EP1784571B1 - Pompe haute pression pour un systeme d'injection de carburant d'un moteur a combustion interne - Google Patents

Pompe haute pression pour un systeme d'injection de carburant d'un moteur a combustion interne Download PDF

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Publication number
EP1784571B1
EP1784571B1 EP05760887A EP05760887A EP1784571B1 EP 1784571 B1 EP1784571 B1 EP 1784571B1 EP 05760887 A EP05760887 A EP 05760887A EP 05760887 A EP05760887 A EP 05760887A EP 1784571 B1 EP1784571 B1 EP 1784571B1
Authority
EP
European Patent Office
Prior art keywords
bore
valve
pump
valve element
head
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.)
Not-in-force
Application number
EP05760887A
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German (de)
English (en)
Other versions
EP1784571A1 (fr
Inventor
Alessandro De Luca
Vittorio Caroli
Angela Cavallo
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1784571A1 publication Critical patent/EP1784571A1/fr
Application granted granted Critical
Publication of EP1784571B1 publication Critical patent/EP1784571B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • 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
    • F02M59/464—Inlet valves of the check valve type
    • 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
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"

Definitions

  • the invention is based on a high-pressure pump for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 197 44 577 A1 known.
  • This high-pressure pump has at least one pump element, with a driven in a stroke, in a cylinder bore of a pump housing part slidably guided pump piston which limits a pump working space in the cylinder bore.
  • the pump working chamber is filled with fuel from a fuel feed via a suction valve, and during the delivery stroke of the pump piston, fuel is expelled from the pump working chamber via an outlet valve.
  • the suction valve has a piston-shaped valve member which cooperates with a valve seat formed in a valve housing for controlling the connection of the pump working chamber with the fuel inlet with a sealing surface formed thereon.
  • valve member On the valve member engages in the closing direction acting on this closing spring.
  • the valve member has a shaft and a diameter in relation to this enlarged head, wherein the shaft is guided displaceably in a bore of the valve housing. It has been found that the valve member can tilt during its closing movement with its longitudinal axis, whereby an initially one-sided contact of the sealing surface is effected on the valve seat. This tilting is caused by the insufficient guidance of the valve member with its shaft in the bore of the valve housing.
  • a high-pressure pump for a fuel injection device which has a suction valve with a piston-shaped valve member.
  • the valve member has a cylindrical shaft and a head enlarged in cross-section with respect to the shaft.
  • the shaft of the valve member is slidably guided in a guide bore of a valve housing, wherein the shaft has fürströmabête which are reduced compared to the guide portions of the shaft in cross section.
  • an annular throttle gap is present. Also with this suction valve is therefore due to the leadership of the valve member only on the shaft tilting possible with corresponding effects on wear and function.
  • the high-pressure pump according to the invention with the features of claim 1 has the advantage that the leadership of the valve member of the suction valve is improved, whereby the wear is reduced and the durability of the suction valve and thus the high pressure pump is improved.
  • the embodiment according to claim 4 allows a quick closing of the suction valve, as can build up in the room no increased pressure.
  • the embodiments according to claims 5 and 6 allow in a simple way the fuel supply to the suction valve and the connection of the valve member limited space with the fuel inlet.
  • FIG. 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section
  • FIG. 2 a suction valve of the high pressure pump in an enlarged view in a longitudinal section according to a first embodiment
  • FIG. 3 the suction valve in a cross section along line III-III in FIG. 2
  • FIG. 4 a valve housing of the suction valve in an enlarged view in a longitudinal section
  • FIG. 5 a valve member of the suction valve
  • FIG. 6 the valve member in a view in the direction of arrow VI in FIG. 5
  • FIG. 7 the suction valve according to a second embodiment.
  • a high pressure pump 10 is shown for a fuel injector of an internal combustion engine, which is preferably a self-igniting internal combustion engine.
  • fuel is conveyed under high pressure into a memory 12, is taken from the fuel for injection to the internal combustion engine by injectors 13.
  • the high-pressure pump 10 is supplied by a feed pump 14 fuel.
  • the high-pressure pump 10 has at least one pump element 16 which has a pump piston 20 driven at least indirectly by a drive shaft 18 of the high-pressure pump 10 in a lifting movement.
