EP1563183A1 - Multiplicateur de pression dont l'amortissement depend de la course - Google Patents

Multiplicateur de pression dont l'amortissement depend de la course

Info

Publication number
EP1563183A1
EP1563183A1 EP03810367A EP03810367A EP1563183A1 EP 1563183 A1 EP1563183 A1 EP 1563183A1 EP 03810367 A EP03810367 A EP 03810367A EP 03810367 A EP03810367 A EP 03810367A EP 1563183 A1 EP1563183 A1 EP 1563183A1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
reinforcement element
drain
shaped
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
EP03810367A
Other languages
German (de)
English (en)
Other versions
EP1563183B1 (fr
Inventor
Christian Grimmiger
Andreas Kellner
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 EP1563183A1 publication Critical patent/EP1563183A1/fr
Application granted granted Critical
Publication of EP1563183B1 publication Critical patent/EP1563183B1/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
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • 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
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric operating means

Definitions

  • Both pressure-controlled and stroke-controlled injection systems can be used to supply the combustion chambers of self-igniting ner internal combustion engines with fuel.
  • accumulator injection systems are also used as fuel injection systems.
  • Accumulator injection systems (common rail) advantageously allow the injection pressure to be adapted to the load and speed of the ner focal plane. In order to achieve high specific outputs and to reduce emissions in the internal combustion engine, the highest possible injection pressure is generally required.
  • This pressure booster is used to further increase the pressure in accumulator injection systems.
  • EP 0 562 046 B1 discloses an actuating and valve arrangement with damping for an electronically controlled injection unit.
  • the actuating and valve arrangement for a hydraulic unit has an electrically excitable electromagnet with a fixed stator and a movable connector.
  • the anchor has a first and a second surface.
  • the first and second surfaces of the armature define first and second cavities, the first surface of the armature facing the stator.
  • a valve is provided which is connected to the armature.
  • the valve is capable of delivering a hydraulic actuating fluid to the injector from a sump.
  • a damping fluid can be collected there with respect to one of the cavities of the electromagnet arrangement or can be discharged again from there.
  • DE 199 10 970 AI and DE 102 18 635.9 show fuel injection devices, each of which contains a pressure transmission unit.
  • the pressure translation unit contains a work space and a differential pressure space which can be depressurized to actuate the pressure translation unit.
  • the differential pressure space and the working space of the pressure translation unit are separated from one another by a piston-shaped translation element.
  • the pressure translation units known from DE 199 10 970 AI and DE 102 18 635.9 are actuated by the pressure relief or pressurization of the differential pressure space, which is more favorable with regard to the decompression losses that occur.
  • An abrupt pressurization of the high-pressure space of the pressure translation unit with pressure relief of the differential pressure space of the pressure translation unit leads to an immediate build-up of maximum pressure in accordance with the dimensioning of the piston-shaped translation element of the pressure translation unit.
  • the pressure translation unit therefore abruptly builds up the maximum pressure in the high-pressure chamber, which can be undesirable with regard to the display of small-volume injections into the combustion chamber of a self-igniting internal combustion engine, for example as part of a pre-injection.
  • a component which is already contained in the pressure booster and which serves to support the return spring can be used for stroke damping by introducing a throttle point therein.
  • the return spring stop which is now fixed to the housing and can be used as a damping element
  • the piston-shaped pressure amplification element of the pressure booster which can be moved relative to this, it can be ensured when the pressure booster is actuated that the throttle point completely compensates for the volume increase from the working area of the pressure booster in a damping space is restricted.
  • a hydraulic surface for example in the shape of a truncated cone, can be provided on the piston-shaped pressure reinforcement element of the drain amplifier.
  • the piston-shaped pressure booster element of the pressure booster travels with one end face into the high-pressure chamber of the pressure booster when the differential pressure chamber is relieved of pressure, but there is an outflow of fuel under increased fuel pressure from the high-pressure chamber due to the downstream hydraulic throttle cross-sections, e.g. B. holes, the combustion chamber side seat of the injection valve member and the spray holes at a lower pressure on the high pressure chamber to a lesser extent.
  • the retraction movement through which the pressure builds up in the high-pressure chamber of the pressure booster, runs considerably slower in the booster.
