JP5727617B2 - Fuel injection system for internal combustion engine - Google Patents
Fuel injection system for internal combustion engine Download PDFInfo
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- JP5727617B2 JP5727617B2 JP2013537051A JP2013537051A JP5727617B2 JP 5727617 B2 JP5727617 B2 JP 5727617B2 JP 2013537051 A JP2013537051 A JP 2013537051A JP 2013537051 A JP2013537051 A JP 2013537051A JP 5727617 B2 JP5727617 B2 JP 5727617B2
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- fuel injection
- injection system
- valve
- throttle valve
- pump
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- 239000000446 fuel Substances 0.000 title claims description 32
- 238000002347 injection Methods 0.000 title claims description 22
- 239000007924 injection Substances 0.000 title claims description 22
- 238000002485 combustion reaction Methods 0.000 title claims description 4
- 239000000314 lubricant Substances 0.000 claims description 3
- 238000005086 pumping Methods 0.000 description 3
- 230000003993 interaction Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
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Classifications
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- 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
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- 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
- F02M59/205—Quantity of fuel admitted to pumping elements being metered by an auxiliary metering device
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- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
-
- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0047—Layout or arrangement of systems for feeding fuel
- F02M37/0052—Details on the fuel return circuit; Arrangement of pressure regulators
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- 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
- F02M59/34—Varying fuel delivery in quantity or timing by throttling of passages to pumping elements or of overflow passages, e.g. throttling by means of a pressure-controlled sliding valve having liquid stop or abutment
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- 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
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
- F02M37/0029—Pressure regulator in the low pressure fuel system
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
本発明は、増圧ポンプを介して高圧ポンプのポンプ内部空間と接続されるタンクを備えた内燃機関の燃料噴射システムであって、ポンプ内部空間は、計量ユニットを介してポンプ加圧室と接続され、ポンプ内部空間はさらに、弁ハウジングと、弁プランジャと、ばね室内に配置された弁ばねと、を有する溢れ弁を介して返流管と油圧連結される、上記燃料噴射システムに関する。 The present invention relates to a fuel injection system for an internal combustion engine having a tank connected to a pump internal space of a high-pressure pump via a booster pump, and the pump internal space is connected to a pump pressurization chamber via a metering unit. The pump internal space further relates to the fuel injection system, wherein the pump internal space is hydraulically connected to the return pipe via an overflow valve having a valve housing, a valve plunger, and a valve spring disposed in the spring chamber.
内燃機関のこの種の燃料噴射システムは、独国特許出願公開第102008042089号明細書で公知である。この燃料噴射システムの場合、計量ユニットの、連結された油圧空間が、燃料管を介して高圧ポンプの3つのポンプ加圧室と接続される。この燃料噴射システムの溢れ弁は、絞り弁が挿入された中空プランジャを有し、この中空プランジャは、溢れ弁のばね室を、溢れ弁の入口側と接続する。この構成によって、計量ユニットの入口の吸入圧力が従来よりも補正されて制御され、キイキイと軋む騒音(Quietschgeraeusch)が鋼製の接続管を利用した際にも確実に防止される。 A fuel injection system of this kind for an internal combustion engine is known from DE 102008042089. In the case of this fuel injection system, the connected hydraulic space of the metering unit is connected to the three pump pressurizing chambers of the high-pressure pump via the fuel pipe. The overflow valve of this fuel injection system has a hollow plunger into which a throttle valve is inserted, and this hollow plunger connects the spring chamber of the overflow valve to the inlet side of the overflow valve. With this configuration, the suction pressure at the inlet of the metering unit is corrected and controlled as compared to the prior art, and noise that is squeaky (Quietschgeraeusch) is reliably prevented even when a steel connecting pipe is used.
さらに、計量ユニットにより接続された油圧空間が、所謂ゼロ圧送絞り弁(Nullfoerderdrossel)を介して、タンクと、又は、増圧ポンプへの入口管と接続されることが公知である。このようなゼロ圧送絞り弁によって、ゼロ圧送(Nullfoerderung)が設定された際の、場合によって生じる計量ユニットの漏れが排流される。 Furthermore, it is known that the hydraulic space connected by the metering unit is connected to the tank or the inlet pipe to the pressure boosting pump via a so-called zero pressure throttle valve. Such a zero pressure feed throttle valve eliminates the leakage of the metering unit that may occur when zero pressure feed (Nullfeederung) is set.
