EP0290797B1 - Pompe d'injection de combustible - Google Patents

Pompe d'injection de combustible Download PDF

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Publication number
EP0290797B1
EP0290797B1 EP88105775A EP88105775A EP0290797B1 EP 0290797 B1 EP0290797 B1 EP 0290797B1 EP 88105775 A EP88105775 A EP 88105775A EP 88105775 A EP88105775 A EP 88105775A EP 0290797 B1 EP0290797 B1 EP 0290797B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
pump
valve
space
piston
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
EP88105775A
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German (de)
English (en)
Other versions
EP0290797A2 (fr
EP0290797A3 (en
Inventor
Anton Dipl.-Ing. Karle
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 EP0290797A2 publication Critical patent/EP0290797A2/fr
Publication of EP0290797A3 publication Critical patent/EP0290797A3/de
Application granted granted Critical
Publication of EP0290797B1 publication Critical patent/EP0290797B1/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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto

Definitions

  • the invention is based on a fuel injection pump according to the preamble of the main claim.
  • the controlling member is designed as a cylindrical evasive piston which is tightly guided in a cylinder bore open to the pump work space.
  • the spring chamber which always remains separate from the pump work chamber, is opened when the internal combustion engine is idling through an electrically pneumatically actuated valve to the relief line, so that the evasive piston can be adjusted by a path determined by a stop through the pressure prevailing in the pump work chamber when pumping the piston. This reduces the delivery rate of the pump piston when the engine is idling, but never stops the fuel injection. Such devices serve to make the combustion process softer in fuel injection pumps with low speeds.
  • the relief line of the spring chamber is either permanently open when idling, or permanently closed at partial load or full load.
  • a fuel injection pump of the generic type is known from EP-A2 0 116 168.
  • the relief space is delimited by the controlling member in the form of a piston, which at the same time represents a sliding wall for changing the volume of the relief space.
  • the controlling member is moved against the force of a first and a second spring, both by one in one Cylinder bore tightly guided spring plate are separated.
  • the position of this spring plate and thus the resetting characteristic of the spring arrangement is determined by a control pressure which is introduced into the space receiving the spring directly acting on the controlling member.
  • the controlling member is thus moved against this control pressure and also against the spring clamped in this space.
  • the control pressure is changed in one embodiment by a pressure-dependent pressure of the pressure source and in the other case by clocked relief of the spring-receiving space, which is now decoupled from the pressure source by means of a throttle.
  • the pressure curve of the high-pressure delivery stroke of the fuel injection pump is to be subdivided into a pre-injection and a main injection, with the aid of the removal space and the controlled member, the injection pause between the pre-injection and the main injection and thus the amount of the fuel pre-injection is controlled.
  • the control pressure can be changed as a function of speed, temperature and load, so that depending on these parameters, a differently large extraction volume per delivery stroke of the pump piston is provided.
  • the high-pressure delivery phase of the pump piston is controlled independently of the control of the relief space by controlling a separate relief channel of the pump work space.
  • the point of use of the main injection or the end of the pre-injection depends on the dynamic behavior of the controlling member and the spring arrangement loading it in connection with the controlling control pressure. At different speeds, there may be deviations in the control times between the pilot injection quantity and the main injection quantity.
  • a fuel injection pump is also known, in which the fuel injection quantity takes place with the aid of a servo valve.
  • the relief line of the pump work space is again controlled to control the fuel injection quantity by means of a flat seat valve which consists of a piston which can be displaced in a cylinder and which opens the connection of the relief line to a relief space from a certain displacement path.
  • this piston encloses a volume which can also be connected to the relief chamber by means of a second relief line which is controlled by a solenoid valve.
  • the solenoid valve is closed, the volume behind the piston is locked in and prevents the piston from evading and thus opening of the relief line when the pump piston delivery stroke begins.
  • US-A-4 590 908 discloses a fuel injection pump in which the pump work space can also be connected to a relief space via a relief line controlled by a servo valve in order to control the fuel injection quantity.
  • the servo valve also consists here, as in the foregoing, of a piston sliding in a cylinder, the front edge of which, after lifting off a flat valve seat, opens the connection of the relief line to the relief chamber.
  • the piston is held in the closed position by a spring, which is on the pump working space attacks the rear of the piston.
  • This back of the piston in turn encloses in the cylinder receiving the piston a pressure chamber which can be relieved via a second relief line which is controlled by a solenoid valve.
  • the pump work space is constantly connected to the rear of the piston via a throttle connection.
  • this pressure is also effective on the rear of the piston when the pump working chamber pressure rises, so that the piston can be held in the closed position by the return spring without great difficulty. If the space on the back of the piston is relieved via the second relief line when the solenoid valve is opened, more fuel flows out there than can flow in via the throttle, so that the pump working chamber pressure brings the piston into the open position against the spring.
  • This servo valve arrangement is provided in the known fuel injection pump for controlling the start of injection and the end of injection.
  • the start of injection in the course of the delivery stroke of the pump piston is controlled by closing the solenoid valve, the return spring bringing the piston into the closed position, which is then held as a result of the pump working space pressure which continues to rise and is also effective in the rear space of the piston.
