EP0318534B1 - Pompe d'injection a distributeur du type a pistons radiaux - Google Patents

Pompe d'injection a distributeur du type a pistons radiaux Download PDF

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Publication number
EP0318534B1
EP0318534B1 EP19880904479 EP88904479A EP0318534B1 EP 0318534 B1 EP0318534 B1 EP 0318534B1 EP 19880904479 EP19880904479 EP 19880904479 EP 88904479 A EP88904479 A EP 88904479A EP 0318534 B1 EP0318534 B1 EP 0318534B1
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EP
European Patent Office
Prior art keywords
pump
distributor
plunger
chamber
switching valve
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.)
Expired - Lifetime
Application number
EP19880904479
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German (de)
English (en)
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EP0318534A1 (fr
Inventor
André Brunel
Jean Paul Morel-Fourrier
Jean Leblanc
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • F02M41/063—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating the distributor and rotary valve controlling fuel passages to pumping elements being combined
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/02—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements
    • F02M41/06—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor being spaced from pumping elements the distributor rotating
    • 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
    • F02M63/0205—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—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 for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits

Definitions

  • the invention relates to a distributor fuel injection pump of the radial piston type of the type defined in the preamble of claim 1.
  • the displacement of the distributor piston serves to control the fuel injection quantity.
  • the point of the pump piston stroke, from which the amount of fuel delivered by the pump piston is interrupted to interrupt the fuel injection, is controlled via an inclined edge on the distributor piston that can be adjusted by the displacement.
  • the deactivated fuel is used to set a pressure in the control chamber with the help of an adjustable discharge throttle, by means of which the distributor piston is adjusted against the force of a control spring.
  • This fuel injection pump is very complex and offers no possibility of electrically controlling the fuel injection quantity taking into account various operating parameters. To adjust the start of spraying, a spray adjustment device is still required in a complex manner.
  • the pump work area is always completely filled with fuel during the suction stroke of the pump piston.
  • the amount of this fuel volume to be injected is determined as a function of parameters of the internal combustion engine, such as load and speed, by the time at which the electrical switching valve closes and opens.
  • the switching valve closes the fuel injection starts in the respective cylinder of the internal combustion engine, while when the switching valve is opened, the pump work chamber is connected to the relief chamber and the fuel injection is suddenly stopped.
  • the internal combustion engine is always supplied with the maximum fuel injection quantity regardless of the load, so that the speed of the internal combustion engine increases uninfluenced, the internal combustion engine "spins".
  • the object of the invention is to develop a generic distributor fuel injection pump so that it has the advantages of an easily and precisely feasible control of the fuel injection with the aid of an electrical switching valve and is further secured against spinning if a malfunction of the switching valve occurs. According to the invention, this object is achieved by the features of the characterizing part of patent claims 1 and 2.
  • the defect of the switching valve is recognized by a monitoring device, which then issues a closing command to the second switching valve.
  • a criterion for the defect of the first switching valve can be, for example, the increase in the speed of the internal combustion engine beyond a maximum speed.
  • the second switching valve is expediently designed such that it is normally closed and opens when actuated. The switching valve then closes when the control is omitted, so that the closing command consists in interrupting the excitation current for the electromagnet of the second switching valve. In this way, the fuel delivery is interrupted even when the control line of the second switching valve is disturbed.
  • the second switching valve can be much simpler and therefore cheaper than the first switching valve.
  • the radial piston type distributor fuel injection pump shown in longitudinal section in FIG. 1 has a cup-shaped housing 10 and a cover 11 closing it, which is pushed in from the open end of the housing 10 and delimits a pump interior 12 with a bottom 10a integral with the housing 10.
  • the pump interior 12 is filled with fuel at low pressure and is connected via a drain opening 13 with an upstream throttle 14 to a fuel return line leading to a fuel tank (both not shown).
