EP0114375B1 - Dispositif d'injection du combustible pour moteurs à combustion interne à auto-allumage par compression d'air - Google Patents

Dispositif d'injection du combustible pour moteurs à combustion interne à auto-allumage par compression d'air Download PDF

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Publication number
EP0114375B1
EP0114375B1 EP83112959A EP83112959A EP0114375B1 EP 0114375 B1 EP0114375 B1 EP 0114375B1 EP 83112959 A EP83112959 A EP 83112959A EP 83112959 A EP83112959 A EP 83112959A EP 0114375 B1 EP0114375 B1 EP 0114375B1
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EP
European Patent Office
Prior art keywords
fuel injection
pressure
regulator
appliance according
piston slide
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
Application number
EP83112959A
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German (de)
English (en)
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EP0114375A2 (fr
EP0114375A3 (en
Inventor
Gerd Wallenfang
Reda Rizk
Hans-Gottfried Michels
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
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Priority to AT83112959T priority Critical patent/ATE40447T1/de
Publication of EP0114375A2 publication Critical patent/EP0114375A2/fr
Publication of EP0114375A3 publication Critical patent/EP0114375A3/de
Application granted granted Critical
Publication of EP0114375B1 publication Critical patent/EP0114375B1/fr
Expired legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46Valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20Varying fuel delivery in quantity or timing
    • F02M59/36Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366Valves being actuated electrically
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46Valves
    • F02M59/466Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00Engines characterised by air compression and subsequent fuel addition
    • F02B3/06Engines characterised by air compression and subsequent fuel addition with compression ignition
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/24Fuel-injection apparatus with sensors

Definitions

  • the invention relates to a fuel injection device for an air-compressing, self-igniting internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is shown in DE-A-2 903 482, which has an electromagnetic actuator for the piston valve.
  • the valve member is brought into its closed position when the winding is excited, while when the winding is de-energized, the valve member is moved into the open position by the spring. Due to the direct coupling of the actuating element of the electromagnetic actuating device to the piston slide, the overall arrangement for opening the valve element must be accelerated. Large spring forces are required for this on the one hand, but on the other hand counteract rapid closing of the valve element when the electromagnetic actuating device is excited.
  • the extremely short injection times in a diesel internal combustion engine to achieve minimal consumption and optimal exhaust gas behavior cannot be achieved with the proposed device.
  • a fuel injection device is known, the electromagnetic control valve of which is controlled by the electrically operating measured value processing device as a function of characteristic operating parameters of the internal combustion engine.
  • the control valve controls an outflow channel provided on the nozzle side, in particular in order to regulate the start of injection and the end of injection of the fuel injection device with regard to the load state of the internal combustion engine.
  • the spool of the electromagnetic control valve has the same cross-section over its entire length because the pump pressure is applied to the end face via pressure compensation lines, in particular to keep the required magnetic valve actuating forces on the control spool low.
  • the spool of the control valve performs uncontrollable movements in the closed position, thus showing an unstable behavior, which is due in particular to uneven pressurization of the end faces of the spool, e.g. B. due to different pressure waves or more or less strong voiding in the pressure compensation lines. Furthermore, a more or less strong formation of cavities in the high-pressure system during the nozzle-side cut-off and the pump-side delivery further influences the injection time control.
  • the invention has for its object to develop the known fuel injection device such that extremely short injection times can be achieved.
  • an adjusting device for the closing movement and another adjusting device for the opening movement makes it advantageously possible to adapt them to the individual movements.
  • the actuator element - before transmitting an opening movement to the piston valve - acquires considerable kinetic energy which impulses on the Piston slide is transmitted and this is suddenly transferred to the open position.
  • extremely short opening times can be achieved, as a result of which the amounts of fuel to be injected can be metered more accurately and also smaller.
  • FR-A-1 566 847 relates only to configurations with two windings, which are intended to increase the electromagnetic force for performing a closing movement.
  • This publication does not contain an actuating device which opens a piston slide in the opening direction after passing through a preliminary stroke path.
  • FR-A-2 465 085 shows no two known electromagnetic actuating devices which work together in the manner according to the invention.
  • the housing space of the control valve has a high-pressure side and a low-pressure side housing space chamber which are assigned to the end faces of the piston valve, the high-pressure side and the low-pressure side housing space chamber being connected to one another by at least one line.
  • the end face of the spool is larger in the high-pressure chamber chamber than that in the low-pressure chamber Housing chamber.
  • these refinements of the fuel injection device according to the invention advantageously support the resulting closing pressure force acting in the closed position of the piston valve. This is due in particular to the fact that in the closed position of the piston valve, the housing chamber chamber on the high-pressure side and the low-pressure chamber chamber on the low-pressure side are filled with fuel via the sealing gap between the high-pressure piston valve region and the housing chamber.
