EP0461213B1 - Pompe d'injection de carburant pour moteurs a combustion interne - Google Patents

Pompe d'injection de carburant pour moteurs a combustion interne Download PDF

Info

Publication number
EP0461213B1
EP0461213B1 EP90916706A EP90916706A EP0461213B1 EP 0461213 B1 EP0461213 B1 EP 0461213B1 EP 90916706 A EP90916706 A EP 90916706A EP 90916706 A EP90916706 A EP 90916706A EP 0461213 B1 EP0461213 B1 EP 0461213B1
Authority
EP
European Patent Office
Prior art keywords
lubricating oil
claw
coupling
claws
driving
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
EP90916706A
Other languages
German (de)
English (en)
Other versions
EP0461213A1 (fr
Inventor
Helmut Laufer
Wolfgang Fehlmann
Ewald Eblen
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 EP0461213A1 publication Critical patent/EP0461213A1/fr
Application granted granted Critical
Publication of EP0461213B1 publication Critical patent/EP0461213B1/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
    • 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
    • F02M59/44—Details, 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
    • 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
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
    • 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
    • F02M41/10—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 pump pistons acting as the distributor
    • F02M41/12—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 pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/121—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 pump pistons acting as the distributor the pistons rotating to act as the distributor with piston arranged axially to driving shaft
    • 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
    • F02M41/10—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 pump pistons acting as the distributor
    • F02M41/12—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 pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123—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 pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/125—Variably-timed valves controlling fuel passages
    • 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
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the invention is based on a fuel injection pump for internal combustion engines of the type defined in the preamble of claim 1, as e.g. is known from DE-A-3 605 452.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that, due to the engine chamber, which is also only partially filled with lubricant, the limit speed of the cam engine is very high and even in the area of the high drive speed of the drive shaft, which is close to the limit speed, the highly loaded drive surfaces of the drive shaft Claw clutch are adequately lubricated. This drastically increases the service life of the fuel injection pump.
  • the lubricating oil flow forced by the lubricating oil pump from the lubricating oil groove to the lubricating openings in the claw surfaces of the claw coupling is realized in a particularly advantageous manner in that the drive shaft has an axial blind bore which is connected to the lubricating oil groove via a radial bore and is closed on the mouth side is. Oblique bores lead from the blind bore into the drive claws of the drive shaft, which are closed at the end. A distributor bore leads from each oblique bore into those claw surfaces of the drive claws which transmit a torque in the intended direction of rotation of the drive shaft. The mouth openings of the distributor bores in the claw surfaces form the lubricating oil openings.
  • the coupling of the drive claws of the drive shaft to the output claws of the lifting disk connected in a rotationally fixed manner to the distributor piston takes place via a coupling disk designed as a cross disk. So that the claw surfaces of the coupling disk transmitting a drive torque are also sufficiently lubricated, second distributor bores run in the clutch disk, which extend from the claw surfaces of the coupling claws, which bear against the claw surfaces of the drive claws that carry the lubricating oil openings, to the claw surfaces of the same coupling claw that lead in the direction of rotation .
  • first distributor bores lead from all claw surfaces of the drive claws to the oblique bores and form the desired lubricating oil openings with their mouth openings in the claw surfaces.
  • all coupling claws are traversed with second distributor bores, each of which opens into the two claw surfaces delimiting the coupling claw and there in each case a lubricating oil opening realize.
  • all claw surfaces are supplied with lubricating oil, regardless of whether or not they are loaded in the current direction of rotation of the drive shaft. This has the advantage that the fuel injection pump can be used for both directions of rotation of the drive shaft and separate storage for left and right rotation of the drive shaft is avoided.
  • the oil emerging at the claw surfaces is thrown outwards by the centrifugal force and lubricates the rollers of the engine.
  • the lubricating oil circuit is maintained by a feed pump which is driven either by the drive shaft or by a separate electric motor and is generally already present in the oil circuit of the internal combustion engine.
  • the lubricating oil circuit required for the lubrication of the drive shaft and dog clutch can also be used to control the injection adjuster.
  • the control chamber delimited by the injection adjustment piston is connected to the lubricating oil circuit via a throttle and is in turn connected to the engine compartment via an electromagnetically actuated shut-off valve.
  • the electromagnetic check valve is controlled in a clocked manner.
  • the roller ring of the cam engine is installed in such a position that when the injection adjuster is depressurized, the start of delivery, based on the rotational position of the drive shaft, is "early".
  • a pump piston 11 which also serves as a distributor, is set into a reciprocating and simultaneously rotating movement by a drive shaft 12 and with the aid of a cam engine or cam gear 13.
  • a pump working space 14 delimited by the pump piston 11 becomes a Longitudinal distributor groove 15 delivers fuel to one of several pressure channels 16, which are arranged around the pump piston 11 at regular intervals of rotation and each lead to an injection valve assigned to a combustion chamber of the internal combustion engine.
  • the pump work chamber 14 is supplied with fuel by a fuel delivery pump 17, which draws fuel from a fuel tank 18, via a solenoid valve 19.
  • the solenoid valve 19 is open and is switched into its blocking position at the beginning of the delivery or pressure stroke.
  • the drive shaft 12 is mounted in the pump housing 10 by means of two spaced sliding bearings 21, 22 and, like the end of the pump piston 11 remote from the pump working chamber 14, projects into an engine chamber 20 which accommodates the cam gear 13.
  • the cam gear 13 has, in a known manner, a cam or lifting disk 23 which is connected in a rotationally fixed manner to the pump piston 11 and, on its underside facing away from the pump piston 11, carries a number of elevations or cams 24 corresponding to the number of pressure channels 16, which have the same angle of rotation are staggered.