  • a drive shaft 15 is passed through the bottom 10a of the housing 10 in a liquid-tight manner, which widens in a pot-shaped manner in the pump interior 12 and rotates with it along its edge connected cam ring 16 carries.
  • the cam ring 16 has on its inside in a known manner a cam track 17 with radially inwardly directed cams, the number and sequence of the number and sequence of radial pump pistons contained in the fuel injection pump and the number with these pump pistons per revolution of the drive shaft 15 piston strokes to be carried out are adapted.
  • a feed pump 18 sits on the drive shaft 15 and is connected to the fuel tank via an intake line 19 and to the pump interior 12 via a pressure line 20 and thereby ensures the fuel filling of the pump interior 12.
  • a distributor piston 21 is also connected to the drive shaft 15 in a rotationally fixed but axially displaceable manner, the axis of which is aligned with the axis of the drive shaft 15.
  • the distributor piston 21 is guided except for the end connected to the drive shaft 15 in the pump interior 12 in a distributor cylinder 22 which is held in a bore 23 of the cover 11 which is coaxial with the axis of the drive shaft 15.
  • Adjacent to the cam track 17, radially inward thereafter, guides 24 are provided in the cover 11 and in the distributor cylinder 22, which are evenly distributed over the circumference of the distributor cylinder 22 and extend close to the distributor piston 21.
  • FIG. 1 for supplying a total of three injection nozzles of an internal combustion engine, in particular a diesel engine, there are a total of three guides 24, of which only one can be seen in FIG. 1.
  • radial through bores 25 are provided in the distributor cylinder 22, in each of which a pump piston 26 is guided so as to be longitudinally displaceable.
  • a so-called roller plunger 27 is guided in a longitudinally displaceable manner, which consists of a roller or roller 28 and one Pusher cup 29 exists.
  • a plunger spring 31 which is basically supported on the one hand and on a spring plate 30 resting on the bottom of the plunger cup 29 on the other hand, presses the plunger cup 29 against the roller 28 and the latter against the cam track 17.
  • the spring plate 30 engages behind a protruding from the radial through bore 25 Collar 26a of the pump piston 26 and thus fixes the latter to the tappet cup 29.
  • Each pump piston 26 delimits a pump working chamber 32 in the radial through bore 25, the other limitation of which is formed by an annular groove 33 on the distributor piston 21.
  • a distributor groove 34 and a filling groove 35 open into the annular groove 33, each of which extends axially in opposite directions from the annular groove 33 on the distributor piston 21.
  • three injection bores 36 open in a cross-sectional plane, which are evenly distributed over the circumference of the distributor cylinder 22 and lead through the distributor cylinder 22 and the cover 11 to an injection nozzle 37 each. Of the three injection nozzles in total, one injection nozzle 37 is indicated schematically in FIG. 1.
  • the axial length of the distributor groove 34 is dimensioned such that it projects into the cross-sectional plane of the mouths of the injection bores 36 and thus connects one of the three injection bores 36 with the annular groove 33 depending on the rotational position of the distributor piston 21.
  • three filling bores 38 open out in the interior of the distributor cylinder 22 and are arranged uniformly distributed around the circumference of the distributor cylinder 22.
  • the axial length of the filling groove 35 is dimensioned such that it projects into this cross-sectional plane of the mouths of the filling bores 38 and thus one of the three, depending on the rotational position of the distributor piston 21 Filling holes 38 connects to the annular groove 33.
  • the coupling of the distributor piston 21 to the drive shaft 15 takes place via a pin-slot connection, in which a driving pin 39 on the drive shaft 15 positively engages in a longitudinal groove 40 in the distributor piston 21.
  • the basic position of the distributor piston 21 shown in FIG. 1 is determined by a helical compression spring 41 which presses the end of the longitudinal groove 40 against the driving pin 39, which thus forms a limit stop for the axial displacement movement of the distributor piston 21.
  • valve housing 42 of an electrical switching valve 43 On the outward-facing end face of the cover 11, the valve housing 42 of an electrical switching valve 43 is placed and fastened there in a corresponding manner.
  • the valve housing 42 engages with a centering pin in the inner cavity of the distributor cylinder 22 and, together with the end face 71 of the distributor piston 21 opposite it, delimits a control chamber 44.
  • the structure of the switching valve is known and is described, for example, in DE-OS 35 23 536.
