EP1563183B1 - Multiplicateur de pression dont l'amortissement depend de la course - Google Patents

Multiplicateur de pression dont l'amortissement depend de la course Download PDF

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Publication number
EP1563183B1
EP1563183B1 EP03810367A EP03810367A EP1563183B1 EP 1563183 B1 EP1563183 B1 EP 1563183B1 EP 03810367 A EP03810367 A EP 03810367A EP 03810367 A EP03810367 A EP 03810367A EP 1563183 B1 EP1563183 B1 EP 1563183B1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
shaped
insert
booster
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
Application number
EP03810367A
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German (de)
English (en)
Other versions
EP1563183A1 (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

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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.
  • fuel injection systems come next pump-injector units, pump-line-nozzle units and storage injection systems are used.
  • Storage injection systems (common rail) advantageously make it possible to adapt the injection pressure to the load and speed of the internal combustion engine. In order to achieve high specific performance and to reduce emissions in the internal combustion engine, the highest possible injection pressure is generally required.
  • the achievable pressure level in storage injection systems used today is limited to about 1600 to 1800 bar.
  • this pressure intensifier is used.
  • EP 0 562 046 B1 discloses a control and valve arrangement with damping for an electronically controlled injection unit.
  • the actuation and valve assembly for a hydraulic unit comprises an electrically energizable electromagnet having a fixed stator and a movable armature.
  • the anchor has a first and a second surface.
  • the first and second surfaces of the armature define first and second cavities, with the first surface of the armature facing the stator.
  • the valve is capable of delivering a hydraulic actuating fluid to the injector from a sump.
  • a damping fluid may be collected or discharged therefrom with respect to one of the cavities of the solenoid assembly.
  • DE 199 10 970 A1 and DE 102 18 635.9 disclose fuel injection devices which each contain a pressure booster unit.
  • the pressure booster unit contains a working space and a differential pressure chamber, which is pressure-relieved for actuating the pressure booster unit.
  • the differential pressure chamber and the working space of the pressure booster unit are separated by a piston-shaped transmission element.
  • the pressure booster units known from DE 199 10 970 A1 and DE 102 18 635.9 are actuated by the pressure relief or pressurization of the differential pressure chamber, which is more favorable with regard to the settling losses occurring.
  • An abrupt pressurization of the high pressure chamber of the pressure booster unit with pressure relief of the differential pressure chamber of the pressure booster unit leads to immediate maximum pressure build-up according to the dimensions of the piston-shaped transmission element of the pressure booster unit.
  • the pressure booster unit therefore abruptly builds up the maximum pressure in the high-pressure chamber, which may be undesirable with regard to a representation of very small quantity injections into the combustion chamber of a self-igniting internal combustion engine, for example as part of a pre-injection.
  • a component already contained in the pressure booster which serves as the return spring support, can be used for stroke damping by introducing a throttle point into it.
  • a tight fit between the housing fixedly arranged now usable as a damping element stuntstellfederanschlag and relative to this movable piston-shaped pressure booster of the pressure booster can be ensured when driving the booster that through the throttle point a full compensation of the increase in volume from the working space of the booster in a damping chamber restricted occurs.
  • an example frusto-conical hydraulic surface can be provided on the piston-shaped pressure booster element of the booster. A part of the surface is enclosed by a ring region of the annular area of the return spring stopper which is now used as a damping element and encloses the piston-shaped pressure intensifying element. As a result, the entire surface of the pressure intensifying element, which limits the damping space below the damping element, is not acted on by the pressure prevailing in the working chamber of the pressure intensifier.
  • the piston-shaped pressure booster element of the booster travels with pressure relief of the differential pressure chamber with an end face in the high-pressure chamber of the booster, but a flow of fuel under increased fuel pressure from the high-pressure chamber due to this downstream hydraulic throttle cross-sections, z. B. holes, the combustion chamber side seat of the injection valve member and the injection holes at a lower pressure of the high-pressure chamber to a lesser extent. Consequently, the retraction movement, by which the pressure build-up in the high pressure chamber of the pressure intensifier takes place, is considerably slower in these.
  • the damping chamber assigning hydraulic surface of the piston-shaped pressure booster element acts.
