EP1377745B1 - Verfahren zum betreiben einer pumpe-düse-einheit sowie pumpe-düse-einheit - Google Patents
Verfahren zum betreiben einer pumpe-düse-einheit sowie pumpe-düse-einheit Download PDFInfo
- Publication number
- EP1377745B1 EP1377745B1 EP02727288A EP02727288A EP1377745B1 EP 1377745 B1 EP1377745 B1 EP 1377745B1 EP 02727288 A EP02727288 A EP 02727288A EP 02727288 A EP02727288 A EP 02727288A EP 1377745 B1 EP1377745 B1 EP 1377745B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- valve
- system pressure
- valve element
- preloading
- 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
- 238000000034 method Methods 0.000 title claims description 34
- 238000002347 injection Methods 0.000 claims description 61
- 239000007924 injection Substances 0.000 claims description 61
- 238000002485 combustion reaction Methods 0.000 claims description 28
- 239000000446 fuel Substances 0.000 claims description 22
- 230000006835 compression Effects 0.000 claims description 18
- 238000007906 compression Methods 0.000 claims description 18
- 238000007789 sealing Methods 0.000 claims description 7
- 238000005086 pumping Methods 0.000 claims description 6
- 230000008569 process Effects 0.000 claims description 4
- 230000036316 preload Effects 0.000 description 12
- 238000011161 development Methods 0.000 description 6
- 230000018109 developmental process Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000000630 rising effect Effects 0.000 description 4
- 239000002828 fuel tank Substances 0.000 description 3
- 238000012549 training Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 241001295925 Gegenes Species 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000003716 rejuvenation Effects 0.000 description 1
- 239000004071 soot Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- 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
- F02M45/02—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
- F02M57/00—Fuel-injectors combined or associated with other devices
- F02M57/02—Injectors structurally combined with fuel-injection pumps
- F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
-
- 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
Definitions
- Pump-nozzle units comprise a valve element, which from a spring is pressed into its closed position.
- One of a piston pump driven by a camshaft delivers one System pressure on a pressure surface of the valve element attacks and with which the valve element against the biasing force can be opened.
- the spring that the valve element in presses its closed position supports itself on her other End on a movable switching element. Will that Moving the switching element towards the valve element increases the biasing force acting on the valve element and the direct related valve opening and closing pressure.
- the system pressure is initially increased so that the Valve element opens against the spring force. Now it will Switching element moves and the preload increases. This happens so that the valve closing pressure increases faster increased than the system pressure acting.
- the system pressure will "Overhauled” by the valve closing pressure, so to speak. Despite As the system pressure rises, the valve closes. In the The valve opening pressure remains in the end position of the switching element and the valve closing pressure constantly increased Level.
- the system pressure is raised further until it is above again of the increased valve opening pressure. Now that opens Again, the valve element against the increased biasing force Main injection. This is ended by the System pressure to a level below the (increased) valve closing pressure is lowered. The switching element is in again moved back to its original position so that the valve opening pressure and the valve closing pressure on again normal level decrease.
- valve opening pressure is in the known Process limited, otherwise the break between the Pre-injection and the main injection would be too long.
- some use cases are very high Injection pressure desired. This is particularly the case if there is a post-injection after the main injection should be done. Too low pressure during post-injection can lead to undesirably high soot formation.
- a fuel injection system is also known from EP 0 805 271 A1, whose pump nozzle injector one pre and one Main injection can inject. This will be done during the Pre-injection the closing pressure increased and the system pressure lowered, which ends the pilot injection. The control this process takes place, among other things, by means of a Overflow valve.
- the object of the present invention is therefore a method of the type mentioned in such a way that with him post-injection with very high injection pressure possible is.
- the Preload force only increases so quickly that the valve closing pressure is always below the system pressure. in the This contrasts with the known method excluded that the valve closing pressure the System pressure "outdated” and thereby despite increasing System pressure closes the valve element. So there is much of the period of main injection for the Increasing the preload and thus for increasing the Valve opening pressure available.
