EP0438479B1 - Elektrisch betätigbares ventil für kraftstoff-einspritzanlagen für brennkraftmaschinen - Google Patents

Elektrisch betätigbares ventil für kraftstoff-einspritzanlagen für brennkraftmaschinen Download PDF

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Publication number
EP0438479B1
EP0438479B1 EP89911706A EP89911706A EP0438479B1 EP 0438479 B1 EP0438479 B1 EP 0438479B1 EP 89911706 A EP89911706 A EP 89911706A EP 89911706 A EP89911706 A EP 89911706A EP 0438479 B1 EP0438479 B1 EP 0438479B1
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EP
European Patent Office
Prior art keywords
armature
valve
fuel
magnetic
pole
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EP89911706A
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English (en)
French (fr)
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EP0438479A1 (de
Inventor
Gerhard Dipl.-Ing. Mesenich
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Siemens AG
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Siemens AG
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    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/005—Arrangement of electrical wires and connections, e.g. wire harness, sockets, plugs; Arrangement of electronic control circuits in or on fuel injection apparatus
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0614—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0614—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature
    • F02M51/0617—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature having two or more electromagnets
    • F02M51/0621—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of electromagnets or fixed armature having two or more electromagnets acting on one mobile armature
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0632—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a spherically or partly spherically shaped armature, e.g. acting as valve body
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto
    • F02M51/0675—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto the valve body having cylindrical guiding or metering portions, e.g. with fuel passages
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0689—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means and permanent magnets
    • F02M51/0692—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means and permanent magnets as valve or armature return 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/08—Injectors peculiar thereto with means directly operating the valve needle specially for low-pressure fuel-injection
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting

Definitions

  • the subject of the invention is a miniature electromagnetic fuel injector intended for the bulk injection of fuel into the suction pipe of combustion motors.
  • the fuel pressure preferably is in the order of 1-4 bar.
  • valves typically are of axially symmetric design.
  • the armature of such valves is located at the central axis of the valve and acts on a valve obturator which in most cases is of needle-type design.
  • the outside diameter of these valves is in general 20-25 mm.
  • Magnetic return flow usually is by means of a massive metallic housing which provides the base for both the magnetic pole and the valve seat. This housing must be precision made to prevent unacceptable dislocations of the magnetic pole. Usually this results in a series of narrowly defined precision tolerance limits which are difficult to achieve in production, or it is necessary to select component parts which fit precisely to each other.
  • the conventional injectors feature only very small stroke heights.
  • Stroke heights of modern injector valves are in the range of 0.05-0.1 mm.
  • the state of the art valves require extremely tight machining tolerances.
  • state of the art valves require a difficult calibration procedure.
  • the fuel injector according to the instant invention in variance from state of the art designs, features a non-magnetizable casing which is solidly joined with the magnet pole and the valve seat, and serves as the radial guidance element of the armature.
  • the casing together with the components contained therein, forms a cartridge which is mounted inside the valve housing.
  • Functional testing of the cartridge can be done independent from the other mounting parts during an early manufacturing stage. This simplifies manufacture of the total valve considerably, rejects are reduced. Loss of a complete valve in case of possible performance problems is thus avoided. Furthermore, no seals are required inside the cartridge.
  • the injector housing is predominately plastic material, therefore inexpensive to manufacture.
  • the fuel injector has small overall dimensions, the external diameter in general is 14-16 mm. The valve is therefore readily adapted to the most varied mounting conditions.
  • the magnetic circuit of the injector according to Fig. 1 consists of magnet pole 103, armature 106 and bracket 104. Magnet pole 103 and armature 106 are encircled by magnet coil 107. Bracket 104 terminates in collar 109, which forms the side-pole of the magnetic circuit. By means of collar 109, the side-pole area is enlarged, which reduces the magnetic resistance between armature 106 and bracket 104. In the energized state, armature 106 closes directly against magnet pole 103. Arrangements for an additional permanent air gap 105 are made between magnet pole 103 and bracket 104, this gap is used for the dynamic calibration of the valve.
