EP0627552B1 - pompe à injection de carburant - Google Patents

pompe à injection de carburant Download PDF

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Publication number
EP0627552B1
EP0627552B1 EP94103494A EP94103494A EP0627552B1 EP 0627552 B1 EP0627552 B1 EP 0627552B1 EP 94103494 A EP94103494 A EP 94103494A EP 94103494 A EP94103494 A EP 94103494A EP 0627552 B1 EP0627552 B1 EP 0627552B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
working space
fuel injection
delivery stroke
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
EP94103494A
Other languages
German (de)
English (en)
Other versions
EP0627552A1 (fr
Inventor
Helmut Dipl.-Ing. Laufer
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 EP0627552A1 publication Critical patent/EP0627552A1/fr
Application granted granted Critical
Publication of EP0627552B1 publication Critical patent/EP0627552B1/fr
Anticipated expiration legal-status Critical
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 Genus of claim 1.
  • a fuel injection pump is already known from DE-A-29 23 445.
  • the problem with fuel injection pumps is as follows: If the Delivery rate of the fuel injection pump at the nominal output point the internal combustion engine at maximum load and maximum speed optimized so that there the maximum permissible pressure in the pump work space the fuel injection pump occurs, then this pressure is in usually at low speed of the fuel injection pump or the associated internal combustion engine in the lower full load point for the Quality of the fuel input into the combustion chambers of the internal combustion engine too low due to injectors. If you raise the funding rate in this area, then the pressure rises as desired this lower full load point, but at the nominal power point the Fuel injection pump overloaded. So there has to be an increase of the pressure in the lower full load point to ensure that the Pump is not overloaded at the nominal output point.
  • features of claim 1 have the advantage that the pressure in the pump workspace in the low speed load range reaches a desired high injection pressure without high Speed load range of the fuel injection pump this too high pressure is overloaded.
  • An advantageous embodiment of the invention consists in the configuration the fuel injection pump according to claim 4, wherein in from a certain load speed point, the delivery rate is simple of the pump piston is delayed over a certain range of rotation angles becomes.
  • This gives an injection pressure curve shape, the controlled by the pressure in the pump work space or by this generated pressure in the working area controlled in front of the adjusting piston becomes.
  • the relief valve can also be used serve as a removal device by starting from or after of the high-pressure delivery stroke of the pump piston at least temporarily is opened.
  • the control of this valve can be advantageous This is done by a sensor that detects the pressure in the pump work space be controlled or by an injection duration control, which itself has an indirect effect on the pressure in the pump work area.
  • the pressure in the work area before the adjusting piston according to claim 10 by a electrically controlled valve controlled according to claim 11 clocked is controlled so that its opening time in essentially complementary to the opening times of the relief valve lies.
  • FIG. 1 shows a first embodiment of the control device separate escape piston
  • Figure 2 a related to Figure 1 Diagram of the cam stroke over the angle of rotation
  • Figure 3 is a diagram the injection course over the angle of rotation
  • Figure 4 shows a second Version with two check valves
  • Figure 5 shows a third version with a drain check valve and an additional one 2/2-way solenoid valve
  • Figure 6 is related to Figure 5 Diagram of the cam stroke at the work of the control valve and additional solenoid valve
  • Figure 7 shows a fourth embodiment with an additional 2/2-way solenoid valve and Figure 8 one on the Figure 7 related diagram of the cam stroke and the element pressure when working the control valve and the additional solenoid valve.
  • FIG. 1 shows a cylinder 1 in which an adjusting piston 2 is movable against the force of a spring 3.
  • the adjusting piston 2 has a recess 4 into which a free end 5 of a bolt 6 intervenes.
  • One of the spring 3 opposite working space 7 of the Cylinder 1 is connected via a line 8 to an additional cylinder 9 namely at its working chamber 10.
  • an additional cylinder 9 is an evasive piston 11 is arranged, the working chamber 10 as movable wall limited.
  • Stop 14 used, the path of the evasive piston 11 on a limited stroke (AW).
  • AW limited stroke
  • On line 8 are one Pressure medium inflow line 15, which is increased by a pressure medium Pressure leading pressure medium source 37 discharges and a pressure medium drain line 16, which leads to a relief room, connected.
  • a pressure medium inflow line 15 In the pressure medium inflow line 15 is an inflow check valve 17 with a throttle 19 and in the pressure medium discharge line 16 an electrically controlled valve, here a solenoid valve 18, is arranged, that serves to regulate the pressure in the work area.
