EP0419612B1 - Pompe a injection de carburant pour moteurs a combustion interne - Google Patents

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

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Publication number
EP0419612B1
EP0419612B1 EP90904766A EP90904766A EP0419612B1 EP 0419612 B1 EP0419612 B1 EP 0419612B1 EP 90904766 A EP90904766 A EP 90904766A EP 90904766 A EP90904766 A EP 90904766A EP 0419612 B1 EP0419612 B1 EP 0419612B1
Authority
EP
European Patent Office
Prior art keywords
pressure
space
return
fuel injection
internal combustion
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
EP90904766A
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German (de)
English (en)
Other versions
EP0419612A1 (fr
Inventor
Josef Hain
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
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Robert Bosch GmbH
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Expired - Lifetime 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
    • F02D1/16—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
    • 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
    • F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support

Definitions

  • the invention relates to a fuel injection pump according to the preamble of main claims 1, 2.
  • a fuel injection pump is known from DE-OS 31 48 214 and EP-A-250785.
  • the pressure valve provided there in the relief line of the return space can be controlled depending on the temperature in such a way that it is closed when the internal combustion engine is cold started and is open at the latest when the internal combustion engine is warm.
  • the pressure valve is designed as a check valve which can open at a maximum pressure and which is opened by a thermostatically controlled element. As long as the pressure valve is closed, the same pressure, which is determined by the delivery rate of the fuel feed pump, is established in the pressure chamber and in the resetting space, which pressure also acts on the spray adjustment device and adjusts it in the "early" direction.
  • This special early adjustment is canceled at the end of the warm-up phase by opening the pressure valve and then the pressure acting on the spray adjustment device is controlled in a known manner as a function of the speed by the pressure control valve.
  • the special early adjustment improves the cold start behavior and the running of the internal combustion engine in the warm-up phase.
  • the fuel injection pump according to the invention with the characterizing features of the main claims has the advantage that the drain throttle on the pressure control valve is closed quickly and safely during cold start, that the pressure mentioned for the cold start early adjustment can be reached regularly.
  • FIG. 1 shows a first exemplary embodiment of the fuel injection pump according to the invention in a schematic illustration
  • FIG. 2 shows a second exemplary embodiment of the invention
  • FIG Pressure curve in the pressure chamber in front of the pressure control valve or the control pressure effective at the spray adjustment device for various functional positions.
  • a spray adjustment device 2 which has a spray adjustment piston 4 which can be displaced in a cylinder 3 and which is acted upon on one end face by a return spring 5 which is supported in a stationary manner on an end face of the cylinder 3 and on the other end of a spray adjuster working space 6 is limited in the cylinder 3.
  • the injection adjuster working space 6 is connected via a throttle bore 7 in the injection adjustment piston to a suction space 9 in the interior of the fuel injection pump.
  • the suction chamber 9 is supplied with fuel by a feed pump 10, which is driven synchronously with the fuel injection pump 1, via a pressure line 11, the feed pump taking the fuel from a fuel reservoir 13 via a suction line 12.
  • a bypass line 15 is provided in parallel to the feed pump 10, in which a pressure control valve 16 is arranged.
  • This has an adjustable wall in the form of a control piston 17, which slides tightly in a cylinder 18 and delimits on one side a pressure chamber 19 into which the bypass line 15 opens from the pressure line 11.
  • the control piston delimits a return space 20 in which a return spring 22 is arranged, which is supported on the one hand on the control piston 17 and on the other hand is supported on an adjustable stop 23.
  • the reset space 20 is constantly connected to the pressure space 19 via a throttle 24.
  • the reset space 20 is connected to the pressure space via a relief line 26 27 of a pressure valve 28, which is designed as a pressure control valve in the form of a check valve, the valve closing member 29 of which can be pushed open by a temperature-dependent actuator 30.
  • This actuator is, for example, a thermostat or an expansion element, which is exposed to the cooling water of the internal combustion engine and thus detects the operating temperature of the internal combustion engine. Accordingly, the closing element 29 is pushed open by the actuator when the internal combustion engine is at operating temperature, and thus the relief line 26 is connected to a relief line part 26 leading further to the fuel supply 13 downstream of the valve closing element 29.