  • This ensures that the maximum pressure in the high-pressure chamber of the pressure intensifier occurs only at fuel quantities that are greater than those required for a small number of pre-injections to be made fuel quantities.
  • This offers the advantage that on the one hand represent pilot injections with low injection quantity and low injection pressure, however, the full, according to the dimensions of the pressure booster achievable pressure increase for main injection phases can be used without restriction.
  • the pressure booster 1 shown in Figure 1 comprises a working space 2.
  • the working space 2 of the pressure booster 1 is acted upon by a high-pressure line 3 with high-pressure fuel.
  • the fuel source which supplies the high-pressure line 3 with the high-pressure fuel is not described in detail in the drawing. This may be, for example, a high-pressure delivery 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 be arranged above the fuel injector.
  • the inflow direction of the fuel under high pressure into the working space 2 of the pressure intensifier 1 is marked with reference numeral 4.
  • the pressure booster 1 comprises a piston-shaped pressure booster element 5.
  • the pressure booster element 5 separates the working chamber 2 of the pressure booster 1 from a differential pressure chamber 6.
  • the differential pressure chamber 6 is pressure-relieved via a control line 7 or pressurizable.
  • a control of fuel volume from the pressure chamber 6 by the operation of a switching valve, not shown in the drawing, for example, a solenoid valve or a piezoelectric actuator or the like.
  • the direction of flow of the fuel flowing out of the differential pressure chamber 6 is symbolized by the arrow pointing away from the control line 7, while the direction of inflow of fuel into the differential pressure chamber 6 during the return phase of the pressure booster element 5 of the booster 1 is indicated by the pointing to the control line 7 arrow.
  • the piston-shaped pressure intensifying element 5 of the pressure intensifier 1 comprises a lower end face 8, which enters into a high-pressure chamber of the pressure intensifier 1 identified by reference numeral 33. From the high-pressure chamber 33, a fuel volume under increased fuel pressure is displaced into a discharge line 9 when the piston-shaped pressure-boosting element 5 retracts.
  • the diversion line 9 may, for example, extend to a nozzle space which serves as a nozzle needle trained injection valve member of a fuel injector encloses. According to the position of the injection valve member which is generally movable in the vertical direction, the combustion chamber-side seat thereof is released or closed, so that injection of fuel under increased fuel pressure into the combustion chamber of the self-igniting internal combustion engine takes place or fails.
  • the housing 10 accommodating the pressure booster 1 may include a first housing part 10.1, which substantially 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 are along a housing division 16 to each other.
  • the wall of the working space 2 is identified by reference numeral 11 and is formed by the material of the first housing part 10.1 of the housing 10.
  • the piston-shaped pressure booster element 5 comprises a support disc 12 arranged in the upper region of the working space 2.
  • a return spring element 13 is supported on the support plate 12, which rest on a disc-shaped damping element 15 at its end opposite the support disc 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 received in a stationary manner in the first housing part 10.1 and is inserted into the first housing part 10.1 during the joining of the multi-part housing 10 into a recess above the dividing joint of the housing part 16.
  • the damping element 15 comprises an outer ring 19 and an inner ring 20. At the lower end of the outer ring 19 of the damping element 15 is an annular surface which is supported on the aforementioned 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 chamber 22 may by a z.
  • frusto-conical or flat running surface area 21 of the pressure booster element 5 are formed. The frusto-conical region 21, forming a hydraulically effective surface 32, is initially effective in the event of overflow of fuel from the working chamber 2 into the damping chamber 22.
  • a damper throttle 24 is provided.
  • the inner ring 20 of the damping element 15 covers an annular region 34 of the pressure booster element 5 which adjoins the frustoconical peripheral surface region 21 and acts hydraulically like the frusto-conical region 21.
  • the gap between the damping element 5 and the lateral surface of the Pressure booster element and in the ring area 34 there is a pressure undercutting, ie in the working chamber 2 and in the damping chamber 22, the same pressure prevails.
  • the self-adjusting gap leakage is small in comparison to the fuel volume flow, which flows over the cross section of the damper throttle 24.
  • a control edge 25 and a plurality of circumferentially of the piston-shaped pressure booster element 5 distributed arranged grinding surfaces 26 are provided.