  • the two valve connections 45, 46 of the switching valve 43 are connected to one another via a valve opening 47, which is controlled by a valve member 48.
  • the valve member 48 is actuated by an electromagnet 49, the valve member 48 opening the valve opening 47 in the non-energized state of the electromagnet 49 under the action of a return spring (not shown) and closing it in the energized state of the electromagnet 49.
  • the valve connection 45 covers a first bore section 51 of a relief line 50 opening into the end face of the cover, while the second valve connection 46 covers an opening in the end face of the cover 11 of a second bore section 52 of the relief line 50.
  • the pump work chamber 32 with the pump interior 12 is in via the relief line 50 Connection.
  • the pressure line 20 between the feed pump 18 and the pump interior 12 is guided via the control chamber 44 in the distributor cylinder 22, which divides the pressure line 20 into a first and second line section 53, 54.
  • a second electrical switching valve 55 is arranged, which controls a valve opening 57 integrated in the second line section 54 with a valve member 56.
  • the valve member 56 is actuated by an electromagnet 58, the valve member 56 closing the valve opening 57 in the non-energized state of the electromagnet 58 under the action of a valve closing spring 59 and releasing the electromagnet 58 in the energized state.
  • the second switching valve 55 is controlled by a monitoring device 60, which constantly monitors the proper functioning of the first switching valve 43 and issues a closing command in the form of switching off the excitation current for the electromagnet 58 to the second switching valve 55 as soon as the valve member 48 of the first switching valve 43 despite Elimination of the excitation of the electromagnet 49 does not open.
  • a monitoring device 60 can be designed, for example, as a speed detector that outputs the closing command to the second switching valve 55 when the speed of the internal combustion engine exceeds a predetermined maximum speed, which is a criterion for the no longer opening first switching valve 43.
  • the distributor piston 21 has a rotational position such that the filling groove 35 covers the filling bore 38.
  • the first switching valve 43 is open when de-energized and the second switching valve 55 is also open when energized.
  • the delivery stroke of the pump piston 26 begins, the pump piston 26 becoming more inclined due to the sliding of the roller tappet 27 Flank of the cam track 17 moved radially inwards.
  • Fuel is pumped back into the pump interior 12 from the pump work chamber 32 via the relief line 50 and the still open first switching valve 43.
  • the first switching valve 43 is closed.
  • the distributor piston 21 has reached a rotational position at the latest in which the distributor groove 34 covers an injection bore 36 and thus connects the pump working chamber 32 to the associated injection nozzle 37 via the injection bore 36.
  • fuel is now Injection nozzle 37 promoted and passes there for injection into the cylinder of the internal combustion engine.
  • the first switching valve 43 is de-energized, as a result of which the opening switching valve 43 connects the pump working chamber 32 to the pump interior 12 via the annular groove 33 and the relief line 50.
  • the pressure in the pump work chamber 32 suddenly drops below the opening pressure of the injection nozzle 37, and the latter closes.
  • the first switching valve 43 closes and / or opens the amount of fuel delivered to the injector 37 and injected there is metered.
  • 1b shows the fuel injection pump for the case in which the first switching valve 43 is defective in such a way that its valve member 48 does not open the valve opening 47 for the electromagnet 49 despite the absence of the excitation current.
  • the first switching valve 43 getting stuck in the closed state.
  • the entire amount of fuel contained in the pump working chamber 32 reaches the injection via the injection nozzle 37 for each delivery stroke of the pump piston 26.
  • the speed of the internal combustion engine thereby increases continuously. This excessive increase in the speed of the internal combustion engine is recognized by the monitoring device 60 and this issues a closing command to the second switching valve 55. This closing command causes the excitation current for the electromagnet 58 of the second switching valve 55 to be switched off.
  • the second switching valve closes under the action of the valve closing spring 59 55.
  • the control chamber 44 in the distributor cylinder 22 is thus separated from the pump interior 12.
  • the pressure in the control chamber 44 increases and causes the distributor piston 21 to be displaced into the axial displacement position shown in FIG. 1b. In this displacement position, it projects in the pump work space 32 opening filling groove 35 freely into the pump work space 12, whereby the pump work space 32 is connected to the pump interior 12.
