EP1377745A1 - Procede pour actionner une unite pompe-ajutage et unite pompe-ajutage correspondante - Google Patents

Procede pour actionner une unite pompe-ajutage et unite pompe-ajutage correspondante

Info

Publication number
EP1377745A1
EP1377745A1 EP02727288A EP02727288A EP1377745A1 EP 1377745 A1 EP1377745 A1 EP 1377745A1 EP 02727288 A EP02727288 A EP 02727288A EP 02727288 A EP02727288 A EP 02727288A EP 1377745 A1 EP1377745 A1 EP 1377745A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
switching element
pump
system pressure
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.)
Granted
Application number
EP02727288A
Other languages
German (de)
English (en)
Other versions
EP1377745B1 (fr
Inventor
Roger Potschin
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1377745A1 publication Critical patent/EP1377745A1/fr
Application granted granted Critical
Publication of EP1377745B1 publication Critical patent/EP1377745B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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

  • the invention initially relates to a method for operating a pump-nozzle unit, * with which fuel is injected into a combustion chamber of an internal combustion engine by opening a valve element against a preload force by increasing a system pressure, the method comprising the following steps in succession :
  • Pump-nozzle units of this type comprise a valve element which is pressed into its closed position by a spring.
  • a piston pump driven by a camshaft provides a system pressure that acts on a pressure surface of the valve element and with which the valve element can be opened against the biasing force.
  • the spring that presses the • valve element into its closed position is supported at its other end on a movable switching element. If the switching element is moved towards the valve element, the pretensioning force acting on the valve element increases and the valve opening and valve closing pressure directly related to it.
  • a double injection can be realized with the known method:
  • the system pressure is initially increased so that the valve element opens against the spring force. Now the switching element is moved and the preload force is increased. This is how it happens; that the valve closing pressure increases faster than the effective system pressure.
  • the system pressure is raised further until it is again above the increased valve opening pressure. Now the valve element opens again for a main injection against the increased pretensioning force. This is ended by lowering the system pressure to a level below the (increased) vent closing pressure. The switching element is moved back to its starting position, so that the valve opening pressure and the valve closing pressure also drop to a normal level.
  • valve opening pressure is at that Known methods limited, otherwise the pause between the pre-injection and the main injection would be too long. In some applications, however, a very high injection pressure is desired. This is particularly the case if a post-injection is to take place after the main injection. Too low a pressure during post-injection can lead to undesirably high soot formation.
  • the object of the present invention is therefore to develop a method of the type mentioned at the outset in such a way that post-injection with a very high injection pressure is possible with it.
  • step b) an increased valve closing pressure due to the increased preload is always below the system pressure, so that the valve element remains open, and that between steps b) and c) the following steps are provided:
  • the pretensioning force is only increased so quickly that the valve closing pressure is always below the system pressure. in the In contrast to the known method, this precludes the valve closing pressure from "overtaking” the system pressure and thereby closing the valve element despite increasing system pressure. A large part of the period of the main injection is thus available for increasing the pretensioning force and thus for increasing the valve opening pressure.
  • the preload can therefore be increased much more than is possible with the known methods. Closing the valve element between the main injection and the post-injection is actively caused that the system pressure is reduced. A "hydraulic" closing as in the known method is therefore not provided here.
  • Post-injection at a very high injection pressure can thus be realized with the method according to the invention. This leads to a particularly consumption- and emission-optimized combustion behavior, particularly in diesel internal combustion engines.
  • step c) the system pressure is reduced to a value below an increased valve closing pressure, so that the valve element closes, and the pretensioning force on the valve element is reduced, the valve opening pressure, which is lower due to the lower pretensioning force, always is above the system pressure so that the valve element remains closed.
  • the valve element is therefore already closed at a relatively high system pressure. This has the advantage that a relatively high level during the entire post-injection Injection pressure is present.
