EP0240686B1 - Pompe d'injection de combustible pour moteurs à combustion interne à recirculation des gaz d'échappement - Google Patents

Pompe d'injection de combustible pour moteurs à combustion interne à recirculation des gaz d'échappement Download PDF

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Publication number
EP0240686B1
EP0240686B1 EP87102705A EP87102705A EP0240686B1 EP 0240686 B1 EP0240686 B1 EP 0240686B1 EP 87102705 A EP87102705 A EP 87102705A EP 87102705 A EP87102705 A EP 87102705A EP 0240686 B1 EP0240686 B1 EP 0240686B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
outlet
channel
injection pump
pump
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
EP87102705A
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German (de)
English (en)
Other versions
EP0240686A1 (fr
Inventor
Karl Konrath
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 EP0240686A1 publication Critical patent/EP0240686A1/fr
Application granted granted Critical
Publication of EP0240686B1 publication Critical patent/EP0240686B1/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
    • 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
    • F02M41/126—Variably-timed valves controlling fuel passages valves being mechanically or electrically adjustable sleeves slidably mounted on rotary 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
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/59—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor
    • F02M26/62—Systems for actuating EGR valves using positive pressure actuators; Check valves therefor in response to fuel pressure

Definitions

  • the invention is based on a fuel injection pump for internal combustion engines with exhaust gas recirculation according to the preamble of claim 1.
  • a centrifugal adjuster is provided which is adjustable depending on the preload of a control spring against which the centrifugal adjuster works as a speed sensor.
  • the adjustment of the control spring is entered arbitrarily as a torque request or as a load signal.
  • the centrifugal adjuster opens a connection channel between a fuel-filled interior with a predetermined pressure level and a relief chamber, such that the amount flowing off is at least partly a measure of the load.
  • the outflowing fuel is throttled at a throttle and thus a control pressure is generated upstream of the throttle, which in turn is to be load-dependent and now acts on a hydraulically actuatable control element by means of which a circuit can be closed.
  • a switching valve which controls an actuating medium to an exhaust gas recirculation valve motor.
  • a fuel injection pump the pump piston of which contains a second channel, but this second channel connects an annular groove provided in the control slide valve on the pump piston side, one boundary edge of which is designed as the control edge controlling the relief channel, with one the annular groove surrounding the pump carbons in the area of the cylinder, which is in turn connected to a fuel inlet of the pump work space.
  • the second channel serves to supply the fuel quantity flowing out of the working space after the high-pressure injection has ended again to the suction side of the fuel injection pump, specifically into a memory which is decoupled from a controlled suction throttle via a check valve opening towards the pump working space .
  • Such a device is intended to achieve an exact metering of the fuel quantity which is controlled as a function of the air flow and is to be injected. This is done via the controlled suction throttle and the inclusion of the scrapped residual amount in the filling of the pump work space per filling cycle of the fuel injection pump.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that for controlling the exhaust gas recirculation valve, the position of the control slide, which is directly decisive for the metering of the injection quantity required for the respective load condition, is used as a measure of the operating load of the internal combustion engine. Another advantage is that, apart from determining the distance of the outlet of the relief channel from the inlet of the other channel in the pump piston, no adjustment or assignment work is required. Another advantage is that the speed-dependent delivery pressure of a delivery pump, which also prevails in the suction chamber of the injection pump receiving the control slide, is used to convert the position of the control slide into an electrical signal.
  • a cylinder liner 3 is inserted, in the cylinder 2 of which a pump piston 4 is displaceable, which is set into a reciprocating and at the same time rotating movement by a drive (not shown).
  • the pump piston 4 closes off one end of a pump working chamber 5 and protrudes with its other end out of the cylinder liner 3 into a suction chamber 7 of the housing 1. At this end the pump piston 4 is connected to the drive (not shown in more detail).
  • the pump working chamber 5 is supplied with fuel from the pump suction chamber 7 via longitudinal grooves 8 arranged in the lateral surface of the pump piston 4 and a suction bore 9 running through the cylinder liner 3 and the housing 1, as long as the pump piston 4 executes its suction stroke or its lower one shown in FIG. 1 Dead center position occupies.
