EP2336546B1 - Pompe à carburant à haute pression - Google Patents

Pompe à carburant à haute pression Download PDF

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Publication number
EP2336546B1
EP2336546B1 EP11157537.9A EP11157537A EP2336546B1 EP 2336546 B1 EP2336546 B1 EP 2336546B1 EP 11157537 A EP11157537 A EP 11157537A EP 2336546 B1 EP2336546 B1 EP 2336546B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
fuel pump
pressure fuel
valve seat
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
EP11157537.9A
Other languages
German (de)
English (en)
Other versions
EP2336546A1 (fr
Inventor
Siamend Flo
Rainer Wilms
Heinz Siegel
Berthold Pfuhl
Volkmar Goldschmitt
Klaus Lang
Hans-Werner Schlingensief
Peter Ropertz
Joachim Zumbraegel
Martin Laich
Victorio Toscano
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 EP2336546A1 publication Critical patent/EP2336546A1/fr
Application granted granted Critical
Publication of EP2336546B1 publication Critical patent/EP2336546B1/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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves
    • 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
    • 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
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F04B49/035—Bypassing
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements

Definitions

  • the invention relates to a high-pressure fuel pump according to the preamble of claim 1.
  • a high pressure fuel pump of the type mentioned is from the DE 10 2004 013 307 A1 known.
  • the delivery chamber can be connected to a high-pressure outlet via a spring-loaded outlet valve.
  • a pressure limiting valve is provided which has a spring-loaded valve ball as the valve element.
  • the pressure relief valve opens to the pumping chamber and connects in the open state, the high-pressure outlet with the pumping chamber.
  • a pressure relief valve arranged in this way has the advantage that it protects the high-pressure region against impermissibly high pressures, but at the same time does not worsen the degree of delivery of the high-pressure fuel pump, since the pressure relief valve only opens when there is a significantly lower pressure in the delivery chamber than in the high-pressure outlet.
  • Object of the present invention is to provide a high pressure fuel pump of the type mentioned, which works very reliable.
  • a valve seat body of the pressure limiting valve comprises a securing section, which extends in the opening direction of the valve element, for the valve element, which is designed as a substantially annular collar.
  • the throttle device comprises a high pressure side arranged from the pressure relief valve and separated from the pressure relief valve part with a flow restrictor, the previously used pressure relief valves can remain unchanged. This lowers the manufacturing costs.
  • the separate part may be cup-shaped with a bottom portion, wherein the flow restrictor is formed by at least one opening in the bottom portion.
  • Such a part can be inexpensively manufactured as Blechform- and stamped part.
  • the free cross-sectional area is at least approximately 0.6 times to 1.1 times the cross-sectional area of a valve seat of the pressure relief valve.
  • the throttle device may also include a flow restrictor, which in a Valve seat body of the pressure relief valve near or immediately adjacent to the valve seat and seen from this high pressure side is arranged. This eliminates the handling of a separate part, which simplifies the assembly of the fuel high-pressure pump according to the invention.
  • the flow restrictor can be easily formed by a constriction in an inflow channel in the valve seat body.
  • the free cross-sectional area of the flow restrictor should be at least approximately 0.5 times to 0.75 times the cross-sectional area of the valve seat of the pressure relief valve.
  • valve element of the pressure relief valve is a spring-loaded ball in question, which can be loosely installed, which is very cost.
  • the valve seat for such a ball is advantageously conical with a cone angle approximately between 30 ° and 50 °. The smaller the angle, the better the seal in the closed state of the pressure relief valve.
  • a free cross-sectional area of an inflow channel immediately upstream (ie high pressure side) of the valve seat (the term upstream is here based on the flow direction of the pressure relief valve) at least about 0.8 times to 0.95 times the cross-sectional area of the valve seat of the pressure relief valve.
