EP2522854A1 - Agencement de soupape pour une pompe à carburant haute pression ainsi qu'une pompe à carburant haute pression - Google Patents

Agencement de soupape pour une pompe à carburant haute pression ainsi qu'une pompe à carburant haute pression Download PDF

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Publication number
EP2522854A1
EP2522854A1 EP12165970A EP12165970A EP2522854A1 EP 2522854 A1 EP2522854 A1 EP 2522854A1 EP 12165970 A EP12165970 A EP 12165970A EP 12165970 A EP12165970 A EP 12165970A EP 2522854 A1 EP2522854 A1 EP 2522854A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
pump
working space
pump working
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.)
Withdrawn
Application number
EP12165970A
Other languages
German (de)
English (en)
Inventor
Alessandro De Luca
Dirk Vahle
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 EP2522854A1 publication Critical patent/EP2522854A1/fr
Withdrawn legal-status Critical Current

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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
    • F04B1/0452—Distribution members, e.g. 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
    • 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
    • F02M59/462—Delivery 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
    • 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
    • F02M63/0031—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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/10—Valves; Arrangement of valves
    • F04B53/109—Valves; Arrangement of valves inlet and outlet valve forming one unit
    • 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
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided

Definitions

  • the invention relates to a valve arrangement for a high-pressure fuel pump with the features of the preamble of claim 1. Furthermore, the invention relates to a high-pressure fuel pump with such a valve arrangement.
  • a radial piston pump for supplying an internal combustion engine with fuel comprising a valve assembly of the type mentioned above.
  • the radial piston pump further comprises at least one of a cam or eccentric of a rotating drive shaft in a cylinder of a housing reciprocally movable piston with a piston axis enclosing cylindrical surface and an end face defining a pump space of the housing.
  • a suction line containing a suction valve with a first orifice and a high-pressure valve containing a high-pressure line open with a second orifice.
  • first and the second orifice in order to allow pump pressures of more than 2000bar without damaging the cylinder head of the radial piston pump, it is further proposed to design and arrange the first and the second orifice in such a way that they concentrically surround a common axis at their end facing the pump chamber.
  • the common axis preferably coincides with the longitudinal axis of the pump piston.
  • the radial piston pump described herein has a valve arrangement with a suction valve and a high-pressure valve, which are contained at least partially in an insert body which is sealingly inserted into the cylinder head above the pump space.
  • the suction valve has a pump chamber facing disc-shaped closing member which is held by the spring force of a compression spring in contact with the insert body.
  • the proposed radial piston pump therefore has an extremely short length in the axial direction.
  • the object of the present invention is to further develop a valve arrangement of the aforementioned type such that the valve arrangement is suitable for even higher pump pressures, for example for pump pressures of 2500 bar and more.
  • valve arrangement having the features of claim 1.
  • Advantageous embodiments of the invention are specified in the subclaims.
  • a high-pressure fuel pump is provided with such a valve arrangement for achieving the above-mentioned object.
  • the proposed valve arrangement comprises two valves arranged concentrically with respect to a common longitudinal axis A, of which the first valve serves as an inlet valve and the second valve as an outlet valve, so that via the first valve a pump working space can be filled with fuel and via the second valve in the pump working space pressurized fuel can be supplied to a high-pressure line.
  • the valves each have a with a valve seat cooperating, along the longitudinal axis A back and forth movable valve member, wherein the valve member of the first valve is designed as a hollow body with a through hole through which the pump working space with the second valve is connectable.
  • the pump working chamber can also be connected via the through-bore with a low-pressure volume which surrounds the valve member of the first valve designed as a hollow body.
  • a low-pressure volume which surrounds the valve member of the first valve designed as a hollow body.
  • the low-pressure volume is formed in a valve body and / or a housing part of the high-pressure fuel pump.
