EP2357354B1 - Hydraulic system and fuel injection system for a combustion engine - Google Patents
Hydraulic system and fuel injection system for a combustion engine Download PDFInfo
- Publication number
- EP2357354B1 EP2357354B1 EP11151136.6A EP11151136A EP2357354B1 EP 2357354 B1 EP2357354 B1 EP 2357354B1 EP 11151136 A EP11151136 A EP 11151136A EP 2357354 B1 EP2357354 B1 EP 2357354B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- accumulator
- pressure accumulator
- fuel injection
- fuel
- 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.)
- Not-in-force
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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
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
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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
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
- F02M55/025—Common rails
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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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
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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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
- F02M63/023—Means for varying pressure in common rails
- F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
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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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
- F02M63/023—Means for varying pressure in common rails
- F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
- F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail
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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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
- F02M63/023—Means for varying pressure in common rails
- F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
- F02M63/025—Means for varying pressure in common rails by bleeding fuel pressure from the common rail
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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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
- F02M63/023—Means for varying pressure in common rails
- F02M63/026—Means for reducing the pressure in common rails at power off
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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
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
- F02M63/0275—Arrangement of common rails
- F02M63/0285—Arrangement of common rails having more than one common rail
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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
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
- F02M69/462—Arrangement of fuel conduits, e.g. with valves for maintaining pressure in the pipes after the engine being shut-down
- F02M69/465—Arrangement of fuel conduits, e.g. with valves for maintaining pressure in the pipes after the engine being shut-down of fuel rails
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/09—Fuel-injection apparatus having means for reducing noise
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
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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
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/022—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type having an accumulator storing pressurised fuel during pumping stroke of the piston for subsequent delivery to the injector
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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
- F02M59/16—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps characterised by having multi-stage compression of fuel
Definitions
- the invention relates to a fuel injection system for an internal combustion engine with a hydraulic system according to the preamble of claim 1.
- Such a hydraulic system is from the DE 10 2007 010 495 A1 the applicant known.
- a high-pressure pump delivers fuel into a fuel reservoir, which in turn is coupled to a pressure booster, the fuel with further pressure increase in a second high-pressure accumulator, in particular as so-called rail is formed promotes.
- the pressure boosting device is equipped with a pressure piston acting for two compression chambers, so that a continuous delivery of the fuel can be done in the second high-pressure accumulator.
- Such fuel injection systems having a pressure boosting device are used in particular at higher system pressures (in this case, system pressures higher than 3000 bar) are used for efficiency and strength reasons.
- the known systems of this kind are usually designed in such a way that the pressure is reduced via the injectors of the fuel injection system, which are subject to leakage. In other words, this means that the pressure reduction rate depends on the leakage quantities of the injectors.
- There are operating conditions of an internal combustion engine or of a fuel injection system in which relatively high pressure reduction rates are desired are. On the one hand, for safety reasons, especially after switching off the engine and on the other hand for reasons of comfort, since in a change from large to small load, the relatively high pressure should be adjusted lower partly for reasons of noise. If this does not happen, the part load has a relatively high noise level.
- the injectors are designed for the lowest possible leakage, so that it becomes increasingly difficult to achieve a sufficiently high pressure reduction rate under the operating conditions mentioned.
- a hydraulic system is known with a high-pressure accumulator, as well as from DE 10 2007 062 176 A1 , From the DE 10 2008 011 677 A1
- a test device for a fuel injection system is known, which also includes a high-pressure accumulator.
- the invention has the object, a fuel injection system for an internal combustion engine with a hydraulic system according to the invention according to the preamble of claim 1 such that an increased pressure reduction speed can be achieved.
- This object is achieved in a hydraulic system with the features of claim 1.
- the invention is based on the idea, by a pressure reduction device which is coupled to the second high-pressure accumulator, specifically and quickly to allow the desired pressure reduction.
- the pressure reduction thus happens mainly not via the or with the second high-pressure accumulator coupled consumers, but via the (separate) pressure reducing device. Therefore, the at least one consumer can be optimized or minimized with regard to its leakage.
- the pressure medium is fuel and the at least one consumer is an injector for injecting fuel into a combustion chamber of the internal combustion engine.
- the pressure reduction device is arranged between the two high-pressure accumulators and leads from the second high-pressure accumulator flowing back into the first high-pressure accumulator.
- the pressure reducing device is designed as a switchable between two positions overflow.
