EP0906506B1 - Pompe d'injection de carburant pour moteur a combustion interne - Google Patents

Pompe d'injection de carburant pour moteur a combustion interne Download PDF

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Publication number
EP0906506B1
EP0906506B1 EP98907857A EP98907857A EP0906506B1 EP 0906506 B1 EP0906506 B1 EP 0906506B1 EP 98907857 A EP98907857 A EP 98907857A EP 98907857 A EP98907857 A EP 98907857A EP 0906506 B1 EP0906506 B1 EP 0906506B1
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EP
European Patent Office
Prior art keywords
pressure
groove
fuel injection
moving part
injection pump
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
EP98907857A
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German (de)
English (en)
Other versions
EP0906506A1 (fr
Inventor
Karl-Friedrich Ruesseler
Bernhard Bonse
Wolfgang Braun
Dieter Junger
Joachim Kurz
Roland Gronenberg
Hubert Greif
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Publication of EP0906506A1 publication Critical patent/EP0906506A1/fr
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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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor

Definitions

  • DE-C-24 49 332 is a fuel injection pump known of this type, which has a pump piston, which in a housing bore back and forth and at the same time is driven in rotation.
  • the outlet opening on the pump piston serves as a distributor opening, one after the other various pressure lines supplied with high pressure fuel become.
  • this known fuel injection pump is about a longitudinal groove opposite the distributor opening arranged in the outer surface of the pump piston, which in constant connection with the high pressure of the distributor opening supplied fuel is.
  • This configuration has the disadvantage that despite a balance of forces, which is achieved on the pump piston by the large-area grooves in the lateral surface of the moving part there is an interruption in a film of lubricating oil, which Oil film the moving part, the pump piston and Distributor is at the same time, when it rotates in the housing bore should wear.
  • the fuel injection pump according to the invention with the features of the characterizing part of claim 1 has the opposite the advantage that the pressure compensation surface according to the invention one from the rotational position of the moving part independent compensation force is generated because of the pressure compensation area always remains closed. It can the pressure that is in the area of the pressure equalization area and that of the outlet pressure of the high pressure source at the adjacent outlet opening, by the dimensioning of the first and the second leak distance in the desired Way to be set.
  • This configuration has further the advantage that in the area of the outlet opening high pressure occurring in the wake of the intermittent high-pressure fuel injection due to the deformation of the moving part on the one hand and the housing bore, on the other hand, the size of the leakage distances, in particular their effective flow cross-section so influenced is that a discharge cross-section over the second leak reduced and an inlet cross-section over the first Leakage distance is increased.
  • the deformation the moving part and this is the receiving housing bore lower.
  • These deformations are in the moving part Flattening of the circular cross-section in the direction of a elliptical cross-section and in the housing bore Boreholes also with an elliptical cross-section, with the main axes of the respective cross sections are perpendicular to each other.
  • this Deformation also results in lower cross contractions or transverse extensions transverse to the triggering deformation, see above that a smaller game between the moving part and the Housing bore in the basic dimension of these parts to each other is feasible.
  • Improved with reducing this game the quantity balance of the high pressure injection, in which the leakage losses caused by this game are reduced become. This is done with continued safe operation without the risk of being too tight an excessive surface pressure between the assigned Sharing occurs, with the result of eating the moving Partly in the housing bore.
  • An advantageous embodiment is according to claim 2 second leak distance essentially twice as long as that first leak distance, which is a favorable volume balance of the Pressure equalization area inflowing high pressure fuel and fuel flowing out again from this pressure compensation surface to a relief room. With the length of the Leakage distances and the resulting cross-sections that arises in the area of the pressure compensation area Set pressure.
  • the invention Solution in a distributor injection pump according to claim 3 realized.
  • the Pressure compensation areas advantageous according to claim 4 as a longitudinal groove or extending in a longitudinal direction to the axis of the rotating moving part extending flattening or ground surface.
  • the length of this Longitudinal groove can advantageously the pressure field in the area Pressure equalization area can be determined and it is one Pressure equalization area in a manufacturing and realization relief between otherwise existing ones high pressure grooves or pressure relief grooves in the area to accommodate the outer surface of the moving part.
  • a further Groove provided, the main setting the desired gap length in favorable for this setting Areas of the lateral surface is used.
  • the pressure equalization area relatively isolated far from the high pressure Outlet opening must be removed and over the further groove or groove-like flattening up to a desired proximity to this outlet opening is sufficient to to define the first leak distance there.
  • Can also over this continued groove also corresponds to a leakage length be set to a discharge side.