  • the fuel of the high-pressure side housing chamber is displaced into the low-pressure side housing chamber, so that fuel is compressed by the stroke movement due to the differently dimensioned piston spool areas, which flows out via the low-pressure sealing gap.
  • this fuel which has flowed off on the low-pressure side, is refilled via the high-pressure channel and the high-pressure side sealing gap, with a pressure drop occurring in the direction of the low-pressure side housing chamber during the filling process, which causes the additional closing pressure force on the piston valve.
  • a fuel injection device in cross section.
  • the fuel injection device is provided in the usual way with a fuel injection pump 1, which consists of a pump housing 2, a pump element 3 designed as a pump piston, which can be moved in a known manner via a cam 4 and a spring-loaded tappet 5 in a pump chamber 6, an intake duct 7 and a high-pressure duct 8.
  • the fuel is supplied to the pump work chamber 6 of the fuel injection pump 1 via a suction channel 7 from a fuel feed pump, not shown, and is conveyed to a fuel injection nozzle 10 via a high-pressure channel 8 during the stroke of the pump piston 3 through the high-pressure channel 8.
  • the high-pressure channel 8 is controlled by an electromagnetic control valve 11, which has a valve body designed as a piston slide 12 and loaded by a compression spring 13, which is operatively connected to an electromagnetic actuating device 14 in the opening direction.
  • an electromagnetic control valve 11 Via the electromagnetic control valve 11, the high-pressure channel 8 in the open position of the control valve 11 can be connected to an outflow channel 15 leading, for example, into a fuel tank, so that opening or closing of the electromagnetic control valve 11 in the high-pressure phase of the fuel injection pump 1 starts and ends the injection the fuel injector 10 is adjustable.
  • the electromagnetic actuation device 14 is actuated for control valve actuation by an electrically working measured value processing device, not shown, which interacts with suitable sensors and, depending on the load condition of the air-compressing, self-igniting internal combustion engine equipped with the fuel injection device according to the invention, regulates the activation times and thus the start of injection and the end of injection.
  • the spool 12 of the electromagnetic control valve 11 has a high-pressure side spool part 17 delimited by a valve body 16 and a low-pressure side spool part 18, the high-pressure side spool part 17 constantly having the diameter of the valve body 16 and the low-pressure side spool part 18 having a smaller diameter than the high-pressure side spool part 17 is trained.
  • the piston slide 12 is axially movable in a housing space 19, the housing space 19 having a high-pressure-side housing space chamber 20 and a low-pressure-side housing space chamber 21, which are each assigned to the end faces of the piston slide 12, and wherein the housing space 19 outside a high-pressure chamber 22 and a low-pressure chamber 23 suitable sealing elements 24 is sealed pressure-tight.
  • the high-pressure-side housing space chamber 20 and the low-pressure-side housing space chamber 21 are connected to one another by a bore 25 which is not visible in the illustration according to FIG. 1.
  • the opening movement of the piston slide 12 is limited by a stop 27, as is the compression spring 13 arranged in the high-pressure-side housing chamber 20, the stop 27, the compression spring 13 and the electromagnetic actuating device 14 in order to generate a resulting pressure closing force in such a manner on the end faces of the Piston slide 12 are provided or the end faces of the piston slide 12 are designed such that the end face area of the piston slide 12 exposed to the high-pressure side chamber pressure is larger than the end face area of the piston slide 12 which is exposed to the low pressure side chamber pressure.
  • the pump piston 3 has in its lateral surface a longitudinal groove 42 which is in flow connection with the pump chamber 6 and can be brought into overlap with the suction channel 7 by rotating the pump piston 3.
  • a mechanical control device (not shown in more detail) is provided, which works as a function of the speed using generally known means, for example centrifugal weights etc., and at a predeterminable maximum speed of the internal combustion engine releases the connection between the pump chamber 6 and the intake duct 7 for the purpose of controlling fuel . This measure serves as an additional safety device.
  • FIG. 3 shows the fuel injection device according to the invention corresponding to FIG. 1 with an electromagnetic actuation device 14 designed according to the invention, although the known parts of the fuel injection pump have not been shown.
  • the electrical actuating device 14 has a second electromagnetic actuating device (coil) 29 with an iron core 30 and an armature 31, a spring element 32 being fastened to the armature 31, which spring element can be pretensioned by the excitation of the actuating device 29 by the movement of the armature 31 , and wherein the preload of the spring element 32 is limited by a spacer 33.
  • the electromagnetic actuation device has a first electromagnetic actuation (coil) 34 with a two-part armature and an iron core 36.
  • the two-piece armature consists of an inner armature part 35a and an outer armature part 35b, the inner armature part 35a being axially movable relative to the outer armature part 35b and being able to be coupled thereto in a fixed manner via a shoulder / collar connection 37.