本発明の根底には、ポンプ加圧室の充填圧力を圧送量に従って調整することが可能な燃料噴射システムを提供するという課題がある。 The basis of the present invention is to provide a fuel injection system capable of adjusting the filling pressure of the pump pressurizing chamber according to the pumping amount.
本課題は、ばね室が絞り弁回路を介して、計量ユニットにより接続される油圧空間と連結されることにより解決される。圧力分配器として機能する上記絞り弁回路によって、計量ユニットが制御する圧力に従って、厳密には差圧調整弁である溢れ弁のばね室内のより大きく又はより小さな圧力が調整される。従って、溢れ弁の前の圧力は、弁ばね特性曲線の純粋に機械的成分と、ばね室内の油圧と、から構成される。従って、ばね室内の圧力が変更されうるため、溢れ弁の前の圧力も変更される。 This problem is solved by connecting the spring chamber to the hydraulic space connected by the measuring unit via the throttle valve circuit. According to the pressure controlled by the metering unit, more or less pressure in the spring chamber of the overflow valve, which is strictly a differential pressure adjusting valve, is adjusted by the throttle valve circuit functioning as a pressure distributor. Accordingly, the pressure before the overflow valve is composed of a purely mechanical component of the valve spring characteristic curve and the hydraulic pressure in the spring chamber. Therefore, since the pressure in the spring chamber can be changed, the pressure before the overflow valve is also changed.
本発明の発展形態において、絞り弁回路は、絞り弁が挿入された管路接続である。計量ユニットと溢れ弁とは通常直接的に高圧ポンプのポンプハウジング内に組み込まれるため、管路接続(Leitungsverbindung)は、例えば、接続通路(Verbindungskanal)として形成されうる。その際に、絞り弁は、接続通路に内装された絞り要素によって、又は、管路接続の製造工程の際の直径減少によっても実現される。 In a development of the invention, the throttle valve circuit is a line connection with a throttle valve inserted. Since the metering unit and the overflow valve are usually directly integrated into the pump housing of the high-pressure pump, the conduit connection (Leitungsverbundung) can be formed, for example, as a connection channel (Verbindskunkal). In this case, the throttle valve can also be realized by a throttle element built into the connection passage or by a diameter reduction during the manufacturing process of the pipe connection.
本発明の発展形態において、ばね室は返流管と接続され、その際に、更なる別の構成において、返流管に返流絞り弁が挿入される。その際に、返流管は、上記挿入された返流絞り弁の後ろの任意の箇所で、管路接続とも接続可能であり、その際、返流絞り弁は、上記接続箇所の下流側で返流管に挿入される必要がある。 In a development of the invention, the spring chamber is connected to the return pipe, in which, in yet another configuration, a return throttle valve is inserted into the return pipe. At that time, the return pipe can be connected to the pipe connection at an arbitrary position behind the inserted return throttle valve. At that time, the return throttle valve is connected to the downstream side of the connection place. Need to be inserted into the return pipe.
本発明の更なる別の構成において、絞り弁は、返流絞り弁よりも低い絞り率を有する。換言すれば、絞り弁の流量断面は、返流絞り弁の流量断面よりも大きい。この調整によって、計量ユニットが解放された際には、ばね室内の圧力が上昇し、計量ユニットが閉鎖された際には、ばね室内の圧力は徐々に、ほぼ戻り圧力レベルにまで落ちる。絞り弁及び返流絞り弁の直径の適切な調整を介して、計量ユニットの開放ポジションと閉鎖ポジションとの間の圧力差を、ほぼ任意に調整することが可能である。 In yet another configuration of the invention, the throttle valve has a lower throttle rate than the return flow throttle valve. In other words, the flow rate cross section of the throttle valve is larger than the flow rate cross section of the return flow throttle valve. By this adjustment, the pressure in the spring chamber increases when the metering unit is released, and the pressure in the spring chamber gradually drops to almost the return pressure level when the metering unit is closed. Through appropriate adjustment of the diameters of the throttle valve and the return throttle valve, the pressure difference between the open position and the closed position of the metering unit can be adjusted almost arbitrarily.
本発明の発展形態において、絞り弁及び/又は返流絞り弁の前にはフィルタが接続され、このフィルタは、例えば発展形態においてディスクフィルタとして構成されうる。このようなフィルタ又はディスクフィルタによって、絞り弁が汚染粒子から確実に保護される。 In a development of the invention, a filter is connected in front of the throttle valve and / or the return throttle, and this filter can be configured, for example, as a disk filter in the development. Such a filter or disc filter ensures that the throttle valve is protected from contaminating particles.
