EP1451465B1 - Pumpe-düse-einheit - Google Patents
Pumpe-düse-einheit Download PDFInfo
- Publication number
- EP1451465B1 EP1451465B1 EP02805256A EP02805256A EP1451465B1 EP 1451465 B1 EP1451465 B1 EP 1451465B1 EP 02805256 A EP02805256 A EP 02805256A EP 02805256 A EP02805256 A EP 02805256A EP 1451465 B1 EP1451465 B1 EP 1451465B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- pump
- valve
- nozzle unit
- unit according
- 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.)
- Expired - Lifetime
Links
- 239000000446 fuel Substances 0.000 claims description 75
- 238000002347 injection Methods 0.000 claims description 54
- 239000007924 injection Substances 0.000 claims description 54
- 238000002485 combustion reaction Methods 0.000 claims description 22
- 230000001419 dependent effect Effects 0.000 description 4
- 238000013461 design Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000014759 maintenance of location Effects 0.000 description 3
- 230000007423 decrease Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000007493 shaping process Methods 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000002123 temporal effect Effects 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Images
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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/08—Injectors peculiar thereto
-
- 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
-
- 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/06—Pumps peculiar thereto
-
- 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
-
- 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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
-
- 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
- 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
- F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
- F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
-
- 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
- F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
Definitions
- the invention relates to a pump-nozzle unit for feeding of fuel into a combustion chamber of an internal combustion engine, with a controllable and / or controllable fuel pump, a fuel injection nozzle, one between a Closed position and an open position movable back and forth Nozzle needle, a first pressure chamber, of the fuel pump with under a first pressure Fuel is refillable, a second pressure chamber, being in the second pressure chamber more than a second pressure Fuel exerts a closing force on the nozzle needle, and a third pressure space communicating with the first pressure space, wherein in the third pressure chamber under a third Pressurized fuel has an opening force on the nozzle needle exercises.
- Such unit injectors are particularly related used with pressure controlled injection systems.
- One essential feature of a pressure-controlled injection system is that the fuel injector opens as soon as influenced at least by currently prevailing pressures Opening force is exerted on the nozzle needle.
- pressure-controlled injection systems are used for fuel metering, fuel processing, shaping of the Injection course and a seal of the fuel supply against the combustion chamber of the internal combustion engine.
- Pressure-controlled injection systems can be the temporal Course of the flow during the injection in an advantageous Steer way. This can have a positive impact on the power, the fuel consumption and the pollutant emission be taken from the engine.
- the fuel pump and the fuel injector as integrated Component formed.
- the Fuel pump typically includes one in one Fuel pump cylinder reciprocating fuel pump piston, either directly via a pestle or indirectly via rocker arm of a camshaft of the internal combustion engine is driven.
- control valve in the form of a Provide solenoid valve.
- solenoid valves usually have a relatively long response time, which in particular is caused by the fact that the armature of a solenoid valve due to the mass inertia forces dependent on its mass can not be accelerated arbitrarily fast can.
- the structure of the magnetic field also requires for generating the tightening time.
- One with a solenoid valve equipped pump-nozzle unit is for example off EP 0 277 939 B1.
- the injection device comprises a housing with a nozzle needle between a closed position and an opening position is arranged to be movable. It is a first pressure chamber provided with fuel under a first pressure is fillable. There is also a second pressure chamber provided, wherein in the second pressure chamber under a second pressurized fuel has a closing force on the Nozzle needle exerts. Furthermore, a third pressure chamber is provided which communicates with the first pressure chamber, wherein in the third pressure chamber is under a third pressure Fuel exerts an opening force on the nozzle needle. Between the first pressure chamber and the second pressure chamber is a Pressure valve provided. The pressure valve is replaced by a Pressure difference actuated.
- the invention is based on the object, the generic Further develop pump-nozzle units such that in a compact Design a defined control of the injection process and the injection pressure is enabled.
- the inventive pump-nozzle unit is based on the generic State of the art in that between the first pressure chamber and the second pressure chamber a pressure limiting and -halteventil is provided.
