EP0970305B1 - Soupape d'injection a vanne de controle - Google Patents

Soupape d'injection a vanne de controle Download PDF

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Publication number
EP0970305B1
EP0970305B1 EP98966221A EP98966221A EP0970305B1 EP 0970305 B1 EP0970305 B1 EP 0970305B1 EP 98966221 A EP98966221 A EP 98966221A EP 98966221 A EP98966221 A EP 98966221A EP 0970305 B1 EP0970305 B1 EP 0970305B1
Authority
EP
European Patent Office
Prior art keywords
control chamber
drain
control
closing element
valve
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
EP98966221A
Other languages
German (de)
English (en)
Other versions
EP0970305A1 (fr
Inventor
Wilhelm Frank
Günter LEWENTZ
Jürgen Rink
Gerd Schmutzler
Joachim Vendulet
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.)
Siemens AG
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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 Siemens AG, Siemens Corp filed Critical Siemens AG
Publication of EP0970305A1 publication Critical patent/EP0970305A1/fr
Application granted granted Critical
Publication of EP0970305B1 publication Critical patent/EP0970305B1/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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements

Definitions

  • the invention relates to an injection valve with a control valve according to the preamble of claim 1
  • Injectors with a control valve are, for example used in a common rail injection system to the Control pressure in a control chamber, the pressure in the control chamber via a control piston onto an injection needle acts depending on the pressure of one Valve seat lifts off, and thereby fuel into an internal combustion engine is injected.
  • EP 0 604 915 A1 already discloses an injection valve with a Control valve known in which a control chamber via a Throttle is connected to a drain by a control valve is controlled.
  • the control valve has a closing member on that is associated with a valve seat that at the end the throttle is formed.
  • the closing element is over spring elements from the low pressure side onto the valve seat pressed.
  • An electromagnet is provided, which Closing member lifts off the associated valve seat, creating a Injection process is started.
  • the injector described has the disadvantage, however, that the throttle at one Break of the spring elements is open.
  • EP 0 826 876 A1 is the closest prior art an injector with a control valve known that a Has closing member which is assigned to a valve seat and that is connected to a piston that is connected to an actuator is in operative connection.
  • the piston is of an annular shape Spring holder partially enclosed, with which a spring element is in operative connection so that the closing member over the piston from the low pressure side onto the valve seat is pressed.
  • the closing element and the valve seat are open attached to the high pressure side.
  • the object of the invention is an injection valve to provide with a control valve that the flow restrictor the control chamber closes reliably.
  • An advantage of the invention is that the closing member of the control valve is arranged on the high pressure side and of the pressure in the control chamber pressed against the valve seat becomes. Another advantage is that the Locking element even if the pretensioning device is damaged the drain is closed securely.
  • Another advantage of the invention is that the closing member is connected via a valve tappet with a small diameter to an actuator piston which has a larger diameter.
  • the valve lifter is guided through a drain hole which has a correspondingly small diameter. Due to the large diameter, the actuator piston has great rigidity, so that the closing member can be moved precisely and quickly by an actuator that controls the actuator piston. Since the drain hole has a small diameter, the closing member can also be made correspondingly small, so that only a small force is required to move the closing member against the pressure in the control chamber and thereby open or close the drain hole.
  • FIG. 1 schematically shows part of an injection valve, in which a control valve is arranged.
  • a control valve for the sake of simplicity is only the control valve and not the entire injector shown.
  • the functioning and structure of a corresponding injector is, for example, in EP 0 604 915 A1.
  • the control valve has a control chamber 1, which has a Inlet throttle 4 in connection with a fuel inlet 3 stands.
  • the control chamber 1 is delimited by a control piston 2, which is movably arranged in a piston bore 35 and which is connected to an injection needle.
  • the control chamber 1 has a drain hole 5 which leads to a second recess 8 is guided via a derivative is connected to the fuel tank.