  • the bearing for magnet pole 103 is provided by the non-magnetizable casing 101, which also serves as the radial guidance element of armature 106. Inside armature 106 provision is made for reset spring 108. Armature 106 terminates in cone-shaped obturator 110. Casing 101 also contains valve seat 111 and nozzles 112. Casing 101, magnet pole 103, armature 106, and valve seat 111, which is inside the casing, jointly form a cartridge which can be manufactured independently from parts which are extraneous to the cartridge. Fuel delivery to the valve seat is via side orifice 102 in the casing. The valve seat region is sealed against the valve housing, which is not drawn, by means of gasket ring 113.
  • Fig. 1 offers many additional advantages over state of the art valves which are not directly obvious.
  • the cartridge design of the valve makes it possible to carry out initial performance testing during early manufacturing stages.
  • valve features several special features with respect to magnetic characteristics.
  • Magnetic return flow is via slide-on bracket 104.
  • Bracket 104 is open on one side, only partially enclosing magnet coil 107 at its outer perimeter. This results in an increase of magnetic resistance between the parts of the magnetic circuit which are inside the magnetic coil (magnet pole and armature), and the section which is outside the magnetic circuit (bracket). Thereby the stray field of the magnetic circuit is reduced, resulting in greater effectiveness of the electric energy conversion.
  • several additional gaps are provided, approximately evenly distributed in the flow of the magnetic field lines.
  • Working gap 114 is arranged inside the magnetic coil, calibration gap 105, and side-gap 115, which is formed by the non-magnetic casing 101, are disposed outside magnetic coil 107.
  • armature 106 closes directly against magnet pole 103.
  • no permanent air gap is present between pole 103 and armature 106.
  • Such permanent air gaps must usually be maintained with great precision.
  • the dimension of the permanent air gap generally is of the same order of magnitude as the armature stroke in case of state of the art valves. Even small changes in the permanent air gap from the set value must then be compensated for by relatively significant changes in the reset spring force. Significant variations from the set point value of the spring are not desirable since they can result in variations of the dynamic flow-through characteristics for the case that the trigger voltage fluctuates.
  • improved electromagnetic efficiency is obtained; a sufficiently fast collapse of the magnetic field, after cutting off the excitation current, is virtually forced by calibration gap 105 and side-gap 115.
  • the overall efficient magnetic design of the circuit makes it possible to reduce its dimensions, without also reducing the magnetic effectiveness in comparison with state of the art valves. This makes it possible to use a small diameter armature which, of course, means an armature with very low mass. In total, the valve permits very fast floating times, coupled with low electric energy consumption.
  • the special feature connected with this valve is found in the additional permanent air gap 105, which serves for dynamic calibration.
  • a change in air gap 105 causes a change in the magnetic resistance of the magnetic circuit.
  • Enlarging air gap 105 causes a delay in pickup and a decrease in drop off. This allows calibration of the dynamic flow characteristics by setting air gap 105 to desired values.
  • Dynamic calibration by means of air gap 105 offers a number of distinct advantages. For a start, such calibration possibilities allow for considerably larger tolerances in the spring resiliency characteristics of reset spring 108. Furthermore, calibration is more stable even in the case of changing excitation voltages, since the spring force is approximately the same for different valves. Due to the approximately even distribution of the individual air gaps in the pathway of the magnetic field, a decrease in the stray magnetic field results, and thus an improvement of electromagnetic efficiency.
  • Magnetic coil 107 is slipped sidewise into bracket 104.
  • Bracket 104 can be thin-walled, since it has no load bearing function with respect to magnetic pole 103.
  • state of the art valves require rather thick-walled housings to prevent unacceptable dislocations of the magnetic pole.
  • magnetic coil 107 is only partially enveloped, it can readily be embedded in plastic, together with the contact pins. This prevents possible leakage paths, and the heat transmission of the coil is improved. The reject losses often incurred during the manufacturing process are reliably precluded. The result is a stable and compact housing design, inside of which the cartridge valve is well protected from mechanical damage.
  • Calibration of the injector proceeds in several separate steps. At first, reset spring 108 is inserted into armature 106, it is to be noted that with regard to spring resiliency, relatively large tolerance values are allowable. Generally, no special selection process with respect to spring resiliency is necessary. Then, the static fuel flow characteristics, or respectively the armature stroke, is set by pressing magnet pole 103 into casing 101 to a desired depth. Dynamic calibration is achieved by pressing the cartridge valve into the valve housing (not drawn) to the desired depth. This changes the distance between pole 103 and bracket 104.
  • valve exhibits some special features with respect to hydraulic design.
