EP0167697B1 - Mécanisme d'avance de l'injection pour des pompes à injection de moteurs à combustion - Google Patents

Mécanisme d'avance de l'injection pour des pompes à injection de moteurs à combustion Download PDF

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Publication number
EP0167697B1
EP0167697B1 EP85100357A EP85100357A EP0167697B1 EP 0167697 B1 EP0167697 B1 EP 0167697B1 EP 85100357 A EP85100357 A EP 85100357A EP 85100357 A EP85100357 A EP 85100357A EP 0167697 B1 EP0167697 B1 EP 0167697B1
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EP
European Patent Office
Prior art keywords
pressure
injection timing
piston
timing adjuster
hydraulic
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
EP85100357A
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German (de)
English (en)
Other versions
EP0167697A1 (fr
Inventor
Albert Nolte
Joachim Altdorf
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
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Publication of EP0167697A1 publication Critical patent/EP0167697A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/16—Adjustment of injection timing
    • F02D1/18—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse
    • F02D1/183—Adjustment of injection timing with non-mechanical means for transmitting control impulse; with amplification of control impulse hydraulic

Definitions

  • the invention relates to a fuel injection timing adjuster according to the preamble of claim 1.
  • a generic injection timing adjuster is known from GB-A 2 029 934.
  • This injection timing adjuster has its own hydraulic pump, which is followed by a hydraulic control valve that can alternately control the hydraulic control fluid in two different pressure chambers. Depending on the position of the control valve and the consequently pressurized pressure chamber, an injection timing adjustment is achieved by moving a helical adjustment device between the primary part and the secondary part.
  • a disadvantage of this injection timing adjuster is the complex hydraulic adjustment device, which has a separate high-pressure pump and a complicated control valve.
  • Another injection timing adjuster (US-A 3,401,572) also requires a hydraulic high-pressure pump, from which the hydraulic fluid must be supplied to the injection timing adjuster in a controlled manner.
  • the hydraulic fluid only adjusts the injection time in one direction, and the return adjustment is carried out by a spring alone. This results in additional problems in coordinating the pressure forces required for the adjustment.
  • the invention is based on the object of proposing a separate injection timing adjuster, which converts the specified size of the injection timing of a control device in a simple manner without retroactive effect on or from the attacking drive torques into an angle of rotation of the injection pump camshaft relative to the drive part.
  • the injection timing distributor should do without complex additional units necessary for adjustment.
  • the primary part is moved on the secondary part by a pressure piston which is acted upon by a pressure medium.
  • the pressure piston is firmly connected to the primary part and forms two pressure chambers in the secondary part, the outflows of which are controlled by a hydraulic control pin.
  • the hydraulic control bolt is controlled directly and without feedback by control electronics.
  • the pressure medium which can be engine oil or fuel of the internal combustion engine in particular and which is under low pressure, is supplied to the two pressure chambers via two check valves.
  • the use of a hydraulic transmission element is particularly useful in connection with the drive of an injection pump.
  • strong alternating torques arise in the entire drive train of the injection pump, which generate a kind of pulsating movement between the drive and output parts of the injection timing adjuster. If the drive part (primary part) is now to be rotated relative to the output part (secondary part), it is not necessary, if these alternating torques are used appropriately, to adjust against the output torque of the injection pump, i. H.
  • the provision of a comparatively low hydraulic medium pressure is sufficient to carry out the adjustment.
  • the injection timing adjuster does not take the force required for the adjustment from the hydraulics, but advantageously adjusts itself self-amplifyingly with the energy of the alternating torques.
  • the control electronics determine the axial position of the pressure piston, and thus also the axial position of the primary part on the secondary part, by opening the discharge opening of the pressure chambers via the hydraulic control pin.
  • An axial displacement of the hydraulic control pin always follows the axial displacement of the primary part and thus the adjustment of the injection timing. Since the displacement of the hydraulic control pin advantageously corresponds exactly to the displacement of the primary part, a return of the controlled variable, namely the angle of rotation of the secondary part to the primary part, is not absolutely necessary, but can also have a positive influence on the quality of the controlled variable.
  • Fig. 1 the individual components of a generic injection timing adjuster are shown schematically, arrows indicating the operative connection between them.
  • the injection timing adjuster is arranged directly on the injection pump camshaft 5 with a secondary part 4.
  • the hub-shaped secondary part 4 is provided with a ring gear-like primary part 3, which is angularly movable and axially displaceable with the secondary part 4 in engagement with helical teeth 9.
