EP2333304A1 - Pompe à carburant à haute pression - Google Patents

Pompe à carburant à haute pression Download PDF

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Publication number
EP2333304A1
EP2333304A1 EP11157492A EP11157492A EP2333304A1 EP 2333304 A1 EP2333304 A1 EP 2333304A1 EP 11157492 A EP11157492 A EP 11157492A EP 11157492 A EP11157492 A EP 11157492A EP 2333304 A1 EP2333304 A1 EP 2333304A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
fuel pump
valve seat
pressure fuel
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.)
Granted
Application number
EP11157492A
Other languages
German (de)
English (en)
Other versions
EP2333304B1 (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 EP2333304A1 publication Critical patent/EP2333304A1/fr
Application granted granted Critical
Publication of EP2333304B1 publication Critical patent/EP2333304B1/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.
  • 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 is arranged in a valve seat body of the pressure relief valve near or immediately adjacent to the valve seat and from this high pressure side. 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 effective.
  • 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 particularly advantageous embodiment of the high-pressure fuel pump according to the invention provides that a valve seat body of the pressure relief valve comprises a securing section extending in the opening direction of the valve element for the valve element, which is designed as a substantially annular collar.
  • the valve element is secured in the open, so lifted from the valve seat state in the lateral direction, so that it is impossible even when dynamic pressure surges and large opening stroke that the valve element between valve seat body and a valve element acting on the valve spring is jammed.
  • the reliability of the fuel high-pressure pump is improved by this measure according to the invention, since it prevents the pressure relief valve jammed in the open state and thereby a high-pressure construction of the high-pressure fuel pump is impossible.
  • the securing section ultimately ensures that the valve element finds its way back safely to the valve seat even with a large stroke.
  • a development for this purpose 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 securing portion are reduced, since the valve seat portion of the pressure relief valve must be processed anyway.
  • At least one flow channel in particular a flow pocket, is formed on the radially inner side of the securing section, preferably at least one flow channel which extends essentially over the length of the securing section.
  • 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 extending at least approximately radially, from which the radial inner side of the securing section extends in the opening direction of the pressure limiting valve.
  • This measure can be related both to the above Flow pockets or flow slots as well as the above cone surface use find. 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 to the low pressure inlet 24th fed back and hereby the delivery 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 from the high pressure port 26 and thus high pressure side arranged inflow 52 immediately adjacent to the valve element 56 at least about 0.8 times to 0.95 times as large as the cross-sectional area F. d1 , which is 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 Fd 1 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: In 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 can flow out of the rail 18 or the high-pressure outlet 26 via the overflow channel 46 and the pressure-limiting valve 42 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 in the valve seat body 44 of the pressure limiting valve 42, namely 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 their diameter D 1 , in this case about 0.5 times the cross-sectional area Fd 1 of the valve seat 54 of the pressure relief valve 42, based on the diameter d 1 .
  • FIG. 7 shows a portion of yet another alternative embodiment of a high-pressure fuel pump 16. This corresponds with respect to the execution of the flow restrictor 70 in the FIGS. 5 and 6 shown embodiment.
  • annular collar 76 extending in the opening direction (arrow 74) of the valve element 56, that is to say in the axial direction of the pressure limiting valve 42, which forms a securing section for the valve element 56, is integrally formed on the valve seat body 44 of the pressure limiting valve 42.
  • 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 annular space bounded by the valve spring 62 (without reference number) into it.
  • 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 immersed in both the closed and open pressure relief valve 42 in the limited of the radial inner surface 80 interior of the collar 76. Also in this way is ensured by the collar 76 that even with dynamic pressure surges and thereby causing large opening strokes of the valve element 56 this out of the limited space by the collar 76 and instead reliably find when closing the pressure relief valve 42 back into the valve seat 54 ,
  • FIGS. 9 and 10 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 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.
  • valve seat 54 is initially followed by a shoulder 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.
  • 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)
EP11157492A 2006-04-25 2007-04-16 Pompe à carburant à haute pression Not-in-force EP2333304B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
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

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP07728147.5 Division 2007-04-16
EP07728147A Division EP2013469B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression

Publications (2)

Publication Number Publication Date
EP2333304A1 true EP2333304A1 (fr) 2011-06-15
EP2333304B1 EP2333304B1 (fr) 2012-08-22

Family

ID=38565035

Family Applications (3)

Application Number Title Priority Date Filing Date
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
EP11157537.9A Not-in-force EP2336546B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP07728147A Active EP2013469B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression
EP11157537.9A Not-in-force EP2336546B1 (fr) 2006-04-25 2007-04-16 Pompe à carburant à haute pression

Country Status (7)

Country Link
US (1) US8202065B2 (fr)
EP (3) EP2333304B1 (fr)
JP (1) JP5069288B2 (fr)
CN (1) CN101432518B (fr)
DE (1) DE102007016134A1 (fr)
ES (2) ES2479691T3 (fr)
WO (1) WO2007122127A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019166136A1 (fr) * 2018-02-27 2019-09-06 Robert Bosch Gmbh Soupape de limitation de pression
WO2021013507A1 (fr) * 2019-07-19 2021-01-28 Robert Bosch Gmbh Pompe à carburant à haute pression

Families Citing this family (35)

* 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
US10371109B2 (en) 2013-12-27 2019-08-06 Hitachi Automotive Systems, Ltd. High-pressure fuel supply pump
DE102014202957A1 (de) 2014-02-18 2015-08-20 Continental Automotive Gmbh Druckbegrenzungsventilvorrichtung für ein Hochdrucksystem
ES2756750T3 (es) * 2014-04-21 2020-04-27 Stanadyne Llc Válvula de descarga de presión para bomba de combustible de émbolo único
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
JP6342020B2 (ja) * 2015-01-26 2018-06-13 日立オートモティブシステムズ株式会社 弁機構及びこれを備えた高圧燃料供給ポンプ
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
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DE102019210654B4 (de) * 2019-07-18 2023-12-14 Vitesco Technologies GmbH Ventilvorrichtung für ein Kraftstoffversorgungssystem einer Brennkraftmaschine
DE102019210655A1 (de) * 2019-07-18 2021-01-21 Vitesco Technologies GmbH Ventilvorrichtung für ein Kraftstoffversorgungssystem und Kraftstoffhochdruckpumpe für eine Brennkraftmaschine
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EP2336546A1 (fr) 2011-06-22
EP2013469A1 (fr) 2009-01-14
ES2370854T3 (es) 2011-12-23
DE102007016134A1 (de) 2007-11-08
WO2007122127A1 (fr) 2007-11-01
US20090252621A1 (en) 2009-10-08
JP2009534582A (ja) 2009-09-24
EP2333304B1 (fr) 2012-08-22
JP5069288B2 (ja) 2012-11-07
EP2013469B1 (fr) 2011-09-28
ES2479691T3 (es) 2014-07-24
EP2336546B1 (fr) 2014-06-18
CN101432518B (zh) 2012-07-11
US8202065B2 (en) 2012-06-19
CN101432518A (zh) 2009-05-13

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