- the pressure reduction device opens the outflow of the fuel from the second high pressure accumulator when a certain pressure ratio between the two high pressure accumulators is exceeded.
- the first high pressure accumulator is coupled to a pressure control valve, which is connected to a low pressure region is.
- the pressure in the first high pressure accumulator is determined by the pressure regulating valve, so that the pressure in the first high pressure accumulator also can not exceed a certain value.
- the pressure regulating valve is formed by a control device of the motor vehicle electrically controlled.
- a pressure reduction can therefore be achieved in a particularly simple manner that the control unit controls the pressure control valve, which then lowers the pressure in the first high pressure accumulator, whereupon the ratio between the pressure in the second high pressure accumulator and the pressure in the first high pressure accumulator increases, which in turn has the consequence in that the pressure in the second high-pressure accumulator is reduced in the desired manner via the pressure reduction device.
- two, in particular identically designed pressure amplification devices are provided, which are independently controllable.
- Such a design has the advantage that it operates particularly reliably or, in the event of a malfunction in a pressure-increasing device, the pressure can be maintained at least at a certain level by means of the second pressure-increasing device.
- a hydraulic system 1 designed as a fuel injection system 10 is shown.
- the fuel injection system 10 is used in particular in a self-igniting internal combustion engine 2, in particular a diesel engine, which has a plurality, for example six, of consumers designed as injectors 3 for injecting fuel into the combustion chambers of the internal combustion engine 2.
- Such, known per se fuel injection system 10 has (among other components, not shown for clarity, such as a fuel filter, a water separator, etc., which are usually present in practice, but are not required for understanding the invention) a fuel tank 11th on, is conveyed from the fuel by means of a high-pressure feed pump 12 in a first high-pressure accumulator 13.
- a high-pressure feed pump 12 By means of such, known from practice high-pressure feed pump 12, for example, a pressure of 1500 bar is generated in the first high-pressure accumulator 13.
- the first high pressure accumulator 13 is equipped with an electrically controllable pressure control valve 14, which allows a backflow of fuel from the first high pressure accumulator 13 into the fuel tank 11 when a certain pressure in the first high pressure accumulator 13 is exceeded.
- the pressure control valve 14 is connected to a control device, not shown, of the motor vehicle and electrically controlled by this, the e.g. at certain operating conditions, e.g. the shutdown of the internal combustion engine 2 or at a partial load operation of the internal combustion engine 2, the pressure in the first high pressure accumulator 13 down regulates.
- the first high-pressure accumulator 13 is coupled to two pressure-increasing devices 17, 18 which are of identical design but can be operated independently of one another and are not shown in detail in the drawing.
- the two pressure increasing devices 17, 18 are each coupled to a 3/2-control valve 19, 20.
- the two outputs of the pressure increasing devices 17, 18 are in turn connected to a second high-pressure accumulator 22 for the fuel.
- the second high-pressure accumulator 22 is designed as a so-called rail and has a pressure sensor 23. From the second high-pressure accumulator 22 in each case a line 24 goes to each of the injectors 3.
- each injector 3 has a return line 16, which connects the injector 3 to the low pressure region 5 of the fuel injection system 1 and the unneeded fuel is returned to the fuel tank 11.
- the two high-pressure accumulators 13 and 22 are coupled to one another with a pressure reduction device 25.
- the pressure reduction device 25 is designed in particular as a mechanically operating, in particular spring-loaded differential pressure overflow valve 26.
- the differential pressure overflow valve 26 has a connection line 27, via which, for example, leakage losses of the differential pressure overflow valve 26 can be diverted into a low-pressure region 5 of the fuel injection system 10.
- the low-pressure region 5 is in turn connected to the fuel tank 11.
- a connection 28 is provided in the differential pressure overflow valve 26, which allows the discharge of the differential pressure overflow valve 26, a drainage of fuel from the second high pressure accumulator 22 into the first high pressure accumulator 13.
- the first pressure boosting device 17 has check valves 30, 31 which prevent a backflow of fuel from the second high-pressure accumulator 22 into the first pressure increasing device 17 or from the first pressure increasing device 17 into the first high-pressure accumulator 13.
- the second pressure increasing device 18 check valves 33, 34, which prevents a backflow of fuel from the second high pressure accumulator 22 in the second pressure increasing means 18 and of the second pressure increasing means 18 in the first high pressure accumulator 13.
