EP0295420B1 - Pompe d'injection de combustible - Google Patents

Pompe d'injection de combustible Download PDF

Info

Publication number
EP0295420B1
EP0295420B1 EP19880107454 EP88107454A EP0295420B1 EP 0295420 B1 EP0295420 B1 EP 0295420B1 EP 19880107454 EP19880107454 EP 19880107454 EP 88107454 A EP88107454 A EP 88107454A EP 0295420 B1 EP0295420 B1 EP 0295420B1
Authority
EP
European Patent Office
Prior art keywords
valve
pump
bore
space
piston
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
EP19880107454
Other languages
German (de)
English (en)
Other versions
EP0295420A2 (fr
EP0295420A3 (en
Inventor
André Brunel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0295420A2 publication Critical patent/EP0295420A2/fr
Publication of EP0295420A3 publication Critical patent/EP0295420A3/de
Application granted granted Critical
Publication of EP0295420B1 publication Critical patent/EP0295420B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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 fuel injection pump for internal combustion engines of the type defined in the preamble of claim 1.
  • a known fuel injection pump of this type which is designed as a so-called pump nozzle (DE-OS 35 23 536)
  • the inlet line opening into the pump work chamber with an inlet opening is separated from the pump work chamber as a result of the pump piston closing the inlet inlet opening.
  • the time at which the inlet opening is closed is structurally determined and determined by the distance of the inlet opening from the bottom dead center position of the pump piston.
  • the pump work space is delimited by an annular groove on the rotating distributor piston, which is connected to filling grooves which are arranged distributed around the circumference of the distributor piston and can be connected to fill bores in the distributor cylinder when the distributor piston rotates.
  • the filling bores open into the fuel-filled pump interior and connect this to the pump work space when the filling grooves are in register with the openings of the filling bores in the distributor cylinder.
  • the pump working space 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 opens, the pump work chamber is connected to the relief chamber and the fuel injection is suddenly stopped. If the switching valve is defective in such a way that it gets stuck in its closed position and no longer opens, 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 fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that in the event of the sticking of the Switching valve in its closed position the fuel supply to the pump work space is automatically prevented. This means that no fuel can be pumped from the pump workspace to the injection nozzles, and the internal combustion engine comes to a standstill because of a missing ignition mixture.
  • the radial piston-type distributor fuel injection pump shown in detail in longitudinal section in FIG. 1 has a cup-shaped housing 10, which is only indicated in FIG. 1, and a cover 11 which closes the latter and is pushed in from the open end of the housing 10 and with a bottom of the housing 10, not shown limited a pump interior 12.
  • the pump interior 12 is filled with fuel under low pressure and serves as a fuel supply and relief space.
  • a drive shaft 13, which is indicated in FIG. 1 by its axis, is passed through the bottom of the housing 10. In the pump interior 12, this drive shaft 13 expands in a pot shape and carries along its edge a cam ring connected to it in a rotationally fixed manner, the cam track 15 provided on its inside being indicated schematically in FIG. 1 and rotated by 90 °.
  • the cam track 15 carries in a known manner inwardly directed cams, the number and sequence of the number and sequence of radial pistons contained in the fuel injection pump and the The number of piston strokes to be carried out with these radial pistons per revolution of the drive shaft 13 are adapted.
  • the feed pump (not shown), which fills the pump interior 12 with fuel, sits on the drive shaft 13 in a conventional manner.
  • a distributor piston 16 is also connected in a rotationally fixed manner to the drive shaft 13, the axis of which is aligned with the axis of the drive shaft 13.
  • the distributor piston 16 is guided except for the end connected to the drive shaft 13 in a cylinder bore 17 in the cover 11 and is fixed in its axial position relative to the cylinder bore 17.
  • guides 18 are provided in the cover, which are evenly distributed over the circumference and extend close to the distributor piston 16.
  • Radial bores 19 are provided coaxially with the guides 18, in each of which a pump piston 20 is guided so as to be longitudinally displaceable.
  • a so-called roller plunger 21 is guided in a longitudinally displaceable manner, which consists of a roller or roller 22 and a plunger cup 23.
  • the roller 22 is shown in Fig. 1 as well as the cam track 15 rotated by 90 °.
  • the spring plate 14 engages behind a collar projecting out of the radial bore 19 20a of the pump piston 20 and thus fixes the latter to the tappet cup 23.
  • Each pump piston 20 delimits a pump chamber 25 in the radial bore 19, the other end face of which is formed by an annular groove 26 on the distributor piston 16.
  • a distributor groove 27 opens axially on the distributor piston 16.
  • three injection bores 28 open in a cross-sectional plane, which are evenly distributed over the circumference of the cylinder bore 17 and through the cover 11 up to one each through one Guide arrow indicated injector 29.
