EP1642023B1 - Raccordement pour espaces haute pression d'injecteurs de carburant - Google Patents

Raccordement pour espaces haute pression d'injecteurs de carburant Download PDF

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Publication number
EP1642023B1
EP1642023B1 EP04726428A EP04726428A EP1642023B1 EP 1642023 B1 EP1642023 B1 EP 1642023B1 EP 04726428 A EP04726428 A EP 04726428A EP 04726428 A EP04726428 A EP 04726428A EP 1642023 B1 EP1642023 B1 EP 1642023B1
Authority
EP
European Patent Office
Prior art keywords
pressure
bore
control line
tie
cylindrically 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.)
Expired - Lifetime
Application number
EP04726428A
Other languages
German (de)
English (en)
Other versions
EP1642023A1 (fr
Inventor
Heinz Haiser
Dominikus Hofmann
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 EP1642023A1 publication Critical patent/EP1642023A1/fr
Application granted granted Critical
Publication of EP1642023B1 publication Critical patent/EP1642023B1/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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors
    • 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
    • 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
    • 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
    • F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations

Definitions

  • DE 101 52 261 A1 discloses a connection point of a high-pressure accumulator designed as a high-pressure chamber of a high-pressure injection system for motor vehicles.
  • the pressurized space is a high-pressure accumulator in the form of a common rail of a diesel injection system.
  • the high-pressure accumulator is formed by a hollow body, in which opens a transverse bore.
  • To increase the compressive strength is proposed to attach to the outer and / or inner surface of the hollow body one or more notches and / or recesses for stress relief of the pressurized hollow body.
  • the notches and recesses are mounted in the vicinity of the transverse bores or extend in the axial direction close to the transverse bore.
  • Another high-pressure accumulator in the form of a common rail for a diesel injection system is known from US 6,520,155 B1.
  • the main body of the high-pressure accumulator has at least two connecting openings, which are arranged diametrically opposite one another, so that in the interior the point of confluence of the transverse bore can simply be rounded off in terms of manufacturing technology.
  • the document DE 199 48 339 C1 also relates to a connection point to a common rail of a diesel injection system, wherein at least two substantially circular-cylindrical recesses are executed in the interior of the base body, so that the transverse bore introduced into the base body into the recess and not in the Cylinder wall of the interior of the high pressure accumulator opens.
  • the document DE 102 18 904 A1 has a fuel injection device for internal combustion engines with a fuel injector, which can be supplied by a high-pressure fuel source, with a pressure intensifier designed as a pressure booster. Between the fuel injector and the high-pressure fuel source, the pressure translation device having a movable pressure booster piston is connected.
  • the pressure booster piston separates a connectable to the high-pressure fuel source space from a high-pressure chamber connected to the fuel injector. By filling a back space (differential pressure chamber) of the pressure booster device with fuel or by emptying the back space of fuel, the fuel pressure in the high-pressure chamber can be varied.
  • the fuel injector has a movable closing piston for opening and closing injection openings.
  • the closing piston protrudes into a closing pressure chamber, so that the closing piston can be acted upon by fuel pressure in order to achieve a force acting on the closing piston in the closing direction.
  • the closing pressure chamber and the rear space are formed by a common closing pressure-return chamber, wherein all portions of the closing pressure-return space are permanently interconnected to exchange fuel.
  • a high-pressure chamber communicates with the high-pressure fuel source in such a way that in High pressure chamber, apart from pressure oscillations, constantly at least the fuel pressure of the high-pressure fuel source may be present, wherein the pressure chamber and the high-pressure chamber are formed by a common injection space. All sections of the injection space are permanently connected to each other for the exchange of fuel.
  • a pressure-reinforced fuel injection device with internal control line can be removed.
  • the fuel injector which communicates with a high pressure source, has a multi-part injector body. In this one is actuated via a differential pressure chamber actuated pressure intensifier whose pressure booster piston separates a working space of the differential pressure chamber.
