CN101713359B - Fuel injection system having a high-pressure pump with a magnetically actuable suction valve - Google Patents
Fuel injection system having a high-pressure pump with a magnetically actuable suction valve Download PDFInfo
- Publication number
- CN101713359B CN101713359B CN200910205203.3A CN200910205203A CN101713359B CN 101713359 B CN101713359 B CN 101713359B CN 200910205203 A CN200910205203 A CN 200910205203A CN 101713359 B CN101713359 B CN 101713359B
- Authority
- CN
- China
- Prior art keywords
- pump
- suction valve
- pressure
- pressure service
- mode
- 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.)
- Active
Links
Images
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
- F02M59/366—Valves being actuated electrically
-
- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
-
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- 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
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
-
- 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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
The invention relates to a fuel injection system having a high-pressure pump with a magnetically actuable suction valve, in particular for an internal combustion engine, in particular a marine diesel engine, having: a fuel container (12); a high-pressure container (9) for feeding the combustion chamber of the internal combustion engine; and a pump assembly having at least two high-pressure pumps (1, 10, 11) for delivering fuel from a fuel tank to the high-pressure tank, each of which has a pump chamber which can be connected on the delivery side to the high-pressure tank (9) and on the intake side to the fuel tank (12), a piston (2) which can be moved in the pump chamber, and a magnetically actuable suction valve (5) for separating the pump chamber from the fuel tank, wherein the switching time of the suction valve is at most 1/10, in particular at most 1/20, of the maximum suction duration of the high-pressure pump.
Description
Technical field
The present invention relates to a kind of for internal-combustion engine, the fuel injection system of marine diesel engine (Schiffsdiesel) especially, this fuel injection system is with fuel container (Kraftstoffreservoir), for the high-pressure bottle (Hochdruckreservoir) of the feed (Beschickung) of the firing chamber of internal-combustion engine, and for the pump assembly from fuel container transfer the fuel to high-pressure bottle (this pump assembly is with at least two high-pressure service pumps); The invention still further relates to a kind of high-pressure bottle for this fuel injection system, and, relate to and a kind ofly by means of this fuel injection system, utilize fuel to carry out internal-combustion engine, the method for the feed of the firing chamber of marine diesel engine especially.
Background technique
Such fuel injection system---, in these fuel injection systems, by separated high-pressure service pump, fuel pressure be reduced to jet pressure and be ejected in each firing chamber by nozzle---in marine diesel engine, be used more and more.In so common rail (Common-Rail) system, it is also known by one or more high-pressure service pumps, carrying out operate high pressure container.
On the other hand, for instance from file EP 0 244 340 B1, file EP 0 481 964B2, file DE 100 52 629 A1 or file WO 00/61939, the suction valve of the high-pressure service pump of common rail fuel injection system (Saugventil) is designed to solenoid valve (Magnetventil), thereby can affects quantity delivered by the suitable opening and closing of suction valve.Yet only controllability of a suction valve of high-pressure service pump (Die blosse Ansteuerbarkeit eines Saugventils) cannot utilize the potential of the suction valve of actuating in the mode of magnetic to optimize the performance of fuel injection system fully.
Summary of the invention
Therefore, the object of the invention is to, improve common rail fuel injection system.
In order to realize this object, by the feature of claim 1 characteristic, improve according to the fuel injection system of the preamble of claim 1.
According to the present invention, fuel injection system for internal-combustion engine (especially marine diesel engine) comprises for storing the fuel container that is in lower pressure, is especially in the fuel under external pressure, and high-pressure bottle, for example, by means of nozzle, the fuel of utilization under elevated pressures, can carry out from this high-pressure bottle the feed of combustion motor firing chamber.Between fuel container and high-pressure bottle, be furnished with concurrently at least two high-pressure service pumps of carrying for the fuel from fuel container to high-pressure bottle, wherein, in preferred design proposal, between fuel container and high-pressure service pump, can be furnished with at least one transfer pump and/or at least one suction booster or booster pump.
According to the present invention, some in pump assembly or preferably all high-pressure service pump respectively have mode (magnetisch betaetigbares) suction valve (or back pressure regulator (Saugdrossel)) of actuating that can magnetic, utilize it can be by the pump chamber of high-pressure service pump---in this pump chamber, movably piston is exerted pressure also to fuel, preferably, by (vorgespanntes) safety check of bias voltage, fuel is expelled to high-pressure bottle---fuel container isolation (abgesperrt) relatively.