  • a narrow valve seat is advantageous in order to ensure a good dirt resistance of the pressure relief valve can.
  • the seat can be embossed particularly well during operation by such a narrow valve seat.
  • a development provides that the securing portion is formed on a valve seat portion of the pressure relief valve in the vicinity of the valve seat. This reduces the number of parts to be handled during assembly, which simplifies assembly. In addition, the manufacturing costs for the security section are reduced because of Valve seat area of the pressure relief valve must be processed anyway.
  • At least one flow channel in particular a flow pocket, preferably extending essentially over the length of the securing section, is formed on the radial inner side of the securing section, which according to the invention is designed as a substantially annular collar.
  • a flow channel introduced, for example, through a recess permits a low-resistance flow between the valve element and the inside of the securing section when the pressure-limiting valve is open, while at the same time guiding the valve element tightly through the securing section.
  • the fluid can easily flow past between the inside of the securing portion and the open valve element and a possibly this holding valve element holder.
  • the securing portion has at least one preferably substantially extending over its length slot.
  • Such a slot is particularly inexpensive to produce.
  • the radial inner side of the securing section comprises a conical surface which widens in the opening direction of the pressure limiting valve.
  • the cone angle of the conical surface at least approximately correspond to the cone angle of the valve seat, which allows a relatively simple production.
  • the cone angle of the conical surface can also be greater than the cone angle of the valve seat, which leads to a comparatively large clearance between the radial inner side of the securing section on the one hand and the valve element or valve element holder on the other hand even with a small opening stroke of the valve element.
  • valve seat body has a shoulder adjacent to the valve seat and at least approximately radially extending paragraph, from which extends in the opening direction of the pressure relief valve, the radial inner side of the securing portion.
  • This measure can be used both in connection with the above-mentioned flow pockets or flow slots and the above-mentioned conical surface. The heel closing flow forces are avoided on the valve element in its open state.
  • the pressure limiting valve may comprise a piston-like valve element holder, which acts on the valve element in the closing direction and immersed in both the closed and open pressure relief valve in the securing portion. As a result, a particularly secure guidance of the valve element is ensured.
  • a fuel system carries the overall reference numeral 10.
  • the in FIG. 1 Fuel system 10 shown only in simplified form comprises a fuel tank 12, from which a prefeed pump 13 conveys the fuel into a low-pressure fuel line 14. This leads to a high-pressure fuel pump 16, which further compresses the fuel and delivers it to a fuel rail 18 in which the fuel is stored under high pressure and which is also referred to as "rail". To the rail 18 a plurality of injectors 20 are connected, which inject the fuel directly into them associated combustion chambers (not shown) of an internal combustion engine to which the fuel system 10 belongs.
  • the high-pressure fuel pump 16 has a housing 22 with a low-pressure inlet 24 and a high-pressure outlet 26. From the low-pressure inlet 24, an inlet channel 28 leads to an inlet valve 30 (in FIG FIG. 2 not visible) and on to a delivery chamber 32, which is bounded by a pump piston 34. An outlet passage 36 leads to the high-pressure outlet 26 via an outlet valve 38.
  • the inlet valve 30 is integrated into a quantity control valve 40, by means of which the delivery space 32 can be forcibly connected to the region of the inlet passage 28 located upstream of the inlet valve 30. In this way, during a delivery stroke, fuel can be conveyed back to the low-pressure inlet 24 and the delivery rate of the high-pressure fuel pump 16 can be adjusted.
