EP1306553A2 - Pompe à carburant, système de distribution, procédé d'exploitation dudit système et moteur à combustion interne - Google Patents

Pompe à carburant, système de distribution, procédé d'exploitation dudit système et moteur à combustion interne Download PDF

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Publication number
EP1306553A2
EP1306553A2 EP02017583A EP02017583A EP1306553A2 EP 1306553 A2 EP1306553 A2 EP 1306553A2 EP 02017583 A EP02017583 A EP 02017583A EP 02017583 A EP02017583 A EP 02017583A EP 1306553 A2 EP1306553 A2 EP 1306553A2
Authority
EP
European Patent Office
Prior art keywords
fuel
fuel pump
pump
internal combustion
combustion engine
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Withdrawn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
EP02017583A
Other languages
German (de)
English (en)
Other versions
EP1306553A3 (fr
Inventor
Helmut Rembold
Klaus Joss
Jens Wolber
Thomas Dr. Frenz
Uwe Mueller
Markus Amler
Thomas Fuerst
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 EP1306553A2 publication Critical patent/EP1306553A2/fr
Publication of EP1306553A3 publication Critical patent/EP1306553A3/fr
Withdrawn legal-status Critical Current

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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
    • F02M63/02—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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/08—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by two or more pumping elements with conjoint outlet or several pumping elements feeding one engine cylinder
    • 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
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F04B1/0536—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units
    • F04B1/0538—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders with two or more serially arranged radial piston-cylinder units located side-by-side
    • 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
    • F04B49/22—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 by means of valves
    • F04B49/24—Bypassing
    • F04B49/243—Bypassing by keeping open the inlet valve