  • the second actuating device 29 with the associated armature 31 and the iron core 30 and the first actuating device 34 with associated armature parts 35a and 35b and the second iron core 36 are assigned to the low-pressure-side housing space chamber 21 and provided with corresponding sealing elements 24, whereby the inner armature part 35a of the first actuating device 34 acts directly on the piston slide 12 and the armature 31 of the second actuating device 29 is in direct operative connection with the inner armature part 35a of the first actuating device 34.
  • a stop element 38 is further provided, which limits the axial lifting movement of the outer armature part 35b of the first adjusting device 34 to one side, the stop element 38 and the spacer element 33 being designed such that between the inner armature part 35a of the first actuating device 34 in the closed position of the spool 12 and the armature 31 of the second actuating device 29 with a maximum preloaded spring element 32, a preliminary stroke distance is present.
  • the axial stroke movement of the outer armature part 35b is limited on the other hand by a non-magnetic spacer 41 towards the iron core 36.
  • the actuating devices 29 and 34 are activated as a function of the control times determined by the electrically working measured value processing device.
  • the second actuating device 29 is energized and the first actuating device 34 is de-energized during the closed position of the spool 12, so that the spring element 32 is pretensioned to a maximum and the outer armature part 35b rests on the stop element 38 and there is a preliminary stroke distance between the inner armature part 35a and armature 31 .
  • the opening signal is generated by the electrically working measured value processing device d. H.
  • the second actuating device 29 is switched off, so that initially only the armature 31, and thus advantageously a very small mass, is accelerated by the spring element 32 and after the preliminary stroke via the inner armature 35a, the piston slide 12 opens suddenly as far as the stop 27, the outer armature 35b of the first actuating device 34 initially remains in the rest position due to the relative possibility of axial movement of the inner armature 35a.
  • the first actuating device 34 is excited so that the outer armature part 35b is brought into contact with the spacer 41. Due to the re-excitation of the second actuating device 29, the spring element 32 is pretensioned again and the armature 31 is brought back into the pretension position.
  • the adjusting device 34 now takes over the holding function of the piston slide 12 against the force of the compression spring 13, the piston slide stroke now no longer being limited by the stop 27, but rather by the inner armature part 35a resting on the outer armature part 35b via the shoulder / collar connection 37.
  • the closing movement of the piston slide 12 is initiated by switching off the first adjusting device 34, so that the compression spring 13 brings the piston slide 12 into the closed position, although in this case advantageously only the armature parts 35a and 35b need to be carried along.
  • This inventive design of the electromagnetic actuating device 14 makes it possible in an advantageous manner to have the magnetic actuating forces to be applied and thus the construction volume claimed low due to the predominant holding function of the first actuating device 34 and the second actuating device 29.
  • a sensor device 40 is provided in the range of movement of the low-pressure side end face of the piston slide 17, which - not shown in detail - has a permanent magnet, pole shoes and an induction coil and, depending on the piston slide movement or an air gap between the piston slide face and the inner armature 35a., Generates an impulsive signal which can be evaluated in the measured value processing device as a closing time or opening time signal of the control valve and can be taken into account accordingly when controlling the actuating devices 29 and 34 to avoid magnetic transmission errors, although the local arrangement shown here Sensor device 40 is not mandatory, but also preferably the one or a second sensor device 40 can be provided between the armature 31 and the outer and inner armature parts 35a and 35b.
  • the embodiment according to FIG. 4 is designed similarly to the embodiment according to FIG. 3, but with the second adjusting device 29, the iron core 30 and the anchor 31 of the low-pressure housing space chamber 21 and the first adjusting device 34 and the inner anchor part 35a, the outer anchor part 35b and the iron core 36 are assigned to the housing chamber 20 on the high-pressure side, again suitable sealing elements 24 being provided for the pressure-tight sealing of the housing chambers 20, 21.
  • the armature 31 of the second actuating device 29 is in direct operative connection with the piston slide 12 and the inner armature part 35a is fastened directly on the piston slide.
  • the spacing element 33 is designed in this embodiment such that in the closed position of the spool 12, the armature 31 can be moved by an excitation of the second actuating device 29 into an axial distance from the spool 12 is.
  • the iron core 36 has a shoulder 36a designed as a spacer element, which interacts with the inner anchor parts 35a.
  • the excitation times or the excitation duration of the second actuating device 29 of the first actuating device 34 determined by the electrically operating measured value processing device takes place in an analogous manner to that in the exemplary embodiment according to FIG. H. that the actuating device 29 can be switched off for valve opening, as a result of which the injection process is ended during the high-pressure phase of the fuel injection pump 1 and thus the end of injection is determined, and the valve closing process is initiated by switching off the first actuating device 34, the piston slide 12 moving under the force of the compression spring 13 moved into the closed position and thus the start of injection of the fuel injection device is determined.
  • the advantages indicated in connection with FIG. 3 apply analogously to this exemplary embodiment.