  • a second pressure valve 33 is connected in parallel to the pressure valve 28 and lies in a bypass line 34 to the pressure valve 28.
  • the second pressure valve 33 has a piston 37 which is tightly displaceable in a cylinder 36 and which delimits a pressure chamber 38 on the one side and a relieved space 39 on the other side, in which a return spring 40 which loads the piston 37 is arranged by means of an adjusting member 41 is adjustable.
  • the pressure chamber 38 is constantly connected to the delivery side of the feed pump 10 and thus has the same pressure that prevails in the suction chamber 9 or in the pressure chamber 19.
  • This pressure allows the piston 37 to be displaced against the return spring and, in the course of the displacement, comes with an annular groove 43 provided on the circumference of the piston in connection with an inlet opening 44 of the bypass line 34 in the cylinder wall of the cylinder 36. Because the annular groove 43 has a longitudinal bore 45 is permanently connected to the relieved space 39, at this moment the bypass line 34 is connected to the continuing part of the relief line 26 via the relieved space 39 and via a part of the bypass line 34 extending therefrom. At this moment, the pressure valve 28 is bypassed, so that the reset space 20 of the pressure control valve 16 is relieved, even when the pressure control valve 28 is closed.
  • the connection is established as a function of the pressure in the pressure chamber 38, which can be set with the aid of the setting member 41 or the return spring 40.
  • the pressure in the pressure chamber 38 is always the same as in the pressure chamber 19 of the pressure control valve, which ultimately controls this pressure in conjunction with the delivery rate of delivery pump 10, which is driven synchronously with the speed of the fuel injection pump.
  • the pressure control valve in the radial wall of the cylinder 18 has a discharge throttle 46 which is connected via a bypass line 15 to the suction line 12 of the feed pump 10 or via this to the relief chamber in the form of the fuel supply 13.
  • the cross section of the discharge throttle is determined by the Position of the control piston 17 determined and controlled by its front edge.
  • the position of the control piston is in turn determined by the pressure in the pressure chamber 19 and the force acting on it from the restoring chamber 20. This is essentially determined by return spring 22, the pretension of which is in turn determined by the adjustable stop 23.
  • This has the shape of a stepped piston, the part 49 of which has a smaller diameter at the end of the reset space 20 and whose larger part 50 includes a working space 51 which is connected via a line 52 to the relief line 26 or to the reset space 20.
  • the interior of the fuel injection pump is filled with fuel.
  • the feed pump 10 is set in motion and generates a pressure in the suction chamber 9 or pressure chamber 19 of the pressure control valve 16.
  • This pressure propagates through the throttle 24 into the reset chamber 20 and from there via the line 52 into the working chamber 51.
  • This pressure quickly causes a displacement of the adjustable stop in the direction of the control piston 17, so that it is moved so that the discharge throttle 46 is initially securely closed.
  • the relief line 26 is closed by the pressure valve 28 and the bypass line 34 is also closed by the second pressure valve 33.
  • an effective control pressure which could now be controlled via the pressure control valve 16, can build up very quickly in the interior of the fuel injection pump.
  • the pressure valve 28 When the internal combustion engine is at operating temperature, the pressure valve 28 is open from the start via the actuator 30, the adjustable stop 23 in its normal position relieving the return spring 22 and the pressure control valve 16 in the normal function. Accordingly, there is a profile of the pressure in the suction chamber 9 as a function of the speed according to the approximately linearly increasing characteristic curve 64 in FIG. 3. Without the measure according to the invention, a pressure curve according to characteristic curve 65 with little pronounced steepness at the start of the speed would result for the cold start.
  • FIG. 2 shows a variant of the embodiment according to FIG. 1.
  • the work space 51 is connected to the pressure space 19 via a separate line 54 in which a throttle 55 is arranged.
  • the pressure chamber 51 is also connected via a controllable pressure-maintaining valve 56 to the suction line 12 of the feed pump 10 or to the relief chamber 13.
  • the throttle 55 takes over the decoupling function that the throttle 24 from FIG. 1 had as a connecting element to the working chamber 51.
  • the controllable pressure-maintaining valve 56 functions in place of the pressure valve 28 or the second pressure valve 33. With the controllable pressure valve, the pressure in the working space 51 can now be controlled more precisely and taking into account specific parameters.
  • the temperature is also the main parameter for this 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)
  • High-Pressure Fuel Injection Pump Control (AREA)