Definitions

  • the invention first relates to a fuel pump, especially high pressure fuel pump for Internal combustion engines, with a housing, with at least a drive shaft, with a plurality of pump elements, which are driven by the drive shaft and each delimit a work space with a low pressure area and a high pressure area, and with at least one controllable valve device for control or regulation the flow rate.
  • Such a fuel pump is a radial piston pump known from the market.
  • the well-known radial piston pump comprises three cylinders arranged in a star shape, in which one pump piston is axially displaceably received.
  • the working spaces of the cylinders are via non-return valves with an inlet-side low pressure area of the Fuel pump connected.
  • the work rooms via check valves with an outlet side High pressure area of the fuel pump connected.
  • the term "work space” refers to that space understood in the during a working game of the Pump chamber associated with the fuel flows in or out of this again by the pump element becomes. Ideally, if there is no leakage, for example the volume of the work area corresponds to that Delivery volume.
  • the control or regulation of the delivery rate of the Fuel pump is operated via a switching valve with which the common exhaust side area of the cylinder with the inlet-side low pressure area are short-circuited can. In the event of such a short circuit, the Fuel not to the high pressure outlet, but back conveyed to the inlet-side low pressure area.
  • the present invention therefore has the task of a Fuel pump of the type mentioned above to further develop that with her the delivery rate simple and can be set quickly and their components in the Operation only be burdened slightly. Even those in inlet-side low-pressure area of the fuel pump used components as well as the leads to Fuel pumps should be built as cheaply as possible can.
  • This task is the beginning of a fuel pump mentioned type solved in that at least one Work area an individually controllable valve device with which this workspace is assigned to the Low pressure area can be forcibly connected, so that from this workspace at least temporarily not in the high pressure area is promoted.
  • the funding comes from said work space completely prevented in the high pressure area.
  • At least one work space no controllable valve device is assigned with which is forcibly connected to the low pressure area can be, so that from this constantly in the High pressure area is promoted.
  • This further training lies based on the idea that a certain minimal Fuel requirement is always present. This can be done through the permanent funding from a work space is covered, where there is therefore no need for funding at times to be able to interrupt. Saving at least one Valve device leads to a cost reduction of fuel pump according to the invention.
  • the inventive structure is particularly simple and compact Fuel pump when the valve device as Inlet valve is formed and two switching positions has, in the one switching position a flow at least from the work area to the low pressure area and in the other switch position only a flow from Low pressure area towards the work area is possible.
  • the fuel pump three Has working rooms with corresponding pump elements, being constantly from a workspace into the high pressure outlet is promoted and the other two work rooms each an individually controllable valve device is assigned with which these workspaces each with the Low pressure area can be forcibly connected, so that from these workspaces at least temporarily not in the high pressure outlet is promoted.
  • the fuel pump three Has working rooms with corresponding pump elements, being constantly from a workspace into the high pressure outlet is promoted and the other two work rooms each an individually controllable valve device is assigned with which these workspaces each with the Low pressure area can be forcibly connected, so that from these workspaces at least temporarily not in the high pressure outlet is promoted.
  • the delivery volume at least one workspace from the funding volume of one different work space.
  • Fuel pump with three work spaces can do four different delivery levels can be achieved if the valve devices of the corresponding work rooms during a complete funding cycle of the corresponding Are open. These four funding levels include funding from only one workspace, one Funding from the first and second workspace, one Funding from the first and third workspace, and funding from all three workspaces.
  • a radial piston pump is particularly inexpensive Execute according to the invention. With her are the necessary Easy to accommodate valve devices without the Overall dimensions of the fuel pump become larger.
  • Training is also particularly preferred in which the fuel pump has a drive shaft with eccentrics and several cylinder planes arranged along the drive shaft has, the eccentrics of a cylinder plane relative to that of another cylinder plane offset by 180 ° are arranged. With such a fuel pump larger production volumes are also provided. Through the staggered arrangement of the eccentric sections Bearing forces of the drive shaft reduced.
  • the second cylinder plane with regard to the valve devices are the same as the first cylinder plane be trained.
  • one Cylinder level without a single work space individually controllable valve device and another Cylinder level with only a single work area individually controllable valve device are also possible.
  • the construction and control costs at the same time sufficient variability of the delivery rate reduced.
  • the invention also relates to a fuel system for Fuel supply to an internal combustion engine with a Fuel tank, with at least one fuel pump, with at least one fuel rail, which from the fuel pump is fed, and with at least one Fuel injector connected to the fuel rail is connected and via which the fuel in reaches the combustion chamber of the internal combustion engine.
  • the Fuel pump is designed in the above manner. By such a fuel system can run the fuel in different quantity levels the fuel injectors to be provided.
  • Fuel quantity can be controlled by a pressure control valve be provided, which with the fuel manifold connected is.
  • a Pressure sensor is present, which the pressure in the Fuel manifold detected, and a control and / or Control device is available, which is the at least one individually controllable valve device Fuel pump and / or the pressure control valve in Controlled depending on the signals of the pressure sensor. In this case, a very precise control or Regulation of the amount of fuel provided possible.
  • the invention further relates to a method for operating a fuel system for supplying fuel to a Internal combustion engine in which at least one fuel pump with multiple work spaces from a fuel tank promotes a fuel rail and the Fuel over at least one with the fuel rail connected fuel injector in reaches the combustion chamber of the internal combustion engine.
  • a gradual adjustment of the delivery rate of the Fuel pump is achieved by at least a workspace throughout its funding cycle is not promoted to a lower output in the Reach fuel manifold.
  • Such Activation of the fuel pump is relatively inexpensive realizable. Is the delivery rate of the fuel pump not varied in stages, but continuously can also only at the beginning of a funding cycle a work space cannot be funded. By the length of the period during which no funding is available, the desired delivery rate can be set. In this way are any different flow rates from the Fuel pump can be pumped, with small delivery rates the power requirement of the fuel pump is also lower.
  • the at least one Valve device depends on the pressure in the fuel rail and / or depending on at least one Operating parameters of the internal combustion engine is controlled.
  • the control depends on the pressure in the fuel rail offers the advantage of a simple one closed loop.
  • Control depending on an operating parameter of the internal combustion engine for example one The speed of a crankshaft, an air filling, etc. has the The advantage of a particularly quick response to a Change in the operating state of the internal combustion engine.
  • the invention also relates to a computer program which is suitable for performing the above method if it is done on a computer. Doing so particularly preferred if the computer program on a Memory, in particular on a flash memory, is saved.
  • the invention relates to a control and / or Control device for operating an internal combustion engine, which on the input side with at least one pressure sensor Fuel manifold or at least one facility is connectable, which has at least one operating parameter the internal combustion engine provides, and which on the output side with a fuel pump of the above type is connectable.
