EP0262197A1 - Soupape d'injection pour moteurs a combustion interne. - Google Patents

Soupape d'injection pour moteurs a combustion interne.

Info

Publication number
EP0262197A1
EP0262197A1 EP87902302A EP87902302A EP0262197A1 EP 0262197 A1 EP0262197 A1 EP 0262197A1 EP 87902302 A EP87902302 A EP 87902302A EP 87902302 A EP87902302 A EP 87902302A EP 0262197 A1 EP0262197 A1 EP 0262197A1
Authority
EP
European Patent Office
Prior art keywords
control piston
injection
hollow needle
valve
spray holes
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
EP87902302A
Other languages
German (de)
English (en)
Other versions
EP0262197B1 (fr
Inventor
Gottfried Haider
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.)
Voestalpine Metal Forming GmbH
Original Assignee
Voestalpine Metal Forming 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 Voestalpine Metal Forming GmbH filed Critical Voestalpine Metal Forming GmbH
Publication of EP0262197A1 publication Critical patent/EP0262197A1/fr
Application granted granted Critical
Publication of EP0262197B1 publication Critical patent/EP0262197B1/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
    • 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
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention relates to an injection nozzle for internal combustion engines with a nozzle body with spray holes for fuel and two coaxial valve needles, in which the outer hollow needle and. the inner valve needle is resiliently supported and cooperate with separate spray holes and the hollow needle has radial bores.
  • a design has become known, for example from DE-OS 31 13 475, in which one has two needles Nozzle is provided.
  • An outer hollow needle contains a coaxially guided nozzle needle, both needles being spring-loaded and axially displaceable.
  • the hollow needle has radial bores for connection to the pressure chamber of the inner valve needle. The needles interact with separate spray holes and the timing for the pre-injection and the main injection can be specified by suitable dimensioning of the springs and the pressure shoulders effective for lifting the needles from their seat.
  • the pre-injection and the main injection merge directly into one another, so that there is no sharp separation between the pre-injection and the main injection.
  • coaxial tapered seats are required, which means that relatively complex machining is necessary to avoid tolerance problems.
  • the start, the end and the duration of the pre-injection depend on wear and are not exactly defined. Because the inner needle is seated in the outer nozzle needle, the movements of the two needles are coupled to one another and a large volume is required between the valve and the spray holes. which entails the risk of the nozzle dripping.
  • a fuel injection nozzle has become known in which a valve needle is guided coaxially in a hollow needle. Both needles are spring-loaded and interact with separate spray holes.
  • the fuel is supplied via radial bores in the hollow needle inside to the nozzle tip, the sequence of the opening and the opening times of the spray holes assigned to the nozzle needles being able to be controlled depending on the spring forces and the surfaces of the nozzle needle that are acted upon.
  • the pre-injection and main injection thus merge directly into one another, so that a sharp separation of the injection processes is not possible.
  • Another known design according to DE-OS 27 10 216 has a control piston guided in a nozzle needle.
  • the control piston releases additional spray holes after lifting the nozzle needle over a predetermined stroke via radial control edges. Since the pre-injection and the main injection are only controlled by a common control element, namely the nozzle needle, which contains the control piston, the advantages of pre-injection are lost at full load and at higher speeds. A clear distinction between pre-injection and main injection is also not possible with this training.
  • the invention now aims to provide an education of an injection nozzle of the type mentioned, which gives the opportunity to the preliminary and main 'injection to separate clearly and to set the timing accurately and independently of the timing of the main injection.
  • the invention aims to implement such a design with the least possible manufacturing effort.
  • the inventor fertilizer essentially in that the inner valve needle is designed as a control piston, the jacket of which has control edges formed by an annular recess in the region of the mouths of the radial bores of the hollow needle, and that, starting from the annular recess of the jacket of the control piston, channels to one arranged on the control piston Seat of a valve closing member interacting with the control piston, such as a ball, or lead to a valve closing member connected to the control piston.
  • a control piston guided in a substantially sealing manner in a hollow needle which cooperates with radial bores of the hollow needle, can initially be displaced independently of a movement of the hollow needle and only defined by the spring load of the control piston of the control piston to release spray holes.
  • the fact that the control piston itself has seating surfaces for a valve closing element which interacts with the control piston means that the opening pressure ratios and the times can be precisely defined and the possibility is created in a simple manner of a self-centering closing element without complex double fitting, for example a ball to use as a valve closing element.
  • the channels of the control piston must open outside the outlet cross-sections to be sealed by the closing element, which results in a somewhat higher production outlay.
  • control piston Spring * can be supported in a simple manner against the hollow needle itself and can be of relatively small dimensions, so that the control piston can be moved with little inertia.
  • the channels of the control piston are formed by an axial bore connected to the annular recess, which is flared at the end face facing the spray holes, and this end face interacts with a valve ball.
  • This conical extension allows the ball to be supported with lateral play, since it is always centered in relation to the conical sealing surface of the control piston.
  • This self-centering design allows inexpensive production with high precision and, due to the small seat diameter, a smaller pressure area, which in turn leads to a reduction in the size of the compression spring.
  • Such a small compression spring for the control piston can be conveniently accommodated inside the hollow needle.
  • valve ball itself can rest against the bottom of the nozzle body, leaving channels to the spray holes of the nozzle body.
  • a particularly short path is achieved between the valve seat and the spray holes, as a result of which a clean separation between pre-injection and main injection can be achieved even at very high engine speeds, with no dripping occurring after the main injection.
  • a favorable flow pattern is achieved between the ball valve and the spray holes, whereby the fact that the valve seals against the control piston means that less acceleration is required for opening, which makes this design particularly suitable for high speeds.