  • a feed pump 10 feeds fuel from a fuel reservoir 11 into the suction space 7 of the housing 1 as the pressure increases as a function of the speed.
  • a pressure control valve 12 connected in parallel with the feed pump 10 controls the pressure in the pump suction space 7 in a known manner as a function of the speed.
  • a radial bore 16 branches off from this relief channel 15 and leads to a distributor groove 17 in the lateral surface of the pump piston 4.
  • a plurality of delivery lines 18 branch off in a radial plane of the cylinder 2 and are arranged distributed uniformly on the circumference of the cylinder 2 in accordance with the number of cylinders of the assigned internal combustion engine to be supplied with fuel.
  • the delivery lines 18 lead to the fuel injection points, not shown, of the internal combustion engine.
  • a radial bore 20 branches off from the relief channel 15 and forms an outlet A in the outer surface of the pump piston 4.
  • an annular regulating slide 21 is displaceably arranged on the pump piston 4 as a quantity adjusting member, the end face of which facing the cylinder liner 3 forms a control edge 22 for the outlet A.
  • the control slide 21 is from a control device, not shown, due to several operating parameters, such as desired speed, speed, air pressure, temperature and. Like. Axially adjusted to the pump piston 4 via a control lever 23.
  • control slide 21 assumes a position shown in the figure, in which, in the bottom dead center position of the pump piston 4, the distance between the outlet A of the relief channel 15 and the control edge 22 of the control slide 21 has the dimension s v .
  • the control slide 21 is adjusted to the left with reference to the drawing, so that the distance between the outlet A and the control edge 22 is reduced.
  • the useful stroke available in each case, which the pump piston 4 or the outlet A must travel from the bottom dead center of the pump piston 4, is thereby changed.
  • the position of the control edge 22 of the control slide 21 is therefore decisive for the respective size of the injection quantity in a specific load range of the internal combustion engine.
  • the pump piston 4 there is also a second channel 25, from which a radial bore 26 with an outlet B branches off in the area of the pump piston section which is always in the cylinder 2, and a radial bore 27 with an inlet E branches off in the effective range of the control slide 21.
  • the inlet E of the channel 25 to the control edge 22 of the control slide 21 has a distance SL which is greater than the distance Sv of the outlet A of the relief channel 15 from the control edge 22, so that the inlet E of the channel 25 to the outlet A of the relief channel 15 is offset by a certain distance.
  • the channel 25 is only opened during the stroke of the pump piston 4 after the outlet A of the relief bore 15 has already been opened.
  • the control slide 21 is adjusted to its rightmost position (drawing)
  • the inlet E of the channel 25 is not opened at all during the pressure stroke of the pump piston 4.
  • the inlet E is released by the control slide 21 towards the end of the pressure stroke of the pump piston 4 when the control slide assumes a position in the partial load range which is to the left of the position shown in the drawing and in which the outlet A of the relief bore 15 is already opened during the pump piston stroke is when the inlet E of the channel 25 reaches the control edge 22 of the control slide 21.
  • annular groove 28 is arranged in the cylinder liner 3, which is connected via a radial bore 29 in the cylinder liner 3 and a bore 30 to a blind bore 31.
  • a bore 32 branches off from the blind bore 31 to an outflow throttle 33, from which a line 34 leads to the unpressurized fuel reservoir 11.
  • a pressure switch 35 known per se is screwed into the blind bore 31 and closes an electrical contact 37 at a pressure which is in the range of the delivery pressure prevailing in the suction chamber 7 and thus generates an electrical signal for controlling an exhaust gas recirculation valve of the internal combustion engine.
  • the application of fuel to the pressure switch 35 from the suction space 7 and the pressure prevailing there is controlled as a function of the position of the control slide 21.
  • the inlet of the channel 25, which is connected to the pressure switch 35 via the annular groove 28 and the bores 29 and 30, is not opened when the control slide 21 is in the fully loaded position during the remaining stroke of the pump piston 4 after opening A has been opened, so that the pressure-relieved via the outflow throttle 33 blind bore 31 and thus the pressure switch 35 are depressurized.
  • the inlet E of the channel 25 is opened towards the end of the pressure stroke of the pump piston 4, so that the pressure in the suction space 7 through the channel 25 and the bores 29, 30 can act on the pressure switch 35.
  • the contact 37 of the pressure switch 35 is closed, so that an electrical control signal is generated that can be used directly to open the exhaust gas recirculation valve of the internal combustion engine or serves as a control signal.
  • a Throttle 36 can be arranged in the radial bore 29 in the cylinder liner 3.
  • a pressure-sensitive sensor element can be arranged instead of the pressure switch, which sensor element emits a proportional electrical signal depending on the control pressure.