- the preload can therefore be increased much more than is possible with the known methods. Closing the valve element between the The main injection and the post-injection become active causes the system pressure to be lowered. On "Hydraulic" closing as in the known method is not provided here.
- step c) the system pressure to a value below an elevated Valve closing pressure is lowered, so that Valve element closes, and the biasing force on the Valve element is reduced, the due to lower preload, lower valve opening pressure is always above the system pressure, so that Valve element remains closed.
- the valve element is already at a relatively high level System pressure closed. This has the advantage that while the overall post-injection is relatively high Injection pressure is present.
- step c) the switching element in the direction of Biasing force is moved back to its original position.
- step b) the Switching element is moved hydraulically. Then this is possible if there is a pressure surface on the switching element which is with a pressure, preferably the system pressure, can be applied. In this case for example, on an electrical control of the Switching element can be dispensed with, which security the implementation of the method according to the invention increased.
- step b) Switching element by successively applying counter at least two pressure areas with the system pressure the application of the biasing element from its Starting position is moved out, the first Printing area always with the system pressure and the second Only then is pressure applied to the system surface is when the switching element is something out of its Has moved out of the starting position.
- the method according to the invention is particularly preferred then when in addition to the main and post-injection a pre-injection can be carried out. hereby the consumption and emission behavior of the with the Internal combustion engine operated method according to the invention optimized again. It is proposed that before Step a) the system pressure to a value above the normal valve opening pressure is raised, so that Valve element against the action of the Preload element for a pre-injection at normal System pressure opens, and then the system pressure opens a value below the normal valve closing pressure is lowered so that the valve element closes.
- the on pre-injection carried out in this way takes place at a relatively low system pressure and at one Switching element, which is in the starting position located.
- valve element Another way to open the valve increase is to counter the valve element Apply pressure to the opening direction. This can in addition or as an alternative to the application of the Valve element done by the biasing element. For this it is also proposed that the valve element against the Opening direction acted upon with system pressure with a time delay becomes. The system pressure is in the area of the valve element anyway before and can therefore without expensive measures Increasing the valve opening pressure can be used.
- the present invention also relates to a pump-nozzle unit for supplying fuel to a combustion chamber Internal combustion engine, with an injection nozzle for injection the fuel into the combustion chamber, with at least one Valve element, which has at least a first pressure surface has, the force resultant approximately in Opening direction of the valve element shows with a Preload element, which the valve element in the direction of Applied to the closed position, with a switching element on the the biasing element is supported and which along the Direction of action movable by the biasing element is, with a pump device, which one on the first Pressure area of the valve element builds up system pressure, and with a control device which assembles and disassembles the Controls system pressure.
- Such a pump-nozzle unit is also known from document EP 805 271 A1. As already mentioned at the beginning, it will be used primarily for Motor vehicle diesel internal combustion engines used. To with of such a pump-nozzle unit is as fuel-efficient as possible Emission-optimized operation of the internal combustion engine To be able to implement, it is proposed according to the invention that the characteristic of the pretensioner and the sizes of the Pressure areas are coordinated so that the valve closing pressure while increasing the system pressure during a main injection always remains below the system pressure, so with such Pump-nozzle unit the procedure of the above type can be carried out.
- the switching element be a first Has printing area and a second printing area
- the first pressure area of the switching element is smaller than that first pressure surface on the valve element
- the first Pressure area and the second pressure area of the switching element together are larger than the entire printing area of the Valve element, wherein the first pressure surface of the Switching element is always connected to the pump device, so that it is always pressurized with the system pressure, and the second pressure surface of the switching element only is then connected to the pump device when the Switching element somewhat from its starting position has moved out.
- a pretensioning device is also particularly simple realize which includes a compression spring.
- the Pump-nozzle unit according to the invention is between the Valve element and the switching element a pressure chamber available, which of a second printing surface of the Valve element is limited, the force resultant too the force resultant of the first pressure surface of the Valve element is oriented approximately opposite, and a flow channel is provided in the switching element which is from the pressure space to the second pressure area of the switching element leads.
