EP1130250A1 - Pompe d'injection de carburant haute pression - Google Patents

Pompe d'injection de carburant haute pression Download PDF

Info

Publication number
EP1130250A1
EP1130250A1 EP00810170A EP00810170A EP1130250A1 EP 1130250 A1 EP1130250 A1 EP 1130250A1 EP 00810170 A EP00810170 A EP 00810170A EP 00810170 A EP00810170 A EP 00810170A EP 1130250 A1 EP1130250 A1 EP 1130250A1
Authority
EP
European Patent Office
Prior art keywords
piston
groove
suction throttle
inlet opening
pump
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Withdrawn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
EP00810170A
Other languages
German (de)
English (en)
Inventor
Norbert Grote
Robert Hofer
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.)
Wartsila NSD Schweiz AG
Original Assignee
Wartsila NSD Schweiz AG
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 Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP00810170A priority Critical patent/EP1130250A1/fr
Publication of EP1130250A1 publication Critical patent/EP1130250A1/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • 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
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the piston
    • 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
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines

Definitions

  • the invention relates to a suction throttle pump for conveying Liquids, especially fuel, according to the preamble of independent claim 1.
  • EP-A-0 863 308 discloses a piston pump which in particular as a high-pressure pump for the injection system Diesel engine is suitable. Since this piston pump is also suitable for heavy oil , it can also be used to deliver fuel to the injection system a large diesel engine can be used. Such large diesel engines that usually with heavy oil as fuel and injection pressures of up to Operated at 2000 bar can be found, for example, as main drive units for ships and in stationary systems for power generation. To the amount of fuel delivered to the desired load state of the To adjust the motor, means must be provided on the high pressure pump with which the amount of fuel delivered per work cycle between approximately zero and a full load amount is adjustable.
  • EP-A-0 863 308 therefore proposes a piston pump which includes a Has pump housing with a work space, a back and forth movable piston for enlarging and reducing the working space, and at least one inlet opening for introducing the fuel into the Working space.
  • the piston is mounted rotatably about its longitudinal axis and points in its outer surface one connected to the work area and with the Inlet opening cooperating recess. This recess is designed so that the amount of fuel flowing into the work area is adjustable by rotating the piston about its longitudinal axis. If the piston in the area of its bottom dead center (maximum volume of the Work area), the recess in the piston and the overlap Inlet opening so that the fuel from the inlet opening through the Recess can flow into the work area.
  • suction throttle pump disclosed in EP-A-0 863 308 is in the Practice has proven itself very well in operating states in which the Pump has to pump no or only very small volume flows, problems shown. If the suction throttle pump, for example, as a high pressure pump for the injection system of a large diesel engine is used in a ship, Such conditions occur in the lower partial load range, or when the engine is turned off, but the crankshaft by the connected to it Propeller continues to be turned. Then the piston also moves the suction throttle pump, which is usually driven by the crankshaft back and forth, but without fuel being promoted. In such Operating states occur increasingly wear and tear Signs of wear on. The piston has a significantly increased Eating tendency, and there is a risk of a piston eater, leading to considerable and costly damage.
  • suction throttle pump solving this task is characterized by the features of characterized independent claim 1.
  • a suction throttle pump is used to convey Liquids, especially fuel, proposed with a Pump housing, which has a working space with a back and forth Movable piston to enlarge and reduce the Working space, which piston is rotatably mounted about its longitudinal axis, and with at least one inlet opening for introducing the liquid into the Working space, one in the outer surface of the piston with the Work space connected and interacting with the inlet opening Recess is provided, which is designed so that the in the Liquid volume flowing into the work area by turning the piston its longitudinal axis is adjustable. Furthermore, a groove is provided, which is extends along the entire circumference of the piston, and its radial Depth is at least one percent of the diameter of the piston.
  • This deep groove which is independent of the angular position of the piston each cycle of the piston fills with the liquid, serves as a reservoir and as Distributor. During the stroke movement of the piston, it is in the groove existing liquid distributed along the running surface of the piston, from which very good lubrication of the piston results. Especially in such Operating conditions in which very little or no liquid flows through the Recess in the piston in the working area of the pump guaranteed the liquid present in the deep groove that the piston is sufficient is lubricated to reliably prevent the piston from seizing. For each The operating state of the suction throttle pump is therefore always sufficient liquid for lubricating the piston.
  • the axial height is the groove preferably at least ten percent of the diameter of the Piston.
