EP0178441B1 - Régulateur de la vitesse de rotation pour pompes d'injection d'essence - Google Patents

Régulateur de la vitesse de rotation pour pompes d'injection d'essence Download PDF

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Publication number
EP0178441B1
EP0178441B1 EP85111138A EP85111138A EP0178441B1 EP 0178441 B1 EP0178441 B1 EP 0178441B1 EP 85111138 A EP85111138 A EP 85111138A EP 85111138 A EP85111138 A EP 85111138A EP 0178441 B1 EP0178441 B1 EP 0178441B1
Authority
EP
European Patent Office
Prior art keywords
control lever
lever part
servomotor
stop
speed governor
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
EP85111138A
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German (de)
English (en)
Other versions
EP0178441A1 (fr
Inventor
Ilija Djordjevic
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 EP0178441A1 publication Critical patent/EP0178441A1/fr
Application granted granted Critical
Publication of EP0178441B1 publication Critical patent/EP0178441B1/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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D1/00—Controlling fuel-injection pumps, e.g. of high pressure injection type
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • 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
    • F02D1/02—Controlling fuel-injection pumps, e.g. of high pressure injection type not restricted to adjustment of injection timing, e.g. varying amount of fuel delivered
    • F02D1/08—Transmission of control impulse to pump control, e.g. with power drive or power assistance
    • F02D1/10—Transmission of control impulse to pump control, e.g. with power drive or power assistance mechanical

Definitions

  • the invention relates to a speed controller for fuel injection pumps according to the preamble of the main claim.
  • a known speed controller of this type US-A 4 416232
  • the actuating movement of the quantity control member corresponds to the manipulated variable of the servomotor, so that the servomotor in normal quantity control, especially in the idling range, has to take very small actuating steps, on the other hand during the reduction or during the transition from start to Normal load range very fast shifts of the quantity control element are required.
  • a relatively weak servo motor is sufficient for the normal control range and the fine ratio required there, a correspondingly stronger and larger motor is required for the regulation and start range and the large steps required there.
  • the linear force (the torque) of the stepper motor is directly related to the frequency, so that a very high frequency range up to more than one kHz is required for such a volielectric controller.
  • the engine is relatively expensive and the energy reserve to be treated sparingly anyway in a motor vehicle is more heavily used.
  • the quantity control element is adjusted much less.
  • the more fuel is set with a lower adjustment rate than the normal adjustment rate.
  • the speed controller according to the invention with the characterizing features of the main claim has the advantage that a small servo motor is sufficient for the required quick adjustments at the start transition and during the reduction due to the changing translation on the control lever, which then in the normal speed and load range without the translation according to the invention can perform the fine adjustment steps of the volume control element.
  • FIG. 1 shows a schematic illustration of the first exemplary embodiment
  • Figure 2 is a diagram for the travel of actuator and quantity control element
  • Figure 3 shows a variant of the first embodiment shown in Figure 1 with two pivot stops
  • Figure 4 is a travel diagram of this variant
  • FIG. 5 shows a quantity-speed function diagram of this variant
  • 6 shows the second exemplary embodiment
  • FIG. 7 shows an actuation path diagram of the controller according to FIG. 5.
  • a pump piston 2 is moved in at least one reciprocating movement by means not shown sets, the pump piston 2 during its pressure stroke from a pump work chamber 3 delivering fuel via a pressure line 4 to the internal combustion engine until a relief bore 5 of this pump work chamber 3 emerges with its radial mouth 6 from a ring slide 7 serving as a quantity control member, which is axially displaceable around the pump piston 2 is arranged.
  • the mouth 6 is opened sooner or later, which corresponds to a smaller or larger injection quantity.
  • the ring slide 7 is thus shifted the most to the right for additional starting quantities, but as far as possible to the left when idling and low load.
  • the ring slide 7 is articulated by a control lever 8 which is pivotable about an axis 9, which in turn is carried by an adjusting lever 10 which is mounted on a stationary adjusting axis 11 and can be adjusted by means of an adjusting screw 12 against the force of a retaining spring 13.
  • the pivot axis 9 is set accordingly when the controller is adapted to the injection pump or to the internal combustion engine.
  • the control lever 8 consists of two parts, a first part 16 and a second part 15, which are connected to one another via a hinge 17.
  • a spring 19 engages, which tries to pull the ring slide 7 in the direction of smaller injection quantities.
  • the spring 19 is suspended with its end facing away from the free lever end 18 on the housing 20 of the controller or the pump.
  • the actuator 21 of an electric servomotor 22 acts on the second control lever part 15, with an actuating travel s M corresponding to the motor manipulated variable, from which the actuating travel s of the ring slide 7 follows.
  • the servomotor 22 is controlled by an electronic control unit processing parameters of the motor and the environment.
  • the first lever part 15 carries a stop 24 which cooperates with the first control lever part 16 when the second control lever part 15 is in a corresponding rotational position.
  • the second control lever part 15 can on a substantially fixed pivot stop 27; 30, 31; 37, 38 start up; between this and the hinge 17, the actuator 21 of the servomotor 22 engages.
  • FIG. 2 the adjustment path s of the ring slide 7 is shown in the adjustment diagram above the ordinate and the adjustment path s M of the adjustment member 21 is shown on the abscissa.
  • the stop 24 is lifted off the second lever part 16, so that, according to the translation of the ring slide 7, a correspondingly large adjustment is made per travel of the actuator 21. From this point s M1, however, this transmission ratio runs much flatter, namely to point s M2 , which corresponds to a path of the ring slide 7 from S2 .
  • the distance between S1 and s 2 is less than half the distance between S1 and the origin 0, while the distances between s M2 and s M1 or SM1 and the origin are approximately the same, ie that with an even adjustment of the actuator 21 from the impact of the stop 24 on the first control lever part 16, the corresponding adjustment movement of the ring slide 7, namely for the normal and idle speed range, runs much more slowly.
  • two pivot stops 30 and 31 are provided, which, viewed in the longitudinal extent of the second control lever part, are arranged one after the other. While the swivel stop 30 serves to limit the start, the swivel stop 31 serves to limit the full load.
  • the distances to the point of attack of the actuator 21 are designated here with a 1 for the start stop 30 and with a 2 for the full load stop 31.
  • the lever ratio in the area in which the stop 24 has lifted from the first control lever part 16 is subdivided again, so that after a very steep reduction after starting speeds, a somewhat flatter one follows for full-load reduction, which is then followed by the normal control range.
  • either one or the other swivel stop 30, 31 can engage.
  • the horizontal lines shown on the curves show the volume differences in the injection quantity resulting from the adjustment movement of the ring slide 7 for the three different situations, namely in the case of start regulation I, full-load regulation II and normal regulation, in particular idling 111, each of these quite different quantity changes representing a uniform step or adjustment path of the actuator 21 correspond, in other words, with an even division of the actuating path of the actuator 21 into individual steps, each step corresponds to a partial injection quantity determined by the section of the horizontal graduation marks in FIG. 5, which according to the invention vary considerably between start, full load and idle control.
  • the spring 119 acts on the first control lever part 116 between the hinge 117 and the pivot axis 109. From this pivot point 117, the first control lever part 116 bifurcates into two arms 33 and 34, on which springs 35 and 36 are supported, which clamp the second control lever part 115 between them.
  • the pivoting movement range of the free end 126 of this first control lever part 115 is limited by two pivoting stops 37 and 38.
  • This second exemplary embodiment is primarily intended to show that different gear ratios also result from different lever ratios and stop arrangements, by means of which almost every task in this regard can be solved, with all the requirements of the controller being satisfied with a short actuating path of the servomotor and with a servomotor which adjusts more precisely with smaller steps but can be adjusted in large steps from a starting additional quantity to normal and full load quantity.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Claims (8)