  • the axial length of the distributor groove 27 is dimensioned such that it projects into the cross-sectional plane of the mouths of the injection bores 28 and thus connects one of the three injection bores 28 with the annular groove 26 depending on the rotational position of the distributor piston 16.
  • the working chamber 25 is filled with fuel from the pump interior 12 during the suction stroke of the pump piston 20 via an inlet line 30 running in the cover 11, which comprises a first bore section 31 running axially to the distributor piston 16 and a second bore section 32 running radially to the distributor piston 16.
  • the first bore section 31 opens in the pump interior 12 and the second bore section 32 in the cylinder bore 17 in the region of the annular groove 26 of the distributor piston 16.
  • Both bore sections 31, 32 are connected to one another via a valve bore 34, which is coaxial to the first bore section 31 with a larger bore diameter is introduced into the lid 11.
  • the mouth of the first bore section 31 in the valve bore 34 forms a valve opening 35 of a check valve 33 arranged in the inlet line 30, the opening direction of which is directed towards the pump working chamber 25.
  • the shut-off valve 33 shown enlarged in FIG. 2 is designed as a seat valve, one in the valve bore 34 has displaceably inserted valve lifter 36.
  • the valve tappet 36 carries on its end facing the valve opening 35 a conical valve member 37 which cooperates with a valve seat 38 surrounding the valve opening 35 to close and open the valve opening 35.
  • the end face of the valve tappet 36 facing away from the valve member 37 delimits a control and spring chamber 39 in which a valve closing spring 40 designed as a helical compression spring lies, which is supported on the one hand on the end face of the valve tappet 36 and on the other hand at the base of the valve bore 34 and the valve tappet 36 in the valve closing direction charged.
  • the control and spring chamber 39 is connected to a relief line 42 via a bore section 41.
  • the relief line 42 which is divided into two bore sections 50, 51 and extends in the cover 11, opens on the one hand in the pump interior 12 and on the other hand in the cylinder bore 17, specifically in the area of the annular groove 26 on the distributor piston 16.
  • An electromagnetic switching valve 43 is switched on in the relief line 42 , via which the relief line 42 is blocked and thus the pump work space 25 is closed or the relief line 42 is released and thus the pump work space 25 can be connected to the pump interior 12 serving as a relief space.
  • the structure and mode of operation of the electromagnetic switching valve 43 is known and is described, for example, in DE-OS 35 23 536.
  • the two valve connections 44, 45 of the switching valve 43 are connected to one another via a valve opening 46, which is controlled by a valve member 47.
  • the valve member 47 is actuated by an electromagnet 48, the valve member 47 opening the valve opening 46 in the non-energized state of the electromagnet 48 under the action of a return spring (not shown) and closing the electromagnet 48 in the energized state.
  • Switch valve 43 having a separate valve housing 49 is placed on the cover 11 and fastened there in a suitable manner, wherein it closes the cylinder bore 17.
  • the valve connection 44 covers an end opening of the first bore section 50 of the relief line 42, while the second valve connection 45 coincides with an end opening of the second bore section 51 of the relief line 42.
  • the mouth of the relief line 42 in the pump interior 12 is closed with a check valve 52, which is integrated in the second bore section 51 of the relief line 42, namely between the mouth of the relief line 42 in the pump interior 12 and the mouth of the control chamber 39 of the check valve 33 with the Bore section 41 connecting relief line 42 in relief line 42.
  • the corresponding pump piston 20 in FIG. 1 is moved outwards on the falling flank of the cam track 15 rotating with the drive shaft 13, on which the roller tappet 21 bears.
  • the switching valve 43 is not energized and is therefore open.
  • This suction stroke of the pump piston 20 takes place in the area between top dead center (point 1 in FIG. 3) and bottom dead center (point 3 in FIG. 3).
  • the suction or suction pressure that occurs in this pump stroke in the pump work chamber 25 causes the valve member 37 to be lifted off the valve seat 38 against the action of the valve closing spring 40 and thus opens the check valve 33.
  • the switching valve 43 is still open, so that fuel flows back into the pump working chamber 12 from the pump interior 25 via the relief line 42 and the check valve 52.
  • the distributor groove 27 connects the pump interior 25 with an associated injection bore 28.
  • the switching valve 43 is actuated and this closes. Fuel is now conveyed via the injection bore 28 to the injection nozzle 29 and arrives there for injection into the cylinder of the internal combustion engine.
  • the control of the switching valve 43 is canceled so that it opens again.
  • the pump working chamber 25 is thus placed via the relief line 42 and the check valve 52 on the pump interior 12 which acts as a relief chamber.
  • the pressure in the pump working chamber 25 thus suddenly drops below the opening pressure of the injection nozzle 29, and this closes.
  • the fuel injection has ended.
  • the fuel injection is stopped, so that the internal combustion engine comes to a standstill due to a lack of fuel supply.