  • a pressure limiting valve 42 is arranged. This is more in detail in FIG. 3 It comprises a valve seat body 44 which is arranged in an overflow channel 46 leading from the high-pressure outlet 26 to the delivery chamber 32 with a fastening region 48 in a press fit. Toward the delivery chamber 32, the outer diameter of the valve seat body 44 tapers toward a valve seat region 50. The outer contour of the valve seat body 44 in this area can also be referred to as bottle neck. This prevents that this valve seat portion 50 is deformed during the pressing of the valve seat body 44 in the overflow 46.
  • the valve seat body 44 is penetrated by an inflow channel 52 in the longitudinal direction, which is designed as a stepped bore whose inner diameter in the valve seat portion 50 is smaller than in the mounting portion 48.
  • the actual valve seat 54 is incorporated for a designed as a valve ball valve element 56.
  • the valve seat 54 is conical with a cone angle in the present case of approximately 30 °.
  • the half cone angle is in FIG. 4 indicated by an arrow with the reference numeral 58. In principle, the cone angle should be approximately between 30 ° and 50 °, with a small cone angle having advantages with respect to the seal.
  • the point of contact of the valve element 56 with the valve seat 54 is linear with a diameter d 1 .
  • the diameter d 2 of the inflow channel 52 is smaller than the diameter d 1 .
  • a free cross-sectional area F d2 of the valve seat 54 as seen from the high pressure port 26 and so far high pressure side arranged inflow channel 52 is immediately adjacent to the valve member 56 at least about 0.8 times to 0.95 times as large as the cross-sectional area F d1 defined by the valve seat diameter d 1 on the valve seat 54.
  • valve element 56 is urged towards the valve seat 54 by a valve element holder 60, which in turn engages a valve spring 62.
  • An immersion depth of the valve element 56 in the inflow channel 52 of the valve seat body 54 is in FIG. 3 denoted by T.
  • a throttle device 64 is held in the overflow 46 in a press fit.
  • This throttle device 64 is in the in the FIGS. 2 to 4 embodiment shown as separate from the pressure relief valve 42 and cup-shaped part 65, which has a bottom portion 66 and an approximately rectangular and circumferential wall portion 68 to this.
  • the part 65 may be made, for example, as sheet metal and stamped part.
  • an opening 70 is present, which has a diameter D 1 and forms a flow restrictor.
  • the free cross-sectional area F D1 on the basis of the diameter D1 of the flow restrictor 70 is 0.6 times the cross-sectional area F d1 on the basis of the diameter d 1 of the valve seat 54 of the pressure relief valve 42.
  • values between the 0 are generally conceivable , 6 times to 1.1 times.
  • the high-pressure fuel pump 16 operates as follows: During a suction stroke of the pump piston 34 opens the inlet valve 30 and fuel flows from the low-pressure fuel line 14 in the delivery chamber 32. In a subsequent delivery stroke of trapped in the delivery chamber 32 fuel is compressed until finally the exhaust valve 38th opens and the fuel is pressed under high pressure in the rail 18. If there is too high a pressure in the rail 18 and thus also in the area of the high-pressure outlet 26, the valve element 56 lifts off from the valve seat 54 and against the force of the valve spring 62 due to the then prevailing pressure difference during a suction stroke of the pump piston 34. In this way, fuel from the rail 18 and the high-pressure outlet 26 via the Overflow 46 and the pressure relief valve 42 flow into the delivery chamber 32. As a result, the rail 18 and the high-pressure outlet 26 is relieved.
  • FIGS. 5 and 6 An alternative embodiment is in the FIGS. 5 and 6 shown.
  • elements and regions which have equivalent functions to previously described elements and regions bear the same reference numerals and are not explained again in detail.
  • the throttle device 64 is not formed as a separate part, but integrated into the valve seat body 44 of the pressure relief valve 42, namely the high pressure side and very close or even immediately adjacent to the valve seat 54 in the form of a constriction 70.
  • Their free cross-sectional area F D1 based on its diameter D 1 , in the present case is approximately 0.5 times the cross-sectional area F d1 of the valve seat 54 of the pressure-limiting valve 42, based on the diameter d 1 .
  • FIGS. 2 to 6 shown high-pressure fuel pumps are not embodiments of the invention.