  • the primary part 3 can be driven by a driving gear 49 via its external teeth and drives on the other hand, via the secondary part 4, the injection pump camshaft 5.
  • a toothed disk 8 is in turn firmly connected to the secondary part 4.
  • a mark is made both on the ring gear of the primary part 3 and on the toothed disk 8.
  • Two electrical pulse generators 6 and 7 register each passage of the markings and in each case send an electrical pulse to control electronics 1. These pulses give control electronics 1 both information about the speed of the injection pump camshaft 5 and information about the exact instantaneous angle of rotation of the secondary to the primary part of the injection timing adjuster.
  • the two further arrows leading into the control electronics 1 are intended to indicate further operating parameters of the internal combustion engine, which have been converted to electrical quantities by suitable sensors and / or sensors.
  • the control electronics 1 processes all incoming quantities to an electrical setpoint of the angle of rotation of the secondary part to the primary part, ie to a setpoint of the injection time. This electrical signal must be converted into a displacement path of a connecting part 10 with the aid of a converter 2.
  • a hydraulic control pin is axially displaced, for which purpose the electrical signal from the control electronics 1 is converted with a known electrical auxiliary device into a feedback-free displacement path which actuates the hydraulic control pin largely without force.
  • the axial displacement of the connecting part 10 leads through the helical toothing 9 to a change in the angular position of the secondary to the primary part, whereby the control loop of the injection point adjuster is closed via the feedback to the pulse generators 6 and 7.
  • the adjustment of the rotational angle position of the secondary part 4 to the primary part 3 is provided with a hydraulic system.
  • the primary part 3 is arranged on the secondary part 4 axially displaceable with a helical toothing 9.
  • the secondary part 4 is provided with a ring gear 8, two pulse generators 6 and 7 forwarding the rotational angle position of the secondary part 4 to the primary part 3 to separate control electronics 1 by means of electrical pulses.
  • a pressure piston 29 is arranged centrally in the inner bore. This pressure piston 29 forms, with the end of the injection pump camshaft 5 and an annular extension of the secondary part 4, two pressure chambers 36 and 37.
  • the pressure piston 29 is designed as an ordinary differential piston 48 with a piston rod 39.
  • the pressure piston 29 is led out of the secondary part 4 on the cylindrical sealing surface 38 with its piston rod 39 in a pressure-tight manner and is connected in a stationary manner to the connecting part 10 via a screw connection of a nut 19 in a central bore 18 of the same.
  • an axial displacement of the pressure piston 29 leads to the same displacement of the primary part 3 on the secondary part 4.
  • a hydraulic control pin 31 is provided in a bore 30 which is arranged axially parallel in its center.
  • This hydraulic control pin has a drain hole 32, two control edges 33 and two connecting drain holes 47.
  • the two pressure chambers 36, 37 are connected via holes 34 to the hole 30 of the hydraulic control bolt 31.
  • the two control edges 33 of the hydraulic control bolt 31 control the outflow of the two pressure chambers 36 and 37 via the connecting bores 34 fed to the two pressure chambers 36 and 37 via two check valves 45. Furthermore, the pressure piston 29 is acted upon in the axial direction by a spring force (spring 35).
  • the injection timing adjuster does not take the force required for the adjustment from the hydraulics, but advantageously adjusts itself self-amplifying with the energy of the alternating torques.
  • an expensive high-pressure hydraulic pump is superfluous and, in particular, the use of the pressurized engine oil of the internal combustion engine as a hydraulic medium is suggested.
  • the primary part 3 is driven from the outside and in turn drives the secondary part 4 via the helical teeth 9.
  • the connecting part 10 and the pressure piston 29 rotate accordingly.
  • the hydraulic control bolt closes with its control edges 33 all connecting bores 34 to the two pressure chambers 36 and 37.
  • no hydraulic fluid can flow into the two pressure chambers 36 and 37 via the two check valves 45, the pressure piston 29 is therefore fixed in its axial position with respect to the secondary part.
  • the control electronics 1 specifies an axial displacement of the hydraulic control pin 31.
  • the electrical impulses or signals of the control electronics 1 from one Known converter implemented in a displacement path proportional to the electrical signals and feedback-free.
  • a feedback of the angle of rotation position of the secondary part 4 to the primary part 3 via electrical pulse generators 6 and 7 can be omitted, since the axial position of the hydraulic control pin 31 uniquely specifies the size of the change in the angle of rotation position. In some cases, however, in the interest of the control quality, it may prove advantageous to feed back the angle of rotation position.
  • the hydraulic control pin 31 To change the injection timing in the other direction, the hydraulic control pin 31 must be shifted in the opposite direction. The process then takes place accordingly on the second control edge 33 of the hydraulic control pin 31.
  • the pressure piston 29 is still acted upon by a spring force of a spring 35.
  • This spring force is not necessary for the operation of the injection timing adjuster, but it ensures that a well-defined value of the injection timing is reached when the internal combustion engines are switched on.