  • valve element opens against the biasing force of a biasing element which is supported by a movable switching element, and that in step b) the switching element is moved against the biasing force during the raising of the system pressure, so that the preload increases.
  • a mechanical movement which can be easily generated, is used to change the pretensioning force and subsequently to change the valve opening pressure or the valve closing pressure.
  • step c) the switching element is moved back into its initial position in the direction of the pretensioning force.
  • the switching element be moved hydraulically in step b). This is possible if there is a pressure surface on the switching element which can be subjected to a pressure, preferably the system pressure. In this case, electrical control of the switching element can be dispensed with, for example, which increases the safety when carrying out the method according to the invention.
  • step b) the switching element is moved out of its initial position by a stepwise application of at least two pressure surfaces with the system pressure against the loading by the biasing element, the first pressure surface always with the system pressure and the second pressure surface only then the system pressure is applied when the switching element is somewhat out of it Has moved out of the starting position.
  • the method according to the invention is particularly preferred if, in addition to the main and post-injection, a pre-injection can also be carried out.
  • the consumption and emission behavior of the internal combustion engine operated with the method according to the invention is further optimized.
  • the system pressure be raised to a value above the normal valve opening pressure before step a), so that the valve element opens against a pre-injection to a pre-injection at normal system pressure, and the system pressure then to a value below of the normal valve closing pressure is lowered so that the valve element closes.
  • the pilot injection carried out in this way therefore takes place at a relatively low system pressure and with a switching element which is in the starting position.
  • valve opening pressure Another possibility of increasing the valve opening pressure is to pressurize the valve element against the opening direction. This can be done in addition or as an alternative to the biasing element acting on the valve element. For this it is also proposed that the valve element be acted upon with the system pressure at a different time from the opening direction. The system pressure is in the area of the valve element anyway and can therefore be used without expensive measures to increase the valve opening pressure.
  • the present invention also relates to a pump-nozzle unit for 'supplying fuel into a combustion chamber of an internal combustion engine, with an injection nozzle for injecting the fuel ' into the combustion chamber, with at least one valve element which has at least a first pressure surface, the force resultant of which shows approximately in the opening direction of the valve element, with a biasing element which acts on the valve element in the direction of the closed position, with a switching element on which the biasing element is supported and which is movable along the direction of loading by the biasing element, with a pump device which one to the first Pressure area of the valve element acting system pressure builds up, and with a control device which controls the build-up and reduction of the system pressure.
  • Such a pump-nozzle unit is known from the market. As already stated at the beginning, it is used primarily in motor vehicle diesel internal combustion engines. In order to be able to achieve the most fuel-efficient and emission-optimized operation of the internal combustion engine with such a pump-nozzle unit, it is proposed according to the invention that the characteristic curve of the pretensioning device and the sizes of the pressure surfaces are matched to one another in such a way that the method of the type mentioned above is used with it can be carried out.
  • the switching element be a first Comprises pressure area and a second pressure area, the first pressure area of the switching element being smaller than the first pressure area on the valve element, the first pressure area and the second pressure area of the switching element being larger than the entire pressure area of the valve element, the first pressure area of the switching element always being included is connected to the pump device so that it is always acted upon by the system pressure, and the second pressure surface of the switching element is only connected to the pump device when the switching element has moved somewhat out of its initial position.
  • This ' pump-nozzle unit has a hysteresis between the system pressure at which the switching element moves out of the starting position and the system pressure at which the switching element moves back to the starting position. This increases the operational reliability of the pump-nozzle unit.