  • the switching valve 43 remains in its open position despite being actuated, the pump work chamber 25 is constantly connected to the pump interior 12. No pressure overcoming the opening pressure of the injector 29 can build up in the pump work chamber 25. The injector 29 remains closed at all times. If the valve member 47 of the switching valve 43 remains stuck in its closed position so that the switching valve 43 no longer opens despite the absence of the excitation current, the fuel-filled control chamber 39 is blocked by the closed switching valve 43 and blocks the opening movement of the valve tappet which usually occurs during the suction stroke of the pump piston 20 36 of the check valve 33.
  • the check valve 33 can no longer open and the pump working space 25 is no longer filled with fuel. As a result, even during the subsequent delivery stroke of the pump piston 20, fuel no longer reaches the injection nozzle 29 via the distributor groove 27 and the injection bore 28. In this case too, the internal combustion engine comes to a standstill due to a lack of fuel.
  • the check valve 33 thus brings about an automatic emergency stop of the internal combustion engine in the event of a fault in the electromagnetic switching valve 43.
  • valve tappet 36 with the valve member 37 is designed such that no force components greater than the spring force of the valve closing spring 40 arise on the surfaces of the valve tappet 36 and valve member 37 which are acted upon by the pressure in the pump working chamber 25 during the delivery stroke of the pump piston 20 so that Lock valve 33 remains securely closed during the delivery stroke of the pump piston 20.
  • valve member 37 and the valve tappet 36 which are acted upon by the fuel pressure in the pump interior 12 and by the suction pressure in the pump work chamber 25 during the suction stroke of the pump piston 20 are matched with the force of the valve closing spring 40 in such a way that the check valve 33 is secure when the suction stroke of the pump piston 20 begins opens and remains open throughout the suction stroke.
  • a check valve 53 is arranged in the second radial bore section 32 of the inlet line 30 between the valve bore 34 and the annular groove 26 in the distributor piston 26, the opening direction of which is directed towards the pump working chamber 25.
  • This check valve 53 results in a simplified design of the check valve 33, since the delivery pressure in the pump work chamber 25 no longer has to be taken into account in the formation of the areas of the valve member 37 which are acted upon by pressure.
  • the shutoff valve 233 is designed as a slide valve, a valve piston 54 sliding in the valve bore 34, which in the same way as the valve tappet in FIGS. 1 and 2 has a valve closing spring 40 is burdened.
  • the valve piston 54 divides the valve bore 34 into a front valve chamber 55, in which the first bore section 31 of the inlet line 30 opens, and into a rear valve chamber, which forms the control and spring chamber 39 and which, as in FIGS. 1 and 2, via the bore section 41 is connected to the relief line 42.
  • the second radial bore section 32 of the feed line 30 opens into an annular groove 56 provided approximately centrally in the valve bore 34.
  • valve piston 5 closes the annular groove 56 with its piston surface in the blocking position of the blocking valve 33 shown in FIG. 5 and partially frees it after covering a predetermined displacement path against the force of the valve closing spring 40, so that now the first bore section 31 of the inlet line 30 via the valve chamber 55 is connected to the second bore section 32 of the feed line 30.
  • the further exemplary embodiment of a distributor fuel injection pump of the radial piston type shown schematically in longitudinal section in FIG. 6 differs from the fuel injection pump shown in FIG. 1 only in that the check valve 33 is integrated in the distributor piston 16.
  • the distributor piston 16 has a blind bore 57, into which a sleeve 58 provided with an internal step bore 59 is inserted.
  • the larger diameter bore section 60 of the inner step bore 59 adjoins the bottom of the blind bore 57 and is connected to the annular groove 26 on the distributor piston 16 via a bore 62 radially penetrating the sleeve 58 and the distributor piston 16.
  • the second bore section 60 is connected via an oblique bore 63 opening at the bottom of the blind bore 57 to a further annular groove 64, which is arranged on the distributor piston 16 at a distance from the annular groove 26 delimiting the pump working space 25.
  • a branch bore 65 leading to the second bore section 32 of the feed line 30 opens into the cylinder bore 17.
  • the valve tappet 36 is axially displaceable in the first bore section 60 from the stop valve 33, which is again designed as a seat valve and is identical to that in FIG. 1 a.
  • the transition stage between the two bore sections 60, 61 is designed as a valve seat 38, which is carried by the valve tappet 36 conical valve member 37 cooperates.
  • valve tappet 36 facing away from the valve member 37 in turn delimits the control and spring chamber 39, in which the valve closing spring 40 lies and which is continuously connected to the relief line 42 via the oblique bore 63, the annular groove 64 and the branch bore 65.
  • the smaller-diameter bore section 61 of the inner step bore 59 is connected to the pump interior 12 and, together with the bore 62, forms the feed line 30.
  • the invention is not limited to the exemplary embodiments of a distributor fuel injection pump with radial pistons described above. It can be used in the same way in distributor fuel injection pumps with axial pistons, as described in DE-OS 35 11 492, or in fuel injection pumps designed as so-called pump nozzles, as described in DE-OS 29 03 482.