  • a roller ring 25 arranged coaxially to the lifting disk 23 is held in the pump housing 10 so that it can be rotated by a certain angle.
  • rollers 26 are rotatably supported, on which the cam-reinforced underside of the lifting plate 23 is supported under spring force.
  • the roller ring 25 is coupled in a rotationally locking manner to an injection adjusting piston 28 of an injection adjuster 30 via an adjusting bolt 27.
  • the injection adjusting piston 28 delimits a control chamber 29 and is displaced by pressurizing the control chamber 29 against the force of a return spring 31, the roller ring 25 being rotated via the adjusting bolt 27.
  • the cam gear 13 also includes a dog clutch 32, which transmits the rotary movement of the drive shaft 12 to the pump piston 11 irrespective of the axial stroke position of the latter.
  • the claw coupling 32 consists of two drive claws 33, 34 connected to the drive shaft 12 in a rotationally fixed manner, two output claws 35, 36 connected to the lifting disk 23 in a rotationally fixed manner, which in relation to the drive claws 33, 34 in the direction of rotation of the drive shaft 12 are offset by 90 °, and from a cross plate 40 with four segment-like coupling claws 41 - 44, which lie between the drive claws 33, 34 and output claws 35, 36 and produce a rotationally fixed connection between them.
  • the cross disk 40 with the drive claws 33, 34 and output claws 35, 36 engaging in it lies in the interior of the roller ring 25.
  • a lubricating oil circuit has a lubricating oil container 45, from which a lubricating oil pump 46 delivers lubricating oil into a lubricating oil supply line 47.
  • the lubricating oil supply line 47 opens into a lubricating oil groove 48 formed in the pump housing 10 on the drive shaft 12 between the two sliding bearings 21, 22 as an annular groove.
  • a lubricating oil return line 49 connects a drain opening 37 in the engine compartment 20 to the lubricating oil reservoir 45 2/2-way solenoid valve 50 is connected to the lubricating oil supply line 47, to which the control chamber 29 of the hydraulic spray adjuster 30 is also connected via a line section 39.
  • a throttle valve 51 is switched on between the connection point of the power section 39 and the lubricating oil pump 46.
  • a lubricating oil collecting groove 52 is provided, which is sealed on the end face and is connected to the engine compartment 20 via a return bore 53.
  • the lubricating oil supplied by the lubricating oil pump 46 to the lubricating oil groove 48 passes through the two sliding bearings 21, 22 and arrives directly or via the lubricating oil collecting groove 52 and the return bore 53 into the engine compartment 20.
  • Its drain opening 37 is arranged such that the engine compartment 20 is only partially filled with lubricating oil is.
  • the speed limit of the drive shaft 12 is defined as the limit speed at which the lifting disk 23 lifts off the rollers 26 of the roller ring 25 and the exact lifting function of the pump piston 11 is no longer guaranteed.
  • a lubricating oil flow from the lubricating oil groove 48 through the drive shaft 12 is provided directly to the claw clutch 32, which exits via lubricating oil openings in the claw surfaces of the claw clutch 32 and into the engine room 20 flows away. It is sufficient to provide lubricating oil openings in those claw surfaces of the claw clutch 32 that have to transmit the torque in the fixed direction of rotation of the drive shaft 12.
  • an axial blind bore 54 is introduced into the drive shaft 12 from the end face carrying the drive claws 33, 34 to realize this lubricating oil flow, which near the bottom of the bag via a radial bore 55 in the drive shaft 12 with the Lubricating oil groove 48 is connected and is closed on the end face of the drive shaft 12 by a ball 56.
  • an oblique bore 57 or 58 is introduced, which opens into the blind bore 54 and is closed at the end by a ball 59 or 60.
  • a first distributor bore 61 or 62 From each oblique bore 57, 58, a first distributor bore 61 or 62 (FIGS.
  • the distributor bore 61 can be seen extended in the sectional view of the drive claw 34 in FIG. 4, while it is indicated in dashed lines in the sectional view of the cross disk 40 according to FIG. 5.
  • the mouth openings of the first distributor bores 61, 62 form the aforementioned lubricating oil openings 64, 65 in the claw surfaces 33a and 34a.
  • second distributor bores 66, 67 lead to the other claw surfaces 41a, 43a of the coupling claws 41, 43.
  • part of the lubricating oil emerging at the lubricating oil openings 64, 65 flows to the claw surfaces 41 a, 43 a, which transmit a torque to the output claws 35, 36 in the direction of rotation 63 of the drive shaft 12 and flows there through the further lubricating oil openings 68,69 forming mouths of the second distributor bores 66,67 between the contact surfaces of coupling claws 41,42 and output claws 35,36 of the lifting disk 23.
  • This construction ensures that the claw surfaces 33a, 34a, 41a, 43a of the claw coupling transmit a torque 32 are always adequately supplied with lubricating oil.
  • the hydraulic spray adjuster 30 is controlled by means of the lubricating oil circuit to adjust the start of the stroke of the pump piston 11 and thus the start of delivery relative to the rotational position of the drive shaft 12.
  • the solenoid valve 50 is actuated in a clocked manner in such a way that the start of delivery is adjusted to "early" at full load and to "late” at partial load.
  • the roller ring 25 Since there is no engine oil pressure at the start of the internal combustion engine, the roller ring 25 is installed with respect to the rotational position of the drive shaft 12 in such a spatial installation position that when the control chamber 29 of the injection adjuster 30 is depressurized, the roller ring 25 assumes such a position that when the internal combustion engine starts cold, delivery begins Pump piston 11 is at "early”.
  • the spray adjustment piston 28 can thus be adjusted with the engine oil pressure from the idling speed.
  • the required late position is achieved Moving the start of delivery determined by closing the solenoid valve 19 with respect to the rotational position of the pump piston 11 is reached.
  • the invention is not restricted to the exemplary embodiment described above.
  • the lubricating oil supply line 47 can connect the feed pump 46 directly to the lubricating oil groove 48.
  • the throttle valve 51 is then connected upstream of the common connection point from line section 39 to the control chamber 29 of the spray adjuster 30 and from solenoid valve 50 on the lubricating oil supply line 47 to the lubricating oil supply line 47.
  • the lubricating oil container 45 can be omitted if the feed pump 46 is connected directly to the lubricating oil return line 49 on the input side. In this case, the engine room 20 takes over the function of the lubricating oil container 45. The engine room 20 is then incorporated into the engine oil circuit of the internal combustion engine by a separate inlet and a separate outlet. The feed pump 46 is expediently driven by the drive shaft 12. The speed-dependent lubricating oil pressure in the engine compartment 20 can also be controlled by means of a pressure control valve.

