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EP0505522B1 - Pompe d'injection de carburant pour moteurs a combustion interne - Google Patents

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

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Publication number
EP0505522B1
EP0505522B1 EP91915790A EP91915790A EP0505522B1 EP 0505522 B1 EP0505522 B1 EP 0505522B1 EP 91915790 A EP91915790 A EP 91915790A EP 91915790 A EP91915790 A EP 91915790A EP 0505522 B1 EP0505522 B1 EP 0505522B1
Authority
EP
European Patent Office
Prior art keywords
fuel
pump
valve
chamber
space
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
EP91915790A
Other languages
German (de)
English (en)
Other versions
EP0505522A1 (fr
Inventor
Wolfgang Braun
Dieter Junger
Helmut 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 EP0505522A1 publication Critical patent/EP0505522A1/fr
Application granted granted Critical
Publication of EP0505522B1 publication Critical patent/EP0505522B1/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
    • F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
    • 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
    • F02M59/20—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

Definitions

  • the invention relates to a fuel injection pump for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection pump is known from DE-A-3 500 618.
  • This fuel injection pump has a pump piston which delimits a pump working chamber which can be connected to a suction chamber which is formed by the collecting chamber during a respective suction stroke and during a controlled part of the delivery stroke of the pump piston via a fuel channel consisting of a first and second prechamber and a collecting chamber is.
  • Fuel is conveyed from a fuel reservoir into the collecting chamber.
  • the fuel channel is controlled by an electrically operated valve.
  • the pump work space can be connected via a distributor opening arranged in a distributor during a respective delivery stroke of the pump piston to one of a plurality of pressure channels which are connected to the injection points of the internal combustion engine via injection lines.
  • the fuel delivery under high pressure in the injection lines is determined by the closing phase of the valve.
  • a return line connected to the suction side of the fuel injection pump branches off from the singing chamber and leads away from the collection chamber. Fuel therefore flows continuously through the collecting chamber.
  • the valve for ending the high-pressure delivery is opened, fuel flows from the pump work space back into the collecting chamber via the fuel channel and can return from the collecting chamber via the fuel return to the suction side of the fuel injection pump.
  • the fuel flowing out of the pump work space is heated as a result of the high pressure formation in the pump work space, so that the temperature of the fuel in the collection chamber is increased.
  • the fuel injection pump with the features according to claim 1 has the advantage that when the high-pressure delivery ends with the valve open, fuel flowing out of the pump work chamber can reach the fuel return directly via the bypass line and thus does not lead to a sharp increase in the temperature of the fuel in the suction chamber.
  • the amount of fuel flowing out via the bypass line can be specifically determined by dimensioning the throttle accordingly.
  • FIG. 1 shows a longitudinal section of a fuel injection pump in a schematic representation
  • FIG. 2 shows the detail of the fuel injection pump designated II in FIG. 1 in an enlarged representation.
  • a fuel injection pump of the distributor type shown in FIGS. 1 and 2 has a pump piston 12 which works in a cylinder bore 10 of a cylinder liner 11 and which is driven via a drive shaft 13 by a cam drive consisting of a roller ring 14 and a front cam disk 15 into a reciprocating as well as is also set into a rotating movement at the same time.
  • the fuel injection pump has a housing 17 which delimits an interior space 18 which serves as a suction space and to which fuel is supplied by a feed pump 19 from a storage container.
  • a distributor body 22 is inserted into the housing.
  • the pump piston 12 is provided with a distributor groove 23 in its end region arranged in the cylinder bore 10.
  • the cylinder liner 11 and the distributor body 22 have delivery channels 24 corresponding to the number of cylinders of the internal combustion engine operated by the fuel injection pump, through which fuel can reach the injection valves on the cylinders of the internal combustion engine via a pressure valve 25 and injection lines 26.
  • the distributor body 22 has a stepped bore 28 which extends coaxially to the longitudinal axis 27 of the pump piston 12.
  • the cylinder liner 11 is inserted into the bore 28 in its area with a smaller diameter facing the interior 18.
  • the cylinder liner 11 projects into the interior 18 of the fuel injection pump and is supported with a flange 29 on an annular shoulder 30 formed at the transition of the bore 28 to the smaller diameter from the interior 18.