Claims (9)

  1. Pompe d'injection de carburant pour moteurs à combustion interne, comportant au moins un piston de pompe (20) délimitant une chambre de travail de la pompe (25), et qui est déplacé par une commande par came (15) pour effectuer une course d'aspiration et de refoulement en un mouvement de va et vient, dans lequel, pendant la course d'aspiration, l'espace de travail de la pompe se remplit de carburant par un conduit d'amenée (30) à partir d'un espace de réserve de carburant, en particulier un espace intérieur de la pompe (12) et pendant la course de refoulement le carburant est envoyé de l'espace de travail de la pompe (25) à un injecteur à raccorder, et comportant une soupape de commande (43) électrique commandant la durée de refoulement, placée sur un conduit de décharge (42) conduisant de l'espace de travail de la pompe (25) à un espace de décharge en particulier une chambre intérieure de pompe (12) et établit par sa fermeture le début du refoulement et par son ouverture la fin du refoulement, caractérisée
    - en ce que le conduit d'amenée (30) est séparé du conduit de décharge (42),
    - en ce que dans le conduit d'amenée (30) entre l'espace de réserve de carburant, de préférence la chambre intérieure de la pompe (12) et la chambre de travail de la pompe (25) est disposée une soupape d'arrêt (33, 133; 233) avec un sens d'ouverture dirigé vers la chambre de travail de la pompe (25), soupape qui comporte un ressort de fermeture de la soupape (40) exerçant une charge sur la partie de soupape (37) dans le sens de fermeture et un espace de commande (39) rempli de carburant par l'intermédiaire duquel la partie de soupape (37) peut être maintenue dans sa position de fermeture, et
    - en ce que l'espace de commande (39) est relié au tronçon (32) du conduit de décharge (30) se situant entre la soupape de commande (43) et l'espace de décharge, de préférence la chambre intérieure de pompe (12) et le conduit de décharge (30) est isolé par une soupape anti-retour (52) par rapport à l'espace de décharge, de préférence la chambre intérieure de pompe (12), soupape dont le sens d'ouverture est dirigé vers l'espace de décharge, de préférence la chambre intérieure de pompe (12).
  2. Pompe selon la revendication 1, caractérisée
    - en ce que les surfaces de la partie de soupape (37) sollicitées par la pression du carburant et le ressort de fermeture de soupape (40) sont accordés l'un à l'autre de façon que la soupape d'arrêt (33, 133, 233) s'ouvre pour la course d'aspiration du piston de pompe (20) et se ferme pour la course de refoulement du piston de pompe (20).
  3. Pompe selon la revendication 1 ou la revendication 2, caractérisée
    - en ce que la soupape d'arrêt (33, 133) est réalisée en soupape à siège avec un poussoir de soupape (36) coulissant dans un alésage de soupape (34) et qui porte sur une de ses faces frontales, la partie de soupape (37) de forme conique ou sphérique agissant de concert avec un siège de soupape (38) entourant une ouverture de soupape (35) dans le conduit d'amenée (30), et qui délimite avec sa face frontale éloignée de la première, un tronçon de l'alésage de soupape (34) constituant l'espace de commande (39),
    - en ce que le ressort de fermeture de soupape (40) est logé dans l'espace de commande (39), et
    - en ce que l'espace de commande (39) est relié au conduit de décharge (42) par un alésage de liaison (41, 63, 64, 65).
  4. Pompe selon la revendication 3, caractérisée