  • the pump piston 20 is tightly guided in a cylinder bore 22 extending at least approximately radially to the drive shaft 18 and delimits a pump working space 24 in the outer end region of the cylinder bore 22 facing away from the drive shaft 18.
  • the drive shaft 18 has a cam or a shaft section 26 eccentric to its axis of rotation 19 , via which during the rotational movement of the drive shaft 18, the lifting movement of the pump piston 20 is effected.
  • the pump piston 20 is held by a return spring 28 directly or via a support member 29 in abutment with the shaft portion 26.
  • the pump working chamber 24 is provided with a fuel inlet from a suction valve 30 which opens into the pump working chamber 24 and is designed as a check valve the delivery pump 14 connectable ago.
  • the pump working chamber 24 can also be connected to the accumulator 12 via a discharge valve 32, which opens out of the pump working chamber 24 and is designed as a check valve, with a fuel outlet.
  • the suction valve 30 When suction stroke of the pump piston 20, the suction valve 30 is opened because of the existing pressure difference, as of the feed pump 14, a higher pressure is generated than the pressure prevailing in the pump working chamber 24, so that funded by the feed pump 14 fuel is sucked into the pump working chamber 24.
  • the outlet valve 32 is closed during the suction stroke of the pump piston 20, as in the memory 12, a higher pressure than in the pump working chamber 24 prevails.
  • the suction valve 30 based on the FIGS. 2 to 6 described in more detail, in which the suction valve 30 is shown according to a first embodiment.
  • the suction valve 30 is as in FIG. 2 represented in a radially outwardly adjoining the cylinder bore 22 bore 34 of a housing part 36 of the high-pressure pump 10 is inserted.
  • the bore 34 is formed larger in diameter relative to the cylinder bore 22.
  • the housing part 36 may for example be a cylinder head which is connected to another housing part in which the drive shaft 18 is mounted, or a housing part, in which the drive shaft 18 is mounted.
  • a fuel inlet channel 38 which is connected to the feed pump 14.
  • a fuel inlet channel 38 which is connected to the feed pump 14.
  • the suction valve 30 has as in the Figures 2 and 4 illustrated a valve housing 42 which is formed approximately pot-shaped.
  • the valve housing 42 has at its annular shoulder 40 facing inner end on an enlarged outer diameter flange 44. Subsequently, the outer diameter of the valve housing is lower on the flange 44 and may be reduced to the outer end of the valve housing 42 facing away from the annular shoulder 40, for example approximately frusto-conically.
  • the valve housing 42 has a through hole 46, which is formed multi-stepped in diameter.
  • the bore 46 has in the outer end region of the valve housing 42 on a small diameter first portion 46 a, to which the inner end of the valve housing 42 is followed by a larger diameter second bore portion 46 b.
  • the second bore section 46b is adjoined by a third bore section 46c, whose diameter increases at least approximately in the shape of a truncated cone towards the inner end of the valve housing 42 and whose lateral surface is inclined at an angle ⁇ to the longitudinal axis 47 of the bore 46.
  • the third bore portion 46c forms a valve seat.
  • the third bore section 46c is adjoined by a fourth bore section 46d, whose diameter increases at least approximately in the shape of a truncated cone towards the inner end of the valve housing 42 and whose lateral surface is inclined at an angle ⁇ to the longitudinal axis 47 of the bore 46.
  • the angle ⁇ of the fourth bore portion 46d is greater than the angle ⁇ of the third bore portion 46c.
  • the fourth bore portion 46d is followed by a fifth bore portion 46e of constant diameter toward the inner end of the valve housing 42.
  • a chamfer may be provided at the transition between the second bore portion 46b and the third bore portion 46c.
  • a chamfer may be provided at the transition between the second bore portion 46b and the third bore portion 46c.
  • the Transition between the fourth bore portion 46d and the fifth bore portion 46e may be rounded.
  • At least one inlet channel 50 is introduced, which opens on the one hand on the outer surface of the valve housing 42 and on the other hand in the second bore portion 46b.
  • a plurality of, for example, three over the circumference of the valve housing 42 evenly distributed feed channels 50 are provided.
  • the inlet channels 50 can open into the bore section 46b such that their longitudinal axes 51 intersect with the longitudinal axis 47 of the bore section 46b.
  • the inlet channels 50 may also open into the second bore section 46b such that their longitudinal axes 51 do not intersect the longitudinal axis 47 of the bore 46 and the inlet channels 50 open at least approximately tangentially into the bore section 46b, as shown in FIG FIG. 3 is shown.
  • the inlet channels 50 may extend with their longitudinal axes 51 at least approximately perpendicular to the longitudinal axis 47 of the bore 46 or as in FIG. 2 and 4 illustrated such that the longitudinal axis 51 of the inlet channels 50 form with the longitudinal axis 47 of the bore 46 to the end of the valve housing 42 with the flange 44 toward an acute angle.