  • FIG. 7 shows a portion of a first embodiment of a high-pressure fuel pump according to the invention 16. This corresponds in terms of the design of the flow restrictor 70 in the FIGS. 5 and 6 shown embodiment.
  • a Valve element 56 is in the opening direction (arrow 74) of the valve seat body 44 of the pressure relief valve 42 a Valve element 56, so in the axial direction of the pressure relief valve 42 extending annular collar 76 formed, which forms a securing portion for the valve element 56.
  • the collar 76 has a radial outer side 78, with which it bears against the inside of the overflow channel 46.
  • a radial inner side 80 of the collar 76 leads from a radially extending shoulder 82 to the projecting end of the collar 76.
  • the shoulder 82 extends in the radial direction approximately from the valve seat 54, thus adjacent thereto.
  • the valve element holder 60 is in the in FIG. 7 shown embodiment having a piston-like design with an approximately disposed in its axial center annular collar 84, on which the valve spring 62 is supported.
  • a pin-like portion 86 of the valve element holder 60 extends from the annular collar 84, starting from similar to those in the Figures 3 and 5 and 6 shown embodiments, in the limited by the valve spring 62 annular space (without reference numeral) inside.
  • a lying in the vicinity of the annular collar 84 portion 88 of the peg-like portion 86 has an outer diameter which is only slightly smaller than the inner diameter of the valve spring 62. In this way, the valve member holder 60 is held tilting on the valve spring 62.
  • the holding section 90 has a cylindrical outer contour with a diameter that remains constant over its length.
  • a blind hole (not numbered) serves to radially support the valve element 56 on the valve element holder 60.
  • the outer diameter of the holding portion 90 is selected so that the holding portion 90 in the in FIG. 7 Having shown closed position of the pressure relief valve 42 relative to the radial inner side 80 of the collar 76 still has a small distance. In this way it is ensured that the holding portion 90 does not abut the collar 76 before the valve element 56 fully abuts the valve seat 54.
  • the length of the collar 76 and the holding portion 90 are coordinated so that the holding portion 90 of the valve element holder 60 both in the closed and open pressure relief valve 42 in the bounded by the radial inside 80 Interior of the collar 76 dips. Also in this way is ensured by the collar 76 that even with dynamic pressure surges and thereby caused large opening strokes of the valve element 56 this out of the limited space by the collar 76 and instead can reliably find back when closing the pressure relief valve 42 into the valve seat 54 ,
  • FIGS. 9 and 10 shown alternative embodiment of the present invention differs from that of FIGS. 7 and 8 in that instead of the flow pockets in the collar / securing portion 76 whose entire thickness passing through slots 94 are introduced, which also extend from the shoulder 82 over the entire length of the collar 76 to its abragendem end.
  • FIG. 11 Another variant of the present invention shows FIG. 11
  • the radial inside 80 of the collar 76 is formed as in the opening direction 74 of the pressure limiting valve 42 widening conical surface.
  • the holding portion 90 of the valve element holder 60 is similarly conical, but with a smaller cone angle than the radial inner side 80 of the collar 76.
  • the cone angle can have approximately the same cone angle as the valve seat 54 (compare in particular FIG. 4 ), or a larger cone angle than the valve seat 54.
  • valve seat 54 passes directly into the radial inside 80.
  • it follows the valve seat 54 first again a paragraph 82 which extends in the radial direction, and only from this then goes from the conical surface of the radial inner side 80 of the collar 76 from.
  • the shoulder 82 prevents or at least reduces a force acting on the valve element 56 in the closing direction when the valve element 56 is open.
  • FIG. 12 shows FIG. 13 in that the cone angle of the conical surface forming the radial inner side 80 of the collar 76 is comparatively steep and the holding portion 90 is cylindrical with a constant diameter.
  • This variant has the advantage that the outflow behavior when the pressure limiting valve 42 is open is largely independent of the opening stroke of the valve element 56.