- the control valve 20 In the in the Fig. 1 illustrated position of the two 3/2-control valves 19, 20, the control valve 20 is shown in the actuated position, in which the associated second pressure increasing means 18 is thus in the delivery phase of their cycle.
- the pressure increasing device 18 in this case conveys a fuel quantity as a function of its geometric transmission ratio from the first high-pressure accumulator 13 into the second high-pressure accumulator 22.
- the control valve 19, however, is shown in the unactuated position, in which the associated pressure booster 17 is in the filling phase of its cycle. Thanks to the spring force, it fills the high-pressure chamber of the pressure-increasing device 17 with fuel via the non-return valve 30 and returns to its initial state after complete filling, in which all volumes are at system pressure level.
- the two pressure boosting devices 17, 18 are not actuated, wherein the two check valves 31, 34 are in their closed position. Since no or only a very small leakage occurs at the injectors 3, initially only a slight pressure reduction occurs in the second high-pressure accumulator 22.
- the differential pressure relief valve 26 is closed due to its geometric pressure area ratio and the spring action (1st position). If the pressure in the first high-pressure accumulator 13 is now reduced by means of the pressure regulating valve 14 as a result of control via the control unit, the closing force at the differential pressure overflow valve 26 is also reduced and it can open (2nd position).
- the pressure in the second high pressure accumulator 22 is reduced, since fuel from the second high pressure accumulator 22 via the connection 28 in the first high pressure accumulator 13 can flow.
- the pressure in the second high-pressure accumulator 22 is lowered relatively quickly.
- the pressure control valve 14 To rebuild the pressure in the second high pressure accumulator 22, the pressure control valve 14 must be closed again, wherein the pressure in the first high pressure accumulator 13 due to the promotion by means of the high pressure feed pump 12 increases again. In this case, the pressure increases until the force acting on the Differenzdrucküberströmventil 26 compressive force closes this and thus the connection between the two high-pressure accumulators 13, 22.
- the gear ratios of the activated pressure increasing means 17, 18 determine the pressure ratio between the two high pressure accumulators 13, 22 and the differential pressure spill valve 26 by the pressure area ratio of the pressure ratio between the high pressure accumulators 13,22 in the pressure reduction.
- the pressure area ratio of the differential pressure overflow valve 26 must be greater than the transmission ratios of the activated pressure increasing devices 17, 18, otherwise the differential pressure overflow valve 26 would also open during the delivery phase of the pressure increasing devices 17, 18, which adversely affects the efficiency.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung betrifft ein Kraftstoffeinspritzsystem für eine Brennkraftmaschine mit einem Hydrauliksystem nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injection system for an internal combustion engine with a hydraulic system according to the preamble of claim 1.
Ein derartiges Hydrauliksystem ist aus der
Derartige, eine Druckverstärkungseinrichtung aufweisende Kraftstoffeinspritzsysteme werden insbesondere bei höheren Systemdrücken (gemeint sind hier Systemdrücke höher als 3000 bar) aus Effizienz- und Festigkeitsgründen eingesetzt. Die bekannten derartigen Systeme sind bezüglich des Druckabbaus meist so ausgelegt, dass der Druckabbau über die mit Leckage behafteten Injektoren des Kraftstoffeinspritzsystems erfolgt. Mit anderen Worten gesagt bedeutet dies, dass die Druckabbaugeschwindigkeit von den Leckagemengen der Injektoren abhängen. Es gibt Betriebszustände einer Brennkraftmaschine bzw. eines Kraftstoffeinspritzsystems, bei denen relativ hohe Druckabbaugeschwindigkeiten erwünscht sind. Zum einen aus Sicherheitsgründen, insbesondere nach dem Ausschalten des Motors und zum anderen aus Komfortgründen, da bei einem Wechsel von großer zu kleiner Last der relativ hohe Druck teilweise aus Geräuschgründen niedriger eingeregelt werden sollte. Passiert dies nicht, ist in der Teillast ein relativ hohes Geräuschniveau zu verzeichnen. Auf der anderen Seite sind die Injektoren aus Systemeffizienzgründen auf eine möglichst geringe Leckage ausgebildet, sodass es immer schwieriger wird, bei den genannten Betriebszuständen eine genügend hohe Druckabbaugeschwindigkeit zu erreichen.Such fuel injection systems having a pressure boosting device are used in particular at higher system pressures (in this case, system pressures higher than 3000 bar) are used for efficiency and strength reasons. With regard to the pressure reduction, the known systems of this kind are usually designed in such a way that the pressure is reduced via the injectors of the fuel injection system, which are subject to leakage. In other words, this means that the pressure reduction rate depends on the leakage quantities of the injectors. There are operating conditions of an internal combustion engine or of a fuel injection system in which relatively high pressure reduction rates are desired are. On the one hand, for safety reasons, especially after switching off the engine and on the other hand for reasons of comfort, since in a change from large to small load, the relatively high pressure should be adjusted lower partly for reasons of noise. If this does not happen, the part load has a relatively high noise level. On the other hand, for system efficiency reasons, the injectors are designed for the lowest possible leakage, so that it becomes increasingly difficult to achieve a sufficiently high pressure reduction rate under the operating conditions mentioned.