本発明の更なる別の構成において、溢れ弁の排流管は返流管と接続される。同様に、更なる別の構成において、高圧ポンプの軸受潤滑剤排流管は返流管と接続される。これらの構成によって、既に高圧ポンプ内で全ての適切な管が返流管に繋がり、返流管が適切な形態で外部の管路接続を介してタンクと接続されることで、高圧ポンプの領域内の燃料噴射システムのコンパクトな構成が可能である。 In yet another configuration of the invention, the overflow valve drain tube is connected to the return tube. Similarly, in yet another configuration, the bearing lubricant discharge pipe of the high pressure pump is connected to the return pipe. With these configurations, all suitable pipes are already connected to the return pipe in the high-pressure pump, and the return pipe is connected to the tank in an appropriate form via an external pipe connection, so that A compact configuration of the internal fuel injection system is possible.
以上、本発明に係る構成によって以下のことが達成される。
‐圧送量に依存した充填圧力が印加され、例えば、充填要求が高い場合には高い充填圧力が設定され、少量の燃料量しか圧送する必要がない場合には、低い充填圧力が設定される。
‐明らかに拡大された作業領域が実現される。即ち、可変的な圧力レベルが安定的に設定されうる。1つの溢れ弁によって(1度の調整で)、絞り弁及び返流絞り弁のスロットル直径のバリエーションを介して、様々な圧力レベルを実現することが可能である。
‐特に弁ばねの、構成部品への小さな負荷が実現される。
‐バリエーションを避け、高価な弁ばねの使用を避けた結果コスト削減が達成され、その際に同時に、公知の解決策よりも高く調整圧力が設定されうる。
‐より小さな設置空間が必要となる。なぜならば、公知の構成では、特に圧力脈動の際の十分な振動の長さの決定の際に、調整圧力が増大するにつれて、弁ばねの、ばねの長さも増大するからである。
‐所謂ワン・アクチュエータ・システム(Ein−Steller−System)(計量ユニットのみを介する調整圧力制御)の場合、絞り弁は追加的に、ゼロ圧送絞り弁の機能を果たしうる。
‐返流絞り弁は追加的に、ばね室・減衰弁の代わりとなりうる。
As described above, the following is achieved by the configuration according to the present invention.
A filling pressure depending on the pumping amount is applied, for example, a high filling pressure is set when the filling demand is high, and a low filling pressure is set when only a small amount of fuel needs to be pumped.
-A clearly expanded work area is realized. That is, the variable pressure level can be set stably. With one overflow valve (with a single adjustment), it is possible to achieve different pressure levels through variations in throttle diameter of the throttle and return throttle valves.
-A small load on the components, especially the valve springs, is realized.
-Cost savings are achieved as a result of avoiding variations and avoiding the use of expensive valve springs, at the same time, the adjustment pressure can be set higher than known solutions.
-A smaller installation space is required. This is because, in the known arrangement, the spring length of the valve spring increases as the adjustment pressure increases, especially when determining the length of sufficient vibration during pressure pulsations.
In the case of the so-called one-actuator system (regulated pressure control only via the metering unit), the throttle valve can additionally function as a zero-feed throttle valve.
-A return throttle can additionally replace the spring chamber / damping valve.