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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 (12)

1. Mécanisme d'avance de. l'injection pour une pompe à injection de moteur à combustion interne, mécanisme monté sur l'entraînement de la pompe à injection, et constitué par un élément primaire (3) servant à entraîner et un élément secondaire (4) entraîné, relié à l'arbre à cames (5) de la pompe à injection, la transmission de force mécanique de l'élément primaire (3) à l'élément secondaire (4) s'effectuant, par l'intermédiaire d'une denture hélicoïdale (9), et un dispositif de réglage hydraulique pour déplacer l'un de ces éléments (3, 4) étant prévu en vue d'obtenir un réglage de l'angle de rotation entre l'élément primaire (3) et l'élément secondaire (4), dispositif de réglage qui est constitué par un piston hydraulique (29) agissant sur un élément et qui peut sous l'effet d'une action de pression sur une première chambre de compression (36), être déplacé dans un sens de réglage, et sous l'effet d'une action de pression sur une seconde chambre de compression (37), être déplacé dans l'autre sens de réglage, et une soupape de commande hydraulique étant prévue pour commander le déplacement dans les sens de réglage, soupape qui s'actionne en fonction de la grandeur prescrite pour la position de l'angle de rotation et déterminée par un dispositif de réglage électrique, cette grandeur prescrite pour la position de l'angle de rotation étant définie au moins d'après la vitesse de rotation de l'élément primaire ou du vilebrequin, détectée par des générateurs d'impulsions, mécanisme d'avance de l'injection caractérisé en ce que les chambres de compression (36, 37) sont alimentées en commun, par l'intermédiaire de soupapes anti-retour (45), en utilisant un afflux d'agent hydraulique, avec des agents sous pression de faible pression, et la soupape de commande (31) commande les moyens d'écoulement (34) des chambres de compression (36, 37).
2. Mécanisme d'avance de l'injection selon la revendication 1 caractérisé en ce que le piston est un piston de pression (29) à double effet, relié rigidement à l'élément primaire (3), et qui dans l'élément secondaire délimite avec celui-ci deux chambres de compression (36, 37).
3. Mécanisme d'avance de l'injection selon la revendication 1 ou 2, caractérisé en ce que la soupape de commande est un boulon de commande hydraulique (31) monté dans un alésage à trou borgne (30) au centre du piston de pression (29), et qui peut s'actionner de l'extérieur grâce à un alésage (18) ménagé dans l'élément primaire (3).
4. Mécanisme d'avance de l'injection selon l'une des revendications 1 à 3, caractérisé en ce que le piston de pression (29) est constitué par un piston différentiel (45) et une tige de piston (39), ce piston de pression délimitant deux chambres de compression (36, 37) de forme annulaire.
5. Mécanisme d'avance de l'injection selon l'une des revendications 1 à 4, caractérisé en ce que le piston de pression (29) fait saillie de l'élément secondaire (4) par sa tige de piston (39) cylindrique, étanchée.
6. Mécanisme d'avance de l'injection selon l'une des revendications 1 à 5, caractérisé en ce que le piston de pression (29) est chargé, sur un côté, par un ressort (35).
7. Mécanisme d'avance de l'injection selon l'une des revendications 1 à 6, caractérisé en ce que l'amenée de l'agent sous pression aux deux chambres de compression (36, 37) est prévue par des alésages creux (41) ménagés dans le carter (11) du mécanisme d'avance de l'injection, par les paliers (42) de l'arbre à cames (5) de la pompe à injection, et par des alésages creux (44) ménagés dans l'arbre à cames (5) de la pompe à injection.
8. Mécanisme d'avance de l'injection selon l'une des revendications 1 à 7, caractérisé en ce que, comme agent sous pression, on peut utiliser le lubrifiant de fonctionnement du moteur à combustion interne ou son carburant.
9. Mécanisme d'avance de l'injection selon l'une des revendications 1 à 8, caractérisé en ce que le boulon de commande hydraulique (31) est pourvu d'un alésage creux axial (32), de deux bords de commande (33), et au moins d'un alésage d'écoulement (47) relié à l'alésage creux (32).
10. Mécanisme d'avance d'injection selon l'une des revendications 1 à 9, caractérisé en ce que le boulon de commande hydraulique (31), dans sa position de repos, ferme aussi bien l'ouverture d'écoulement (34) de la première chambre de compression (36) que l'ouverture d'écoulement (34) de la seconde chambre de compression (37).
11. Mécanisme d'avance de l'injection selon l'une des revendications 1 à 10, caractérisé en ce que lorsque le boulon de commande hydraulique (31) est déplacé dans un sens, l'ouverture d'écoulement (34) d'une chambre de compression est libérée par un bord de commande (33), tandis que l'ouverture d'écoulement (34) de l'autre chambre de compression reste fermée, et inversement.
12. Mécanisme d'avance de l'injection selon l'une des revendications 1 à 11, caractérisé en ce que le boulon de commande hydraulique (31) peut se commander par le dispositif électronique de réglage, par l'intermédiaire d'un convertisseur (2) transformant le signal électrique en une course proportionnelle, la position du piston de pression (29) étant déterminée de façon fixe d'après la position du boulon de commande hydraulique (31).
EP85100357A 1984-05-17 1985-01-15 Mécanisme d'avance de l'injection pour des pompes à injection de moteurs à combustion Expired - Lifetime EP0167697B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3418321 1984-05-17
DE19843418321 DE3418321A1 (de) 1984-05-17 1984-05-17 Einspritzzeitpunktversteller einer einspritzpumpe fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0167697A1 EP0167697A1 (fr) 1986-01-15
EP0167697B1 true EP0167697B1 (fr) 1990-01-24