  • the fuel will now flow out of the pump working chamber 32 via the filling groove 35 into the pump interior 12, so that no pressure exceeding the opening pressure of the injection nozzle 37 can build up in the pump working chamber 32.
  • the second exemplary embodiment of a radial piston type distributor fuel injection pump shown in FIG. 2 differs from the fuel injection pump in FIG. 1 only in that the annular groove 33 delimiting the pump working space 32 on the distributor piston 21 is divided by an annular web 62 which has an outer diameter of the distributor piston 21 has the corresponding outer diameter.
  • the annular web 62 is placed within the annular groove 33 in such a way that in the axial displacement position shown in FIG Separates annular groove 33 from the right part of the annular groove 33 and thus from the pump working space 32.
  • the filling groove 35 opens into this now sealed part of the annular groove 33, in the axial displacement position of the distributor piston 21, the filling groove 35 is separated from the pump working chamber 32 in each of its rotational positions and thus the latter relative to the fuel-filled pump interior 12 cordoned off.
  • the axial length of the filling groove 35 is shorter here or the filling bore 38 is made further away from the pump interior end of the distributor cylinder 22, so that the filling groove is in the axial displacement position of the distributor piston (Fig. 2b) 35 is not released from the distributor cylinder 22 to the pump interior 12.
  • annular groove 33 itself can be made so narrow that it is covered by the through holes 25 in the distributor cylinder 22 in the normal operating position of the distributor piston 21 (FIG. 2a) and in the axial displacement position of the distributor piston 21 (FIG. 2b ) is covered in its full length by the inner wall of the distributor cylinder 22.
  • FIG. 3 of a radial piston type distributor fuel injection pump differs from the fuel injection pump in FIG. 1 in that in the relief line 50 there is provided a bypass 63 which bridges the first switching valve and is opened or closed by the distributor piston 21.
  • a first bypass section 64 is connected to the first bore section 51 of the relief line 50 and a second bypass section 65 is connected to the second bore section 52 of the relief line 50.
  • Each bypass section 64, 65 opens into the interior of the distributor cylinder 22.
  • the orifices are placed in such a way that they are closed by the distributor piston 21 in the normal operating position of the distributor piston 21 (FIG. 3a) and in which the first switching valve 43 is defective by the distributor piston 21 assumed axial displacement position (Fig.
  • the exemplary embodiment of a distributor fuel injection pump of the radial piston type shown in FIG. 4 is modified somewhat more than the exemplary embodiments in FIGS. 2 and 3 compared to the fuel injection pump in FIG. 1.
  • the pressure line 20 leading away from the feed pump 18 is directly connected to the pump interior 12.
  • the control chamber 44 in the distributor cylinder 22 is connected to the pump interior 12 via an inlet line 66 and connected via an outlet line 67 with the interposition of a throttle 68 to a drain opening 69 provided in the cover 11, which in turn is connected to the fuel tank via a fuel return line.
  • the second switching valve 55 is arranged in the inlet line 66.
  • the connection of the drive shaft 15 and the distributor piston 21 is made such that the end face 70 of the distributor piston 21 projecting into the pump interior 12 is acted upon by the fuel pressure prevailing in the pump interior 12.
  • the first switching valve 43 remains stuck in its closed position, then, as with the fuel injection pump in FIG Monitoring device 60 controls the second switching valve 55. This closes so that no more fuel can flow into the control chamber 44 from the pump interior 12 via the feed line 66. Only the connection of the control room 44 via the drain line 67 to the drain opening 69 remains. The pressure acting on the end face 70 of the distributor piston 21 is now opposed to no counter pressure in the control chamber 44, as a result of which the distributor piston 21 is displaced to the right in FIG. 4a and assumes its axial displacement position shown in FIG. 4b.
  • the filling groove 35 is shifted to the right so far that it is no longer able to cover the filling bore 38 in the distributor cylinder 22 (FIG. 4b).
  • the pump working space 32 is thus separated from the pump interior 12 and can no longer be filled with fuel during the suction stroke of the pump piston 26. If the first switching valve 43 is defective, the fuel delivery to the injection nozzle 37 is interrupted.
  • FIGS. 2-4 differ from the fuel injection pump in FIG. 1 only in the modifications highlighted above. Otherwise, the structure and mode of operation are the same, so that the same reference numerals have been used for the same components. For the sake of clarity, the reference numerals in FIGS. 2-4 are only entered to the extent necessary to understand the deviations from FIG. 1.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