Compare with the known so far pump assembly with passive (passiven) suction valve, by the high-pressure service pump that uses mode that a plurality of that connect concurrently, its suction valves can magnetic to actuate, can improve the characteristic of fuel injection system.
For example, pump assembly can magnetic the mode suction valve of actuating individually (individuell) controlled, to reduce the pressure surge (Druckschwankungen) in high-pressure bottle.
At this, two or more high-pressure service pumps of pump assembly can magnetic the mode suction valve of actuating for instance can stagger in time (zeitlich versetzt) open and/or close.Thus, to the inflow of each pump chamber and/or from the discharge of each pump chamber no longer synchronously but carry out in time, with staggering thus can adjust in time the pressure peak of high-pressure service pump (its piston synchronous ground motion) and can reduce thus to suck or delivery line in total pressure peak value.Equally likely, opening and closing suction valve in multiple times during suction stroke, to reduce thus pressure surge.
Additionally or alternatively, the inefficacy of a high-pressure service pump of pump assembly can by extend pump assembly other high-pressure service pump can magnetic the mode suction valve of actuating opening time (Oeffnungszeit) and compensated.Therefore, a pump lost efficacy and can not cause immediately the inefficacy of whole fuel injection system again or cause urgent running state, because can improve the delivered volume of remaining high-pressure service pump and compensate at least in part thus this inefficacy in total value by extending the opening time.
The inefficacy (so-called interruption (Blackout)) that is arranged in transfer pump between fuel container and high-pressure service pump or booster pump equally can by extend in the high-pressure service pump of pump assembly at least one can magnetic opening time of the mode suction valve of actuating deal with.Because the suction valve that mode that can magnetic by this is actuated can be realized, even if there is no or only have very little inlet pressure (Vorlaufdruck) in aspiration, high-pressure service pump also can be transported to fuel in high-pressure bottle and maintain thus by this aspiration the fuel of internal-combustion engine and supply with.
The opening time of the suction valve that the mode that additionally or alternatively, this of the high-pressure service pump of pump assembly can magnetic is actuated can change during work cycle (Arbeitszyklus).The quantity delivered that can especially promptly change thus each high-pressure service pump also (for example) shows as conveying Intensity Abrupt, to as quickly as possible sudden load change is reacted.
For this reason, according to an aspect of the present invention, high-pressure service pump can magnetic switching time (Schaltzeit) of the mode suction valve of actuating,, between the enable possition of suction valve and closed position, change the time used, be up to 10% of the high-pressure service pump maximum aspiration endurance (that is, maximum, given by piston movement, fuel flow into the time the pump chamber of high-pressure service pump from fuel container therein), preferably the highest 5% and particularly preferably the highest by 1/30.In a kind of form of implementation of the present invention, can be for example 4 milliseconds (ms) at the most this switching time of suction valve, preferably 1ms at the most.
The solenoid valve of suction valve for closing under (the normalerweise geoeffnetes) that often open, excitation at magnet in previously described file EP 0 244 340 B1 and file EP 0 481 964 B2, and in high-pressure service pump according to the present invention preferably, the suction valve that the mode that this can magnetic is actuated in flexible mode (elastisch), hydraulically and/or be pneumatically biased in closed position and can be by the attraction (passing through electromagnet) of armature (Anker) on one's own initiative (aktiv) open.Thus, under the situation of this electromagnet power supply trouble, can guarantee the isolation of the relative fuel container of pump chamber.In addition, electromagnet only must be powered at (for working stroke) shorter suction duration.At this, electromagnet should design in this wise,, the power being applied on solenoid valve armature by this electromagnet can be opened suction valve (even at the joint (Anschluss that aspirates side, sometimes or claim hydraulic fluid port) in there is no inlet pressure), so that, even if also can realize interruption-startup (Blackout-Start) under little inlet pressure.
For designing and promote suction valve by the active force limiting, the armature chamber of the suction valve that the mode that this can magnetic is actuated preferably relative jam joint (Sauganschluss) is liquid-tight (fluessigdicht) or be connected with this suction joint (kommuniziert).