- a pressure limiting and -halteventil is provided between the first pressure chamber and the second pressure chamber .
- the intended Pressure relief and retention valve it is possible in particular the prevailing in the second pressure chamber second pressure adjusted so that one can be used for the respective operating and load conditions of the internal combustion engine suitable on the nozzle needle acting closing force.
- the closing force acts one also exerted on the nozzle needle Opening force opposite to that in the third pressure chamber ruling third pressure.
- a pilot injection in the second Pressure chamber to set a relatively small second pressure, so that the nozzle needle already in an open position is moved when in the third pressure chamber a the opening force conditionally relatively small third Pressure prevails.
- the pressure in the second pressure chamber be further built, whereby the nozzle needle for the subsequent main injection only then back into the Opening position moves when the third pressure in the third Pressure chamber has risen to a relatively high value. While the main injection remains the second pressure in the second pressure chamber due to the pressure limiting and Retaining valve approximately constant. The amount of during the Main injection substantially constant pressure influences the length of the main injection.
- the Pressure difference is the difference between the first pressure and the second pressure is.
- the mode of operation is such that the pressure prevailing in the first pressure chamber, the pressure limiting and holding valve initially opens, causing the second pressure in the second pressure chamber is increased. Enlarged the respective opening cross-section initially with a rising first pressure. As soon as one of them influenced by the choice of the respective opening cross-sections Pressure difference between the first pressure and the second pressure is reached, the pressure limiting and holding valve closed, whereby the second pressure in the second pressure chamber, for example, during a main injection can be kept substantially constant.
- the pressure limiting and holding valve is designed as a 2/3 valve.
- One 2/3-valve has two connections, of which in the present Connection of the first pressure chamber and a can be assigned to the second pressure chamber.
- a 2/3-valve three different switching states. Transfer to the present context, these three Switching states, in particular the closed valve, a Valve opening with an opening cross-section and an unstable Valve opening associated with an opening cross-section become.
- the pressure limiting and holding valve a first working position in which it is closed.
- the first job is a rest position forced by spring forces.
- the pressure limiting and Retaining valve a second working position with an opening cross-section having.
- the pressure limiting and Retaining valve an unstable third working position with a Has opening cross-section.
- Under unstable working position in this case is to be understood in particular a position that is no defined intermediate and final position.
- a likewise preferred embodiment of the present invention provides that the pressure relief and retention valve one different from the first job fourth work position in which it is closed.
- the pressure limiting and Retaining valve occupies the fourth working position when the first pressure the second pressure by a predetermined value exceeds. As soon as the first pressure decreases, leaves the pressure limiting and holding valve the fourth working position preferably again and in preferred embodiments, depending on the amount of the current difference between the first pressure and the second pressure, in the third, the second or first working position back.
- a first spring is provided, the exerts a closing force on the nozzle needle.
- first spring ensures, among other things, that the fuel supply to the combustion chamber the internal combustion engine is sealed when the pump-nozzle unit is at rest.
- the first spring Closing force exerted on the nozzle needle complements the Operation of the pump-nozzle unit according to the invention with the by the second pressure in the second pressure chamber on the nozzle needle applied closing force.
- the first spring is dependent different working positions of the pressure relief and -halteventils is biased differently.
- the spring preload before a pre-injection less than before a skin injection is.
- the setting of the respective bias of the first Spring takes place in an advantageous manner via the pressure limiting and -halteventil or one or more associated components.
- the pressure limiting and holding valve is a valve disk has, which cooperates with a first valve seat, which is provided adjacent to the first pressure chamber. It is considered particularly advantageous if at least the cooperating with the first valve seat section the valve disc is rounded, in particular spherical. In this case, the geometry of the first valve seat preferably adapted to that of the valve disk.
- the pressure relief and retention valve having a plate which cooperates with a stop, which is provided adjacent to the second pressure chamber.
- the dish may for example be disc-shaped.
- Pump-nozzle unit are the valve plate and the plate through separate parts formed.
- valve disk continues to cooperate with a second valve seat, the disposed between the first valve seat and the stop is.