  • the control valve 11 is provided in a special holding element 52, which makes it possible to retrofit today's common fuel injection pump elements with the control valve designed according to the invention without any special rework on the pump side. It is essential when fastening the control valve 11 according to the invention in the holding element 52 that the holding force exerted on the control valve 11 is exerted in the longitudinal direction of the piston slide 12 in order to reliably avoid any deformation or tension of the high-pressure and low-pressure sealing gaps 28a and 28b.
  • the holding element 52 has a stepped bore 43, into which the control valve 11 is inserted with the interposition of a sealing element 50.
  • An end face of the control valve which protrudes from the holding element 52, is provided with a thread onto which a nut 44 can be screwed, so that the control valve 11 is connected pressure-tight to the holding element 52 by a holding force oriented in the longitudinal direction of the piston valve 12.
  • the holding element 52 On the pump side, the holding element 52 has a connection part 45 which can be inserted into a connection bore 48 of the fuel injection pump 1.
  • This connection bore 48 of the fuel injection pump 1 has the usual dimensions for receiving the pressure valve 9, so that the control valve 11 is mounted via the holding element 52 without reworking on the pump side.
  • the pump-side connecting part 45 is provided with a recess 46, into which preferably two ring-shaped pressing elements 47 are inserted.
  • a fastening member 49 is screwed onto the thread of the connection bore 48, which is in operative connection with the pressing elements 47 and connects the holding element 52 pressure-tightly to the fuel injection pump 1 and thus to the pump chamber 6 via these pressing elements 47.
  • a receiving space 51 for the pressure valve 9 is provided facing away from the fuel injection pump and is designed in a manner analogous to the receiving bore 48 of the fuel injection pump 1. It should be noted that the bore 43 of the holding element 52 is made with a slight oversize, in order to avoid any deformation or tensioning of the sealing gaps 28a and 28b on the low-pressure and high-pressure side resulting from the fastening of the pressure valve 9 in the receiving space 51.

Claims (25)

1. Dispositif d'injection du combustible pour moteurs à combustion interne à auto-allumage par compression d'air, avec une soupape de commande (11) disposée entre une pompe d'injection de carburant (1) et un injecteur (10), dans le carter de laquelle un corps de soupape (16), réalisé sous forme de tiroir à piston (12) et mobile axialement, au moyen d'un dispositif de réglage (34) électromagnétique, avec une chambre à haute pression (22), disposée dans le carter, qui est reliée à un canal à haute pression (8) de la pompe d'injection (1), ainsi qu'avec l'injecteur (10), et avec une chambre de basse pression (23), qui est disposée dans le carter, qui est reliée à un canal de basse pression, de préférence un canal d'écoulement (15), un siège de soupape étant disposé entre la chambre à haute pression (22) et la chambre à basse pression (23), siège avec lequel collabore le corps de soupape (16) du tiroir à piston (12) et le tiroir a piston (12) étant maintenu sur le siège de soupape, par un ressort (13), en position de fermeture, caractérisé en ce que la partie (17) côté haute pression du tiroir à piston (12) possède un diamètre constant, qui est approximativement égal au diamètre extérieur de la zone d'étanchéité du corps de soupape (16) collaborant avec le siège de soupape, en ce que la partie basse pression (18) du tiroir à piston (12) possède un diamètre plus petit que la partie (17) côté haute pression du tiroir à piston (12) et qu'il est prévu un deuxième dispositif de réglage (29) électromagnétique, dont l'élément d'actionnement (31) attaque le tiroir à piston (12), après une course préliminaire, et actionne celui-ci, dans le sens de l'ouverture.
2. Dispositif d'injection du combustible selon la revendication 1, avec des chambres d'enceinte de carter (20, 21) disposées sur les deux côtés frontaux du tiroir à piston (12), qui sont reliées ensemble par une conduite, caractérisé en ce que la surface frontale du tiroir à piston (12) est plus importante, dans la chambre d'enceinte de carter (20), côté haute pression, que la surface frontale, dans la chambre d'enceinte de carter (21), côté basse pression.
3. Dispositif d'injection du combustible selon la revendication 1 ou 2, caractérisé en ce que le ressort (13) est prévu sur la surface frontale de côté haute pression du tiroir à piston (12).
4. Dispositif d'injection du combustible selon l'une des revendications précédentes, caractérisé en ce que les deux dispositifs de réglage (34, 29) sont disposés sur la surface frontale de côté basse pression du tiroir à piston (12).
5. Dispositif d'injection du combustible selon l'une des revendications 1 à 4, caractérisé en ce que le tiroir à piston (12) est maintenu en position d'ouverture au moyen du deuxième dispositif de réglage (29).
6. Dispositif d'injection du combustible selon l'une des revendications 1 à 5, caractérisé en ce qu'un ressort (32) est fixé sur l'élément d'actionnement (31) du deuxième dispositif de réglage (29) et est précontraint par l'excitation de la bobine magnétique du deuxième dispositif de réglage (29).