Une pompe d'injection de carburant à distributeur comprend au moins un piston radial (26) effectuant une course d'aspiration et une course de refoulement, un piston distributeur rotatif (18) reliant des injecteurs (37) à la chambre de travail (32) de la pompe délimitée par le piston (26) et une soupape électrique de commutation (43) qui commande la quantité de carburant injecté et est en communication avec la chambre de travail (32) de la pompe et avec une chambre intérieure (12) de la pompe remplie de carburant. Afin d'assurer l'arrêt d'urgence du moteur lors d'un mauvais fonctionnement de la soupape de commutation (43), le piston distributeur (21) est axialement mobile de façon à arrêter lorsqu'il est dans une certaine position de déplacement axial le transport de carburant jusqu'aux injecteurs (37). Le piston distributeur (21) délimite avec une de ses faces frontales (71) une chambre de commande (44) connectée à une deuxième soupape électrique de commutation (55). Lorsque la deuxième soupape de commutation (55) est fermée, une supression ou une dépression par rapport à la chambre intérieure (12) de la pompe est générée et entraîne le piston distributeur (21) jusqu'à sa position axiale de déplacement.

Claims (12)

1. Pompe d'injection de carburant, du type à pistons radiaux comportant un volume intérieur de pompe (12) entouré par un carter de pompe (10) et rempli de carburant fourni par une pompe d'alimentation, d'un entraînement par cames (16, 27) couplé à un axe d'entraînement (15) et dont chaque rotation assure l'entraînement d'au moins un piston de pompe (26) délimitant une chambre de travail (32) pour exécuter une course d'aspiration et de transfert au cours d'un mouvement alternatif, radial par rapport à l'axe d'entraînement (15), et au cours de la course d'aspiration, la chambre de travail (32) de la pompe est remplie de carburant et au moment de la course de transfert, le carburant passe de la chambre de travail (32) de la pompe dans un injecteur correspondant, un piston distributeur (21) fermé d'un côté, guidé coaxialement au cylindre distributeur (22) par rapport à l'axe d'entraînement (15) et qui comprend dans sa face frontale une chambre de commande (44), piston qui est déplacé axialement contre la force développée par un ressort (41), d'une position de sortie déterminée par la venue contre une butée, par une pression commandée à partir de la chambre de commande (44) à travers une soupape de commande (55), et dont l'extrémité qui est en saillie par rapport au cylindre distributeur (22) et vient dans le volume intérieur (12) de la pompe est couplée à l'axe d'entraînement (15) en coopérant par des canaux (34, 35) avec les perçages (36, 38) du cylindre distributeur (22), et dans au moins une première position de rotation, la chambre de travail (32) de la pompe est reliée au volume intérieur de la pompe et dans au moins une seconde position de rotation la communication est établie avec l'injecteur et pour une certaine position de translation axiale, la liaison se fait par une conduite de décharge (35, 38, 50, 64, 65, 52) vers le volume intérieur (12), pompe caractérisée en ce que la durée de transfert et ainsi la quantité de carburant injectée sont commandées par une première soupape de commutation (43) à commande électrique, qui relie d'une part le volume de travail (32) de la pompe et d'autre part une chambre de décharge notamment le volume intérieur (12) de la pompe et dont la fermeture définit le début du transfert et l'ouverture de la fin du transfert et en ce que la chambre de commande (44) est reliée par une conduite de pression (53, 66) au côté de pression de la pompe de transfert (18) et par une conduite de pression (54, 67) à une chambre de décharge, la liaison par l'une des conduites de pression (53, 66) existant en permanence et la liaison par l'autre conduite de pression (54, 67) étant susceptible d'être interrompue par la soupape de commande en forme de seconde soupape de commutation (55) électrique, lorsque la pompe d'injection de distribution de carburant dépasse la vitesse de rotation maximale ou en présence d'un défaut de la première soupape de commutation à commande électrique (43), pour que le piston distributeur (21) puisse être conduit dans la position de translation axiale en modifiant les forces auxquelles il est soumis à partir de sa position de sortie, cette position établissant la liaison entre la chambre de travail (32) de la pompe et le volume intérieur (12) de la pompe.