- the pressure limiting and holding valve is then preferred closed both when the valve plate on the first valve seat abuts, as well as when the valve disc to abuts the second valve seat.
- at least one Bore can be provided in the plate:
- An equivalent Effect can be achieved when the stop with equipped with corresponding grooves.
- the dimensions of the Hole or holes and / or the groove or the grooves are preferably chosen such that that they at least the pressure build-up in the second pressure chamber do not delay excessively.
- valve disk in the first working position abuts the first valve seat.
- valve disc in the second working position not on the first valve seat and not abutting the second valve seat, and that the Plunger rests against the stop in the second working position.
- valve disc in the third working position not on first valve seat and not on the second valve seat, and that the plate in the third working position not on Stop abuts.
- the first spring supported on the plate.
- the first spring becomes dependent from the movement of the plate (further) biased.
- bias of the first spring may be desired be that required for a main injection Increase opening pressure.
- Fuel pump piston has.
- the fuel pump piston can in particular via a camshaft the internal combustion engine are driven. It can the drive directly via plunger or indirectly via rocker arm respectively.
- the fuel pump has a control valve with which the first pressure chamber completely or partially opposite to one Fuel low pressure range is closable. It allows an open control valve that sucked fuel is a compression while a closed control valve the previously sucked fuel and thus a pressure build-up allows.
- control valve operated piezoelectrically becomes.
- a piezoelectric operated control valve for example, compared to a Solenoid valve, a much more precise and faster control.
- the invention is based on the finding that the controller in particular the nozzle opening pressure compared to The prior art can be improved by adding a Closing force on the nozzle needle exerting pressure over Pressure limiting and holding valve is set.
- FIG. 1 shows a schematic embodiment of the pump-nozzle unit according to the invention.
- the illustrated pump-nozzle unit for supplying fuel 10 into a combustion chamber 12 of an internal combustion engine has a fuel pump 14-22.
- a fuel pump piston 14 in a fuel pump cylinder 16 is movable back and forth.
- the fuel pump piston 14 is driven directly or indirectly via a camshaft, not shown, of the internal combustion engine.
- the compression space of the fuel pump cylinder 16 forms the first pressure chamber 28.
- the first pressure chamber 28 is connected via a fuel line 20 with a known, piezoelectrically operated control valve 22.
- the control valve 22 serves either to close the fuel line 20 or to connect it to a low-pressure fuel area 18, from which fuel 10 can be sucked.
- the illustrated unit injector further includes a fuel injector, generally designated 24, which has a nozzle needle 26 reciprocable between a closed position and an open position.
- a fuel injector generally designated 24
- nozzle needle 26 reciprocable between a closed position and an open position.
- upper end portion of the nozzle needle 26 has a nozzle needle piston 50 which is guided in a second pressure chamber 30, wherein in the second pressure chamber 30 at a second pressure p 30 standing fuel 10 one based on the illustration of Figure 1 down directed closing force on the nozzle needle 26 exerts.
- the nozzle needle piston 50 is preferably only so strongly sealed relative to the second pressure chamber 30 that the second pressure p 30 is already reduced again before the start of a new injection cycle.
- a further downwardly directed further closing force is exerted by a first spring 36 on the nozzle needle 26, wherein the first spring 36 is disposed in the second pressure chamber 30 and is supported at its rear end to the nozzle needle piston 50.
- a shoulder 58 of the nozzle needle 26 is surrounded by a third pressure chamber 32, which communicates with the first pressure chamber 28 via a connecting line 48.
- a third pressure p 32 is built up in the third pressure chamber 32, depending on the first pressure p 28 prevailing in the first pressure chamber 28.
- the standing in the third pressure chamber 32 under the third pressure p 32 fuel 10 exerts a reference to the illustration of Figure 1 upward opening force on the nozzle needle 26 from.
- the nozzle needle 26 assumes its open position as long as a difference between the opening force caused by the third pressure p 32 and the sum of the closing force generated by the second pressure p 30 and the closing force generated by the first spring 36 exceeds a predetermined value.