  • a control edge provided on the latter in the region of the damping element ensures that, when it is opened, the working pressure present in the working space of the pressure booster in the damping chamber below the ring-shaped damping element applies to the entire damping chamber the hydraulic surface of the piston-shaped pressure intensifying element. It is thereby achieved that the maximum pressure in the high-pressure chamber of the pressure intensifier only occurs with fuel quantities that are greater than those that require the fuel quantities required for a small number of pre-injections.
  • pre-injections with a small injection quantity and low injection pressure can be represented, but the full pressure increase that can be achieved in accordance with the dimensioning of the pressure booster can be used without restriction for main injection phases.
  • Figure 1 shows a section through the pressure booster proposed according to the Invention with integrated, stroke-dependent damping element
  • Figure 2 shows an embodiment of a stroke-dependent damping element.
  • the pressure booster 1 shown in FIG. 1 comprises a work space 2.
  • the work space 2 of the pressure booster 1 is acted upon by a high-pressure line 3 with fuel under high pressure.
  • the fuel source that supplies the high-pressure fuel to the high-pressure line 3 is not described in more detail in the drawing.
  • This can be, for example, a high-pressure conveyor unit or a high-pressure storage space (common rail).
  • the pressure booster 1 shown in section in the drawing can be integrated in the injector body of a fuel injector and preferably arranged above the fuel injector.
  • the inflow direction of the fuel under high pressure into the working space 2 of the drain amplifier 1 is marked with reference number 4. '
  • the pressure booster 1 comprises a piston-shaped pressure boosting element 5.
  • the pressure boosting element 5 separates the working space 2 of the pressure booster 1 from a differential pressure chamber 6.
  • the differential pressure chamber 6 can be depressurized or pressurized via a control line 7. " Fuel volume from pressure chamber 6 is deactivated by actuating a switching valve (not shown in the drawing), for example a solenoid valve or a piezo actuator or the like. The direction of flow of the fuel flowing out of differential pressure chamber 6 is symbolized by the arrow pointing away from control line 7, while the direction of flow of fuel into the differential pressure chamber 6 is indicated by the arrow pointing to the control line 7 during the reset phase of the pressure amplification element 5 of the pressure amplifier 1.
  • the piston-shaped drain reinforcement element 5 of the drain amplifier 1 comprises a lower end face 8, which moves into a high-pressure chamber of the pressure amplifier 1 identified by reference numeral 33.
  • a fuel volume under increased fuel pressure is displaced from the high-pressure chamber 33 into a control line 9.
  • the diverter line 9 can extend, for example, to a nozzle chamber which is a encloses a needle injector member of a fuel injector.
  • the injection valve element which is generally movable in the vertical direction, its seat on the combustion chamber side is released or closed, so that fuel under increased fuel pressure is injected into the combustion chamber of the self-igniting internal combustion engine or is omitted.
  • the housing 10 accommodating the pressure booster 1 can contain a first housing part 10.1, which essentially encloses the working space 2, and a further housing part 10.2.
  • the two housing parts 10.1 and 10.2 of the housing 10 rest against one another along a housing division 16.
  • the wall of the working space 2 is identified by reference numeral 1 1 and is formed by the material of the first housing part 10.1 of the housing 10.
  • the piston-shaped drain reinforcing element 5 comprises a support disk 12 arranged in the upper region of the working space 2.
  • a restoring spring element 13 is supported on the support disk 12 and rests on a disk-shaped damping element 15 with its end opposite the support disk 12.
  • the damping element comprises a support surface 14 on which the return spring 13 rests.
  • the damping element 15 is supported along an attachment surface 17 on the second housing part 10.2 of the housing 10. It is accommodated in a stationary manner in the first housing part 10.1 and is inserted into the first housing part 10.1 when the multi-part housing 10 is joined into a recess above the dividing joint of the housing division 16.
  • the damping element 15 comprises an outer ring 19 and an inner ring 20.
  • a lower end of the outer ring 19 of the damping element 15 is an annular surface which is supported on the already mentioned attachment surface 17 of the damping element 15 on the second housing part 10.2.
  • the damping element 15 further comprises a boundary surface 23 which delimits a damping space 22.
  • a further limitation of the damping space 22 can be achieved by a z.
  • frustoconical or planar surface area 21 of the pressure reinforcing element 5 are formed. The frustoconical region 21, which forms a hydraulically effective surface 32, is initially effective when fuel flows over from the working chamber 2 into the damping chamber 22.
  • a damper throttle 24 is provided penetrating the damping element 15, ie penetrating its support surface 14.