Abstract

Pour obtenir une augmentation de pression extrêmement rapide à l'intérieur de la pompe à injection de carburant, on modifie une soupape de commande de pression, qui commande cette pression, de telle manière que cette soupape se ferme immédiatement et sans faute lorsque le moteur à combustion interne démarre à froid. A cet effet, un piston de commande (17) de la soupape de commande de pression (16) est soumis en sa partie postérieure à l'effet d'un ressort de rappel (22), dont l'autre point d'appui est une butée mobile (23), qui est soumise à la pression générée dans la pompe à injection de carburant et essaie en conséquence de précontraindre le ressort de rappel (22). Cela provoque la fermeture d'un papillon d'écoulement (46) commandé par le piston de commande (17), de sorte que la totalité du carburant déplacé par une pompe de circulation (10) reste à l'intérieur de la pompe et contribue à augmenter la pression. Grâce à cette pression, on obtient un déplacement extrêmement rapide d'un piston régulateur d'injection (4), hâtant le début de l'injection de carburant pour favoriser le démarrage à froid et l'échauffement.

Claims (4)

  1. Pompe d'injection de carburant pour moteurs à combustion interne, notamment pompe distributrice, comportant :
    - un dispositif (2) de réglage du début d'injection, équipé d'un organe de réglage constitué d'une première paroi réglable (4) sous l'effet de la pression de commande, en fonction de la vitesse, d'un fluide de pression et contre l'action d'un ressort de rappel (5),
    - une pompe de refoulement (10) entraînée en synchronisme avec la pompe d'injection de carburant, dont la pression de refoulement est utilisée comme pression de commande et qui est commandée par une soupape de commande de pression (16) comprenant une seconde paroi réglable (17) qui peut être soumise à la pression de commande, contre l'action d'un ressort de rappel (22),
    - la paroi réglable (17) sépare une chambre de pression (19) d'une chambre de rappel (20) où est logé le ressort de rappel (22) et qui est reliée en permanence à la chambre (19) par un étranglement (24),
    - le mouvement de réglage de la seconde paroi réglable (17) commande un orifice d'échappement (46) reliant la chambre de pression (19) à un volume de décharge (13) tandis que la chambre de rappel (20) est mise en relation avec le volume de décharge (13) par une conduite de décharge contenant une soupape de maintien de pression (28), ouverte lorsque le moteur a atteint sa température de fonctionnement caractérisée en ce que le ressort de rappel (22) de la soupape de commande de pression (16) s'appuie sur une butée réglable (23) dont la face située à l'opposé de la chambre de rappel (20) est plus grande que la face en regard de cette chambre et constitue une surface de pression délimitant une chambre de travail (51), qui peut être reliée, par l'intermédiaire de la soupape de commande de maintien de pression (28) au volume de décharge (13) et qui est reliée à la chambre de pression (19) de la soupape de commande de pression (16) par un étranglement (24).
  2. Pompe d'injection de carburant pour moteurs à combustion interne, notamment pompe distributrice, comportant :
    - un dispositif (2) de réglage du début d'injection, équipé d'un organe de réglage constitué d'une première paroi mobile (4) sous l'effet de la pression de commande, en fonction de la vitesse, d'un fluide de pression et contre l'action d'un ressort de rappel (5),
    - une pompe refoulante (10) entraînée en synchronisme avec la pompe d'injection de carburant, dont la pression de refoulement est utilisée comme pression de commande et qui est pilotée par une soupape de commande de pression (16) comprenant une seconde paroi mobile (17) qui peut être soumise à la pression de commande, contre l'action d'un ressort de rappel (22),
    - la paroi mobile (17) sépare une chambre de pression (19) d'une chambre de rappel (20) où est logé le ressort de rappel (22) et qui est reliée en permanence à la chambre (19) par un étranglement (23),
    - le mouvement de réglage de la seconde paroi mobile (17) commande un orifice d'échappement (46) reliant la chambre de pression (19) à un volume de décharge (13) tandis que la chambre de rappel (20) est mise en relation avec le volume de décharge (13) par une conduite de décharge contenant une soupape de maintien de pression (28), ouverte lorsque le moteur a atteint sa température de fonctionnement caractérisée en ce que le ressort de rappel (22) de la soupape de commande de pression (16) s'appuie sur une butée réglable (23) dont la face située à l'opposé de la chambre de rappel (20) est plus grande que la face en regard de cette chambre et constitue une surface de pression délimitant une chambre de travail (51), qui peut être reliée, par l'intermédiaire d'une seconde soupape pilotable de maintien de pression (56) au volume de décharge (13) et qui est reliée à la chambre de pression (19) de la soupape de commande de pression (16) par un second étranglement (55).
  3. Pompe d'injection de carburant selon la revendication 2, caractérisée en ce que le second étranglement (55) est monté dans une canalisation (51) reliant la chambre de pression (19) à la chambre de travail (51).
  4. Pompe d'injection de carburant selon la revendication 1, caractérisée en ce que la pression de maintien de la seconde soupape de maintien de pression (56) peut être commandée en fonction de la température.
EP90904766A 1989-04-18 1990-03-23 Pompe a injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0419612B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3912624A DE3912624A1 (de) 1989-04-18 1989-04-18 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3912624 1989-04-18
PCT/DE1990/000235 WO1990012957A1 (fr) 1989-04-18 1990-03-23 Pompe a injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0419612A1 EP0419612A1 (fr) 1991-04-03
EP0419612B1 true EP0419612B1 (fr) 1994-08-03