- the nozzle opening pressure can be influenced via the second pressure p 30 in the second pressure chamber 30.
- a pressure limiting and holding valve 34 is provided between the first pressure chamber 28 and the second pressure chamber 30.
- FIG. 2 shows an enlarged view of the region of FIG Pump-nozzle unit of Figure 1, in which the pressure limiting and -halteventil 34 is provided.
- the pressure limit and -halteventil 34 a valve disc 38, whose Top 60 is hemispherical in shape.
- the top 60 of the valve plate 38 is designed to be with a adjacent the first pressure chamber 28 provided first valve seat 40 cooperate, which later with reference to Figure 4 will be explained in more detail.
- the flat bottom 62 of the valve disk 38 is designed with a second valve seat 46 cooperate, which later with reference to Figure 7 still is explained in more detail.
- the valve plate 38 is with a game led, based on the representation of a movement allows up and down.
- the pressure limiting and -halteventil 34 further includes a plate 42, which is formed separately from the valve disk 38. At the Bottom of the plate 42 is supported in the second Pressure chamber 30 provided first spring 36 from. From the top of the plate 42 extends from a creature 68, the one of second spring 56 is surrounded, which is located both on the valve plate 38 and supported on the plate 42 and related to the illustration of Figure 2 thus an upward Force on the valve plate 38 and a downward Force on the plate 42 exercises.
- the plate 42 is designed to cooperate with a stop 44, which will be explained in more detail later with reference to Figures 4 and 5. Of the Plate 42 has a bore 52 and a plurality of grooves 54, whose mode of action later with reference to FIG 5 closer is explained.
- FIG. 3 shows a plan view of an embodiment of the valve disk. It can be seen that the plate 42 at the illustrated embodiment, a bore 52 and three grooves 54, whose operation as mentioned with reference to FIG 5 will be explained.
- FIG. 4 shows a schematic detail view of the pressure limiting and holding valve 34 according to FIG. 2 in its first working position, in which it is closed.
- This first job corresponds to. (Also) the rest position of the pressure limiting and retaining valve 34, in which the first pressure p 28 in the first pressure chamber 28 corresponds to the second pressure p 30 in the second pressure chamber 30. 4 corresponds to the rest position, it is necessary that the first spring 36, which is supported on the underside of the plate 42, generates a greater spring force than the second spring 56, located at the top 64 of the plate 42nd and the bottom 62 of the valve plate 38 is supported.
- first spring 36 and the second spring 56 of the valve plate 38 abuts with its hemispherical surface 60 on the first valve seat 40, so that the pressure limiting and -halteventil 34 is closed. Furthermore, the upper side 64 of the plate 42 bears against the stop 44.
- first working position shown in Figure 4 corresponds to the rest position of the pressure limiting and -halteventils, this working position can be taken in other operating conditions, provided that the pressure difference between the first pressure p 28 and the second pressure p 30 a by the spring constant of the first spring 36 and the second spring 56 set value does not exceed.
- the first working position can be assumed to hold the second pressure p 30 when the first pressure p 28 in the first pressure chamber 28 is smaller than the second pressure p 30 in the second pressure chamber 30.
- FIG. 5 shows a schematic detail view of the pressure limiting and holding valve 34 according to FIG. 2 in its second working position, in which it has an opening cross section.
- the valve disk 38 In this second working position, the valve disk 38 has moved downward by, for example, 50 ⁇ m, so that an opening cross-section is formed between the hemispherical surface 60 of the valve disk 38 and the first valve seat 40, through the fuel 10 standing below the first pressure p 28 first pressure space 28 can flow.
- the plate 42 is in the illustrated second working position with its top 64 on the stop 44. However, since the plate 42 has a bore 52 and three grooves 54, the abutment of the surface 64 of the plate 42 with the stop 44 does not achieve complete sealing.
- FIG. 6 shows a schematic detail view of the pressure limiting and holding valve according to FIG. 2 in its unstable third working position.