  • the solenoid valve opens, the fuel injection is ended, which also determines the fuel injection quantity. A pre-injection is not provided in this known pump.
  • the fuel injection pump according to the invention has the advantage that a pre-injection is possible in the entire speed-load range and the distance pre-injection to main injection can be set variably.
  • only one control device is required when using a plurality of injection nozzles.
  • the control device can work with a single pressure valve or a constant pressure valve and is constructed in such a way that the pump piston drive is also prevented from jumping off the drive cam.
  • FIG. 1 An embodiment of the invention is shown in the drawing and is explained in the following description.
  • the figure shows a partial section through a fuel injection pump.
  • the figure shows a part of a known distributor injection pump schematically in section.
  • the figure discloses a pump piston 1, which slides in a cylinder 9 and is set in a reciprocating, pumping and rotating movement by a cam drive, not shown.
  • the pump piston 1 delimits a pump work space 2.
  • This pump work space 2 is filled via filling grooves 14 which come into contact with a suction line 5 during the suction stroke of the pump piston 1.
  • the suction line 5 branches off from a suction space 6 which is filled with fuel which is subjected to speed-dependent pressure.
  • the pump piston 1 of this fuel injection pump acts as a distributor during operation, fuel being conveyed from the pump working chamber 2 via an injection line 12 to the injection valve 41 via a longitudinal or distributor bore 48 in the pump piston 1.
  • a relief line 4 leads away from the pump work space 2 and cooperates with a valve closing element 7 which controls the relief line 4.
  • This valve closing member 7 is part of a pressure valve 50 and has a valve cone 35 on the underside, which cooperates with a valve seat 32 attached to the relief line 4.
  • This valve closing member 7 slides back and forth with guide ribs 51 on its shaft in a cylinder 43 surrounding the pressure valve 50.
  • this valve closing member 7 is provided with longitudinal grooves 52, which begin at the valve cone 35.
  • the valve closing member 7 is acted upon by a return spring 8.
  • the return spring 8 is placed in a relief chamber 10 under tension so that it presses the closing member 7 onto the valve seat 32.
  • the return spring 8 is accommodated in the cylindrical space, in the relief space 10, from which a second relief line 22 with a valve seat 15 leads away.
  • This valve seat 15 acts with a valve closing member 18 of an electrically controlled valve, here a solenoid valve 11 together.
  • the valve closing member 18 is designed as an armature of the solenoid valve with a conical tip 44, which has a sealing surface 45, and comes to rest on the valve seat 15 of the second relief line 22.
  • a return line 16 leads from the relief chamber 10 to the suction chamber 6 via the valve seat 15 and the second relief line 22.
  • a spring 46 which cooperates with a part 47 connected to the armature, ensures that the armature of the solenoid valve 11 lifts off the valve seat 15 in the de-energized, non-activated state.
  • valve closing member 7 Only when the pressure in the pump work chamber 2 increases further is the force of the return spring 8 of the valve closing member 7 overcome, and now the fuel can pass through the longitudinal grooves 52 of the valve closing member 7 to the relief chamber 10, the second relief line 22, which is open in the uncontrolled state, and the return line 16 flow to the suction space 6. With the opening process, the valve closing member 7 is suddenly loaded on a larger area by the pressure of the pump work space and quickly brought into the fully open position. With this backflow of the fuel into the suction chamber 6, the pressure in the pump working chamber 2 is reduced again, so that the pressure drops below the level that was present at the beginning in order to push the valve needle 54 away from the valve seat 55 and that led to the pre-injection.
  • the solenoid valve 11 When the injection valve 41 is closed, the solenoid valve 11 is actuated at the same time, as a result of which the valve seat 45 on the armature 18 presses onto the valve seat 15 and closes the second relief line 22 Cam drive takes place, the above-mentioned pressurized parts are pressurized, and the valve closing member 7 is brought back into the closed position by the return spring 8.
  • the fuel that continues to be delivered can now only flow to the injection valve 41 via the longitudinal bore 48 in the pump piston 1, the distributor groove 30, the delivery line 12. Therefore, the valve needle 54 of the injection valve 41 lifts off the valve seat 55 and the main injection occurs.
  • the duration is determined by the time in which the solenoid valve 11 remains closed. If the solenoid valve 11 opens, the back of the valve closing member 7 is suddenly relieved and the valve closing member is opened immediately due to the high pressure in the pump work space, so that the pump work space is relieved and the injection is ended.
  • valve closing member 7 Another alternative embodiment is shown in dashed lines in the figure.
  • a through hole 56 is made, into which a pressure spring-loaded ball valve 57 is introduced on one side, through which the relief chamber 10 can flow.
  • no feed line 5 from the suction chamber 6 to the pump work chamber 2 is required.
  • a line with a ball valve leading around the valve closing element 7 could also be installed.
  • the fuel could get from the suction chamber 6 via the return line 16, the second relief line 22, the through bore 56, the ball valve 57, the first relief bore 4 into the pump work chamber 2.
  • the fuel injection pump according to the invention can also be operated without pre-injection if the solenoid valve 11 remains closed from the beginning.
  • the pump piston 2 is moved upward, so that the fuel entering the pump work chamber 2 via a feed line 5 and a filling groove 14 begins to compress and the pressure in the pump work chamber 2 increases.
  • the increase in pressure opens the injection valve 41.
  • the valve closing member 7 is closed and the solenoid valve 11 is closed.
  • the rotation of the cam continues, the pump piston 1 moves upward, compresses more and injects until the solenoid valve 11 opens.
  • the pressure in the pump work chamber 2 is reduced via the return line 16 and the injection valve 41 closes. A new cycle can begin.

