel injection system |
| WO2001059292A1 (en) * | 2000-02-07 | 2001-08-16 | Bosch Automotive Systems Corporation | Fuel injection device |
| US7066152B2 (en) | 2004-09-03 | 2006-06-27 | Ford Motor Company | Low evaporative emission fuel system depressurization via solenoid valve |
| JP2012533010A (en) * | 2009-07-08 | 2012-12-20 | デルファイ・テクノロジーズ・ホールディング・エス．アー．エール．エル． | Pump device |
| JP2013531176A (en) * | 2010-07-14 | 2013-08-01 | ボルボ ラストバグナー アーベー | Fuel injection system with pressure controlled bleed function |
Also Published As
| Publication number | Publication date |
|---|---|
| GB2279706B (en) | 1996-02-07 |
| DE4320620A1 (en) | 1995-01-05 |
| GB2279706A (en) | 1995-01-11 |
| KR100340741B1 (en) | 2002-11-29 |
| DE4320620B4 (en) | 2004-04-01 |
| JP3574681B2 (en) | 2004-10-06 |
| GB9412430D0 (en) | 1994-08-10 |
| KR950001085A (en) | 1995-01-03 |
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