  • the design can be such that the hollow needle has a blind hole in which the spray holes facing end wall, a bore for the connection to the spraying holes associated with the control piston is arranged in the nozzle body, that the hollow needle cooperates with a seat surface of the nozzle body on a larger radius than the spraying holes controlled by the control piston and that the valve ball and, if applicable, a channel-free ball support between the control piston and the end wall of the blind hole facing the spray holes are arranged.
  • the tip of the nozzle body is largely protected and tolerance compensation is achieved by the optionally provided ball support as a separate component.
  • an accurate manufacture of the blind hole bottom is not necessary.
  • the hollow needle in its end region of the bore facing away from the needle tip, has a spring space for receiving the spring acting on the control piston.
  • the measure of providing the spring chamber in the bore itself is due in particular to the fact that the control piston has only a small pressure area and the opening pressure for the pre-injection is low and can therefore be supported with relatively low spring forces.
  • the spring chamber can advantageously be locked with a pressure pin that has an adjustable stop for the control piston. This adjustability of the stop allows the pre-injection quantity to be set exactly and simplifies processing and assembly.
  • the design is such that the nozzle has separate feed lines for the main injection and the pre-injection, and that a control pressure which can be acted upon by a speed-dependent pressure, in particular the backing pump pressure, is introduced into the feed lines. Slider is switched on and that the control slide has a releasing or throttling cross-section in the feed lines depending on the pressurizing pressure.
  • the control slide is preferably switched into the feed line for the pre-injection and into a bypass line for the line for the main injection, as a result of which the stress on the control slide can be significantly reduced since only a part of the high-pressure main injection quantity is directed through the spool.
  • the procedure is such that when the cross section in the feed line to the main injection is throttled, the control slide releases an enlarged cross section in the feed line to the pre-injection, as a result of which the quantitative ratio between the pre-injection and the main injection is shifted in favor of the pre-injection as the speed increases.
  • FIG.l show schematically a pump-nozzle assembly, wherein the details of the nozzle can not be found in this figure.
  • 2 shows an enlarged illustration of a first embodiment of the injection Nozzle shown in longitudinal section.
  • 3 shows a section along the line III-III of FIG. 2 and
  • FIG. 4 shows an enlarged illustration of the lower end region of the nozzle according to FIG. 5 shows a modified embodiment of a nozzle according to FIGS. 2, 3 and 4, in which the ball of the valve is mounted on a ball support.
  • Figure 6 shows a section along the line VI-VI of Figure 5.
  • Fig. 7 shows the injection pressure curve over the camshaft angle for different speeds.
  • FIGS. 8 and 9 show in a modified embodiment a section through a control spool switched into the supply lines and Fig. 9 shows a section along the line IX-IX of Fig. 8. Finally, in Fig. 10 the injection pressure curve over the camshaft angle for different speeds is at Use of a control slide shown in FIGS. 8 and 9.
  • a pump-nozzle assembly is shown, in which the pump piston is designated 1. Following the working chamber 2 of this pump piston, a check valve 3 is provided, from which fuel reaches the nozzle 6 via supply lines 4 and 5 for the main injection and the pre-injection.
  • the nozzle contains nozzle needles 7, the nozzle needle spring for the outer valve needle being denoted by '8.
  • the nozzle needle spring 8 is designed as a helical spring and is supported on a spring plate 9 which cooperates with the outer nozzle needle via a spherical bearing.
  • the nozzle body is designated by 10 and contains spray holes 11 and 12, the details of the configuration of the nozzle 6 being shown, for example, in FIG.
  • FIG. 2 it can be seen that within the outer nozzle needle 7 a control piston 13 is sealingly guided in the radial direction and displaceable in the axial direction.
  • the control piston 13 is resiliently supported by a helical spring 29 contained in the interior of the hollow nozzle needle 7.
  • a pressure pin 16 is provided as a closure piece for the bore of the hollow nozzle needle 7, which has a pin-shaped extension 17 as a stop for a pin-shaped extension 18 of the control piston 13. The free distance between these two stops 17 and 18 determines the possible pre-injection quantity.
  • the hollow needle 7 has a blind hole 23, the end wall 24 facing the spray holes 11 and 12 of which has an axial bore 25 for supplying fuel to the spray holes 12.
  • a support part 26 is fixed, which carries the ball 21 representing the valve closing member and allows the free passage of fuel to the axial bore 25.
  • the support part 26 has webs 27, between which openings 28 remain free.
  • the seat surface 20 of the control piston 13 is conical, as can be seen in particular in FIG. 5, so that a loose support of the ball 21 as a valve closing member on the base or the end wall 24 of the blind hole 23 is sufficient, to ensure a securely sealing closure between valve ball 21 and seat surface 20.
  • pressures between 100 and 150 bar are sufficient as the pre-injection pressure, the main injection being able to be achieved from pressures of over 200 bar, for example 240 bar. As soon as the injection pressure has dropped below the closing pressure, all the spray openings are closed at the same time.
  • the injection pressure curve over the camshaft angle can be seen from FIG. 7. At the speeds of 400, 1300 and 2200 revolutions per minute shown in comparison, the injection pressure between the pilot and main injection drops to zero for all embodiments, so that a clear separation of the pilot injection and the main injection is achieved at any speed.
  • FIG. 8 shows a modified embodiment, a control slide 29 being arranged in a slide seat 30 after the check valve in the inlet lines.
  • 5 again designates the feed line for the pre-injection, while the feed line 4 for the main injection is indicated by dashed lines.
  • the control slide 29 is switched into the feed line 5 and into a bypass line 31 of the feed line 4 for the main injection.
  • the control slide has annular recesses 32 in the area of the lines 5 and 31 on its circumference.
  • control slide 29 By applying a speed-dependent pressure, in particular the fore-pump pressure, the control slide 29 is displaced in the direction of arrow 33 against the force of a compression spring 34 arranged inside the control slide, whereby the cross section exposed in the feed line 5 by the recess 32 is increased , while the cross section released in the bypass line 31 is reduced. It therefore results with increasing speed and therefore increasing Control pressure a shift in the quantity ratio in favor of the pilot injection. With 35 O-rings for the seal are indicated.
  • the injection pressure curve over the camshaft angle can be seen from FIG. 7. At the speeds of 400, 1300 and 2200 revolutions per minute shown in comparison, the injection pressure between the pilot and main injection drops to zero for all embodiments, so that a clear separation of the pilot injection and the main injection is achieved at any speed.