  • the partial extent of the pressure compensation surface according to claim 5 substantially parallel to a radial plane to the axis of the moving part made what enables the pressure equalization area if possible to accommodate in the peripheral area of the lateral surface, in which the outlet opening is also provided under Taking into account that during the back and forth Movement of the pump piston not the pressure compensation grooves Range of relief openings from the housing bore come off, get.
  • the distributor opening according to claim 7 designed as a longitudinal groove
  • the further groove which is from the pressure compensation surface dissipates, is formed as a partial groove, which is in the axial direction ends below or above the distributor longitudinal groove and defines the first leak distance there.
  • the second Leakage path through the pressure equalization area and yourself also formed in the circumferential direction, the one with a relief chamber of the fuel injection pump connected is.
  • FIG. 1 shows a fuel injection pump shown in section and simplified
  • Figure 2 a distributor piston, in the view as in the pump 1 is used
  • FIG. 3 is a section along the line III - III through the distributor piston according to FIG. 2
  • 4 shows a development of the distributor piston according to FIG.
  • Figure 5 shows a section through the Pump piston along the line V - V of Figure 2 and the this receiving housing part with housing bore
  • Figure 6 a second embodiment of the invention using a Development of the pump piston
  • Figure 7 shows a third embodiment of the invention, shown on a settlement of Pump piston
  • Figure 8 shows a fourth embodiment the invention with an additional annular groove.
  • a distributor pump piston 6 in its axial bore 5 is guided by a cam drive, not shown both in a reciprocating and a rotating Movement.
  • a cam drive not shown both in a reciprocating and a rotating Movement.
  • the movement of the distributor pump piston changes one side pump work space enclosed by him in the cylinder sleeve 4 8 such that this space during the downward stroke of Pump piston, which is also a suction stroke is enlarged and in the upward stroke of the pump piston corresponding to one Conveying stroke is reduced with the promotion of this Pump work chamber 8 fuel brought to high pressure.
  • the distributor pump piston has one of its Front 9 outgoing conveyor channel 10, in the lateral surface 11 of the distributor pump piston in a distributor opening 12 as the outlet opening of the pump work space 8 empties.
  • This distributor opening is preferably a longitudinal groove executed.
  • the distributor opening comes during its rotation each with a delivery stroke of the pump piston of several pressure lines 14 in connection, each as an injection line to a fuel injection valve 15 lead and according to the fuel injectors to be supplied distributed around the circumference of the inner surface the axial bore 5 are arranged.
  • a delivery valve 17 is preferably provided, e.g. as Equal pressure valve or as a valve with a valve member a continuously open throttle connection between the fuel injector and has fuel injection pump.
  • a filling groove 18 in the lateral surface 11 of the Pump piston 6 is provided, which via a longitudinal channel 19 in Distributor pump piston 6 with an annular groove 20 in the outer surface of the distributor pump piston is connected.
  • This Ring groove is with a relief bore 22 in the cylinder sleeve connected in a pump suction chamber 24 of the Fuel injection pump that flows through one out of one Fuel tank 27 suction feed pump 25 is supplied if necessary with the interposition of a further pre-feed pump.
  • a pressure control valve 26 which is parallel to the feed pump 25 is arranged, the pressure in the pump suction chamber set.
  • the part of the non-fuel injection participating Fuel is controlled by means of a solenoid valve 29, whose valve member 30 has a connecting bore 31 between pump work chamber 8 and one to pump suction chamber 24 leading suction channel 32 when lifting off the valve seat of the Manufactures solenoid valve.
  • This connection serves on the one hand for filling the pump workspace during the suction stroke of the pump piston and on the other hand, as already mentioned, for relief the pump workspace over a certain, defined Pump piston stroke. This can be done before the actual Pump piston stroke with effective delivery are defined the start of fuel injection and also after injection a desired fuel injection quantity to determine of the high pressure injection end.
  • the solenoid valve is thereby electrically controlled by a control device 34.
  • Figure 1 shows the known design of the distributor injection pump with a solenoid valve for injection quantity control.
  • an embodiment according to the invention is only visible in Figure 2.
  • the distributor groove 12 and the filling groove are designed as longitudinal grooves.
  • the pressure compensation surface 36 is also longitudinal groove-like, e.g. executed in the form of a bevel.
  • This pressure equalization surface, the diametrically opposite the distributor groove 12 is connected to a partial annular groove 37, which extends to below the distributor groove 12.
  • Figure 3 are the assignments of pressure equalization area 36, distributor groove 12 and filling groove 18 are shown more clearly and the partial ring groove 37 can also be seen in dashed lines.
  • the pressure compensation surface can be used instead of a bevel 36 just as well as flattening produced in some other way be executed.
