EP1687524B1 - Pompe d'alimentation haute pression destinee a des moteurs a combustion interne - Google Patents

Pompe d'alimentation haute pression destinee a des moteurs a combustion interne Download PDF

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Publication number
EP1687524B1
EP1687524B1 EP04797222A EP04797222A EP1687524B1 EP 1687524 B1 EP1687524 B1 EP 1687524B1 EP 04797222 A EP04797222 A EP 04797222A EP 04797222 A EP04797222 A EP 04797222A EP 1687524 B1 EP1687524 B1 EP 1687524B1
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EP
European Patent Office
Prior art keywords
actuator
pressure
feed pump
valve
inlet
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.)
Not-in-force
Application number
EP04797222A
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German (de)
English (en)
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EP1687524A1 (fr
Inventor
Marco A. Ganser
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Ganser Hydromag AG
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Ganser Hydromag AG
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Publication of EP1687524A1 publication Critical patent/EP1687524A1/fr
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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
    • 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
    • F04B1/0404—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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0038—Piston machines or pumps characterised by having positively-driven valving the distribution member forming a single inlet for a plurality of pumping chambers or a multiple discharge for one single pumping chamber
    • 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
    • F04B7/00—Piston machines or pumps characterised by having positively-driven valving
    • F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic 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
    • F02M63/02—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