- valve element alternatively or in addition to the pretension e.g. by means of a compression spring acted upon by hydraulic pressure be, which also the valve opening pressure or Valve closing pressure can be increased.
- the application takes place in that the pressure space between the Switching element and the valve element fluidly with that Pressure chamber is connected by the second printing area of the switching element is limited.
- Loading of the Pressure space between the switching element and the valve element with hydraulic pressure only takes place when that Switching element somewhat from its starting position has moved out.
- the flow channel is a Flow restrictor includes. This builds up the pressure in the Pressure space between valve element and switching element only gradually on. This in turn ensures that during the increase in system pressure from the valve closing pressure is not "caught up".
- a simple realization for one Flow channel possibly with flow restrictor, consists of a through hole through the shank element. Furthermore, it is also possible to have a gap between the Switching element and a surrounding the switching element Provide housing. This can take the form of, for example Grinding on an area of the outer jacket of the Switching element take place. All of these trainings one Flow channels are easy to implement.
- the Control device comprises a switching valve; which the Connect the pump device to a low pressure area can. This ensures that when the Pumping device delivers fuel to the valve element however, an increase in system pressure is not desired is the volume flow towards the low pressure area can be drained and therefore there is no system pressure builds.
- a particularly fast switching of such Switching valve is reached when the switching valve as Actuator has at least one piezo element.
- valve opening pressures can be achieved.
- the increased valve opening pressure is more than twice that high than the normal valve opening pressure, further it is preferably 400 to 800 bar, still further preferably at 700 to 800 bar.
- a 'first embodiment of a unit injector bears overall reference number 10 in FIG. 1 a pump device 12, a nozzle device 14 and a Control device 16.
- the pump device 12 is a Single-cylinder piston pump 18, which is driven by a cam 20 is driven.
- the cam 20 is in turn with the Crankshaft of an internal combustion engine (not shown) coupled.
- the pumping device conveys each delivery stroke 12 fuel from a line, not shown a reservoir 64 via a fuel line 22 to Nozzle device 14.
- the nozzle device 14 comprises a housing 24 in which one Stepped bore 26 is formed.
- a valve element 28 In the stepped bore 26 is a valve element 28 with a circular cylindrical cross section guided.
- the valve element 28 is along its longitudinal axis 29 movable.
- At the lower end of the housing 24 is one Injection opening 30 is present.
- the valve element 28 will by a compression spring 32 against a valve seat (not visible) pressed in the area of the injection opening 30.
- the Valve element 28 has a circumferential oblique first Printing area 34, which of an annular pressure chamber 36 is surrounded.
- the pressure chamber 36 is in turn with the Fuel line 22 connected.
- the end of the compression spring remote from the valve element 28 32 is supported on a circular cylindrical switching element 38 from.
- the switching element 38 has one of the compression springs 32 facing section 40 with a constant diameter and a section 42 facing away from the compression spring 32, which is conical in the manner of a truncated cone rejuvenated.
- the blunt tip of the conical section 42 forms a first pressure surface 44 of the switching element 38, whereas the sloping surface of the conical Section 42 of the switching element 38 a second pressure surface 46 forms.
- the switching element 38 can be located in the stepped bore 26 along the longitudinal axis 29 between that in FIG. 1 shown starting position and one by a radial inwardly facing ring web 54 limited switching position move. In this switching position, the sealing edge 48 lies no longer on the oblique pressure surface 46 of the Switching element 38 on, so that the two pressure chambers 50 and 51 are connected.
- a branch line 56 branches off from the fuel line 22 which leads to the control device 16.
- the Control device 16 comprises a piezo actuator 58 actuable switching valve 60, which on the output side a low pressure line 62 with the fuel tank 64 connected is.
- the piezo actuator 58 of the control device 16 is from a control and not shown in the figure Control device controlled. In a not shown Embodiment is used instead of a piezo actuator Magnetic actuator used.
