WO2014029649A1 - Culasse destinée à une pompe, en particulier à une pompe à carburant haute pression, et pompe munie de ladite culasse - Google Patents

Culasse destinée à une pompe, en particulier à une pompe à carburant haute pression, et pompe munie de ladite culasse Download PDF

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Publication number
WO2014029649A1
WO2014029649A1 PCT/EP2013/066783 EP2013066783W WO2014029649A1 WO 2014029649 A1 WO2014029649 A1 WO 2014029649A1 EP 2013066783 W EP2013066783 W EP 2013066783W WO 2014029649 A1 WO2014029649 A1 WO 2014029649A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder head
pump
valve member
housing
bore
Prior art date
Application number
PCT/EP2013/066783
Other languages
German (de)
English (en)
Inventor
Friedrich Boecking
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 WO2014029649A1 publication Critical patent/WO2014029649A1/fr

Links

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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F02M59/367—Pump inlet valves of the check valve type being open when actuated
    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0019—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of electromagnets or fixed armatures
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
    • 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
    • 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
    • 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
    • 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
    • F04B53/108—Valves characterised by the material
    • F04B53/1082—Valves characterised by the material magnetic
    • 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
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps

Definitions

  • Cylinder head for a pump in particular high-pressure fuel pump, and
  • Such a pump with a cylinder head is known from DE 196 44 915 AI, this pump as a high-pressure fuel pump for a
  • Fuel injection device of an internal combustion engine is used.
  • This pump has a pump housing and at least one pump element.
  • Pump housing has a cylinder head in which a pump piston of the pump element is guided in a cylinder bore, which limits a pump working space in the cylinder bore.
  • the pump working chamber can be connected to an inlet via an electromagnetically actuated inlet valve.
  • Inlet valve has a valve member which cooperates for controlling the connection with the inlet with a valve seat and which is acted upon by a closing spring in the closing direction. By energizing the electromagnet, the valve member is movable against the force of the closing spring in an open position.
  • the intake valve in this pump is in one with the cylinder head
  • the cylinder head according to the invention with the features according to claim 1 has the advantage that the inlet valve is integrated into this, whereby the space can be kept compact and also no dead volume between the pump working chamber and the inlet valve is present.
  • the pump with the features of claim 8 accordingly has the advantages of a compact size and a low dead volume.
  • Training according to claim 2 allows an advantageous arrangement of the magnetic core and the magnetic coil with a small space requirement.
  • the embodiment according to claim 3 allows an advantageous recording of the magnetic core with the solenoid and its attachment to the cylinder head.
  • the embodiment according to claim 4 enables easy contacting of the magnetic coil.
  • housing on the cylinder head whereby in particular a defined orientation of the electrical connection is set for the solenoid. Due to the construction according to claim 6 assembly of the magnet armature is arranged at the cylinder head arranged housing and a subsequent closing of the housing. The embodiment according to claim 8 allows easy attachment of the housing to the cylinder head.
  • FIG. 1 shows a pump in a longitudinal section and Figure 2 a designated in Figure 1 with II section with an inlet valve of the pump in an enlarged view.
  • the pump has at least one pump element 10, which in turn has a pump piston 12, which at least indirectly by a drive shaft 14 in a lifting movement in at least approximately radially
  • the drive shaft 14 may be part of the pump or alternatively may also be provided that the pump does not have its own drive shaft and the drive shaft 14 is part of the internal combustion engine.
  • the drive shaft 14 can thereby
  • Gas exchange valves of the internal combustion engine are operated or a
  • the drive shaft 14 may have a cam 16 or eccentric for driving the pump piston 12.
  • the pump has a multi-part pump housing.
  • the pump piston 12 is in a cylinder bore 20 of a first housing part 22 in the form of a