  • the formed as a hollow body valve member of the first valve thus seals both in its function as a liftable valve member, and as the low-pressure volume radially limiting body from the high pressure region of the valve assembly relative to the low pressure region.
  • the sealing points can be reduced to a minimum.
  • the tightness in the region of the sealing points can also be realized via a component, namely the valve member of the first valve. Due to its rotationally symmetrical design, the valve member is subjected to a uniform load when subjected to high pressure, which leads to a uniform deformation over the circumference of the valve member. The deformation can, in turn, be used to increase the sealing effect of the valve member in the region of sealing and / or guide surfaces formed on the outer side of the valve member.
  • the through-bore serves as both an inlet and outlet. Accordingly, the through-hole is alternately traversed by fuel in both directions and consequently subjected to alternating low-pressure and high-pressure.
  • designed as a hollow body valve member of the first valve has a guide portion having an outer diameter D 2 , with which the valve member is received axially displaceably in a guide bore.
  • the guide bore is preferably formed in the valve body and / or in the housing part. Further preferably, the guide bore formed in the valve body and / or in the housing part merges into the low-pressure volume, which is likewise formed in the valve body and / or in the housing part.
  • the guide bore may, for example, be designed as a stepped bore, which widens into the low-pressure volume.
  • the inner diameter of the guide bore substantially corresponds to the outer diameter D 2 of the guide section formed on the valve body in order to ensure a high-pressure-tight guide region.
  • the guide bore which is preferably formed in the valve body and / or in the housing part, directly adjoins the pump working chamber in the axial direction.
  • the pump working space preferably has an inner diameter D 1 , which is smaller than the outer diameter D 2 of the guide portion of the valve member of the first valve and thus smaller than the inner diameter of the guide bore.
  • serving as a stroke stop radially extending step is formed on the valve body or on the housing part, by means of which the stroke of the valve member of the first valve can be fixed.
  • serving as a stroke stop radially extending step is formed on the valve member, which for this purpose has a further portion with an outer diameter D 6 , which is greater than the outer diameter D 2 of the guide portion.
  • the guide bore formed in the valve body and / or in the housing part and the pump working chamber can then have the same inner diameter D 1 .
  • the outer diameter D 2 of the guide member formed on the valve member corresponds in this case to the inner diameter D 1 .
  • the through hole of the valve member of the first valve has an inner diameter D 3 , which is smaller than the inner diameter D 1 of the pump working space.
  • this keeps the damaged volume low
  • the fuel flowing into or out of the pump working chamber into the pump working space undergoes throttling.
  • a closing force can be effected via the pump working space defining end face, which causes a closing of the first valve in the conveying operation of the high-pressure fuel pump.
  • valve member of the first valve is acted upon by the pressure force of a closing spring, which is supported on the one hand on a radially extending shoulder of the valve member, on the other hand on the valve body or the housing part.
  • the closing spring causes a bias of the valve member in the axial direction.
  • the valve member of the first valve has a cooperating with the valve seat sealing surface which is formed on the pump working space facing away from the end face and has a sealing diameter D 4 , which is preferably smaller than the outer diameter D 2 of the guide portion of the valve member.
  • the sealing surface may be flat, conical, concave or convex.
  • the conical, concave or convex design of the sealing surface has the advantage that a biting edge defining the sealing diameter D 4 is formed, with which the valve member sealingly bears against the valve seat of the first valve.
  • the valve seat is preferably designed as a flat seat. In addition, however, the valve seat can also be designed conical, concave or convex.
  • the sealing diameter D 4 can also be greater than the outer diameter D 2 of the guide portion of the valve member of the first valve can be selected so that the ratio D 2 / D 4 ⁇ 1 and not> 1.
  • About the diameter ratio and the spring force of the closing spring required for filling the pump working space with fuel differential pressure between the pressure in the pump working chamber and the pressure in the low pressure volume can be influenced. To fill the pump work space with fuel, the pressure in the pump work space must be below the pressure in the low pressure volume.