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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)
  • Safety Valves (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (18)

  1. Pompe à carburant à haute pression (16), comprenant au moins un espace de refoulement (32), une sortie haute pression (26) et une soupape de limitation de la pression (42) avec un élément de soupape (56) commandé par la différence de pression, qui peut s'ouvrir de la sortie haute pression (26) vers l'espace de refoulement (32), l'élément de soupape (56) pouvant être sollicité vers un siège de soupape (54) par un support d'élément de soupape (60), et un corps de siège de soupape (44) étant disposé dans un canal de tropplein (46) conduisant de la sortie haute pression (26) à l'espace de refoulement (32), caractérisée en ce que, vu depuis le siège de soupape (54) de la soupape de limitation de la pression (42), un dispositif d'étranglement (64) est disposé sur son côté haute pression, dont la section transversale libre (FD1 ; FD2) est au maximum approximativement égale à une section transversale d'ouverture maximale souhaitée (FR) de la soupape de limitation de la pression (42), en ce que le corps de siège de soupape (44) de la soupape de limitation de la pression (42) comprend une portion de fixation (76) pour l'élément de soupape (56) s'étendant dans la direction d'ouverture (74) de l'élément de soupape (56), qui est réalisée sous forme d'un collet (76) essentiellement annulaire, en ce que sur un côté interne radial (80) du collet annulaire (76) est réalisé au moins un canal d'écoulement, et en ce qu'une longueur du collet annulaire (76) et une longueur d'une portion de retenue (90) du support d'élément de soupape (60) sont ajustées l'une à l'autre de telle sorte que seulement la portion de retenue (90) du support d'élément de soupape (60), tant lorsque la soupape de limitation de la pression (42) est fermée que lorsqu'elle est ouverte, plonge dans un espace interne du collet (76) limité par le côté interne radial (80).
  2. Pompe à carburant à haute pression (16) selon la revendication 1, caractérisée en ce que le dispositif d'étranglement (64) comprend une partie (65) disposée du côté haute pression, vu depuis la soupape de limitation de la pression (42), et séparée de la soupape de limitation de la pression (42), avec un étranglement d'écoulement (70).
  3. Pompe à carburant à haute pression (16) selon la revendication 2, caractérisée en ce que la partie séparée (65) est maintenue en ajustement serré dans un canal de débordement (46) d'un boîtier de pompe (22).
  4. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications 2 ou 3, caractérisée en ce que la partie séparée (65) est formée en forme de pot avec une portion de fond (66) et l'étranglement d'écoulement est formé par au moins une ouverture (70) dans la portion de fond (66).
  5. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications 2 à 4, caractérisée en ce que le dispositif d'étranglement (64) est formé par l'étranglement d'écoulement (70), dont la surface en section transversale (FD1) représente approximativement 0,6 à 1,1 fois la surface en section transversale (Fd1) d'un siège de soupape (54) de la soupape de limitation de la pression (42).
  6. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que le dispositif d'étranglement (64) comprend un étranglement d'écoulement (70) qui est disposé dans un corps de siège de soupape (44) de la soupape de limitation de la pression (42) près, ou directement à côté, du siège de soupape (54) et du côté haute pression, vu depuis celui-ci.
  7. Pompe à carburant à haute pression (16) selon la revendication 6, caractérisée en ce que l'étranglement d'écoulement est formé par un rétrécissement (70) dans un canal d'afflux (52) dans le corps de siège de soupape (44).
  8. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications 5 ou 6, caractérisée en ce que le dispositif d'étranglement (64) est forme par l'étranglement d'écoulement (70) dont la surface en section transversale libre (FD2) représente au moins approximativement 0,5 à 0,75 fois la surface en section transversale (Fd1) du siège de soupape (54) de la soupape de limitation de la pression (42).
  9. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'élément de soupape de la soupape de limitation de la pression (42) comprend une bille (56) sollicitée par ressort, et en ce que le siège de soupape (54) est conique, avec un angle de conicité (58) compris entre environ 30° et 50°.
  10. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications précédentes, caractérisée en ce qu'une surface de section transversale libre (Fd2) du canal d'afflux (52) directement en amont du siège de soupape (54) vaut au moins approximativement 0,8 fois à 0,95 fois la surface en section transversale (Fd1) du siège de soupape (54) de la soupape de limitation de la pression (42).
  11. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que la portion de fixation (76) est façonnée sur une région de siège de soupape (50) de la soupape de limitation de la pression (42) à proximité de son siège de soupape (54).
  12. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que l'au moins un canal d'écoulement s'étend de préférence essentiellement sur la longueur de la portion de fixation (76) sur le coté intérieur (80) de la portion de fixation (76) et est réalisé notamment sous forme d'une cavité d'écoulement (92).
  13. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que la portion de fixation (76) présente au moins une fente (94) s'étendant de préférence sur sa longueur.
  14. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que le côté interne radial (80) de la portion de fixation (76) comprend une surface conique s'élargissant dans la direction d'ouverture (74) de la soupape de limitation de la pression (42).
  15. Pompe à carburant à haute pression (16) selon la revendication 14, caractérisée en ce que l'angle de conicité de la surface conique (80) correspond au moins approximativement à l'angle de conicité du siège de soupape (54).
  16. Pompe à carburant à haute pression (16) selon la revendication 14, caractérisée en ce que l'angle de conicité de la surface conique (80) est supérieur à l'angle de conicité du siège de soupape (54).
  17. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications précédentes, caractérisée en ce que le corps de siège de soupape (44) présente un épaulement (82) adjacent au siège de soupape (54) et s'étendant approximativement radialement, depuis lequel le côté interne radial (80) de la portion de fixation (76) s'étend dans la direction d'ouverture (74) de la soupape de limitation de la pression (42).
  18. Pompe à carburant à haute pression (16) selon l'une quelconque des revendications 1 à 15, caractérisée en ce que la soupape de limitation de la pression (42) comprend un support d'élément de soupape de type piston (60), qui sollicite l'élément de soupape (56) dans la direction de fermeture et qui plonge dans l'espace interne limite par la portion de fixation (76) à la fois lorsque la soupape de limitation de la pression (42) est fermée et lorsqu'elle est ouverte.
EP11157537.9A 2006-04-25 2007-04-16 Pompe à carburant à haute pression Not-in-force EP2336546B1 (fr)