  • the pump piston 12 in the cylinder bore 20 defines a pump working space 24.
  • the pump working space 24 has a
  • Inlet valve 26 connects to one example of a
  • Pump work chamber 24 also has an outlet valve 30, for example, a out of the pump working chamber 24 out opening
  • Outlet check valve is a connection to a drain 32, which leads, for example, to a high-pressure fuel accumulator 34 and over the radially outward from the rotational axis 15 of the drive shaft 14 directed away delivery stroke of the pump piston 12 fuel is displaced from the pump working chamber 24.
  • the pump piston 12 is supported indirectly via a roller tappet 36 on the cam 16 of the drive shaft 14.
  • a roller 37 is rotatably mounted, which runs on the cam 16.
  • the pump piston 12 is connected to the roller tappet 36 in a manner not shown.
  • the roller plunger 36 and with this the pump piston 12 is acted upon by a spring 38 to the cam 16 of the drive shaft 14 out, so that the roller 37 constantly, so even during the suction stroke of the pump piston 12, remains in contact with the cam 16.
  • the housing of the pump has a second housing part 40, in which the
  • Drive shaft 14 may be rotatably supported via one or more bearings.
  • the inlet 28 can run through the housing part 40, in particular through an interior 42 of the housing part 40, in which the cam 16 of the drive shaft 14 is arranged, and through holes 43 or channels in the housing part 40th
  • the cylinder head 22 protrudes with an end region, in which the cylinder bore 20 is formed, in which the pump piston 12 is arranged, through an opening 44 of the second housing part 40 in the interior 42 thereof.
  • the cylinder bore 20 opposite end portion of the cylinder head 22 is disposed outside of the second housing part 40.
  • Cylinder head 22 lies with its flange 46 on the outside of the second
  • Cylinder head 22 is fixed in the longitudinal direction of the second housing part 40.
  • the inlet valve 26 is an electromagnetically actuated valve and will be described in more detail below.
  • the inlet valve 26 has a piston-shaped valve member 50, which has a shaft 52 and at one end of the shaft 52 has a larger diameter in diameter relative to the shaft 52 head 54.
  • the valve member 50 is guided with its shaft 52 in a bore 56 in the cylinder head 22, which connects at least approximately coaxially to the cylinder bore 20 on the pump piston 12 side facing away from the pump working chamber 24.
  • the bore 56 has a smaller diameter than the cylinder bore 20 and at the transition from the cylinder bore 20 to the bore 56, a valve seat 58 is formed for the valve member 50, which is for example at least approximately conical.
  • a sealing surface 60 is formed, which cooperates with the valve seat 58 and correspondingly may also be at least approximately conical.
  • the outside of the cylinder head 22 surrounding the bore 56 is at least substantially planar and extends perpendicular to the longitudinal axis 57 of the bore 56.
  • the mouth of the bore 56 on the outside of the cylinder head 22 is surrounded by a collar 62, through which the length of the bore 56 and thus the guide length of the shaft 52 of the valve member 50 is extended.
  • annular space 64 of the inlet 28 opens, for example via at least one or more distributed over the circumference of the annular space 64 inlet bores 66 in
  • Cylinder head 22 In the outer side of the cylinder head 22, a circumferential annular groove 68 is introduced into which the inlet 28 opens and in which also the
  • Inlet bores 66 open. In the head 54 facing away from the bore 56 projecting end of the
  • Shaft 52 of the valve member 50 is attached as part of the solenoid of the inlet valve 26, a magnet armature 70 which is disc-shaped. Between the armature 70 and the collar 62 surrounding outer side of the cylinder head 22, a closing spring 72 is clamped, which is designed here as a cylindrical helical compression spring. By the closing spring 72 is the
  • Valve member 50 is acted upon in the closing direction and by the pressure prevailing in the annular space 64 of the inlet 28, which acts on the head 54 of the valve member 50, the valve member 50 is acted upon in the opening direction.
  • the electromagnet of the intake valve 26 are a
  • Magnetic core 74 and a magnetic coil 76 is present.
  • the magnetic core 74 is surrounded by a tubular housing 78 which has an at least approximately circular cross-section and is fastened to the cylinder head 22 in a manner described in more detail below.
  • the magnetic core 74 adjoins the outside of the cylinder head 22 and the solenoid 76 is on the outside of the Cylinder head 22 remote from the magnetic core 74 arranged.