Accompanying drawing explanation
Other advantage and feature can draw in dependent claims and embodiment.At this, unique
Fig. 1 has partly shown the fuel injection system according to a kind of form of implementation of the present invention in graphic mode.
List of reference characters
1 high-pressure service pump
2 pistons
3 suction joints
4 carry joint (Foerderanschluss)
5 solenoid valves
5.1 valve gap
5.2 valve armature
6 safety check
7 electromagnet
8 biasing springs
9 high-pressure bottles
10 high-pressure service pumps
11 high-pressure service pumps
12 fuel containers
Fig. 1 shows the fuel injection system according to an embodiment of the present that is marine diesel engine (not shown) common rail system form used.It comprises fuel container or fuel tank 12, and diesel oil leaves in wherein under external pressure, and comprises high-pressure bottle 9, and fuel is under high pressure stored in this high-pressure bottle, to be injected into (not shown) in the firing chamber of marine diesel engine by nozzle.
For fuel is transported to high-pressure bottle 9 and is taken on desired pressure from fuel container 12, between fuel container and high-pressure bottle, be furnished with concurrently three high-pressure service pumps 1,10,11.Roughly the same on these three high-pressure pump structures, therefore below by the high-pressure service pump 1 being shown specifically in explanatory drawing 1 only.
This high-pressure service pump is connected with fuel container 12 by suction joint 3 in suction side.Although not shown, between fuel container 12 and high-pressure service pump 1, also can be furnished with transfer pump and/or booster pump, to set up certain inlet pressure in suction joint 3.
At conveyor side, high-pressure service pump 1 is by carrying joint 4 for example, to be so connected with high-pressure bottle 9 by the safety check 6 of the bias voltage that spring loaded with (), that is,, once carry the pressure in joint 4 to meet or exceed the pressure in high-pressure bottle 9, high-pressure service pump is pushed into fuel in high-pressure bottle 9.
For example periodically becoming by the reciprocal piston 2 on corresponding cam profile (not shown) of suction joint 3 and high-pressure service pump 1, between pump chamber large and that diminish, be furnished with the solenoid valve 5 as suction valve that can ACTIVE CONTROL.It comprises valve gap 5.1, and it makes relative fuel container 12 cut-offs of pump chamber in the closed position shown in Fig. 1.In this closed position, valve gap is by 8 bias voltages of the spring of the spring force with such, and this spring force is greater than or at least equals to aspirate the peak suction sum in maximum precompressed (Druckvorlauf) in joint 3 and pump chamber.
At run duration, the suction valve 5 of synchronizeing in time with the stroke of piston 2, actuate in the mode of magnetic is opened on suction stage (in this suction stage, piston 2 makes pump chamber become large) one or many ground.Length by (each) open stage can be controlled intake.In addition, the time sequencing by enable possition and closed position can make pressure diagram (Druckverlauf) become stable and can reduce pressure surge in particular.For instance, suction valve 5 can be opened first momently, thereby is created in the pressure wave (Druckwelle) in pump chamber direction.With get back to fuel container 12 this pressure wave reflection in time synchronously, suction valve (its during this period again closed) can be opened again, thereby causes another pressure wave in pump chamber direction.The pressure wave interference of this pressure wave and reflection in opposite directions and cause thus uniform pump chamber to be filled.Certainly, also only single ground (for example, haply during the suction stage of high-pressure service pump 1) unlatching of suction valve.
During compression stage (in this compression stage, piston 2 pump chamber is diminished and the situation of the high pressure in overcoming biasing force and high-pressure bottle 9 under by safety check 6, the fuel under high pressure is transported in high-pressure bottle 9) suction valve 5 closes.In order to reduce quantity delivered under constant stroke of piston, additional or alternative as to the locking of suction stage, suction valve 5 also can be opened by one or many during compression stage, so that fuel is transmitted back in fuel container 12.
The variation of controlling by electromagnet during work cycle 7, in particular by the change of opening and/or the shut-in time puts, can very rapidly react to the loading condition changing and demonstrate corresponding quantity delivered sudden change.
The non-desired backflow of the fuel in suction joint 3 and the cavitation occurring at this place can for example, be reduced or be avoided by control accordingly ((sanftes) that do sth. in advance and/or mild of suction valve close) of electromagnet 7 equally.