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 soupape d'injection pour moteurs à combustion interne comprend un corps d'injecteur (10) ayant des orifices d'injection (11, 12) du carburant et deux aiguilles coaxiales de soupape sollicitées par un ressort et coopérant avec des orifices séparés d'injection. L'aiguille creuse extérieure (7) comprend des alésages radiaux et l'aiguille intérieure de la soupape est conçue comme un piston de commande (13) dont l'enveloppe, dans la région des ouvertures des alésages radiaux (14) de l'aiguille creuse (7), a des bords de commande formés par un évidement annulaire (15). Des conduits, ou de préférence un alésage axial (19), partent de l'évidement de l'enveloppe du piston de commande (13) et s'étendent jusqu'à un siège (20), agencé sur le piston de commande (13), d'un élément (21) de fermeture de la soupape, qui coopère avec le piston de commande et qui a par exemple une forme conique ou sphérique. Après un déplacement prédéterminé du piston de commande (13), l'évidement (15) formant les bords de commande provoque une chute de la pression et la fermeture des orifices d'injection correspondants (12), ce qui crée une séparation entre la pré-injection et l'injection principale amenées par la montée de l'aiguille creuse (7).
EP87902302A 1986-04-15 1987-04-08 Soupape d'injection pour moteurs a combustion interne Expired - Lifetime EP0262197B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT988/86 1986-04-15
AT98886 1986-04-15