  • an annular space 52 is present, into which the fuel inlet channel 38 opens.
  • the valve housing 42 is held in the bore 34 of the housing part 36 by an inserted into the bore 34 holding member 54 which is preferably formed as a screwed into an internal thread of the bore 34 retaining screw.
  • an elastic sealing ring 56 is clamped, through which the bore 34 is sealed to the outside.
  • the valve housing 42 is replaced by the retaining screw 54th pressed with its flange 44 against the annular shoulder 40 of the housing part 36.
  • the flange 44 and / or the annular shoulder 40 may have a raised web 58 which is elastically and / or plastically deformed by the pressure of the valve housing 42 against the annular shoulder 40 and thereby ensures a seal of the pump working chamber 24 to the bore 34.
  • a separate sealing element for sealing can be arranged between the flange 44 and the annular shoulder 40.
  • the retaining screw 54 may have on its side facing the bore 34 side a recess 55 having a non-circular cross-section into which a suitably trained tool for screwing or unscrewing the retaining screw 54 can be inserted into the thread of the bore 34.
  • the retaining screw 54 has on its side facing the valve housing 42 a recess 57 into which the valve housing 42 is immersed.
  • the valve housing 42 has in its the screw 54 facing the front side a central depression, into which the bore 46 opens. By lowering the valve housing 42, a space 60 is limited between this and the retaining screw 54, in which the bore 46 opens.
  • the space 60 is connected to the second bore portion 46b through at least one bore 62 in the valve housing 42, the bore 62 being at least approximately parallel to the first bore portion 46a and laterally adjacent thereto.
  • the space 60 is thus constantly connected to the second bore portion 46 b and thus to the fuel inlet passage 38.
  • the suction valve 30 also has as in the Figures 2 . 5 and 6 10 illustrates a piston-shaped valve member 64 which has a cylindrical shaft 66 and a head 68 which is larger in cross-section than the shaft 66.
  • a sealing surface 70 is arranged at its edge facing the shaft 66, which is formed at least approximately frusto-conical and whose lateral surface is inclined at an angle ⁇ to the longitudinal axis 65 of the valve member 64.
  • the sealing surface 70 is adjoined by a cylindrical or at least approximately frusto-conical widening in cross section to the end of the head 68 facing away from the shaft 66.
  • a plurality of distributed over the circumference of the head 68 and spaced apart guide portions 74 are arranged, whose outer contours lie on a common diameter.
  • the guide sections 74 may be part of the truncated cone of the region of the head 68. However, the guide portions 74 may also have an at least approximately cylindrical outer contour. Between the guide portions 74 are present in cross-section with respect to these reduced portions 76, which are formed for example by bevels or flats on the periphery of the head 68. From the shaft 66 facing away from the end face of the head 68 of the valve member 64 is at least approximately coaxially to the longitudinal axis 65, a short pin 78 out.
  • an undercut can be provided in each case to simplify the manufacturability of the valve member 64.
  • an annular groove 72 is preferably provided between the sealing surface 70 and the head 68 with the guide portions 74.
  • the opening behavior of the valve member 64 is improved by the pressure acting in the opening direction can act on the sealing surface 70, and thus improves the filling of the pump working chamber 24.
  • the wear behavior of the sealing surface 70 is improved by the annular groove 72 by the wear of the sealing surface 70 is stopped at the annular groove 72.
  • the valve member 64 is slidably guided with its shaft 66 in the first bore portion 46 a of the valve housing 42 with a small clearance.
  • the first bore portion 46a thus forms a guide bore for the shaft 66 of the valve member 64.
  • the valve member 64 is guided over its guide portions 74 with greater clearance in the fifth bore portion 46e of the valve housing 42.
  • the possible tilting of the longitudinal axis 65 of the valve member 64 with respect to the longitudinal axis 47 of the bore 46 is limited by the guide portions 74, for example to a maximum of about 0.5 °, preferably to a maximum of about 0.25 °.
  • the angle ⁇ under which the lateral surface of the valve seat 46c is inclined to the longitudinal axis 47, deviates from the angle ⁇ , under which the lateral surface of the sealing surface 70 of the valve member 64 is inclined to the longitudinal axis 47.
  • the angle ⁇ can be slightly larger than the angle ⁇ , wherein the difference can be relatively small and, for example, can be only a few degrees or only about 1 °.
  • FIG. 2 1 shows a closing spring 80 acting in the closing direction, which is supported on the pump piston 20 on the one hand and on the end face of the head 68 of the valve member 64 facing the pump piston 20 on the other hand.