  • the second recess 8 goes up into a wider guide bore 34.
  • In the control chamber 1 has a first closing element 10, which merges into a valve rod 11 through the drain hole 5 is guided into the second recess 8.
  • a spring plate 13 is inserted in the second recess 8, which extends into the guide bore 35.
  • the Spring plate 13 has a U-shape with a base plate 16 is completed.
  • the bottom plate 16 is the drain hole 5 assigned.
  • the valve rod 11 is in the second recess 8 through a central bore 27 of the base plate 16 out.
  • the valve rod 11 preferably closes flush with the top of the bottom plate 16 and is preferred over a weld 17 in this area with the Bottom plate 16 connected.
  • the bottom plate 16 merges into a sleeve 28 which an angled stop ring in the upper end area 29 has.
  • the second recess 8 and the first recess 7, which forms part of the control chamber 1 preferably introduced into a valve plate 6.
  • the valve plate 6 is non-positively connected to the housing 36 of the injection valve connected.
  • a spring element preferably a compression spring 14 introduced under tension, so that in the rest position the first closing member 10 upwards in the direction of the drain hole 5 against an associated, first sealing seat 25 is pressed.
  • too other spring means such as a disc spring can be used.
  • the first sealing seat 25 is part of the wall surface of the control chamber formed in the entrance area to the drain hole 5.
  • the drain hole 5 preferably provides a drain throttle However, in a further development of the invention the discharge throttle be formed after the discharge hole.
  • the drain hole is in the rest position by the compression spring 14 5 closed by the first closing member 10. Moreover this embodiment offers the advantage that at one Failure of the compression spring 14, the spring plate 13 or the valve rod 11 the first closing member 10 from the pressure in the control chamber 1 prevails against the first sealing seat 25 is pressed and thereby the first closing member 10 the first Sealing seat 25 closes self-locking.
  • the bottom plate 16, the sleeve 28 and the stop ring 29 form the spring plate 13, in its cylindrical cavity an actuator piston 12 is inserted with its end face abuts the bottom plate 16.
  • the actuator piston 12 is movable arranged in the spring plate 13 and stands with an actuator, for example a piezoelectric actuator, in operative connection, that moves the actuator piston.
  • the first sealing seat 25 is preferably designed as a conical seat.
  • the first closing member 10 is partially spherical, the partial spherical shape associated with the first sealing seat 25 is.
  • the partial spherical shape is centered on the upper vertex into the cylindrical shape of the valve rod 11.
  • the part-spherical Shell surface of the first closing member 10 is adapted to the shape of the first sealing seat 25.
  • the flow rate that flows through the drain hole 5 is determined by the annular drain channel 30, the results from the drain hole 5 and the rod 11.
  • the drain channel 30 is designed in such a way that the drain channel 30 acts as a drain throttle.
  • the small diameter of the drain hole 5 now brings that Disadvantage that the valve rod through the drain hole is guided, an even smaller diameter having. Due to the small diameter, the valve stem has 10 low rigidity. This is disadvantageous for one fast and precise control of the first closing element 10.
  • the discharge throttle 5 as short as possible to make the valve rod 11 as short as possible can be trained.
  • the overall drive, which results from the valve rod, is harder 11 and the actuator piston 12.
  • the actuator piston 12 is located outside of the control chamber in a second Recess 8, which is connected to a guide bore 35.
  • the actuator piston 12 can have a larger diameter be formed so that the elasticity of the actuator piston 12 is less than that of the valve rod 11. Since the actuator piston is harder than the valve rod 11, the length of the actuator piston 12 for the adjustment of the elastic properties of little importance.
  • a further optimization of the control valve is achieved that the first closing member 10 of the shape of the control chamber 1 is adapted in such a way that the control volume in the Control chamber 1, which is not filled by the first closing member 10 is as small as possible. This makes it quick It is possible to empty and fill the control chamber, which makes the Switching times in which pressure is up or down in the control chamber is reduced, minimized. As a result, the switching times, with which the control piston 2 and thus the injection needle are moved, minimized.