  • the magnetic coil 76 is arranged opposite the magnet armature 70, wherein between
  • Magnetic coil 76 and armature 70 is a sufficiently large distance is available to allow the opening and closing movement of the valve member 50.
  • At least one electrical connection 80 is present on the magnet coil 76, for which a plug connection 82 is provided on the outside of the housing 78, for example on its circumference.
  • a plug connection 82 is provided on the outside of the housing 78, for example on its circumference.
  • Plug housing 86 of the connector 82 can by a partial
  • Encapsulation of the housing 78 may be formed with plastic, wherein the housing 78 is made of metal.
  • the housing 78 extends beyond the magnet armature 70 away from the outside of the cylinder head 22 and is at its end by means of a
  • Lid part 88 sealed.
  • the cover part 88 is, for example, pressed into the housing 78 or otherwise connected to the housing 78
  • the diameter of the armature 70 is slightly smaller than the inner diameter of the housing 78, wherein the armature 70 may be provided with one or more openings or recesses 71.
  • the armature 70 In its the cylinder head 22 facing end portion of the outer diameter of the
  • Housing 78 increases, whereby an away from the cylinder head 22 annular shoulder 90 is formed on the housing 78.
  • the housing 78 facing the end region of the cylinder head 22 is cylindrical and provided with an external thread 92.
  • the housing 78 is by means of this
  • the sealing element 96 may be formed as an elastic sealing ring, which in an annular groove 97 in
  • Cylinder head 22 or the front side of the housing 78 may be inserted.
  • At least one centering element 98 can be arranged, which ensures that the Housing 78 can be fixed only in a predetermined rotational position on the cylinder head 22, in which the connector 82 is in a fixed orientation.
  • the centering element 98 may for example be a pin which engages in corresponding bores in the housing 78 and the cylinder head 22.
  • valve member 50 is guided by the cylinder bore 20 forth with its shaft 52 through the bore 56.
  • housing 78 is placed with the magnetic core 74 disposed therein and the magnetic coil 76 on the cylinder head 22, wherein the cover member 88 is not yet inserted.
  • Housing 78 is fixed by means of the clamping nut 94 in the predetermined rotational position on the cylinder head 22. Subsequently, the closing spring 72 is pushed onto the shaft 52 of the valve member 50 and the armature 70 is connected to the shaft 52. Finally, the lid part 88 is inserted.
  • the inlet valve 26 When not energized solenoid 76, the inlet valve 26 functions like a conventional check valve. If the pressure prevailing in the inlet 28 and thus in the annular space 64 causes a force on the valve member 50 in the opening direction, which is greater than the force of the closing spring 72 and the force caused by the pressure prevailing in the pump working chamber 24 force on the valve member 50, so opens the
  • Inlet valve 26 During the suction stroke of the pump piston 12 prevails in
  • the inlet valve 26 can be opened by energizing the solenoid coil 76 independently of the prevailing pressure difference between inlet 28 and pump working chamber 24. This allows opening of the inlet valve 26 also during the delivery stroke of the pump piston 12.
  • the solenoid 76 is not energized during the entire delivery stroke of the pump piston 12, so that the inlet valve 26 remains closed and the entire during the suction stroke of the pump piston 12 in the
  • the inlet valve 26 is opened so that the pump piston 12 displaced fuel is not conveyed into the high-pressure accumulator 34 but is fed into the inlet 28. It may be provided that the inlet valve 26 is initially held open by energizing the solenoid 76 at the beginning of the delivery stroke of the pump piston 12 and only at a certain time during the delivery stroke, the solenoid 76 is no longer energized, so that the inlet valve 26 closes and the
  • High pressure pumping begins.
  • the magnetic coil 76 is not energized at the beginning of the delivery stroke, so that the inlet valve 26 is closed and the high pressure pumping begins and that the high pressure pumping by energizing the solenoid 76 and opening the inlet valve 26 at a certain time during the delivery is ended.
  • the control of the solenoid 76 is performed by the
  • Control device 84 such that in the high-pressure accumulator 34 by the funded by the pump fuel, a predetermined pressure is maintained.
  • a pressure sensor 85 is arranged, through which the control device 84, a signal on the actual pressure in
  • High-pressure accumulator 34 receives.