  • the partial ring groove can also be ground in be carried out. It limits in their rimpedement to the distributor opening 12 at a vertical distance from this a first leakage path 39. Also on the lateral surface 11 the distributor pump piston 6 recognizes the annular groove 20, which was already shown in Figure 1 and the one below Limitation of the sealing outer surface of the pump piston forms, which on the other hand is limited by the partial ring groove 37 is.
  • a bevel or flattened pressure compensation surface 36 leads from its uppermost pump workspace Limitation from the partial ring groove 37 from parallel to a radial plane of the distributor piston 6.
  • the partial ring groove ends so that seen in the axial direction partial ring groove and distributor opening 12 overlap, wherein between partial ring groove 37 and the lowest boundary edge 40 the distributor opening over the between the outer surface of the distributor pump piston and lateral surface of the axial bore 5 available Gap the first leakage path 39 is formed.
  • the second leakage path 42 is determined by the vertical distance between the lower, facing away from the pump work chamber 8 Boundary edge 43 and the annular groove 20 are formed.
  • the filling groove 18 is also entered, which in Intermediate area between the distributor opening 12 and the Pressure compensation surface 36 is. This overlaps in the circumferential direction seen the distribution opening to a large extent 12 in such a way that when the distributor pump piston rotates 6 also in connection with the individual mouths of the Pressure lines 14 can reach.
  • the pressure equalization surface 36 enclosing line 44 is a line of one currently the same high pressure specified in the range between the outer surface of the distributor pump piston 6 and the housing bore during the delivery stroke of the pump piston prevails. It can be seen that in the case of high-pressure production the Surrounding the distributor groove still in the gap between the Shell surface 11 and the housing bore in from the high Pressure is applied.
  • this high pressure will in the area of the filling groove 18 connected to the suction space 24 dismantled and also in the area of not at the high pressure injection involved mouths of the pressure lines 14.
  • the Distance between the closest boundary edge of the Pressure compensation surface 36 to the filling groove 18 or to one of the in the meantime pressure-relieved pressure lines 14 a Leakage path as a second leakage path 42 a or 42 b as an alternative or be formed in addition.
  • FIG. 6 shows an alternative embodiment to FIG. 4 of the pump piston, again in the form of a lateral surface development.
  • Deviate from the embodiment Figure 4 are here two pressure compensation areas instead of one 36a and 36b are provided, which are now symmetrical to the filling groove 18 lie, which in turn diametrically opposite the distributor groove 12 lies.
  • These two pressure compensation surfaces 36a and 36b are in turn connected to one another by a partial annular groove 37 ' in such a way that this partial ring groove describes almost 360 ° with the exception of the area in which the filling groove 18 seen in the circumferential direction in overlap with the pressure compensation surfaces 36a and 36b.
  • the first leak route 39 is in turn determined by the vertical distance between Partial ring groove 37 and the lower edge 40 of the distributor groove 12 are formed and the second leak section again between the lower one Limiting edge 43 of the pressure compensation surface 36a or 36b and the annular groove 20.
  • the pressure compensation surfaces are preferred arranged rotated by 120 ° to the distributor groove 12.
  • the second leak path would also be Another leakage path between the pressure compensation areas 36a or 36b and the filling groove 18 possible.
  • FIG. 7 shows a third exemplary embodiment, which in turn is based on the exemplary embodiment according to FIG. 4 inspired.
  • a pressure compensation area 136a a pressure field boundary surface 136b is provided, which now continuously connected to one another by an annular channel 137 are.
  • the second leakage path 42 in turn between the lower boundary 43 of the one pressure compensation surface 136a and the annular groove 20 are formed.
  • the first Leakage path 139 is now between the upper boundary edge the pressure field boundary surface 136b and the lower boundary edge 40 of the distributor opening 12. Die
  • the pressure field delimitation surface 136b is aligned with the distributor opening 12 arranged, i.e.
  • the common center line forms a surface line of the outer surface 11 of the distributor pump piston.
  • the Pressure compensation surface 136a generates a compensation force
  • the print field boundary surface 136b mainly the balance pressure supply, but also the limitation of the Distributor groove pressure field and thus serves the shear force.
  • FIG. A fourth exemplary embodiment is shown in FIG. which in turn is based on the exemplary embodiment according to FIG. 6 inspired.
  • the arrangement of the fill bores 118a and 118b are chosen so that they are during a full work cycle (Suction / delivery) with one of the injection lines 14 overlap.
  • the filling bores are preferably To be arranged at 90 ° to the distributor groove.
  • the second leak gap 142 is between the lower boundary edges 43 of the pressure compensation surfaces 36a, and 36b and one on the outer surface of the distributor pump piston circumferential additional annular groove 48 formed, which lies above the annular groove 20.
  • Another third leakage path 49 between the additional annular groove 48 and the annular groove 20 is formed. That there of the additional Ring groove 48 leakage volumes flowing over the circumference to the ring groove 20, can correspond to the circumference of the gap of the distributor pump piston be different, whereby different pressure conditions develop, one Favor balance of forces.
  • the third leak path 49 is essentially in relation to the second leak path 2.5 times as large.