Definitions

  • the invention relates to a high-pressure feed pump, in particular for an injection system for internal combustion engines, according to the preamble of claim 1.
  • CH-A-689 281 discloses a fuel injection system for an internal combustion engine, in particular for a diesel engine, and a method for monitoring the same disclosed.
  • the fuel injection system has for each combustion cylinder at least one controlled by a control unit injection element, which has a leading into the cylinder, closable by this injection port and a pressure chamber arranged in front of the latter.
  • the pressure chamber is connected to a supplied by a fuel pump in response to engine speed, load and load change high pressure part.
  • the injection quantity of the fuel into the combustion cylinder can be supplied by means of a quantity metering device which is preferably connected upstream of the fuel pump and actuated by the control unit.
  • the metering device has a valve which is assigned to a pump piston of the fuel pump.
  • a high-pressure scribe system is described with common rail, which has a provided with at least one outlet channel channel element with opposite end faces.
  • On the front sides are on high-pressure sealing surfaces on the one hand a plunger cylinder of a high-pressure pump and on the other hand connected to a common rail, so that the high-pressure pump via an inlet valve suck in a pumped medium and can introduce with increased pressure through the outlet channel of the channel element and an outlet valve via a drain channel in the space provided in the common rail pressure chamber.
  • the flow rate of the pumped medium to the pump cylinder is controlled by a suction throttle valve projecting into a transfer channel.
  • the present invention is based on the object to provide a high pressure pump with a precise, reliable and very cost effective flow control.
  • the high-pressure feed pump according to the invention which is provided in particular for use in an injection system for internal combustion engines, has at least two delivery chambers delimited by a respective pump cylinder and a driven plunger.
  • the two delivery chambers communicate with a low pressure inlet port via single actuator controlled intake valves and a high pressure exhaust port with a pressure controlled exhaust port.
  • valve members of the intake valves are connected to each other by means of a rocker pivotally mounted on an actuator shaft of the actuator. Upon energization of the actuator, the actuator shaft is displaced and those intake valves located in an open position closed at where the associated plunger is in a delivery stroke.
  • the precision of the delivery quantity metering of the high-pressure delivery pump according to the invention corresponds to that of known high-pressure delivery pumps. In the subject invention, however, this is achieved by a smaller number of required actuators with significantly lower material and cost. In addition, the actuator requirements are reduced by operating in a pulsed mode and thus being in an energized state only for a short time. Another factor for reducing costs is the modular design of a preferred embodiment, in which form cylinder heads, cylinder body and a housing for receiving an eccentric shaft stand-alone mounting units, which are pressed tightly by means of bolts by screw. Furthermore, in one embodiment, the housing and the eccentric shaft are designed such that a simple assembly by inserting the eccentric shaft from an end face of the housing is possible in the same.
  • FIG. 1 is a longitudinal section of an inventive high-pressure pump 10 in the embodiment of a radial piston pump with four pump cylinders 12.1, 12.2, 12.3, 12.4 shown in a series arrangement.
  • the high-pressure pump 10 is provided for internal combustion engines, in particular for diesel engines with a common rail.
  • Each of the pump cylinders 12.1, 12.2, 12.3, 12.4 has a similar structure and has one of the inner walls of all pump cylinders 12.1, 12.2, 12.3, 12.4 common cylinder head 14, a cylinder body 16 and a plunger 18.1, 18.2, 18.3, 18.4 limited delivery space 20 on.
  • the inner walls of the hollow cylindrical cylinder body 16 are designed as tight sliding fits (2 ⁇ m to 10 ⁇ m) for the plunger 18.1, 18.2, 18.3, 18.4.
  • the cylinder body 16 are sandwiched between the cylinder head 14 and the housing 22 by means of bolts 24 and pressed tightly together.
  • the plungers 18.1, 18.2, 18.3, 18.4 are supported on them by compressive springs 26 against the cylinder body 16 and sit with their Plungerglassen 27 on a lubricant film sliding on two-piece rolling elements 28.
  • the rolling body 28 surround cylindrical crank bearing 30, which is connected to a drive of the plunger 18.1, 18.2, 18.3, 18.4 serving eccentric shaft 32 rotatable are stored.
  • the two-part crank bearings 30 in turn surround eccentric, which are formed eccentrically offset from the longitudinal axis of the eccentric shaft 32.
  • the eccentric shaft 32 is rotatably mounted on shaft bearings 31 in the housing 22.
  • the plungers 18.1, 18.2, 18.3, 18.4 of the pump cylinders 12.1, 12.2, 12.3, 12.4 differ in their in Fig. 2 illustrated stroke position: the designated 18.1 plunger is located at a bottom dead center at the beginning of the delivery stroke, designated 18.2 at a top dead center at the beginning of the suction stroke, so moved by 180 ° against the stroke position of the plunger 18.1, the designated 18.3 plunger in the middle winninghubposition, ie 90 ° ahead of the stroke position of the plunger 18.1, and the designated 18.4 plunger in the middle suction stroke position, so moved by 180 ° against the stroke position of the plunger 18.3.