If the transfer pump of arranging between fuel container 12 and suction joint 3 or booster pump (not shown) lost efficacy (so-called interruption), so that the inlet pressure of suction in joint 3 declines, the unlatching of active that still can be by the suction valve 5 of actuating in the mode of magnetic is filled pump chamber and thus fuel is under high pressure transported in high-pressure bottle 9.
Three essentially identical high-pressure service pumps 1,10 of structure and 11 piston can be synchronously or on the time by corresponding cam profile and driven with staggering.In particular, when these pistons synchronously suck in time and carry, independent the controlling by each suction valve can reduce pressure surge.Except reducing pressure surge by opening and closing repeatedly, can make the skew relative to each other in time of the unlatching of pump 1,10 and 11 and/or shut-in time point, thereby all pumps not to put at one time but suction or be back to the conveying of fuel container 12 from fuel container 12 one by one for this reason.
When a pump lost efficacy, can compensate at least in part conveyance loss by the controlling accordingly (especially by the opening time during prolongation suction stage) of suction valve of other pump.
Armature chamber is connected with suction joint 3 by compensation conduit.Thus, do not have the motion that pressure reacts on valve armature 5.2, thereby suction valve can design and promote with the mode of the power limiting.
Solenoid valve 5 with affiliated electromagnet 7 and spring 8 for example can be arranged in valve support, but also can be arranged in pumping cylinder, and by clamping and guide sleeve (not shown) and liquid-tight screw lid, is fixed in preferred form of implementation.
Claims (15)
1. for the fuel injection system of internal-combustion engine, its with
Fuel container (12);
High-pressure bottle (9) for the feed of the firing chamber of described internal-combustion engine; And
With at least two high-pressure service pumps (1,10,11) for fuel is transported to the pump assembly described high-pressure bottle from described fuel container;
It is characterized in that, the high-pressure service pump of described pump assembly has suction valve (5) isolation with respect to described fuel container for pump chamber that can actuate in the mode of magnetic, wherein, and suction valve during compression stage (5) opening and closing in multiple times.
2. fuel injection system according to claim 1, is characterized in that, described fuel injection system also comprises the independent control gear of controlling for the suction valve that can actuate in the mode of magnetic of pump assembly.
3. fuel injection system according to claim 1 and 2, is characterized in that, described internal-combustion engine is marine diesel engine.
4. one kind for according to the high-pressure service pump of fuel injection system in any one of the preceding claims wherein (1,10,11), its with
The pump chamber that can be connected with high-pressure bottle (9) at conveyor side and can be connected with fuel container (12) in suction side,
The piston (2) that can move in described pump chamber, and
Can actuate in the mode of magnetic, the suction valve (5) for described pump chamber with respect to the isolation of described fuel container,
It is characterized in that, be up to the switching time of described suction valve described high-pressure service pump the maximum aspiration endurance 1/10, wherein, suction valve during compression stage (5) opening and closing in multiple times.
5. high-pressure service pump according to claim 4, is characterized in that, is up to 4ms the switching time of described suction valve.
6. according to the high-pressure service pump described in any one in aforementioned claim 4 to 5, it is characterized in that, the described suction valve that can actuate in the mode of magnetic is elastically biased toward in closed position and can passes through electromagnet (7) and open on one's own initiative by the attraction of armature (5.2).
7. according to the high-pressure service pump described in any one in aforementioned claim 4 to 5, it is characterized in that, the armature chamber of the suction valve that the described mode that can take magnetic is actuated with respect to suction joint (3) as liquid-tight or be connected with this suction joint (3).
8. according to the high-pressure service pump described in any one in aforementioned claim 4 to 5, it is characterized in that, be up to the switching time of described suction valve described high-pressure service pump the maximum aspiration endurance 1/20.
9. according to the high-pressure service pump described in any one in claim 4 to 5, it is characterized in that, be up to 1ms the switching time of described suction valve.
10. one kind for by means of utilizing the firing chamber of fuel combustion motor to carry out the method for feed according to the fuel injection system described in aforementioned claims 1 to 3 any one, it is characterized in that, the suction valve (5) that can actuate in the mode of magnetic of pump assembly is controlled individually, to reduce the pressure surge in high-pressure bottle (9), wherein, suction valve (5) opening and closing in multiple times during compression stage.
11. methods according to claim 10, is characterized in that, the suction valve (5) that can actuate in the mode of magnetic of two high-pressure service pumps of described pump assembly staggers in time and opens and/or close.