  • the inner ring 20 of the damping element 15 covers an annular region 34 of the pressure reinforcing element 5 which adjoins the frustoconical peripheral surface area 21 and which acts hydraulically like the frustoconical region 21.
  • the gap between the damping element 5 and the lateral surface of the Pressure amplification element and in the ring area 34 there is a drain underneath, ie the same pressure prevails in the working space 2 and in the damping space 22.
  • the gap leakage that occurs is small in comparison to the fuel volume flow that flows over the cross section of the damper throttle 24.
  • a control edge 25 and a plurality of abutment surfaces 26 arranged on the circumference of the piston-shaped drain reinforcement element 5 are provided.
  • the control edge 25 moves vertically downward, so that the contact surfaces 26, for example, orientate one another at an angle of 90 ° on the circumference of the piston-shaped pressure reinforcing element 5 can be fuel under high pressure flows from the working space 2 into the damping space 22, d. H. the throttling point 24 in the damping element 15 becomes ineffective as the stroke of the drain reinforcing element 5 progresses.
  • the damping element 15 comprises a closely tolerated bore 28 through which the piston-shaped drain reinforcement element 5 moves in accordance with its direction of retraction 29 when the differential pressure chamber 6 is relieved of pressure; In addition, the damping element 15 is centered on the drain reinforcing element 5 through the narrow-tolerance bore 28.
  • the piston-shaped drain reinforcing element 5 is guided within a guide section 30 in the second housing part 10.2 of the housing 10 which is formed in several parts.
  • An annular surface delimiting the differential pressure space 6 on the piston-shaped drain reinforcement element 5 is marked with reference number 31.
  • the mode of operation of the pressure booster according to the drawing is as follows.
  • the working space 2 is filled with fuel via the high-pressure connection 3.
  • the working space 2 of the drain booster 1 there is the fuel pressure that can be built up by the high-pressure source or that prevails in the interior of a high-pressure accumulator.
  • the high pressure chamber 33 of the pressure booster 1 is also filled with fuel which is under the pressure that a high-pressure delivery unit or a high-pressure storage chamber builds up.
  • the position of the piston-shaped drain reinforcement element 5 of the pressure booster 1 shown in the drawing this is in its rest position.
  • the control edge 25 on the piston-shaped drain reinforcement element 5 is covered by the inner ring 20 of the damping element 15, which is designed as an annular insert, so that the free surfaces that can be configured as contact surfaces extend into the working space 2 26 are closed. Furthermore, an annular surface 34 adjacent to the, for example, frustoconical surface 21 of the piston-shaped drain reinforcement element 5 is covered by the inner ring 20 of the damping element 15.
  • the fuel entering the damping space 22 via the damper throttle 24 of the damping element 15 from the working space 2 of the pressure booster 1 fills the damping space 22 and also ensures the fuel pressure that can be built up by the high-pressure source or prevails in the interior of a high-pressure fuel accumulator.
  • the pressure booster 1 is balanced out and is held in its initial position by the return spring element 13.
  • the pressure in the differential pressure chamber 6 decreases. Due to the high pressure that continues to prevail in the working space 2, applied by a high-pressure delivery unit (not shown) or a high-pressure storage space (common rail), the drain reinforcement element 5 begins to move downward and the fuel in the high-pressure space 33 and with it via the connection 9 connected rooms, e.g. B. a nozzle space to compress. Because of the increase in volume in the damping chamber 22, there is a gradual reduction in pressure, since the fuel entering the hydraulic chamber 22 from the working chamber 2 of the drain booster 1 is throttled in accordance with the dimensioning of the damper throttle 24.
  • the piston-shaped drain reinforcement element 5 Due to the limited pressure build-up within the hydraulic space 22 acting as a damping space below the damping element 15, the piston-shaped drain reinforcement element 5, which is acted upon by a pressure lower than the pressure prevailing in the working space 2, moves more slowly into the high-pressure space 33.
  • Fuel under increased pressure flows from the high-pressure chamber 33 of the pressure booster 1 into the control line 9 to a fuel injector (not shown in the drawing). Downstream of the high-pressure chamber 33, this comprises bores adjoining the control line 9, a nozzle seat at the end on the combustion chamber side, and injection openings which act as hydraulic throttles. act as cross sections. Therefore, at a lower pressure prevailing in the high-pressure chamber 33 than the design pressure of the pressure booster 1, less amount flows out.
  • the reduced pressure build-up within the hydraulic space 22 also moves the piston-shaped drain reinforcement element 5 more slowly into the high-pressure space 33.
  • the control edge 25 When a stroke distance defined by the position of the control edge 25 on the circumference of the piston-shaped drain reinforcement element 5 is exceeded, the control edge 25 extends out of the bore 28 of the damping element 15.
