EP0530206A1 - Pompe d'injection de carburant pour moteurs a combustion interne. - Google Patents

Pompe d'injection de carburant pour moteurs a combustion interne.

Info

Publication number
EP0530206A1
EP0530206A1 EP91907821A EP91907821A EP0530206A1 EP 0530206 A1 EP0530206 A1 EP 0530206A1 EP 91907821 A EP91907821 A EP 91907821A EP 91907821 A EP91907821 A EP 91907821A EP 0530206 A1 EP0530206 A1 EP 0530206A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel
pump
channel
fuel injection
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.)
Granted
Application number
EP91907821A
Other languages
German (de)
English (en)
Other versions
EP0530206B1 (fr
Inventor
Wolfgang Fehlmann
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 EP0530206A1 publication Critical patent/EP0530206A1/fr
Application granted granted Critical
Publication of EP0530206B1 publication Critical patent/EP0530206B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means

Definitions

  • the invention is based on a fuel injection pump for internal combustion engines according to the preamble of the patent claim.
  • a check valve opening in the direction of flow to the fuel supply and the suction space of a distributor fuel injection pump is arranged downstream of the solenoid valve in the fuel channel.
  • the rear of the check valve in the filling channel is connected to the fuel channel.
  • the function of this device is to prevent the check valve serving to fill the pump work chamber in the event of the electrically operated valve getting stuck in its closed position, which would be associated with an excess of fuel delivered with each pump piston delivery stroke, since between the electrically operated valve Valve and the check valve of the fuel channel a counter pressure determined by the opening pressure of the check valve in the fuel channel is present, which is greater than the opening pressure which acts on the check valve in the filling channel.
  • This prevents the internal combustion engine from being damaged as a result of the malfunction of the electrically operated valve.
  • the electrically operated valve must be equipped with a sufficiently large passage cross-section so that the injection phase can be ended quickly and the pump work space can also be filled from the fuel supply at a constant pressure during its filling stroke.
  • This large cross section makes the electrically operated valve more expensive, which is preferably designed as a solenoid valve.
  • the actuation time becomes longer with increasing opening cross section, which is disadvantageous for exact and fast control in all speed ranges of the internal combustion engine.
  • the fuel injection pump according to the invention with the characterizing features of claim 1 has the advantage that the electrically controlled valve only has to serve the requirements for relieving the pump work space. To this end, it is sufficient to reduce the pressure in the pump work chamber to a certain level at the end of the injection without the latter immediately having to assume the pressure of the fuel supply.
  • the cross section of the check valve in the filling channel is also available for filling the pump working space during the suction stroke of the pump piston. This ensures that the pump work space is always sufficiently filled to a desired size even with a small cross section of the electrically operated valve and thus a small size.
  • the switching times of the electrically operated valve can be shorter for a given size and for a given effort.
  • FIG. 1 the schematic structure of a distributor fuel injection pump of the reciprocating type is shown.
  • a pump piston 1 moves back and forth in a pump cylinder 2 driven by a cam disk 6 running on a roller ring 4 (here pivoted by 90 ° and shown offset) and rotating at the same time.
  • the pump piston also serves as a distributor, alternately actuating one of several injection lines 7 arranged around the pump cylinder 2 via a distributor groove 8 in the course of its rotation.
  • the distributor groove is permanently connected via a longitudinal channel 9 in the pump piston to a pump work space 10 enclosed by the pump piston in the pump cylinder 2.
  • the injection lines each lead via a pressure valve 12 to an injection valve 13.
  • the pump piston During the suction stroke of the pump piston - the pump piston is held on the cam disk by a spring (not shown here) and this is held on the rollers of the roller ring - fuel is supplied via a filling channel 15, in which a check valve 16 opening in the direction of the pump work chamber is arranged, is connected to a pump suction chamber 17, which serves as a fuel supply.
  • the pump suction chamber is supplied with fuel by a fuel delivery pump 18 from a fuel tank 19 and is kept at a certain pressure via a pressure control valve 20.
  • the pump suction chamber is also connected to the fuel tank or to the suction side of the fuel feed pump 18 via a flushing throttle 22 and is connected to a working chamber 24 in front of an injection start piston 25 via a decoupling throttle 23.