  • a cylinder head body 36 of the cylinder head 14 has four identical intake valves 40.1, 40.2, 40.3, 40.4, each associated with one of the four pump cylinders 18.1, 18.2, 18.3, 18.4, each having a valve member movably arranged in a cylindrical recess in the form of a valve stem 38.1, 38.2, 38.3 , 38.4 on.
  • Two inlet valves 40.1 and 40.2 and 40.3 and 40.4, which are associated with the plungers 18.1 and 18.2 and 18.3 and 18.4, are each actuated via a respective pivotable rocker 42.1 or 42.2.
  • the middle support position of the rocker 42.1, 42.2 is controlled by an actuator 44.1, 44.2.
  • a longitudinally rectilinear, tubular inlet channel 46 which is connected to the recesses for the inlet valves 40.1, 40.2, 40.3, 40.4 and the supply of a pumped medium 48 is used.
  • the delivery medium 48 is already in the inlet channel 46 under a pressure between 100 kPa and 600 kPa, which has been generated by a not shown prefeed pump.
  • the cylinder head 14 further per per pump cylinder 12.1, 12.2, 12.3, 12.4 depending on a pressure-controlled outlet valve 50.1, 50.2, 50.3, 50.4 in a corresponding recess.
  • the recesses are connected to a high-pressure outlet channel 52, whose volume forms a pressure accumulator.
  • Fig. 2 is an enlarged section of Fig. 1 with two jointly controlled intake valves 40.1, 40.2 shown. Based on Fig. 2 will describe further details of the structure and the operation of the high-pressure pump 10 below. Due to the similar structure, these details as well as their function can be transferred to the not shown part of the high-pressure pump 10.
  • the delivery chamber 48 of the pump cylinder 12.1, 12.2, 12.3, 12.4 narrows in the direction of the inlet valve 40.1, 40.2, 40.3, 40.4 to a valve seat 56 of the valve stem 38.1, 38.2, 38.3, 38.4 cooperating inlet valve seat 54.1, 54.2, 54.3, 54.4.
  • the valve stem 38.1, 38.2, 38.3, 38.4 is biased at its, the valve plate 56 opposite end portion by means of a compression spring 58 against the cylinder head body 36 in its closed position. In the closed position, the valve plate 56 sits tightly on the inlet valve seat 54.1, 54.2, 54.3, 54.4.
  • valve stem 38.1, 38.2, 38.3, 38.4 the valve plate 56 formed opposite hemispherical valve stem 60 is in a cup-shaped valve stem 62 of the rocker 42.1, 42.2 stored.
  • the rocker 42.1, 42.2 has on the same side in the opposite end region a second valve stem receptacle 62 for receiving the associated second valve stem 38.1, 38.2, 38.3, 38.4 of the second inlet valve 40.1, 40.2, 40.3, 40.4.
  • a hemispherical actuator receptacle 64 is formed on the rocker 42.1, 42.2.
  • the actuator shaft 66 presses into the actuator receptacle 64.
  • a positional shift of the rocker 42.1, 42.2 in the direction of the longitudinal axis of the Aktuatorschafts 66 is controlled by the actuator 44.1, 44.2.
  • the actuator shaft 66 is biased against the actuator 44.1, 44.2 in the direction of the open position of the associated intake valves 40.1, 40.2 or 40.3, 40.4 by means of an actuator shaft spring 67 designed as a compression spring.
  • the bias of the Aktuatorschaftfeder 67 is greater than the sum of the oppositely acting biases of the respective associated compression springs 58 of the intake valves 40.1, 40.2 and 40.3, 40.4.
  • the actuator 44.1, 44.2 preferably has an electromagnet; a piezoelectric element would also be conceivable.
  • the actuator shaft 66 is formed as an extension of an actuator armature.
  • the actuator 44.1, 44.2 and thus the position of the Aktuatorschafts 66 is influenced by a not shown, preferably electronic control.
  • the actuator 44.1, 44.2 is mounted on a cylinder head cover 68 fastened to the cylinder head 14.
  • the cylinder head cover 68 has centrally a recess through which the actuator shaft 66 is movably passed.
  • the cylinder head cover 68 spans a recess in the cylinder head body 36, in which the valve stem heads 60 emerge with the compression springs 58 and the bearing on the valve stem heads 60 rocker 42.1, 42.2 is located.
  • a thrust washer 78 is mounted opposite an outer circumferential shoulder of the eccentric shaft 32.
  • a further thrust washer 78 supports the end face of the eccentric shaft 32 directly against a further housing cover 74, which is provided with a passage for the supply of lubricant from.
  • the thrust washers 78 are used for the transverse guidance of the eccentric shaft 32 in the housing 22.
  • a circumferential lip seal 80 is connected to the housing cover 74, which prevents leakage of lubricant from the housing 22 by their concerns on the drive pin 31.
  • sealing rings 82 are inserted into correspondingly shaped grooves. Due to the strong pressure of the said parts on each other, a tight closure of the high-pressure feed pump 10 is ensured and prevents leakage of the pumped medium 48 or of the lubricant.
  • the discharge of the pumped medium 48 during the delivery stroke of the plunger 18.1, 18.2, 18.3, 18.4 takes place through the pressure-controlled outlet valves 50.1, 50.2, 50.3, 50.4 in the outlet channel 52.
  • the exhaust valves 50.1, 50.2, 50.3, 50.4 are designed as ball valves known type.
  • a ball 84 is in Pressed their closed position by a biased Auslassdruckfeder 86 in their Auslassventilsitz 88 and closes the high-pressure outlet channel 52 tightly against the delivery chamber 20.