  • the free surfaces 26, which adjoin the control edge 25 and are formed on the circumference of the piston-shaped drain reinforcement element 5, allow fuel to flow from the working space 2 of the drain amplifier into the hydraulic space 22, which increases continuously due to the movement of the piston-shaped drain reinforcement element 5 in the direction of the pillar 29
  • the damper throttle 24 becomes ineffective due to the release of the free areas 26, the fuel flows unhindered into the hydraulic space 22 via the bore 28.
  • the working pressure in the hydraulic chamber 22 is applied to the pressure-relieved differential pressure chamber 6 in accordance with the retraction movement 29 of the piston-shaped drain reinforcement element 5 and thus acts on the entire end face, including the surface 34 previously covered by the inner ring 20 of the damping element 15. This increases the pressure in the high pressure space 33 to the design pressure. However, the complete build-up of pressure within the high-pressure space 33 takes place only after the quantity of fuel required for pre-injections has already flowed out of it into the control line 9 to the fuel injector (not shown in the drawing).
  • the design pressure of the pressure booster acts on the piston-shaped drain reinforcement element 5, which due to the dimensioning of the hydraulically effective surfaces 21 and 34, the dimensioning of the surface of the drain reinforcement element 5, the of the bore 28 is surrounded, is predetermined.
  • the surface of the pressure reinforcing element 5, which is surrounded by the bore 28, is always acted upon by the pressure prevailing in the working space 2.
  • the annular insert element 15 comprises an outer ring 19 which laterally surrounds the return spring 13 which is supported on the surface 14 of the annular insert 15, so that it is always held in position on the annular insert 15.
  • the return spring 13, on the other hand, is supported on a disk surface 12 arranged on the piston-shaped pressure reinforcing element 5.
  • the recess 18 on the damping element forms the upper stroke stop of the drain reinforcement element 5.
  • a plub stop for the drain reinforcement element 5 of the pressure booster 1 can also be realized by striking the upper end of the drain reinforcement element 5 on the first housing part 10.1.
  • Figure 2 shows an embodiment of a stroke-dependent damping element.
  • the annular insert 15 acting as a damping element according to FIG. 2 it comprises an outer ring 19.
  • the outer ring has been eliminated.
  • the ring-shaped insert 35, as shown in FIG. 2 is configured essentially in the form of a disk and lies within a recess 18 in the upper first housing part 10.1 of the drain amplifier 1.
  • the return spring 13 acting on the drain reinforcement element 5 is supported on the support surface 14 of the annular damping element 35.
  • the return spring 13 is centered by a contact surface 36 in the first housing part 10.1.
  • the configuration of the drain reinforcement element 5 as shown in FIG. 2 essentially corresponds to that of the drain reinforcement element 5 according to FIG. 1, ie on the side of the drain reinforcement facing the annular insert 35 according to FIG. Kungsiatas 5 is a hydraulically effective surface 32, which is designed analogous to the representation of the drain reinforcing element 5 according to Figure 1 as a frustoconical surface 21.
  • the first housing part 10.1 and the second housing part 10.2 abut one another along a housing division 16.
  • the ring-shaped insert 35 comprises a bore 28 which surrounds the peripheral surface of the drain reinforcing element 5 below the control edge 25. Above the control edge 25, free surfaces 26 are formed on the drain reinforcement element 5.
  • the inner ring 20 is missing from the annular insert 35, so that the underside of the disk-shaped insert (damping element 35) and the upper end face of the pressure-reinforcing element 5 limit the damping space 22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un multiplicateur de pression conçu pour un dispositif d'injection de carburant, comprenant un élément de multiplication de pression en forme de piston (5) qui est disposé dans un logement (10) et sépare une chambre de travail (2) d'une chambre de pression différentielle (6). Cette chambre de pression différentielle (6) peut être reliée à une source haute pression par l'intermédiaire d'une ligne pilote (7) ou subir une décompression pour atteindre un niveau basse pression. L'élément de multiplication de pression en forme de piston (5) est soumis à l'action d'un ressort de rappel (13). Ce ressort de rappel (13) repose contre un insert annulaire (15) au sein dudit logement (10). Un papillon (24) est ménagé dans cet insert annulaire (15) et est traversé par le carburant qui provient de la chambre de travail (2) du multiplicateur de pression (1) et se dirige vers une chambre hydraulique (22) lors de la décompression de la chambre de pression différentielle (6).
EP03810367A 2002-11-07 2003-07-10 Multiplicateur de pression dont l'amortissement depend de la course Expired - Lifetime EP1563183B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10251679 2002-11-07
DE10251679A DE10251679A1 (de) 2002-11-07 2002-11-07 Druckverstärker mit hubabhängiger Bedämpfung
PCT/DE2003/002312 WO2004042223A1 (fr) 2002-11-07 2003-07-10 Multiplicateur de pression dont l'amortissement depend de la course