Applications Claiming Priority (3)

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DE102006019049 2006-04-25
DE102007016134A DE102007016134A1 (de) 2006-04-25 2007-03-29 Kraftstoff-Hochdruckpumpe
EP07728147A EP2013469B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression

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EP07728147A Division EP2013469B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression

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EP2336546B1 true EP2336546B1 (fr) 2014-06-18

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EP11157537.9A Not-in-force EP2336546B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression
EP11157492A Not-in-force EP2333304B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression
EP07728147A Active EP2013469B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression

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EP07728147A Active EP2013469B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression

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EP (3) EP2336546B1 (fr)
JP (1) JP5069288B2 (fr)
CN (1) CN101432518B (fr)
DE (1) DE102007016134A1 (fr)
ES (2) ES2479691T3 (fr)
WO (1) WO2007122127A1 (fr)

Families Citing this family (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008057451A (ja) * 2006-08-31 2008-03-13 Hitachi Ltd 高圧燃料供給ポンプ
JP4380739B2 (ja) 2007-07-06 2009-12-09 株式会社デンソー 高圧燃料ポンプ
JP4595996B2 (ja) * 2007-11-16 2010-12-08 トヨタ自動車株式会社 内燃機関の高圧燃料供給装置
DE102008043217A1 (de) * 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
DE102009014072B4 (de) * 2009-03-20 2014-09-25 Continental Automotive Gmbh Common-Rail-Einspritzsystem sowie Verfahren zur Druckentlastung eines Common-Rail-Einspritzsystems
IT1396473B1 (it) * 2009-03-30 2012-12-14 Magneti Marelli Spa Pompa carburante con una valvola di massima pressione perfezionata per un sistema di iniezione diretta
JP5158219B2 (ja) * 2010-06-29 2013-03-06 株式会社デンソー リリーフ弁及びこれを用いた高圧ポンプ
JP5770458B2 (ja) * 2010-11-30 2015-08-26 アルバック機工株式会社 ポンプシステム
DE102011005487A1 (de) * 2011-03-14 2012-09-20 Robert Bosch Gmbh Ventileinrichtung, insbesondere Auslassventil einer Kraftstoff-Hochdruckpumpe einer Brennkraftmaschine
DE102011089288A1 (de) 2011-12-20 2013-06-20 Robert Bosch Gmbh Mengensteuerventil, und Hochdruckpumpe mit Mengensteuerventil
FI20126142A (fi) * 2012-11-01 2014-05-02 Waertsilae Finland Oy Polttoaineen ruiskutusjärjestelmä ja varoventtiilijärjestely
DE102013210760A1 (de) 2013-06-10 2014-12-11 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für ein Kraftstoffsystem für eine Brennkraftmaschine
DE102013215754A1 (de) * 2013-08-09 2015-02-12 Robert Bosch Gmbh Ventil zum hydraulischen Ansteuern einer Zumessblende, über die ein hydraulischer Verbraucher mit Druckmittel versorgbar ist, sowie hydraulische Anordnung mit einer Zumessblende und mindestens einem derartigen Ventil