  • reset spring 108 is positioned in a chamber 116 which is open at one end and is located inside of armature 106.
  • Annular pole surface 117 of armature 106 features engraved hydraulic damping slots which attenuate armature movement and permit fuel to flow into chamber 116 even while the armature is in the closed position. This prevents hydraulic sticking of armature 106 at magnet pole 103.
  • the damping slots are arranged in such a manner that between them three contact areas result which are distributed evenly around the circumference of the armature pole surface. The contact surfaces should extend radially over the total width of annular pole area 117. Chamber 116 enhances the damping effects of the hydraulic damping slots.
  • the depth of the slots should be about 10-20 micrometers. At this depth, good hydraulic damping of the closing movement of the armature is obtained, without also resulting in unacceptable damping of the reset step. Because of hydraulic damping in working gap 114, relatively soft material can be used in this region without resulting in unacceptable wear.
  • the design of the hydraulic damping gaps in particular is described in a separate application (Electromagnetic Injector and Procedures for its Manufacture).
  • the injector also is characterized by steady state characteristics where the hydraulic reset forces for the energized armature are larger than for the armature in reset position. Given such steady state characteristics, the drop-off time of the armature is considerably shortened. To achieve this, the valve obturator 110 of armature 106 is internally guided by casing 101 with a slight amount of radial play of some 1/100 mm. This results in an annular gap which surrounds obturator 110. Inside this gap a pressure drop results which grows with increasing flow, and therefore with increasing armature stroke. Due to this pressure drop, as the armature stroke increases, a hydraulic force is generated which opposes the magnetic force.
  • the radial play of the obturator is set in such a way that for the energized armature a permanent pressure drop of about 10-20% of the static fuel pressure is produced behind the annular gap.
  • the diameter of the annular gap should be chosen to be 2-3 times larger than that of valve seat 111.
  • the obturator is hydraulically centered, and impacting of the obturator onto the valve seat is dampened.
  • the employment of hardened materials for both obturator and valve seat does not have to be considered for the dimensions stated. By dampening the reset movement, armature bounce is significantly reduced.
  • the obturator also features a groove 118, which serves to increase the permanent pressure drop and to uniformly distribute the pressure drop around the perimeter of the annular gap.
  • valve seat 111 The hydraulic reset feature and the defined steady state characteristics are especially useful for multipoint injection where each motor cylinder is separately supplied with fuel by an individual injector.
  • Multipoint injection requires only a minimal amount of fuel flow which can be achieved already with a small diameter of valve seat 111.
  • Valve seat diameters in general need not be larger than 1-2 mm. The stated dimensions can thus be implemented already for an obturator diameter of 3-4 mm.
  • the injector shown in Fig. 2 features a plastic housing 222.
  • Magnetic coil 212 and connection pins 223, as well as bracket 213, are encased by injection-moulded plastic.
  • the upper part of housing 222 carries a threaded segment 225 into which the valve cartridge fits.
  • the magnetic circuit of the valve consists of armature 201, magnetic pole 221 and bracket 213. These components of the magnetic circuit consist of ferro-magnetic material.
  • Magnetic pole 221 is mounted in non-magnetizable casing 208. Mounting is preferably by pressure insertion, followed by laser welding. At the bottom end of casing 208, valve carrier 203 is pressed in and welded.
  • Reset spring 216 is located inside armature 201.
  • Reset spring 216 is located on valve needle 202 which is pressure fitted into armature 201. Reset spring 216 is held by chamber 230, located inside pole 221 and armature 201. Chamber 230 is closed off to the side for the energized armature. At the top of chamber 230 a drilled passage 217 is arranged which connects chamber 230 with the outer volume. Passage 217 reduces the danger of steam bubbles in the upper section of chamber 230, and also decreases the possibility of hydraulic sticking of armature 210 at pole 221. Furthermore, an additional damping effect of armature movement can be obtained by reducing the diameter of orifice 217 to 0.2-0.4 mm so that the outflow of fuel from chamber 230 towards the end of armature movement is restrained.
  • valve seat 207 On the face surface of armature 201 a circumferential damping slot 231 is provided, which attenuates armature movement. This damping slot additionally results in hydraulic parallel guidance of the armature. Based on this hydraulic parallel guidance, the flow conditions at valve seat 207 are easily reproducible without requiring radial guidance for the valve needle in the region of valve seat 207.