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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)

Claims (16)

  1. Pompe d'injection de carburant pour un moteur à combustion interne comportant une pièce (6) mobile dans un perçage (5) réalisé dans le corps de la pompe, pièce dont la surface enveloppe (11) comporte un orifice de sortie (12) alimenté en carburant à haute pression par un canal (10) dans la partie mobile (6) à partir d'une source de haute pression (8), de manière intermittente, et au cours du mouvement de la pièce mobile (6), cet orifice est mis en liaison avec une conduite de pression (14) partant du perçage (5) pour transmettre le carburant venant de la source de haute pression, et
    la surface enveloppe de la pièce (6) comporte au moins une surface de compensation (36 ; 36a, 136a ; 136b) soumise à la haute pression, cette surface se trouvant de préférence sur le côté de cette surface enveloppe (11) à l'opposé de l'orifice de sortie (12),
    caractérisée en ce que
    la surface de compensation de pression (36 ; 36a, 136a ; 136b), est couverte en permanence par la paroi intérieure du perçage (5) au cours du mouvement de la pièce mobile (6), et
    elle est reliée par un premier chemin de fuite (39) entre la surface enveloppe (11) de la pièce mobile (6) et la paroi intérieure du perçage (5) à des pièces (12) de la pompe conduisant la haute pression et
    par un second chemin de fuite (42) à une zone (20) reliée à une source basse pression (24), cette zone étant définie entre la surface enveloppe (11) de la pièce mobile (6) et le perçage (5).
  2. Pompe d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    le second chemin de fuite (42) est essentiellement de longueur double du premier chemin de fuite (39).
  3. Pompe d'injection de carburant selon l'une quelconque des revendications 1 ou 2,
    caractérisée en ce que
    la pièce mobile est un distributeur entraíné en rotation, comportant un orifice de distribution (12) comme orifice de sortie alimenté périodiquement par du carburant à haute pression et, au cours de la rotation du distributeur (6), cet orifice de distribution est mis en communication successivement avec différentes conduites de pression partant de la périphérie du distributeur (6) dans le perçage (5), pour transmettre le carburant débité à haute pression à l'orifice de distribution (12) vers chaque fois un injecteur.
  4. Pompe d'injection de carburant selon l'une quelconque des revendications 1 à 3,
    caractérisée en ce qu'
    au moins une surface de compensation de pression (36 ; 36a, 136a ; 136b) est une rainure longitudinale ou un méplat ou une surface meulée s'étendant dans la direction longitudinale, parallèlement à l'axe de la pièce mobile en rotation.
  5. Pompe d'injection de carburant selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que
    la surface de compensation de pression (36 ; 36a, 136a ; 136b) de la pièce mobile (6) comporte au moins une extension partielle de préférence sous la forme d'une rainure de transmission ou d'un méplat en forme de rainure (37, 37', 137) usinée dans la surface enveloppe et arrivant dans une zone de la surface enveloppe (11) dans laquelle existe, entre la pièce mobile (6) et le perçage (5), défini comme premier chemin de fuite (39), la plus petite distance par rapport aux pièces soumises à la haute pression.
  6. Pompe d'injection selon la revendication 5,
    caractérisée en ce que
    l'extension partielle (37, 37', 137) de la surface de compensation de pression est essentiellement parallèle à un plan radial par rapport à l'axe de la pièce mobile (6).
  7. Pompe d'injection selon l'une quelconque des revendications 5 ou 6,
    caractérisée en ce que
    les pièces soumises à la haute pression sont constituées par un orifice de distribution réalisé dans la surface enveloppe de la pièce mobile, notamment une rainure de distribution (12).
  8. Pompe d'injection selon l'une quelconque des revendications 5 à 7,