2. Pompe d'injection de carburant, du type à pistons radiaux, caractérisée en ce que la durée de transfert et ainsi la quantité de carburant injectée sont commandées par une première soupape de commutation (43) à commande électrique qui est d'une part reliée à la chambre de travail (32) de la pompe et d'autre part à une chambre de décharge notamment le volume intérieur (12) de la pompe et en ce que par fermeture, elle définit le début du transfert et par ouverture, la fin du transfert et en ce que la chambre de commande (44) est reliée par une conduite de pression (53, 66) au côté de pression de la pompe de transfert (18) et par une conduite de pression (54, 67) à la chambre de décharge, la liaison existant en permanence par l'intermédiaire de l'une des conduites de pression (53, 66) et la liaison par l'autre conduite de pression (54, 67) se faisant par l'autre soupape de commande en forme de soupape de commutation (55) à commande électrique, en ce que lors du dépassement de la vitesse de rotation maximale de la pompe d'injection de distribution de carburant ou en cas de défaut de la première soupape de commutation à commande électrique, cette liaison est interrompue et ce que le piston distributeur (21) peut être mis dans la position de translation axiale à partir de sa position de sortie, par modification des efforts agissant sur ce piston et en ce que dans cette position de translation la liaison entre la chambre de travail (32) de la pompe et le volume intérieur (12) de la pompe est coupée notamment à la première position de rotation du piston distributeur (figures 2 et 4).
3. Pompe selon la revendication 1 ou 2, caractérisée en ce que la conduite d'alimentation (20) qui relie la pompe d'alimentation (18) et le volume intérieur de la pompe passe par la chambre de commande (44) et ce que la seconde soupape de commutation (55) est prévue dans le segment de conduite (54) reliant la chambre de commande (44) et le volume intérieur (12) de la pompe, segment qui est muni d'un orifice d'évacuation (13) comportant un organe d'étranglement (14).
4. Pompe selon la revendication 3, caractérisée en ce que le cylindre distributeur (22) comporte un perçage (61) débouchant à l'intérieur de celui-ci et débouchant par ailleurs dans le volume intérieur (12) de la pompe, perçage dont l'embouchure est prévue à l'intérieur du cylindre distributeur (22) pour être recouverte par le piston distributeur (21) et n'être libérée vers la chambre (44) que lorsque le piston distributeur (21) occupe la position de translation axiale.
5. Pompe selon les revendications 1 et 3 ou 4, caractérisée en ce que le piston distributeur (21) comporte à sa périphérie une rainure annulaire (33) qui délimite avec le piston de pompe (26) la chambre de travail (32) de la pompe, rainure qui recouvre par une rainure de remplissage axiale (35) du piston distributeur (21) lorsque celui-ci occupe sa première position de rotation, un perçage de remplissage (38) prévu à l'intérieur du cylindre distributeur (22) et débouchant dans le volume intérieur (12) de la pompe, et en ce que la longueur axiale de la rainure de remplissage (35) est telle que dans la position de translation axiale du piston distributeur (21), elle passe du cylindre distributeur (22) jusque dans le volume intérieur (12) de la pompe (figure 1).
6. Pompe selon les revendications 2 et 3 ou 4, caractérisée en ce que le piston distributeur (21) porte à sa périphérie une rainure annulaire (33) qui délimite la chambre de travail (32) de la pompe avec le piston de pompe (26), cette rainure recouvrant par une rainure de remplissage axiale (35) du piston distributeur (21) dans la première position de rotation de celui-ci, un perçage de remplissage (38) débouchant à l'intérieur du cylindre distributeur (22) et dans le volume intérieur (12) de la pompe et en ce que la rainure annulaire (33) est subdivisée par une plage annulaire (62) de diamètre extérieur correspondant au diamètre extérieur du piston distributeur (21), cette plage étant prévue pour que dans la position de translation axiale du piston distributeur (21) elle bloque la partie de la rainure annulaire (33) reliée à la rainure de remplissage (35) avec la paroi intérieure du cylindre distributeur (21) par rapport à l'autre partie de la rainure annulaire (33) (figure 2).
