EP2027387B1 - Dispositif d'amortissement pour un composant oscillant - Google Patents

Dispositif d'amortissement pour un composant oscillant Download PDF

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Publication number
EP2027387B1
EP2027387B1 EP07718499A EP07718499A EP2027387B1 EP 2027387 B1 EP2027387 B1 EP 2027387B1 EP 07718499 A EP07718499 A EP 07718499A EP 07718499 A EP07718499 A EP 07718499A EP 2027387 B1 EP2027387 B1 EP 2027387B1
Authority
EP
European Patent Office
Prior art keywords
damping
piston
valve
opening
damping device
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.)
Not-in-force
Application number
EP07718499A
Other languages
German (de)
English (en)
Other versions
EP2027387A2 (fr
Inventor
Otfried Derschmidt
Harald Arnulf Philipp
Heribert Kammerstetter
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.)
AVL List GmbH
Original Assignee
AVL List 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
Priority claimed from AT10052006A external-priority patent/AT501574B1/de
Priority claimed from AT10982006A external-priority patent/AT501679B1/de
Application filed by AVL List GmbH filed Critical AVL List GmbH
Publication of EP2027387A2 publication Critical patent/EP2027387A2/fr
Application granted granted Critical
Publication of EP2027387B1 publication Critical patent/EP2027387B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • 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
    • F02M2200/24—Fuel-injection apparatus with sensors
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • 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
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/161—Means for adjusting injection-valve lift

