EP0606436B1 - Injecteur de carburant pour moteurs a combustion interne - Google Patents

Injecteur de carburant pour moteurs a combustion interne Download PDF

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Publication number
EP0606436B1
EP0606436B1 EP93915674A EP93915674A EP0606436B1 EP 0606436 B1 EP0606436 B1 EP 0606436B1 EP 93915674 A EP93915674 A EP 93915674A EP 93915674 A EP93915674 A EP 93915674A EP 0606436 B1 EP0606436 B1 EP 0606436B1
Authority
EP
European Patent Office
Prior art keywords
valve needle
piston
stroke
pressure
injection nozzle
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
EP93915674A
Other languages
German (de)
English (en)
Other versions
EP0606436A1 (fr
Inventor
Karl Hofmann
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 EP0606436A1 publication Critical patent/EP0606436A1/fr
Application granted granted Critical
Publication of EP0606436B1 publication Critical patent/EP0606436B1/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
    • 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
    • F02M45/08—Injectors peculiar thereto

Definitions

  • the invention relates to a fuel injector according to the preamble of claim 1.
  • Injectors of this type have a pre-injection and a main injection to reduce the combustion noise by controlling the stroke of the valve needle.
  • valve needle In an injection nozzle of this type known from EP-A-240 693, the valve needle abuts the piston of the pressure transmission device at the end of the forward stroke, which stops the further movement of the valve needle until the fuel pressure has risen to such an extent that its force exerted on the valve needle in the opening direction the force of the closing spring and the force exerted by the piston exceeds.
  • the known injection nozzle is small, the partition is subject to a complicated manufacturing process due to the design of the pressure chamber and its connecting channel.
  • a further injection nozzle is known from GB-A-2 086 473, which forms the closest prior art, in which a pressure space is limited between the rear of the valve needle and an intermediate piston.
  • This pressure chamber cannot be relieved during the first stroke phase of the valve member, or can only be relieved via a throttle, so that the forward stroke of the valve member is damped and only a very flat opening stroke curve takes place.
  • the pressure chamber is then relieved of pressure over a larger opening cross section, so that the opening stroke movement against the force of the return spring now takes place very quickly in this second stroke phase.
  • a two-stage opening stroke profile is thus achieved on this injection nozzle, in which initially a very small opening cross section is slowly released and in a second opening stroke phase the remaining opening stroke path is traveled very quickly.
  • the invention has for its object to form a two-stage opening stroke course of the valve member in a structurally simple manner, in which the opening stroke course of the preliminary stroke is relatively steep, while after passing through the preliminary stroke there is a flatter opening of the valve needle.
  • the fuel injector according to the invention with the features of claim 1 has the advantage that Achieve a stepped opening stroke of the closing needle down to the piston, the same parts are used as in a single-spring holder, the piston being formed by a special but nevertheless easy to manufacture design of the pressure bolt transmitting the closing force of the closing spring to the valve needle.
  • FIG. 1 shows an injection nozzle in longitudinal section
  • FIG. 2 shows a detail A from FIG. 1 on an enlarged scale, left in the closed and right in the open position of the valve needle
  • FIG. 3 shows an alternative to the exemplary embodiment according to FIG. 2, also left in the closed and right in the open position of the valve needle.
  • the injection nozzle has a nozzle body 10 which is clamped together with an intermediate disk 11 with a union nut 13 to a holding body 12.
  • a valve needle 15 is slidably mounted in the nozzle body 10 and cooperates with a valve seat 16 which is turned inwards and which is arranged in front of a plurality of spray openings 17 in the nozzle body 10.
  • the guide bore 18 of the valve needle 15 is, as usual, expanded at one point to a pressure chamber 19, in the area of which the valve needle 15 has a pressure shoulder 19 and which is connected via a channel 22 and a filter body 23 to a connecting piece 24 on the holding body 12 for connecting a fuel line is.
  • the fuel acting on the pressure shoulder 20 of the valve needle 15 pushes the valve needle 15 upward against the graduated force curve of a closing force arrangement described below, the fuel being injected through the injection openings 17 in a pre-injection phase and a main injection phase.
  • a spring chamber 26 is formed for receiving a closing spring 27, which is supported on the one hand via a disk 28 on the bottom of the chamber 26 and on the other hand on a pressure piece 29.
  • the pressure piece 29 rests on a piston 30 which is tightly guided in a cylindrical through bore 31 in the intermediate plate 11.
