EP0150471B1 - Pompe d'injection de combustible - Google Patents

Pompe d'injection de combustible Download PDF

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Publication number
EP0150471B1
EP0150471B1 EP84116075A EP84116075A EP0150471B1 EP 0150471 B1 EP0150471 B1 EP 0150471B1 EP 84116075 A EP84116075 A EP 84116075A EP 84116075 A EP84116075 A EP 84116075A EP 0150471 B1 EP0150471 B1 EP 0150471B1
Authority
EP
European Patent Office
Prior art keywords
pump
fuel
distributor
piston
fuel injection
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
EP84116075A
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German (de)
English (en)
Other versions
EP0150471A3 (en
EP0150471A2 (fr
Inventor
Jean Leblanc
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 EP0150471A2 publication Critical patent/EP0150471A2/fr
Publication of EP0150471A3 publication Critical patent/EP0150471A3/de
Application granted granted Critical
Publication of EP0150471B1 publication Critical patent/EP0150471B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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

Definitions

  • a fuel injection pump known from DE-C-18 07 554 is designed as a reciprocating piston distributor pump with a relief channel running in the pump piston and branching off from the pump work space, which has a lateral outlet on the pump piston and is connected to a relief line from a certain stroke position of the respective pump delivery stroke is connected to a discharge volume of constant content via a variable and a fixed throttle.
  • the capacity of this volume is determined on the one hand by the variable throttle, which is adjustable depending on the load, and on the other hand by the fixed throttle, which acts as a function of the speed.
  • the known device does not permit universal use and, in particular, the amount of a pre-injection before the actual main injection and the time interval between the pre-injection and the main injection cannot be determined over wide operating ranges of the internal combustion engine.
  • a distributor fuel injection pump is also known, in which, similarly to the distributor fuel injection pump mentioned at the beginning, part of the fuel delivered by the pump piston can be dispensed into a fuel removal space which is activated again with each fuel injection process of the distributor fuel injection pump.
  • this activation takes place with a fixed stroke of the pump piston or with a fixed rotational position of a distributor of the distributor fuel injection pump, the removal space consisting of a combination between a fixed volume accumulator and an escape piston connected upstream of this accumulator.
  • the distance covered by this decreases, which corresponds in each case to the effective receiving volume of the accumulator under the action of a throttle which restricts the return movement of the piston.
  • a reduction in the injection rate and thus also the injection quantity is achieved over the duration of the total injection time.
  • the device is only effective within a single speed range.
  • a fuel injection pump is also known from FR-C-1 495 537, in which the pump work space is continuously connected to a fuel extraction space via a throttle. This is limited by an evasive piston, the evasive movement of which can be blocked by an additional device in a certain operating range of the internal combustion engine in such a way that the removal function of the fuel removal space is canceled.
  • the fuel injection rate is reduced over part of the delivery stroke of the pump piston.
  • a fuel injection pump of the generic type is known from DE-C-585 014.
  • the movable wall executes its stroke up to the adjustable stop with each actuation process of the relief opening, a certain fixed quantity of fuel being taken from the quantity of fuel delivered by the pump piston.
  • the point in time at which the fuel injection is interrupted during the course of the injection can be varied as a function of the main injection quantity. If the start of delivery remains the same, the fuel pre-injection quantity decreases as the load decreases. With such a fuel injection pump, the amount of pre-injection can therefore only be controlled in a very specific law. Furthermore, the distance between the pre-injection and the main injection is determined by the withdrawal volume.
  • the fuel injection pump with the characterizing features of the main claim has the advantage that a desired distance of the pre-injection before the main injection can be set sufficiently accurately in wide operating ranges of the internal combustion engine with the help of the adjustable fuel removal volume.
  • the point in time at which the connection between the pump chamber and the fuel extraction chamber is opened determines the amount of the pre-injection, which in turn depends on the geometric variables that are independent of the speed and for sufficient operating ranges of the internal combustion engine speed can be adjusted.
  • the fuel injection pump according to the invention can also be implemented on a radial piston pump without significant effort.
  • FIG. 1 shows the first exemplary embodiment in longitudinal section
  • FIG. 2 shows a partial section through the injection pump according to FIG. 1 perpendicular to the sectional plane shown there
  • FIG. 3 shows a development of the distributor according to FIG. 1 together with the lateral surfaces surrounding it
  • FIG. 4 shows part of the cam elevation curve of the cam drive 1 with an assigned injection quantity curve over the angle of rotation
  • FIG. 5 shows a partial development of the distributor and the peripheral surface surrounding it from a further development of the exemplary embodiment according to FIG. 1
  • FIG. 6 shows a second exemplary embodiment in use with an in-line or reciprocating piston injection pump