7. Pompe selon la revendication 1, caractérisée en ce que le piston distributeur (21) comporte à sa périphérie une rainure annulaire (33) qui délimite la chambre de travail (32) de la pompe avec le piston de pompe (26), cette rainure recouvrant par une rainure de remplissage axiale (35) du piston distributeur (21) lorsque celui-ci occupe sa première position de rotation, un perçage de remplissage (38) débouchant à l'intérieur du cylindre distributeur (22) et dans le volume intérieur (12) de la pompe et en ce que sa longueur axiale est telle que dans la position de translation axiale du piston distributeur (21) elle soit recouverte par la paroi intérieure du cylindre distributeur (22) entre le perçage de remplissage (38) et la chambre de travail de pompe.
8. Pompe selon la revendication 1, caractérisée en ce qu'à l'intérieur du cylindre distributeur (22), il est prévu un premier segment de dérivation (64) entre la chambre de travail (32) de la pompe et la première soupape de commutation (43) et en ce qu'un second segment de dérivation (65) d'une dérivation (63) est prévu entre la première soupape de commutation (43) et le volume intérieur (12) de la pompe, pour déboucher au niveau de la première soupape de commutation (43) en ce que les embouchures sont telles que la dérivation (63) soit bloquée lorsque le piston distributeur (21) occupe la position normale et que dans la position de translation axiale du piston distributeur (21), elle soit fermée par la chambre de commande (44) (figure 3).
9. Pompe selon la revendication 2, caractérisée par une conduite de pression (66) qui relie la chambre de commande (44) directement au volume intérieur (12) de la pompe, par le côté de pression de la pompe de transfert et en ce que l'autre conduite de pression (67) est reliée à un orifice d'évacuation (69) du carter de pompe (10, 11) muni d'un organe d'étranglement (68) et la seconde soupape de commutation (55) est prévue dans l'une des conduites de pression (66) et la surface frontale (70) de l'extrémité du piston distributeur (21) reliée à l'axe d'entraînement (15) est soumise à la pression régnant dans le volume intérieur (12) de la pompe.
10. Pompe selon la revendication 9, caractérisée en ce que le piston distributeur (21) porte à sa périphérie une rainure annulaire (33) qui délimite la chambre de travail (32) de la pompe en combinaison avec le piston de pompe (26), cette rainure recouvrant par une rainure de remplissage axiale (35) du piston distributeur (21) dans sa première position de rotation, un perçage de remplissage (38) débouchant à l'intérieur du cylindre distributeur (22) et du volume intérieur (12) de la pompe et en ce que la longueur axiale de la rainure de remplissage (35) est telle qu'en position de fermeture axiale du piston distributeur (21), elle soit éloignée de la zone d'embouchure du perçage de remplissage (38) du cylindre distributeur (22) (figure 4).
11. Pompe selon l'une des revendications 1 à 10, caractérisée par un dispositif (60) pour surveiller le fonctionnement de la première soupape de commutation (43), dispositif qui fournit un ordre de fermeture à la seconde soupape de commutation (55) lorsque l'organe (48) de la première soupape de commutation (43) reste en position de fermeture malgré la disparition du signal de commande.
12. Pompe selon l'une des revendications 1 à 11, caractérisée en ce que la seconde soupape de commutation (55) est telle qu'elle est fermée en position de base non excitée et qu'elle s'ouvre en position de travail, excitée.
EP19880904479 1987-06-13 1988-05-28 Pompe d'injection a distributeur du type a pistons radiaux Expired - Lifetime EP0318534B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873719807 DE3719807A1 (de) 1987-06-13 1987-06-13 Verteilerkraftstoffeinspritzpumpe der radialkolbenbauart
DE3719807 1987-06-13