    - en ce que la surface de la partie de soupape (37) de la soupape d'arrêt (33), influencée par la pression dans l'espace de travail de la pompe (25) pendant la course de refoulement du piston de pompe (20) est réalisée de façon que l'ouverture de la soupape (35) reste fermée de façon sûre, même avec la pression d'injection régnant dans la chambre de travail de la pompe (25).
  5. Pompe selon la revendication 3, caractérisée
    - en ce qu'une soupape anti-retour (53) est mise en place avec un sens d'ouverture dirigé vers la chambre de travail de la pompe (25), dans un tronçon de conduit (32) du conduit d'amenée (30), se situant entre l'ouverture de soupape (35) de la soupape d'arrêt (133) et la chambre de travail de la pompe (25).
  6. Pompe selon la revendication 1 ou la revendication 2, caractérisée
    - en ce que la soupape d'arrêt (233) est réalisée en soupape à coulisse comportant un piston de soupape (54) pouvant coulisser axialement dans un alésage de soupape (34), et qui sépare ou relie entre eux un premier tronçon de conduit (31) débouchant dans l'alésage de soupape (34), conduisant vers l'espace de réserve de carburant, de préférence la chambre intérieure de pompe (12), et un deuxième tronçon de conduit (32) débouchant dans l'alésage de soupape (34), conduisant à la chambre de travail de la pompe (25),
    - en ce que l'une des parois frontales du piston de pompe (54) délimite un tronçon de conduite (55), dans lequel débouche le premier tronçon de conduit (31), et
    - en ce que l'autre paroi frontale du piston de soupape (54) délimite un tronçon d'alésage constituant l'espace de commande (39), qui est relié par un alésage de liaison (41) avec le conduit de décharge (42).
  7. Pompe selon l'une quelconque des revendications 1 à 6, caractérisée
    - en ce que la soupape d'arrêt (33; 133; 233) est placée dans le carter de pompe.
  8. Pompe selon l'une quelconque des revendications 1 à 6, avec un piston distributeur tournant pour alimenter un certain nombre d'injecteurs, caractérisée
    - en ce que la soupape d'arrêt (33) est intégrée dans le piston distributeur.
  9. Pompe selon la revendication 8, caractérisée
    - en ce que dans le piston distributeur (16) est prévu un alésage borgne à gradins (57, 58, 59),
    - en ce que le poussoir de soupape (36), ou piston de soupape, de la soupape d'arrêt (33) est inséré en pouvant coulisser axialement dans le tronçon d'alésage (60) arrière de plus grand diamètre se situant dans l'alésage borgne et s'appuie contre le fond de l'alésage borgne par l'intermédiaire du ressort de fermeture (40),
    - en ce que la partie du tronçon d'alésage arrière (60) délimitée par la surface frontale du poussoir de soupape (36) ou piston de soupape tournée vers le fond de l'alésage borgne, est reliée par un alésage (63) à une rainure annulaire (64) sur l'enveloppe du piston distributeur (16), qui se trouve en liaison avec un alésage (65) conduisant au conduit de décharge (41), et
    - en ce que la partie du tronçon d'alésage arrière (60) délimitée par la surface frontale du poussoir de soupape (36) ou piston de soupape, éloignée du fond de l'alésage borgne, est reliée par un alésage (62) à la chambre de travail de la pompe (25), partie qui constitue, de concert avec le tronçon d'alésage avant (61) de l'alésage borgne (57, 58, 59) comportant le plus petit diamètre, le conduit d'amenée (30).
EP19880107454 1987-06-13 1988-05-10 Pompe d'injection de combustible Expired - Lifetime EP0295420B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3719831 1987-06-13
DE19873719831 DE3719831A1 (de) 1987-06-13 1987-06-13 Kraftstoffeinspritzpumpe