Landscapes

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

Abstract

Une pompe d'injection de carburant pour moteurs à combustion interne présente un corps de pompe (10), un piston distributeur (11) mené de manière axiale et rotative, un arbre de commande (12) tournant dans le corps de pompe (10), un équipage mobile (13) accouplant l'arbre de commande (12) au piston distributeur (11) avec unaccouplement à griffes (32) et avec un disque à cames (23) roulant sur une bague porte-galets (25) munie de cames (26) ainsi qu'un circuit de graissage avec une arrivée d'huile de graissage (47) débouchant dans une rainure de graissage (48) et une conduite de retour (49) pour l'huile de graissage provenant du compartiment (20) partiellement rempli d'huile de l'équipage mobile. Pour assurer une alimentation suffisante en huile de graissage des surfaces d'entraînement hautement sollicitées de l'accouplement à griffes (32), un flux d'huile passe à travers l'arbre de commande (12) depuis la rainure de graissage (48) jusque dans l'accouplement à griffes (32) et sort par les orifices de graissage (64, 65, 68, 69) dans le compartiment (20) de l'équipage mobile dans au moins les surfaces à griffes de l'accouplement (32) qui transmettent une force de rotation.

Claims (6)

  1. Pompe d'injection de carburant pour moteurs à combustion interne avec un carter de pompe (10), avec un piston de distribution (11) pouvant tourner dans le carter de pompe (10) et pouvant coulisser axialement avec un arbre d'entraînement (12), monté de façon à tourner dans le carter de pompe, pour au moins le piston de distribution (11), avec un mécanisme d'entraînement (13) accouplant l'arbre d'entraînement au piston de distribution (11), mécanisme qui est disposé dans une chambre (20) de mécanisme d'entraînement et pour produire un mouvement de rotation du piston de distribution présente un accouplement à crabots (32) et pour produire un mouvement de coulissement axial du piston de distribution présente une bague à rouleaux (25) avec des rouleaux (26) et un disque à cames (23) relié au piston de distribution, disque qui s'appuie par sa face frontale portant des cames (24) sur les rouleaux (26) de la bague à rouleaux (25) en étant comprimé par un ressort et avec une conduite d'alimentation d'huile de lubrification (47) qui débouche via une rainure d'huile de lubrification (48) entourant l'arbre d'entraînement et un alésage (54) dans l'arbre d'entraînement (12) dans la chambre (20) du mécanisme d'entraînement et présente une ouverture d'écoulement de l'huile de lubrification (37) partant de la chambre (20) du mécanisme d'entraînement, pompe d'injection dans laquelle à travers l'alésage (54) dans l'arbre d'entraînement (12), il y a un écoulement d'huile de lubrification depuis la rainure d'huile de lubrification (48) vers l'accouplement à crabots (32), pompe d'injection de carburant caractérisée en ce que via des orifices d'huile de lubrification (64, 65, 68, 69) dans au moins celles des surfaces (33a, 34a, 41a, 43a) des crabots d'entraînement (33, 34) reliés de façon solidaire en rotation à l'arbre d'entraînement, de l'accouplement à crabots (32), qui transmettent une force de rotation, l'écoulement de l'huile de lubrification sort dans la chambre (20) du mécanisme d'entraînement et pour produire le flux de l'huile de lubrification la conduite d'alimentation en huile de lubrification (47) est raccordée à une pompe d'huile de lubrification entraînée par la pompe d'injection.