  • the piston 30 passes through the through hole 31 completely and is supported on the valve needle 15, which loads it in the closing direction.
  • a longitudinal groove 35 in the jacket of the piston 30 connects this pressure chamber 33 at times with the spring chamber 26, which is relieved of pressure via a leak channel 38 and a connecting piece 39.
  • the longitudinal groove 35 is delimited by a control edge 36 which, in the closed position of the valve needle 15 and piston 30 supported thereon, is at a distance from the annular edge 37 at the transition of the partial surface into the through bore 31 of the intermediate disk 11 h v , which corresponds to the required advance stroke of the valve needle 11.
  • a flat ablation for example a surface grinding, can alternatively also be arranged on the piston 30.
  • the diameter d K or the hydraulic effective area of the piston 30 is smaller than the diameter D N or the effective area of the valve needle 15.
  • the end face 41 of the valve needle 15 delimiting the pressure chamber 33 is flat and the opposite end face 42 of the Piston 30 crowned.
  • the valve needle 15 has, as usual, a pressure pin 44 which is offset over a shoulder 43 and which projects with play into a blind bore 45 of the piston 30 and supports it on the base 46 of the blind bore 45.
  • the injection nozzle works as follows: When fuel is supplied from an injection pump through the channel 22 into the pressure chamber 19, when a certain opening pressure is reached, the valve needle 15 is counteracted by the action of the closing spring 27, which loads the valve needle 15 indirectly via the piston 30 Valve seat 16 lifted off; injection begins. With increasing pressure, the valve needle 15 continues to lift off the valve seat 16 and thereby moves the piston 30 until its control edge 36 interrupts the connection of the pressure chamber 33 to the spring chamber 26 after a preliminary stroke h v . During this preliminary stroke phase, the valve needle 15 displaces more fuel volume in the pressure chamber 33 due to its large diameter than is released by directly displacing the piston 30, which has a smaller diameter.
  • the differential volume is displaced from the pressure chamber 33 through the longitudinal groove 35 in the piston 30 into the pressure-relieved spring chamber 36.
  • the closing spring 27 is tensioned with a force that results from the increasing fuel supply pressure in connection with the effective area of the valve needle 15, neglecting the friction losses.
  • a control pressure then builds up in the pressure chamber 33 under the pumping action of the valve needle 15, which is still acted upon by the increasing supply pressure. which acts on the piston 30. Since the effective area on the supply side of the valve needle 15 and the effective area on the side delimiting the pressure chamber 33 are of the same size, this control pressure is essentially the same as the supply pressure.
  • the volume displaced by the valve needle 15 displaces the piston 30, which is loaded by the closing spring 26 which is further biased by the forward stroke h v .
  • the effective area of the piston 30 is smaller than that of the valve needle 15, and thus at the end of the forward stroke h V, the force generated by the piston 30 is smaller than the force generated by the valve needle 15, which is the same as the closing spring force, the piston 30 remains so long in contact with the valve needle 15 until the supply pressure and thus the control pressure in the pressure chamber 33 have risen so far that the force generated by the piston 30 exceeds the biasing force of the closing spring 27 reached at the end of the forward stroke in the preliminary stroke position.
  • valve needle 15 also remains in the pre-stroke position. If the supply pressure and thus also the control pressure in the pressure chamber 33 then reach a value on the basis of which the piston 30 is loaded with a force which is equal to and greater than that of the pretensioned closing spring 26, a hydraulic stroke conversion from the valve needle 15 to the piston 30 takes place a, due to which the tensioning of the closing spring 27 is now carried out by the piston 30. Depending on the difference in the diameter of the valve needle 15 and the piston 30, the piston 30 is now displaced by a larger lifting unit as the pressure increases per stroke unit of the valve needle 15.
  • the piston 30 thereby lifts off the end face 41 of the valve needle 15 and moves away from it until the valve needle 15 strikes the intermediate disk 11 with its end face 41 or shoulder 43 after passing through the entire stroke h g . Since, as mentioned above, the effective area of the piston 30 is smaller than that of the valve needle 15, the travel of the piston 30 becomes greater than that of the valve needle 15 after the advance stroke h v has been completed. that with the same spring stiffness the closing force exerted by the piston 30 on the hydraulic cushion in the pressure chamber 33 on the valve needle 15 becomes greater, the characteristic of the described injection nozzle thus corresponds to that of a two-spring holder.