Landscapes

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

Claims (6)

1. Pompe d'injection de combusubfe pour moteurs à combustion interne à recirculation des gaz d'échappement, pourvue d'un élément de commande (35) électrique, actionné en fonction de la charge servant à émettre un signal électrique pour commander une soupape de retour des gaz d'échappement, et pourvue d'un piston (4) entraîné dans un cylindre (2) en étant animé d'un mouvement de va-et-vient en même temps que de rotation, et obturant une chambre de travail (5) de la pompe, piston dans lequel est ménagé un canal de décharge (15) relié en permanence à la chambre de travail de la pompe, et pourvue également d'un coulisseau de réglage (21) qui entoure le piston de la pompe dans une chambre (7) soumise à l'action de la pression du combustible, et peut être déplacé en fonction de la charge, et qui obture la sortie (A) du canal de décharge pendant une partie variable de la trajectoire de la course du piston de la pompe, l'élément de commande (35) s'actionnant par voie hydraulique, pompe d'injection caractérisée en ce que dans le piston (4) de la pompe est ménagé un second canal (25), dont la sortie (B) est en liaison avec une conduite (29, 30) menant à l'élément de commande (35), et dont l'entrée (E) est prévue dans la zone d'action du coulisseau de réglage (21) à un e certaine distance de la sortie (A) du canal de décharge (15) de telle manière, que l'entrée (E) du canal (25) n'est ouverte que lorsque la sortie du canal de décharge a déjà son ouverture commandée.
2. Pompe d'injection de combustible selon la revendication 1, caractérisé en ce que l'entrée (E) du canal (25) est éloignée de la sortie (A) du canal de décharge (15) d'une distance qui est supérieure à la course résiduelle du piston (4) de la pompe après ouverture de la sortie (A) par le coulisseau de réglage (21) lors de la position de celui-ci en pleine charge.
3. Pompe d'injection de combustible selon la revendication 1 ou 2, caractérisée en ce qu'un étranglement d'écoulement (33) est relié à l'endroit du raccordement de l'élément de commande (35).
4. Pompe d'injection de combustible selon la revendication 3, caractérisée en ce qu'un étranglement (36) est prévu dans la conduite (29, 30) menant à l'élément de commande (35).
5. Pompe d'injection de combustible selon l'une des revendications 1 à 4, caractérisée en ce que l'élément de commande est un commutateur électrique (35).
6. Pompe d'injection de combustible selon l'une des revendications 1 à 4, caractérisé en ce que l'élément de commande est un détecteur de pression, qui émet un signal électrique proportionnel à la pression qui s'exerce.
EP87102705A 1986-04-10 1987-02-26 Pompe d'injection de combustible pour moteurs à combustion interne à recirculation des gaz d'échappement Expired - Lifetime EP0240686B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3612068 1986-04-10
DE19863612068 DE3612068A1 (de) 1986-04-10 1986-04-10 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen mit abgasrueckfuehrung

Publications (2)

Publication Number Publication Date
EP0240686A1 EP0240686A1 (fr) 1987-10-14
EP0240686B1 true EP0240686B1 (fr) 1990-05-02

Family

ID=6298389

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87102705A Expired - Lifetime EP0240686B1 (fr) 1986-04-10 1987-02-26 Pompe d'injection de combustible pour moteurs à combustion interne à recirculation des gaz d'échappement

Country Status (4)