  • the diameter of valve needle 202 is approximately 2 mm, that of the armature is about 4 mm.
  • the cone shaped valve seat 207 is machined into valve carrier 203.
  • Valve carrier 203 also serves as the mounting location for nozzle plate 204 in diffuser 205, both are securely clamped in position. The valve is continuously perfused by fuel. Fuel enters via side orifice 210 into the lower section of valve housing 222.
  • annular channel 232 which serves as fuel passage.
  • annular channel 232 results in a floating mounting arrangement for the cartridge valve, so that virtually no radial forces from housing 222 can be exerted on the cartridge valve.
  • fuel reaches the upper housing region via passages 218, 219, and 220. From there, the fuel proceeds via orifice 226 into circumferential annular channel 227, and from there to fuel recycle.
  • Housing 222 is sealed in the mounting hole by means of gasket rings 211 and 224.
  • the cartridge valve is sealed against the housing by means of gasket ring 226, which is located on valve carrier 203.
  • Housing 222 is surrounded by a fuel filter, which has not been drawn.
  • Dynamic calibration of the valve is achieved by changing the axial location of the cartridge valve with respect to housing 222. Positioning is done by threading the cartridge to a given depth. As the exact location of the cartridge changes, the relative locations of the working pole in relation to the magnetic coil, and the overlapping in the area of side-gaps 214 and 215 is changed. During this positioning process, two magnetic parameters are being used for calibration: on the one hand a change in the stray field, by the relative positions of working pole and magnetic coil, on the other hand a change in magnetic resistance by the changes in the overlap of the side-gaps. In this case, the radial arrangement of upper gap 215, in comparison with the axial arrangement of calibration gap 105 in Fig. 1, results in lower sensitivity.
  • the design according to Fig. 2 requires greater axial dislocations. This renders the valve less sensitive to possible changes in the position of the cartridge valve, such changes might, for instance be caused by aging effects or by improper handling. Furthermore, this makes possible larger tolerances in the housing area.
  • FIG. 3 A further advantageous design of armature and valve needle, with respect to magnetic principles and kinematic concerns, is shown in Fig. 3.
  • This type of armature design is preferably used for valves of the type described in Fig. 2.
  • tubular armature 302 is directly pressed onto valve needle 301; the armature seals against pole 304 with closing pin 303.
  • the diameter of valve needle 301 is about 2 mm.
  • Closing pin 303 has a diameter of about 1 mm.
  • the reset spring is inside armature 302, mounted on closing pin 303. Armature 302 is pressed onto valve needle 301 and further secured against dislocations by welding bead 309.
  • the contact surface of closing pin 303 extends about 20 micrometers beyond pole surface 307, resulting in an annular damping slot in the pole region.
  • the advantage of the design according to Fig. 3 is to be found in exceptionally effective damping of the closing movement of the armature with only minimal hydraulic sticking. This damping effect is obtained by displacement of fluid from the annular chamber 310, located inside the armature, which results in an especially strong damping effect. Because of the very small closing surface of pin 303, hydraulic sticking is prevented. In addition, it is of advantage that no limit stop is present in the working pole area, in contrast to the design in Fig. 2. This results in a faster decay of the magnetic field after cutting off the energizing current.
  • Fig. 4 describes a valve of especially small dimensions, equipped with a ball armature.
  • Armature diameter is preferably about 2.5-3 mm.
  • Housing diameter is about 14 mm.
  • Magnetic features are those of the valve design according to Fig. 1.
  • the magnetic circuit of the valve consists of armature 412, magnetic pole 408, and bracket 402.
  • the working gap of the magnetic circuit is located about in the middle of the coil.
  • Around armature 412 an additional side-pole is arranged. Two different designs are represented: in the right half of the drawing, side-pole 417 has been pressed onto non-magnetizable casing 423. This approach is inexpensive, but less advantageous from magnetic considerations.
  • pole 408 is mounted directly on valve carrier 413; both valve seat 416 and the space for pole 408 are machined into valve carrier 413.
  • pole 408 is mounted on non-magnetic casing 419, which is joined to side-pole 418. Side-pole 418 is connected to valve carrier 413.
  • Nozzle plate 415 is clamped by diffuser 414 in valve carrier 413.
