EP0880647A1 - Electrovanne - Google Patents

Electrovanne

Info

Publication number
EP0880647A1
EP0880647A1 EP97941849A EP97941849A EP0880647A1 EP 0880647 A1 EP0880647 A1 EP 0880647A1 EP 97941849 A EP97941849 A EP 97941849A EP 97941849 A EP97941849 A EP 97941849A EP 0880647 A1 EP0880647 A1 EP 0880647A1
Authority
EP
European Patent Office
Prior art keywords
armature
valve
solenoid valve
anchor
anchor bolt
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.)
Withdrawn
Application number
EP97941849A
Other languages
German (de)
English (en)
Inventor
Holger Rapp
Andreas Kellner
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 EP0880647A1 publication Critical patent/EP0880647A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0689—Braking of the valve element
    • 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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0021—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures
    • F02M63/0022—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of mobile armatures the armature and the valve being allowed to move relatively to each other
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to a solenoid valve according to the preamble of the main claim.
  • a solenoid valve is known from EP 0 690 223 A2. This is used there to control an electrically controlled fuel injection valve.
  • the valve needle of the fuel injection valve is loaded in the closing direction by pressure prevailing in a control chamber.
  • the solenoid valve works in a known manner so that it initiates the discharge of the control chamber to initiate the injection when the magnet of the solenoid valve is excited and thus the valve needle of the injection valve is lifted from its seat under the action of the high pressure acting on it.
  • the armature is firmly connected to an armature bolt, on which in turn the valve member of the solenoid valve sits.
  • the disadvantage of the known solenoid valve is that the armature can oscillate and / or the valve member can bounce during operation, which is particularly the case is disadvantageous if a fast switching sequence of the solenoid valve is required and controlled by the solenoid valve, an injection divided into a pre-injection and main injection is to be carried out.
  • Solenoid valve can come with the same control, which causes a spread of the injection quantities.
  • the solenoid valve with the characterizing features of the main claim has the advantage over that a bouncing of the valve member on its seat and a reverberation of the first armature part are prevented, so that after closing the solenoid valve this
  • Valve member maintains its closed position and the armature part quickly returns to its rest position after a desired first evasive movement before the main injection begins.
  • damping of a deflection movement of the armature part can be achieved without additional parts by creating a damper pocket in the region of the armature part.
  • FIG. 1 shows a section through part of an injection valve with the solenoid valve according to the invention in section, with an anchor plate movably coupled to an anchor bolt
  • FIG. 2 shows a first damper pocket type
  • FIG. 3 shows a second damper pocket type.
  • FIG. 1 shows a partial section through an electrically controlled injection valve 1, as is known, for example, from the prior art mentioned at the beginning.
  • an injection valve is intended for use in a fuel injection system which is equipped with a high-pressure fuel reservoir which is continuously supplied with high-pressure fuel by a high-pressure feed pump and from which this fuel can be supplied to the internal combustion engine under injection pressure via individual electrically controlled injection valves.
  • the injection valve 1, shown in part and in section, has an injection valve housing 4 with a longitudinal bore 5, in which a valve piston 6 is received, which acts at one end on a valve needle, not shown, which in turn is known, e.g. interacts with injection openings of the fuel injection valve in the manner described at the beginning of EP 0 690 223.
  • the valve piston 6 serves to actuate the
  • Valve needle in the closed position, which in turn is constantly exposed to high-pressure fuel acting in the opening direction, which is supplied from the high-pressure accumulator via a pressure bore 8 running in the longitudinal direction in the valve housing 4. About this hole is the Injection openings also supplied the amount of fuel to be injected, which is injected into the combustion chamber of the associated internal combustion engine.
  • a connection piece 9 is provided on the valve housing 4.
  • valve piston 6 is guided at its end opposite the valve needle, not shown, in a cylinder bore 11 which is introduced into a valve piece 12.
  • the end face 13 of the valve piston includes a control pressure chamber 14, which is constantly connected via a radial throttle bore 15 leading through the wall of the valve piece to an annular space 16 surrounding the valve piece, which is also in constant communication with the connecting piece 9 and the high fuel pressure prevailing in the high-pressure fuel reservoir.
  • valve piece 12 Coaxial to the valve piston 6 branches off from the control pressure chamber 14 a bore 17 running in the valve piece 12, which contains a relief throttle 18 and opens into a relief chamber 19, which is connected here in a manner not shown with a fuel return of the injection valve.
  • the bore 17 emerges from the valve piece in the region of a conically countersunk part 21 of the outer end face of the valve piece 12.
  • the valve piece 12 is firmly clamped to the valve housing 4 in a flange area 22 via a screw member 23.