Publications (2)

Publication Number Publication Date
EP0318534A1 EP0318534A1 (fr) 1989-06-07
EP0318534B1 true EP0318534B1 (fr) 1991-07-10

Family

ID=6329656

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880904479 Expired - Lifetime EP0318534B1 (fr) 1987-06-13 1988-05-28 Pompe d'injection a distributeur du type a pistons radiaux

Country Status (5)

Country Link
US (1) US4971012A (fr)
EP (1) EP0318534B1 (fr)
JP (1) JP2604841B2 (fr)
DE (2) DE3719807A1 (fr)
WO (1) WO1988009870A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3900318A1 (de) * 1989-01-07 1990-07-12 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe fuer brennkraftmaschinen
GB8918429D0 (en) * 1989-08-12 1989-09-20 Lucas Ind Plc Fuel pumping apparatus
DE3927742A1 (de) * 1989-08-23 1991-02-28 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4032279A1 (de) * 1990-10-11 1992-04-16 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5103792A (en) * 1990-10-16 1992-04-14 Stanadyne Automotive Corp. Processor based fuel injection control system
US5215060A (en) * 1991-07-16 1993-06-01 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
DE4135595A1 (de) * 1991-10-29 1993-05-06 Robert Bosch Gmbh, 7000 Stuttgart, De Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5215449A (en) * 1991-12-05 1993-06-01 Stanadyne Automotive Corp. Distributor type fuel injection pump
EP0596054B1 (fr) * 1992-04-25 1996-03-13 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
DE4243665C2 (de) * 1992-12-23 2003-11-13 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung, insbesondere Pumpedüse für Brennkraftmaschinen
FR2856007B1 (fr) * 2003-06-11 2005-08-26 Essilor Int Vanne et dispositif d'alimentation convenant au remplissage, avec une matiere polymerisable, d'une cavite de moulage

Citations (1)

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Publication number Priority date Publication date Assignee Title
DE3523536A1 (de) * 1984-09-14 1986-03-27 Robert Bosch Gmbh, 7000 Stuttgart Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Family Cites Families (5)

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Publication number Priority date Publication date Assignee Title
US3485225A (en) * 1968-04-15 1969-12-23 Caterpillar Tractor Co Rotary distributor fuel pump
GB2108727B (en) * 1980-10-29 1985-02-06 Lucas Industries Ltd Fuel injection pumping apparatus
DE3243348A1 (de) * 1982-11-24 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
DE3612942A1 (de) * 1986-04-17 1987-10-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3719831A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3523536A1 (de) * 1984-09-14 1986-03-27 Robert Bosch Gmbh, 7000 Stuttgart Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Also Published As

Publication number Publication date
JPH02500206A (ja) 1990-01-25
EP0318534A1 (fr) 1989-06-07
US4971012A (en) 1990-11-20
WO1988009870A1 (fr) 1988-12-15
DE3863630D1 (de) 1991-08-14
JP2604841B2 (ja) 1997-04-30
DE3719807A1 (de) 1988-12-22

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