- the valve disk 38 has moved downwards, for example by 100 ⁇ m, relative to the first working position, so that an opening cross-section is still present between the hemispherical surface 60 of the valve disk 3.8 and the first valve seat 40.
- This opening cross-section is preferably defined by the radius of the hemispherical surface 60 of the valve disk 38.
- the underside 62 of the valve disk 38 has exerted a force on the body 68, by which the plate 42, against the by the first spring 36 and the force caused by the second pressure p 30 was moved by, for example 50 microns down, so that the top 64 of the plate 42 no longer abuts against the stop 44.
- the first spring 36 is further biased so that the opening of the nozzle needle 24 in the third pressure chamber 32 required third pressure p 32 is increased.
- FIG. 7 shows a schematic detail view of the pressure limiting and holding valve 34 according to FIG. 2 in its fourth working position, in which it is likewise closed.
- This fourth working position corresponds to a pressure limiting position of the pressure limiting and retaining valve 34.
- the flat bottom 62 of the valve disk 38 bears against the second valve seat 46, so that the pressure limiting and retaining valve is closed.
- the valve disk 38 has moved downwards relative to its rest position by, for example, 150 ⁇ m.
- a force was exerted on the body 68, which moved the plate 42 based on its rest position shown in FIGS. 4 and 5 by, for example, 100 ⁇ m downwards.
- the first spring 36 has been preloaded further compared to the third working position of the pressure limiting and holding valve 34 explained with reference to FIG.
- the third pressure p 32 required for opening the nozzle needle 26 in the third pressure chamber 32 is further increased.
- the adjustment of the opening of the nozzle needle 26 required in the third pressure chamber 32 third pressure p 32 can be used for example to provide different for a pilot injection and a main injection opening pressures.
- FIG. 8 shows a curve which illustrates a possible course of the second pressure within the second pressure space as a function of the crankshaft angle.
- FIG. 9 shows a curve which illustrates a possible course of the third pressure within the third pressure space as a function of the crankshaft angle, and FIG a curve illustrating a possible injection curve as a function of the crankshaft angle.
- the illustrated and other curves can be achieved in particular by a suitable control of the control valve 22.
- the beginning of a pilot injection is designated by ° KW V
- the beginning of the main injection is designated by ° KW H.
- the second pressure p 30 in the second pressure chamber 30 is still relatively low, so that a relatively small pre-injection opening pressure p 32V in the third pressure chamber 32 is sufficient to open the nozzle needle 26, which is shown in FIG.
- the pre-injection begins as soon as the pre-injection opening pressure p 32V in the third pressure chamber 32 is reached, which can be seen from a comparison of FIGS. 9 and 10.
- the pressure limiting and holding valve 34 is in its second or third working position, so that the second pressure p 30 in the second pressure chamber 30 continues to increase, as shown in FIG. Also, the third pressure p 32 in the third pressure chamber 32 is rebuilt after the pilot injection.
- first spring 36 is required to trigger the main injection third pressure p 32H in the third pressure chamber 32 compared to that required for the pilot injection Pre-injection opening pressure p 32V significantly increased.
- this main injection opening pressure p 32H in the third pressure space 32 is reached, the main injection starts, as can be seen by a comparison of FIGS. 9 and 10.
- the second pressure p 30 in the second pressure chamber 30 is initially further built up, as shown in FIG.
- the pressure limiting and -halteventil 34 changes to its fourth working position.
- the second pressure p 30 is limited in the second pressure chamber 30 and kept approximately constant over the remaining period of the main injection. After the main injection, the second pressure p 30 in the second pressure chamber 30 decreases again, for example because of the clearance between the nozzle needle piston 50 and the second pressure chamber 30. This is advantageous in order to achieve defined initial conditions for the next injection cycle. If the clearance between the nozzle needle piston 50 and the second pressure chamber 30 for a sufficiently rapid degradation of the second pressure p 30 is not sufficiently large, additional or alternative suitable bypasses can be provided.
- the curves shown in Figures 8 to 10 vary, for example, depending on the control of the control valve 22, the respective type of internal combustion engine, the load conditions, speeds and so on.