  • FIG. 7 a third embodiment modification to the embodiment of Figures 1 and 2.
  • a distributor 3 is mounted in a bore 2 and is driven at a pump speed by a drive (not shown further here).
  • the distributor can be coupled at its end to a cam ring carrier 7 via a pin 5 guided through a longitudinal groove 4 provided there, which is approximately cup-shaped and carries a cam ring 8 with a radially inwardly directed cam track 9 on its upper edge. In this way, the cam track and distributor are moved synchronously with one another, the distributor being displaceable in the longitudinal direction by a drive (not shown further here).
  • the distributor has an annular groove 11 on its outer surface, which is in constant connection with one or more pump piston guide bores 12 radially extending from the bore 2, in which pump pistons 14 are arranged, the end face of which has a working space 15 to the side of the annular groove 11 include.
  • Roller plungers 17, which are in contact with the cam track 9 via rollers 18, are guided coaxially with the pump pistons in an adjacent bore 16 with a larger diameter than that of the guide bore 12. Through relative movement of the same, the pistons are set in a reciprocating, pumping and sucking movement.
  • a first control groove 20 and a second control groove 21 branch off from the annular groove 11, which are worked into the surface of the distributor and initially move away from one another in the manner of a V, starting from the annular groove.
  • the second control groove 21 is longer and merges into an axially parallel part 22, which finally opens into a rectangular control surface 23.
  • In the area of the control surface there are outlets of injection lines 25 into the bore 2 distributed on the circumference of the distributor within a radial plane, the injection lines being arranged in accordance with the number and distribution of the combustion chambers to be supplied of the associated internal combustion engine.
  • a plurality of control openings 27 are provided in the lateral surface of the bore 2 in a radial plane, which are connected via lines 28 to a fuel storage space 30.
  • This is supplied in a known manner by a fuel feed pump, not shown here, with fuel which is kept at a relatively low pressure level.
  • the distribution of the control openings 27, which are distributed around the circumference in accordance with the number of fuel injection lines to be supplied, can be seen in the processing according to FIG. 3. They have an approximately trapezoidal cross-section such that the side flanks are opened or closed across the entire width by the first control groove 20 or second control groove 21, each running at the same angle. As can be seen from the processing in FIG.
  • filling channels 34 with a rectangular inlet cross section 33 on the lateral surface of the bore 2 are also provided in the same number and distribution as the control openings 27 in a second radial plane in the region of the axially parallel part 22 of the second control groove 21 such that the inlet cross-section 33 is closed at the same time as the control opening 27 is closed after passing through the second control groove.
  • the fill channels are also connected to the fuel reservoir 30.
  • the distributor 3 has an end part 35 protruding from the bore 2, on which an annular slide 36 is placed, from the inner bore 37 of which a channel 38 radially leads away, which leads into a cylinder 40 incorporated in an extension 39 of the annular slide.
  • a piston 41 is slidably arranged as a movable wall, which is loaded on its rear side by a return spring 42 and on its front side includes a fuel removal space 43 which is connected to the channel 38.
  • the working path of the piston 41 can be limited by an adjustable pin 45, which is used as an adjustable stop coaxially with the return spring 42.
  • the distributor In the area of the ring slide, the axial position of which can be fixed, the distributor has relief openings in the form of longitudinal grooves 46. the axially parallel according to the development of Figure 3. These longitudinal grooves are also arranged according to the number and distribution of the injection lines 25 on the circumference of the distributor and are connected to one another via radial bores 49, which in turn are connected to the control surface 23 or to the annular groove 11 or the pump working chamber 15 via a pressure channel 50 in the distributor.
  • the injection pump shown in this example is a pump for supplying a six-cylinder internal combustion engine with six injection lines 25.
  • the control surface 23 is in register with one of the injection lines 25, into which fuel is subsequently conveyed.
  • the just effective longitudinal groove 46 connected to the control surface 23 has not yet overlapped with the channel 38 branching off from the inner bore 37.
  • a pre-injection according to FIG. 4 is initially carried out over the area ⁇ , which the distributor must rotate further in order to bring the longitudinal groove 46 into overlap with the channel 38 the cam track rolls off. Apply on the cam track, the stretches have been drawn out for which the pre-injection VS and the main injection HS take place. The injection quantities are plotted against the cam angle under the cam elevation curve. As soon as the longitudinal groove 46 comes into overlap with the channel 38, the pressure in the work space is reduced, fuel flowing into the removal space 43, which subsequently receives the fuel delivered by the pump pistons.
  • the trailing boundary edge of the second control grooves 21 inclined in the direction of rotation can be referred to as the first control edges determining the start of spraying
  • the leading boundary edges of the first control grooves 20 inclined in the opposite direction of rotation can be referred to as the second control edges 52 determining the end of the spray .