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EP85100357A Expired - Lifetime EP0167697B1 (fr) 1984-05-17 1985-01-15 Mécanisme d'avance de l'injection pour des pompes à injection de moteurs à combustion

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EP (1) EP0167697B1 (fr)
JP (1) JPS60249629A (fr)
DE (2) DE3418321A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3830382C1 (fr) * 1988-09-07 1990-01-18 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE3929620A1 (de) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Verstellanordnung fuer eine vorrichtung zur drehwinkelverstellung einer welle relativ zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine
CN113738548B (zh) * 2021-07-27 2022-06-03 东风汽车集团股份有限公司 进气相位传感器失效后的高压油轨压力控制方法及***

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FR895657A (fr) * 1942-06-17 1945-01-31 Heberlein & Co Ag Dispositif modifiant le calage entre un arbre menant et un arbre mené
US3401572A (en) * 1966-09-12 1968-09-17 Caterpillar Tractor Co Compact speed sensitive timing device for internal combustion engines
FR1527768A (fr) * 1966-11-15 1968-06-07 Bosch Gmbh Robert Perfectionnements apportés aux pompes d'injection à pistons radiaux et à avance à l'injection variable
US3603112A (en) * 1968-09-28 1971-09-07 Fiat Spa Injection pump for internal combustion engines
IT965124B (it) * 1972-08-25 1974-01-31 Fiat Spa Variatore d anticipo a comando elet tronico per pompe d iniezione
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GB2029934B (en) * 1978-05-30 1982-12-22 Sanwa Seiki Mfg Co Ltd Injection timing control systems for fuel injection pump for engine
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DE3101167A1 (de) * 1981-01-16 1982-08-26 Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh, 7990 Friedrichshafen "elektronisch gesteuerter spritzversteller"
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JPS5964441U (ja) * 1982-06-30 1984-04-27 株式会社小松製作所 蓄圧電子噴射システムの噴射タイミングコントロ−ル装置
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DE3313733C2 (de) * 1983-04-15 1986-09-11 Klöckner-Humboldt-Deutz AG, 5000 Köln Einspritzzeitpunktversteller für eine Einspritzpumpe einer Brennkraftmaschine

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Title
Patents Abstracts of Japan,vol.8, no.136(M-304)(1573), 23.06.1984 *

Also Published As

Publication number Publication date
JPS60249629A (ja) 1985-12-10
DE3418321A1 (de) 1986-04-24
EP0167697A1 (fr) 1986-01-15
DE3575588D1 (de) 1990-03-01

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