本発明の更なる別の有利な構成は、図面の説明から明らかとなろう。図面の説明では、図示される本発明の実施例がより詳細に記述される。
図1は、本発明に係る燃料噴射システムの基本的な構成要素の相互作用を概略的に示している。増圧ポンプ1によって、燃料がタンク2からフィルタ装置を介して高圧ポンプ5のポンプ内部空間3内へと圧送される。
FIG. 1 schematically shows the interaction of the basic components of a fuel injection system according to the present invention. The booster pump 1 pumps fuel from the
高圧ポンプ5は、ポンプハウジングを有し、ポンプハウジング内では、ポンプカムシャフトが軸受箇所4a、4b内に回転自在に保持される。軸受箇所4a、4bは燃料により潤滑され、軸受潤滑剤排流管6a、6bを介して、ポンプ内部空間3から流れ出た軸受箇所4a、4bの燃料が、タンク2に通じる再循環管7へと排流される。ポンプカムシャフトは、当該ポンプカムシャフトの回転運動の際に、ローラタペットを介して、ポンププランジャ8を上下に並進運動させる。ポンププランジャ8はポンプ加圧室9と相互作用し、ポンプ加圧室9は、計量ユニット10を介してポンプ内部空間3と接続可能である。計量ユニット10によって、ポンプ加圧室9に供給される燃料量が、例えば、高圧貯圧器内の圧力に従って任意に設定されうる。ポンププランジャ8が上に向かって移動する際には、ポンプ加圧室9に搬入された燃料が、高圧油路11を介して高圧貯圧器へと圧送される。上記加圧室9に搬入される燃料のためのこの圧送行程に必要な吸入弁は、高圧ポンプ5のポンプシリンダヘッド12に直接的に挿入される。
The high-pressure pump 5 has a pump housing, and the pump camshaft is rotatably held in the bearing portions 4a and 4b in the pump housing. The bearing locations 4a and 4b are lubricated by the fuel, and the fuel in the bearing locations 4a and 4b flowing out from the pump internal space 3 through the bearing lubricant discharge pipes 6a and 6b leads to the recirculation pipe 7 leading to the
計量ユニットにより接続される(ポンプ加圧室9への接続管13により提示される)油圧空間は、管路接続14を介して、溢れ弁16のばね室と直接的又は間接的に連結される。溢れ弁16は弁ハウジング17を有し、弁ハウジング17内では、弁プランジャ18が弁ばね19の力に抗するように位置調整されうる。弁制御室20は、ポンプ内部空間3(又は、計量ユニット10の供給管)と接続される。計量ユニット10の閉鎖により、ポンプ内部空間3内の燃料圧力が上昇した際には、弁プランジャ18がばね室15の方向に動かされて、返流管7に通じる排流管21と接続された排流孔を解放する。この排流管21を介して、例えばゼロ圧送が設定された際には、増圧ポンプ1により圧送された燃料であって、軸受の潤滑に必要ではない上記燃料が排流される。
The hydraulic space connected by the metering unit (presented by the connecting
先に記載したように、計量ユニット10により接続される油圧空間(接続管13)は、管路接続14を介してばね室15と接続される。その際に、管路接続14には絞り弁22が挿入される。さらに、ばね室15は返流管7と接続され、その際、ばね室の近傍の返流管7内に返流絞り弁23が挿入される。管路接続14が、図示されるように、返流管7を介してばね室15と接続される場合には、返流絞り弁23は、いずれの場合にも接続箇所の下流に配置される。絞り弁22のスロットル直径は、返流絞り弁23のスロットル口径よりも大きく、従って、計量ユニット10が解放される際には、ばね室15内の圧力が上昇し、計量ユニット10が閉鎖される際には、ばね室15内の圧力は、返流管7内の圧力へと継続的に下げられる。
As described above, the hydraulic space (connection pipe 13) connected by the measuring unit 10 is connected to the spring chamber 15 via the pipe connection 14. At that time, a throttle valve 22 is inserted into the pipe connection 14. Further, the spring chamber 15 is connected to the return pipe 7, and a
絞り弁22及び返流絞り弁23の前には、フィルタ、特にディスクフィルタが接続されうる。
A filter, particularly a disk filter, may be connected in front of the throttle valve 22 and the return
Claims (10)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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DE102010043439.6 | 2010-11-05 | ||
DE102010043439A DE102010043439A1 (en) | 2010-11-05 | 2010-11-05 | Fuel injection system of an internal combustion engine |
PCT/EP2011/066401 WO2012059267A1 (en) | 2010-11-05 | 2011-09-21 | Fuel injection system of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
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JP2013545015A JP2013545015A (en) | 2013-12-19 |
JP5727617B2 true JP5727617B2 (en) | 2015-06-03 |
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JP2013537051A Expired - Fee Related JP5727617B2 (en) | 2010-11-05 | 2011-09-21 | Fuel injection system for internal combustion engine |
Country Status (7)
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EP (1) | EP2635791B1 (en) |
JP (1) | JP5727617B2 (en) |
KR (1) | KR101900965B1 (en) |
CN (1) | CN103201495B (en) |
DE (1) | DE102010043439A1 (en) |
RU (1) | RU2573068C2 (en) |
WO (1) | WO2012059267A1 (en) |
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US9422898B2 (en) | 2013-02-12 | 2016-08-23 | Ford Global Technologies, Llc | Direct injection fuel pump |
US9429124B2 (en) | 2013-02-12 | 2016-08-30 | Ford Global Technologies, Llc | Direct injection fuel pump |
US9599082B2 (en) | 2013-02-12 | 2017-03-21 | Ford Global Technologies, Llc | Direct injection fuel pump |