- the invention can be summarized as follows:
- the invention relates to a pump-nozzle unit for supplying fuel in a combustion chamber of an internal combustion engine.
- a defined control of Allow injection course as well as the injection pressure is between a first pressure chamber, that of a fuel pump with fuel under a first pressure and a second pressure chamber is a pressure relief and -halteventil provided, wherein in the second Pressure chamber under a second pressure standing fuel Closing force exerts on the nozzle needle.
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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
- Figur 1
- eine schematische Ausführungsform der erfindungsgemäßen Pumpe-Düse-Einheit;
- Figur 2
- eine vergrößerte Darstellung des Bereichs der Pumpe-Düse-Einheit von Figur 1, in dem das Druckbegrenzungs- und -halteventil vorgesehen ist;
- Figur 3
- eine Draufsicht einer Ausführungsform des Tellers;
- Figur 4
- eine schematische Detailansicht des Druckbegrenzungs- und -halteventils gemäß Figur 2 in seiner ersten Arbeitsstellung, in der es geschlossen ist;
- Figur 5
- eine schematische Detailansicht des Druckbegrenzungs- und -halteventils gemäß Figur 2 in seiner zweiten Arbeitsstellung, in der es einen Öffnungsquerschnitt aufweist;
- Figur 6
- eine schematische Detailansicht des Druckbegrenzungs- und -halteventils gemäß Figur 2 in seiner unstabilen dritten Arbeitsstellung in der es ebenfalls einen Öffnungsquerschnitt aufweist;
- Figur 7
- eine schematische Detailansicht des Druckbegrenzungs- und -halteventils gemäß Figur 2 in seiner vierten Arbeitsstellung, in der es ebenfalls geschlossen ist;
- Figur 8
- eine Kurve, die einen möglichen Verlauf des zweiten Drucks innerhalb des zweiten Druckraums in Abhängigkeit vom Kurbelwellenwinkel veranschaulicht;
- Figur 9
- eine Kurve, die einen möglichen Verlauf des dritten Drucks innerhalb des dritten Druckraums in Abhängigkeit vom Kurbelwellenwinkel veranschaulicht; und
- Figur 10
- eine Kurve, die einen möglichen Einspritzverlauf in Abhängigkeit vom Kurbelwellenwinkel veranschaulicht.
Claims (22)
- Pumpe-Düse-Einheit zum Zuführen von Kraftstoff (10) in einen Verbrennungsraum (12) einer Brennkraftmaschine, miteiner steuer- und/oder regelbaren Kraftstoffpumpe (14-22),einer Kraftstoffeinspritzdüse (24), die eine zwischen einer Schließstellung und einer Öffnungsstellung hin und her bewegliche Düsennadel 826) aufweist,einem ersten Druckraum (28), der von der Kraftstoffpumpe (14-22) mit unter einem ersten Druck (p28) stehendem Kraftstoff (10) befüllbar ist,einem zweiten Druckraum (30), wobei in dem zweiten Druckraum (30) unter einem zweiten Druck (p30) stehender Kraftstoff (10) eine Schließkraft auf die Düsennadel (26) ausübt, undeinem dritten Druckraum (32), der mit dem ersten Druckraum (28) kommuniziert, wobei in dem dritten Druckraum (32) unter einem dritten Druck (p32) stehender Kraftstoff (10) eine Öffnungskraft auf die Düsennadel (26) ausübt,
das Druckbegrenzungs- und -halteventil (34) durch eine Druckdifferenz betätigt wird,
dadurch gekennzeichnet, dass die Druckdifferenz die Differenz zwischen dem ersten Druck (p28) und dem zweiten Druck (p30) ist. - Pumpe-Düse-Einheit nach Anspruch 1,