  • the fuel injection device can be actuated via a switching valve.
  • a pressure change in the differential pressure chamber of the pressure booster via a central control line which extends through the pressure booster piston.
  • the central control line is guided through the working space of the pressure booster and sealed against this via a high-pressure-tight connection.
  • DE 196 11 884 A1 relates to a fuel injection valve for internal combustion engines.
  • This comprises a valve member in an axially displaceable piston-shaped valve member.
  • This has at its combustion chamber end a valve sealing surface which cooperates to open up an injection cross-section with a provided on the combustion chamber end of the bore valve seat. Further, this has a pointing in the direction of valve sealing surface pressure shoulder, through which the valve member is divided into a larger diameter in the bore slidably guided guide member and a smaller diameter free shaft portion.
  • valve body is traversed by a pressure channel, which opens radially outward of the bore in the valve seat facing away from the end of the pressure chamber.
  • the pressure shoulder on the valve member constantly immersed so far in the guide portion of the bore, that at the pressure chamber adjacent the end of the guide portion of the bore an annular gap between the valve member and the wall of the bore remains. In this a counterforce is built up on a remaining between the bore and the pressure channel web.
  • the differential pressure chamber is connected by a generally horizontal bore to a second valve-carrying bore.
  • the production of horizontal drilling turns out to be extremely difficult. Time-consuming and expensive processes such as electrochemical sinking or erosion must be used here.
  • electrochemical sinking or erosion must be used here.
  • occur at the Verschneidungsstellen between the back space and the horizontal bore the highest stresses in the component.
  • a higher surface quality and a rounding of production-related resulting edges are no longer sufficient for the desired still to be increased system pressures to obtain durable components.
  • the known from DE 102 47 903 A1 inside central control line requires a higher manufacturing and assembly costs than simple holes within the injector.
  • the connection of the differential pressure chamber to the control line constitutes a potential weak point. Since the control valve for operating the pressure intensifier is arranged above the pressure intensifier for reasons of space, the control line is guided laterally past the pressure intensifier.
  • the connection between the differential pressure chamber (back space) and the control line which is usually designed as a bore and leads to the valve, represented by a circumferential groove or a side pocket in the cylindrical rear space of the booster.
  • the voltage overshoot can be significantly reduced, so that realize with such a fuel injector with optimized connection between the high-pressure chambers at the pressure booster higher injection pressures to let.
  • Another advantage of the proposed solution according to the invention is to be seen in that a tolerance insensitive Verschneidungsstelle between the groove or the pocket and the bore formed as a control line is achieved, since purely mechanical, machining production method for producing the groove or pocket can be used.
  • FIG. 1 is a schematic illustration of a pressure booster whose working space is separated from a pressure-relieving or pressurizable differential pressure chamber via a booster piston.
  • the pressure booster 1 comprises a compression chamber 5 formed in its body 11.
  • the booster piston 3 separating the differential pressure chamber 4 (back space) from the working space 2 comprises a first end face 6 and a first end face 6
  • the compression chamber 5 limiting the second end face 7.
  • the working space 2 of the pressure booster 1 with system pressure (P rail ) is applied.
  • the system pressure (p rail ) also prevails in the compression chamber 5 of the pressure booster 1, which is shown in its deactivated position 8 in FIG. 1, the system pressure level p rail also prevails.
  • the pressure booster 1 is therefore pressure-balanced, since the pressure forces acting on the second end face 7 and the annular surface in the differential pressure arm 4 of the pressure amplifier 1 correspond to the pressure force acting on the first end face 6 of the booster piston 3.
  • FIG. 2 shows a pressure amplifier according to the representation in FIG. 1 in its activated state.