JP6193402B2 (ja) * 2013-12-27 2017-09-06 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
DE102014202957A1 (de) 2014-02-18 2015-08-20 Continental Automotive Gmbh Druckbegrenzungsventilvorrichtung für ein Hochdrucksystem
US9556836B2 (en) * 2014-04-21 2017-01-31 Stanadyne Llc Pressure relief valve for single plunger fuel pump
JP6302735B2 (ja) * 2014-04-24 2018-03-28 Ｋｙｂ株式会社 リリーフ弁
DE102014208891B3 (de) * 2014-05-12 2015-09-24 Continental Automotive Gmbh Druckbegrenzungsventil und Bauteil für ein Kraftstoffeinspritzsystem sowie Verfahren zur Herstellung eines Druckbegrenzungsventils
DE102014214627B4 (de) * 2014-07-25 2020-04-02 Continental Automotive Gmbh Hochdruckpumpe
EP2993341B1 (fr) * 2014-09-08 2017-03-29 Magneti Marelli S.p.A. Pompe a combustible pour systeme a injection directe
JP2016109032A (ja) * 2014-12-05 2016-06-20 株式会社デンソー 高圧ポンプ
US20170356412A1 (en) * 2015-01-26 2017-12-14 Hitachi Automotive Systems, Ltd. Valve mechanism and high-pressure fuel supply pump including valve mechanism
US10006423B2 (en) 2015-03-06 2018-06-26 Hitachi Automotive Systems Americas Inc. Automotive fuel pump
JP6432440B2 (ja) * 2015-05-15 2018-12-05 株式会社デンソー 高圧ポンプ
DE102015210800A1 (de) * 2015-06-12 2016-12-15 Continental Automotive Gmbh Ventilvorrichtung für ein Kraftstoffeinspritzsystem und Kraftstoffeinspritzsystem
CN105090151A (zh) * 2015-09-01 2015-11-25 芜湖德孚转向系统有限公司 一种安装于变量泵中的阀体
DE102017212003A1 (de) * 2016-09-16 2018-03-22 Robert Bosch Gmbh Überströmventil, insbesondere zur Verwendung in einem Kraftstoffeinspritzsystem, Hochdruckpumpe sowie Kraftstoffeinspritzsystem
DE102017204925B3 (de) 2017-03-23 2018-09-13 Continental Automotive Gmbh Ventilanordnung für ein Kraftstoffeinspritzsystem sowie Kraftstoffeinspritzsystem
US10094346B1 (en) * 2017-10-18 2018-10-09 MAGNETI MARELLI S.p.A. Fuel pump with an improved maximum-pressure valve for a direct-injection system
DE102018202928A1 (de) * 2018-02-27 2019-08-29 Robert Bosch Gmbh Druckbegrenzungsventil
JP7139265B2 (ja) * 2019-02-19 2022-09-20 日立Astemo株式会社 高圧燃料供給ポンプ及びリリーフ弁機構
DE102019210655A1 (de) * 2019-07-18 2021-01-21 Vitesco Technologies GmbH Ventilvorrichtung für ein Kraftstoffversorgungssystem und Kraftstoffhochdruckpumpe für eine Brennkraftmaschine
DE102019210653A1 (de) * 2019-07-18 2021-01-21 Vitesco Technologies GmbH Ventilvorrichtung für ein Kraftstoffversorgungssystem einer Brennkraftmaschine
DE102019210654B4 (de) * 2019-07-18 2023-12-14 Vitesco Technologies GmbH Ventilvorrichtung für ein Kraftstoffversorgungssystem einer Brennkraftmaschine
DE102020208228A1 (de) * 2019-07-19 2021-01-21 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe
DE102019212247A1 (de) * 2019-08-15 2021-02-18 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
EP4286718A1 (fr) * 2021-09-03 2023-12-06 Hitachi Astemo, Ltd. Pompe à carburant