  • the diameter ratio D 2 / D 4 as a hydraulic design parameter for the filling of the pump working space must therefore be selected depending on the requirements of the pump delivery.
  • the diameter ratio D 2 / D 4 > 1 is formed by a remaining annular surface according to the formula ⁇ / 4 * (D 2 2 -D 3 2 ) and the internal pressure an additional sealing holding force on the formed on the valve member of the first valve Sealing surface causes, which contributes to the improvement of the sealing of the high pressure area relative to the low pressure area.
  • An improved sealing effect in the region of the guide section of the valve member of the first valve can be achieved by a radial widening of the valve member in the region of the guide section.
  • a radial expansion requires that the valve member on the inner circumference side via the through hole with high pressure and the outer circumference is subjected to low pressure. With rising Hydraulic pressure in the through hole increases the radial expansion of the valve member, so that reduces the guide gap between the guide portion and the guide bore. The guide gap can even be completely closed in this way.
  • the through-hole has a conically extending portion.
  • the conical extending portion is formed and arranged to face the pump working space and has a tapered cross section toward the valve seat.
  • the through hole then has the inner diameter D 3 .
  • the conical section causes a uniform expansion of the valve member in the region of the guide portion, so that an improved sealing effect is achieved.
  • a pump piston cooperating with the valve arrangement is provided on the end face with a filling body dipping into the through-bore, so that the void volume is reduced to a minimum.
  • the geometry of the filling body is preferably selected corresponding to the geometry of the through hole. If this has, for example, a conically extending section, the filler body is preferably designed as a conical truncated cone. In the case of a cylindrical through-bore may be formed on the pump piston a simple cylindrical approach.
  • the valve member of the second valve to form a part-spherical sealing surface is at least partially spherical.
  • the part-spherical sealing surface in turn cooperates with a valve seat, which is preferably formed conical.
  • a good sealing effect can be achieved.
  • valve member of the second valve is acted upon by the pressure force of a closing spring.
  • the task of the closing spring is to hold the valve member of the second valve in contact with the valve seat.
  • the valve member of the second Valve has a throttle bore, which connects the pump working space with the high pressure line. About the throttle bore acting on the valve member hydraulic closing force can be effected.
  • a stroke stop may be formed, which limits the stroke of the valve member.
  • a stop plate be used to form a Hubanschlages.
  • the solution to the above-mentioned object also proposed high-pressure fuel pump for a fuel injection system for injecting fuel into the combustion chamber of an internal combustion engine is characterized in that it comprises a valve assembly according to the invention.
  • the valve assembly is received in a housing part of the high-pressure fuel pump.
  • FIG. 1 The schematic longitudinal section of FIG. 1 is a first preferred embodiment of a valve assembly according to the invention can be seen.
  • This comprises a first valve 1 serving as an inlet valve and a second valve 2 serving as an outlet valve, which are formed concentrically with respect to a common longitudinal axis A.
  • the first and the second valve 1, 2 each have a valve member 7, 8, which cooperates with a valve seat 5, 6 and can be moved back and forth along the longitudinal axis A and which is in each case rotationally symmetrical with respect to the longitudinal axis A.
  • the valve member 7 of the first valve 1 is designed as a hollow body with a central through-hole 9, which - when using the valve arrangement in a high-pressure fuel pump according to the invention - opens into a pump working space 3.
  • the through-hole 9 connects the pump working chamber 3 with the second valve 2, which - viewed from the pump working space - is arranged in the axial direction behind the first valve 1. Via the second valve 2, the pump working space 3 can be connected to a high-pressure line 4.
  • the through hole 9 of the valve member 7 of the first valve 1 has an inner diameter D 3 , which is smaller than the inner diameter D 1 of the pump working space 3 is selected.
  • the valve member 7 of the first valve 1 has a guide portion 13, with which the valve member 7 is guided axially displaceably in a guide bore 14.
  • the guide section 13 has an outer diameter D 2 , which in the present case is larger than the inner diameter D 1 of the pump working chamber 3, so that in the transition region of the guide bore 14 in the pump working space 3 serving as a stroke stop radially extending step 15 is formed, on which the valve member. 7 strikes when performing an opening stroke.