  • the pump-nozzle according to the invention is Einhei t I, the successive actuation of the switching element with the
  • a pretensioning device z u ⁇ which comprises a compression spring, is also particularly simple to implement.
  • a pressure space> is present between the valve element and the switching element, which is from a second pressure surface of
  • 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 in which a flow channel is provided in the switching element, which leads from the pressure chamber to the second pressure surface of the switching element.
  • the valve element can be used as an alternative or in addition to the pretension e.g. be acted upon by a hydraulic pressure by means of a compression spring, as a result of which the valve opening pressure or w. the valve closing pressure can be increased.
  • the application takes place in that the pressure space between the switching element and the valve element is fluidly connected to that pressure space which is delimited by the second pressure surface of the switching element. Hydraulic pressure is therefore not applied to the pressure chamber between the switching element and the valve element until the switching element has moved somewhat out of its initial position.
  • the flow channel comprises a flow restrictor.
  • the control device comprises a switching valve which can connect the pump device to a low-pressure area. It is hereby achieved that when the pumping device conveys fuel to the valve element, but an increase in the system pressure is not desired, the volume flow can be released in the direction of the low-pressure region and thus no system pressure builds up.
  • a particularly fast switching of such a switching valve is achieved if the switching valve has at least one P ' iezo element as an actuator.
  • valve opening pressures can be achieved.
  • the increased valve opening pressure is more than twice the normal valve opening pressure, more preferably it is 400 to 800 bar, still more preferably 700 to 800 bar.
  • Fig. 1 a schematic representation of a first
  • Fig. 2 a diagram in which the switching state of a
  • Control valve of the unit injector from Flg. 1 is shown over time;
  • Fig. 3 a diagram in which the course of the system pressure the pump-nozzle unit of Figure 1 is shown over time;
  • Fig. 4 a diagram in which the switching state of a
  • Switching element of the pump-nozzle unit of Figure 1 is plotted against time.
  • Fig. 5 a diagram in which the switching state of a
  • Valve element of the pump-nozzle unit of Figure 1 is plotted over time.
  • Fig. 6 a section of a second
  • Embodiment of a pump-nozzle unit Embodiment of a pump-nozzle unit
  • Fig. 7 a view similar to Fig. 6 of a third
  • Fig. 8 a view similar to Fig. 6 of a fourth
  • Embodiment of a pump-nozzle unit Embodiment of a pump-nozzle unit.
  • a 'first embodiment of a pump-nozzle unit carries in Fig. 1 overall by reference numeral 10. u ⁇ nankt a pump means 12, a nozzle device 14 and a controller 16.
  • the pump device 12 is a single-cylinder piston pump 18 which is driven by a cam 20.
  • the cam 20 is in turn coupled to the crankshaft of an internal combustion engine (not shown).
  • the pump device 12 conveys fuel via a line (not shown) to a reservoir 64 via a fuel line 22 to the nozzle device 14.
  • the nozzle device 14 comprises a housing 24, in which a stepped bore 26 is formed. In the stepped bore 26. a valve element 28 with a circular cylindrical cross section. The valve element 28 is movable along its longitudinal axis 29. An injection opening 30 is provided at the lower end of the housing 24.
  • the valve element 28 is pressed by a compression spring 32 against a valve seat (not visible) in the region of the injection opening 30.
  • the valve element 28 has a circumferential oblique first pressure surface 34, which is surrounded by an annular pressure space 36.
  • the pressure chamber 36 is in turn connected to the fuel line 22.
  • the end of the compression spring 32 remote from the valve element 28 is supported on a circular-cylindrical switching element 38.
  • the switching element 38 has a section 40. Facing the compression spring 32 with a constant diameter and a section 42 facing away from the compression spring 32, which tapers conically in the manner of a truncated cone.
  • the blunt tip of the conical section 42 forms a first pressure surface 44 of the switching element 38, whereas the oblique lateral surface of the conical section 42 of the switching element 38 forms a second pressure surface 46.
  • the switching element 38 In the starting position shown in Fig. 1, the switching element 38 is pressed by the compression spring 32. In this initial position, an upper region of the conical pressure surface 46 is located at an annular sealing edge 48 of the stepped bore '26th The area above the first pressure surface 44 of the switching element 38 forms a first pressure chamber 50, which is permanently fluidly connected to the fuel line 22 via a branch line 52. A second annular pressure chamber 51 is present between the housing 24 and the pressure surface 46.