  • the booster piston 3 moves into the compression space due to the pressure force acting on its first end face 6 in the working space 2, which is generated by the system pressure (p rail ) 5 on.
  • the second end face 7, which delimits the compression space 5 of the pressure booster 1 compresses the fuel supply contained in the compression space 5 to an elevated pressure level (p amplified ) which can be achieved in the direction of an inlet 10 to one in FIG. 2, in accordance with the design ratio of the pressure booster piston 3 directed injection valve member is passed.
  • Figure 3 shows a half section through a body of a pressure intensifier according to the prior art.
  • the pressure booster 1 comprises a body 11 in which a control line 12 designed as a bore runs. Trained as a bore control line 12 is connected via a horizontal bore 13 with the differential pressure chamber 4 (back space) of the booster 1 in combination.
  • a first Verschneidungsstelle 15 forms with the bore formed as a control line 12 and the horizontal bore 13 and a second critical Verschneidungsstelle 16 between the horizontal bore 13 and the rear space 4 of the booster 1 from.
  • the highest voltages occur during operation of the pressure booster 1, which affect the continuous operating stability of such a pressure booster 1 with horizontal bore 13 crucial.
  • the compression chamber 5 is shown, branches off from the under an adjusting depending on the design of the booster 1 angle of the inlet 10 to an injection valve member, not shown in Fig. 3.
  • FIG 4 shows an embodiment according to the invention of a connection between the control line 12 designed as a bore and a differential pressure chamber (back space) of a pressure booster.
  • a circulation groove 18 can be formed at the lower end of the differential pressure chamber 4 of the pressure intensifier 1 or a cylindrically shaped pocket 19.
  • the cylindrically shaped pocket 19 adjusts itself to a first bore intersection 17, while a second bore intersection 22 is formed between the differential pressure space 4 (rear space) of the pressure booster 1 and the cylindrically shaped pocket 19 or the circumferential groove 18.
  • the differential pressure chamber 4 is limited at its lower end by an annular surface 20; in half section of FIG. 4 is shown at the lower end of the body 11 of the booster 1 of the compression chamber 5, from the lower an angle of inclination of the inlet 10 branches off to the injection valve member, not shown in Fig. 4.
  • FIG. 5 shows a boundary wall of a high-pressure container with a cylindrically shaped pocket shown in an extended position of 180 °.
  • connection of the control line 12 designed as a bore to the differential pressure chamber 4 is designed as a cylindrically shaped pocket 19 which exhibits no notch effect.
  • the connection of the differential pressure chamber 4 to the formed as a bore control line 12 of FIG. 3 by means of a horizontal bore 13 results from the invention shown in Fig. 5 Forming the connection only a notch action point 23 along the bore 12, at which compared to Both results in accordance with FIG. 3 notch action points 15 and 16, sets a significantly lower voltage level.
  • connection of the differential pressure chamber to a control line designed as a bore is represented by means of a circumferential groove.
  • a connection of the differential pressure chamber to a bore formed as a control line 12 is shown in unwound 21 position wall of a high-pressure chamber such as a differential pressure chamber 4 of a pressure booster 1 also shown in a stretched circumferential groove 18.
  • the circumferential groove 18 is not kerb Angelsok, along the bore 12 forms the notch action point 23, which represents the location at which the maximum stresses 24 occur.
  • those in the component, i. Tangential voltages occurring in the body 11 in the unwound layer 21 of the body 11 are shown as Zuditionen.
  • a circumferential groove 18 in FIG. 6 weakens the overall cross-section of the body 11 somewhat, the circumferential groove 18 does not act like a notch under tensile load with respect to the resulting mechanical load. As a result, a voltage increase at the notch action point 23 is avoided, so that only one notch action point 23 is formed, which represents the location 24 at which the maximum stresses occur. Compared to the embodiment according to FIG. 3 with the embodiment of the connection as a horizontal bore 13, however, a considerably lower stress level arises at the notch action point 23.