  • the stroke of the valve member 7 is in FIG. 1 indicated by the reference H.
  • the pump working chamber 3 and the guide bore 14 are formed in a valve body 10, which - in the present example - is inserted into a housing part 11 of a high-pressure pump.
  • the pump working chamber 3 and the guide bore 14 may also be formed directly in the housing part 11, for example in the cylinder head of the high-pressure pump.
  • the low-pressure volume 12 is therefore limited radially by the valve member 7.
  • the pump working space 3 is supplied with fresh fuel via an inlet bore 24 which opens into the low-pressure volume 12 and extends essentially radially, as well as the low-pressure volume 12.
  • valve seat 5 To form a cooperating with the valve seat 5 sealing surface 18, the valve member 7 of the first valve 1 on its side facing away from the pump working chamber 3 end face on a frusto-conical sealing geometry.
  • the valve seat 5 is in the present case designed as a flat seat.
  • the sealing diameter D 4 of the frusto-conical sealing geometry is smaller than the inner diameter D 1 of the pump working chamber 3 chosen.
  • the frustoconical sealing geometry widens to a sealing cone whose outer diameter is greater than the outer diameter D 2 of the guide portion 13 of the valve member 7.
  • a radially extending shoulder 17 is formed on the valve member 7, on which a closing spring 16 is supported. With its other end, the closing spring 16 is supported on the valve body 10.
  • the closing spring 16 causes an axial bias of the valve member 7 in the direction of its valve seat fifth
  • the valve member 8 of the second valve 2 is embodied here as a ball and thus has a part-spherical sealing surface 20. This cooperates with the valve seat 6, which in the present case is cone-shaped.
  • a stroke stop 25 for the valve member 8 of the second valve 2 a stop plate with flow openings for the outflowing fuel is inserted into the valve body 10. Via the flow-through openings of the stop plate, the fuel passes into the high-pressure line 4, which in the present case is formed in a connection element 26 which is inserted into the valve body 10.
  • All high-pressure components in particular the valve body 10 and the valve member 7 of the first valve 1 accommodated therein, are rotationally symmetrical with respect to the longitudinal axis A.
  • the components are therefore exposed over its circumference of a uniform load. This leads in the case of the valve member 7 that this expands radially when exposed to high pressure in the region of the guide portion 13. This leads to a reduction of the guide gap between the guide portion 13 and the valve body 10 formed in the guide bore 14, so that the Sealing effect is improved.
  • the valve assembly is thus able to absorb fuel pressures of more than 2500 bar.
  • FIG. 2 differs from the previously described in that the spherical valve member 8 of the second valve 2 is acted upon in the closing direction by the spring force of a closing spring 21.
  • the FIG. 2 shows the valve assembly also with open first valve 1 and closed second valve 2, that is, in the suction operation of the high pressure pump, while in the representation of the FIG. 1 exactly the reverse behaves.
  • FIG. 1 shows the valve assembly accordingly in the conveying operation of the high-pressure pump.
  • FIG. 2 H also denotes the stroke of the valve member 8 of the second valve. 2
  • FIG. 3 A further preferred embodiment of a valve arrangement according to the invention is the FIG. 3 refer to.
  • the valve member 8 is formed as a dome, that is as a cylinder with a frontally formed part-spherical sealing geometry. Via the cylindrical part, the valve member 8 of the second valve 2 is guided axially displaceably in a guide bore 27.
  • the valve member 8 has a throttle bore 22, which replaces a closing spring 21 or can be used in addition to a closing spring 21 in order to support their function.
  • the latter variant is in the FIG. 4 shown.
  • FIGS. 5 and 6 Further preferred embodiments of a valve arrangement according to the invention are the FIGS. 5 and 6 refer to.
  • the focus here is always to be directed to the formation of the first valve 1.
  • the second valve 2 can arbitrarily according to one of the in the Figure 1 to 4 be formed illustrated embodiments.
  • a pump piston 23 of a pump element of the high-pressure pump has on its end face facing the valve member 7 a filling body 28 whose geometry corresponds to the geometry of the through-hole 9.
  • the filler 28 dips into the through hole 9, so that the harmful volume is reduced.
  • the geometry of the through hole 9 can - as in the FIG.
  • a conical portion 19 include.
  • the conical portion 19 causes a uniform load on the valve member 7 in the region of its guide portion 13 so that it undergoes a uniform radial expansion. This in turn means that the guide gap between the guide portion 13 and the guide bore 14 is uniformly reduced over the circumference and thus the sealing effect is improved.