Aus der
Ausgehend von dem dargestellten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, ein Kraftstoffeinspritzsystem für eine Brennkraftmaschine mit einem erfindungsgemäßen Hydrauliksystem nach dem Oberbegriff des Anspruchs 1 derart weiterzubilden, dass eine erhöhte Druckabbaugeschwindigkeit erreicht werden kann. Diese Aufgabe wird bei einem Hydrauliksystem mit den Merkmalen des Anspruchs 1 gelöst. Der Erfindung liegt dabei die Idee zugrunde, durch eine Druckreduzierungseinrichtung, die mit dem zweiten Hochdruckspeicher gekoppelt ist, gezielt und schnell den gewünschten Druckabbau zu ermöglichen. Der Druckabbau geschieht somit hauptsächlich nicht über den bzw. die mit dem zweiten Hochdruckspeicher gekoppelten Verbraucher, sondern über die (separate) Druckreduzierungseinrichtung. Daher kann der wenigstens eine Verbraucher hinsichtlich seiner Leckage optimiert bzw. minimiert werden. Das Druckmittel ist Kraftstoff und der wenigstens eine Verbraucher ein Injektor zum Einspritzen von Kraftstoff in einen Brennraum der Brennkraftmaschine. Als Brennkraftmaschine sind hierbei insbesondere selbstzündende Brennkraftmaschinen (Dieselmotoren) in Nutzfahrzeugen oder Personenkraftfahrzeugen vorgesehen. Außerdem ist die Druckreduzierungseinrichtung zwischen den beiden Hochdruckspeichern angeordnet und führt vom zweiten Hochdruckspeicher rückströmenden Kraftstoff in den ersten Hochdruckspeicher ab. Eine derartige Anordnung hat den Vorteil, dass der Wirkungsgrad des Gesamtsystems relativ hoch ist, da der rückgeführte Kraftstoff bei einer erneuten Förderung lediglich von dem Druckniveau des ersten Hochdruckspeichers mittels der Druckverstärkungseinrichtung auf das Druckniveau des zweiten Hochdruckspeichers gebracht werden muss.Based on the illustrated prior art, the invention has the object, a fuel injection system for an internal combustion engine with a hydraulic system according to the invention according to the preamble of claim 1 such that an increased pressure reduction speed can be achieved. This object is achieved in a hydraulic system with the features of claim 1. The invention is based on the idea, by a pressure reduction device which is coupled to the second high-pressure accumulator, specifically and quickly to allow the desired pressure reduction. The pressure reduction thus happens mainly not via the or with the second high-pressure accumulator coupled consumers, but via the (separate) pressure reducing device. Therefore, the at least one consumer can be optimized or minimized with regard to its leakage. The pressure medium is fuel and the at least one consumer is an injector for injecting fuel into a combustion chamber of the internal combustion engine. As an internal combustion engine in particular self-igniting internal combustion engines (diesel engines) are provided in commercial vehicles or passenger vehicles. In addition, the pressure reduction device is arranged between the two high-pressure accumulators and leads from the second high-pressure accumulator flowing back into the first high-pressure accumulator. Such an arrangement has the advantage the efficiency of the overall system is relatively high, since the recirculated fuel only has to be brought to the pressure level of the second high-pressure accumulator by the pressure boosting device once again from the pressure level of the first high-pressure accumulator.
Vorteilhafte Weiterbildungen des erfindungsgemäßen Kraftstoffeinspritzsystems für eine Brennkraftmaschine sind in den weiteren Ansprüchen angegeben. In den Rahmen der Erfindung fallen sämtliche Kombinationen aus zumindest zwei von in den Ansprüchen, der Beschreibung und/oder den Figuren offenbarten Merkmalen.Advantageous developments of the fuel injection system according to the invention for an internal combustion engine are specified in the further claims. All combinations of at least two of the features disclosed in the claims, the description and / or the figures fall within the scope of the invention.