Definitions

  • the damping device for an oscillating component in particular a preferably designed as an injection valve valve of an internal combustion engine, which component is hydraulically actuated via an actuating piston, wherein the preferably loaded by a restoring force actuating piston adjacent to a pressure chamber, which is acted upon via a pressure medium leading to a working pressure line , wherein the damping device is arranged in the pressure line, wherein the damping device comprises a damping piston in a cylinder between two end positions longitudinally displaceable, wherein in the damping piston at least one substantially extending in the longitudinal direction of the damping piston damping channel is arranged, which two mutually remote end faces of the damping piston with each other strömungsverbindet, and wherein in the damping channel, a throttle check valve is arranged, the throttling effect of the flow direction depends.
  • a damping device for effecting damping of the opening movement of a needle valve, which is pushed down by supplying fuel under pressure into a pressure control chamber and lifted by discharging the fuel from the pressure control chamber.
  • a damping element is slidably supported on the needle valve.
  • a damping chamber is formed between the damping element and the needle valve and is filled with fuel. Through a branch passage, fuel can be taken from the interior of the damping chamber and discharged outside the chamber.
  • the GB 2 138 884 A describes an injection valve for an internal combustion engine with an actuating piston having a damping device, wherein the valve body of the injection valve is hydraulically actuated.
  • the valve body is mounted axially displaceable and can be opened against the restoring force of two springs.
  • the fuel flow from the housing into the chamber of the first spring chamber is throttled by stroke-dependent adjustable openings in order to dampen the valve opening. Measures for damping the closing movement are not provided.
  • the object of the invention is to avoid these disadvantages and to reduce the placement speed of an oscillating component on a seat, in particular a valve on the valve seat, without significantly delaying the closing duration of the valve.
  • the damping device is designed as a closing damper, wherein the throttle resistance of the throttle check valve in the flow direction of the working medium at opening of the component is lower than in the reverse direction and that the damper is preceded by an opening damper, which preferably is identical to the closing damper trained opening damper compared to the closing damper with respect to the flow is oriented oppositely oriented.
  • a spring acts on the damping piston in the opening direction of the throttle check valve, which presses the damping piston into a first end position corresponding to the rest position.
  • the initial position of the damping device is defined by acting on the damping piston in the opening direction of the throttle check valve, a spring which presses the damping piston in a first end position corresponding to the rest position.
  • the pressure line is pressurized again, wherein the check valve is opened within the throttle piston.
  • the actuating medium can thus be supplied very quickly to the actuating piston both through the bypass line, as well as through the open check valve, whereby the valve is opened according to the selected characteristic.
  • the amount of pressure of the actuating medium is an essential parameter for the opening characteristic of the valve.
  • the closing of the valve is initiated by lowering the pressure in the pressure line.
  • the damping piston is displaced by its predefined stroke counter to the force of a counteracting spring up to a stop from an end position corresponding to the rest position into a second end position.
  • the hydraulic medium is pushed back by the spring-loaded actuating piston.
  • a high closing speed of the valve can be achieved in a first closing area.
  • the closing damper also has an advantageous effect on the post-swinging of the valve after the opening process.
  • a further improvement of the Nachschwing s after opening the valve can be achieved if the damper is preceded by an opening damper, wherein the preferably constructed identical with the closing damper opening damper in comparison to the closing damper with respect to the flow is arranged oppositely oriented.
  • the damping piston of the opening damper is held by a spring counter to the opening flow direction of the working medium in an initial position.
  • the check valve of the opening damper closes in the opening flow direction of the working medium and opens in the closing direction of the working medium.
  • the damping piston of the opening damper If the pressure in the pressure line increases, the damping piston of the opening damper is displaced against the force of the spring in its second end position, which is defined by a stop. By the deflection of the piston, the pressure downstream of the opening damper is transmitted freely, whereby the check valve of the closing damper is opened. During this phase, the opening pressure is transferred virtually unthrottled to the actuating piston of the nozzle needle, so that the valve needle is opened very quickly in the first opening phase.
  • the damping piston of the opening damper rests against its stop, the sudden increase in pressure in the pressure line downstream of the opening damper is stopped or greatly reduced, since the actuating medium can only flow through the bypass channel of the opening damper. Due to the throttle resistance of the bypass channel, the opening characteristic is determined in the second opening phase of the valve needle. There is thus a slowing of the opening movement of the valve at the end of the opening phase, so that over- and Nachschwingerscheinept be largely prevented.