    caractérisée en ce que
    la rainure ou le méplat en forme de rainure (36, 36a, 36b, 136a, 136b) et/ou la seconde rainure ou le méplat en forme de rainure sont réalisés sous la forme d'une rainure annulaire partielle (37, 37') parallèle à un plan radial de la pièce mobile et dont les extrémités sont situées dans un chevauchement axial par rapport à la pièce (12) soumise à la haute pression.
  9. Pompe d'injection selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    le second chemin de fuite (42) est formé entre les surfaces de compensation de pression (36, 36a, 36b, 136a) et une zone (18) située dans la direction périphérique de la pièce mobile et voisine de la source basse pression (24).
  10. Pompe d'injection selon la revendication 9,
    caractérisée en ce que
    la zone reliée à la source basse pression arrive jusque dans une rainure annulaire (20) dans la surface enveloppe (11) de la pièce mobile (6).
  11. Pompe d'injection selon l'une quelconque des revendications 4 à 10,
    caractérisée par
    plusieurs surfaces de compensation de pression reliées par une rainure périphérique (137) ou une partie aplatie en forme de rainure, s'étendant parallèlement à un plan radial par rapport à l'axe de la pièce mobile (6), cette rainure étant usinée dans la surface enveloppe.
  12. Pompe d'injection de carburant selon la revendication 9,
    caractérisée en ce que
    la surface enveloppe (11) de la pièce mobile (6) comporte deux surfaces de compensation de pression (36a, 36b), symétriques par rapport à une rainure de remplissage (18) et qui sont prévues essentiellement en opposition par rapport à la rainure de distribution, la rainure de remplissage (18) reliant au fur et à mesure de la rotation de la pièce mobile (6), les conduites de pression (6) à une chambre de décharge.
  13. Pompe d'injection de carburant selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    la dimension de la surface de compensation (36) correspond à la surface de l'orifice de sortie (12).
  14. Pompe d'injection de carburant selon la revendication 11,
    caractérisée en ce que
    la surface enveloppe (11) de la pièce mobile (6) comporte deux surfaces de compensation de pression (36a, 36b) qui sont essentiellement équidistantes angulairement et sont situées par rapport à la rainure distributrice (12) et comportent en outre deux perçages de remplissage (118a, 118b) qui, au fur et à mesure de la rotation de la pièce mobile, relient les conduites de pression (14) non soumises à une pression d'injection et relient celles-ci à une chambre de décharge elle-mème reliée à la source basse pression et dont l'intervalle angulaire entre les surfaces de pression et par rapport à la rainure distributrice (12) est défini par l'embouchure des conduites de pression (14) et se situe essentiellement en regard des deux surfaces d'équilibrage de pression.
  15. Pompe d'injection de carburant selon la revendication 14,
    caractérisée en ce qu'
    entre les surfaces de compensation (36a, 36b) et la rainure annulaire (20) reliée à la source basse pression (24), il est prévu une rainure supplémentaire (48) et un troisième chemin de fuite (49) est formé entre cette rainure et la rainure (20).
  16. Pompe d'injection de carburant selon la revendication 15,
    caractérisée en ce que
    la longueur du troisième chemin de fuite (49) représente principalement 2,5 fois la longueur du second chemin de fuite (142).
EP98907857A 1997-04-04 1998-01-24 Pompe d'injection de carburant pour moteur a combustion interne Expired - Lifetime EP0906506B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19713868 1997-04-04
DE19713868A DE19713868A1 (de) 1997-04-04 1997-04-04 Kraftstoffeinspritzpumpe für Brennkraftmaschinen
PCT/DE1998/000217 WO1998045592A1 (fr) 1997-04-04 1998-01-24 Pompe d'injection de carburant pour moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0906506A1 EP0906506A1 (fr) 1999-04-07
EP0906506B1 true EP0906506B1 (fr) 2002-05-08