Country Link
US (1) US4718385A (fr)
EP (1) EP0240686B1 (fr)
JP (1) JPS62261662A (fr)
DE (2) DE3612068A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3644147A1 (de) * 1986-12-23 1988-07-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3644583A1 (de) * 1986-12-27 1988-07-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3740968C1 (de) * 1987-12-03 1988-12-15 Bosch Gmbh Robert Abgasrueckfuehreinrichtung fuer Brennkraftmaschinen
DE4106813A1 (de) * 1991-03-04 1992-09-10 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE19713868A1 (de) * 1997-04-04 1998-10-08 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
US5865156A (en) * 1997-12-03 1999-02-02 Caterpillar Inc. Actuator which uses fluctuating pressure from an oil pump that powers a hydraulically actuated fuel injector
US6050248A (en) * 1997-12-03 2000-04-18 Caterpillar Inc. Exhaust gas recirculation valve powered by pressure from an oil pump that powers a hydraulically actuated fuel injector
US6148805A (en) * 1998-12-15 2000-11-21 Caterpillar Inc. Engine with hydraulic fuel injection and EGR valve using a single high pressure pump
JP3771454B2 (ja) * 2001-02-21 2006-04-26 本田技研工業株式会社 内燃機関の制御装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2520812A1 (fr) * 1982-02-03 1983-08-05 Bosch Gmbh Robert Pompe d'injection de carburant pour moteurs a combustion interne

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2353737A1 (de) * 1973-10-26 1975-05-07 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE2448693C2 (de) * 1974-10-12 1983-11-24 Robert Bosch Gmbh, 7000 Stuttgart Drehzahlregler für eine Verteilereinspritzpumpe
DE2855027A1 (de) * 1976-12-22 1980-07-10 Bosch Gmbh Robert Einrichtung zur betaetigung eines auf eine abgasrueckfuehrsteuereinrichtung wirkenden stellorgans bei brennkraftmaschinen
US4090950A (en) * 1977-04-26 1978-05-23 Sun Petroleum Products Company Process for manufacturing refrigeration oils
DE2841807A1 (de) * 1978-09-26 1980-04-03 Bosch Gmbh Robert Einrichtung zum regeln des mengenverhaeltnisses luft/kraftstoff bei brennkraftmaschinen
JPS5627058A (en) * 1979-08-13 1981-03-16 Toyota Motor Corp Exhaust gas recycling controller in internal combustion engine
DE2946557A1 (de) * 1979-11-17 1981-05-27 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zur steuerung einer abgasrueckfuehrvorrichtung bei brennkraftmaschinen
DE3013087A1 (de) * 1980-04-03 1981-10-15 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer selbstzuendende brennkraftmaschinen
JPS57137644A (en) * 1981-02-19 1982-08-25 Mazda Motor Corp Exhaust gas recirculation device for diesel engine
US4411242A (en) * 1981-04-03 1983-10-25 Nippon Soken, Inc. Method and apparatus for controlling EGR in internal combustion engine
DE3135234A1 (de) * 1981-09-05 1983-03-17 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zur lastabhaengigen betaetigung eines stellorgans einer brennkraftmaschine
DE3138606A1 (de) * 1981-09-29 1983-04-14 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JPS5885353A (ja) * 1981-11-17 1983-05-21 Nissan Motor Co Ltd 内燃機関の排気還流制御装置
US4537170A (en) * 1984-02-28 1985-08-27 Diesel Kiki Co., Ltd. Distribution type fuel injection pump
DE3424883A1 (de) * 1984-07-06 1986-02-06 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JP3363031B2 (ja) * 1996-06-24 2003-01-07 株式会社クボタ スラグの洗浄方法及びスラグ洗浄装置

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2520812A1 (fr) * 1982-02-03 1983-08-05 Bosch Gmbh Robert Pompe d'injection de carburant pour moteurs a combustion interne

Also Published As

Publication number Publication date
US4718385A (en) 1988-01-12
DE3612068A1 (de) 1987-10-15
JPS62261662A (ja) 1987-11-13
DE3762536D1 (de) 1990-06-07
EP0240686A1 (fr) 1987-10-14

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