dadurch gekennzeichnet, dass das Druckbegrenzungs- und -halteventil (34) ein 2/3-Ventil ist. - Pumpe-Düse-Einheit nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass das Druckbegrenzungs- und -halteventil eine erste Arbeitsstellung aufweist, in der es geschlossen ist. - Pumpe-Düse-Einheit nach Anspruch 3,
dadurch gekennzeichnet, dass die erste Arbeitsstellung eine durch Federkräfte erzwungene Ruhestellung ist. - Pumpe-Düse-Einheit nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass das Druckbegrenzungs- und -halteventil (34) eine zweite Arbeitsstellung mit einem Öffnungsquerschnitt aufweist. - Pumpe-Düse-Einheit nach Anspruch 5,
dadurch gekennzeichnet, dass das Druckbegrenzungs- und -halteventil (34) eine unstabile dritte Arbeitsstellung mit einem Öffnungsquerschnitt aufweist. - Pumpe-Düse-Einheit nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass das Druckbegrenzungs- und -halteventil (34) eine von der ersten Arbeitsstellung verschiedene vierte Arbeitsstellung aufweist, in der es geschlossen ist. - Pumpe-Düse-Einheit nach Anspruch 1 und 7,
dadurch gekennzeichnet, dass das Druckbegrenzungs- und -halteventil (34) die vierte Arbeitsstellung einnimmt, wenn der erste Druck (p28) den zweiten Druck (p30) um einen vorgegebenen Wert übersteigt. - Pumpe-Düse-Einheit nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass in dem zweiten Druckraum (30) eine erste Feder (36) vorgesehen ist, die eine Schließkraft auf die Düsennadel (26) ausübt. - Pumpe-Düse-Einheit nach Anspruch 9,
dadurch gekennzeichnet, dass die erste Feder (36) in Abhängigkeit von unterschiedlichen Arbeitsstellungen des Druckbegrenzungs- und -halteventils (34) unterschiedlich vorgespannt ist. - Pumpe-Düse-Einheit nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass das Druckbegrenzungs- und -halteventil (34) einen Ventilteller (38) aufweist, der mit einem ersten Ventilsitz (40) zusammenwirkt, der benachbart zum ersten Druckraum (28) vorgesehen ist. - Pumpe-Düse-Einheit nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass das Druckbegrenzungs- und -halteventil (34) einen Teller (42) aufweist, der mit einem Anschlag (44) zusammenwirkt, der benachbart zum zweiten Druckraum (30) vorgesehen ist. - Pumpe-Düse-Einheit nach Anspruch 11 und 12,
dadurch gekennzeichnet, dass der Ventilteller (38) weiterhin mit einem zweiten Ventilsitz (46) zusammenwirkt, der zwischen dem ersten Ventilsitz (40) und dem Anschlag (44) angeordnet ist. - Pumpe-Düse-Einheit nach Anspruch 12 und 13,
dadurch gekennzeichnet, dass beim Anliegen des Tellers (42) am Anschlag (44) keine vollständige Abdichtung erzielt wird. - Pumpe-Düse-Einheit nach einem der Ansprüche 3 bis 14,
dadurch gekennzeichnet, dass der Ventilteller (38) in der ersten Arbeitstellung am ersten Ventilsitz (40) anliegt. - Pumpe-Düse-Einheit nach einem der Ansprüche 5 bis 15,
dadurch gekennzeichnet, dass der Ventilteller (38) in der zweiten Arbeitstellung nicht am ersten Ventilsitz (40) und nicht am zweiten Ventilsitz (46) anliegt, und dass der Teller (42) in der zweiten Arbeitsstellung am Anschlag (44) anliegt. - Pumpe-Düse-Einheit nach einem der Ansprüche 5 bis 16,
dadurch gekennzeichnet, dass der Ventilteller (38) in der dritten Arbeitstellung nicht am ersten Ventilsitz (40) und nicht am zweiten Ventilsitz (46) anliegt, und dass der Teller (42) in der dritten Arbeitsstellung nicht am Anschlag (44) anliegt. - Pumpe-Düse-Einheit nach einem der Ansprüche 7 bis 17,