7. Dispositif d'injection du combustible selon la revendication 6, caractérisé en ce qu'un élément d'écartement (33) est prévu sur l'élément d'actionnement (31) du deuxième dispositif de réglage (29) et limite la course préliminaire du ressort (32).
8. Dispositif d'injection du combustible selon l'une des revendications 1 à 7, caractérisé en ce que l'induit du premier dispositif de réglage (34) électromagnétique est réalisé en deux pièces et possède une partie d'induit (35a, 35b) intérieure et extérieure, la partie d'induit (35a) intérieure étant à cette occasion mobile axialement, par rapport à la partie d'induit (35b) extérieure.
9. Dispositif d'injection du combustible selon la revendication 8, caractérisé en ce que les parties d'induit (35a, 35b) intérieure et extérieure sont susceptibles d'être accouplées, par rapport au mouvement axial.
10. Dispositif d'injection du combustible selon l'une des revendications 1 à 9, caractérisé en ce que le premier et le deuxième dispositif de réglage (34, 29) électromagnétique sont affectés, avec leurs induits (31, 35a, 35b) et leurs noyaux de fer (30, 36), à la surface frontale de côté basse pression du tiroir à piston (12), la partie d'induit (35a) intérieure du premier dispositif de réglage (34) étant à cette occasion en relation fonctionnelle directe avec le tiroir à piston (12) et l'induit (31) du deuxième dispositif de réglage (29) étant en relation fonctionnelle indirecte, avec la partie d'induit (35a) intérieure du premier dispositif de réglage (34).
11. Dispositif d'injection du combustible selon la revendication 10, caractérisé en ce qu'un élément de butée est disposé entre le premier et le deuxième dispositif de réglage (34, 29), pour exercer une limitation axiale de la course de partie d'induit (35b) extérieure du premier dispositif de réglage (34).
12. Dispositif d'injection du combustible selon la revendication 7 et 11, caractérisé en ce que l'élément de butée (38) de l'élément d'actionnement (31) du deuxième dispositif de réglage (29) est réalisé, de telle sorte que la course préliminaire est formée entre la partie d'induit (35a) intérieure du premier dispositif de réglage (34), le tiroir à piston en position de fermeture, et l'élément d'actionnement (31) du deuxième dispositif de réglage (29), pour un ressort (32) précontraint au maximum.
13. Dispositif d'injection du combustible selon l'une des revendications 10 à 12, caractérisé en ce qu un élément d'écartement (41) est disposé entre le noyau de fer (36) et la partie d'induit extérieure (35b) du premier dispositif de réglage (34), élément qui limite le mouvement axial de la partie d'induit (35b) extérieure.
14. Dispositif d'injection du combustible selon l'une des revendications 10 à 13, caractérisé en ce qu'une butée est affectée à la surface frontale de la partie (17) de côté haute pression du tiroir à piston.
15. Dispositif d'injection du combustible selon l'une des revendications 1 à 9, caractérisé en ce que le deuxième dispositif de réglage (29) avec son noyau de fer (30) et l'induit (31) est affecté à la surface frontale de côté basse pression du tiroir à piston (12) et que le premier dispositif de réglage (34) avec ses parties d'induit (35a, 35b) et le noyau de fer (36) sont affectés à la surface frontale de côté haute pression du tiroir à piston (12).
16. Dispositif d'injection du combustible selon la revendication 15, caractérisé en ce que l'induit (31) du deuxième dispositif de réglage (29) est directement opposé au tiroir à piston (12) et attaque celui-ci et que l'induit intérieur (35a) du premier dispositif de réglage (34) est fixé sur le tiroir à piston (12).
17. Dispositif d'injection du combustible selon la revendication 15 ou 16, caractérisé en ce que le noyau de fer (36) du premier dispositif de réglage (34) possède un gradin (36a), réalisé sous forme d'élément d'écartement qui est associé à la partie d'induit (35a) intérieure.
18. Dispositif d'injection du combustible selon la revendication 15 ou 17, caractérisé en ce que l'élément d'écartement (33) du deuxième dispositif de réglage (29) est réalisé de telle sorte que, dans la position de fermeture du tiroir à piston (12), l'induit (31) du deuxième dispositif de réglage (29) est déplacé, avec un écartement axial, vis-à-vis du tiroir à piston (12).
19. Dispositif d'injection du combustible selon l'une des revendications 1 à 18, caractérisé en ce que la pompe d'injection de carburant (1) comprend un piston de pompe (3), qui est tournant autour d'un axe s'étendant en direction longitudinale du piston de pompe (3) et est pourvu d'une rainure longitudinale (42), prévue dans la surface d'enveloppe et qui est susceptible d'être reliée à une enceinte de travail de pompe.
20. Dispositif d'injection du combustible selon la revendication 19, caractérisé en ce que le piston de pompe (3) est susceptible d'être actionné dans le sens de rotation d'un dispositif de réglage mécanique influencé par la vitesse de rotation du moteur à combustion interne et que la rainure longitudinale (42) est susceptible d'être placée en recouvrement du canal d'aspiration.