Family

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Application Number Title Priority Date Filing Date
EP98907857A Expired - Lifetime EP0906506B1 (fr) 1997-04-04 1998-01-24 Pompe d'injection de carburant pour moteur a combustion interne

Country Status (8)

Country Link
US (1) US6152708A (fr)
EP (1) EP0906506B1 (fr)
JP (1) JP2000512362A (fr)
KR (1) KR20000016237A (fr)
CN (1) CN1084841C (fr)
CZ (1) CZ358698A3 (fr)
DE (2) DE19713868A1 (fr)
WO (1) WO1998045592A1 (fr)

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US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump
ITBO20040322A1 (it) * 2004-05-20 2004-08-20 Magneti Marelli Powertrain Spa Metodo ed impianto per l'iniezione diretta di carburante in un motore a combustione interna
GB0715982D0 (en) * 2007-08-15 2007-09-26 Itw Ltd Check valve
CN105697205B (zh) * 2016-01-28 2018-06-22 山东康达精密机械制造有限公司 一种直列分配式电控喷油泵用高压燃油分配装置

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DE3819996A1 (de) * 1988-06-11 1989-12-14 Bosch Gmbh Robert Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen
DE3943297A1 (de) * 1989-12-29 1991-07-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
JP3041210B2 (ja) * 1994-12-28 2000-05-15 トヨタ自動車株式会社 分配型燃料噴射ポンプ

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US6152708A (en) 2000-11-28
EP0906506A1 (fr) 1999-04-07
DE59804032D1 (de) 2002-06-13
CN1222952A (zh) 1999-07-14
KR20000016237A (ko) 2000-03-25
WO1998045592A1 (fr) 1998-10-15
JP2000512362A (ja) 2000-09-19
CZ358698A3 (cs) 1999-03-17
DE19713868A1 (de) 1998-10-08
CN1084841C (zh) 2002-05-15

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