  • Preferred configurations are those in which the radial depth of the groove at least six percent, in particular about ten percent, of The diameter of the piston is approximately and the axial height of the groove fifteen percent of the diameter of the piston. These dimensions have proven themselves in practice to provide particularly good lubrication of the Ensure piston.
  • the groove is rounded Has edges.
  • the groove is arranged with respect to its axial position so that it the inlet opening fully or partially opposite when the piston is in its top dead center. This measure is namely the open one Flow cross section between the inlet opening and the groove just then maximum or particularly large if the piston speed is minimal.
  • the suction throttle pump according to the invention is particularly suitable for Use as a high pressure pump to deliver fuel, especially heavy oil, for the injection system in a diesel engine.
  • suction throttle pump Since the suction throttle pump is suitable for pumping heavy oil, it is suitable itself to feed the fuel into the injection system Large diesel engine.
  • suction throttle pump as a high pressure pump for pumping heavy oil for the injection system a large diesel engine is used.
  • Fig. 1 shows the parts essential for an understanding of the invention Embodiment of the suction throttle pump according to the invention, the is generally designated with the reference number 1, in part cut and partially symbolic representation.
  • the suction throttle pump 1 comprises a pump housing 2, in which a Work space 3 is provided, and a back and forth arranged piston 4, which by its oscillatory movement between two reversal points periodically enlarged and downsized.
  • a reversal point which is a minimum Volume of the work space 3 corresponds to, referred to as top dead center and the turning point, the maximum volume of the work space corresponds as bottom dead center.
  • Fig. 1 shows the piston 4 in its lower Dead center.
  • the piston 4 is essentially cylindrical and pivoted about its longitudinal axis A.
  • Driver bushing 7 is provided with teeth.
  • the piston 4 is through accordingly moving the control rod 6 in the direction of Double arrow B in both directions C rotatable about its longitudinal axis A.
  • the stroke movement of the piston can e.g. B. in a conventional manner a cam 11 arranged on a shaft 10 and a cam follower 12 are driven.
  • the shaft 10 is, for example, by the Crankshaft of the engine set in rotation.
  • the cam 11 presses the Piston 4 against the force of a piston spring, not shown as shown upwards.
  • the suction throttle pump 1 further comprises at least one inlet opening 21 for introducing the liquid (heavy oil) into the work area 3 and one Outlet opening 22 through which the pressurized heavy oil is pushed out.
  • the inlet opening 21 is connected via a suction line 13 connected to a low pressure system for the heavy oil. That under pressure Heavy oil that has been placed enters through outlet opening 22 via Check valve 14 in a pressure line 15 which to the injection system of Motors, for example for the pressure accumulator of a common rail system, leads.
  • FIG. 2 shows a view of the piston 4 for better understanding Direction of the inlet opening 21, which is indicated by dashed lines.
  • the piston 4 is at its bottom dead center.
  • the pump housing is in section indicated.
  • Fig. 3 is analogous to Fig. 2, but the piston 4 is in his shown top dead center. In Fig. 2 and Fig. 3 the piston 4 is in an angular position in which only a very small amount of liquid is pumped becomes.
  • the embodiment 5 described here extends the recess 5 initially in the form of a groove 51 (see FIGS. 2 and 3) of the Working space 3 facing end face 49 of the piston 4 along the Lateral surface of the piston parallel to its longitudinal axis A and then goes in a substantially V-shaped portion 52 which extends in the circumferential direction of the piston 4 is tapered.
  • the inlet opening 21 is arranged so that it is at the same height (with respect to the longitudinal axis A) as the V-shaped one Part 52 of the recess 5 when the piston 4 in its lower Dead center is (see Fig. 2). To those that occur in the material To lower voltage peaks are the edges of the recess 5 rounded. This applies in particular to the edges of the groove 51 in the Mouth area in the end face 49, for the edges in the transition area between the groove 51 and the V-shaped part 52 and for the edge on the Tip of the V-shaped part 52.
  • At least two substantially identical recesses 5 in the The outer surface of the piston 4 is provided, preferably diametrically are arranged opposite each other and up to the Work area 3 facing end face 49 of the piston 4 extend. Naturally can also be provided more than two such recesses 5, the preferably evenly distributed in the lateral surface of the piston 4 are arranged. It is understood that in such cases where several Recesses 5 are also arranged in the outer surface of the piston more than one inlet opening 21 can be provided in the pump housing. Since it is sufficient for understanding, only one of the possibly considered several recesses 5.
  • the recess 5 is used in the operating state for the controllable introduction of Heavy oil in the work area 3.
  • the piston is located in FIGS. 1 and 2 4 roughly at its bottom dead center. In this state the Recess 5 (in the angular position of the piston 4 shown) Connection between the inlet opening 21 and the work space 3.
  • the for The heavy oil prepared for combustion passes through the suction line 13 Inlet opening 21, as symbolically represented by the one with the reference symbol BE provided arrow is indicated, and from there through the recess 5 in the work area 3.