  • the damping device 7 is suitable for oscillating components, in particular for valves 1, for example for an outwardly opening injection valve 2 of an internal combustion engine.
  • Fig. 1 shows an injection valve 2 with a damping device 7 for an internal combustion engine.
  • the valve 1 of the injection valve 2 is opened by a longitudinally displaceable actuating piston 3 by means of a hydraulic working medium and closed by a closure force F on the actuating piston 3 performing closing spring 4.
  • the axially longitudinally displaceable actuating piston 3 is adjacent to a pressure chamber 5, in which opens a pressure line 6 for the working fluid.
  • a damping channel 11 is arranged, which fluidly connects the two end faces 12, 13 of the damping piston 9, wherein the end faces 12, 13 border on spaces in which the pressure line 6 opens.
  • a throttle check valve 14 is arranged, which is formed in the embodiment by a by-passable via a bypass passage 15 check valve 16.
  • the check valve 16 is pressed by a valve spring 17 against the effective direction of the spring 10 against a valve seat 18, wherein in the closed state of the check valve 16, the flow around the bypass channel 15 is possible.
  • the bypass channel 15 has a defined throttle resistance, which is denoted by the reference numeral 19 in FIG Fig. 2 to Fig. 8 is indicated. With reference numeral 20, the throttle resistance of the damping channel 11 is designated.
  • a control valve 21 is arranged in the pressure line 6.
  • the damping piston 9 has a diameter d 1 and can be moved within the cylinder 8 by the stroke h 1 .
  • the reference numerals d 2 and h 2 , the diameter, or the stroke of the actuating piston 3 are designated.
  • the check valve 16 opens in the flow when opening the valve needle 1 from the working fluid direction.
  • Fig. 9 a lift curve of the valve 1 is shown, wherein the stroke h is plotted against the time t.
  • the arrows II, III, IV, V, VI and VII are different opening phases of the valve 1 according to the FIGS. 2 to 7 shown.
  • Fig. 2 shows the valve 1 at rest according to the arrow II in Fig. 9 ,
  • the actuating piston 3 is loaded by a force F in the closing direction of the valve 1, for example by the closing fields 4.
  • the damping piston 9 is in its first end position defined by the spring 10, which corresponds to its rest position, the check valve 16 is closed.
  • Fig. 3 shows the opening phase of the valve 1 according to the arrow III in Fig. 9 .
  • the check valve 16 is opened, whereby a maximum flow cross section through the damping channel 11 in the damping piston 9 is released for the actuating medium (p B > p A ).
  • the actuating piston 3 according to the arrow P in Fig. 3 moved down, the valve 1 thus opened.
  • the pressure p medium is held in the pressure line 6.
  • the closing operation of the valve 1 according to arrow V in Fig. 9 is introduced by pressure reduction in the pressure line 6 via the control valve 21, as in Fig. 5 is shown, so that p B ⁇ p A.
  • a first closing phase 22 of the damping piston 9 is moved according to the arrow P 1 against the force of the spring 10 due to the pressure difference p A -p B on both sides of the damping piston 9 upwards until the damping piston 9 rests against a stop 24.
  • the hydraulic medium is thereby pushed back by the prestressed actuating piston 3 in the pressure line 6, wherein the actuating piston 3 moves with the medium.
  • the movement of the medium is designated P 2 .
  • the stroke h 2 of the damping piston 9 must be such that the damping piston 9 rests against the stop 24 before the valve 1 strikes its valve seat.
  • the pressure p A increases rapidly in the working space 5.
  • the pressure p A can be reduced only slowly corresponding to the throttle resistance 19 of the bypass channel 11, which is why a significant slowing down of the closing movement of the valve 1 occurs.
  • This second closing area is in Fig. 9 denoted by 23.
  • the corresponding phase of the damping device 7 is in Fig. 6 shown.
  • suitable tuning of the throttle resistors 19, 20 is too hard Opening the valve 1 prevents the valve seat, but still allows a total of fast closing within a short period of time.
  • the opening damper 26 is of identical design to the closing damper 25, but arranged inversely oriented in the pressure line 6, wherein the check valve 16a of the throttle check valve 14a now opens against the direction which flows through the working fluid when opening the valve 1.
  • the spring 10a of the opening damper 26 acts on the damping piston 9a of the opening damper 26 in a direction opposite to the spring 10 so that it is pressed counter to the opening flow direction of the working medium in a rest position corresponding to its first end position.
  • the direction of the rest position is in Fig. 8 indicated by the arrows 27, 28.
  • the effect of the opening damper 26 is analogous to the Fig. 2 to Fig. 7 , but in the opposite direction. If pressure is applied to the pressure line 6, the damping piston 9a of the opening damper 26 is moved out of the rest position against the force of the spring 10a until the damping piston 9a bears against the stop 24a. During this phase, the opening pressure prevails in the pressure line 6 downstream of the opening damper 26 unhindered, the check valve 16 of the damper 25 is opened and opened as a result of the valve 1 by the increasing pressure in the pressure chamber 5 very quickly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Valve Device For Special Equipments (AREA)
  • Length Measuring Devices By Optical Means (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)
  • Glass Compositions (AREA)
  • Noodles (AREA)