Publications (2)

Publication Number Publication Date
EP1563183A1 true EP1563183A1 (fr) 2005-08-17
EP1563183B1 EP1563183B1 (fr) 2006-08-16

Family

ID=32115300

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03810367A Expired - Lifetime EP1563183B1 (fr) 2002-11-07 2003-07-10 Multiplicateur de pression dont l'amortissement depend de la course

Country Status (5)

Country Link
US (1) US20060048751A1 (fr)
EP (1) EP1563183B1 (fr)
JP (1) JP2006505733A (fr)
DE (2) DE10251679A1 (fr)
WO (1) WO2004042223A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005007543A1 (de) * 2005-02-18 2006-08-24 Robert Bosch Gmbh Kraftstoffinjektor mit direkter Nadelsteuerung für eine Brennkraftmaschine
DE102006038840A1 (de) * 2006-08-18 2008-02-21 Robert Bosch Gmbh Kraftstoffinjektor mit Kolbenrückholung eines Druckübersetzerkolbens
FI122557B (fi) * 2009-04-02 2012-03-30 Waertsilae Finland Oy Mäntämoottorin polttoaineenruiskutusjärjestely

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Publication number Priority date Publication date Assignee Title
JPS61261653A (ja) * 1985-05-16 1986-11-19 Nippon Soken Inc 燃料供給装置
US4948049A (en) * 1989-02-24 1990-08-14 Ail Corporation Rate control in accumulator type fuel injectors
DE69121904D1 (de) * 1991-10-11 1996-10-10 Caterpillar Inc Gedämpfte betätigungs- und ventilanordnung für eine elektronisch-gesteuerte einspritzeinheit
US5894992A (en) * 1995-03-31 1999-04-20 Cummins Engine Company, Inc. Hydraulically actuated fuel injector with injection rate shaping pressure intensifier
JP3783266B2 (ja) * 1996-02-09 2006-06-07 いすゞ自動車株式会社 内燃機関の燃料噴射装置
DE19848904A1 (de) * 1998-10-23 2000-04-27 Hydraulik Ring Gmbh Druckstufe zur Regulierung einer Voreinspritzmenge von Kraftstoff in Verbrennungsmotoren, vorzugsweise in Dieselmotoren
DE19910970A1 (de) * 1999-03-12 2000-09-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung
JP3555588B2 (ja) * 2001-03-23 2004-08-18 トヨタ自動車株式会社 コモンレール式燃料噴射装置
US6805101B2 (en) * 2001-05-17 2004-10-19 Robert Bosch Gmbh Fuel injection device
DE10123911A1 (de) * 2001-05-17 2002-11-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung mit Druckübersetzungseinrichtung und Druckübersetzungseinrichtung
DE10218635A1 (de) * 2001-05-17 2002-11-28 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004042223A1 *

Also Published As

Publication number Publication date
US20060048751A1 (en) 2006-03-09
EP1563183B1 (fr) 2006-08-16
JP2006505733A (ja) 2006-02-16
WO2004042223A1 (fr) 2004-05-21
DE50304682D1 (de) 2006-09-28
DE10251679A1 (de) 2004-05-19

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