Family

ID=6378874

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90904766A Expired - Lifetime EP0419612B1 (fr) 1989-04-18 1990-03-23 Pompe a injection de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US5085196A (fr)
EP (1) EP0419612B1 (fr)
JP (1) JP2895218B2 (fr)
DE (2) DE3912624A1 (fr)
WO (1) WO1990012957A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4117813A1 (de) * 1991-05-31 1992-12-03 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5462033A (en) * 1992-04-09 1995-10-31 Lucas Industries Public Limited Company Fuel pumping apparatus
DE19832842C1 (de) * 1998-07-21 2000-02-17 Bosch Gmbh Robert Kraftstoff-Fördersystem zur Kraftstoffversorgung einer Brennkraftmaschine

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1932600C3 (de) * 1969-06-27 1978-07-27 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzanlage für selbstzündende Brennkraftmaschinen mit Änderung des Spritzbeginns
DE2854422A1 (de) * 1978-12-16 1980-07-03 Bosch Gmbh Robert Kraftstoffeinspritzanlage fuer diesel- brennkraftmaschinen, insbesondere fuer fahrzeug-dieselmotoren
DE2925418A1 (de) * 1979-06-23 1981-01-29 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2931938A1 (de) * 1979-08-07 1981-02-26 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2931937A1 (de) * 1979-08-07 1981-02-26 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3037730A1 (de) * 1980-10-06 1982-05-19 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzanlage fuer brennkraftmaschinen
DE3138607A1 (de) * 1981-09-29 1983-04-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3138606A1 (de) * 1981-09-29 1983-04-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3211877A1 (de) * 1982-03-31 1983-10-06 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE3410146A1 (de) * 1984-03-20 1985-10-03 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3517974A1 (de) * 1985-05-18 1986-11-20 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
GB2178559A (en) * 1985-07-26 1987-02-11 Perkins Engines Group Fuel injection pump
DE3619325A1 (de) * 1986-06-09 1987-12-10 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3822257A1 (de) * 1988-07-01 1990-01-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen

Also Published As

Publication number Publication date
WO1990012957A1 (fr) 1990-11-01
JPH03505477A (ja) 1991-11-28
US5085196A (en) 1992-02-04
DE3912624A1 (de) 1990-10-25
EP0419612A1 (fr) 1991-04-03
JP2895218B2 (ja) 1999-05-24
DE59006681D1 (de) 1994-09-08

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