  • the switching element 38 can move in the stepped bore 26 along the longitudinal axis 29 between the starting position shown in FIG. 1 and a switching position delimited by an annular web 54 pointing radially inwards. In this switching position, the sealing edge 48 no longer lies against the inclined pressure surface 46 of the switching element 38, so that the two pressure spaces 50 and 51 are connected to one another.
  • a branch line 56 branches off from the fuel line 22 and leads to the control device 16.
  • the control device 16 comprises a switching valve 60 which can be actuated by a piezo actuator 58 and which is connected on the output side to the fuel tank 64 via a low pressure line 62.
  • the piezo actuator 58 of the control device 16 is controlled by a control and regulating device, not shown in the figure. In an embodiment not shown, a magnetic actuator is used instead of a piezo actuator.
  • the pump-nozzle unit 10 shown in FIG. 1 is used for injecting fuel into the combustion chamber of an internal combustion engine.
  • a separate pump-nozzle unit 10 is provided for each combustion chamber (that is, for each cylinder) of the internal combustion engine.
  • the fuel can get into the combustion chamber of the internal combustion engine through a "triple injection". The method by which such a triple injection takes place is now explained with reference to FIGS. 2-5:
  • the cam 20 of the pump device 12 is synchronized with the crankshaft of the internal combustion engine in such a way that the single-cylinder piston pump always performs a delivery stroke during an injection stroke of the cylinder assigned to it.
  • the switching valve 60 is initially at the beginning of an injection cycle closed (rising edge 66 in Fig. 2). As can be seen from FIG. 3, this leads to an increase in the system pressure in the fuel line 22 and subsequently also in the pressure chamber 36 (rising edge 68 in FIG. 3).
  • the valve element 28 is pressed with a certain force against the corresponding 'valve seat in the region of the injection hole 30th As a result, a normal valve opening force is specified.
  • the increasing pressure in the pressure chamber 36 now acts on the pressure surface 34 on the valve element 28. If the force resulting therefrom exceeds the closing force exerted by the compression spring 32, i.e. if the normal valve opening pressure of the valve element 28 is exceeded, the valve element 28 lifts from the valve seat in the region of Injection opening 30 from ' and opens.
  • the normal valve opening pressure is shown in FIG. 3 by a dash-dotted curve and is identified by POVN.
  • the opening of the valve element 28 can be seen in FIG. 5 on the rising flank 70.
  • the pilot injection is ended by the switching valve 60 opening again (falling edge 72 in FIG. 2).
  • the system pressure in the fuel line 22 drops since it is now open to the fuel tank 64. This is shown by the falling edge 74 in FIG. 3.
  • the valve element 28 closes (falling edge 76 in FIG. 5) as soon as the system pressure P in FIG. 3 has dropped below a normal valve closing pressure PSW.
  • the valve closing pressure PSVN is shown in Fig. 3 by a double-dash line.
  • the switching valve 60 is closed again (rising edge 78 in FIG. 2).
  • the system pressure P increases accordingly
  • 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 detach from the sealing edge 48. This is again the case when the force emanating from the pressure surface 44 exceeds the prestressing force of the compression spring 32.
  • the starting position is denoted by SO
  • the switching position in which the switching element 38 rests on the ring land 54 is denoted by S1.
  • the characteristic curve of the spring 32 and the sizes of the pressure surfaces 34 and 44 are coordinated with one another in such a way that the valve closing pressure PSV is always below the system pressure P during this increase in the system pressure P.
  • the main injection is ended by the switching valve 60 being opened again, analogously to the end of the pre-injection. .,
  • the corresponding falling edges in Figures 2, 3 and 5, bear the reference numerals 88, '90 and 92.
  • the closing of the valve element 28 is caused by the fact that the system pressure P in Figure 3 under the elevated valve -. Drops closing pressure PSVH.
  • the drop in system pressure P is limited so that . a switching pressure PSS, at which the switching element 38 returns to its initial position SO, is not fallen below.
  • Post-injection is initiated again by closing the switching valve 60.
  • the corresponding flanks in FIGS. 2, 3 and 5 bear the reference symbols 94, 96 and 98.
  • the system pressure P again exceeds the increased valve opening pressure POVH, so that the valve element 28 opens again.
  • the increased valve opening pressure POVH is significantly above the normal valve opening pressure POVN, the post-injection takes place at a correspondingly high injection pressure.