  • Fuel supply is via annular channel 406 through filter 407 into the interior of housing 401. From there the fuel path proceeds on the outside of the cartridge via orifices 420 to valve seat 416.
  • Bracket 402, magnetic coil 403 and connection pins 404 are embedded in injection-moulded plastic during manufacture of housing 401. Dynamic calibration is by means of the insertion depth of the cartridge valve, this changes calibration gap 425.
  • the cartridge valve is sealed through gasket 421, the housing is sealed with gaskets 405 and 422.
  • Fig. 5 describes a valve where the armature reset is effected by means of a permanent magnet. This allows omission of the otherwise necessary reset spring. Dynamic calibration of the valve is by means of an externally generated alternating magnetic field.
  • the electromagnetic circuit of the valve consists of armature 514, working pole 505, return flow cap 503 and side-pole 506.
  • the electromagnetic circuit encloses magnetic coil 504.
  • the permanent magnetic circuit consists of armature 514, side-pole 506, permanent magnet 508, pole fixture 509 and resting pole 528. Resting pole 528 has been machined into valve carrier 510. Armature 514 has been pressed onto valve needle 513. With coil 504 in the unenergized state, armature 514 is drawn in the direction of resting pole 528 under the influence of the permanent magnetic field; valve needle 513 in this case closes against valve seat 530. For the closed valve, a permanent air gap 527 remains between armature 514 and resting pole 528.
  • this permanent air gap should be about the same as the armature stroke and be at least 0.1 mm.
  • the closing force at the end of the stroke movement would be too strong.
  • Such strongly increasing closing forces are unfavorable for the dynamic characteristics of the valve.
  • part of the magnetic field passes through the permanent air gap 526, causing a permanent pull in this area.
  • a permanent residual gap is necessary in the area of working gap 526. Without this permanent residual gap there is a danger of hydraulic sticking of armature 514 at working pole 505.
  • valve carrier 510 also contains nozzle plate 512 which is clamp-fastened by diffuser 511.
  • Valve carrier 510 is threaded into pole fixture 509. Non-magnetizable casing 507 is pressed onto valve carrier 510, it provides the mounting base for working pole 505.
  • Fuel supply is via orifices 519 in the lower section of housing 501.
  • Fuel passes then through slanted channels 518 into annular channel 523, and from there along the outside of the cartridge into the upper housing section.
  • the armature region is connected to the outer volume of the cartridge by side passages 524 and 525. These orifices can be executed in relatively small diameters in order to obtain additional attenuation of the floating movements of the armature.
  • fuel passes through radial channels 516 to fuel recycle.
  • the valve cartridge is sealed against housing 501 by gasket ring 521.
  • the outer segments of the magnetic circuit are embedded in injection-moulded plastic, together with coil 504 and connection pins 502.
  • Assembly of permanent magnet 508 can be done in the unmagnetized state in order to facilitate handling.
  • Calibration of the valve is done in several sequential steps. At first, a suitable armature with valve needle is matched with the valve carrier so that the preset permanent air gap 527 in the rest-pole area is produced. Because of the relatively large dimension of permanent air gap 527, matching of suitable parts allows for relatively large tolerances. Then working pole 505 is pressed into casing 507 in such a manner that the desired armature stoke is established. Dynamic calibration of the valve is done after complete assembly. To this effect an alternating magnetic field is applied to the permanent magnet, using a suitable magnetizing device, which causes it to be weakened and at the same time become stabilized with respect to magnetic properties. For increasing weakening of the permanent magnet the reset time of the valve is lengthened.
  • Pick-up time can be shortened or lengthened by weakening the permanent magnet depending on the flow direction of the current through coil 504.
  • the effect of weakening the permanent magnet is considerably larger with respect to reset time, thus allowing always for the desired change in calibration.
  • the direction of the current through coil 504 should be chosen in such a way that the coil-generated field is co-directional to the permanent magnetic field, when the armature is energized. Armature drop-off can be accelerated by a brief counter pulse.
  • Fig. 6 describes another valve where armature reset is by means of a permanent magnet.
  • an additional magnetic coil 610 has been installed near the permanent magnet.
  • the valve features two magnetic circuits with opposing magnetic fields.
  • permanent magnet 607 is positioned on one side only, resulting in a mono-stable behavior mode.