- the pump-nozzle unit 10 shown in Fig. 1 becomes Injection of fuel into the combustion chamber Internal combustion engine used. There is for every combustion chamber (that is, for each cylinder) of the internal combustion engine own pump-nozzle unit 10 is provided. The fuel can by a "triple injection" in the Coming to the combustion chamber of the internal combustion engine. The procedure after such a triple injection takes place, is now explained with reference to FIGS. 2-5:
- the cam 20 of the pump device 12 is so with the Crankshaft of the internal combustion engine synchronizes that Single-cylinder piston pump during an injection stroke of the always assigned a delivery stroke to its assigned cylinder performs.
- Switch valve 60 initially at the beginning of an injection cycle closed (rising edge 66 in Fig. 2). This leads to, 3, an increase in the System pressure in the fuel line 22 and in the sequence also in the pressure chamber 36 (rising edge 68 in FIG. 3).
- the spring force of the compression spring 32 will Valve element 28 with a certain force against the corresponding valve seat in the area of the injection opening 30 pressed. This will result in a normal valve opening force specified.
- the increasing pressure in the pressure chamber 36 now acts on the Pressure surface 34 on the valve element 28. Exceeds this resulting force the pressure exerted by the compression spring 32 Closing force becomes the normal valve opening pressure of the valve element 28 is exceeded, the valve element lifts 28 from the valve seat in the region of the injection opening 30 opens.
- the normal valve opening pressure is in Fig. 3 represented by a dash-dotted curve and is with POVN marked.
- the opening of the valve element 28 is 5 recognizable on the rising edge 70. By this opening of the valve element 28 becomes a Pre-injection performed.
- Switch valve 60 opens again (falling edge 72 in FIG. 2). This causes the system pressure in the Fuel line 22, since this is now for Fuel tank 64 is open. This is through the falling edge 74 shown in FIG. 3. Corresponding closes the valve element 28 (falling edge 76 in FIG. 5) as soon as the system pressure P in FIG. 3 is below a normal valve closing pressure PSVN has dropped.
- the Valve closing pressure PSVN is double in Fig. 3 by one dash-dotted line shown.
- the switching valve 60 is closed again (increasing Edge 78 in Fig. 2).
- the system pressure P increases accordingly (Edge 80 in Fig. 3).
- the valve opening pressure POVN is exceeded, the valve element 28 opens (Rising edge 82 in Fig. 5).
- the system pressure P exceeds an opening switching pressure POS of the switching element 38.
- This pressure POS corresponds to the pressure at which the switching element 38 begins to separate from the sealing edge 48. This is again the case when the pressure surface 44 outgoing force the biasing force of the compression spring 32nd exceeds.
- the second pressing surface 46 With the system pressure P. This will causes the switching element 38 to oppose the Acted upon by the compression spring 32 moved down, until it rests on the ring web 54 (flank 83 in FIG. 4).
- the starting position is designated by S0, whereas the switch position, in which the Switching element 38 rests on the ring web 54, designated S1 is.
- the characteristic of the spring 32 and the sizes of the Printing areas 34 and 44 are coordinated so that the valve closing pressure PSV during this increase in System pressure P is always below the system pressure P.
- the main injection is ended by the fact that the Switch valve 60 is opened again, analogously to the end of Pilot injection.
- the corresponding falling edges in 2, 3 and 5 bear the reference numerals 88, '90 and 92.
- the closing of the valve element 28 is brought about by that the system pressure P in Fig. 3 is below the increased valve closing pressure PSVH drops.
- the drop in system pressure P is limited so that a switching pressure PSS, in which the switching element 38 again in its Starting position S0 returns, is not fallen below.
- a post-injection is again by closing the Switching valve 60 initiated.
- the corresponding edges in 2, 3 and 5 bear the reference numerals 94, 96 and 98.
- the system pressure P again exceeds the increased pressure Valve opening pressure POVH, so that the valve element 28 opens again.
- the post-injection takes place accordingly high injection pressure.