  • a first plunger 18.1 of a pump cylinder 12.1 is initially in its suction stroke, the associated outlet valve 50.1 in its closed position and the actuator 44.1 in a non-excited state.
  • the associated first inlet valve 54.1 is in the open position during the suction stroke due to the dominant bias of the actuator stem spring 67.
  • the conveying medium 48 which is already below the pressure generated by an upstream, not shown prefeed pump, is moved from the low-pressure inlet channel 46 through the opened inlet valve 40 Suction chamber 20 sucked.
  • the plunger 18.1 reaches the bottom dead center at the end of its suction stroke. In this, in Fig. 3 shown position of the plunger 18.1, the volume of the conveying space 20 is maximum.
  • the delivery chamber volume is reduced by the movement of the plunger 18.1 and delivery medium 48 is pushed back through the open inlet valve 40.1 into the inlet channel 46 until the delivery chamber volume corresponds to the desired delivery quantity.
  • the actuator shaft 66 is attracted along its longitudinal axis against the bias of the Aktuatorschaftfeder 67 and closed the inlet valve 40.1 at this time.
  • the rocker 42.1 follows this movement due to the bias of the pressure spring 26 mounted on the valve stem 38.1 and the pressure increase subsequently occurring in the pumping chamber 20 as a result of the movement of the plunger 18.1 in the direction of the inlet valve 40.1.
  • the valve plate 56 of the valve stem 38.1 is pressed against its inlet valve seat 54.1, so that no pumped medium 48 can leave the delivery chamber 20 through the inlet valve 40.1.
  • a second, associated with the same rocker 42.1 inlet valve 40.2 remains in spite of the excitation of the actuator 44.1 in its open position, since the 180 ° out of phase with the first plunger 18.1 moving second plunger 18.2 is in the suction stroke and because of the pressure difference between the low-pressure inlet port 46 and the delivery chamber 20 the valve stem 38.2 while doing in the direction of the conveyor 20 holds open.
  • the first inlet valve 40.1 After the end of the pulse-like excitation of the actuator 44.1, the first inlet valve 40.1 remains in its closed position until the next following suction stroke.
  • the associated second inlet valve 40.2 is replaced by the Stopping the excitation of the actuator 44.1 is not affected and remains in its open position.
  • the first inlet valve 40.1 is opened and the delivery medium 48 is sucked into the delivery chamber 20.
  • the associated second plunger 18.2 passes through the bottom dead center and begins to push the medium 48 back into the inlet channel 46 until the inlet valve 40.2 is closed by means of a renewed pulse-like excitation of the actuator 44.1.
  • the described mode of operation continues periodically and, by controlling the time from opening to closing of the inlet valves 40.1, 40.2, 40.3, 40.4, makes it possible to control the quantity of the pumped medium 48 forced into the high-pressure outlet channel.
  • the amount in this case ranges from a maximum, namely a delivery chamber volume per plunger period and pump cylinders 12.1, 12.2, 12.3, 12.4, to zero, in which case the inlet valves 40.1, 40.2, 40.3, 40.4 remain open during the entire plunger period. In the latter case, the high pressure pump 10 operates at idle.
  • the flow rate by closing the intake valves 40.1, 40.2, 40.3, 40.4 already in the intake stroke be limited.
  • the preloads of the compression springs 58 of the inlet valves 40.1, 40.2, 40.3, 40.4 and the actuator shaft 66 must be adjusted accordingly.
  • the bias of Compression springs 58 must be chosen such that the inlet valves 40.1, 40.2, 40.3, 40.4 can also be closed during the suction stroke.
  • a modification of the actuators 44.1, 44.2 in particular with regard to longer holding times necessary.
  • a series arrangement of radial piston pumps can alternatively also be replaced by a boxer arrangement or an arrangement with pump cylinders rotated at an angle about the longitudinal axis of the eccentric shaft.
  • the rocker is preferably formed star or triangular.
  • Three corresponding valve stem receptacles can be arranged, for example, evenly around a central actuator receptacle.
  • the dosage of the flow rate is limited to a range between zero and about 2/3 of the maximum flow before an irregular promotion occurs.
  • the maximum flow rate corresponds to the flow rate in the event that each of the inlet valves is closed at the exact time at which the respective associated plunger passes through its bottom dead center before the subsequent pressure stroke.
  • the plungers 18.1, 18.2, 18.3, 18.4 can also be mounted in a floating manner by means of a pressure compensation for the extremely low-friction movement on the rolling bodies 28.
  • the plunger 18.1, 18.2, 18.3, 18.4 are equipped with hollow shafts, in which stamps are guided freely movable. In a delivery stroke of the plunger 18.1, 18.2, 18.3, 18.4 of the punch is pressed in the direction of the rolling body 28 and located in the hollow shaft lubricant between the plunger 27 and the Abicalz stresses 28 is pressed.
  • the assembly of the high-pressure pump is particularly simple and inexpensive due to the modular structure of the separately manufactured assembly units cylinder head 14, cylinder body 16 and housing 22.
  • the possibility for lateral insertion of the eccentric shaft 32 in the housing 22 contributes to ease of assembly.