  • Mono-stable behavior is characterized by the fact that the valve returns automatically to the closed position as the energizing current is cut, without requiring an electrical counter pulse.
  • Mono-stable behavior is a safety requirement for injector valves, so that closing of the valve is guaranteed even for possible service interruptions of the electric triggering circuits.
  • the cartridge design of the injector in line with the present invention, allows for an especially simple and cost effective construction of the magnetic circuit. For comparable dynamic behavior, electric energy consumption is considerably less than for state of the art valves.
  • the upper magnetic circuit for the valve consists of working pole 604, armature 605 and return flow cap 614.
  • the lower magnetic circuit consists of armature 605, side-pole 611, return flow cap 614 and rest-pole 606.
  • the upper magnetic circuit surrounds magnetic coil 609, the lower magnetic circuit surrounds magnetic coil 610.
  • the permanent magnetic circuit is parallel to the lower magnetic circuit.
  • the permanent magnetic circuit consists of permanent magnet 607, pole fixture 608, rest-pole 606, armature 605, side-pole 611, and return flow cap 614. The latter is perforated and thus only partially visible.
  • a side-gap 622 is provided between rest-pole 606 and return flow cap 614, the side-gap serves to stabilize the demagnetization curve of the permanent magnet.
  • All segments of magnetic circuits consist of magnetically soft material.
  • a strong magnetic field establishes itself between armature 605 and rest-pole 606, this field acts toward closing of the valve.
  • permanent air gap 627 which is also designed as a hydraulic damping slot.
  • the resting-gap 626 should preferably have a length of about 20 micrometers, it may also be longer for practical reasons. Armature diameter should be about 4 mm.
  • the magnetic circuits are connected in such a way that for the energized state the magnetic field of the upper coil 609 is co-directional with the field of the permanent magnet, while that of the lower coil 610 is opposed to the field of the permanent magnet.
  • Armature reset can be considerably accelerated by a brief counter pulse.
  • Such a counter pulse can be generated in especially simple fashion by connecting a condenser in parallel to the triggering circuit.
  • Armature 605 is pressed onto valve needle 630 and can additionally be welded to same.
  • Valve needle 630 is radially guided inside rest-pole 606.
  • Rest-pole 606 is pressed into valve carrier 616 and welded to it.
  • Resting-gap 626 can be set by pressing rest-pole 606 to the corresponding depth into valve carrier 616.
  • the non-magnetizable casing 613 is fastened onto rest-pole 606 and provides the mounting base for working pole 604.
  • Working pole 604 contains damping passages 621 which provide fuel entry and exit to the armature region.
  • the outer sections of the magnetic circuit, together with contact pins 602 and the magnet coils, are completely embedded in injection-moulded plastic during manufacture of the housing.
  • Permanent magnet 607 is assembled from several segments, between these orifices 615 are provided, which serve as fuel inlets. Fuel passes along the outside of the cartridge valve into the upper housing region and from there via side passages 603 to recycle. The valve is sealed in the mounting opening by means of gasket rings 619 and 620. Lower gasket ring 619 is located directly on valve carrier 616, making a separate seal of the cartridge valve against housing 601 unnecessary. The cartridge valve is threaded into the lower pole fixture 608 and float-mounted inside housing 601.
  • Dynamic calibration is by means of weakening the permanent magnetic field through application of an alternating magnetic field.
  • the alternating magnetic field can also be applied by overexciting the magnetic coils of the valve with alternating current.
  • valve according to the instant invention can also be provided with a connection piece which is located in the central axis and serves as fuel supply device.
  • the contact pins for the magnetic coil are then moved to the side.
  • the design is externally similar to state of the art needle injector valves.
  • the valve is then directly exchangeable for one of these state of the art devices.
  • the central fuel connector can also be directly attached to the magnetic pole, however, this results in higher mechanical loads on the cartridge valve. It is therefore advantageous, even for the case of a central fuel connector, to connect it directly to the valve housing in order to reduce mechanical loading on the cartridge.
  • the non-magnetizable casing of the cartridge can be made thin-walled with less than 0.2 mm wall thickness.
  • the casing with as thin a wall as possible is of advantage from a magnetic perspective.
  • the proposed dimensions and methods of connecting are to be considered as suitable, but only as examples.
  • threaded connections could be employed.