  • the adjusting piston 2 is the one used in fuel injection pumps known pistons of an injection start adjustment device. Adjusted according to the displacement of the adjusting piston the bolt 6 as the corresponding bolt in one by the DE-A-21 58 689 known fuel injection pump one in this Registration not shown roller ring, but rotatable except for the Rotation by the pin 6 stationary in the housing of the fuel injection pump is stored and on its rollers a cam expires with their cams.
  • the cam disc is included a drive shaft of the fuel injection pump and coupled to another with a pump piston, which due to the rotation of the Drive shaft rotating together with the cam disc Performs movement while serving as a distributor and at the same time due to the cam disc running on the rollers back and forth Performing movement and suction and as a pump piston Carrying out strokes.
  • the pump piston closes as usual known, but not shown here, a pump work room one that is filled with fuel during the suction stroke and during the delivery stroke Fuel under high pressure to one injector on each Promotes internal combustion engine.
  • the injectors are essentially the beginning of the Stroke movement of the cam disc together with the pump piston the course of which determines the roles of the roller ring and that End of delivery, to determine the fuel injection quantity by opening a relief channel.
  • the cam disc is replaced by a resetting Force in the form of return springs on the roller ring held. This restoring force is also due to the reaction force of the pump piston during its delivery stroke.
  • the roller ring experiences via the flank of the cams of the cam disc a force in its circumferential direction, which force is the actuating force counteracts the adjusting piston.
  • the degree of this pressure increase corresponds to the pressure generated in the pump work space.
  • the pressure increase on the other hand is only possible because the check valve 17, that to the pressure medium source closes that supplied to the work area Pressure medium volume with closed solenoid valve includes.
  • the bias of the spring 12 so chosen that in an upper range of the achievable pressure in Pump work area uses the evasive movement of the evasive piston and thus prevents excessive pressure in the pump work space arises. Because of the throttling effects in the high pressure side Line system is in a known manner at low speed lower delivery rate with a lower final maximum pressure in Pump workspace achieved and a high at high speed Delivery rate with a correspondingly higher final maximum pressure in Pump work room. This high one that arises at high speed Ultimate maximum pressure is now with the device according to the invention Helped by the evasive piston 12. This effect is special Particularly pronounced even at full load, since the attainable one Ultimate maximum pressure depends on the high pressure displacement of the Pump piston. At full load, the final maximum pressure reached is greater than at partial load.
  • the stop 14 comes into play.
  • the Preload of the preloaded spring 12 is designed to be lower, so the escape piston 11 already at a lower pressure in the pump work space start at a lower injection rate to dodge.
  • the injection rate would then range according to the injection curve display with escape piston 11 (AWK) of the diagram in FIG. 3 over the angle of rotation ⁇ with a smaller slope until the Dodge piston comes to rest on the stop 14.
  • ANK injection curve display with escape piston 11
  • FIGS. 5 and 6 A solution that is improved in comparison is shown in FIGS. 5 and 6 shown.
  • Deviating from the design according to Figure 4 is here in addition to the solenoid valve 18 and instead of the check valve 17 with a throttle a further 2/2 solenoid valve 34 in the pressure medium supply line 15 have been used.
  • the additional solenoid valve 34 enables fast over a large opening cross-section Refill the amount of liquid escaped via the check valve 33.
  • the two solenoid valves 18 and 34 switched so that the control of the inflow and outflow in the suction stroke phase of the pump piston.
  • Figure 6 shows the assignment of the solenoid valve opening phases of the Solenoid valve 34 (MV 34) and the solenoid valve 18 (MV 18) in relation to the cam elevation curve via the angle of rotation ⁇ .
  • the solenoid valves 34 and 18 are driven in opposite directions in such a way that for a pressure increase in the working space 7, the solenoid valve 18 a is open for a shorter time than the solenoid valve 34.
  • the solenoid valves can also be controlled complementarily with one another variable duty cycle, with the variation of the duty cycle the opening time of one valve at the expense of the other Valve is changed.
  • the pressure medium inflow line 15 is again the 2/2 solenoid valve 34 and in the pressure medium drain line 16 the 2/2-solenoid valve 18.
  • a pressure sensor 35 is provided, which is symbolically in the drawing in Figure 7 is connected to the line 8 and on the other hand in connection with a control device, not shown stands, depending on how, depending on operating parameters also the solenoid valves 18 in the exemplary embodiment according to FIG. 5 and 34 can be controlled to the desired pressure in the work space 7 to control the start of funding.