21. Dispositif d'injection du combustible selon l'une des revendications 1 à 20, caractérisé en ce qu'un capteur (40) est prévu dans la zone de mouvement d'une surface frontale du tiroir à piston (12), ou bien d'un induit (31, 35a, 35b), capteur qui possède un aimant permanent, des pièces polaires et une bobine d'induction et qui produit un signal de début de fermeture et/ou d'ouverture de la soupape de commande (11), en forme d'impulsion, en fonction du mouvement de tiroir à piston ou d'un entrefer, sur une surface frontale du tiroir à piston (12).
22. Dispositif d'injection du combustible selon l'une des revendications 1 à 21, caractérisé en ce que la soupape de commande (11) est prévue sur un élément de maintien (52) susceptible d'être relié à la pompe d'injection de carburant et est fixée sur celui-ci au moyen d'une force de maintien exercée dans la direction longitudinale du tiroir à piston (12).
23. Dispositif d'injection du combustible selon la revendication 22, caractérisé en ce que l'élément de maintien (52) possède un alésage (43) étagé, pour recevoir la soupape de commande (11), et que la soupape de commande (11) est serrée avec l'élément de maintien (52), au moyen d'une liaison visée (44).
24. Dispositif d'injection du combustible selon la revendication 22 ou 23, caractérisé en ce que l'élément de maintien (52) possède une partie de raccordement (45) située côté pompe, avec un évidement (46), pour recevoir un ou plusieurs éléments de pression (47) et qu'un élément de fixation (49), vissé dans un alésage de raccordement (48) de la pompe d'injection de carburant (1), situé en liaison fonctionnelle avec des éléments de pression (47), est relié à la pompe d'injection de carburant (1).
25. Dispositif d'injection du combustible selon l'une des revendications 22 à 24, caractérisé en ce que l'élément de maintien possède une enceinte de réception (51), pour une soupape de refoulement (9).
EP83112959A 1983-01-25 1983-12-22 Dispositif d'injection du combustible pour moteurs à combustion interne à auto-allumage par compression d'air Expired EP0114375B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83112959T ATE40447T1 (de) 1983-01-25 1983-12-22 Kraftstoffeinspritzvorrichtung fuer luftverdichtende, selbstzuendende brennkraftmaschinen.

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DE19833302294 DE3302294A1 (de) 1983-01-25 1983-01-25 Kraftstoffeinspritzvorrichtung fuer luftverdichtende, selbstzuendende brennkraftmaschinen
DE3302294 1983-01-25

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EP0114375A2 EP0114375A2 (fr) 1984-08-01
EP0114375A3 EP0114375A3 (en) 1986-02-05
EP0114375B1 true EP0114375B1 (fr) 1989-01-25

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EP (1) EP0114375B1 (fr)
JP (1) JPS59165859A (fr)
AT (1) ATE40447T1 (fr)
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DE (2) DE3302294A1 (fr)
ES (1) ES8500387A1 (fr)
RU (1) RU1830109C (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4001435A1 (de) * 1990-01-19 1991-07-25 Kloeckner Humboldt Deutz Ag Steuerventil
DE4212797A1 (de) * 1992-04-16 1993-10-21 Kloeckner Humboldt Deutz Ag Hochdruckabdichtung für Brennstoffeinspritzvorrichtung
DE19721841A1 (de) * 1997-05-24 1998-09-03 Mtu Friedrichshafen Gmbh Kraftstoffeinspritzsystem für eine selbstzündende Brennkraftmaschine

Families Citing this family (49)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3427421A1 (de) * 1984-07-25 1986-01-30 Klöckner-Humboldt-Deutz AG, 5000 Köln Steuerventil fuer eine kraftstoffeinspritzvorrichtung
EP0178427B1 (fr) * 1984-09-14 1990-12-27 Robert Bosch Gmbh Pompe d'injection de carburant commandée par électricité pour moteurs à combustion interne
DE3523536A1 (de) * 1984-09-14 1986-03-27 Robert Bosch Gmbh, 7000 Stuttgart Elektrisch gesteuerte kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3506392A1 (de) * 1985-02-23 1986-09-04 Motoren-Werke Mannheim AG vorm. Benz Abt. stationärer Motorenbau, 6800 Mannheim Einspritzsystem fuer einen dieselmotor mit einer hochdruck-einspritzpumpe fuer jeden zylinder