Um einen relativ einfachen Aufbau der Druckreduzierungseinrichtung zu ermöglichen, die darüber hinaus einen besonders sicheren Betrieb gewährleistet, ist es in einer konstruktiven Ausgestaltung der Erfindung vorgesehen, dass die Druckreduzierungseinrichtung als zwischen zwei Stellungen schaltbares Überströmventil ausgebildet ist.In order to allow a relatively simple construction of the pressure reducing device, which also ensures a particularly safe operation, it is provided in a constructive embodiment of the invention that the pressure reducing device is designed as a switchable between two positions overflow.
In einer weiteren Ausgestaltung der Erfindung wird vorgeschlagen, dass die Druckreduzierungseinrichtung beim Überschreiten eines bestimmten Druckverhältnisses zwischen den beiden Hochdruckspeichern den Abfluss des Kraftstoffes aus dem zweiten Hochdruckspeicher öffnet. Eine derartige Ausbildung hat den Vorteil, dass eine Überlastung bzw. ein zu hoher Druck im zweiten Hochdruckspeicher vermieden werden kann.In a further embodiment of the invention, it is proposed that the pressure reduction device opens the outflow of the fuel from the second high pressure accumulator when a certain pressure ratio between the two high pressure accumulators is exceeded. Such a design has the advantage that an overload or too high pressure in the second high-pressure accumulator can be avoided.
Insbesondere ist es dabei vorgesehen, dass der erste Hochdruckspeicher mit einem Druckregelventil gekoppelt ist, das mit einem Niederdruckbereich verbunden ist. Somit wird der Druck im ersten Hochdruckspeicher durch das Druckregelventil bestimmt, sodass der Druck im ersten Hochdruckspeicher ebenfalls einen bestimmten Wert nicht überschreiten kann.In particular, it is provided that the first high pressure accumulator is coupled to a pressure control valve, which is connected to a low pressure region is. Thus, the pressure in the first high pressure accumulator is determined by the pressure regulating valve, so that the pressure in the first high pressure accumulator also can not exceed a certain value.
Besonders bevorzugt ist es hierbei, dass das Druckregelventil von einer Steuereinrichtung des Kraftfahrzeuges elektrisch ansteuerbar ausgebildet ist. Ein Druckabbau lässt sich daher auf besonders einfache Weise erzielen, dass das Steuergerät das Druckregelventil ansteuert, welches daraufhin den Druck im ersten Hochdruckspeicher absenkt, worauf sich das Verhältnis zwischen dem Druck im zweiten Hochdruckspeicher und dem Druck im ersten Hochdruckspeicher vergrößert, was wiederum zur Folge hat, dass über die Druckreduzierungseinrichtung der Druck im zweiten Hochdruckspeicher in gewünschter Weise reduziert wird.It is particularly preferred in this case that the pressure regulating valve is formed by a control device of the motor vehicle electrically controlled. A pressure reduction can therefore be achieved in a particularly simple manner that the control unit controls the pressure control valve, which then lowers the pressure in the first high pressure accumulator, whereupon the ratio between the pressure in the second high pressure accumulator and the pressure in the first high pressure accumulator increases, which in turn has the consequence in that the pressure in the second high-pressure accumulator is reduced in the desired manner via the pressure reduction device.
In einer weiteren Ausgestaltung der Erfindung ist es darüber hinaus vorgesehen, dass zwei insbesondere identisch ausgebildete Druckverstärkungseinrichtungen vorgesehen sind, die voneinander unabhängig ansteuerbar sind. Eine derartige Ausbildung hat den Vorteil, dass sie besonders zuverlässig arbeitet bzw. bei einer Funktionsstörung an einer Druckerhöhungseinrichtung der Druck mittels der zweiten Druckerhöhungseinrichtung zumindest auf einem bestimmten Niveau gehalten werden kann.In a further embodiment of the invention, it is also provided that two, in particular identically designed pressure amplification devices are provided, which are independently controllable. Such a design has the advantage that it operates particularly reliably or, in the event of a malfunction in a pressure-increasing device, the pressure can be maintained at least at a certain level by means of the second pressure-increasing device.
Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung. Diese zeigt in
- Fig. 1
- ein erfindungsgemäßes, als Kraftstoffeinspritzsystem ausgebildetes Hydrauliksystem unter Verwendung einer Druckreduzierungseinrichtung in einer schematischen Darstellung.
- Fig. 1
- an inventive, designed as a fuel injection system hydraulic system using a pressure reducing device in a schematic representation.
In der
Ein derartiges, an sich bekanntes Kraftstoffeinspritzsystem 10 weist (neben anderen, aus Übersichtlichkeitsgründen nicht dargestellten Bauteilen, wie einem Kraftstofffilter, einem Wasserabscheider usw., die in der Praxis in der Regel vorhanden sind, jedoch zum Verständnis der Erfindung nicht erforderlich sind) einen Kraftstoffvorratsbehälter 11 auf, aus dem Kraftstoff mittels einer Hochdruckförderpumpe 12 in einen ersten Hochdruckspeicher 13 gefördert wird. Mittels einer derartigen, aus der Praxis bekannten Hochdruckförderpumpe 12 wird in dem ersten Hochdruckspeicher 13 beispielsweise ein Druck von 1500bar erzeugt.Such, known per se fuel injection system 10 has (among other components, not shown for clarity, such as a fuel filter, a water separator, etc., which are usually present in practice, but are not required for understanding the invention) a fuel tank 11th on, is conveyed from the fuel by means of a high-
Der erste Hochdruckspeicher 13 ist mit einem elektrisch ansteuerbaren Druckregelventil 14 ausgestattet, das beim Überschreiten eines bestimmten Druckes im ersten Hochdruckspeicher 13 einen Rückfluss von Kraftstoff aus dem ersten Hochdruckspeicher 13 in den Kraftstoffvorratsbehälter 11 ermöglicht. Das Druckregelventil 14 ist dabei mit einem nicht dargestellten Steuergerät des Kraftfahrzeuges verbunden und von diesem elektrisch ansteuerbar, das z.B. bei bestimmten Betriebszuständen, z.B. dem Abstellen der Brennkraftmaschine 2 oder aber bei einem Teillastbetrieb der Brennkraftmaschine 2, den Druck im ersten Hochdruckspeicher 13 herabregelt.The first
Der erste Hochdruckspeicher 13 ist mit zwei, identisch ausgebildeten, jedoch unabhängig voneinander betreibbaren, und in der Zeichnung nicht im Detail dargestellten Druckerhöhungseinrichtungen 17, 18 gekoppelt. Die beiden Druckerhöhungseinrichtungen 17, 18 sind jeweils mit einem 3/2-Steuerventil 19, 20 gekoppelt. Die beiden Ausgänge der Druckerhöhungseinrichtungen 17, 18 sind wiederum mit einem zweiten Hochdruckspeicher 22 für den Kraftstoff verbunden. Der zweite Hochdruckspeicher 22 ist als sogenanntes Rail ausgebildet und weist einen Drucksensor 23 auf. Von dem zweiten Hochdruckspeicher 22 geht jeweils eine Leitung 24 zu jedem der Injektoren 3 ab. Ferner weist jeder Injektor 3 eine Rücklaufleitung 16 auf, die den Injektor 3 mit dem Niederdruckbereich 5 des Kraftstoffeinspritzsystems 1 verbindet und den nicht benötigten Kraftstoff in den Kraftstoffvorratsbehälter 11 zurückgeführt wird.The first high-
Erfindungsgemäß ist es vorgesehen, dass die beiden Hochdruckspeicher 13 und 22 mit einer Druckverminderungseinrichtung 25 miteinander gekoppelt sind. Hierbei ist die Druckverminderungseinrichtung 25 insbesondere als mechanisch arbeitendes, insbesondere federbelastetes Differenzdrucküberströmventil 26 ausgebildet. Das Differenzdrucküberströmventil 26 weist eine Verbindungsleitung 27 auf, über die beispielsweise Leckageverluste des Differenzdrucküberströmventils 26 in einen Niederdruckbereich 5 des Kraftstoffeinspritzsystems 10 abgeleitet werden können. Der Niederdruckbereich 5 ist wiederum mit dem Kraftstoffvorratsbehälter 11 verbunden. Weiterhin ist im Differenzdrucküberströmventil 26 eine Verbindung 28 vorgesehen, die beim Ansprechen des Differenzdrucküberströmventils 26 einen Abfluss von Kraftstoff von dem zweiten Hochdruckspeicher 22 in den ersten Hochdruckspeicher 13 ermöglicht.According to the invention, it is provided that the two high-
Die erste Druckverstärkungseinrichtung 17 weist Rückschlagventile 30, 31 auf, die ein Rückströmen von Kraftstoff von dem zweiten Hochdruckspeicher 22 in die erste Druckerhöhungseinrichtung 17 bzw. von der ersten Druckerhöhungseinrichtung 17 in den ersten Hochdruckspeicher 13 verhindert. Ebenso weist die zweite Druckerhöhungseinrichtung 18 Rückschlagventile 33, 34 auf, die ein Rückströmen von Kraftstoff vom zweiten Hochdruckspeicher 22 in die zweite Druckerhöhungseinrichtung 18 bzw. von der zweiten Druckerhöhungseinrichtung 18 in den ersten Hochdruckspeicher 13 verhindert.The first