  2. Pompe d'injection de carburant selon la revendication 1, caractérisée en ce que l'accouplement à crabots (32) présente au moins deux crabots d'entraînement (33, 34) reliés de façon solidaire en rotation à l'arbre d'entraînement (12), au moins deux crabots entraînés (35, 36), disposés de façon décalée dans l'espace par rapport aux précédents, reliés de façon solidaire en rotation au disque à cames (23), et un disque d'embrayage (40) venant en prise entre les crabots d'entraînement et les crabots entraînés (33, 34, 35, 36) avec les crabots d'accouplement (41 à 44), en ce que l'arbre d'entraînement (12) présente un trou borgne axial (54), qui via un alésage radial (55) est en liaison avec la rainure d'huile de lubrification (48) et est fermé à l'extrémité, située du côté de l'accouplement, de l'arbre d'entraînement (12), en ce qu'à partir des crabots d'entraînement (33, 34) on ménage respectivement un trou oblique (57, 58) allant jusqu'au trou borgne (54) et on ferme ce trou oblique du côté frontal, en ce que des premiers alésages de distribution (61, 62) mènent des trous obliques (57, 58) aux surfaces (33a, 34a) des crabots d'entraînement (33, 34) se trouvant en avant dans le sens de rotation de l'arbre d'entraînement (12) et forment à cet endroit du côté de la sortie les orifices d'huile de lubrification (64, 65) et en ce qu'à partir des surfaces de crabots (41b, 43b) reposant sur les surfaces de crabots d'entraînement (33a, 34a) portant les orifices d'huile de lubrification (64, 65) des alésages de distribution (66, 67) conduisent aux surfaces de crabots (41a, 43a) du disque d'embrayage (40), reposant dans le sens de rotation sur les surfaces de crabots entraînés (35, 36) du disque à cames (23) et forment à cet endroit du côté de la sortie les orifices d'huile de lubrification (68, 69).
  3. Pompe d'injection de carburant selon la revendication 2, caractérisée en ce que d'autres premiers alésages de distribution (70, 71) mènent des alésages obliques (57, 58) en plus aux autres surfaces de crabots d'entraînement (33, 34) et forment à cet endroit d'autres orifices d'huile de lubrification situés du côté de la sortie et en ce qu'à partir des surfaces de crabots du disque d'embrayage (40), qui sont tournées vers ces surfaces de crabots portent les autres orifices d'huile de lubrification, d'autres alésages de lubrification (72, 73) mènent aux autres surfaces de crabots du disque d'embrayage (40) et débouchent à cet endroit du côté de la sortie dans d'autres orifices d'huile de lubrification.
  4. Pompe d'injection de carburant selon l'une des revendications 1 à 3, caractérisée en ce que l'arbre d'entraînement (12) est monté dans deux paliers lisses (21, 22) disposés à distance l'un de l'autre et en ce que la rainure d'huile de lubrification (48) est disposée entre les deux paliers lisses (21, 22).
  5. Pompe d'injection de carburant selon l'une des revendications 1 à 4, caractérisée en ce qu'il est prévu un dispositif hydraulique de réglage de l'injection (30) qui présente un piston (28) de réglage de l'injection délimitant une chambre de commande (29) avec un ressort de rappel (31) pour déplacer la bague à rouleaux (25) d'une manière telle que le début de la course du piston de distribution (11) soit déplacé par rapport à la position angulaire de l'arbre d'entraînement (12) vers "avance", en ce que la chambre de commande (29) est raccordée d'une part par un étranglement (51) à la conduite d'alimentation en huile de lubrification (47) et d'autre part par un distributeur 2/2 voies (50) à la chambre (20) du mécanisme d'entraînement, qui est commandé pour établir une pression d'huile de lubrification fonction de la vitesse de rotation de façon synchronisée dans la chambre de commande (29).
  6. Pompe d'injection de carburant selon la revendication 5, caractérisée en ce que la bague à rouleaux (25) est montée dans une position telle dans le carter de pompe (10) que quand la chambre de commande (29) du dispositif de réglage (30) de l'injection est sans pression le début du refoulement du piston de distribution (11) en cas de démarrage à froid du moteur à combustion interne soit sur "avance" par rapport à la position angulaire de l'arbre d'entraînement (12).
EP90916706A 1989-12-29 1990-11-24 Pompe d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0461213B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3943299 1989-12-29
DE3943299A DE3943299A1 (de) 1989-12-29 1989-12-29 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0461213A1 EP0461213A1 (fr) 1991-12-18
EP0461213B1 true EP0461213B1 (fr) 1993-11-03