  • the control chamber preferably has a cylindrical shape, which changes into a cone shape in the upper area, and the thus in the direction of the centrally arranged drain hole 5 tapered.
  • the conical shape represents the first sealing seat 25
  • the first closing member 10 is preferably part-spherical formed, the diameter of the partial spherical shape somewhat is smaller than the diameter of the cylindrical shape Control chamber 1.
  • the flat cutting surface on the underside of the first closing member 10 is parallel to the flat end surface of the control piston 1 and the end face of the Control piston 1 facing.
  • the control chamber 1 is preferred formed in length so that when fully open first closing member 10, i.e. at maximum deflection of the first closing member 10, the closing member 10 is not on pushes the control piston 2 so that the control volume as possible is kept small. This tuning can be carried out precisely be because the cut surface of the first closing member and the end face of the spool is flat and parallel to each other are arranged.
  • the operation of the control valve according to Figure 1 is as follows: The first closing member 10 is in the rest position pressed against the first sealing seat 25 by the compression spring 14, so that the drain hole 5 is closed. In order to is the control chamber 1 only via the inlet throttle 4 with the Fuel inlet 3 connected. In this state there is the control chamber 1 the same fuel pressure as in Fuel supply 3. As a result, the control piston is 2 acted upon by the high fuel pressure of the fuel inlet 3 and is pressed down with the appropriate force. The control piston 2 in turn presses an injection needle on an associated sealing seat so that no fuel is injected.
  • the actuator piston 12 is removed from the assigned actuator is moved up to the rest position, so that the first closing member 10 essentially of the compression spring 14 pressed against the first sealing seat 25 becomes.
  • the pressure is in the control chamber 1 at this time too low to make a noticeable contribution to closing the flow restrictor 5 to contribute. So that the drain hole 5 is closed and in the control chamber 1 turns out after some Time again the fuel pressure in the fuel supply 3 prevails, since fuel flows into the via the inlet throttle Control chamber 1 flows.
  • the control piston is through the adjusting high pressure moves back down so that also the injection needle back on the assigned sealing seat is pressed, thus interrupting the injection of fuel becomes.
  • the fuel pressure drops when the drain hole 5 is open, because more fuel flows through the drain hole 5 than flows through the inlet throttle 4.
  • the drain hole 5 is dimensioned accordingly and preferably provides a flow restrictor represents.
  • the arrangement according to FIG. 1 offers the advantage that the control volume is small in the control chamber 1, and thus the drain hole 5 opened faster and closed faster can be, since only the first closing member 10 in the control chamber 1 is arranged.
  • the volume is under control volume the control chamber 1, which is filled with fuel can be.
  • the compression spring 14, because of the large bias required is relatively large, is preferably outside the control chamber 1 and thus does not affect the control volume the control chamber 1.
  • first closing member is essentially spherical. This has the advantage that the spherical closing member on a conical first sealing seat when closing of the first sealing seat 25 independently due to the spherical shape adjusted.
  • the first closing member 10 can also in the sealing area preferably be conical, the Cone shape of the first closing member 10 to the cone shape of the first Sealing seat 25 is assigned symmetrically. At this Embodiment, however, the first closing member 25 should be in the middle and are guided symmetrically to the first sealing seat 25, so that the first sealing seat 25 is closed precisely.
  • the dimensioning of the drain hole is particularly advantageous 5 or the discharge channel 30 as a discharge throttle, whereby an additional outlet throttle is saved, and the outlet throttle directly adjacent to the control chamber, creating a low tax volume is achieved.
  • Derivation recess 37 is provided so that fuel from the Drain hole 5 even with the bottom plate 16 resting on the drain can drain, since the base plate 16 in the working position rests on the valve plate 6.
  • the actuator piston 12 directly on the Valve rod 11 on, the valve rod 11 as short as possible is formed and nevertheless a relatively large compression spring 14 can be used. This creates a large contact pressure in the rest position for securely sealing the first sealing seat 25 guaranteed.