- Usual values for a normal one Valve opening pressure is approximately 300 bar, whereas the injection pressure during post-injection due to the increased valve opening pressure POVH is about 500 to 600 bar.
- Fig. 1st illustrated embodiment of a pump-nozzle unit 10 relate to the design of the switching element 38 the embodiment shown in Fig. 1 was the between the valve element 28 and the switching element 38 formed area of the stepped bore 26 is not under pressure set. In this case, the valve element 28 thus acts only the preload force, which is caused by the compression spring 32 is applied.
- the switching element 38 lifts from the sealing edge 48, so that the second pressure chamber 51 and the first pressure chamber 50 with the fuel line 22 is connected and thus the two pressure surfaces 44 and 46 with the system pressure P.
- the Flow channel 110 now also flows into the fuel between the switching element 38 and the valve element 28 formed pressure chamber 108, so that this also a corresponding pressure builds up to the system pressure P.
- This pressure also acts on that of the compression spring 32 facing printing area (not visible in FIGS. 6 - 8) of the valve element 28, so that this in addition to Biasing force of the compression spring 32 with a corresponding Pressure force is applied.
- valve opening pressure POV again raised so that in these embodiments particularly high injection pressure of up to 800 bar can be realized.
- pressure chamber 108 also system pressure could be a hazard exist that act on the switching element 38 hydraulic force resultant becomes smaller than that of the compression spring 32 force exerted on the switching element 38. In this case, the switching element 38 would be in again to move back to its original position.
- This second Flow channel connects the pressure chamber 108 with the Low pressure area, for example the fuel tank.
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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
- b1)
- Absenken des Systemdrucks auf einen Wert unterhalb des Ventil-Schließdrucks, so dass das Ventilelement schließt,
- b2)
- Erhöhen des Systemdrucks, so dass das Ventilelement zu einer Nacheinspritzung bei einem aufgrund der gestiegenen Vorspannkraft erhöhten Ventil-Öffnungsdruck öffnet.
- Fig. 1:
- eine schematische Darstellung eines ersten Ausführungsbeispiels einer Pumpe-Düse-Einheit;
- Fig. 2:
- ein Diagramm, in dem der Schaltzustand eines Steuerventils der Pumpe-Düse-Einheit von Fig. 1 über der Zeit dargestellt ist;
- Fig. 3:
- ein Diagramm, in dem der Verlauf des Systemdrucks der Pumpe-Düse-Einheit von Fig. 1 über der Zeit dargestellt ist;
- Fig. 4:
- ein Diagramm, in dem der Schaltzustand eines Schaltelements der Pumpe-Düse-Einheit von Fig. 1 über der Zeit aufgetragen ist;
- Fig. 5:
- ein Diagramm, in dem der Schaltzustand eines Ventilelements der Pumpe-Düse-Einheit von Fig. 1 über der Zeit aufgetragen ist;
- Fig. 6:
- einen Ausschnitt eines zweiten Ausführungsbeispiels einer Pumpe-Düse-Einheit; .
- Fig. 7:
- eine Ansicht ähnlich Fig. 6 eines dritten Ausführungsbeispiels einer Pumpe-Düse-Einheit; und
- Fig. 8:
- eine Ansicht ähnlich Fig. 6 eines vierten Ausführungsbeispiels einer Pumpe-Düse-Einheit.