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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)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Claims (12)

  1. Pompe d'alimentation haute pression destinée à un système d'injection de moteurs à combustion interne, comportant au moins deux chambres d'alimentation (20) délimitées par un cylindre de pompe (12.1, 12.2, 12.3, 12.4) et un plongeur entraîné (18.1, 18.2, 18.3, 18.4), qui sont en communication avec un canal d'admission basse pression (46) au moyen d'une soupape d'admission (40.1, 40.2, 40.3, 40.4) respectivement commandée au moyen d'un actionneur (44.1, 44.2) et avec un canal d'échappement haute pression (52) au moyen d'une soupape d'échappement (50.1, 50.2, 50.3, 50.4) commandée par la pression, caractérisée en ce qu'au moins deux soupapes d'admission (40.1, 40.2, 40.3, 40.4) sont commandées au moyen d'un actionneur unique (44.1, 44.2).
  2. Pompe d'alimentation haute pression selon la revendication 1, caractérisée en ce que, pendant une course d'aspiration du plongeur (18.1, 18.2, 18.3, 18.4) avec la soupape d'admission (40.1, 40.2, 40.3, 40.4) ouverte, la chambre d'alimentation (20) est remplie entièrement d'un fluide d'alimentation et le fluide d'alimentation est de nouveau refoulé par le plongeur (18.1, 18.2, 18.3, 18.4) à travers la soupape d'admission (40.1, 40.2, 40.3, 40.4) ouverte pendant la course de refoulement qui suit, jusqu'à ce que le volume de chambre d'alimentation de la chambre d'alimentation (20) corresponde à une quantité d'alimentation de consigne et que la soupape d'admission (40.1, 40.2, 40.3, 40.4) soit fermée par un actionnement de préférence impulsionnel de l'actionneur (44.1, 44.2).
  3. Pompe d'alimentation haute pression selon la revendication 1 ou 2, caractérisée en ce que les soupapes d'admission (40.1, 40.2, 40.3, 40.4) et les soupapes d'échappement (50.1, 50.2, 50.3, 50.4) sont disposées dans un corps de culasse (36) d'une culasse (14).
  4. Pompe d'alimentation haute pression selon l'une quelconque des revendications 1 à 3, caractérisée en ce que les plongeurs (18.1, 18.2, 18.3, 18.4) associés aux soupapes d'admission (40.1, 40.2, 40.3, 40.4) commandées au moyen de l'actionneur (44.1, 44.2) sont entraînés en synchronisme, mais avec un déphasage de préférence de 180° ou de 120° l'un par rapport à l'autre.
  5. Pompe d'alimentation haute pression selon l'une quelconque des revendications 1 à 4, caractérisée en ce que chaque soupape d'admission (40.1, 40.2, 40.3, 40.4) comprend un organe de soupape (38.1, 38.2, 38.3, 38.4) coopérant avec un siège de soupape d'admission (54.1, 54.2, 54.3, 54.4), les organes de soupape des soupapes d'admission (40.1, 40.2, 40.3, 40.4) commandés au moyen de l'actionneur (44.1, 44.2) sont reliés l'un à l'autre au moyen d'une bascule (42.1, 42.2) pouvant pivoter sur une tige d'actionneur (66) de l'actionneur (44.1, 44.2) et l'actionneur (44.1, 44.2) commande la position de la tige d'actionneur (66).
  6. Pompe d'alimentation haute pression selon la revendication 5, caractérisée en ce que les organes de soupape (38.1, 38.2, 38.3, 38.4) sont précontraints dans leur position de fermeture.
  7. Pompe d'alimentation haute pression selon la revendication 5 ou 6, caractérisée en ce que la tige d'actionneur (66) est précontrainte dans la direction de la position d'ouverture des organes de soupape (38.1, 38.2, 38.3, 38.4).
  8. Pompe d'alimentation haute pression selon l'une quelconque des revendications 5 à 7, caractérisée en ce que les soupapes d'admission (40.1, 40.2, 40.3, 40.4), associées à la bascule (42.1, 42.2) et se trouvant dans une position d'ouverture, de cylindres de pompe (12.1, 12.2, 12.3, 12.4) dont les plongeurs (18.1, 18.2, 18.3, 18.4) se trouvent dans la course de refoulement, sont amenées dans une position de fermeture par une excitation de l'actionneur (44.1, 44.2) lors d'un déplacement de la tige d'actionneur (66).
  9. Pompe d'alimentation haute pression selon l'une quelconque des revendications 5 à 8, caractérisée en ce que la pompe d'alimentation haute pression (10) est une pompe à pistons axiaux et deux ou trois soupapes d'admission (40.1, 40.2, 40.3, 40.4) sont commandées au moyen d'un actionneur unique (44.1, 44.2), dans laquelle la bascule (42.1, 42.2) présente trois bras de bascule disposés en étoile dans le cas de trois soupapes d'admission (40.1, 40.2, 40.3, 40.4).
  10. Pompe d'alimentation haute pression selon l'une quelconque des revendications 1 à 9, caractérisée en ce que les soupapes d'admission (40.1, 40.2, 40.3, 40.4) sont amenées, dans le but de doser la quantité, dans leur position de fermeture pendant la course de refoulement des plongeurs respectifs correspondants (18.1, 18.2, 18.3, 18.4).
  11. Pompe d'alimentation haute pression selon l'une quelconque des revendications 1 à 10, caractérisée en ce que la pompe d'alimentation haute pression (10) est une pompe à pistons radiaux et chaque fois deux soupapes d'admission (40.1, 40.2, 40.3, 40.4) sont commandées au moyen d'un actionneur unique (44.1, 44.2).
  12. Pompe d'alimentation haute pression selon la revendication 1, caractérisée en ce que l'actionneur (44.1, 44.2) comprend une tige d'actionneur (66) dont la position peut être influencée, qui presse dans un logement d'actionneur (64) d'une bascule pivotante (42.1, 42.2), montée sur des têtes de poussoir de soupape (60) d'organes de soupape (38.1, 38.2, 38.3, 38.4) des soupapes d'admission (40.1, 40.2, 40.3, 40.4), qui est prédéfinie pour actionner chaque fois deux soupapes d'admission (40.1, 40.2, 40.3, 40.4) et en ce que l'actionneur (44.1, 44.2) commande un déplacement de position de la bascule (42.1, 42.2).
EP04797222A 2003-11-28 2004-11-04 Pompe d'alimentation haute pression destinee a des moteurs a combustion interne Not-in-force EP1687524B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH20352003 2003-11-28
PCT/CH2004/000665 WO2005052357A1 (fr) 2003-11-28 2004-11-04 Pompe d'alimentation haute pression destinee a des moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1687524A1 EP1687524A1 (fr) 2006-08-09
EP1687524B1 true EP1687524B1 (fr) 2008-07-02