  • the control edge 25 moves vertically downwards, so that over the stop surfaces 26, which may be oriented on the circumference of the piston-shaped pressure booster element 5 at an angle of 90 °, for example to each other , under high pressure fuel flows from the working space 2 in the damping chamber 22, d. H. the throttle point 24 in the damping element 15 becomes ineffective as the stroke of the pressure booster element 5 progresses.
  • the damping element 15 comprises a tightly tolerated bore 28, through which the piston-shaped pressure booster element 5 moves in pressure relief of the differential pressure chamber 6 according to its retraction direction 29; In addition, the damping element 15 is centered by the tight bore 28 on the pressure booster element 5.
  • the piston-shaped pressure-intensifying element 5 is guided within a guide section 30 in the second housing part 10.2 of the multi-part housing 10.
  • a the differential pressure chamber 6 limiting annular surface on the piston-shaped pressure booster element 5 is marked with reference numeral 31.
  • the operation of the pressure intensifier according to the drawing is as follows.
  • the working space 2 is filled with fuel.
  • the working space 2 of the pressure booster 1 prevails that can be built by the high pressure source or prevailing in the interior of a high-pressure accumulator fuel pressure.
  • About the control line 7 of the differential pressure chamber 6 and the Abêttechnisch 9 of the high-pressure chamber 33 of the booster 1 is also filled with fuel, which is under pressure, which builds a high-pressure pumping unit or a high-pressure accumulator. In the reproduced in the drawing position of the piston-shaped pressure booster element 5 of the booster 1, this is in its rest position.
  • the damper throttle 24 in the damping element 15 is a complete compensation of the increase in volume of the hydraulic chamber 22 in the movement of the piston-shaped pressure booster element 5 in the retraction 29, ie to a high-pressure chamber 33 of the booster 1, not possible.
  • the pressure booster 1 builds up less pressure within the high-pressure chamber 33.
  • the z. B. frusto-conical or planar surface 21 formed as a hydraulic surface 32 and the adjacent thereto annular surface 34 from the beginning of the movement of the pressure booster element 5 of the booster 1 effective, since the inner ring 20 of the annular insert formed as a damping element 15, the surface 34 releases.
  • the piston-shaped pressure boosting element 5 Due to the limited pressure build-up within the hydraulic chamber 22 acting as a damping chamber below the damping element 15, the piston-shaped pressure boosting element 5, which is acted upon by a smaller than the pressure prevailing in the working chamber 2, moves more slowly into the high-pressure chamber 33.
  • the high pressure chamber 33 of the pressure booster 1 Under increased pressure fuel flows into the discharge line 9 to a fuel injector, not shown in the drawing. This includes downstream of the high-pressure chamber 33, to the discharge line 9 subsequent holes, a nozzle seat at the combustion chamber end and injection openings, which act as hydraulic throttle cross-sections act. Therefore, at a lower pressure prevailing in the high-pressure space 33 than the design pressure of the booster 1, less amount flows.
  • the reduced pressure build-up within the hydraulic chamber 22 also moves the piston-shaped pressure booster element 5 more slowly into the high-pressure chamber 33.
  • the annular insert member 15 includes an outer ring 19 which laterally surrounds the return spring 13 supported on the surface 14 of the annular insert 15 so that it is always held in position on the annular insert 15.
  • the restoring spring 13 is supported on a disk surface 12 arranged on the piston-shaped pressure-intensifying element 5.
  • a stroke stop for the pressure boosting element 5 of the pressure booster 1 can also be realized by abutting the upper end of the pressure booster element 5 on the first housing part 10.1.
  • Figure 2 shows a variant of a stroke-dependent acting damping element.
  • annular insert 15 acting as a damping element this comprises an outer ring 19.
  • annular insert 35 (damping element) shown in FIG. 2
  • the annular insert 35 is configured substantially disc-shaped and is located within a recess 18 in the upper first housing part 10.1 of the booster 1 at.
  • the pressure-exerting element 5 acting on the return spring 13 is supported on the support surface 14 of the annular damping element 35 from.
  • the return spring 13 is centered by a contact surface 36 in the first housing part 10.1.
  • the design of the pressure-intensifying element 5 according to the illustration in FIG. 2 essentially corresponds to that of the pressure-intensifying element 5 according to FIG. 1, ie on the side of the pressure-intensifying element facing the annular insert 35 according to FIG 5 is a hydraulically effective surface 32, which is formed as a truncated cone-shaped surface 21 analogous to the representation of the pressure booster element 5 according to FIG.
  • the ring-shaped insert 35 comprises a bore 28 which surrounds the peripheral surface of the pressure-intensifying element 5 below the control edge 25. Above the control edge 25 5 free surfaces 26 are formed on the pressure booster element.
  • the inner ring 20 is absent 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-intensifying element 5 delimit the damping chamber 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)