  • connection between the control line formed as a bore 12 and a high-pressure container, however, designed as a cylindrically shaped pocket 19 offers the advantage that the cylindrically shaped pocket 19 causes a smaller dead volume compared to a circumferential groove 18, i. the high-pressure vessel when forming the connection as a cylindrically shaped pocket 19 can be filled with a smaller volume. If the dead volume can be reduced, for example, in the differential pressure chamber 4 of the pressure booster 1, this advantageously leads to an increase in the efficiency; Furthermore, the hydraulic tuning can be improved and last but not least - in the case of a booster - smaller Abêtmengen be moved when activating the booster.
  • Fig. 7.1 is a connection of a differential pressure chamber to a bore formed as a control line by means of a horizontal bore removed.
  • the differential pressure chamber 4 is constructed symmetrically to an axis of symmetry 25.
  • the control line 12 and the differential pressure chamber 4 are connected to each other via the horizontal bore 13, so that the first Verschneidungsstelle 15 between the horizontal bore 13 and the control line 12 results, and the second Verschneidungsstelle 16 through the horizontal bore 13 and the differential pressure chamber 4 (rear space) is shown ,
  • the notch effects formed at the Verschneidungsstelle 15 add up, so that sets a first, very high voltage level ⁇ max, 1 during operation of the pressure booster.
  • connection of the differential pressure chamber (rear space) to the control line designed as a bore is formed by a cylindrically shaped pocket.
  • the cylindrically shaped pocket 19 is formed in the lower region of the differential pressure chamber 4 in its inner wall.
  • the cylindrically shaped pocket 19 forms the attachment point between the control line 12 formed as a bore and the differential pressure chamber 4 (rear space) in the body 11.
  • the control line 12 can be designed both as a blind bore (FIG. 7.1) and as a through bore 12.1. Due to the shape of the attachment point as a cylindrically shaped pocket 19, a first bore intersection 17 sets in which represents the notch action point 23. In comparison to the illustration according to FIG. 7.1, only one notch effect contribution through the bore intersection 17 is shown.
  • This stress concentration point 23 represents the location 24 represents, at which a maximum stress ⁇ max, 2 occurs, which significantly added under the occurring in Fig. 7.1 maximum stress ⁇ max, 1.
  • the cylindrically shaped pocket 19 is formed in the lower portion of the inner wall of the differential pressure chamber 4 (back space) in the body 11 and also provides only a small increase in the dead volume within the differential pressure chamber 4.
  • the maximum height of the cylindrically shaped pocket 19 is identified by reference numeral 30; the cylindrically shaped pocket 19 extends symmetrically semicircular and runs in outlet areas 31 in the inner wall of the differential pressure chamber 4 (rear space).
  • the notch effect occurring at the second bore intersection 22 between the cylindrically shaped pocket 19 and the wall of the differential pressure chamber 4 is negligible compared to the stress exaggeration caused by the notch effect at the first bore intersection 17.
  • Fig. 7.3 shows the impact variant in cross section, in which the connection of the bore formed as a control line to the differential pressure chamber via a circumferential groove in the pressurized body.
  • the first hole intersection 17 marks the transition point of the bore 12 formed as a control line to the circumferential groove 18;
  • a second bore intersection 22 sets in which represents the transitional area between the differential pressure chamber 4 (rear space) and the circumferential groove 18.
  • the lower annular surface of the circumferential groove 18 is identified by reference numeral 20.
  • To the circumferential groove 18 more holes 33 may be connected, one of which is shown in Fig. 7.3.
  • the intersection 17 between the control line 12 designed as a bore and the circumferential groove 18 represents the notch action point 23, which represents the location 24 of the maximum stress ⁇ max, 3 .
  • the maximum stress ⁇ max, 3 occurring in the embodiment according to FIG. 7.3 is again reduced.
  • the contour of the circumferential groove 18 and the cylindrically shaped pocket 19 may be arcuate, angular, formed with rounded corners or in other geometry.
  • FIGS. 5, 6 and 7.2 and 7.3 of connection sites between high-pressure-carrying spaces and a bore extending essentially vertically through a body avoid sharp-edged transitions and thus permit a reduction of the occurring stress level.
  • the reduction of the maximum voltage occurring in the body 11 due to tangential stress when pressurizing the differential pressure chamber 4 (back space), for example, a pressure booster 1 allows on the one hand a further increase in the pressure level within the body 11, on the other hand, while maintaining the currently prevailing pressure levels, an extension of the service life of a pressurized body 11th ,