  • the distance between the first control edge 51 and the second control edge 52 in the region of the radial plane of the control openings 27 thus determines the injection quantities which, due to the inclined arrangement of the control grooves, can be changed by axially displacing the distributor.
  • the angular distance between the pre-injection VS and HS is influenced by the swallowing volume of the fuel removal space 43, which can be adjusted by adjusting the pin 45.
  • the amount of the pre-injection is, as already mentioned, determined by the angle of rotation ⁇ , which, according to the configuration according to FIG.
  • the relief openings or longitudinal grooves 46 are arranged obliquely to the axis of the distributor, the preferably rectangular configuration of the connecting cross section of the channel 38 being adapted to this oblique position with its lateral orientation.
  • FIG. 2 Another embodiment variant is shown in Figure 2, where the ring slide 36 is rotatable with axial fixation by means of a z. B. electrically controlled actuator 54.
  • the point can be varied at which the relief opening 46 connects the pump work space with the fuel removal space. Additional influences on the pre-injection quantity are possible here as a function of further parameters, regardless of the above-mentioned mode of operation.
  • the relief openings used in a radial piston pump can also be designed as inclined longitudinal grooves 46. Instead of a rotary drive, a stroke drive or an axial displacement of the ring slide is also possible, in which case the longitudinal grooves 46 must be inclined in order to effect the adjustment of the pre-injection quantity.
  • This version can be implemented in reciprocating injection pumps. Which is ultimately also applicable to in-line pumps.
  • FIG. 6 An application of the exemplary embodiment to a series pump or a piston injection pump is shown in FIG. 6.
  • a series injection pump only one pump piston 81 is shown, which is set in a generally known manner by a cam of a cam drive shaft into a reciprocating pumping movement.
  • the pump piston encloses a pump working space 88 in a pump cylinder 82.
  • An injection line leads from the latter via a pressure valve to an injection valve assigned to one of the cylinders of the internal combustion engine.
  • a filling and relief line 85 which is connected to a fuel supply pump, opens into the pump cylinder 82.
  • this filling and relief line is controlled by the end face 86 of the pump piston, which delimits the pump working space 88, or by a control edge on this end face, such that during the suction stroke of the pump piston the working space via the filling and relief line 85 at the bottom dead center at the latest , which is now open, is filled with fuel.
  • the effective delivery stroke of the pump piston begins when this line is closed.
  • the pump piston has, in a known manner, an annular groove 83, the boundary edge of which on the pump working space is designed as an oblique control edge 84.
  • the annular groove 83 is connected to the pump working space 88 via a radial bore 90 extending from an axial bore 89 in the pump piston.
  • the pump piston effectively delivers fuel under high pressure into the injection line until the oblique control edge 84 opens the filling and relief line 85 again, so that the pump working space is relieved via the axial bore 89 and the radial bore 90 to the filling and relief line 85 can take place. This stops the high-pressure delivery and ends the injection.
  • the pump piston has a generally known turning device (not shown further here), with which the assignment of the control edge 84 to the mouth of the filling and relief line 85 can be varied and the effective delivery stroke or the fuel injection quantity can be controlled.
  • a part of the pump piston protrudes into a space 91 inside the fuel injection pump.
  • the pump piston carries a ring slide 92 arranged on it in the same way as the ring slide 36 according to the exemplary embodiment according to FIGS. 1 and 2.
  • a channel 95 which corresponds to the channel 38 in FIG. 3, branches off from the inner bore 93 through which the pump piston is tightly guided .
  • This opens into a fuel removal space 96, which is enclosed in a cylinder 97 by a piston 98 which can be moved there tightly.
  • the piston in turn is loaded on its rear side by a return spring 99 and can move against the force of this spring by an amount ⁇ up to an adjustable stop 100.
  • the pump piston In the area of the inner bore 93, the pump piston has an oblique groove 101, in which the axial bore 89 starting from the end face 86 ends.
  • the ring slide is adjustable in the same way as in the exemplary embodiment according to FIGS. 1 and 2 by an adjusting device and can either be axially displaced, rotated or adjusted in both directions, depending on the configuration of the adjusting device and the parameters to be taken into account.
  • the inclined position of the groove 101 allows, for example, a pure rotation of the ring slide 92, so that a larger or smaller pre-injection stroke a becomes effective by the rotation of the ring slide and / or the rotation of the pump piston according to its load position, until the connection between the channel 95 and the ring groove 101 is manufactured.
  • a load-dependent influence on the injection process can be exerted.
  • this can also be compensated for in a targeted manner by rotating the ring slide accordingly. Additional influences can be made via an axial adjustment of the ring slide.
  • the corresponding stop can be designed as a bolt 103 which plunges coaxially into the cylinder 142 and its immersion depth through a effectrically controlled actuator 104 is controlled. In this way, the amount ⁇ or the distance of the pre-injection from the main injection can be varied during ongoing operation.