  • An advantageous embodiment is a pre-assembled and to provide preset control valve unit, the throttle plate 6 with the drain hole 5 and with the first sealing seat 25, the first closing member 10 with the Valve rod 11, which is guided through the drain hole 5, the spring plate 13 to which the valve rod 11 is connected is, and the spring element 14, which between the spring plate 13 and the throttle plate 6 introduced biased is.
  • the throttle plate 6 preferably has the first recess 7, which represents at least part of the control chamber 1. Furthermore, in one embodiment, a second recess 8 for receiving the spring plate 13 in the Throttle plate 6 may be incorporated.
  • the control valve unit has the advantage that the individual Components are pre-assembled, and that an adjustment of maximum stroke of the first closing member 10 is made.
  • the spring plate 13 from one side against the Spring force of the spring element 14 against the throttle plate 6 pressed and the first closing member 10 from the other side with the valve rod 11 through the drain hole 5 into the hole 27 pushed the bottom plate 16.
  • the valve rod 11 becomes fixed to the base plate 16 welded. This is preferably done using laser welding. The laser beam falls over the open U-shape of the spring plate 13 and welds the valve rod 11 on the Top of the bottom plate 16 with a weld 17 with the Base plate 16.
  • Figure 2 shows schematically an injection valve with a Control valve in which the essential Differences compared to Figure 1 in the form of Closing member, the shape of the spring plate and an outlet throttle 23 lie.
  • a second closing member 19 is one assigned second sealing seat 26, the second sealing seat 26 and the associated second sealing surface 31 of the second Closing member 19 are formed as plane-parallel surfaces, that are associated with each other.
  • the second closing member 19 has essentially the shape of a T-piece, which in a second rod 20 passes through the drain hole 5 and through a second bore 32 of a second spring plate 21 is guided up to the top of the second spring plate 21.
  • the second spring plate 21 At the top of the second spring plate 21 is the second Rod 20 via a second weld 24 to the second Spring plate 21 connected.
  • the second spring plate is in the designed essentially cylindrical and points in the upper End area a second stop ring 33. Between the second stop ring 33 and the valve plate 6 is one Compression spring 14 clamped, the second closing member 19th biased upward against the second sealing seat 26.
  • the second spring plate 21 On the top of the second spring plate 21 there is a second one Actuator piston 22.
  • the second actuator piston 22 and the second spring plate 21 are in a guide bore 34 of the injector.
  • the guide bore 34 extends a drain line from a drain throttle 23 to Fuel tank is guided.
  • a discharge duct 37 is provided in the lower area, that from the mouth of the drain hole 5 to the edge region in which the compression spring 14 is arranged is.
  • the outlet throttle 23 can also be used 5 or the drain channel 30 is designed as a drain throttle his.
  • the arrangement according to FIG. 2 works as follows: In the rest position is the second closing member 19 through the Compression spring 14 with the second sealing surface 31 against the second Sealing seat 26 pressed and thus the drain hole 5 closed. So there is in the rest position in the control chamber 1 the same fuel pressure as in the fuel supply 3 is present. Consequently, the control piston 2 with a correspondingly large pressure.
  • the second actuator piston 22 is assigned by the Actuator moved down towards drain hole 5, so the second closing member 19 gives the drain channel 30 free, in the drain hole 5 from the free space results that the second rod 20 does not fill.
  • the derivative and the outlet throttle 23 to the fuel tank back. Since the inlet throttle 4 has a smaller cross section has as the outlet throttle 23, the fuel pressure drops in the control chamber 1.
  • the drain channel 30 with such a large flow cross section, that the throttle function by the discharge throttle 23rd is pictured. Consequently, the force on the spool increases 2 acts.
  • the flow restrictor can 23 omitted and the function of the outlet throttle 23 is by appropriate dimensioning of the drain channel 30 reached.
  • a control valve unit can be used that made the throttle plate 6 with the second closing member 19, that via the second spring plate 21 and a spring means 14 is biased and by determining the distance between the second closing member 19 and the second spring plate 21 is set to a defined maximum stroke.
  • the invention was based on the example of a control chamber with a Inlet and an outlet throttle described, but the Invention is applicable to any type of injection valve.