12. according to the method described in any one in aforementioned claim 10 to 11, it is characterized in that, the opening time of the suction valve that can actuate in the mode of magnetic of the high-pressure service pump of described pump assembly changes during work cycle.
13. according to the method described in any one in aforementioned claim 10 to 11, it is characterized in that, when a high-pressure service pump of described pump assembly lost efficacy, extends opening time of the suction valve that can actuate in the mode of magnetic of at least one other the high-pressure service pump of described pump assembly.
14. according to the method described in any one in aforementioned claim 10 to 11, it is characterized in that, when being arranged in transfer pump between fuel container and high-pressure service pump or booster pump and losing efficacy, the suction valve that can actuate in the mode of magnetic of at least one high-pressure service pump of described pump assembly is opened in mode initiatively.
15. according to the method described in any one in aforementioned claim 10 to 11, it is characterized in that, described internal-combustion engine is marine diesel engine.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102008050060.7 | 2008-10-01 | ||
| DE102008050060A DE102008050060A1 (en) | 2008-10-01 | 2008-10-01 | Common-rail fuel injection system for combustion engine, particularly marine diesel engine, has fuel reservoir and high pressure reservoir for filling of combustion chambers of combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101713359A CN101713359A (en) | 2010-05-26 |
| CN101713359B true CN101713359B (en) | 2014-03-05 |
Family
ID=41136374
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200910205203.3A Active CN101713359B (en) | 2008-10-01 | 2009-09-30 | Fuel injection system having a high-pressure pump with a magnetically actuable suction valve |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JP5528754B2 (en) |
| KR (1) | KR101514464B1 (en) |
| CN (1) | CN101713359B (en) |
| DE (1) | DE102008050060A1 (en) |
| FI (1) | FI20095906A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010031390B4 (en) * | 2010-07-15 | 2018-08-09 | Man Diesel & Turbo Se | Suction valve of a fuel supply system of an internal combustion engine |
| CN102859149A (en) * | 2011-04-27 | 2013-01-02 | 丰田自动车株式会社 | Metering device for high-pressure pump |
| JP6473045B2 (en) * | 2015-05-20 | 2019-02-20 | ヤマハ発動機株式会社 | Multi-cylinder engine and outboard motor |
| CN112483269B (en) * | 2020-12-16 | 2024-04-16 | 中车资阳机车有限公司 | Diesel engine safety protection system |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5133645A (en) * | 1990-07-16 | 1992-07-28 | Diesel Technology Corporation | Common rail fuel injection system |
| EP0962650A2 (en) * | 1998-06-01 | 1999-12-08 | Toyota Jidosha Kabushiki Kaisha | Accumulator-type fuel injection apparatus and control method for the same |
| CN1789694A (en) * | 2004-12-17 | 2006-06-21 | 株式会社电装 | Solenoid valve, flow-metering valve, high-pressure fuel pump and fuel injection pump |
| CN1952381A (en) * | 2005-10-19 | 2007-04-25 | 株式会社日立制作所 | High-pressure fuel supply system using variable displacement fuel pump |
| CN101063434A (en) * | 2006-04-27 | 2007-10-31 | 株式会社电装 | Fuel pressure controller |
| EP1930582A2 (en) * | 2006-11-30 | 2008-06-11 | Mitsubishi Heavy Industries, Ltd. | Fuel injection apparatus for engines and method of operating the apparatus |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4757795A (en) | 1986-04-21 | 1988-07-19 | Stanadyne, Inc. | Method and apparatus for regulating fuel injection timing and quantity |
| US5058553A (en) | 1988-11-24 | 1991-10-22 | Nippondenso Co., Ltd. | Variable-discharge high pressure pump |
| JP3110021B2 (en) | 1999-04-12 | 2000-11-20 | 株式会社ボッシュオートモーティブシステム | Fuel supply pump |
| DE10052629A1 (en) | 2000-10-24 | 2002-05-08 | Bosch Gmbh Robert | High pressure fuel pump with variable delivery rate |