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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)
  • High-Pressure Fuel Injection Pump Control (AREA)

Claims (9)

1. Pompe d'injection de carburant pour moteur à combustion interne comportant au moins un piston de pompe (14) qui délimite une chambre de pompage (15) reliée pour chaque course du piston de pompe à une conduite d'injection de carburant (25), chambre qui, au cours de la course d'aspiration du piston de pompe est reliée à une chambre d'alimentation de carburant (30) et qui est reliée à une chambre de prélèvement de carburant (43) à partir d'une course partielle réglable du piston, par l'intermédiaire d'un orifice de décharge (46) pendant les courses de transfert du piston de pompe, piston qui comporte une paroi mobile (41) susceptible de venir contre une butée réglable (47) sous l'effet de la pression du carburant dans la chambre de la pompe et contre une force de rappel, le prélèvement du carburant pendant la course de transfert de la pompe assurant une interruption du transfert à haute pression du carburant et une subdivision de l'injection du carburant en une pré-injection et une injection principale, pompe caractérisée en ce qu'elle comporte un distributeur (3) entraîné en rotation de manière synchrone avec le piston de pompe, distributeur comportant un orifice de distribution (23) qui est permanence en liaison avec la chambre de pompe (15) et qui, lors de la rotation du distributeur peut être relié successivement à chaque course de pompage du piston de pompe à l'une des différentes conduites d'injection de carburant (25) prévues à la périphérie du distributeur et en ce que la chambre de prélèvement de carburant (45) se trouve sur une partie (36) guidée sur le distributeur et qui est déplacée par un moyen d'entraînement de réglage (54) suivant les paramètres de fonctionnement, pour être reliée à un canal (33) partant de la chambre de prélèvement de carburant et dont l'orifice coopère avec un orifice de décharge (46) de la chambre de pompe débouchant dans le distributeur en synchronisme avec l'entraînement du piston de pompe, avec plusieurs orifices de décharge dont le nombre et la répartition correspondent aux courses de transfert de pompe d'au moins un piston de pompe par rotation du distributeur et un orifice du canal (38), ou encore plusieurs orifices de canal (38) correspondant au nombre et à la répartition des courses de transfert de pompe d'au moins un piston de pompe par rotation du distributeur avec un orifice de sortie (46).
2. Pompe d'injection de carburant selon la revendication 1, caractérisée en ce que la partie mobile est réglable dans la direction de déplacement de l'orifice de décharge.
3. Pompe d'injection de carburant selon la revendication 1, caractérisée en ce que la partie mobile est réglable perpendiculairement à la direction de déplacement de l'orifice de décharge.
4. Pompe d'injection de carburant selon la revendication 2 ou la revendication 3, caractérisée en ce que l'orifice de décharge (46) ou l'orifice du canal (38) est en forme de rainure longitudinale.
5. Pompe d'injection de carburant selon la revendication 4, caractérisée en ce que la rainure longitudinale est inclinée par rapport à la direction de déplacement de la partie mobile.
6. Pompe d'injection de carburant selon l'une des revendications précédentes, caractérisée en ce qu'elle est logée dans un boîtier séparément du distributeur et comporte un piston de pompe (14) actionné par un mécanisme d'entraînement à cames (8) entraîné en synchronisme avec l'entraînement du distributeur, le distributeur (3) étant mobile alternativement dans un perçage de guidage (2) et sa surface périphérique comporte au moins une première arête de commande (51) et au moins une seconde arête de commande (52), les arêtes de commande appartenant à au moins une rainure (20, 21) reliées en permanence à la chambre de pompage, rainures qui sont en outre inclinées et qui coopèrent avec des orifices de commande (27) dérivant du perçage de guidage (2), orifices qui sont reliés par une conduite (28) à la chambre d'alimentation en carburant (30) et dont la fermeture par une première arête définit le début du transfert et dont l'ouverture par la seconde arête définit la fin du transfert.
7. Pompe d'injection de carburant selon la revendication 6, caractérisée en ce que le distributeur comporte au moins deux rainures (20, 21, 20', 21') divergentes l'une de l'autre, dont l'une porte la première arête de commande et dont l'autre porte la seconde arête de commande en communiquant en même temps avec l'ouverture de distribution (23) et l'ouverture de décharge (46).
8. Pompe d'injection de carburant selon la revendication 7, caractérisée en ce que la (les) rainure (21, 21') comportant la première arête de commande (51) coopère avec les sections d'entrée (33) de canaux de remplissage (34) réalisées dans la surface extérieure du perçage de guidage (2) suivant le nombre et la répartition des orifices de commande (27) en pouvant être fermées en même temps que les orifices de commande (27) par la première arête de commande.
9. Pompe d'injection de carburant pour moteur à combustion interne comportant au moins un piston de pompe (81) guidé dans un cylindre de pompe (82) et dont la position en rotation est réglable, piston qui définit à chaque course de transfert du piston de pompe une chambre de pompage (88) reliée à la conduite d'injection de carburant et dont la surface périphérique comporte une cavité (83) reliée en permanence à la chambre de pompe (88), l'arête limite (84) de ce piston étant en forme d'arête de commande qui, suivant la position de rotation du piston de pompe, peut être commandée pour avancer ou retarder l'instant au cours de la course du piston de pompe auquel une conduite de remplissage ou de décharge (85) partant du cylindre de pompe (82) est commandée dans le sens de l'ouverture et avec un canal (95) partant de la paroi cylindrique entourant le piston de pompe et dont l'ouverture est prévue dans la paroi cylindrique avec un orifice de sortie (101) prévu dans la surface extérieure du piston de pompe et qui communique en permanence avec la chambre (88) en fonction de la position de rotation du piston pour coïncider en avance ou en retard suivant le profil de la course du piston de la pompe, le canal (95) aboutissant dans une chambre de prélèvement de carburant (95) délimitée par une paroi coulissante sous l'effet de la pression de carburant contre une force de rappel jusqu'à une butée réglable (100, 104), chambre de prélèvement qui, par le prélèvement du carburant pendant la course de transfert du piston assure une interruption du transfert de carburant sous pression élevée dans la conduite d'injection et provoque une subdivision de l'injection de carburant en une pré-injection et une injection principale, pompe caractérisée en ce que la chambre de prélèvement de carburant (96) se trouve dans une partie (92) mobile montée sur la surface extérieure de la partie du piston de pompe sortant du cylindre de pompe, suivant l'entraînement de réglage (54) selon les paramètres de fonctionnement, partie mobile qui présente une paroi cylindrique et est guidée par celle-ci sur la surface extérieure du piston de pompe.
EP84116075A 1984-01-11 1984-12-21 Pompe d'injection de combustible Expired EP0150471B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3400612 1984-01-11
DE3400612 1984-01-11
DE19843444234 DE3444234A1 (de) 1984-01-11 1984-12-05 Kraftstoffeinspritzpumpe
DE3444234 1984-12-05