In der in der
Das Steuerventil 19 ist hingegen in der unbetätigten Stellung dargestellt, in der die zugeordnete Druckerhöhungseinrichtung 17 in der Füllphase ihres Zyklusses ist. Sie befüllt dank der Federkraft den Hochdruckraum der Druckerhöhungseinrichtung 17 über das Rückschlagventil 30 mit Kraftstoff und nimmt nach vollständiger Befüllung wieder ihren Ausgangszustand an, in dem alle Volumina auf Systemdruckniveau liegen.The
Falls nun ein Druckabbau gewünscht ist, werden die beiden Druckverstärkungseinrichtungen 17, 18 nicht betätigt, wobei die beiden Rückschlagventile 31, 34 in ihrer geschlossenen Stellung sind. Da an den Injektoren 3 keine oder nur eine sehr geringe Leckage auftritt, tritt zunächst nur ein geringer Druckabbau im zweiten Hochdruckspeicher 22 ein. Das Differenzdrucküberströmventil 26 ist aufgrund seines geometrischen Druckflächenverhältnisses und der Federwirkung geschlossen (1. Stellung). Wird nun mittels des Druckregelventils 14 infolge einer Ansteuerung über das Steuergerät der Druck in dem ersten Hochdruckspeicher 13 reduziert, reduziert sich auch die Schließkraft am Differenzdrucküberströmventil 26, und es kann öffnen (2. Stellung). Nun wird auch der Druck im zweiten Hochdruckspeicher 22 abgebaut, da Kraftstoff von dem zweiten Hochdruckspeicher 22 über die Verbindung 28 in den ersten Hochdruckspeicher 13 strömen kann. Somit wird in gewünschter Weise der Druck in dem zweiten Hochdruckspeicher 22 relativ rasch abgesenkt.If now a pressure reduction is desired, the two
Zum Wiederaufbauen des Drucks in dem zweiten Hochdruckspeicher 22 muss das Druckregelventil 14 erneut geschlossen werden, wobei der Druck in dem ersten Hochdruckspeicher 13 infolge der Förderung mittels der Hochdruckförderpumpe 12 wieder ansteigt. Hierbei steigt der Druck so lange an, bis die auf das Differenzdrucküberströmventil 26 wirkende Druckkraft dieses verschließt und somit auch die Verbindung zwischen den beiden Hochdruckspeichern 13, 22. Hierbei stellt sich immer ein nahezu identisches Druckverhältnis zwischen den Drücken in den beiden Hochdruckspeichern 13, 22 ein, da nur das Druckflächenverhältnis am Differenzdrucküberströmventil 26 die Druckniveaus bestimmen. Somit bestimmen die Übersetzungsverhältnisse der aktivierten Druckerhöhungseinrichtungen 17, 18 das Druckverhältnis zwischen den beiden Hochdruckspeichern 13, 22 und das Differenzdrucküberströmventil 26 durch dessen Druckflächenverhältnis das Druckverhältnis zwischen den Hochdruckspeichern 13,22 im Druckabbau. Hierbei muss das Druckflächenverhältnis des Differenzdrucküberströmventils 26 größer sein als die Übersetzungsverhältnisse der aktivierten Druckerhöhungseinrichtungen 17, 18, da ansonsten auch während der Förderphase der Druckerhöhungseinrichtungen 17, 18 das Differenzdrucküberströmventil 26 öffnen würde, was den Wirkungsgrad ungünstig beeinflusst.To rebuild the pressure in the second
Claims (7)
- Fuel injection system (10; 10a) for an internal combustion engine (2), having a hydraulic system (1), having a pump device (12), which is connected to a first high-pressure accumulator (13) and which delivers pressure medium into the first high-pressure accumulator (13) with an increase in pressure, having at least one pressure-boosting device (17, 18), which is coupled to the first high-pressure accumulator (13) and which delivers the pressure medium situated in the first high-pressure accumulator (13) into a second high-pressure accumulator (22) with a further increase in pressure, wherein at least one consumer (3) is supplied with pressure medium from the second high-pressure accumulator (22), wherein, between the two high-pressure accumulators (13, 22), at least one valve device (31, 34) is coupled to the at least one pressure-boosting device (17, 18), which at least one valve device prevents an outflow of pressure medium from the second high-pressure accumulator (22) in the direction of the at least one pressure-boosting device (17, 18), wherein the second high-pressure accumulator (22) is coupled to a pressure-reducing device (25; 25a) by means of which pressure medium can flow out of the second high-pressure accumulator (22) such that the pressure in the second high-pressure accumulator (22) is reduced, wherein the pressure medium is fuel and the at least one consumer is an injector (3) for injecting fuel into a combustion chamber of the internal combustion engine (2),