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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)
  • Braking Systems And Boosters (AREA)

Abstract

L'invention concerne un point de raccordement d'un espace (4) soumis à une pression élevée, dans un corps sollicité par une pression élevée (11) d'un système d'injection haute pression de carburant, à un trou (12) s'étendant à travers le corps (11). Ce trou s'étend sensiblement verticalement à l'intérieur du corps (11). Une poche de configuration cylindrique (19) ou une rainure périphérique (18) est formée dans l'espace (4) soumis à la pression élevée, poche dans laquelle débouche le trou (12) avec formation d'un point d'intersection (17).

Claims (9)

  1. Point de jonction d'une chambre de pression différentielle (4) sollicitée par haute pression d'un amplificateur de pression (1) dans un corps (11) sollicité par haute pression d'un système d'injection de carburant sous haute pression, sur une conduite de commande (12) passant à côté de l'amplificateur de pression et traversant le corps (11), la conduite de commande (12) s'étendant jusqu'à une soupape actionnant l'amplificateur de pression (1),
    caractérisé en ce que
    la chambre de pression différentielle (4), comporte une poche cylindrique (19) ou une rainure périphérique (18) dans laquelle débouche la conduite de commande (12) en formant un point d'intersection (17).
  2. Point de jonction selon la revendication 1,
    caractérisé en ce que
    la poche cylindrique (19) ou la rainure périphérique (18) est dans la zone de fond de la chambre de pression différentielle (4) sollicitée par haute pression.
  3. Point de jonction selon la revendication 1,
    caractérisé en ce que
    la rainure périphérique (18) présente un contour en forme d'arc ou angulaire dans une profondeur (32) constante dans le corps (11).
  4. Point de jonction selon la revendication 1,
    caractérisé en ce que
    la poche cylindrique (19) est réalisée en forme de demi-cercle, d'arc ou angulaire dans la paroi du corps (11) délimitant la chambre de pression différentielle (4) sollicitée par haute pression.
  5. Point de jonction selon la revendication 4,
    caractérisé en ce que
    la poche cylindrique (19) présente sa profondeur maximale (30) au niveau de la bouche de la conduite de commande (12).
  6. Point de jonction selon la revendication 4,
    caractérisé en ce que
    la poche cylindrique (19) présente des zones d'écoulement symétriques (31) des deux côtés de la bouche de la conduite de commande (12) dans celle-ci.
  7. Point de jonction selon la revendication 1,
    caractérisé en ce que
    le point d'intersection (17) est un passage de géométrie ovale ou rectangulaire en fonction de la forme de la rainure.
  8. Point de jonction selon la revendication 1,
    caractérisé en ce que
    la conduite de commande (12) est un alésage traversant (12.1) dans le corps (11) sollicité par haute pression.
  9. Point de jonction selon la revendication 1,
    caractérisé en ce qu'
    à la rainure périphérique (18) est relié au moins un autre alésage (33) dans le corps (11) sollicité par haute pression.
EP04726428A 2003-06-27 2004-04-08 Raccordement pour espaces haute pression d'injecteurs de carburant Expired - Lifetime EP1642023B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10329052A DE10329052A1 (de) 2003-06-27 2003-06-27 Verbindung für Hochdruckräume von Kraftstoffinjektoren
PCT/DE2004/000743 WO2005010347A1 (fr) 2003-06-27 2004-04-08 Raccordement pour espaces haute pression d'injecteurs de carburant

Publications (2)

Publication Number Publication Date
EP1642023A1 EP1642023A1 (fr) 2006-04-05
EP1642023B1 true EP1642023B1 (fr) 2007-02-28

Family

ID=33521120

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04726428A Expired - Lifetime EP1642023B1 (fr) 2003-06-27 2004-04-08 Raccordement pour espaces haute pression d'injecteurs de carburant

Country Status (4)

Country Link
US (1) US7717087B2 (fr)
EP (1) EP1642023B1 (fr)
DE (2) DE10329052A1 (fr)
WO (1) WO2005010347A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005095216A1 (fr) 2004-03-26 2005-10-13 Csp Technologies, Inc. Film actif colle a des emballages flexibles et procede associe
DE102006036103A1 (de) * 2006-08-02 2008-02-07 Siemens Ag Kanalanordnung
JP4501983B2 (ja) 2007-09-28 2010-07-14 アイシン・エィ・ダブリュ株式会社 駐車支援システム、駐車支援方法、駐車支援プログラム
DE102008003347A1 (de) * 2008-01-07 2009-07-09 Robert Bosch Gmbh Druckverstärkeranordnung
US10034455B2 (en) 2015-12-17 2018-07-31 Lumo Llc Self-cleaning pet grooming implement

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1179542A (fr) * 1957-07-08 1959-05-26 Perfectionnements apportés à des pompes alternatives autorégulatrices, notamment pour l'injection de combustible dans des moteurs
US4700680A (en) * 1984-05-08 1987-10-20 Teledyne Industries, Inc. Two stage fuel pump
DE19948341A1 (de) * 1999-10-07 2001-04-19 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
DE19948339C1 (de) * 1999-10-07 2000-12-14 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
DE10022378A1 (de) 2000-05-08 2001-11-22 Bosch Gmbh Robert Hochdruckfester Injektorkörper
DE10146741A1 (de) 2001-09-22 2003-04-17 Bosch Gmbh Robert Kraftstoffhochdruckspeicher
DE10152261A1 (de) 2001-10-20 2003-04-30 Bosch Gmbh Robert Hochdruckspeicher wie Kraftstoffhochdruckspeicher

Also Published As

Publication number Publication date
WO2005010347A1 (fr) 2005-02-03
DE10329052A1 (de) 2005-01-13
EP1642023A1 (fr) 2006-04-05
DE502004003063D1 (de) 2007-04-12
US20070095325A1 (en) 2007-05-03
US7717087B2 (en) 2010-05-18

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