Family

ID=6396608

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90916706A Expired - Lifetime EP0461213B1 (fr) 1989-12-29 1990-11-24 Pompe d'injection de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US5146895A (fr)
EP (1) EP0461213B1 (fr)
JP (1) JP3051164B2 (fr)
DE (2) DE3943299A1 (fr)
WO (1) WO1991010063A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19739653A1 (de) * 1997-09-10 1999-03-11 Bosch Gmbh Robert Verfahren zum Erzeugen von unter Hochdruck stehendem Kraftstoff sowie System zur Kraftstoffhochdruckerzeugung
DE19801355B4 (de) * 1998-01-16 2004-04-08 Robert Bosch Gmbh Hochdruckpumpe zur Kraftstoffversorgung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen
DE10155522C1 (de) * 2001-11-12 2003-04-03 Bosch Gmbh Robert Verteilereinspritzpumpe mit vorgespanntem Kraftübertragungselement
JP3852753B2 (ja) * 2001-12-04 2006-12-06 株式会社デンソー 燃料噴射ポンプ
US6668797B2 (en) * 2002-05-13 2003-12-30 Advanced Vehicle Technologies Fuel injection pump system
DE102005033638A1 (de) * 2005-07-19 2007-01-25 Robert Bosch Gmbh Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine
DE102010041429A1 (de) 2010-09-27 2012-03-29 Robert Bosch Gmbh Kreuzscheibenkupplung sowie Kraftstoffhochdruckpumpe mit einer Kreuzscheibenkupplung
JP6411313B2 (ja) * 2015-11-26 2018-10-24 ヤンマー株式会社 燃料噴射ポンプ
CN117738826B (zh) * 2024-02-19 2024-05-03 江苏中奕和创智能科技有限公司 一种带有控油组件的柴油发电机