  • the assembly of the internal combustion engine is particularly simple and the operation of the internal combustion engine reliably possible if the control and / or regulating device to control and / or regulate the above method suitable is.
  • control and / or Control device includes a memory on which a Computer program of the above type is stored.
  • the invention also relates to a Internal combustion engine, in particular for motor vehicles, which a fuel system includes with a fuel tank, with at least one fuel pump, with a fuel manifold, which is fed by the fuel pump, and with at least one fuel injection device, through which the fuel enters a combustion chamber Internal combustion engine can get.
  • reference numeral 10 denotes a Internal combustion engine. This includes a fuel system 12. Part of the fuel system 12 is in turn Radial piston pump 14 with three cylinders 15 a - 15c. their Low pressure area 18 is in turn connected to a low pressure fuel line 16 connected. A high pressure area 20 the radial piston pump 14 is with a high pressure fuel line 22 connected to a fuel rail 24 leads. To the fuel rail 24 are a total of four fuel injectors 26, in the present injectors, connected via which the Fuel into corresponding combustion chambers 28 Internal combustion engine 10 arrives.
  • a pressure control valve 30 connected, which is controlled by a control and regulating device 32 is controlled.
  • the pressure in the fuel rail 24 is detected by a pressure sensor 34, the corresponding one Provides signals to the control and regulating device 32.
  • the Pressure control valve 30 is connected via a return line 36 the low pressure fuel line 16 connected.
  • the radial piston pump 14 includes a drive shaft 38 an eccentric section 40 is provided. At the Eccentric section 40 are distributed over the circumference three Sliding portions 42a, 42b and 42c attached. On this are pistons 44a, 44b and 44c. The pistons 44a to 44c limit together with one shown only schematically Housing 46 each have a working space 48a, 48b or 48c.
  • the upper working space 48a in FIG. 1 is over a Check valve 50a with the low pressure region 18 connectable.
  • the check valve 50a opens to the work space 48a there.
  • the work space 48a is also via a Check valve 52a opening working space 48a with the High pressure area 20 connectable.
  • the working spaces 48b and 48c of the cylinders 15b and 15c are also from workrooms 48b and 48c way opening check valves 52b and 52c with the High pressure area 20 connectable.
  • Working space 48a are the working spaces 48b and 48c with the Low pressure area 18 each switchable Valve devices 54b and 54c connectable.
  • switch position 56b or 56c there is a free one Flow possible in both directions, d. H. from inlet-side low pressure area 18 to the working space 48b or 48c and from the working space 48b or 48c to inlet-side low-pressure region 18.
  • switch position 58b or 58c is a Flow only from inlet-side low pressure area 18 to the work area 48b or 48c possible, whereas the other Flow direction is blocked.
  • the valve device 54b or 54c thus acts as a check valve which leads to the working space 48b or 48c opens and to the inlet-side low pressure region 18 locks out.
  • the valve devices 54b and 54c are magnet operated and are operated by a spring (without Reference numerals) in the rest switch position 56b or 56c pressed.
  • the radial piston pump 14 shown in Fig. 1 operates as follows: For an optimal injection of the Fuel through the injectors 26 into the combustion chambers 28 ensure the pressure in the fuel rail 24 relatively constant at a certain value being held. This value is usually approximately 120, but possibly also up to 200 bar. Keeping pressure constant in the fuel rail 24 guaranteed by a closed controlled system, which the pressure sensor 34, the control and regulating device 32 and the Radial piston pump 14 and the pressure control valve 30 comprises.
  • Embodiment are the diameters of the pistons 44a, 44b and 44c different. Also vary accordingly the maximum delivery volumes of the respective cylinders 15a, 15b and 15c. In this way, the individual Quantity levels optimally to the specific requirements of the respective internal combustion engine 10 are adapted. Out For reasons of service life, the piston of the long-term Cylinder in this case the smallest diameter exhibit.
  • FIG. 2 An embodiment for the integration of a Valve device 54 in a cylinder 15b is in FIG. 2 shown.
  • the valve device 54 comprises a housing 60, which is cylindrical. In its upper A magnetic coil 62 is recorded on the area movable magnet armature 64 acts. The magnet armature 64 supports itself on a cover 68 via a compression spring 66.
  • a valve tappet 70 is attached to the magnet armature 64 through an opening 72 into a valve space 74 is passed through.
  • collar 76 extending downward, which forms a valve seat for a valve member 78.
  • Compression spring 80 is supported on a lower plate 82.
  • the lower plate 82 is fixedly connected to the housing 60.
  • the valve device 54b is in an opening 84 in the housing 46 of the radial piston pump 14 introduced.
  • the bottom plate 82 of the valve device 54, the housing 46 of the Radial piston pump 14 and piston 44b limit the Work space 48b.
  • FIG. 5 Another version of a three-cylinder Radial piston pump 14 is shown in section in FIG. 5.
  • the inlet side Low pressure area 18 is here with that hole in the housing 46 of the radial piston pump 14 in which the Drive shaft 38 is arranged.
  • Corresponding bores 86 extend obliquely inward from the valve devices 54.
  • the valve devices 54b and 54c are laterally on the Cylinders 15b and 15c attached.
  • the figures 6-10 relate to a radial piston pump 14 two cylinder planes 86 and 88.
  • the first cylinder plane 86 are three cylinders 15a to 15c arranged in a star shape present, whereas in the second cylinder plane 88 another three star-shaped cylinders 15d to 15f available.
  • the individual cylinders 15 are in FIG. 6 only indicated by dash-dotted lines.
  • the cylinders 15d to 15f the second cylinder plane 88 are 180 ° with respect to Cylinders 15a to 15c of the first cylinder plane 86 offset arranged. This goes particularly well from the Representation in Fig. 7. From this is too can be seen that the drive shaft 38 in addition to the Eccentric section 40 for the first cylinder plane 86 still a further eccentric section 90 for the second Cylinder plane 88 has.
  • Radial piston pump 14 delivers the cylinder 15a of the first Cylinder plane 86 continuously, whereas cylinders 15b and 15c have valve devices (not shown) via which they can be turned off.
  • valve devices not shown
  • the second Cylinder plane 88 are cylinders 15d and 15e permanent, whereas the cylinder 15f by a Valve device (not shown) can be switched off can.
  • the eccentricity of the second eccentric section 90 is slightly less than the eccentricity of the first Eccentric section 40 of the drive shaft 38. Furthermore the diameters of the pistons 44 also differ first cylinder plane 86 with one another and the pistons 92 the second cylinder plane 88 also with one another. The different delivery volumes of the individual cylinders 15a to 15f are shown as bar graphs in FIGS. 8 and 9 shown.
  • the switchable cylinder 15b and 15c of the first cylinder plane 86 the same Have funding volume and also the non-switchable Cylinder 15d and 15e of the second cylinder plane 88 that have the same volume.
  • FIGS. 11 and 12 show the same volume.
  • a Flow rate level can be two different Species can be achieved: The same flow rate results with a combination of the delivery volumes of the non-switchable Cylinder 15a, 15d and 15e with the Delivery volumes of the switchable cylinders 15b or 15c. in the With regard to an even load, if this funding level is active, between one Turn on the cylinder 15b and turn on the Cylinder 15c can be varied cyclically.
  • valve devices 54 depending on the signal of the pressure sensor 34.
  • Control is also possible of valve devices 54 depending on operating parameters the internal combustion engine. These include e.g. B. the speed a crankshaft of the internal combustion engine, a torque, an air filling of the internal combustion engine etc. is possible also a direct coupling to the position of an accelerator pedal, with which the internal combustion engine is operated. In these Is a particularly quick adjustment of the cases Delivery rate of the radial piston pump 14 to the required Operating state of the internal combustion engine possible. On the other hand, the power requirement of the fuel pump For example, immediately reduced with a low torque requirement become.