  • the working space 24 is clocked or relieved analogously via an electromagnetic valve 27 and a downstream throttle 28 to the reservoir 19, so that the pressure in the working space can be modified independently of the pressure in the suction space 17 if the electromagnet is actuated accordingly.
  • the pressure in the working chamber 24, which is set in this corresponding manner adjusts and adjusts the injection start adjusting piston against the force of a return spring 29 the rotational position of the roller ring 4.
  • This rotational position determines the start of the stroke of the pump piston with each pump piston stroke in the course of its rotation. A change in the start of spraying is thus achieved.
  • the rotational position of the roller ring can be detected by a transmitter 30 and reported back to a control device 31, which in turn controls the solenoid valve 27.
  • the fuel displaced by the pump piston can be displaced via a fuel channel 33, which has a part of the filling channel 15 located upstream of the check valve 16, as long as there is no pressure build-up in the pump working chamber 10, as long as one is used in the fuel channel 33 electrically controlled valve 34 is open.
  • the fuel channel 33 downstream of the electrically controlled valve is connected to the filling channel 15 downstream of the check valve 16.
  • the electrically controlled valve 34 is controlled by the control device 31, opened during the respective suction stroke of the pump piston, so that the pump working space can be filled with fuel via the fuel channel 33 and in parallel via the filling channel 15.
  • the fuel channel 33 can initially still be open, whereas the filling channel is closed by the check valve 16.
  • the electrically controlled valve closes, the high-pressure build-up in the pump work space then begins with the displacement of the displaced fuel via the longitudinal channel 9, the distributor groove 8 and the fuel injection line 7, which is actuated by the latter, to the fuel injection nozzle 13.
  • the electrical controlled is then again ended to end the high-pressure fuel delivery Solenoid valve 34 opened so that the pump working space can be relieved via the fuel line 33 to the pump suction chamber 17.
  • FIG. 2 shows an exemplary embodiment of the electrically controlled valve 34, in which the check valve 16 is integrated.
  • the valve is designed as an electromagnetic valve and has a valve housing 36 which adjoins the pump work chamber 10 according to FIG. 1 with its end face 37 and seals it tightly.
  • a guide bore 38 is provided in the valve housing, in which a stem 39 of the valve member 40 is guided.
  • the guide bore 38 opens into an annular space 41, in which the closing part 42 of the valve member 40 which adjoins the shaft 39 projects.
  • the closing part 42 has on its side facing away from the shaft 39 a conical sealing surface 43 which cooperates with a corresponding conical ring-shaped valve seat 44.
  • the valve seat delimits a bore 46 which extends coaxially to the guide bore 39 and into which an extension 47 of the valve member 40 projects, on which a return spring 48 is supported on the end face.
  • the return spring on the other hand, is supported in a narrowing part 49 of the bore 46, which merges into a passage opening 50 for the guide bore.
  • a conical seat 51 and a check valve 52 then adjoin the passage opening.
  • the check valve 52 has a hemispherical element, the ball surface 54 of which cooperates with the conical seat 51 as a sealing surface.
  • the valve closing member is acted upon by a closing spring 55, which is supported on a bore 56 extending from the conical seat 51, which now opens directly into the guide bore 38 in the pump work space.
  • a fuel channel 133 which corresponds to the fuel channel 33 of FIG. 1, leads into the valve housing, opens into the annular space 41 and leads from there via the annular valve seat into the bore 36, from where it leads as a transverse bore 58 to the fuel supply, the pump suction chamber 17.
  • the valve member is actuated by an electromagnet 60 which is integrated in the valve housing 36 in a manner not shown and which, when current is applied, presses the valve member 40 against the force of the return spring 48 on the valve seat and closes the fuel duct 33.
  • the pump piston can suck in fuel from the pump suction chamber 17 via the transverse bore 58, which is part of the fuel channel 33 from FIG. 1 or 133 from FIG. 3, and via the check valve 52.
  • the bore 46, the opening 50, the conical seat 51 and the bore 56 form the filling channel, which was designated 15 in the exemplary embodiment according to FIG.
  • the check valve is closed, in particular when the valve member 40 is also in the closed position, and when the magnet is not energized, the valve member 40 goes into the open position and ends the injection in a manner analogous to that described in FIG.
  • This version has the advantage that it is very compact and no unnecessary line connections, which also represent harmful rooms, are necessary.