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1413117A (en) * 1921-07-09 1922-04-18 Higgins Eugene Shaft coupling
US2670684A (en) * 1950-01-21 1954-03-02 Volvo Ab Fuel injection device for internalcombustion engines
GB1562019A (en) 1977-03-18 1980-03-05 Davy Loewy Ltd Splinedarticulated coupling
US4493623A (en) * 1983-02-22 1985-01-15 Chandler Evans Inc. Oil lubricated main drive shaft for fuel pump
DE3410911A1 (de) * 1983-04-06 1984-10-11 Ernst Dipl.-Ing. 4600 Dortmund Korthaus Kolbenpumpe
JPH0212299Y2 (fr) * 1984-12-28 1990-04-06
JPH034780Y2 (fr) 1985-02-22 1991-02-07
DE3704578A1 (de) * 1987-02-13 1988-08-25 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5000668A (en) * 1988-04-27 1991-03-19 Diesel Kiki Co., Ltd. Distribution-type fuel injection pump
DE3819996A1 (de) * 1988-06-11 1989-12-14 Bosch Gmbh Robert Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen

Also Published As

Publication number Publication date
DE3943299A1 (de) 1991-07-04
US5146895A (en) 1992-09-15
DE59003366D1 (de) 1993-12-09
JPH04504748A (ja) 1992-08-20
WO1991010063A1 (fr) 1991-07-11
EP0461213A1 (fr) 1991-12-18
JP3051164B2 (ja) 2000-06-12

Similar Documents

Publication Publication Date Title
EP0335083B1 (fr) Dispositif de déplacement angulaire relatif entre deux arbres en liaison d'entraînement
EP0571472B1 (fr) Systeme hydraulique
DE19860025B4 (de) Ventilsteuerzeitenregelvorrichtung
EP0295420B1 (fr) Pompe d'injection de combustible
EP1573176A1 (fr) Moteur a combustion interne comportant un dispositif de reglage hydraulique de l'angle de rotation de l'arbre a cames par rapport au vilebrequin ainsi qu'une pompe a vide destinee a un servorecepteur notamment con u pour un amplificateur de freinage
EP0461213B1 (fr) Pompe d'injection de carburant pour moteurs a combustion interne
EP0489740B1 (fr) Pompe d'injection distributrice de carburant pour moteurs a combustion interne
DE19827930C2 (de) Ventilsteuerungsvorrichtung
EP0642430B1 (fr) Pompe hydraulique entrainee par un moteur a combustion interne
DE4210580C2 (de) Vorrichtung zur Winkelverstellung der Nockenwelle einer Brennkraftmaschine
DE3622335C2 (de) Antriebseinrichtung für Nebenaggregate einer Brennkraftmaschine
EP0153982B1 (fr) Machine à piston, particulièrement pompe à piston
DE3911160C2 (de) Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE3928219A1 (de) Kraftstoff-einspritzpumpe mit verteilerfunktion
DE69406235T2 (de) Kraftstoffpumpe
WO1991002897A1 (fr) Pompe d'injection de carburant pour moteurs a combustion interne
EP0323591A2 (fr) Dispositif de réglage de l'injection à 2 points
DE4137073A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
EP0369461A1 (fr) Moteur à combustion interne avec au moins un tiroir rotatif par cylindre
EP0090797B1 (fr) Système de réglage électro-hydraulique du début de refoulement d'une pompe d'injection d'un moteur à combustion interne à injection
EP0615063B1 (fr) Pompe à injection de combustible
DE3943246A1 (de) Kraftstoffeinspritzpumpe
DE1940995A1 (de) Brennstoffeinspritzpumpe mit Verteiler fuer Brennkraftmaschinen
DE2365317C3 (de) Einspritzzeitpunkt-Verstellvorrichtung einer Brennstoffeinspritzpumpe für Brennkraftmaschinen
DE4423133C2 (de) Betätigungseinheit für eine Verstellvorrichtung, vorzugsweise für eine Ventilhubverstelleinrichtung von Kraftfahrzeugen

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

17P Request for examination filed

Effective date: 19910716

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

RAP3 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ROBERT BOSCH GMBH

17Q First examination report despatched

Effective date: 19920331

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: 59003366

Country of ref document: DE

Date of ref document: 19931209

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

Effective date: 19931112

ITF It: translation for a ep patent filed
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: GB

Payment date: 20011105

Year of fee payment: 12

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

Ref country code: FR

Payment date: 20011120

Year of fee payment: 12

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

Ref country code: DE

Payment date: 20011227

Year of fee payment: 12

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: GB

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

Effective date: 20021124

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: 20030603

GBPC Gb: european patent ceased through non-payment of renewal fee
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: 20030731

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: 20051124