  • a valve seat 24 is formed, with which a valve member 25 of a solenoid valve 30 controlling the injection valve interacts.
  • the valve member 25 is coupled to a two-part armature in the form of an anchor bolt 27 and an armature disk 28, which with a Electromagnet 29 of the solenoid valve 30 acts together.
  • the anchor plate is dynamically displaceably mounted on the anchor bolt under the action of its inertial mass against the biasing force of a return spring spring 35 and is pressed by this return spring against a stop ring 26 on the anchor bolt in the idle state.
  • the return spring 35 is supported on the housing via a flange 32 of a guide piece 34 guiding the anchor bolt, which is firmly clamped with this flange between valve piece 12 and screw part 23 in the valve housing.
  • the armature bolt and with it the armature disk and the valve member 25 connected to the armature bolt are constantly acted upon in the closing direction by a locking spring 31 which is fixed to the housing, so that the valve member 25 is normally in the closed position on the valve seat 24.
  • valve member 25 Between the valve member 25 and the armature plate 28 there is an annular shoulder 33 on the armature bolt 27, which strikes the flange 32 when the electromagnet is excited and thus limits the opening stroke of the valve member 25.
  • an adjusting washer 38 is inserted between flange 32 and valve part 12.
  • the opening and closing of the valve needle is controlled in the following way by the solenoid valve.
  • the control pressure chamber 14 In the closed position of the solenoid valve member 25, the control pressure chamber 14 is closed towards the relief side 19, so that the high pressure builds up there very quickly via the inlet via the throttle 15, which pressure is also present in the high-pressure fuel accumulator.
  • the pressure in the control pressure chamber 14 Over the surface of the end face 13, the pressure in the control pressure chamber 14 generates a closing force on the valve needle which is greater than the forces acting in the opening direction as a result of the high pressure.
  • the solenoid valve 30 closes the bore 17 again, the pressure in the control pressure chamber 14 can be built up very quickly again by the fuel flowing in via the throttle bore 15, so that the original closing force is immediately present and the valve needle of the fuel injection valve closes.
  • a bouncing occurs here when a relatively large mass is accelerated and then suddenly abruptly braked when anchor bolts with the anchor plate and valve member hit the valve seat as mass. Because now a substantial part of the anchor mass, the anchor plate, is slidably mounted on the other part of the anchor mass, the anchor bolt, the anchor plate 28 can move further against the force of the return spring 35 after the valve member 25 has been placed on the valve seat 24. so that once the effectively braked mass is less and the elastic deformation of the valve seat as an energy store, which leads to the disadvantageous rebounding of the valve member, is now less.
  • the trailing armature plate also generates a force increasing with the compression of the return spring 35 on the valve member, which additionally holds the valve member stably in its seat and counteracts the bouncing.
  • this overrun can then disadvantageously produce a considerable swinging of the armature plate 28 against the return spring 35, so that the position of the armature plate is undefined when the valve member is actuated immediately thereafter, and the solenoid valve is not switched sufficiently quickly and with a reproducibly constant switching time .
  • FIG. 2 shows only the part of the anchor bolt 27 with the anchor plate 28 ′ and the slider 34 ′ that can be seen in FIG. 1.
  • the armature is designed as a disk which adjoins the poles of the electromagnet 29 in a plane-parallel manner and which, on the other hand, merges into a sliding sleeve 39 which slides on the armature bolt 27.
  • the glide path is in turn determined on the one hand by the stop 26 in the form of a snap ring inserted in the anchor bolt 27 and on the other hand by the contact of the sliding sleeve 39 with its end face 40 on the end face 41 of the slider 34 '.
  • the compression spring 35 normally holds the anchor plate 28 'in contact with the stop 26, as shown in FIG.
  • the end faces 40 and 41 are now designed in such a way that they form a damping space 50, in that one end face, for example the end face 40, is of stepped design with a projection 51 pointing in the axial direction, which directly comprises the anchor bolt, and the other end face 41 one Has axial recess 52 complementary to the projection 51, in the case of a relative movement of the anchor plate 28 'to the sliding sleeve 39 when the anchor bolt is stationary, the projection dips and encloses the damping chamber 50 in the recess 52 on the end face, compresses the amount of fuel contained in the relief chamber 19 there and thereby brakes the relative movement.
  • the anchor bolt has brought the valve member 25 into the closed position and is thus fixed in place.
  • the anchor bolt 27 ' is now designed in a stepped manner, with an anchor bolt part 42 having a smaller diameter to the side of the anchor plate 28' and a larger anchor bolt part 43 to the side of the valve member 25 out.
  • An annular shoulder 45 is formed between the two and points toward the electromagnet 29.
  • the longitudinal bore through the sliding sleeve 39 of the armature 28 ' is also formed as a stepped bore with an im
  • the damping dynamics are also set for the return movement of the anchor plate via the leakage gap between the anchor bolt and the sliding sleeve. This leakage gap also serves to replenish the damping space 50 '.