  • the closing spring 80 is formed, for example, as a helical compression spring and is placed on the pin 78 on the valve member 64 and is centered by this.
  • valve member 64 is acted upon in its opening direction by the pressure supplied via the inlet channels 50 to the second bore section 46b, generated by the feed pump 14.
  • a higher pressure generated by the feed pump 14 prevails in the fuel feed than in the pump working chamber 24, so that the valve member 64 opens against the force of the closing spring 80 and lifts off with its sealing surface 70 from the valve seat 46c and thereby an annular flow cross-section into the pump working space 24 releases.
  • a sufficiently large flow cross section is released to allow filling of the pump working chamber 24 with fuel.
  • the inflow of the fuel from the inlet channels 50 into the second bore section 46b takes place as a result of the tangential mouth of the inlet channels 50 into the bore section 46b with low flow losses. Due to the tangential mouth of the inlet bores 50, the incoming fuel receives a twist. The outlet of the inlet channels 50 in the bore section 46b can be rounded. Thus, a good filling of the pump working space 24 is made possible.
  • the space 60 between the valve housing 42 and the retaining screw 54 is connected via the bore 62 with the fuel inlet 38, so that in the closing movement of the valve member 64 of this from the space 60 fuel can be displaced into the fuel inlet 38, whereby a rapid closing of the Suction valve 30 is reached and a pressure increase in the space 60 is avoided.
  • the suction valve opens 30, as caused by the pressure acting on the valve member 64 in the opening direction in the fuel inlet 38 pressure opening force is greater than the force of the closing spring 80 and the force generated by the pressure prevailing in the pump working chamber 24 in the closing direction on the valve member 64.
  • the delivery stroke of the pump piston 20 in which it moves away from the drive shaft 18 to the outside, closes the suction valve 30, since the sum of the force generated by the pressure prevailing in the pump working chamber 24 and the force of the closing spring 80 is greater than the opening force on the Valve member 64.
  • FIG. 7 the suction valve 30 is shown according to a second embodiment, in which the basic structure is the same as in the first embodiment, but the valve housing and the retaining screw are integrally formed as a valve housing 142.
  • the valve member 64 of the suction valve 30 is formed identical to the first embodiment and will therefore not be described again in more detail below.
  • the bore 46 with the bore portions 46a, 46b, 46c, 46d and 46e is arranged, wherein the bore 46 is formed as a blind bore.
  • the valve member 64 is guided with its shaft 66 with little play in the guide bore 46a and guided with greater play with its head 68 via the guide portions 74 in the bore portion 46e.
  • the valve housing 142 is provided with an external thread, with which it is screwed into a corresponding internal thread of the bore 34 in the housing part 36 of the high-pressure pump, wherein the sealing of the bore 34 takes place to the outside by the sealing ring 56.
  • the seal between the valve housing 142 and the annular shoulder 40 at the transition of the bore 34 to the cylinder bore 22 is the same as in the first embodiment.
  • the fuel inlet channel 38 opens into The bore 34 in the valve housing 142 surrounding annular space 52.
  • a plurality of circumferentially distributed fuel inlet channels 150 are formed, which open on the one hand on the outer surface of the valve housing 142 and on the other hand in the second bore portion 46 b.
  • the course of the inlet channels 150 is analogous to the first exemplary embodiments, so that they preferably open at least approximately tangentially into the second bore section 46b.
  • the inlet channels 150 may extend with their longitudinal axes 151 at least approximately perpendicular to the longitudinal axis 47 of the bore 46 or as in FIG. 7 illustrated such that the longitudinal axis 151 of the inlet channels 150 with the longitudinal axis 47 of the bore 46 to the outer end of the valve housing 142 form an acute angle.
  • the valve housing 142 also has a bore 162 is introduced, which opens on the one hand on the outer surface of the valve housing 142 in the annular space 52 and the other part in the first bore portion 46 a in the limited space by the shaft 66 of the valve member 64 space 160.
  • the space 160 is thus permanently connected to the fuel inlet channel 38.
  • the valve housing 142 and the bore 34 of the housing part 36 of the sealing ring 56 is clamped to seal the annular space 52, in which the fuel supply pressure generated by the feed pump 14, to the outside.
  • the sealing against the pressure prevailing in the pump working chamber 24 high pressure takes place as in the first embodiment between the housing part 36 and the valve housing 142 by a raised web on one of these parts or by a separate sealing ring.