| JP4106663B2 (en) * | 2004-03-26 | 2008-06-25 | 株式会社デンソー | Fuel supply device for internal combustion engine |
| JP4672640B2 (en) * | 2006-11-30 | 2011-04-20 | 三菱重工業株式会社 | Engine fuel injection apparatus and operation method |
-
2008
- 2008-10-01 DE DE102008050060A patent/DE102008050060A1/en not_active Ceased
-
2009
- 2009-09-03 FI FI20095906A patent/FI20095906A/en not_active Application Discontinuation
- 2009-09-25 JP JP2009221175A patent/JP5528754B2/en active Active
- 2009-09-30 KR KR1020090092934A patent/KR101514464B1/en active IP Right Grant
- 2009-09-30 CN CN200910205203.3A patent/CN101713359B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5133645A (en) * | 1990-07-16 | 1992-07-28 | Diesel Technology Corporation | Common rail fuel injection system |
| EP0962650A2 (en) * | 1998-06-01 | 1999-12-08 | Toyota Jidosha Kabushiki Kaisha | Accumulator-type fuel injection apparatus and control method for the same |
| CN1789694A (en) * | 2004-12-17 | 2006-06-21 | 株式会社电装 | Solenoid valve, flow-metering valve, high-pressure fuel pump and fuel injection pump |
| CN1952381A (en) * | 2005-10-19 | 2007-04-25 | 株式会社日立制作所 | High-pressure fuel supply system using variable displacement fuel pump |
| CN101063434A (en) * | 2006-04-27 | 2007-10-31 | 株式会社电装 | Fuel pressure controller |
| EP1930582A2 (en) * | 2006-11-30 | 2008-06-11 | Mitsubishi Heavy Industries, Ltd. | Fuel injection apparatus for engines and method of operating the apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2010084761A (en) | 2010-04-15 |
| FI20095906A0 (en) | 2009-09-03 |
| CN101713359A (en) | 2010-05-26 |
| KR20100037559A (en) | 2010-04-09 |
| FI20095906A (en) | 2010-04-02 |
| JP5528754B2 (en) | 2014-06-25 |
| KR101514464B1 (en) | 2015-04-22 |
| DE102008050060A1 (en) | 2010-04-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101779033B (en) | Fuel pump | |
| KR100514275B1 (en) | High pressure pump | |
| CN100381691C (en) | Common rail type fuel injection system | |
| EP1707799B1 (en) | Fuel pump having plunger and fuel supply system using the same | |
| US7377266B2 (en) | Integrated fuel feed apparatus | |
| EP2558708A1 (en) | High-pressure pump | |
| US9657700B2 (en) | Inlet valve arrangement for a fuel pump | |
| US20110223040A1 (en) | High-pressure pump arrangement | |
| CN101713359B (en) | Fuel injection system having a high-pressure pump with a magnetically actuable suction valve | |
| EP1651863B1 (en) | Common rail fuel pump | |
| JP3028471B2 (en) | Fuel pressure operated engine compression brake system | |
| JP3574681B2 (en) | Fuel injection device for internal combustion engine | |
| US7950373B2 (en) | Check valve with separate spherical spring guide | |
| CN1160120A (en) | Hydraulic valve drive | |
| CN106414967B (en) | Method for operating a fuel supply system for an internal combustion engine | |
| US20050287021A1 (en) | Variable discharge fuel pump | |
| US6763809B2 (en) | Fuel injection apparatus for an internal combustion engine | |
| JP4404056B2 (en) | Fuel injection device for internal combustion engine | |
| EP1696117B1 (en) | Electromagnetic controlled fuel injector | |
| KR101540502B1 (en) | Hydraulic pump, in particular a fuel pump | |
| US20040099246A1 (en) | Fuel injector with multiple control valves | |
| WO2010082217A1 (en) | A fuel injection system for an internal combustion engine | |
| US10519940B2 (en) | Hydraulic drive system for a linearly actuated hydraulic piston pump | |
| US20190309713A1 (en) | Pump having pilot-actuated admission valve | |
| JP2011064246A (en) | Regulating valve and fuel injection device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CP01 | Change in the name or title of a patent holder | ||
| CP01 | Change in the name or title of a patent holder |
Address after: Augsburg Patentee after: MAN ENERGY SOLUTIONS SE Address before: Augsburg Patentee before: Man Diesel & Turbo SE |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190426 Address after: Augsburg Patentee after: MAN DIESEL & TURBO SE Address before: Augsburg Patentee before: MAN DIESEL SE |