  • the flange 29 of the cylinder liner 11 is conical in its end region arranged in the region of the bore 28 with the larger diameter, with a cross section tapering towards its end.
  • the cylinder bore 10 has an enlarged diameter in the end region of the cylinder liner 11 arranged in the bore 28.
  • an electrically controlled valve 32 is used from the outside, which closes the bore 28.
  • the valve 32 is designed, for example, as a solenoid valve.
  • the bore 28 is sealed to the outside by two sealing rings 35 inserted at a distance from each other in an annular groove 33 on the outer circumference of the valve housing 34.
  • a valve body 37 is inserted, which projects with its end region out of the valve housing towards the cylinder liner 11 and there clamps a sealing ring 38 between it and the cylinder liner 11.
  • the sealing ring 38 is fitted radially with a small clearance in a shoulder, which is preferably arranged in the cylinder liner 11, and can thereby absorb radial forces which occur as a result of the pressurization, and thus seals a pump work chamber 40 enclosed by the pump piston 12 in the cylinder bore 10 Hole 28 down.
  • This configuration defines an annular space 41 between the end of the cylinder liner 11, the valve body and the valve housing 34.
  • the annular space 41 is connected to the interior 18 of the fuel injection pump via a fuel channel 42 in the distributor body 22.
  • a bypass line 43 leads through the valve housing 34 diametrically opposite the channel 42 and extends approximately parallel to the longitudinal axis 27 of the pump piston, in which a throttle 44 is arranged.
  • the bypass line 43 opens via a short transverse bore 46 into an annular space 48 formed by an annular groove arranged between the sealing rings 35 in the outer circumference of the valve housing 34 and the wall of the bore 28, which in turn is connected to a transverse bore 49 in the distributor body 22.
  • the transverse bore 49 in the distributor body 22 is connected via a return line 51 to the fuel reservoir 20 or the suction line of the feed pump 19.
  • the interior 18 of the fuel injection pump is also connected in a known manner to the fuel return line 51 via a throttle 52.
  • the valve 32 has, as the closing member, a needle 57 which is tightly guided in a blind bore 56 in the valve body 37, the blind bore 56 having an enlarged cross-sectional area which forms a pressure chamber 58.
  • the pressure chamber 58 of the valve 32 is connected to the pump working chamber 40 via a transverse bore 61 and a longitudinal bore 59 in the valve body 37.
  • the needle 57 has a conical sealing surface 62 towards the working chamber 40, which cooperates with a sealing seat 63 of the blind bore 56, which is likewise conical, at the transition from the pressure chamber 58 to the blind bore.
  • the needle 57 has an area 64 with a reduced cross section.
  • the pressure prevailing in the pump work chamber 40 acts in the pressure chamber 58 on both end faces of the area 64 of the needle 57, so that no resulting compressive force acts on it.
  • the pump working chamber 40 is connected via the bore 59, the transverse bore 61, the pressure chamber 58, a further transverse bore 66 in the valve body 37 and an opening 67 in the valve housing 34 to the annular space 41 and via this and the fuel channel 42 to the interior 18 .
  • the opening and closing times and the opening and closing times of the valve 34 are controlled as a function of various operating parameters, such as speed, load, etc.
  • a rotary encoder 68 is provided for detecting the speed and the rotational position of the drive shaft 13.
  • the distributor groove 23 is connected to one of the delivery channels 24 and as soon as the injection valve opens, fuel flows under high pressure to the relevant injection point.
  • the valve 32 is opened and the fuel flows from the pump working space 40 through the valve 32 into the annular space 41. From there, part of the fuel flows back through the fuel channel 42 into the interior 18. Another part of the fuel flows through the throttle 44 into the further annular space 48, flows through this and the transverse bore 49 in the distributor body 22 and returns via the return line 51 to the fuel reservoir 20.
  • fuel flows continuously from the interior 18 via the annular space 41, the throttle 44 and the annular space 48, since there is a higher fuel pressure in the interior 18 than in the return line 51.
  • the fuel flow through the two annular spaces 41 and 48 causes the valve 32 and the cylinder sleeve in the area of the pump work space 40 is washed by the cooler fuel from the interior and thus cooled, and the heated fuel flowing out of the pump work space following the fuel injection phase is returned to the pump work space to a much lesser extent during the suction stroke.
  • the fuel flow flowing through the annular spaces 41 and 48 can be adjusted by appropriate dimensioning and tuning of the throttles 44 and 52 to achieve a desired cooling.