Claims (20)
- Verfahren zum Betreiben einer Pumpe-Düse-Einheit (10), mit dem Kraftstoff in einen Brennraum einer Brennkraftmaschine dadurch eingespritzt wird, dass ein Ventilelement (28) durch eine Erhöhung eines Systemdrucks (P) gegen eine Vorspannkraft geöffnet wird, wobei das Verfahren nacheinander folgende Schritte umfasst:a) Anheben (80) des Systemdrucks (P) auf einen Wert oberhalb eines normalen Ventil-Öffnungsdrucks (POVN), so dass das Ventilelement (28) gegen die Vorspannkraft zu einer Haupteinspritzung öffnet (82),b) Erhöhen der Vorspannkraft während des Anhebens (80) des Systemdrucks (P),c) Absenken (102) des Systemdrucks (P) und Absenken der Vorspannkraft, so dass das Ventilelement (28) schließt (104),
im Schritt b) ein aufgrund der gestiegenen Vorspannkraft erhöhter Ventil-Schließdruck (PSVH) immer unterhalb des Systemdrucks (P) liegt, so dass das Ventilelement (28) geöffnet bleibt, und dass zwischen den Schritten b) und c) nacheinander folgende Schritte vorgesehen sind:b1) Absenken (90), des Systemdrucks (P) auf einen Wert unterhalb des erhöhten Ventil-Schließdrucks (PSVH), so dass das Ventilelement (28) schließt (92),b2) Erhöhen (96) des Systemdrucks (P), so dass das Ventilelement (28) zu einer Nacheinspritzung bei einem aufgrund der gestiegenen Vorspannkraft erhöhten Ventil-Öffnungsdruck (POVH) öffnet (98). - Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass im Schritt c) der Systemdruck (P) auf einen Wert unterhalb eines erhöhten Ventil-Schließdrucks (PSVH) abgesenkt wird (102), so dass das Ventilelement (28) schließt, und die Vorspannkraft auf das Ventilelement (28) verringert wird, wobei der aufgrund der geringeren Vorspannkraft niedrigere Ventil-Öffnungsdruck (POV) dabei immer oberhalb des Systemdrucks (P) liegt, so dass das Ventilelement (28) geschlossen bleibt.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Ventilelement (28) gegen die Vorspannkraft eines.Vorspannelements (32') öffnet, welches durch ein bewegliches Schaltelement (38) abgestützt wird, und dass im Schritt b) das Schaltelement (38) während des Anhebens (80) des Systemdrucks (P) entgegen der Vorspannkraft bewegt wird (83), so dass sich die Vorspannkraft erhöht.
- Verfahren nach Anspruch 3, dadurch gekennzeichnet, dass im Schritt c) das Schaltelement (38) in Richtung der Vorspannkraft in seine Ausgangsstellung (S0) zurückbewegt wird (106).
- Verfahren nach einem der Ansprüche 3 oder 4, dadurch gekennzeichnet, dass im Schritt b) das Schaltelement hydraulisch bewegt wird (106).
- Verfahren nach Anspruch 5, dadurch gekennzeichnet, dass im Schritt b) das Schaltelement (38) durch eine sukzessive Beaufschlagung von mindestens zwei Druckflächen (44, 46) mit dem Systemdruck (P) entgegen der Beaufschlagung durch das Vorspannelement (32) aus seiner Ausgangsstellung ( SO) herausbewegt wird, wobei die erste Druckfläche ( 44) immer mit dem Systemdruck (P) und die zweite Druckfläche (46) erst dann mit dem Systemdruck (P) beaufschlagt wird, wenn sich das Schaltelement (38) etwas aus seiner Ausgangsstellung (S0) herausbewegt hat.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass vor dem Schritt a) der Systemdruck (P) auf einen Wert oberhalb des normalen Ventil-Öffnungsdrucks ( POVN) angehoben wird (68), so dass das Ventilelement (28) entgegen der Beaufschlagung durch das Vorspannelement (32) zu einer Voreinspritzung bei normalem Systemdruck ( P) öffnet (70), und der Systemdruck (P) anschließend auf einen Wert unterhalb des normalen Ventil-Schließdrucks (PSVN) abgesenkt wird (74), so dass das Ventilelement (28) schließt (76).
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Ventilelement (28) entgegen der Öffnungsrichtung mit Druck (P) beaufschlagt und hierdurch der Ventil-Öffnungsdruck (POV) erhöht wird.
- Verfahren nach Anspruch 8, dadurch gekennzeichnet, dass das Ventilelement (28) entgegen der Öffnungsrichtung zeitversetzt mit dem Systemdruck ( P) beaufschlagt wird.