Publications (3)

Publication Number Publication Date
EP0295420A2 EP0295420A2 (fr) 1988-12-21
EP0295420A3 EP0295420A3 (en) 1990-05-02
EP0295420B1 true EP0295420B1 (fr) 1991-11-13

Family

ID=6329672

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19880107454 Expired - Lifetime EP0295420B1 (fr) 1987-06-13 1988-05-10 Pompe d'injection de combustible

Country Status (6)

Country Link
US (1) US4840162A (fr)
EP (1) EP0295420B1 (fr)
JP (1) JP2695842B2 (fr)
KR (1) KR950003755B1 (fr)
CN (1) CN1013892B (fr)
DE (2) DE3719831A1 (fr)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3719807A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe der radialkolbenbauart
DE3719832A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE3722265A1 (de) * 1987-07-06 1989-01-19 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE3900318A1 (de) * 1989-01-07 1990-07-12 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3910793C2 (de) * 1989-04-04 1996-05-23 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzvorrichtung
DE3924127A1 (de) * 1989-07-20 1991-01-31 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3927742A1 (de) * 1989-08-23 1991-02-28 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3928612A1 (de) * 1989-08-30 1991-03-07 Bosch Gmbh Robert Kraftstoffverteilereinspritzpumpe fuer brennkraftmaschinen
US5215060A (en) * 1991-07-16 1993-06-01 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
DE4137252A1 (de) * 1991-11-13 1993-05-19 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4315646A1 (de) * 1993-05-11 1994-11-17 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE4338344A1 (de) * 1993-11-10 1995-05-11 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe für Brennkraftmaschinen
DE19631655C2 (de) * 1996-08-05 2003-03-27 Hatz Motoren Motorabschaltung für eine Brennkraftmaschine
GB9701877D0 (en) * 1997-01-30 1997-03-19 Lucas Ind Plc Fuel pump
US5887569A (en) * 1997-07-17 1999-03-30 Pacer Industries, Inc. Centrifugal fuel distributor
KR20020063163A (ko) * 1999-09-22 2002-08-01 가네가후치 가가쿠 고교 가부시키가이샤 신규 빵 효모 및 그 효모를 함유하는 밀가루 반죽
US20060159572A1 (en) * 2005-01-18 2006-07-20 Malcolm Higgins Pilot injection pump
US8316875B2 (en) * 2008-12-30 2012-11-27 General Electric Company Methods, apparatus and/or systems relating to fuel delivery systems for industrial machinery
CN102434320A (zh) * 2010-09-29 2012-05-02 戴长春 一种一体化燃气喷射器总成
CN102434323A (zh) * 2010-09-29 2012-05-02 戴长春 一种一体化燃气喷射器总成的切断阀机构