  • the piston closes the inlet opening 21 and reduces the size Workroom 3, which puts the heavy oil in it under pressure becomes. This passes through the outlet opening 22 and the check valve 14 into the pressure line 15.
  • the load-dependent takes place Regulation of the amount of heavy oil extracted by regulating the in the Working area 3 entering heavy oil quantity.
  • the recess 5 geometrically designed such that, depending on the angular position of the piston 4 relative to the pump housing 2 more or less fuel in the Working space 3 can reach when the piston 4 is in its lower Dead center is located.
  • the Delivery increased compared to the situation shown in Fig. 2 the piston 4 is activated by operating the control rod 6 rotated counterclockwise as shown.
  • a groove 8 is provided in the suction throttle pump 1, which extends along the entire circumference of the piston 4, and whose radial depth T is at least one percent of the diameter D of Piston 4 is.
  • the radial depth is the depth in the Longitudinal axis A of the piston 4 meant the vertical direction.
  • the axial height H of the groove 8 is at least ten percent of Diameter D of the piston 4.
  • the axial height is the expansion of the Groove 8 meant in the direction of the longitudinal axis A.
  • the radial depth T is at least six percent is specifically about 10 percent of the diameter D.
  • the groove 8 has a value of approximately fifteen percent of the diameter D. proven. "Approximately" denotes dimensions that are up to ⁇ 30% from corresponding nominal value may differ.
  • the groove 8 is in relation to the axial direction, with which the Direction of the longitudinal axis A is meant, arranged so that the groove 8 is the same height as the inlet opening 21 and thus this opposite when the piston is at top dead center. This is 3 can be seen in particular.
  • the groove 8 with respect to Axial direction can also be arranged so that it the inlet opening 21st only partially opposite when the piston 4 is at top dead center is located, that is, the inlet opening 21 is partially at the top dead center covered by the piston 4.
  • the groove 8 has rounded edges 81 has, as shown in Fig. 2 and Fig. 3.
  • the edges 81 which limit the groove 8 with respect to the radial direction to the outside each rounded down. As a result, the lubrication of the piston 4 can still continue to improve, and the stress peaks in the material are reduced.
  • Relief grooves 9 below the groove 8 provided for pressure equalization, each along the entire Extend circumference of the piston 4 and ensure that around the circumference the piston 4 around there is essentially the same pressure everywhere.
  • the Relief grooves 9 are usually with respect to their respective axial Height and their respective radial depth significantly smaller than that Slot 8.
  • the groove 8 ensures in particular in such operating states Suction throttle pump 1, in which only very small or no volume flows are promoted, so very little or no fuel in the Workspace 3 arrives, ensuring that it is not a defective one Lubrication of the piston 4 comes.
  • the groove 8 is a large one Cross-sectional area, with each working cycle with the inlet opening 21 connected when the piston 4 is at top dead center. Consequently fills the groove 8 - regardless of the respective angular position of the Piston 4 - with each stroke in the area of top dead center with fuel, which can flow into the groove 8 from the inlet opening 21.
  • the fuel located in the groove 8 along the tread of the Piston 4 distributed and thus ensures good lubrication of the piston 4th
  • the piston 4 returns to the upper one Dead center, fuel can flow in from the inlet opening 21, so that the groove 8 is filled again.
  • the groove 8 serves as a storage and distribution element for the lubricant that is identical to the fluid being pumped.
  • the groove 8 thus ensures that even in such Operating states in which the suction throttle pump 1 has no or only very much promotes small amounts of liquid, always sufficient lubrication of the Piston 4 is present so that there is no excessive wear, heavy wear or the piston 4 may seize. This significantly increases the operational safety of the suction throttle pump 1.
  • groove 8 can also deviate from that in FIGS. 1-3 Design shown cross-sectional areas other than a square have, for example, a partially curved or rounded Cross-section.
  • the terms axial height and radial depth then denote the maximum axial height or the maximum radial depth.
  • the suction throttle pump according to the invention is suitable for delivery any liquids.
  • a preferred use is as High pressure pump to deliver fuel to the injection system of a Diesel engine.
  • the suction throttle pump according to the invention especially as a high-pressure fuel pump in a fuel oil-powered one Large diesel engine suitable.
  • the suction throttle pump 1 is preferred driven by the crankshaft of the large diesel engine and promotes that Heavy oil under a pressure of up to 2000 bar, for example approximately 1200 bar into the injection system of the large diesel engine. If this after The suction throttle pump feeds the common rail principle Heavy oil under high pressure in the pressure accumulator (accumulator) of the common Rail systems.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
EP00810170A 2000-03-01 2000-03-01 Pompe d'injection de carburant haute pression Withdrawn EP1130250A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP00810170A EP1130250A1 (fr) 2000-03-01 2000-03-01 Pompe d'injection de carburant haute pression