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 carburant pour moteur à combustion interne, comprenant au moins un piston de pompe (1) et une chambre de travail (2) délimitée par ce piston et qui, lors de la course de transfert du piston de pompe (1), peut être reliée par une conduite d'injection de carburant (12) à un injecteur de carburant (14) et par une première conduite de décharge (4), commandée par un organe de commande (7) avec une chambre de décharge (10), l'organe de commande (7) étant sollicité dans la direction d'ouverture par la pression régnant dans la chambre de travail de la pompe agissant sur une surface plus faible pour la position de fermeture que lorsque cet organe de commande est en position d'ouverture, contre la force d'un ressort de rappel (8) logé dans une chambre ressort (10) qui peut elle-même être évacuée par une seconde conduite de décharge (22) contenant une électrovanne, pompe caractérisée en ce que la chambre à ressort (10) peut être déchargée seulement par l'intermédiaire de la seconde conduite de décharge (22) lorsque l'organe de commande (7) est en position de fermeture et cette chambre constitue par ailleurs une chambre fermée, et lorsque l'organe (7) est en position d'ouverture, la chambre (10) est reliée par la section d'écoulement (52) à la première conduite de décharge (4), la pression d'ouverture de l'organe de commande (7), lorsque la seconde conduite de décharge (22) est ouverte, étant supérieure à la pression d'ouverture de l'injecteur (41).
  2. Pompe d'injection de carburant selon la revendication 1, caractérisée en ce que la chambre à ressort (10) peut être reliée à la première conduite de décharge (4) par une soupape anti-retour (57) qui s'ouvre dans la direction de la chambre de travail (2) de la pompe.
  3. Pompe d'injection de carburant selon la revendication 1 ou 2, caractérisée en ce que l'organe (7) peut être soumis à l'action d'un ressort de rappel (8) réglable selon les paramètres de fonctionnement du moteur à combustion interne.
  4. Pompe d'injection de carburant selon l'une des revendications précédentes, caractérisée en ce que la section de passage de la seconde conduite de décharge (22) peut être modifiée par palier par l'électrovanne au cours d'une phase d'injection de carburant.
  5. Pompe d'injection de carburant selon l'une des revendications précédentes, caractérisée en ce que dans une première plage de travail de la pompe, l'électrovanne s ouvre pour commander une quantité de pré-injection de carburant au début de la course de transfert du piston de la pompe et qu'à partir d'une certaine course de transfert du piston de la pompe cette électrovanne se ferme pour commander le début de l'injection principale et au début de l'injection de carburant l'électrovanne s'ouvre de nouveau et dans la seconde plage de travail, l'électrovanne (11) est fermée au début de la course de transfert du piston de la pompe et s'ouvre pour terminer l'injection de carburant.
  6. Pompe d'injection de carburant selon l'une des revendications précédentes, caractérisée en ce que la pompe est une pompe d'injection distributrice.
EP88105775A 1987-05-11 1988-04-12 Pompe d'injection de combustible Expired - Lifetime EP0290797B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873715614 DE3715614A1 (de) 1987-05-11 1987-05-11 Kraftstoffeinspritzpumpe
DE3715614 1987-05-11