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)

Claims (11)

  1. Pompe d'injection de carburant pour moteur à combustion interne comprenant un piston de pompe entraíné par un entraínement par came qui délimite une chambre active de pompe dans un cylindre de pompe,
    lors d'une course de transfert du piston de pompe, le carburant est transféré à haute pression de cette chambre vers l'injecteur de carburant,
    l'entraínement par came comprenant une partie essentiellement fixe et une partie entraínée par l'arbre d'entraínement de la pompe d'injection, une des parties comportant un chemin de came et l'autre partie suivant le chemin de came en déplaçant en même temps le piston de pompe par une force de refoulement exercée par le chemin de came sur la partie essentiellement fixe, et un piston de réglage (2) délimitant une chambre active (7) dans un cylindre (1) pour fournir du fluide sous pression à partir d'une source de fluide sous pression, ce piston étant réglable par le fluide sous pression ou contre une force de rappel (3), la partie essentiellement fixe de l'entraínement par came étant couplée à ce piston, la force de refoulement étant dirigée dans le même sens que la force de rappel et par son déplacement se règle le début du transfert à haute pression du piston de pompe par rapport à une position de rotation de l'arbre d'entraínement,
    la pression du fluide sous pression régnant dans la chambre active (7) pour modifier le début de la course de transfert se commandant selon les paramètres de fonctionnement du moteur à combustion interne et avec le dispositif de prélèvement pour le prélèvement commandé de quantité de fluide sous pression de la chambre active (7) pendant la course de transfert à haute pression du piston de pompe,
    la chambre active (7) ayant une conduite d'alimentation de fluide sous pression (15) comportant un organe de commande (17, 34), venant de la source de fluide sous pression ainsi qu'une soupape de décharge (18) à commande électrique avec une conduite de sortie de fluide sous pression (16) vers une chambre de décharge,
    cet organe commandant la pression dans la chambre active (7) pour modifier le début respectif de la course de transfert pour que ce début soit toujours réglé avant le début de la course de transfert de chaque course de transfert de piston de pompe,
    caractérisée en ce que
    le prélèvement des quantités de fluide sous pression est commandé par le dispositif de prélèvement en fonction de la pression régnant dans la chambre active (7) ou de la pression dans la chambre active de la pompe pendant la course de transfert à haute pression.
  2. Pompe d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    le dispositif de prélèvement se compose d'un clapet antiretour (33) communiquant en permanence avec la chambre active (7), et la pression d'ouverture de ce clapet définit la forme de la pression dans la chambre active (7) ou dans la chambre active de pompe pendant la course de transfert à haute pression du piston de pompe.
  3. Pompe d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    l'installation de prélèvement comporte une cloison mobile (11) qui délimite hydrauliquement la chambre active (7) et dont le côté arrière est sollicité par un ressort (12), précontraint qui est réglé pour que la cloison mobile se déplace à partie d'une certaine pression régnant dans la chambre active ou dans la chambre de pompe.
  4. Pompe d'injection de carburant selon la revendication 3,
    caractérisée en ce que
    sur le côté arrière de la cloison mobile (11), il est prévu une butée de limitation de course (14) pour le mouvement de la cloison mobile contre la force du ressort de précontrainte (12) et la pression déterminée, se situe dans la plage moyenne de la pression atteinte par le piston de pompe dans la plage de fonctionnement de la pompe d'injection de carburant pendant sa course de transfert respective.
  5. Pompe d'injection de carburant selon les revendications 3 et 4,
    caractérisée en ce que
    le ressort précontraint s'appuie de manière fixe contre le corps de la pompe.
  6. Pompe d'injection de carburant selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    l'organe de commande dans la conduite d'alimentation en pression (15) est un clapet antiretour (17) qui s'ouvre en direction de la chambre active.
  7. Pompe d'injection de carburant selon la revendication 1,
    caractérisée en ce que
    la soupape de décharge (18) sert de dispositif de prélèvement et s'ouvre en fonction des paramètres de fonctionnement pendant au moins une partie de la course de transfert du piston de pompe.
  8. Pompe d'injection de carburant selon la revendication 7,
    caractérisée en ce que
    la soupape de décharge (18) s'ouvre en fonction de la pression atteinte dans la chambre active de la pompe à partir du dépassement d'une pression prédéterminée.
  9. Pompe d'injection de carburant selon la revendication 7,
    caractérisée en ce que
    la soupape de décharge (18) est commandée par une régulation de durée d'injection, la durée d'injection étant mesurée par un capteur détectant la durée d'ouverture d'un injecteur alimenté à partir de la pompe d'injection.
  10. Pompe d'injection de carburant selon l'une quelconque des revendications 1 à 9,
    caractérisée en ce que
    l'organe de commande de la conduite d'alimentation en fluide sous pression est une soupape d'alimentation (34) à commande électrique.
  11. Pompe d'injection de carburant selon la revendication 10,
    caractérisée en ce que
    la soupape de décharge (18) et la soupape d'alimentation (34) sont commandées entre les durées de fonctionnement dans lesquelles le piston de pompe effectue sa course de transfert, de préférence avec des rapports de travail variables pour modifier la pression régnant dans la chambre active (7) et qui commande le réglage du début chaque fois souhaité de la course de transfert.
EP94103494A 1993-04-08 1994-03-08 pompe à injection de carburant Expired - Lifetime EP0627552B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4311672A DE4311672A1 (de) 1993-04-08 1993-04-08 Kraftstoffeinspritzpumpe
DE4311672 1993-04-08