Claims (12)

  1. Amplificateur de pression pour une installation d'injection de carburant comportant un élément amplificateur de pression (5) en forme de piston logé dans un boîtier (10) et séparant une chambre de travail (2) d'une chambre de pression différentielle (6) pouvant être reliée par une conduite de commande (7) à une source de haute pression ou être déchargée dans une zone basse pression, alors que l'élément amplificateur de pression (5) en forme de piston est sollicité par un ressort de rappel (13) qui s'appuie contre un insert annulaire (15) du boîtier (10),
    caractérisé en ce que
    l'insert (15, 35) comporte un organe d'étranglement d'amortissement (24) par lequel le carburant passe de la chambre de travail (2) de l'amplificateur de pression (1) en cas de décharge de pression de la chambre de pression différentielle (6) dans une chambre hydraulique (22).
  2. Amplificateur de pression selon la revendication 1,
    caractérisé en ce que
    la chambre hydraulique (22) est délimitée par une surface limite (23) de l'insert (15, 35) et une surface à effet hydraulique (32, 34) de l'élément amplificateur de pression (5) en forme de piston.
  3. Amplificateur de pression selon la revendication 1,
    caractérisé en ce que
    l'effet d'organe d'étranglement d'amortissement (24) est neutralisé après une certaine course de l'élément amplificateur de pression (5).
  4. Amplificateur de pression selon la revendication 2,
    caractérisé en ce que
    l'insert (15, 35) couvre une surface annulaire (34) de l'élément amplificateur de pression (5) en forme de piston, lorsque celui-ci est en position de repos, cette surface annulaire étant adjacente à la surface (32) à effet hydraulique.
  5. Amplificateur de pression selon la revendication 1,
    caractérisé en ce que
    l'insert (15) fonctionnant comme élément amortisseur comporte un anneau extérieur (19) et un anneau intérieur (20) délimitant un orifice de passage (28).
  6. Amplificateur de pression selon la revendication 5,
    caractérisé en ce que
    l'anneau extérieur (19) est soutenu par la surface d'appui (17) d'une partie (10.2) du boîtier (10).
  7. Amplificateur de pression selon la revendication 5,
    caractérisé en ce que
    l'anneau extérieur (19) est logé dans une cavité d'une paroi (11) de la chambre de travail (2) de l'amplificateur de pression.
  8. Amplificateur de pression selon les revendications 1 et 3,
    caractérisé en ce que
    l'élément amplificateur de pression (5) en forme de piston comporte une arête de commande (25) couverte en position de repos de l'élément amplificateur de pression (5) en forme de piston par l'insert (15, 35).
  9. Amplificateur de pression selon la revendication 8,
    caractérisé en ce que
    l'élément amplificateur de pression (5) en forme de piston comporte des surfaces de dégagement (26) adjacentes à l'arête de commande (25) et la surface enveloppe de l'élément amplificateur de pression (5) sert de moyen de guidage et/ou de centrage du ressort de rappel (13) au niveau des surfaces de dégagement (26).
  10. Amplificateur de pression selon la revendication 9,
    caractérisé en ce que
    les surfaces de dégagement (26) sont réalisées sous la forme de parties meulées de l'élément amplificateur de pression (5) en forme de piston.
  11. Amplificateur de pression selon la revendication 9,
    caractérisé en ce que
    les surfaces de dégagement (26) s'étendent dans la chambre de travail (2).
  12. Amplificateur de pression selon la revendication 1,
    caractérisé en ce que
    l'insert (35) fonctionnant comme élément amortisseur est en forme de rondelle intégrée dans une cavité (18) d'une première partie (10.1) du boîtier (10).
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 EP1563183A1 (fr) 2005-08-17
EP1563183B1 true 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

Family Cites Families (11)

* Cited by examiner, † Cited by third party
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
KR100203322B1 (ko) * 1991-10-11 1999-06-15 매리 제이 캘라한 전자 제어식 분사기용 댐핑 작동기 및 밸브 조립체
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
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
WO2002092997A1 (fr) * 2001-05-17 2002-11-21 Robert Bosch Gmbh Systeme d'injection de carburant

Also Published As

Publication number Publication date
WO2004042223A1 (fr) 2004-05-21
JP2006505733A (ja) 2006-02-16
EP1563183A1 (fr) 2005-08-17
DE10251679A1 (de) 2004-05-19
US20060048751A1 (en) 2006-03-09
DE50304682D1 (de) 2006-09-28

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