DE102013212145A1 (en) * | 2013-06-25 | 2015-01-08 | Robert Bosch Gmbh | pump |
DE102013226649A1 (en) * | 2013-12-19 | 2015-06-25 | Robert Bosch Gmbh | Fuel supply device of a fuel injection system of an internal combustion engine and overflow valve to it |
US9683512B2 (en) | 2014-05-23 | 2017-06-20 | Ford Global Technologies, Llc | Pressure device to reduce ticking noise during engine idling |
DE102014223240A1 (en) * | 2014-11-14 | 2016-05-19 | Robert Bosch Gmbh | Low pressure control system of a fuel delivery system of a fuel injection system and a Absteuerventil thereto |
DE102014223788A1 (en) * | 2014-11-21 | 2016-05-25 | Robert Bosch Gmbh | Pressure control device, in particular for a fluid-conveying high-pressure pump |
DE102018211338A1 (en) * | 2018-07-10 | 2020-01-16 | Robert Bosch Gmbh | Fuel delivery device for cryogenic fuels and method for operating a fuel delivery device |
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---|---|---|---|---|
RU2071572C1 (en) * | 1992-10-15 | 1997-01-10 | Ефим Яковлевич Мошинский | High-pressure fuel injection pump |
DE19846157A1 (en) * | 1998-10-07 | 2000-04-13 | Bosch Gmbh Robert | Pump arrangement for high-pressure fuel generation |
JP3709755B2 (en) * | 1999-12-08 | 2005-10-26 | 日産自動車株式会社 | Fuel supply device for internal combustion engine |
DE10100700C1 (en) * | 2001-01-10 | 2002-08-01 | Bosch Gmbh Robert | Fuel injection system with pressure control in the return line |
RU2241850C2 (en) * | 2002-12-31 | 2004-12-10 | Мошинский Ефим Яковлевич | Fuel system |
EP1712775A4 (en) * | 2004-02-06 | 2010-01-20 | Bosch Corp | Fuel supply device |
DE102005033638A1 (en) * | 2005-07-19 | 2007-01-25 | Robert Bosch Gmbh | Fuel conveyor, in particular for an internal combustion engine |
DE102006027486A1 (en) | 2006-06-14 | 2007-12-20 | Robert Bosch Gmbh | Fuel injection device for an internal combustion engine |
DE102007052665A1 (en) * | 2007-11-05 | 2009-05-07 | Robert Bosch Gmbh | Fuel overflow valve for a fuel injector and fuel injector with fuel spill valve |
US20090211556A1 (en) * | 2008-02-25 | 2009-08-27 | Perkins Engines Company Limited | System for maintaining a pump inlet pressure |
DE102008042089A1 (en) | 2008-09-15 | 2010-03-18 | Robert Bosch Gmbh | Overflow valve for inlet pipe of dosing unit of high-pressure pump of fuel injecting device of internal combustion engine, has spring area that is connected with inlet via pressure balance pipeline, where throttle is provided in pipeline |
DE102009001563A1 (en) * | 2009-03-16 | 2010-09-23 | Robert Bosch Gmbh | high pressure pump |
JP5464649B2 (en) * | 2009-09-07 | 2014-04-09 | ボッシュ株式会社 | Control device for internal combustion engine |
EP2492480B1 (en) | 2009-10-23 | 2015-11-25 | Bosch Corporation | Control device for internal combustion engine |
-
2010
- 2010-11-05 DE DE102010043439A patent/DE102010043439A1/en not_active Withdrawn
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2011
- 2011-09-21 EP EP11757896.3A patent/EP2635791B1/en active Active
- 2011-09-21 KR KR1020137011510A patent/KR101900965B1/en active IP Right Grant
- 2011-09-21 RU RU2013125689/06A patent/RU2573068C2/en active
- 2011-09-21 JP JP2013537051A patent/JP5727617B2/en not_active Expired - Fee Related
- 2011-09-21 CN CN201180052758.4A patent/CN103201495B/en active Active
- 2011-09-21 WO PCT/EP2011/066401 patent/WO2012059267A1/en active Application Filing
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DE102010043439A1 (en) | 2012-05-10 |
JP2013545015A (en) | 2013-12-19 |
KR101900965B1 (en) | 2018-09-20 |
RU2013125689A (en) | 2014-12-10 |
CN103201495B (en) | 2016-08-17 |
KR20130126906A (en) | 2013-11-21 |
WO2012059267A1 (en) | 2012-05-10 |
CN103201495A (en) | 2013-07-10 |
RU2573068C2 (en) | 2016-01-20 |
EP2635791B1 (en) | 2015-01-07 |
EP2635791A1 (en) | 2013-09-11 |
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