- Pumpe-Düse-Einheit (10) zur Zufuhr von Kraftstoff in einen Brennraum einer Brennkraftmaschine, mit einer Einspritzdüse (30) zum Einspritzen des Kraftstoffs in den Brennraum, mit mindestens einem Ventilelement (28), welches mindestens eine erste Druckfläche (34) aufweist, deren Kraft-Resultierende in etwa in Öffnungsrichtung des Ventilelements ( 28) zeigt, mit einem Vorspannelement (32), welches das Ventilelement (28) in Richtung der Schließstellung beaufschlagt, mit einem Schaltelement (38), an dem sich das Vorspannelement (32) abstützt und welches längs der Beaufschlagungsrichtung durch das Vorspannelement (32) beweglich ist, mit einer Pumpeinrichtung (12), welche einen auf die erste Druckfläche (34) des Ventilelements (28) wirkenden Systemdruck (P) aufbaut, und mit einer Steuereinrichtung (16), welche den Auf- und Abbau des Systemdrucks (P) steuert, dadurch gekennzeichnet, dass die Kennlinie der Vorspanneinrichtung (32) und die Größen der Druckflächen (34) so aufeinander abgestimmt sind, dass der Ventil-Schließdruck (PSV) während der Erhöhung des Systemsdrucks (P) während einer Haupteinspritzung immer unterhalb des Systemdrucks (P) bleibt, so dass mit der Pumpe-Düse-Einheit das Verfahren nach einem der Ansprüche 1 bis 9 durchgeführt werden kann.
- Pumpe-Düse-Einheit (10) nach Anspruch 10, dadurch gekennzeichnet, dass das Schaltelement (38) eine erste Druckfläche ( 44) und eine zweite Druckfläche (46) aufweist, wobei die erste Druckfläche (44) des Schaltelements (38) kleiner ist als die erste Druckfläche (34) am Ventilelement (28), wobei die erste Druckfläche (44) und die zweite Druckfläche (46) des Schaltelements (38) zusammen größer sind als die gesamte Druckfläche (34) des Ventilelements (28), wobei die erste Druckfläche (44) des Schaltelements (38) immer mit der Pumpeinrichtung (12) verbunden ist, so dass sie immer mit dem Systemdruck (P) beaufschlagt wird, und wobei die zweite Druckfläche (46) des Schaltelements (38) erst dann mit der Pumpeinrichtung (12) verbunden wird, wenn sich das Schaltelement (38) etwas aus seiner Ausgangsstellung (S0) herausbewegt hat.
- Pumpe-Düse-Einheit (10) nach Anspruch 11, dadurch gekennzeichnet, dass eine Dichtkante (48) vorhanden ist, welche in der Ausgangsstellung (S0) des Schaltelements (38) die beiden Druckflächen (44, 46) voneinander trennt.
- Pumpe-Düse-Einheit (10) nach einem der Ansprüche 10 bis 12, dadurch gekennzeichnet, dass die Vorspanneinrichtung eine Druckfeder (32) umfasst.
- Pumpe-Düse-Einheit (10) nach einem der Ansprüche 10 bis 13, dadurch gekennzeichnet, dass zwischen dem Ventilelement (28) und dem Schaltelement (38) ein Druckraum (108) vorhanden ist, welcher von einer zweiten Druckfläche (112) des Ventilelements (28) begrenzt wird, deren Kraft-Resultierende zu der Kraft-Resultierenden der ersten Druckfläche (34) des Ventilelements (28) in etwa entgegengesetzt ausgerichtet ist, und dass im Schaltelement (38) ein Strömungskanal (110) vorgesehen ist, welcher von dem Druckraum (108) zu der zweiten Druckfläche (46) des Schaltelements (38) führt.
- Pumpe-Düse-Einheit (10) nach Anspruch 14, dadurch gekennzeichnet, dass der Strömungskanal (110) eine Strömungsdrossel umfasst.