Abstract

La présente invention porte sur une électrovanne (30) dont le rotor de magnéto (28, 27) est conçu en plusieurs parties et présente un disque d'armature (28) ainsi qu'un boulon d'armature (27) guidé dans une pièce coulissante (34). Pour éviter une oscillation après impulsion du disque d'armature (28) après une fermeture de l'électrovanne (30), le rotor de magnéto (25) est équipé d'un amortisseur (50) qui permet de respecter rigoureusement les courts temps de commutation nécessaires de l'électrovanne (30). Celle-ci (30) est destinée à des systèmes d'injection employés avec des rails d'utilisation courante.
EP97941849A 1996-12-07 1997-08-29 Electrovanne Withdrawn EP0880647A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19650865A DE19650865A1 (de) 1996-12-07 1996-12-07 Magnetventil
DE19650865 1996-12-07
PCT/DE1997/001887 WO1998025025A1 (fr) 1996-12-07 1997-08-29 Electrovanne

Publications (1)

Publication Number Publication Date
EP0880647A1 true EP0880647A1 (fr) 1998-12-02

Family

ID=7813965

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97941849A Withdrawn EP0880647A1 (fr) 1996-12-07 1997-08-29 Electrovanne

Country Status (9)

Country Link
US (1) US6062531A (fr)
EP (1) EP0880647A1 (fr)
JP (1) JP2000505855A (fr)
KR (1) KR19990077074A (fr)
CN (1) CN1095931C (fr)
DE (1) DE19650865A1 (fr)
HU (1) HU220553B1 (fr)
RU (1) RU2190119C2 (fr)
WO (1) WO1998025025A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013038186A1 (fr) 2011-09-16 2013-03-21 Clyne Energy Limited Appareil de chauffage d'aliments

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HUP9901293A3 (en) 2000-12-28
DE19650865A1 (de) 1998-06-10
HU220553B1 (hu) 2002-03-28
WO1998025025A1 (fr) 1998-06-11
HUP9901293A2 (hu) 1999-08-30
CN1095931C (zh) 2002-12-11
RU2190119C2 (ru) 2002-09-27
CN1210575A (zh) 1999-03-10

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