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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)
EP02017583A 2001-10-27 2002-08-07 Pompe à carburant, système de distribution, procédé d'exploitation dudit système et moteur à combustion interne Withdrawn EP1306553A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10153189 2001-10-27
DE2001153189 DE10153189A1 (de) 2001-10-27 2001-10-27 Kraftstoffpumpe, Kraftstoffsystem, Verfahren zum Betreiben eines Kraftstoffsystems sowie Brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP1306553A2 true EP1306553A2 (fr) 2003-05-02
EP1306553A3 EP1306553A3 (fr) 2004-08-04

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EP02017583A Withdrawn EP1306553A3 (fr) 2001-10-27 2002-08-07 Pompe à carburant, système de distribution, procédé d'exploitation dudit système et moteur à combustion interne

Country Status (3)

Country Link
EP (1) EP1306553A3 (fr)
JP (1) JP2003148290A (fr)
DE (1) DE10153189A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1251272A2 (fr) * 2001-04-16 2002-10-23 Siemens Diesel System Technologies, LLC Système de pompes hydrauliques à plusieurs étages
EP1674716A1 (fr) * 2004-12-23 2006-06-28 C.R.F. Società Consortile per Azioni Système d'injection de carburant comprenant une pompe à carburant à haute pression à débit variable
WO2009103572A1 (fr) * 2008-02-22 2009-08-27 Robert Bosch Gmbh Pompe haute pression destinée à fournir du carburant haute pression à un moteur à combustion interne
EP2241744A1 (fr) * 2009-04-15 2010-10-20 Delphi Technologies Holding S.à.r.l. Pompe à carburant à rampe commune haute pression et procédé de contrôle d'une pompe à carburant à rampe commune haute pression
DE102009003066A1 (de) 2009-05-13 2010-11-18 Robert Bosch Gmbh Kolbenmaschine, insbesondere Flüssigkeitskolbenmaschine
EP2933485A1 (fr) * 2014-04-17 2015-10-21 Danfoss Power Solutions GmbH & Co. OHG Pompe hydraulique à écoulement de fluide variable
WO2016037655A1 (fr) * 2014-09-11 2016-03-17 Gaydoul Jürgen Dispositif de déplacement
ITUB20159428A1 (it) * 2015-12-29 2017-06-29 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
EP2766594B1 (fr) * 2012-01-19 2018-03-28 Continental Automotive GmbH Système d'injection à rampe commune pour moteur à combustion interne