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EP04797222A Not-in-force EP1687524B1 (fr) 2003-11-28 2004-11-04 Pompe d'alimentation haute pression destinee a des moteurs a combustion interne

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EP (1) EP1687524B1 (fr)
AT (1) ATE399936T1 (fr)
DE (1) DE502004007514D1 (fr)
WO (1) WO2005052357A1 (fr)

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WO2009003443A1 (fr) * 2007-07-03 2009-01-08 Robert Bosch Gmbh Machine hydraulique à commande par soupapes

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DE102008040083A1 (de) * 2008-07-02 2010-01-07 Robert Bosch Gmbh Hochdruckpumpe
DE102011082733A1 (de) * 2011-09-15 2013-03-21 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
CH716632A1 (de) * 2019-09-25 2021-03-31 Liebherr Machines Bulle Sa Reihenkolbenpumpe.

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CH635167A5 (de) * 1979-01-25 1983-03-15 Sulzer Ag Einspritzeinrichtung eines dieselmotorzylinders.
DE3112381A1 (de) * 1981-03-28 1982-11-11 Robert Bosch Gmbh, 7000 Stuttgart Elektrisch gesteuerte kraftstoffeinspritzeinrichtung fuer mehrzylinder-brennkraftmaschinen, insbesondere zur kraftstoffdirekteinspritzung bei fremdgezuendeten brennkraftmaschinen
US5701873A (en) * 1993-11-08 1997-12-30 Eidgenoessische Technische Hochschule Laboratorium Fuer Verbrennungsmotoren Und Verbrennungstechnik Control device for a filling-ratio adjusting pump
EP1101931B1 (fr) * 1999-11-19 2006-08-30 CRT Common Rail Technologies AG Système d'injection à haute pression avec common rail
WO2003023232A2 (fr) * 2001-09-10 2003-03-20 Stanadyne Corporation Commande hybride de la demande pour une pompe hydraulique
EP1321663A3 (fr) * 2001-12-19 2003-07-02 Robert Bosch Gmbh Dispositif d'injection de combustible pour moteur à combustion interne

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009003443A1 (fr) * 2007-07-03 2009-01-08 Robert Bosch Gmbh Machine hydraulique à commande par soupapes

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DE502004007514D1 (fr) 2008-08-14
EP1687524A1 (fr) 2006-08-09
WO2005052357A1 (fr) 2005-06-09
ATE399936T1 (de) 2008-07-15

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