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

Un injecteur de carburant pour moteurs à combustion interne pour préinjection/injection principale comporte un pointeau (15) s'ouvrant vers l'intérieur qui est taré par un seul ressort de fermeture (27). Après une précourse (hv) pendant laquelle la pression d'alimentation commande la course en liaison avec la surface active du pointeau (15), il y a inversion de course sur un piston intercalé (30) dont la surface active est moins grande que celle du pointeau (15). En raison de la force du piston (30) qui tend le ressort de fermeture (27), proportionnellement réduite par rapport à la force du pointeau, ce dernier s'ouvre de manière plus plate après la précourse (hv) que pendant la précourse.

Claims (6)

  1. Injecteur de carburant pour moteurs à combustion interne comprenant un corps (10) recevant en coulissement une aiguille d'injecteur (15) ouverte vers l'intérieur, ainsi qu'un organe de fixation (12) portant le corps d'injecteur (10) par une cloison intermédiaire (11), corps dans lequel est formée une chambre à ressort (26) pour recevoir un ressort d'obturation (27) qui charge l'aiguille (15) dans le sens de la fermeture, et une installation de transmission de force qui traverse la cloison intermédiaire (11) et transmet la force du ressort d'obturation (27) à l'aiguille d'injecteur (15), installation de transmission de force qui comprend un piston (30) délimitant une chambre de pression (33), la surface active hydraulique du piston étant inférieure à celle de l'aiguille d'injecteur (15), cette aiguille (15) délimitant par son côté opposé à celui de l'injection, la chambre de pression (33), le piston (30) délimitant d'un côté la chambre de pression (33) vers l'aiguille (15) et son autre côté étant chargé par un ressort de fermeture (27), caractérisé en ce que le piston (30) comprend une arête de commande (36) commandant la liaison vers un côté déchargé en pression (26) et vers la chambre de pression (33), en ce qu'en position de fermeture et pendant la course préalable de l'aiguille (15), pendant que le piston (30) est poussé sous la force du ressort d'obturation (27) contre l'aiguille (15), cette arête permet une liaison entre la chambre de pression (33) et le côté (26) déchargé en pression, et en ce qu'après avoir parcouru la course préalable (vh), au cours de la course résiduelle de l'aiguille d'injecteur (15) et du piston (30), cette liaison est coupée, de sorte que la course résiduelle du piston (30) se fait par conversion hydraulique de course.
  2. Injecteur de carburant selon la revendication 1, caractérisé en ce que la cloison (11) est formée par une rondelle intermédiaire (11) fixée entre le corps d'injecteur (10) et le corps de support (12) et en ce que la chambre de pression (33) est située au niveau des deux zones d'extrémité adjacentes du corps de pression (30) et la rondelle intermédiaire (11).
  3. Injecteur de carburant selon la revendication 2, caractérisé en ce que la chambre de pression (33) est formée par une extension (32) du perçage de guidage (18) de l'aiguille d'injecteur (15) à l'extrémité du corps d'injecteur (10) proche de la rondelle intermédiaire (11).
  4. Injecteur de carburant selon l'une des revendications 1 à 3, caractérisé en ce que l'arête de commande (36) du piston (30) se poursuit par une rainure longitudinale (35) ou une partie enlevée conduisant à la chambre à ressort (26) du corps de support (12).
  5. Injecteur de carburant selon la revendication 4, caractérisé en ce que le piston (30) a une face bombée tournée vers l'aiguille d'injecteur (15) et la face frontale (41) opposée de l'aiguille (15) est plane.
  6. Injecteur de carburant selon la revendication 4, caractérisé en ce que le piston (30) présente un perçage borgne (45) dans lequel vient prendre un ergot de pression (44) de l'aiguille d'injecteur (15).
EP93915674A 1992-08-05 1993-07-29 Injecteur de carburant pour moteurs a combustion interne Expired - Lifetime EP0606436B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4225805 1992-08-05
DE4225805A DE4225805A1 (de) 1992-08-05 1992-08-05 Kraftstoff-Einspritzdüse für Brennkraftmaschinen
PCT/DE1993/000669 WO1994003720A1 (fr) 1992-08-05 1993-07-29 Injecteur de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0606436A1 EP0606436A1 (fr) 1994-07-20
EP0606436B1 true EP0606436B1 (fr) 1996-10-02

Family

ID=6464844

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93915674A Expired - Lifetime EP0606436B1 (fr) 1992-08-05 1993-07-29 Injecteur de carburant pour moteurs a combustion interne

Country Status (5)

Country Link
US (1) US5464158A (fr)
EP (1) EP0606436B1 (fr)
JP (1) JP3433938B2 (fr)
DE (2) DE4225805A1 (fr)
WO (1) WO1994003720A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4440182C2 (de) * 1994-11-10 2003-09-18 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
US5950931A (en) * 1998-01-30 1999-09-14 Caterpillar Inc. Pressure decay passage for a fuel injector having a trapped volume nozzle assembly
US6543706B1 (en) * 1999-02-26 2003-04-08 Diesel Technology Company Fuel injection nozzle for an internal combustion engine
DE102005054927A1 (de) * 2005-11-17 2007-05-31 Siemens Ag Kraftstoffinjektor mit verbesserter Einspritzmengenstabilität
CN102428065B (zh) 2009-05-15 2014-02-26 株式会社日本触媒 制备(甲基)丙烯酸的方法
US9605639B2 (en) 2012-07-12 2017-03-28 Ford Global Technologies, Llc Fuel injector

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3041018C2 (de) * 1980-10-31 1986-03-20 Daimler-Benz Ag, 7000 Stuttgart Kraftstoffeinspritzeinrichtung für eine luftverdichtende Einspritzbrennkraftmaschine
DE3611316A1 (de) * 1986-04-04 1987-10-08 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
ATE119238T1 (de) * 1989-01-12 1995-03-15 Bosch Robert Ag Kraftstoffeinpritzdüse.
DE4126698A1 (de) * 1991-08-13 1992-10-15 Daimler Benz Ag Kraftstoffeinspritzduese fuer brennkraftmaschinen

Also Published As

Publication number Publication date
JPH07502585A (ja) 1995-03-16
US5464158A (en) 1995-11-07
JP3433938B2 (ja) 2003-08-04
DE4225805A1 (de) 1994-02-10
DE59304048D1 (de) 1996-11-07
WO1994003720A1 (fr) 1994-02-17
EP0606436A1 (fr) 1994-07-20

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