  • Typical values for a normal valve opening pressure are approximately 300 bar, whereas the injection pressure for post-injection is approximately 500 to 600 bar due to the increased valve opening pressure POVH. ,
  • the entire injection sequence is ended by the switching valve 60 being opened again (falling edge 100 in FIG. 2).
  • the system pressure P now drops completely again and falls below the increased valve closing pressure PSVH (falling edge 102 in FIG. 3) and then also the closing switching pressure PSS for the switching element 38.
  • the valve element 28 thus closes first (falling edge -104 5), and then (if P ⁇ PSS) the switching element 38 also moves back to its starting position (falling edge 106 in FIG. 4).
  • Such post-injection at a relatively high injection pressure makes it possible to burn the fuel in the combustion chamber of the internal combustion engine in a manner that is optimal in terms of consumption and emissions.
  • Analpg to increase the pressures POV and PSV also ensures here that during the drop in the system pressure P the pressures POV and PSV are always above the system pressure P.
  • FIGS. 6-8 The differences between the exemplary embodiments shown in FIGS. 6-8 and the exemplary embodiment of a pump-nozzle unit 10 shown in FIG. 1 relate to the configuration of the switching element 38.
  • the switching element 38 formed area of the stepped bore 26 is not pressurized. In this case, only the pretensioning force, which is applied by the compression spring 32, acts on the valve element 28.
  • the area of the stepped bore 26 formed between the valve element 28 and the switching element 38 is designed as a pressure chamber 108, which communicates via a flow channel 110 with the pressure chamber 51 above the second pressure surface 46 of the switching element 38 connected is.
  • the flow channel is designed as a flat ground section 110 on the otherwise circular-cylindrical outer surface of the switching element 38.
  • a through-bore 110 designed as a flow restrictor through the switching element 38 passed. 8
  • the switching element 38 lifts off the sealing edge 48, so that the second pressure chamber 51 and the first pressure chamber 50 are connected to the fuel line 22 and thus the two pressure surfaces 44 and 46 system pressure P are applied.
  • Via the flow channel 110 of the fuel now flows in the between the switching element 38 and the valve member 28 - the formed pressure chamber 108 so that 'in this also a corresponding pressure through. builds up to system pressure P.
  • This pressure also acts on the pressure surface facing the compression spring 32 (not visible in FIGS. 6-8) of the valve element 28, so that in addition to the pretensioning force of the compression spring 32, a corresponding pressure force is applied.
  • valve opening pressure POV is raised again, so that a particularly high injection pressure of up to 800 bar can be achieved in these exemplary embodiments. If the pressure chamber 108 is also acted upon by the system pressure, there could be a risk that the hydraulic force resultant acting on the switching element 38 will become smaller than the force exerted on the switching element 38 by the pressure spring 32. In this case, the switching element 38 would move back to its starting position.
  • the system pressure does not increase further with the injection duration.
  • a lot is injected just as is requested via the piston (without reference number) of the single-cylinder piston pump 18.
  • the pressure here is in the range of the static opening pressure of the valve element 28.
  • the switching element 38 remains in its initial position. There is therefore no fluid connection between the pressure chamber 108 and the pressure chamber 50 or the fuel line 22. This means that the pressure chamber 108 is not pressurized.
  • transition area in which the switching element 38 has disengaged from its initial position, but the system pressure is set to a constant level above the switching pressure POS, it could happen, despite the throttling effect in the flow channel 110, that in the pressure chamber 10.8 on the one hand and in the pressure chambers 50 and 51- on the other hand there is the same pressure.
  • the area ratios between on the one hand the pressure chamber are selected in accordance with 50 and 51,108-facing surface of the switching element 38 and on the other hand the two pressure surfaces can. It is also possible that Cross section of the flow restrictor 110 to be chosen accordingly small.
  • This flow channel which has a corresponding flow throttling effect, ensures that the maximum pressure in the pressure chamber is always in a certain ratio to the system pressure. At relatively low pressure, a relatively low pressure would therefore also prevail in pressure chamber 108, whereas the pressure in Dr .uckraum 108 is correspondingly higher at high system pressure. This measure also prevents it from the switching element or the valve element comes through an unacceptably large increase in pressure in the pressure chamber 108 between the valve element and the Wegeleroent unwanted movements'.