Publications (3)

Publication Number Publication Date
EP0150471A2 EP0150471A2 (fr) 1985-08-07
EP0150471A3 EP0150471A3 (en) 1985-08-21
EP0150471B1 true EP0150471B1 (fr) 1988-07-27

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ID=25817470

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84116075A Expired EP0150471B1 (fr) 1984-01-11 1984-12-21 Pompe d'injection de combustible

Country Status (3)

Country Link
US (1) US4696271A (fr)
EP (1) EP0150471B1 (fr)
DE (2) DE3444234A1 (fr)

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MX154828A (es) * 1981-12-24 1987-12-15 Lucas Ind Plc Mejoras en un sistema de inyeccion de combustible para un motor de combustion interna
US4505244A (en) * 1982-05-06 1985-03-19 Cummins Engine Company, Inc. Fuel injection system
DE3224152A1 (de) * 1982-06-29 1983-12-29 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4037165A1 (de) * 1990-11-22 1992-05-27 Kloeckner Humboldt Deutz Ag Kraftstoffeinspritzpumpe mit voreinspritzung

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DE3473005D1 (en) 1988-09-01
DE3444234A1 (de) 1985-07-18
EP0150471A3 (en) 1985-08-21
US4696271A (en) 1987-09-29
EP0150471A2 (fr) 1985-08-07

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