Publications (2)

Publication Number Publication Date
EP0627552A1 EP0627552A1 (fr) 1994-12-07
EP0627552B1 true EP0627552B1 (fr) 1999-12-01

Family

ID=6485117

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94103494A Expired - Lifetime EP0627552B1 (fr) 1993-04-08 1994-03-08 pompe à injection de carburant

Country Status (4)

Country Link
US (1) US5413080A (fr)
EP (1) EP0627552B1 (fr)
JP (1) JPH074272A (fr)
DE (2) DE4311672A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0814067A (ja) * 1994-06-24 1996-01-16 Zexel Corp 燃料噴射ポンプのサーボバルブ式タイマ
GB9826348D0 (en) * 1998-12-02 1999-01-27 Lucas Ind Plc Advance arrangement
DE19812698A1 (de) * 1998-03-23 1999-09-30 Volkswagen Ag Einrichtung zum Regeln des Spritzbeginns in einer Verteiler-Kraftstoffeinspritzpumpe für Verbrennungsmotoren
DE19935211A1 (de) * 1999-07-27 2001-02-01 Deutz Ag Hydraulischer Förderbeginn-Versteller
US20070056287A1 (en) * 2005-09-13 2007-03-15 Cyclone Technologies Lllp Splitter valve in a heat regenerative engine

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5339528B1 (fr) * 1971-03-06 1978-10-21
US4132508A (en) * 1974-10-01 1979-01-02 C.A.V. Limited Fuel injection pumping apparatus
DE2648043C2 (de) * 1976-10-23 1984-05-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE2923445A1 (de) * 1979-06-09 1980-12-18 Bosch Gmbh Robert Steuereinrichtung fuer eine kraftstoffeinspritzpumpe
DE3121635A1 (de) * 1981-05-30 1982-12-23 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3203583A1 (de) * 1982-02-03 1983-08-11 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit spritzzeitpunktverstellung
DE3822257A1 (de) * 1988-07-01 1990-01-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3827206A1 (de) * 1988-08-11 1990-02-15 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5180290A (en) * 1989-06-02 1993-01-19 Lucas Industries Fuel injection pumping apparatus
DE3943246A1 (de) * 1989-12-29 1991-07-04 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
GB9026013D0 (en) * 1990-11-29 1991-01-16 Lucas Ind Plc Fuel pumping apparatus
DE4117813A1 (de) * 1991-05-31 1992-12-03 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
WO1993021438A1 (fr) * 1992-04-09 1993-10-28 Lucas Industries Public Limited Company Appareil servant a pomper du carburant

Also Published As

Publication number Publication date
DE4311672A1 (de) 1994-10-13
EP0627552A1 (fr) 1994-12-07
DE59408957D1 (de) 2000-01-05
US5413080A (en) 1995-05-09
JPH074272A (ja) 1995-01-10

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