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3269406A (en) * 1965-03-25 1966-08-30 Ansel B Grose Valve
DE7925377U1 (de) 1979-09-07 1979-12-06 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US4675003A (en) * 1985-12-23 1987-06-23 Cordis Corporation Three stage pressure regulator valve
FR2606454B1 (fr) 1986-11-06 1990-04-20 Peugeot Clapet antiretour pour circuit de liquide sous pression dans un moteur a combustion interne, et moteur equipe de ce clapet
JPS63297170A (ja) * 1987-05-27 1988-12-05 Toyoda Mach Works Ltd 流体絞り装置
US5265644A (en) 1992-06-02 1993-11-30 Walbro Corporation Fuel pressure regulator
DE4426667A1 (de) 1994-07-28 1996-02-01 Bosch Gmbh Robert Vorrichtung zum Fördern von Kraftstoff aus einem Vorratsbehälter zur Brennkraftmaschine eines Kraftfahrzeuges
DE4430472A1 (de) 1994-08-27 1996-02-29 Bosch Gmbh Robert Druckregelventil
DE19548167A1 (de) 1995-12-22 1997-06-26 Bosch Gmbh Robert Druckregelventil
DE19739904A1 (de) 1997-09-11 1999-03-18 Bosch Gmbh Robert Rückschlagventil, insbesondere für eine Kolbenpumpe
DE19927197B4 (de) 1999-06-15 2013-10-10 Robert Bosch Gmbh Ventil, insbesondere Rückschlagventil für eine Hochdruckpumpe
DE10059425A1 (de) * 2000-11-30 2002-06-06 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen, insbesondere Dieselmotoren
JP2002250258A (ja) * 2001-02-22 2002-09-06 Denso Corp 燃料噴射装置用定残圧弁
DE10231135A1 (de) * 2002-07-10 2004-01-29 Robert Bosch Gmbh Druckentlastungsventil
EP1411238B1 (fr) * 2002-10-15 2006-01-11 Robert Bosch Gmbh Soupape de limitation de pression pour un système d'injection de carburant
JP2006504904A (ja) * 2002-10-31 2006-02-09 ローベルト　ボツシユ　ゲゼルシヤフト　ミツト　ベシユレンクテル　ハフツング 低圧入口に玉型弁を備えた燃料高圧ポンプ
DE10251014A1 (de) * 2002-11-02 2004-05-19 Robert Bosch Gmbh Kraftstoffzumesseinheit für Kraftstoffeinspritzanlagen von Brennkraftmaschinen
DE10355124B4 (de) 2003-11-24 2005-09-22 L'orange Gmbh Druckbegrenzungsventil für Kraftstoff-Einspritzeinrichtungen
JP2005214303A (ja) * 2004-01-29 2005-08-11 Aisin Seiki Co Ltd リリーフバルブ
DE102004013307B4 (de) 2004-03-17 2012-12-06 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil

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CN101432518A (zh) 2009-05-13
US20090252621A1 (en) 2009-10-08
JP5069288B2 (ja) 2012-11-07
EP2336546A1 (fr) 2011-06-22
EP2333304A1 (fr) 2011-06-15
DE102007016134A1 (de) 2007-11-08
ES2479691T3 (es) 2014-07-24
WO2007122127A1 (fr) 2007-11-01
CN101432518B (zh) 2012-07-11
ES2370854T3 (es) 2011-12-23
EP2013469B1 (fr) 2011-09-28
US8202065B2 (en) 2012-06-19
EP2333304B1 (fr) 2012-08-22
JP2009534582A (ja) 2009-09-24
EP2013469A1 (fr) 2009-01-14

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