Publications (2)

Publication Number Publication Date
EP0262197A1 true EP0262197A1 (fr) 1988-04-06
EP0262197B1 EP0262197B1 (fr) 1990-06-06

Family

ID=3504362

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87902302A Expired - Lifetime EP0262197B1 (fr) 1986-04-15 1987-04-08 Soupape d'injection pour moteurs a combustion interne

Country Status (3)

Country Link
EP (1) EP0262197B1 (fr)
AT (1) ATE53436T1 (fr)
WO (1) WO1987006308A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2204570A1 (fr) * 2008-12-30 2010-07-07 Robert Bosch GmbH Injecteur de carburant
WO2016118012A3 (fr) * 2015-01-23 2016-09-22 Paul Johan Willem Maria Nooijen Ensemble injecteur et son procédé d'utilisation
CN113423945A (zh) * 2019-02-12 2021-09-21 利勃海尔零部件德根多夫有限公司 用于燃料喷射器的喷嘴

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5458292A (en) * 1994-05-16 1995-10-17 General Electric Company Two-stage fuel injection nozzle
GB9913314D0 (en) * 1999-06-09 1999-08-11 Lucas Ind Plc Fuel injector
GB9914644D0 (en) 1999-06-24 1999-08-25 Lucas Ind Plc Fuel injector
WO2005073546A1 (fr) * 2004-02-02 2005-08-11 Siemens Aktiengesellschaft Corps de buse et soupape
DE102009027727A1 (de) * 2009-07-15 2011-01-20 Robert Bosch Gmbh Ventilanordnung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE829682C (de) * 1941-10-12 1952-01-28 Bosch Gmbh Robert Einspritzventil fuer Brennkraftmaschinen
DE1270883B (de) * 1966-10-28 1968-06-20 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE1284687B (de) * 1967-10-18 1968-12-05 Bosch Gmbh Robert Kraftstoffeinspritzventil fuer Vor- und Haupteinspritzung
DE2710216A1 (de) * 1977-03-09 1978-09-14 Bosch Gmbh Robert Kraftstoffeinspritzduese
DE3113475A1 (de) * 1981-04-03 1982-10-21 Robert Bosch Gmbh, 7000 Stuttgart "kraftstoffeinspritzduese"

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8706308A1 *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2204570A1 (fr) * 2008-12-30 2010-07-07 Robert Bosch GmbH Injecteur de carburant
WO2016118012A3 (fr) * 2015-01-23 2016-09-22 Paul Johan Willem Maria Nooijen Ensemble injecteur et son procédé d'utilisation
CN108064322A (zh) * 2015-01-23 2018-05-22 保罗·约翰·威廉·玛丽·纽诺茜 喷射器组件及其使用方法
CN108064322B (zh) * 2015-01-23 2020-08-21 保罗·约翰·威廉·玛丽·纽诺茜 喷射器组件及其使用方法
CN113423945A (zh) * 2019-02-12 2021-09-21 利勃海尔零部件德根多夫有限公司 用于燃料喷射器的喷嘴
CN113423945B (zh) * 2019-02-12 2024-02-06 利勃海尔零部件德根多夫有限公司 用于燃料喷射器的喷嘴

Also Published As

Publication number Publication date
WO1987006308A1 (fr) 1987-10-22
EP0262197B1 (fr) 1990-06-06
ATE53436T1 (de) 1990-06-15

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