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

Claims (6)

  1. Soupape d'injection, comportant un boítier (36) dans lequel une chambre de commande (1) est pratiquée,
       comprenant un piston de commande (2) délimitant la chambre de commande et pouvant se déplacer dans le boítier (36),
       comprenant une amenée (4) alimentant la chambre de commande avec un fluide pressurisé, en particulier avec du carburant,
       comprenant un écoulement (5, 37) par lequel le fluide pressurisé s'écoule de la chambre de commande,
       comprenant un organe de fermeture (10, 19) affecté à un siège d'étanchéité de l'écoulement (5) et qui ouvre et ferme l'écoulement (5),
       comprenant un moyen de commande disposé à l'extérieur de la chambre de commande (1) et étant en relation opérationnelle avec l'organe de fermeture (10, 19),
       le siège d'étanchéité (25, 26) étant formé du côté de la haute pression,
       l'organe de fermeture (10, 19) étant disposé du côté de la haute pression,
       l'organe de fermeture (10, 19) étant relié à une tige de soupape (11, 20),
       la tige de soupape (11, 20)traversant l'écoulement (5),
       la tige de soupape (11, 20) étant en relation opérationnelle avec le moyen de commande,
       l'organe de fermeture (10, 19) étant disposé dans la chambre de commande (1) et l'organe de fermeture (11, 19) étant sollicité contre le siège d'étanchéité (25, 26) par un moyen de ressort (14) disposé à l'extérieur de la chambre de commande,
       caractérisée en ce que
    la tige de soupape (11, 20) est reliée du côté de la basse pression à un porte-ressort (13),
    le moyen de ressort (14) est tendu entre le porte-ressort (13) et le boítier (36), de sorte que l'organe de fermeture (11, 19) est poussé contre le siège d'étanchéité (25, 26),
    le porte-ressort (13) est réalisé en forme de douille comportant à une extrémité une plaque de fond (16) qui ferme la forme de la douille et qui est adjointe à l'écoulement (5),
    la plaque de fond (16) est reliée à la tige de soupape (11), et
    un piston de travail (12) qui est en relation opérationnelle avec le moyen de commande, est inséré dans la forme creuse de la douille.
  2. Soupape d'injection selon la revendication 1, caractérisée que la plaque de fond (16) comporte un alésage (27), que la tige de soupape (11) traverse l'alésage (27), et que la tige de soupape (11) est reliée à la plaque de fond (16) dans la partie supérieure de la plaque de fond (16).
  3. Soupape d'injection selon la revendication 1, caractérisée que l'écoulement (5) est agencé en étranglement.
  4. Soupape d'injection selon la revendication 1, caractérisée qu'une plaque (6) est prévue dans laquelle l'écoulement (5) est pratiqué, que la plaque (6) comporte un second évidement (8) pour le logement partiel d'un porte-ressort (13), et
       qu'un premier évidement (7) pour la formation partielle de la chambre de commande (1) et pour la formation du siège d'étanchéité est installé.
  5. Soupape d'injection selon la revendication 1, caractérisée que la forme de l'organe de fermeture (10, 19) est adaptée à la forme de la chambre de commande (1) de telle façon que le volume de commande de la chambre de commande (1) reste petit.
  6. Soupape d'injection selon la revendication 1, caractérisée qu'un ensemble de soupape de commande est prévu,
    qui comporte une plaque (6) dans laquelle l'écoulement (5) est pratiqué,
    qui contient l'organe de fermeture (10) avec la tige de soupape (11) traversant l'écoulement (5),
    qui contient le porte-ressort (13) auquel la tige de soupape (11) est connectée,
    qui comprend un élément de ressort (14) tendu entre le porte-ressort (13) et la plaque (6) et charge l'organe de fermeture (10) contre le siège d'étanchéité (25), la distance entre l'organe de fermeture (10) et le porte-ressort (13) étant fixée à une valeur prédéterminée de sorte qu'une course maximum de l'organe de fermeture (10) est ajustée.
EP98966221A 1997-12-23 1998-12-18 Soupape d'injection a vanne de controle Expired - Lifetime EP0970305B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19757656 1997-12-23
DE19757656 1997-12-23
PCT/DE1998/003746 WO1999034111A1 (fr) 1997-12-23 1998-12-18 Soupape d'injection a vanne de controle

Publications (2)

Publication Number Publication Date
EP0970305A1 EP0970305A1 (fr) 2000-01-12
EP0970305B1 true EP0970305B1 (fr) 2003-05-21

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP98966221A Expired - Lifetime EP0970305B1 (fr) 1997-12-23 1998-12-18 Soupape d'injection a vanne de controle

Country Status (4)

Country Link
US (1) US6168132B1 (fr)
EP (1) EP0970305B1 (fr)
DE (1) DE59808465D1 (fr)
WO (1) WO1999034111A1 (fr)

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DE19624001A1 (de) * 1996-06-15 1997-12-18 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
US5779149A (en) * 1996-07-02 1998-07-14 Siemens Automotive Corporation Piezoelectric controlled common rail injector with hydraulic amplification of piezoelectric stroke
JP3823391B2 (ja) 1996-08-31 2006-09-20 いすゞ自動車株式会社 エンジンの燃料噴射装置
US5875764A (en) * 1998-05-13 1999-03-02 Siemens Aktiengesellschaft Apparatus and method for valve control

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DE59808465D1 (de) 2003-06-26
EP0970305A1 (fr) 2000-01-12
WO1999034111A1 (fr) 1999-07-08
US6168132B1 (en) 2001-01-02

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