Publications (3)

Publication Number Publication Date
EP0290797A2 EP0290797A2 (fr) 1988-11-17
EP0290797A3 EP0290797A3 (en) 1989-10-18
EP0290797B1 true EP0290797B1 (fr) 1992-04-01

Family

ID=6327245

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88105775A Expired - Lifetime EP0290797B1 (fr) 1987-05-11 1988-04-12 Pompe d'injection de combustible

Country Status (4)

Country Link
US (1) US4840155A (fr)
EP (1) EP0290797B1 (fr)
JP (1) JPS63295854A (fr)
DE (2) DE3715614A1 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3722264A1 (de) * 1987-07-06 1989-01-19 Bosch Gmbh Robert Kraftstoffeinspritzanlage fuer brennkraftmaschinen
DE3819996A1 (de) * 1988-06-11 1989-12-14 Bosch Gmbh Robert Hydraulische steuereinrichtung insbesondere fuer kraftstoffeinspritzanlagen von brennkraftmaschinen
EP0348865A3 (fr) * 1988-06-27 1990-10-10 Nippondenso Co., Ltd. Dispositif à injection-pilote pour pompes à injection de combustible
DE3929747A1 (de) * 1989-09-07 1991-03-14 Bosch Gmbh Robert Verfahren und einrichtung zum steuern der kraftstoffeinspritzung
DE3934953A1 (de) * 1989-10-20 1991-04-25 Bosch Gmbh Robert Magnetventil, insbesondere fuer kraftstoffeinspritzpumpen
FR2678025A1 (fr) * 1991-06-21 1992-12-24 Bosch Gmbh Robert Procede et dispositif pour commander un systeme de dosage de carburant commande par une electrovanne, notamment pour moteur diesel a combustion interne.
GB9203636D0 (en) * 1992-02-19 1992-04-08 Lucas Ind Plc Fuel pumping apparatus
GB9322850D0 (en) * 1993-11-05 1993-12-22 Lucas Ind Plc Control valve
US5873527A (en) * 1997-02-19 1999-02-23 Caterpillar Inc. Fuel injector with regulated plunger motion
US5979415A (en) * 1997-11-12 1999-11-09 Caterpillar Inc. Fuel injection pump with a hydraulically-spill valve
US6102004A (en) * 1997-12-19 2000-08-15 Caterpillar, Inc. Electronic control for a hydraulically activated, electronically controlled injector fuel system and method for operating same
JP2000186649A (ja) * 1998-12-24 2000-07-04 Isuzu Motors Ltd 吐出量可変制御型高圧燃料ポンプ
US6347614B1 (en) 1999-07-23 2002-02-19 Lawrence W. Evers Mechanical fuel injection system
US6824081B2 (en) 2002-06-28 2004-11-30 Cummins Inc. Needle controlled fuel injector with two control valves
JP6222623B2 (ja) * 2015-12-24 2017-11-01 マツダ株式会社 圧縮自己着火式エンジンの燃料噴射制御方法及び燃料噴射制御装置
DE102018206334A1 (de) * 2018-04-25 2019-10-31 Robert Bosch Gmbh Kraftstofffördereinrichtung für kryogene Kraftstoffe
CN117738826B (zh) * 2024-02-19 2024-05-03 江苏中奕和创智能科技有限公司 一种带有控油组件的柴油发电机

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58149566U (ja) * 1982-03-31 1983-10-07 株式会社デンソー 分配型燃料噴射ポンプ
DE3211877A1 (de) * 1982-03-31 1983-10-06 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
JPS5951139A (ja) * 1982-09-17 1984-03-24 Nippon Soken Inc 燃料供給装置
DE3245142A1 (de) * 1982-12-07 1984-06-07 Robert Bosch Gmbh, 7000 Stuttgart Verfahren und vorrichtung zum einspritzen von kraftstoff
DE3300876A1 (de) * 1983-01-13 1984-07-19 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
JPS6098146A (ja) * 1983-11-02 1985-06-01 Nippon Soken Inc 内燃機関の燃料制御方法
DE3629751C2 (de) * 1986-09-01 1998-07-02 Bosch Gmbh Robert Voreinspritzvorrichtung für Brennkraftmaschinen

Also Published As

Publication number Publication date
EP0290797A2 (fr) 1988-11-17
DE3715614A1 (de) 1988-11-24
EP0290797A3 (en) 1989-10-18
US4840155A (en) 1989-06-20
DE3869652D1 (de) 1992-05-07
JPS63295854A (ja) 1988-12-02

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