1. Régulateur de vitesse de rotation pour pompe à injection de carburant d'un moteur à combustion interne, avec un moteur électrique (22) de réglage commandé par un appareil électronique de commande fonctionnant avec un paramètre, avec une pièce (7) de commande du débit déterminant la quantité de carburant injectée et actionnée par le moteur (22) de réglage, avec un levier (8) de réglage soumis à un ressort (19, 119) en direction du réglage et transmettant la grandeur du réglage du moteur (22) de réglage à la pièce (7) de commande du débit, articulé autour d'un axe (9), et avec un butoir articulé (27 ; 30, 31 ; 37, 38) limitant la manoeuvre articulée du levier (8) de réglage, caractérisé en ce que le levier (8) de réglage est formé de deux parties, avec une première partie (16, 116) de levier de réglage, constituée de deux bras dont l'un des bras est accouplé à la pièce (7) de commande du débit, et dont l'autre bras est relié au moyen d'une charnière (17, 117) à une seconde partie (15.115) du levier de réglage, laquelle est en contact avec le moteur (22) de réglage, la première partie (16, 116) du levier de réglage étant articulée autour d'un axe (9) d'articulation essentiellement fixe par rapport au carter, et étant soumise par le ressort (19,119) dans la direction des réglages de plus petites quantités de carburant injecté, et la seconde partie (15, 115) du levier de réglage pouvant être amenée en position contre le butoir articulé (27 ; 30, 31 ; 37, 38) essentiellement fixe localement, par le mouvement de réglage du moteur (22) de réglage en direction de la force du ressort (19, 119), grâce à quoi le moteur (22) de réglage touche le levier de réglage entre ce butoir (27 ; 30, 31 ; 37, 38) et la charnière (17, 117), et la faculté d'articulation de la seconde partie (15, 115) du levier de réglage par rapport à la première partie (16,116) du levier de réglage est limitée par un butoir (24, 34, 36) de torsion formé avec l'autre bras de la seconde partie (16, 116) du levier de réglage.
2. Régulateur de vitesse de rotation selon la revendication 1, caractérisé en ce que la position de l'axe (9, 109) d'articulation de la première partie (16) du levier de réglage est modifiable pour ajustement.
3. Régulateur de vitesse de rotation selon la revendication 2, caractérisé en ce que l'axe (9, 109) d'articulation est rattaché à un levier (10) d'ajustement, qui est articulé autour d'un axe (11) d'ajustement et une vis (12) d'ajustement.
4. Régulateur de vitesse de rotation selon la revendication 1, caractérisé en ce que, par un butoir supplémentaire (33) de torsion, le mouvement de torsion des parties (115, 116) du levier de réglage l'une par rapport à l'autre peut être limité dans la direction de l'augmentation du débit injecté.
5. Régulateur de vitesse de rotation selon la revendication 1, caractérisé en ce qu'un ressort (35, 36) peut être prévu entre la seconde partie (115) du levier de réglage et la première partie (116) du levier de réglage.
6. Régulateur de vitesse de rotation selon les revendications 1, 4 ou 5, caractérisé en ce qu'en plus du butoir articulé (37), un second butoir articulé (38) est prévu, limitant le déplacement de la seconde partie (115) du levier de réglage dans la direction des débits injectés plus faibles.
7. Régulateur de vitesse de rotation selon la revendication 6, caractérisé en ce que les butoirs articulés (37, 38) présentent les mêmes distances par rapport à l'axe (21) du moteur (22) de réglage, et les rapports des courses de réglage par rapport à la pièce (7) de commande de débit sont les mêmes.
8. Régulateur de vitesse de rotation selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un butoir articulé (31) est disposé au delà du butoir articulé (30) dans la direction de l'étendue longitudinale de la seconde partie (15) du levier de réglage, cette seconde partie (15) du levier de réglage, lors de son déplacement par le moteur (22) de réglage, avant d'être en contact avec le butoir articulé (30), vient en contact avec le butoir articulé (31).
EP85111138A 1984-10-01 1985-09-04 Régulateur de la vitesse de rotation pour pompes d'injection d'essence Expired EP0178441B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3435986 1984-10-01
DE19843435986 DE3435986A1 (de) 1984-10-01 1984-10-01 Drehzahlregler fuer kraftstoffeinspritzpumpen