Abstract

L'invention concerne une culasse (22) destinée à une pompe, en particulier à une pompe à carburant haute pression, comportant un alésage de cylindre (20), dans lequel est guidé un piston de pompe (12) qui délimite dans l'alésage de cylindre un espace de travail (24) de la pompe. L'espace de travail (24) de la pompe peut être raccordé à une alimentation (28) par l'intermédiaire d'une soupape d'admission électromagnétique (26), la soupape d'admission (26) comportant un élément de soupape (50) qui coopère avec un siège de soupape (58) pour la commande du raccordement de l'espace de travail (24) de la pompe à l'alimentation (28). L'élément de soupape (50)) est soumis à l'action d'un ressort de fermeture (72) dans la direction de fermeture, et peut être ouvert par l'alimentation en courant de l'aimant permanent (70, 74, 76). L'élément de soupape (50) est réalisé en forme de piston et comporte une tête (54) coopérant avec le siège de soupape (58) et une tige (52) raccordée à la tête (54). La tige (52) de l'élément de soupape (50) est guidée dans un alésage (56) de la culasse (22) raccordé à l'alésage de cylindre (20), et le siège de soupape (58) est réalisé dans la culasse (22) au niveau de la transition entre l'alésage de cylindre (20) et l'alésage (56). Un noyau magnétique (70) de l'électroaimant est connecté à la tige (52) de l'élément de soupape (50), et le ressort de fermeture (72) est serré entre le noyau magnétique (70) et la culasse (22).
PCT/EP2013/066783 2012-08-24 2013-08-12 Culasse destinée à une pompe, en particulier à une pompe à carburant haute pression, et pompe munie de ladite culasse WO2014029649A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012215068.4A DE102012215068A1 (de) 2012-08-24 2012-08-24 Zylinderkopf für eine Pumpe, insbesondere Kraftstoffhochdruckpumpe, und Pumpe mit Zylinderkopf
DE102012215068.4 2012-08-24

Publications (1)

Publication Number Publication Date
WO2014029649A1 true WO2014029649A1 (fr) 2014-02-27

Family

ID=48986108

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/066783 WO2014029649A1 (fr) 2012-08-24 2013-08-12 Culasse destinée à une pompe, en particulier à une pompe à carburant haute pression, et pompe munie de ladite culasse

Country Status (2)

Country Link
DE (1) DE102012215068A1 (fr)
WO (1) WO2014029649A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201600121614A1 (it) * 2016-11-30 2018-05-30 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016215304A1 (de) * 2016-08-17 2018-02-22 Robert Bosch Gmbh Elektromagnetisch betätigbares Saugventil und Kraftstoff-Hochdruckpumpe

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1967721A2 (fr) * 2007-03-08 2008-09-10 Hitachi, Ltd. Dispositif de contrôle de pompe à carburant haute pression pour moteur à combustion interne
EP2182199A1 (fr) * 2008-10-30 2010-05-05 Hitachi Automotive Systems Ltd. Mécanisme de soupape à commande électromagnétique et pompe d'alimentation à carburant haute pression l'utilisant
WO2011104907A1 (fr) * 2010-02-26 2011-09-01 日立オートモティブシステムズ株式会社 Pompe à carburant haute pression
DE102012203243A1 (de) * 2012-03-01 2013-09-05 Robert Bosch Gmbh Kraftstoffpumpe

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19644915A1 (de) 1996-10-29 1998-04-30 Bosch Gmbh Robert Hochdruckpumpe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1967721A2 (fr) * 2007-03-08 2008-09-10 Hitachi, Ltd. Dispositif de contrôle de pompe à carburant haute pression pour moteur à combustion interne
EP2182199A1 (fr) * 2008-10-30 2010-05-05 Hitachi Automotive Systems Ltd. Mécanisme de soupape à commande électromagnétique et pompe d'alimentation à carburant haute pression l'utilisant
WO2011104907A1 (fr) * 2010-02-26 2011-09-01 日立オートモティブシステムズ株式会社 Pompe à carburant haute pression
EP2541039A1 (fr) * 2010-02-26 2013-01-02 Hitachi Automotive Systems, Ltd. Pompe a carburant haute pression
DE102012203243A1 (de) * 2012-03-01 2013-09-05 Robert Bosch Gmbh Kraftstoffpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201600121614A1 (it) * 2016-11-30 2018-05-30 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna

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Publication number Publication date
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