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP00810170A EP1130250A1 (fr) 2000-03-01 2000-03-01 Pompe d'injection de carburant haute pression

Publications (1)

Publication Number Publication Date
EP1130250A1 true EP1130250A1 (fr) 2001-09-05

Family

ID=8174574

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00810170A Withdrawn EP1130250A1 (fr) 2000-03-01 2000-03-01 Pompe d'injection de carburant haute pression

Country Status (1)

Country Link
EP (1) EP1130250A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004088120A2 (fr) * 2003-04-01 2004-10-14 Avl List Gmbh Moteur a combustion interne
EP1598549A1 (fr) * 2004-05-20 2005-11-23 Magneti Marelli Powertrain S.p.A. Méthode d'injection directe de carburant dans un moteur à combustion interne
EP1598548A1 (fr) * 2004-05-20 2005-11-23 Magneti Marelli Powertrain S.p.A. Méthode et système d'injection directe de carburant dans un moteur à combustion interne
EP1930582A2 (fr) * 2006-11-30 2008-06-11 Mitsubishi Heavy Industries, Ltd. Appareil d'injection de carburant pour moteurs et procédé de fonctionnement de l'appareil
US7794216B2 (en) 2005-12-02 2010-09-14 Toyota Jidosha Kabushiki Kaisha High-pressure pump
WO2020064064A1 (fr) * 2018-09-25 2020-04-02 Continental Automotive Gmbh Dispositif pour faire fonctionner une pompe d'alimentation en fluide pour un véhicule automobile et pompe d'alimentation en fluide pour un véhicule automobile

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1068783A (fr) * 1951-08-23 1954-06-30 Bosch Gmbh Robert Pompe d'injection notamment pour moteurs à combustion interne
GB1406435A (en) * 1971-11-30 1975-09-17 Bryce Berger Ltd Fuel pumping apparatus
US4184816A (en) * 1977-05-05 1980-01-22 Robert Bosch Gmbh Angled-edge controlled fuel injection pump for internal combustion engines
DD236775A1 (de) * 1985-05-02 1986-06-18 Renak Werke Veb Pumpenelement fuer kraftstoffeinspritzpumpen
EP0863308A1 (fr) 1997-03-05 1998-09-09 Wärtsilä NSD Schweiz AG Pompe à piston pour refoulement des liquides