Landscapes

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

Abstract

Une pompe d'injection de carburant comprend un piston (12) qui fonctionne dans un alésage cylindrique (10) d'une douille cylindrique (11). Une chambre de pompage (40) est délimitée dans l'alésage cylindrique (10) d'une part par le piston (12) et d'autre part par une soupape (32) à commande électrique. Pendant la course d'aspiration du piston (12) et afin de commander la course du piston qui provoque l'injection, la chambre de pompage (40) peut être reliée par la soupape (32) à une chambre d'aspiration (18). La douille cylindrique (11) est partiellement entourée d'un espace annulaire (41) à travers lequel le carburant s'écoule entre la chambre de pompage (40) et la chambre intérieure (18). Le carburant s'écoule dans un autre espace annulaire (48) qui entoure partiellement la soupape (32) par un conduit de dérivation (43) qui part de l'espace annulaire (41). L'espace annulaire (48) est déchargé au moyen d'un conduit de retour au réservoir de carburant. Compte tenu de la pression qui règne dans la chambre intérieure (18), les deux espaces annulaires (41, 48) sont traversés en continu par du carburant, ce qui assure le refroidissement de la chambre de pompage (40) et de la soupape (32).

Claims (2)

  1. Pompe d'injection de carburant pour des moteurs à combustion interne, comprenant un piston de pompe (12) délimitant une chambre active (40) de pompe, et pendant chaque course d'aspiration et pendant une partie commandée de la course de transfert du piston (12), cette chambre étant reliée par un canal à carburant (42, 41, 67, 66, 61, 59) commandé par une soupape à action électrique (32), avec une chambre d'aspiration (18) recevant le carburant d'un réservoir (20), la chambre active (40) pouvant être reliée au cours de chaque course de transfert du piston de pompe (12) avec l'un des canaux de pression (24), reliés par les conduites d'injection aux points d'injection du moteur à combustion interne, le transfert de carburant à haute pression aux conduites d'injection étant défini par la phase de fermeture de la soupape (32) et un retour de carburant (51) relié au côté aspiration de la pompe d'injection est dérivé de la chambre d'aspiration (18), caractérisée en ce qu'une conduite de dérivation (43, 46, 48, 49) dérive du canal à carburant (41), entre la chambre d'aspiration (18) et la soupape (32), cette dérivation (43, 46, 48, 49) reliée au retour de carburant (51) comporte un organe d'étranglement (44) et la partie du canal à carburant (42, 41) entre la chambre d'aspiration (18) et l'embranchement de la dérivation (43, 46, 48, 49) est parcourue en permanence par le carburant.
  2. Pompe d'injection selon la revendication 1, caractérisée en ce que la chambre active (40) est délimitée à sa périphérie par une chemise de cylindre (11) logée dans un perçage (28) de la partie de boîtier (22) et entre le perçage (28) et la chemise de cylindre (11), il est formé un volume annulaire (41) relié d'une part à la chambre d'aspiration (18) et d'autre part à la soupape (32) et la conduite de dérivation (43) débouche dans le volume annulaire (41) entourant la chemise de cylindre (11).
EP91915790A 1990-10-11 1991-09-11 Pompe d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0505522B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4032279 1990-10-11
DE4032279A DE4032279A1 (de) 1990-10-11 1990-10-11 Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
PCT/DE1991/000723 WO1992007182A1 (fr) 1990-10-11 1991-09-11 Pompe d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0505522A1 EP0505522A1 (fr) 1992-09-30
EP0505522B1 true EP0505522B1 (fr) 1996-12-27

Family

ID=6416088

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91915790A Expired - Lifetime EP0505522B1 (fr) 1990-10-11 1991-09-11 Pompe d'injection de carburant pour moteurs a combustion interne

Country Status (6)