Claims (4)

  1. Dispositif d'amortissement (7, 7a) pour un composant oscillant, en particulier une soupape (1), réalisée de préférence sous forme de soupape d'injection (2), d'un moteur à combustion interne, ledit composant étant actionnable hydrauliquement par l'intermédiaire d'un piston d'actionnement (3), le piston d'actionnement (3), sollicité de préférence par une force de rappel (F), étant en limite à une enceinte à pression (5), susceptible d'être sollicitée par une pression par l'intermédiaire d'une conduite à pression (6) guidant une fluide de travail, le dispositif d'amortissement (7, 7a) étant disposé dans la conduite à pression (6), le dispositif d'amortissement (7, 7a) présentant un piston d'amortissement (9, 9a), déplaçable longitudinalement dans un cylindre (8, 8a) entre deux positions finales, dans le piston d'amortissement (9, 9a) étant disposé au moins un canal d'amortissement (11, 11a), s'étendant sensiblement dans la direction longitudinale du piston d'amortissement (9, 9a), reliant en écoulement ensemble deux faces frontales (12, 13), opposées l'une à l'autre, du piston d'amortissement (9, 9a) et, dans le canal d'amortissement (11, 11a) étant disposé un clapet anti-retour à étranglement (14, 14a), dont l'effet d'étranglement dépend du sens de passage de l'écoulement, caractérisé en ce que le dispositif d'amortissement (7, 7a) est réalisé sous forme d'amortisseur à la fermeture (25), la résistance à l'étranglement du clapet anti-retour à étranglement (14) étant moindre dans le sens d'écroulement du fluide de travail à l'ouverture du composant que dans le sens inverse, et en ce que, en amont de l'amortisseur à la fermeture (25), est disposé un amortisseur à l'ouverture (26), l'amortisseur à l'ouverture (26), réalisé de préférence avec une construction identique à celle de l'amortisseur à la fermeture (25), étant disposé selon une orientation opposée par rapport à l'amortisseur à la fermeture (25), en se référant au passage de l'écoulement.
  2. Dispositif d'amortissement (7, 7a) selon la revendication 1, caractérisé en ce que le clapet anti-retour à étranglement (14, 14a) présente un clapet anti-retour (16, 16a) contournable par un canal de dérivation (15, 15a).
  3. Dispositif d'amortissement (7, 7a) selon la revendication 1 ou 2, caractérisé en ce qu'un ressort (10, 10a), pressant le piston d'amortissement (9, 9a) en une première position finale correspondant à la position de repos, agit sur le piston d'amortissement (9, 9a), dans le sens d'ouverture du clapet anti-retour à étranglement (14, 14a).
  4. Dispositif d'amortissement (7, 7a) selon l'une des revendications 1 à 3, caractérisé en ce que la course du composant, provoquant effectivement, par déplacement de volume, la course du piston d'amortissement (9, 9a), est inférieure à la course maximale du composant.
EP07718499A 2006-06-13 2007-06-13 Dispositif d'amortissement pour un composant oscillant Not-in-force EP2027387B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT10052006A AT501574B1 (de) 2006-06-13 2006-06-13 Optischer wegsensor
AT10982006A AT501679B1 (de) 2006-06-29 2006-06-29 Dämpfungseinrichtung für einen oszillierenden bauteil
PCT/AT2007/000288 WO2007143770A2 (fr) 2006-06-13 2007-06-13 Dispositif d'amortissement pour un composant oscillant

Publications (2)

Publication Number Publication Date
EP2027387A2 EP2027387A2 (fr) 2009-02-25
EP2027387B1 true EP2027387B1 (fr) 2010-09-15

Family

ID=38565744

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07718499A Not-in-force EP2027387B1 (fr) 2006-06-13 2007-06-13 Dispositif d'amortissement pour un composant oscillant

Country Status (5)

Country Link
EP (1) EP2027387B1 (fr)
JP (1) JP5042309B2 (fr)
AT (1) ATE481567T1 (fr)
DE (1) DE502007005050D1 (fr)
WO (1) WO2007143770A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT512027B1 (de) * 2013-01-30 2014-04-15 Avl List Gmbh Durchflussmessgerät
DE102015202876A1 (de) * 2015-02-18 2016-08-18 Robert Bosch Gmbh Ventileinrichtung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2138884B (en) * 1983-04-26 1987-02-18 Maschf Augsburg Nuernberg Ag I c engine fuel injection nozzle
EP0343147A3 (fr) * 1988-05-16 1990-10-03 Steyr-Daimler-Puch Aktiengesellschaft Soupape d'injection pour moteurs à combustion interne à injection à compression d'air
JPH0269063A (ja) * 1988-09-05 1990-03-08 Sharp Corp 自動情報配送システム
JP2887970B2 (ja) * 1991-09-17 1999-05-10 株式会社デンソー 燃料噴射装置
JP2950031B2 (ja) * 1992-08-11 1999-09-20 トヨタ自動車株式会社 燃料噴射弁
JPH09217665A (ja) * 1996-02-14 1997-08-19 Denso Corp 燃料噴射装置
DE60025939T2 (de) 2000-11-17 2006-09-21 Delphi Technologies, Inc., Troy Nadelhubdämpfer eines injektors für brennstoffeinspritzung und dämpfungsverfahren

Also Published As

Publication number Publication date
JP2009540197A (ja) 2009-11-19
JP5042309B2 (ja) 2012-10-03
DE502007005050D1 (de) 2010-10-28
EP2027387A2 (fr) 2009-02-25
ATE481567T1 (de) 2010-10-15
WO2007143770A2 (fr) 2007-12-21
WO2007143770A3 (fr) 2008-03-27

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