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1068783A (fr) * 1951-08-23 1954-06-30 Bosch Gmbh Robert Pompe d'injection notamment pour moteurs à combustion interne
GB1406435A (en) * 1971-11-30 1975-09-17 Bryce Berger Ltd Fuel pumping apparatus
US4184816A (en) * 1977-05-05 1980-01-22 Robert Bosch Gmbh Angled-edge controlled fuel injection pump for internal combustion engines
DD236775A1 (de) * 1985-05-02 1986-06-18 Renak Werke Veb Pumpenelement fuer kraftstoffeinspritzpumpen
EP0863308A1 (fr) 1997-03-05 1998-09-09 Wärtsilä NSD Schweiz AG Pompe à piston pour refoulement des liquides

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004088120A2 (fr) * 2003-04-01 2004-10-14 Avl List Gmbh Moteur a combustion interne
WO2004088120A3 (fr) * 2003-04-01 2005-06-09 Avl List Gmbh Moteur a combustion interne
EP1598549A1 (fr) * 2004-05-20 2005-11-23 Magneti Marelli Powertrain S.p.A. Méthode d'injection directe de carburant dans un moteur à combustion interne
EP1598548A1 (fr) * 2004-05-20 2005-11-23 Magneti Marelli Powertrain S.p.A. Méthode et système d'injection directe de carburant dans un moteur à combustion interne
US7063073B2 (en) 2004-05-20 2006-06-20 Magneti Marelli Powertrain, S.P.A. Method for the direct injection of fuel into an internal combustion engine
US7198034B2 (en) 2004-05-20 2007-04-03 Magneti Marelli Powertrain Spa Method and system for the direct injection of fuel into an internal combustion engine
US7794216B2 (en) 2005-12-02 2010-09-14 Toyota Jidosha Kabushiki Kaisha High-pressure pump
EP1930582A2 (fr) * 2006-11-30 2008-06-11 Mitsubishi Heavy Industries, Ltd. Appareil d'injection de carburant pour moteurs et procédé de fonctionnement de l'appareil
EP1930582A3 (fr) * 2006-11-30 2011-09-07 Mitsubishi Heavy Industries, Ltd. Appareil d'injection de carburant pour moteurs et procédé de fonctionnement de l'appareil
WO2020064064A1 (fr) * 2018-09-25 2020-04-02 Continental Automotive Gmbh Dispositif pour faire fonctionner une pompe d'alimentation en fluide pour un véhicule automobile et pompe d'alimentation en fluide pour un véhicule automobile

Similar Documents

Publication Publication Date Title
DE102006056600B4 (de) Hochdruckpumpe
DE69920601T2 (de) Brennstoffzufuhrpumpe für benzineinspritzanlagen
WO2004072477A1 (fr) Pompe haute pression
DE2503346A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE69724695T2 (de) Radialkolbenpumpe
DE2353737A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE102006026220B4 (de) Fluidpumpe mit Kurbeltrieb
EP1395753B1 (fr) Pompe haute pression pour un systeme de carburant d'un moteur a combustion interne
EP1130250A1 (fr) Pompe d'injection de carburant haute pression
DE60200507T2 (de) Kraftstoffeinpritzpumpe mit gedrosseltem Kraftstoffkanal zur Schmierung
EP2795095A1 (fr) Pompe, en particulier pompe d'alimentation en carburant haute pression d'un dispositif d'injection de carburant
DE3911160C2 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE19531870C2 (de) Kraftstoffeinspritzsystem
DD151487A5 (de) Kolbenmaschine,insbesondere kolbenpumpe
EP1454055B1 (fr) Pompe a piston radiaux a graissage force
DE2342107A1 (de) Drehzahlregler fuer kraftstoffeinspritzpumpen
DE10208574A1 (de) Radialkolbenpumpe
DE19844326A1 (de) Radialkolbenpumpe
WO1991010063A1 (fr) Pompe d'injection de carburant pour moteurs a combustion interne
DE60203777T2 (de) Kraftstoffeinspritzpumpe
EP4168673A1 (fr) Pompe à piston alternatif pour transporter un milieu
EP0863308A1 (fr) Pompe à piston pour refoulement des liquides
WO2005003558A1 (fr) Mecanisme de transmission excentrique destine a des pompes d'action volumetrique ou moteurs
EP0881380A1 (fr) Pompe d'alimentation haute-pression
DE2425361C3 (de) Kraftstoffverteilereinspritzpumpe für Brennkraftmaschinen

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

AKX Designation fees paid
REG Reference to a national code

Ref country code: DE

Ref legal event code: 8566

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20020306