characterized
in that the pressure-reducing device (25) is arranged between the two high-pressure accumulators (13, 22) and discharges fuel flowing back from the second high-pressure accumulator (22) into the first high-pressure accumulator (13) . - Fuel injection system according to Claim 1,
characterized
in that the pressure-reducing device (25; 25a) is formed as an overflow valve (26) which is switchable between two positions. - Fuel injection system according to either of Claims 1 and 2,
characterized
in that the pressure-reducing device (25; 25a) opens up the outflow of the fuel from the second high-pressure accumulator (22) in the event of a certain pressure ratio between the two high-pressure accumulators (13, 22) being exceeded. - Fuel injection system according to Claim 3,
characterized
in that the first high-pressure accumulator (13) is coupled to a pressure regulating valve (14) which, in an open position, effects a return flow of fuel into the low-pressure region (5). - Fuel injection system according to Claim 4,
characterized
in that the pressure regulating valve (14) is electrically actuatable by a control device of a motor vehicle. - Fuel injection system according to one of Claims 2 to 5,
characterized
in that the overflow valve (26) is designed as a mechanically operating, in particular springloaded valve. - Fuel injection system according to one of Claims 1 to 6,
characterized
in that two pressure-boosting devices (17, 18) are provided which are in particular of identical design and which are actuatable independently of one another.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE102010002033A DE102010002033A1 (en) | 2010-02-17 | 2010-02-17 | Hydraulic system and fuel injection system for an internal combustion engine |
Publications (3)
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EP2357354A2 EP2357354A2 (en) | 2011-08-17 |
EP2357354A3 EP2357354A3 (en) | 2015-12-23 |
EP2357354B1 true EP2357354B1 (en) | 2018-04-25 |
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EP11151136.6A Not-in-force EP2357354B1 (en) | 2010-02-17 | 2011-01-17 | Hydraulic system and fuel injection system for a combustion engine |
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DE (1) | DE102010002033A1 (en) |
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DE102016202916B4 (en) | 2016-02-25 | 2021-07-29 | Ford Global Technologies, Llc | Method set up for controlling a fuel supply system for an internal combustion engine |
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DE4401083A1 (en) * | 1994-01-15 | 1995-07-20 | Daimler Benz Ag | Fuel injection unit for IC engine |
KR100580699B1 (en) * | 2003-10-27 | 2006-05-15 | 현대자동차주식회사 | Common rail system |
US7392791B2 (en) * | 2006-05-31 | 2008-07-01 | Caterpillar Inc. | Multi-source fuel system for variable pressure injection |
DE102007010495A1 (en) | 2007-03-05 | 2008-09-11 | Robert Bosch Gmbh | Fuel injection system and pressure boosting device for a fuel injection system |
DE102007062176A1 (en) * | 2007-12-21 | 2009-06-25 | Robert Bosch Gmbh | Pressure control valve for regulating the pressure in a high pressure fuel accumulator |
DE102008011677A1 (en) * | 2008-02-28 | 2009-09-03 | Robert Bosch Gmbh | Testing unit for testing structure for fuel injection system of combustion engine, has test trigger equipment for measuring unit, which receives signals of injection trigger equipment |
-
2010
- 2010-02-17 DE DE102010002033A patent/DE102010002033A1/en not_active Withdrawn
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2011
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