dadurch gekennzeichnet, dass der Ventilteller (38) in der vierten Arbeitstellung am zweiten Ventilsitz (46) anliegt, und dass der Teller (42) in der vierten Arbeitsstellung nicht am Anschlag (44) anliegt. - Pumpe-Düse-Einheit nach einem der Ansprüche 7 bis 18,
dadurch gekennzeichnet, dass sich die erste Feder (36) an dem Teller (42) abstützt. - Pumpe-Düse-Einheit nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass die Kraftstoffpumpe (14-22) einen von der Brennkraftmaschine angetriebenen Kraftstoffpumpenkolben (14) aufweist. - Pumpe-Düse-Einheit nach einem der vorhergehenden Ansprüche,
dadurch gekennzeichnet, dass die Kraftstoffpumpe (14-22) ein Steuerventil (22) aufweist, mit dem der erste Druckraum (28) ganz oder teilweise gegenüber einem Kraftstoff-Niederdruckbereich (18) verschließbar ist. - Pumpe-Düse-Einheit nach Anspruch 20,
dadurch gekennzeichnet, dass das Steuerventil (22) piezoelektrisch betrieben wird.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10160080 | 2001-12-07 | ||
DE2001160080 DE10160080A1 (de) | 2001-12-07 | 2001-12-07 | Pumpe-Düse-Einheit |
PCT/DE2002/004426 WO2003054379A1 (de) | 2001-12-07 | 2002-12-03 | Pumpe-düse-einheit |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1451465A1 EP1451465A1 (de) | 2004-09-01 |
EP1451465B1 true EP1451465B1 (de) | 2005-08-31 |
Family
ID=7708334
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02805256A Expired - Lifetime EP1451465B1 (de) | 2001-12-07 | 2002-12-03 | Pumpe-düse-einheit |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1451465B1 (de) |
DE (2) | DE10160080A1 (de) |
WO (1) | WO2003054379A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003106836A1 (de) * | 2002-06-13 | 2003-12-24 | Siemens Aktiengesellschaft | Pumpe-düse-einheit |
EP1662133A1 (de) * | 2004-11-26 | 2006-05-31 | Siemens AG | Einspritzventil |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3411406A1 (de) * | 1983-07-29 | 1985-02-07 | Robert Bosch Gmbh, 7000 Stuttgart | Pumpduese fuer die kraftstoffeinspritzung bei brennkraftmaschinen |
JP2523759B2 (ja) * | 1987-02-04 | 1996-08-14 | フエスト − アルピネ オウトモチブ ゲゼルシャフト ミットベシュレンクテル ハフツンク | 燃料噴射ノズル |
DE19835494C2 (de) * | 1998-08-06 | 2000-06-21 | Bosch Gmbh Robert | Pumpe-Düse-Einheit |
GB9820237D0 (en) * | 1998-09-18 | 1998-11-11 | Lucas Ind Plc | Fuel injector |
DE19844891A1 (de) * | 1998-09-30 | 2000-04-06 | Bosch Gmbh Robert | Kraftstoffeinspritzventil für Brennkraftmaschinen |
DE19942846C1 (de) * | 1999-09-08 | 2000-11-16 | Bosch Gmbh Robert | Vorrichtung und Verfahren zur druckgesteuerten Einspritzung eines Fluids |
DE10012552A1 (de) * | 2000-03-15 | 2001-09-27 | Bosch Gmbh Robert | Einspritzeinrichtung mit einem Aktor zur Nadelhubsteuerung |
-
2001
- 2001-12-07 DE DE2001160080 patent/DE10160080A1/de not_active Ceased
-
2002
- 2002-12-03 EP EP02805256A patent/EP1451465B1/de not_active Expired - Lifetime
- 2002-12-03 DE DE50204124T patent/DE50204124D1/de not_active Expired - Fee Related
- 2002-12-03 WO PCT/DE2002/004426 patent/WO2003054379A1/de not_active Application Discontinuation
Also Published As
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DE50204124D1 (de) | 2005-10-06 |
DE10160080A1 (de) | 2003-06-26 |
WO2003054379A1 (de) | 2003-07-03 |
EP1451465A1 (de) | 2004-09-01 |
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