Publications (2)

Publication Number Publication Date
EP0178441A1 EP0178441A1 (fr) 1986-04-23
EP0178441B1 true EP0178441B1 (fr) 1988-08-17

Family

ID=6246820

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85111138A Expired EP0178441B1 (fr) 1984-10-01 1985-09-04 Régulateur de la vitesse de rotation pour pompes d'injection d'essence

Country Status (4)

Country Link
US (1) US4685433A (fr)
EP (1) EP0178441B1 (fr)
JP (1) JPS61229931A (fr)
DE (2) DE3435986A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3703073A1 (de) * 1987-02-03 1988-08-11 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE4117267A1 (de) * 1991-05-27 1992-12-03 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE4122879A1 (de) * 1991-07-11 1993-01-14 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2568912A (en) * 1949-05-12 1951-09-25 Deere Mfg Co Speed-responsive fuel-control means for internal-combustion engines
DE2802607A1 (de) * 1978-01-21 1979-07-26 Bosch Gmbh Robert Drehzahlregler fuer kraftstoffeinspritzpumpen
DE2845095A1 (de) * 1978-10-17 1980-04-30 Bosch Gmbh Robert Regeleinrichtung fuer eine kraftstoffeinspritzpumpe
JPS55167535U (fr) * 1979-05-21 1980-12-02
US4470763A (en) * 1980-01-17 1984-09-11 Nissan Motor Company Fuel injection control system
JPS5720525A (en) * 1980-07-14 1982-02-03 Nippon Denso Co Ltd Electric governor for fuel injection pump
DE3121107A1 (de) * 1981-05-27 1982-12-16 Robert Bosch Gmbh, 7000 Stuttgart "drehzahlregler einer kraftstoffeinspritzpumpe"
JPS5867932A (ja) * 1981-10-19 1983-04-22 Nissan Motor Co Ltd 燃料噴射ポンプの吐出量調整装置
DE3237499A1 (de) * 1982-10-09 1984-04-12 Robert Bosch Gmbh, 7000 Stuttgart Schrittmotor zur verstellung von stellgliedern
JPS5974336A (ja) * 1982-10-19 1984-04-26 Nippon Denso Co Ltd デイ−ゼル機関用電気的制御装置
DE3243349A1 (de) * 1982-11-24 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe

Also Published As

Publication number Publication date
JPH0568623B2 (fr) 1993-09-29
EP0178441A1 (fr) 1986-04-23
US4685433A (en) 1987-08-11
JPS61229931A (ja) 1986-10-14
DE3435986A1 (de) 1986-04-10
DE3564467D1 (en) 1988-09-22

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