JPS61247861A (ja) * 1985-04-24 1986-11-05 Ishikawajima Harima Heavy Ind Co Ltd デイ−ゼル機関燃料噴射ポンプ
DE3536828A1 (de) * 1985-10-16 1987-04-16 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzvorrichtung mit einem elektromagnetischen steuerventil zwischen einspritzpumpe und einspritzduese
US4884549A (en) * 1986-04-21 1989-12-05 Stanadyne Automotive Corp. Method and apparatus for regulating fuel injection timing and quantity
DE3614495A1 (de) * 1986-04-29 1987-11-05 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzvorrichtung fuer eine brennkraftmaschine
JPH07117012B2 (ja) * 1986-09-05 1995-12-18 トヨタ自動車株式会社 ユニツトインジエクタ
IT1198062B (it) * 1986-10-22 1988-12-21 Piaggio & C Spa Motore a combustione interna a due tempi,ad iniezione di combustibile ed accensione comandata
GB8703419D0 (en) * 1987-02-13 1987-03-18 Lucas Ind Plc Fuel injection pump
IT1217256B (it) * 1987-08-25 1990-03-22 Weber Srl Pompa di iniezione per impianti di iniezione del combustibile con iniettori comandati per motori a ciclo diesel
DE3729636A1 (de) * 1987-09-04 1989-03-16 Bosch Gmbh Robert Verfahren zur steuerung der zeit der kraftstoffhochdruckfoerderung einer kraftstoffeinspritzpumpe
DE3732553A1 (de) * 1987-09-26 1989-04-13 Bosch Gmbh Robert Magnetventil
DE3819996A1 (de) * 1988-06-11 1989-12-14 Bosch Gmbh Robert Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen
GB2224786B (en) * 1988-09-21 1992-09-23 Toyota Motor Co Ltd A fuel injection device
DE3841462C2 (de) * 1988-12-09 1996-05-30 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzvorrichtung
DE3910793C2 (de) * 1989-04-04 1996-05-23 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzvorrichtung
DE3922859A1 (de) * 1989-07-12 1991-01-24 Bosch Gmbh Robert Verfahren zur steuerung der kraftstoffzumessung in eine brennkraftmaschine
DE4142998C1 (fr) * 1991-12-24 1993-07-22 Robert Bosch Gmbh, 7000 Stuttgart, De
DE4412948C2 (de) * 1994-04-14 1998-07-23 Siemens Ag Elektrohydraulische Absperrvorrichtung
US6161770A (en) 1994-06-06 2000-12-19 Sturman; Oded E. Hydraulically driven springless fuel injector
US6257499B1 (en) 1994-06-06 2001-07-10 Oded E. Sturman High speed fuel injector
US5720261A (en) * 1994-12-01 1998-02-24 Oded E. Sturman Valve controller systems and methods and fuel injection systems utilizing the same
US6148778A (en) 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
WO1997001031A1 (fr) * 1995-06-23 1997-01-09 Diesel Technology Company Pompe a carburant et son procede de fonctionnement
US5954487A (en) * 1995-06-23 1999-09-21 Diesel Technology Company Fuel pump control valve assembly
US5749717A (en) * 1995-09-12 1998-05-12 Deisel Technology Company Electromagnetic fuel pump for a common rail fuel injection system
DE19641952C5 (de) * 1996-10-11 2005-06-02 Daimlerchrysler Ag Kraftstofführung für eine mehrzylindrige Brennkraftmaschine mit Aufnahmebohrungen für Steckpumpen
US6000379A (en) * 1997-11-25 1999-12-14 Caterpillar Inc. Electronic fuel injection quiet operation
US5975053A (en) * 1997-11-25 1999-11-02 Caterpillar Inc. Electronic fuel injection quiet operation
DE19809627A1 (de) * 1998-03-06 1999-09-09 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US6029628A (en) * 1998-05-07 2000-02-29 Navistar International Transportation Corp. Electric-operated fuel injection having de-coupled supply and drain passages to and from an intensifier piston
US6085991A (en) 1998-05-14 2000-07-11 Sturman; Oded E. Intensified fuel injector having a lateral drain passage
DE19837333A1 (de) * 1998-08-18 2000-02-24 Bosch Gmbh Robert Steuereinheit zur Steuerung des Druckaufbaus in einer Pumpeneinheit
US6276610B1 (en) * 1998-12-11 2001-08-21 Diesel Technology Company Control valve
DE19908102C1 (de) * 1999-02-25 2000-05-04 Daimler Chrysler Ag Ventil mit variablem Ventilquerschnitt
US6089470A (en) * 1999-03-10 2000-07-18 Diesel Technology Company Control valve assembly for pumps and injectors
US6158419A (en) * 1999-03-10 2000-12-12 Diesel Technology Company Control valve assembly for pumps and injectors