Country Link
US (1) US5273017A (fr)
EP (1) EP0505522B1 (fr)
JP (1) JP3167324B2 (fr)
DE (2) DE4032279A1 (fr)
ES (1) ES2095952T3 (fr)
WO (1) WO1992007182A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5215060A (en) * 1991-07-16 1993-06-01 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
US5325837A (en) * 1992-11-19 1994-07-05 Robert Bosch Gmbh Fuel injection apparatus for internal combustion engines
DE4243665C2 (de) * 1992-12-23 2003-11-13 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung, insbesondere Pumpedüse für Brennkraftmaschinen
DE4322546A1 (de) * 1993-07-07 1995-01-12 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
EP0816672B1 (fr) * 1996-07-05 2003-04-09 Nippon Soken, Inc. Pompe haute pression
JP3426439B2 (ja) * 1996-07-17 2003-07-14 三菱ふそうトラック・バス株式会社 蓄圧式燃料噴射制御装置
JP3237549B2 (ja) * 1996-11-25 2001-12-10 トヨタ自動車株式会社 内燃機関の高圧燃料供給装置
JP2000345901A (ja) * 1999-05-31 2000-12-12 Isuzu Motors Ltd 電子燃料噴射装置
US6953022B1 (en) * 2000-05-26 2005-10-11 Yanmar Co., Ltd. Fuel injection pump
DE10059424A1 (de) * 2000-11-30 2002-06-06 Bosch Gmbh Robert Hubgesteuertes Ventil als Kraftstoff-Zumesseinrichtung eines Einspritzsystems für Brennkraftmaschinen
DE102010026159A1 (de) * 2010-07-06 2012-01-12 Audi Ag Kraftstoffsystem für eine Brennkraftmaschine
US20170049274A1 (en) * 2015-08-19 2017-02-23 Terri Lynn Minor Cooking Assembly
IT201700077449A1 (it) * 2017-07-10 2019-01-10 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, da un serbatoio di contenimento ad un motore a combustione interna
DE102018200715A1 (de) * 2018-01-17 2019-07-18 Robert Bosch Gmbh Kraftstofffördereinrichtung für kryogene Kraftstoffe
DE102018211338A1 (de) * 2018-07-10 2020-01-16 Robert Bosch Gmbh Kraftstofffördereinrichtung für kryogene Kraftstoffe und Verfahren zum Betreiben einer Kraftstofffördereinrichtung

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4385614A (en) * 1979-04-06 1983-05-31 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
JPS60159363A (ja) * 1980-01-12 1985-08-20 フオード　モーター　カンパニー 燃料噴射ポンプ
DE3142750C2 (de) * 1980-12-19 1984-06-20 Nissan Motor Co., Ltd., Yokohama, Kanagawa Treibstoffeinspritzpumpe für eine Diesel-Brennkraftmaschine
DE3211680A1 (de) * 1982-03-30 1983-10-06 Espenschied Helmut Dipl Ing Kraftstoffeinspritzsystem fuer brennkraftmaschinen
US4480619A (en) * 1982-06-08 1984-11-06 Nippon Soken, Inc. Flow control device
DE3300876A1 (de) * 1983-01-13 1984-07-19 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
JPS60147544A (ja) * 1984-01-10 1985-08-03 Diesel Kiki Co Ltd 分配型燃料噴射ポンプ
JPS62206238A (ja) * 1986-03-05 1987-09-10 Nippon Denso Co Ltd 燃料噴射ポンプのパイロツト噴射装置
DE3612942A1 (de) * 1986-04-17 1987-10-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3719807A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Verteilerkraftstoffeinspritzpumpe der radialkolbenbauart
DE3719833C2 (de) * 1987-06-13 1996-05-30 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
DE3721352C2 (de) * 1987-06-29 1995-05-11 Bosch Gmbh Robert Verfahren zur Steuerung der Kraftstoffeinspritzmenge bei einer Kraftstoffeinspritzpumpe für Brennkraftmaschinen
US5033443A (en) * 1988-06-27 1991-07-23 Nippondenso Co., Ltd. Pilot injection device for fuel injection pump
JP2829639B2 (ja) * 1989-09-22 1998-11-25 株式会社ゼクセル 電子制御式分配型燃料噴射ポンプの送油率可変制御方法

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6773240B2 (en) 2002-01-28 2004-08-10 Visteon Global Technologies, Inc. Single piston dual chamber fuel pump

Also Published As

Publication number Publication date
DE59108434D1 (de) 1997-02-06
WO1992007182A1 (fr) 1992-04-30
JP3167324B2 (ja) 2001-05-21
EP0505522A1 (fr) 1992-09-30
JPH05502494A (ja) 1993-04-28
ES2095952T3 (es) 1997-03-01
DE4032279A1 (de) 1992-04-16
US5273017A (en) 1993-12-28

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