Landscapes

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

Abstract

On propose une pompe d'injection de carburant pour moteurs à combustion interne, laquelle est munie, pour le débit d'injection de carburant amené par elle sous haute pression, d'une électrovanne (34) commandant un canal de carburant (33) menant depuis la chambre de travail de pompe (10) à la chambre d'aspiration de pompe (17) et servant de canal de décharge. Une fois l'électrovanne (34) fermée, du carburant peut être amené sous haute pression à l'injecteur de carburant (13). La même électrovanne sert lors de la course d'aspiration du piston de pompe au remplissage de la chambre de travail depuis la chambre d'aspiration (17). Afin de pouvoir garder étroits les diamètres de passage des électrovannes, on a prévu parallèlement à ces dernières un clapet de non-retour (16) dans un canal de remplissage (15) menant de la chambre d'aspiration (17) à la chambre de travail (10) de la pompe.
EP91907821A 1990-05-21 1991-04-25 Pompe d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0530206B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4016309 1990-05-21
DE4016309A DE4016309A1 (de) 1990-05-21 1990-05-21 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
PCT/DE1991/000341 WO1991018200A1 (fr) 1990-05-21 1991-04-25 Pompe d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0530206A1 true EP0530206A1 (fr) 1993-03-10
EP0530206B1 EP0530206B1 (fr) 1994-08-24

Family

ID=6406874

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91907821A Expired - Lifetime EP0530206B1 (fr) 1990-05-21 1991-04-25 Pompe d'injection de carburant pour moteurs a combustion interne

Country Status (6)

Country Link
US (1) US5343845A (fr)
EP (1) EP0530206B1 (fr)
JP (1) JP3027185B2 (fr)
DE (2) DE4016309A1 (fr)
ES (1) ES2059135T3 (fr)
WO (1) WO1991018200A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19648690A1 (de) * 1996-11-25 1998-05-28 Bosch Gmbh Robert Kraftstoffeinspritzsystem
US6128653A (en) * 1997-03-17 2000-10-03 Microsoft Corporation Method and apparatus for communication media commands and media data using the HTTP protocol
JPH11200990A (ja) * 1998-01-07 1999-07-27 Unisia Jecs Corp 燃料噴射制御装置
JP2000345901A (ja) * 1999-05-31 2000-12-12 Isuzu Motors Ltd 電子燃料噴射装置
US6298826B1 (en) 1999-12-17 2001-10-09 Caterpillar Inc. Control valve with internal flow path and fuel injector using same
US6647966B2 (en) 2001-09-21 2003-11-18 Caterpillar Inc Common rail fuel injection system and fuel injector for same
US9422898B2 (en) * 2013-02-12 2016-08-23 Ford Global Technologies, Llc Direct injection fuel pump

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2942010A1 (de) * 1979-10-17 1981-05-07 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
JPS5741462A (en) * 1980-08-25 1982-03-08 Mazda Motor Corp Fuel injection device for diesel engine
JPS57193729A (en) * 1981-05-25 1982-11-29 Nissan Motor Co Ltd Fuel shutoff device of fuel injection pump
DE3144361A1 (de) * 1981-11-07 1983-05-19 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzeinrichtung fuer brennkraftmaschinen
JPS59128967A (ja) * 1983-01-11 1984-07-25 Nissan Motor Co Ltd デイ−ゼルエンジンの燃料噴射ポンプ
DE3429129C2 (de) * 1984-08-08 1995-01-19 Bosch Gmbh Robert Dosiervorrichtung zur Zumessung von Flüssigkeitsmengen
US4643155A (en) * 1984-10-05 1987-02-17 Olin Corporation Variable stroke, electronically controlled fuel injection control system
DE3436768A1 (de) * 1984-10-06 1986-04-10 Robert Bosch Gmbh, 7000 Stuttgart Verfahren zur steuerung der kraftstoffeinspritzung bei brennkraftmaschinen und kraftstoffeinspritzsystem zur durchfuehrung des verfahrens
US4884549A (en) * 1986-04-21 1989-12-05 Stanadyne Automotive Corp. Method and apparatus for regulating fuel injection timing and quantity
DE3711744A1 (de) * 1987-04-07 1988-10-27 Bosch Gmbh Robert Verfahren und vorrichtung zur steuerung der kraftstoffeinspritzmenge
DE3722151A1 (de) * 1987-07-04 1989-01-12 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE4119467C2 (de) * 1991-06-13 1996-10-17 Daimler Benz Ag Nach dem Verdrängerprinzip arbeitende Vorrichtung zur Kraft- und Hubübersetzung bzw. -übertragung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9118200A1 *

Also Published As

Publication number Publication date
JPH05507136A (ja) 1993-10-14
WO1991018200A1 (fr) 1991-11-28
EP0530206B1 (fr) 1994-08-24
US5343845A (en) 1994-09-06
JP3027185B2 (ja) 2000-03-27
DE59102657D1 (de) 1994-09-29
ES2059135T3 (es) 1994-11-01
DE4016309A1 (de) 1991-11-28

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