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1210233A (en) * 1967-03-28 1970-10-28 Cav Ltd Liquid fuel injection pumping apparatus
GB2076561B (en) * 1980-04-26 1985-04-03 Diesel Kiki Co Distribution type fuel injection apparatus
JPS5741462A (en) * 1980-08-25 1982-03-08 Mazda Motor Corp Fuel injection device for diesel engine
DE3142750C2 (de) * 1980-12-19 1984-06-20 Nissan Motor Co., Ltd., Yokohama, Kanagawa Treibstoffeinspritzpumpe für eine Diesel-Brennkraftmaschine
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
DE3119050A1 (de) * 1981-05-05 1982-11-18 Gebrüder Sulzer AG, 8401 Winterthur "brennstoffeinspritzvorrichtung mit elektromagnetisch betaetigtem umschaltventil"
DE3123325A1 (de) * 1981-06-12 1982-12-30 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen
DE3124500A1 (de) * 1981-06-23 1983-01-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
DE3127543A1 (de) * 1981-07-11 1983-01-20 Robert Bosch Gmbh, 7000 Stuttgart "kraftstoffversorgungseinrichtung fuer brennkraftmaschinen"
JPS5951139A (ja) * 1982-09-17 1984-03-24 Nippon Soken Inc 燃料供給装置
JPS60122268A (ja) * 1983-12-07 1985-06-29 Nippon Soken Inc 内燃機関の燃料供給装置
GB8417862D0 (en) * 1984-07-13 1984-08-15 Lucas Ind Plc Fuel pumping apparatus
GB8417861D0 (en) * 1984-07-13 1984-08-15 Lucas Ind Plc Fuel pumping apparatus
GB8417860D0 (en) * 1984-07-13 1984-08-15 Lucas Ind Plc Fuel injection pumping apparatus
JPS61138837A (ja) * 1984-12-07 1986-06-26 Nippon Denso Co Ltd デイ−ゼル機関用燃料噴射率制御装置
GB8611687D0 (en) * 1986-05-13 1986-06-18 Lucas Ind Plc Liquid fuel injection pump

Also Published As

Publication number Publication date
US4840162A (en) 1989-06-20
KR950003755B1 (ko) 1995-04-18
KR890000775A (ko) 1989-03-16
CN88103541A (zh) 1988-12-28
DE3719831A1 (de) 1988-12-22
EP0295420A2 (fr) 1988-12-21
JPS6419164A (en) 1989-01-23
EP0295420A3 (en) 1990-05-02
CN1013892B (zh) 1991-09-11
DE3866170D1 (de) 1991-12-19
JP2695842B2 (ja) 1998-01-14

Similar Documents

Publication Publication Date Title
EP0295420B1 (fr) Pompe d'injection de combustible
DE3235413C2 (fr)
EP0290797B1 (fr) Pompe d'injection de combustible
EP0688950B1 (fr) Système d'injection de carburant
EP0489740B1 (fr) Pompe d'injection distributrice de carburant pour moteurs a combustion interne
EP0322426B1 (fr) Pompe d'injection de carburant
EP0451227B1 (fr) Pompe d'injection de carburant
DE2401736A1 (de) Kraftstoffeinspritzvorrichtung fuer verbrennungskraftmaschinen
EP0318534B1 (fr) Pompe d'injection a distributeur du type a pistons radiaux
DE1476247A1 (de) Kraftstoffeinspritzvorrichtung fuer mit Kraftstoffeinspritzung und Kompressionszuendung arbeitende Brennkraftmaschinen
DE19833692C2 (de) Injektoreinheit mit Zeitsteuerplungerkolben mit festem Anschlag
EP0318535B1 (fr) Pompe d'injection de carburant
DE2930221A1 (de) Kraftstoffeinspritzsystem und -pumpe, dafuer vorgesehenes druckventil und kraftstoffeinspritzverfahren
EP0406592B1 (fr) Pompe à injection de combustible
DE3102801C2 (fr)
DE3236828A1 (de) Brennstoffeinspritzvorrichtung
DE3644257C2 (fr)
EP0032168A1 (fr) Installation d'injection de combustible pour moteurs à combustion interne, notamment pour moteurs diesel
DE2716854A1 (de) Kraftstoff-foerderanlage
DE3429128A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE916605C (de) Verfahren einer in Vor- und Haupteinspritzung unterteilten Kraftstoffeinspritzung mittels Einspritzpumpe
EP0396127B1 (fr) Appareil d'injection de combustible
EP0372238B1 (fr) Pompe d'injection de combustible pour moteurs à combustion interne
DE4315646A1 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE3719833C2 (de) Kraftstoffeinspritzpumpe

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: A2

Designated state(s): DE FR GB IT

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19900929

17Q First examination report despatched

Effective date: 19910429

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

ET Fr: translation filed
REF Corresponds to:

Ref document number: 3866170

Country of ref document: DE

Date of ref document: 19911219

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

RAP4 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: ROBERT BOSCH GMBH

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19991230

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20010423

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20010528

Year of fee payment: 14

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020510

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20020510

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030131

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050510