- Pumpe-Düse-Einheit (10) nach einem der Ansprüche 14 oder 15, dadurch gekennzeichnet, dass eine Durchgangsbohrung (110) durch das Schaltelement (38) vorhanden ist.
- Pumpe-Düse-Einheit (10) nach einem der Ansprüche 14 bis 16, dadurch gekennzeichnet, dass ein Spalt (110) zwischen dem Schaltelement (38) und einem das Schaltelement (38) umgebenden Gehäuse (24) vorhanden ist.
- Pumpe-Düse-Einheit (10) nach einem der Ansprüche 10 bis 17, dadurch gekennzeichnet, dass die Steuereinrichtung (16) ein Schaltventil (60) umfasst, welches die Pumpeinrichtung (12) mit einem Niederdruckbereich (62, 64) verbinden kann.
- Pumpe-Düse-Einheit (10) nach Anspruch 18, dadurch gekennzeichnet, dass das Schaltventil (60) als Aktor mindestens ein Piezo-Element (58) aufweist.
- Pumpe-Düse-Einheit (10) nach einem der Ansprüche 10 bis 19, dadurch gekennzeichnet, dass der erhöhte Ventil-Öffnungsdruck (POVH) mehr als doppelt so hoch ist als der normale Ventil-Öffnungsdruck (POVN), vorzugsweise bei ungefähr'400 bis 800 bar, weiter vorzugsweise bei 700 bis 800 bar liegt.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10116635 | 2001-04-04 | ||
DE10116635A DE10116635A1 (de) | 2001-04-04 | 2001-04-04 | Verfahren zum Betreiben einer Pumpe-Düse-Einheit sowie Pumpe-Düse-Einheit |
PCT/DE2002/001235 WO2002081900A1 (de) | 2001-04-04 | 2002-04-04 | Verfahren zum betreiben einer pumpe-düse-einheit sowie pumpe-düse-einheit |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1377745A1 EP1377745A1 (de) | 2004-01-07 |
EP1377745B1 true EP1377745B1 (de) | 2004-11-03 |
Family
ID=7680252
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP02727288A Expired - Lifetime EP1377745B1 (de) | 2001-04-04 | 2002-04-04 | Verfahren zum betreiben einer pumpe-düse-einheit sowie pumpe-düse-einheit |
Country Status (4)
Country | Link |
---|---|
US (1) | US20040020458A1 (de) |
EP (1) | EP1377745B1 (de) |
DE (2) | DE10116635A1 (de) |
WO (1) | WO2002081900A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2003106836A1 (de) * | 2002-06-13 | 2003-12-24 | Siemens Aktiengesellschaft | Pumpe-düse-einheit |
DE10233101A1 (de) * | 2002-07-20 | 2004-01-29 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
WO2004057176A1 (de) * | 2002-12-20 | 2004-07-08 | Volkswagen Mechatronic Gmbh & Co. Kg | Pumpe-düse-einheit |
DE102004057151B4 (de) * | 2004-11-26 | 2009-04-16 | Continental Automotive Gmbh | Einspritzventil mit einem Druckhalteventil zur Fluiddruckbeaufschlagung eines Federraums |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
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GB9609382D0 (en) * | 1996-05-03 | 1996-07-10 | Lucas Ind Plc | Fuel injection system |
-
2001
- 2001-04-04 DE DE10116635A patent/DE10116635A1/de not_active Withdrawn
-
2002
- 2002-04-04 WO PCT/DE2002/001235 patent/WO2002081900A1/de active IP Right Grant
- 2002-04-04 US US10/297,218 patent/US20040020458A1/en not_active Abandoned
- 2002-04-04 EP EP02727288A patent/EP1377745B1/de not_active Expired - Lifetime
- 2002-04-04 DE DE50201468T patent/DE50201468D1/de not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
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DE10116635A1 (de) | 2002-10-17 |
EP1377745A1 (de) | 2004-01-07 |
US20040020458A1 (en) | 2004-02-05 |
DE50201468D1 (de) | 2004-12-09 |
WO2002081900A1 (de) | 2002-10-17 |
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