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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)

Abstract

L'invention concerne une unité pompe-ajutage (10) servant à injecter du carburant dans la chambre de combustion d'un moteur à combustion interne. A cet effet, un élément de soupape (28) est ouvert par augmentation d'une pression du système à l'encontre d'une force de précontrainte. Pendant l'élévation de la pression du système, la force de précontrainte est également augmentée, notamment de sorte qu'une pression de fermeture de soupape augmentée en raison de la force de précontrainte augmentée, se situe toujours en dessous de la pression de système. Ladite pression du système est ensuite abaissée à une valeur située en dessous de la pression de fermeture de soupape, de sorte que l'élément de soupape (28) se ferme.
EP02727288A 2001-04-04 2002-04-04 Procede pour actionner une unite pompe-ajutage et unite pompe-ajutage correspondante Expired - Lifetime EP1377745B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10116635A DE10116635A1 (de) 2001-04-04 2001-04-04 Verfahren zum Betreiben einer Pumpe-Düse-Einheit sowie Pumpe-Düse-Einheit
DE10116635 2001-04-04
PCT/DE2002/001235 WO2002081900A1 (fr) 2001-04-04 2002-04-04 Procede pour actionner une unite pompe-ajutage et unite pompe-ajutage correspondante

Publications (2)

Publication Number Publication Date
EP1377745A1 true EP1377745A1 (fr) 2004-01-07
EP1377745B1 EP1377745B1 (fr) 2004-11-03

Family

ID=7680252

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02727288A Expired - Lifetime EP1377745B1 (fr) 2001-04-04 2002-04-04 Procede pour actionner une unite pompe-ajutage et unite pompe-ajutage correspondante

Country Status (4)

Country Link
US (1) US20040020458A1 (fr)
EP (1) EP1377745B1 (fr)
DE (2) DE10116635A1 (fr)
WO (1) WO2002081900A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003106836A1 (fr) * 2002-06-13 2003-12-24 Siemens Aktiengesellschaft Unite pompe-injecteur
DE10233101A1 (de) * 2002-07-20 2004-01-29 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
WO2004057176A1 (fr) * 2002-12-20 2004-07-08 Volkswagen Mechatronic Gmbh & Co. Kg Unite d'injecteur-pompe
DE102004057151B4 (de) * 2004-11-26 2009-04-16 Continental Automotive Gmbh Einspritzventil mit einem Druckhalteventil zur Fluiddruckbeaufschlagung eines Federraums

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9609382D0 (en) * 1996-05-03 1996-07-10 Lucas Ind Plc Fuel injection system

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO02081900A1 *

Also Published As

Publication number Publication date
WO2002081900A1 (fr) 2002-10-17
US20040020458A1 (en) 2004-02-05
DE10116635A1 (de) 2002-10-17
DE50201468D1 (de) 2004-12-09
EP1377745B1 (fr) 2004-11-03

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