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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)
EP12165970A 2011-05-09 2012-04-27 Agencement de soupape pour une pompe à carburant haute pression ainsi qu'une pompe à carburant haute pression Withdrawn EP2522854A1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201110075516 DE102011075516A1 (de) 2011-05-09 2011-05-09 Ventilanordnung für eine Kraftstoffhochdruckpumpe sowie Kraftstoffhochdruckpumpe

Publications (1)

Publication Number Publication Date
EP2522854A1 true EP2522854A1 (fr) 2012-11-14

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EP12165970A Withdrawn EP2522854A1 (fr) 2011-05-09 2012-04-27 Agencement de soupape pour une pompe à carburant haute pression ainsi qu'une pompe à carburant haute pression

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EP (1) EP2522854A1 (fr)
DE (1) DE102011075516A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20130023A1 (it) * 2013-01-09 2014-07-10 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
CN104018968A (zh) * 2013-03-01 2014-09-03 罗伯特·博世有限公司 高压供油泵以及具有这种高压供油泵的柴油机
ITMI20131263A1 (it) * 2013-07-26 2015-01-27 Bosch Gmbh Robert Gruppo valvola per gruppo pompa di alta pressione per alimentare combustibile ad un motore a combustione interna e detto gruppo pompa di alta pressione
CN105637212A (zh) * 2013-08-02 2016-06-01 罗伯特·博世有限公司 具有出口阀的燃料高压泵
EP3249209A1 (fr) * 2016-05-26 2017-11-29 Delphi International Operations Luxembourg S.à r.l. Régulateur de pression
WO2023097330A1 (fr) * 2021-11-29 2023-06-01 Forum Us, Inc. Extrémité de fluide pour systèmes de pompes volumétriques

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021000327A1 (de) 2021-01-22 2022-07-28 Hydac Fluidtechnik Gmbh Pumpenvorrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1281861A2 (fr) * 2001-07-30 2003-02-05 L'orange Gmbh Dispositif d'injection de carburant pour moteurs à combustion interne
DE102008002360A1 (de) 2008-06-11 2009-12-17 Robert Bosch Gmbh Radialkolbenpumpe
DE102008042650A1 (de) 2008-10-07 2010-04-08 Robert Bosch Gmbh Radialkolbenpumpe zur Versorgung einer Verbrennungskraftmaschine mit Kraftstoff
EP2302194A1 (fr) * 2009-07-08 2011-03-30 Delphi Technologies Holding S.à.r.l. Unité de pompe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1281861A2 (fr) * 2001-07-30 2003-02-05 L'orange Gmbh Dispositif d'injection de carburant pour moteurs à combustion interne
DE102008002360A1 (de) 2008-06-11 2009-12-17 Robert Bosch Gmbh Radialkolbenpumpe
DE102008042650A1 (de) 2008-10-07 2010-04-08 Robert Bosch Gmbh Radialkolbenpumpe zur Versorgung einer Verbrennungskraftmaschine mit Kraftstoff
EP2302194A1 (fr) * 2009-07-08 2011-03-30 Delphi Technologies Holding S.à.r.l. Unité de pompe

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMI20130023A1 (it) * 2013-01-09 2014-07-10 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
CN104018968A (zh) * 2013-03-01 2014-09-03 罗伯特·博世有限公司 高压供油泵以及具有这种高压供油泵的柴油机
EP2789843A1 (fr) * 2013-03-01 2014-10-15 Robert Bosch Gmbh Pompe d'alimentation en carburant haute pression et moteur diesel équipé de ce système
CN104018968B (zh) * 2013-03-01 2019-04-23 罗伯特·博世有限公司 高压供油泵以及具有这种高压供油泵的柴油机
ITMI20131263A1 (it) * 2013-07-26 2015-01-27 Bosch Gmbh Robert Gruppo valvola per gruppo pompa di alta pressione per alimentare combustibile ad un motore a combustione interna e detto gruppo pompa di alta pressione
CN105637212A (zh) * 2013-08-02 2016-06-01 罗伯特·博世有限公司 具有出口阀的燃料高压泵
CN105637212B (zh) * 2013-08-02 2018-09-28 罗伯特·博世有限公司 具有出口阀的燃料高压泵
EP3249209A1 (fr) * 2016-05-26 2017-11-29 Delphi International Operations Luxembourg S.à r.l. Régulateur de pression
WO2023097330A1 (fr) * 2021-11-29 2023-06-01 Forum Us, Inc. Extrémité de fluide pour systèmes de pompes volumétriques

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Publication number Publication date
DE102011075516A1 (de) 2012-11-15

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