DE19916658A1 (de) * 1999-04-14 2000-10-19 Hydraulik Ring Gmbh Steuerventil, insbesondere für Einspritzvorrichtungen für Verbrennungsmaschinen, vorzugsweise Dieselmotoren
DE19954058A1 (de) * 1999-11-10 2001-05-23 Bosch Gmbh Robert Kraftspeicherunterstützte Steuerung der Einspritzmengen bei Großdieselmotoren
JP3905282B2 (ja) 2000-04-18 2007-04-18 トヨタ自動車株式会社 高圧ポンプ
US6450778B1 (en) 2000-12-07 2002-09-17 Diesel Technology Company Pump system with high pressure restriction
US7328688B2 (en) * 2005-06-14 2008-02-12 Cummins, Inc Fluid pumping apparatus, system, and method
CN102808712B (zh) * 2012-07-17 2014-01-15 华中科技大学 一种直线电磁驱动柱塞泵
CN104061097A (zh) * 2014-07-18 2014-09-24 山东鑫亚工业股份有限公司 一种柴油机用电控单体喷油泵
CN104847554A (zh) * 2015-04-09 2015-08-19 中国第一汽车股份有限公司无锡油泵油嘴研究所 一种柴油机用电控单体泵
CN105782498A (zh) * 2016-04-26 2016-07-20 武汉理工大学 一种双电磁铁控制高速电磁阀
CN111794887B (zh) * 2019-04-08 2022-04-12 纬湃汽车电子(长春)有限公司 高压泵

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1526633A1 (de) * 1951-01-28 1970-01-29 Bosch Gmbh Robert Elektromagnetisch betaetigtes Kraftstoffeinspritzventil fuer Brennkraftmaschinen
DE936838C (de) * 1953-01-18 1955-12-22 Erich Herion Fa Magnetventil mit Springschaltersteuerung
FR1179542A (fr) * 1957-07-08 1959-05-26 Perfectionnements apportés à des pompes alternatives autorégulatrices, notamment pour l'injection de combustible dans des moteurs
DE1576536A1 (de) * 1967-04-19 1970-06-18 Gehap Gmbh & Co Kg Elektromagnetisch betaetigte Sperr-Duese mit Einrichtung fuer schnelles Schliessen und OEffnen der Duesenoeffnung
US3851635A (en) * 1969-05-14 1974-12-03 F Murtin Electronically controlled fuel-supply system for compression-ignition engine
FR2145080A5 (fr) * 1971-07-08 1973-02-16 Peugeot & Renault
US3779225A (en) * 1972-06-08 1973-12-18 Bendix Corp Reciprocating plunger type fuel injection pump having electromagnetically operated control port
DE2425946A1 (de) * 1974-05-30 1975-12-11 Dungs Karl Fa Doppelmagnetventil
GB1538226A (en) * 1975-03-07 1979-01-10 Cav Ltd Fuel injection systems for internal combustion engines
US4276000A (en) * 1978-01-31 1981-06-30 Lucas Industries Limited Liquid fuel pumping apparatus
US4310143A (en) * 1978-11-29 1982-01-12 Gresen Manufacturing Company Electrically controlled proportional valve
DE2935912A1 (de) * 1979-09-06 1981-03-26 MAN B & W Diesel GmbH, 86153 Augsburg Brennstoffeinspritzvorrichtung fuer brennkraftmaschinen
US4336896A (en) * 1979-12-31 1982-06-29 Lunau John A Electrically controlled in-line dispensing faucet
JPS56118529A (en) * 1980-02-22 1981-09-17 Nippon Denso Co Ltd Rotational speed controlling method for engine
FR2480356A1 (fr) * 1980-04-14 1981-10-16 Lucas Industries Ltd Appareil de pompage et d'injection de combustible
GB2076561B (en) * 1980-04-26 1985-04-03 Diesel Kiki Co Distribution type fuel injection apparatus
FR2481752A1 (fr) * 1980-04-30 1981-11-06 Renault Vehicules Ind Amelioration des dispositifs mecaniques d'injection de combustible, notamment pour des moteurs diesel
US4361309A (en) * 1980-06-23 1982-11-30 Niipondenso Co., Ltd. Electromagnetic actuator
JPS58128428A (ja) * 1982-01-28 1983-08-01 Nippon Soken Inc エンジンの燃料噴射制御装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4001435A1 (de) * 1990-01-19 1991-07-25 Kloeckner Humboldt Deutz Ag Steuerventil
DE4212797A1 (de) * 1992-04-16 1993-10-21 Kloeckner Humboldt Deutz Ag Hochdruckabdichtung für Brennstoffeinspritzvorrichtung
DE19721841A1 (de) * 1997-05-24 1998-09-03 Mtu Friedrichshafen Gmbh Kraftstoffeinspritzsystem für eine selbstzündende Brennkraftmaschine

Also Published As

Publication number Publication date
JPS59165859A (ja) 1984-09-19
DE3302294A1 (de) 1984-07-26
ATE40447T1 (de) 1989-02-15
EP0114375A2 (fr) 1984-08-01
DE3379070D1 (en) 1989-03-02
CA1208511A (fr) 1986-07-29
ES529100A0 (es) 1984-10-01
EP0114375A3 (en) 1986-02-05
US4619239A (en) 1986-10-28
RU1830109C (ru) 1993-07-23
ES8500387A1 (es) 1984-10-01

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