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

Claims (7)

  1. Pompe haute pression pour une installation d'injection de carburant d'un moteur à combustion interne comprenant au moins un élément de pompe (16) muni d'un piston de pompe (20) guidé en coulissement en étant entraîné, suivant un mouvement de translation dans un alésage (22) d'une partie de boîtier de pompe (36), le piston délimitant une chambre de travail de pompe (24) dans l'alésage (22), cette chambre de travail se remplissant de carburant à partir d'une alimentation en carburant (38) pendant la course d'aspiration du piston de pompe (20), la soupape d'aspiration (30) comportant un organe de soupape (64) en forme de piston coopérant avec un siège de soupape (46c) pour commander la liaison de la chambre de travail de la pompe (24) avec l'alimentation en carburant (38),
    l'organe de soupape (64) étant sollicité dans le sens de l'ouverture par la pression régnant dans l'alimentation en carburant (38) et dans le sens de la fermeture par la pression régnant dans la chambre de travail de pompe (24),
    l'organe de soupape (64) ayant un corps cylindrique (66) et une tête (68) de section plus grande que celle du corps (66),
    au moins le corps (66) de l'organe de soupape (64) étant guidé en coulissement dans un perçage de guidage (46a) d'un boîtier de soupape (42 ; 142),
    caractérisée en ce qu'
    en plus, la tête (68) de l'organe de soupape (64) est guidée en coulissement dans un perçage (46e) du boîtier de soupape (42 ; 142) par des segments de guidage (74), réalisés sur la tête et écartés les uns des autres dans la direction périphérique, et
    entre les segments de guidage (74), la tête (68) de l'organe de soupape (64) comporte des segments de passage (76) de section réduite par rapport à celle des segments de guidage (74), et permettant le passage du carburant à partir de l'alimentation en carburant (38) vers la chambre de travail (24).
  2. Pompe haute pression selon la revendication 1,
    caractérisée en ce que
    la tête (68) de l'organe de soupape (64) présente, à la jonction avec le corps (66), une surface d'étanchéité (70) au moins sensiblement de forme tronconique, coopérant avec le siège de soupape (46c).
  3. Pompe haute pression selon la revendication 2,
    caractérisée par
    une gorge annulaire (72) réalisée à la jonction entre la surface d'étanchéité (70) et la tête (68) dans l'organe de soupape (64).
  4. Pompe haute pression selon l'une des revendications 1 à 3,
    caractérisée en ce que
    l'organe de soupape (64) délimite un volume (60 ; 160) relié en permanence à l'alimentation en carburant (38) par l'extrémité frontale du corps (66) guidée dans le perçage (46a) du boîtier de soupape (42 ; 142).
  5. Pompe haute pression selon la revendication 4,
    caractérisée en ce que
    dans une zone comprise entre la zone du corps (66) reçue dans le perçage de guidage (46a) et la tête (68) de l'organe de soupape (64), le corps (66) de l'organe de soupape (64) est entouré par le perçage (46b) du boîtier de soupape (42) de diamètre plus grand que celui du perçage de guidage (46a), de façon que l'alimentation en carburant (38) débouche dans le perçage (46b) et que le volume (60) délimité par le corps (66) de l'organe de soupape (64) soit relié au perçage (46b) par au moins un perçage de liaison (62) réalisé dans le boîtier de soupape (42).
  6. Pompe haute pression selon la revendication 4,
    caractérisée en ce que
    dans la zone comprise entre la zone du corps (66) dans le perçage de guidage (46a) et la tête (68) de l'organe de soupape (64) le corps (66) de l'organe de soupape (64) est entouré par le perçage (46b) du boîtier de soupape (142) plus grand que le diamètre du perçage de guidage (46a), de façon à former un volume annulaire (52) entre le boîtier de soupape (142) et le perçage (34) de la partie de boîtier de pompe (36) logeant le boîtier de soupape (142), l'alimentation en carburant (38) débouchant dans ce volume annulaire et,
    le perçage (46b) et le volume (160) délimité par le corps (66) de l'organe de soupape (64) sont reliés respectivement par au moins un perçage de liaison (150 ; 162) au volume annulaire (52).
  7. Pompe haute pression selon l'une des revendications 1 à 6,
    caractérisée par
    un ressort de fermeture (80) appliqué à l'organe de soupape (64) qui s'appuie de préférence au moins indirectement contre le piston de pompe (20).
EP05760887A 2004-08-28 2005-07-05 Pompe haute pression pour un systeme d'injection de carburant d'un moteur a combustion interne Not-in-force EP1784571B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004041764A DE102004041764A1 (de) 2004-08-28 2004-08-28 Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
PCT/EP2005/053183 WO2006024569A1 (fr) 2004-08-28 2005-07-05 Pompe haute pression pour un systeme d'injection de carburant d'un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1784571A1 EP1784571A1 (fr) 2007-05-16
EP1784571B1 true EP1784571B1 (fr) 2008-12-10