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Publication number Priority date Publication date Assignee Title
DE10335603A1 (de) * 2003-08-04 2005-03-03 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
JP2006170169A (ja) * 2004-12-20 2006-06-29 Denso Corp 燃料供給ポンプ

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EP0840009A2 (fr) * 1996-10-29 1998-05-06 Robert Bosch Gmbh Pompe à haute pression
WO2000047888A1 (fr) * 1999-02-09 2000-08-17 Hitachi, Ltd. Pompe d'alimentation en combustible a haute pression faisant partie d'un moteur a combustion interne

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DE19612412B4 (de) * 1996-03-28 2006-07-06 Siemens Ag Regelung für ein Druckfluid-Versorgungssystem, insbesondere für den Hochdruck in einem Kraftstoff-Einspritzsystem
DE19622776B4 (de) * 1996-06-07 2010-11-25 Robert Bosch Gmbh Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine
DE19646581A1 (de) * 1996-11-12 1998-05-14 Bosch Gmbh Robert Kraftstoffeinspritzsystem
DE10010945B4 (de) * 2000-03-06 2004-07-22 Robert Bosch Gmbh Pumpe zur Versorgung eines Kraftstoffeinspritzsystems und einer hydraulischen Ventilsteuerung für Brennkraftmaschinen

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DE4320620A1 (de) * 1993-06-22 1995-01-05 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
EP0840009A2 (fr) * 1996-10-29 1998-05-06 Robert Bosch Gmbh Pompe à haute pression
WO2000047888A1 (fr) * 1999-02-09 2000-08-17 Hitachi, Ltd. Pompe d'alimentation en combustible a haute pression faisant partie d'un moteur a combustion interne

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1251272A2 (fr) * 2001-04-16 2002-10-23 Siemens Diesel System Technologies, LLC Système de pompes hydrauliques à plusieurs étages
EP1251272A3 (fr) * 2001-04-16 2004-09-29 Siemens Diesel System Technologies, LLC Système de pompes hydrauliques à plusieurs étages
EP1674716A1 (fr) * 2004-12-23 2006-06-28 C.R.F. Società Consortile per Azioni Système d'injection de carburant comprenant une pompe à carburant à haute pression à débit variable
US7784447B2 (en) 2004-12-23 2010-08-31 C.R.F. Societa Consortile Per Azioni Fuel injection system comprising a high-pressure variable-delivery pump
WO2009103572A1 (fr) * 2008-02-22 2009-08-27 Robert Bosch Gmbh Pompe haute pression destinée à fournir du carburant haute pression à un moteur à combustion interne
EP2241744A1 (fr) * 2009-04-15 2010-10-20 Delphi Technologies Holding S.à.r.l. Pompe à carburant à rampe commune haute pression et procédé de contrôle d'une pompe à carburant à rampe commune haute pression
CN102422021A (zh) * 2009-05-13 2012-04-18 罗伯特·博世有限公司 活塞机，尤其是液体活塞机
WO2010130495A1 (fr) 2009-05-13 2010-11-18 Robert Bosch Gmbh Machine à pistons, en particulier machine à pistons pour fluide
DE102009003066A1 (de) 2009-05-13 2010-11-18 Robert Bosch Gmbh Kolbenmaschine, insbesondere Flüssigkeitskolbenmaschine
EP2766594B1 (fr) * 2012-01-19 2018-03-28 Continental Automotive GmbH Système d'injection à rampe commune pour moteur à combustion interne
EP2933485A1 (fr) * 2014-04-17 2015-10-21 Danfoss Power Solutions GmbH & Co. OHG Pompe hydraulique à écoulement de fluide variable
CN105020113A (zh) * 2014-04-17 2015-11-04 丹佛斯动力***有限责任两合公司 可变流体流量液压泵
US10012228B2 (en) 2014-04-17 2018-07-03 Danfoss Power Solutions Gmbh & Co. Ohg Variable fluid flow hydraulic pump
WO2016037655A1 (fr) * 2014-09-11 2016-03-17 Gaydoul Jürgen Dispositif de déplacement
EP3181902A1 (fr) 2014-09-11 2017-06-21 Hermetik Hydraulik Ab Organe de refoulement
ITUB20159428A1 (it) * 2015-12-29 2017-06-29 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna

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DE10153189A1 (de) 2003-05-15
EP1306553A3 (fr) 2004-08-04

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