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ID=34972365

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05760887A Not-in-force EP1784571B1 (fr) 2004-08-28 2005-07-05 Pompe haute pression pour un systeme d'injection de carburant d'un moteur a combustion interne

Country Status (7)

Country Link
US (1) US7571713B2 (fr)
EP (1) EP1784571B1 (fr)
JP (1) JP4571980B2 (fr)
CN (1) CN100575700C (fr)
AT (1) ATE417200T1 (fr)
DE (2) DE102004041764A1 (fr)
WO (1) WO2006024569A1 (fr)

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DE102006017036A1 (de) * 2006-04-11 2007-10-18 Siemens Ag Radialkolbenpumpe zur Kraftstoff-Hochdruckversorgung bei einer Brennkraftmaschine
AT503697B1 (de) * 2006-06-02 2008-06-15 Bosch Gmbh Robert Pumpenelement für eine hochdruckpumpe
IT1395606B1 (it) * 2009-09-14 2012-10-16 Bosch Gmbh Robert Pompa ad alta pressione migliorata per alimentare combustibile a un motore a combustione interna e anello di tenuta albero migliorato per la stessa
JP5288058B1 (ja) * 2011-09-06 2013-09-11 トヨタ自動車株式会社 燃料ポンプおよび内燃機関の燃料供給システム
US9816493B2 (en) * 2013-03-21 2017-11-14 Exergy Engineering Llc Fuel injection pump
DE102013210036A1 (de) * 2013-05-29 2014-12-04 Robert Bosch Gmbh Hochdruckpumpe für ein Kraftstoffeinspritzsystem
CN104061100A (zh) * 2014-06-30 2014-09-24 南岳电控(衡阳)工业技术有限公司 一种高压供油泵所用的密封结构
IT201700095355A1 (it) * 2017-08-23 2019-02-23 Bosch Gmbh Robert Gruppo pompa per alimentare carburante ad un motore a combustione interna

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CN101010508A (zh) 2007-08-01
CN100575700C (zh) 2009-12-30
US7571713B2 (en) 2009-08-11
EP1784571A1 (fr) 2007-05-16
DE502005006224D1 (de) 2009-01-22
JP2008511787A (ja) 2008-04-17
WO2006024569A1 (fr) 2006-03-09
JP4571980B2 (ja) 2010-10-27
ATE417200T1 (de) 2008-12-15
US20070251499A1 (en) 2007-11-01
DE102004041764A1 (de) 2006-03-02

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