  • a fuel filter will always be part of the valve, separate representation of it has been omitted.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Manufacturing & Machinery (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (3)

  1. Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine mit einem Hauptteil (222) mit einem Elektromagneten (212), einem nicht magnetischen Rohr (208), das sich durch den Elektromagneten erstreckt, einem magnetischen Polelement (221), das in einen ersten Abschnitt des Rohres eingesetzt ist und hiermit in Eingriff steht, einem magnetisch leitenden Anker (201), der in einen zweiten Abschnitt des Rohres eingesetzt ist und hiermit geführt in Eingriff steht, um sich in Abhängigkeit von einer Erregung und Aberregung des Elektromagneten in Längsrichtung des Rohres zu bewegen, einem Ventilelement (202), das durch die Bewegung des Ankers betätigt wird, um sich auf einen Ventilsitz (207), der an einem Ventilsitzelement (203) vorgesehen ist, zu setzen und von diesem abgehoben zu werden, einem Kraftstoffeinlaß eines Kraftstoffkanales, der zu einer Einlaßseite des Ventilsitzes führt und Öffnungseinrichtungen (209) zum Einführen von Kraftstoff in das Innere des nicht magnetischen Rohres besitzt, wobei sich der Kraftstoffkanal im Inneren des nicht magnetischen Rohres von den Öffnungseinrichtungen in Richtung auf die Einlaßseite des Ventilsitzes fortsetzt und wobei der Ventilsitz eine Auslaßseite aufweist, die sich gegenüber seiner Einlaßseite befindet und über die die Kraftstoffeinspritzvorrichtung Kraftstoff in den Motor einspritzt, dadurch gekennzeichnet, daß das nicht magnetische Rohr (208), das Polelement (221), der Anker (201) und das Ventilsitzelement (203) so miteinander verbunden sind, daß sie einen Einsatz bilden, der innerhalb des Hauptteiles (222) der Einspritzvorrichtung montiert ist, daß sich die Öffnungseinrichtungen (209) durch die Seitenwand des nicht magnetischen Rohres in einem dritten Abschnitt des nicht magnetischen Rohres erstrecken, der vom ersten und zweiten Abschnitt des nicht magnetischen Rohres verschieden ist, und daß der Anker keine inneren Kanäle aufweist, so daß ein Abschnitt des Kraftstoffkanales gemeinsam durch das Innere des nicht magnetischen Rohres und durch eine Außenseitenwandfläche des Ankers gebildet wird.
  2. Kraftstoffeinspritzvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Ventilelement einstückig mit dem Anker ausgebildet ist (Figur 1), so daß das Ventilelement und der Anker ein einziges Teil bilden.
  3. Kraftstoffeinspritzvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das nicht magnetische Rohr an den Öffnungseinrichtungen eine kreiszylindrische Form besitzt und daß der Anker einen diametral reduzierten Abschnitt aufweist, der den Öffnungseinrichtungen gegenüberliegt (Figur 1).
EP89911706A 1988-10-10 1989-10-10 Elektrisch betätigbares ventil für kraftstoff-einspritzanlagen für brennkraftmaschinen Expired - Lifetime EP0438479B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3834446 1988-10-10
DE3834446A DE3834446A1 (de) 1988-10-10 1988-10-10 Elektromagnetisches einspritzventil in patronenbauweise

Publications (2)

Publication Number Publication Date
EP0438479A1 EP0438479A1 (de) 1991-07-31
EP0438479B1 true EP0438479B1 (de) 1994-02-16

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EP89911706A Expired - Lifetime EP0438479B1 (de) 1988-10-10 1989-10-10 Elektrisch betätigbares ventil für kraftstoff-einspritzanlagen für brennkraftmaschinen

Country Status (5)

Country Link
EP (1) EP0438479B1 (de)
JP (1) JPH04502947A (de)
KR (1) KR960010294B1 (de)
DE (2) DE3834446A1 (de)
WO (1) WO1990004098A1 (de)

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Also Published As

Publication number Publication date
KR960010294B1 (ko) 1996-07-27
JPH04502947A (ja) 1992-05-28
KR900702219A (ko) 1990-12-06
DE68913209D1 (de) 1994-03-24
WO1990004098A1 (en) 1990-04-19
DE68913209T2 (de) 1994-07-14
EP0438479A1 (de) 1991-07-31
DE3834446A1 (de) 1990-04-12

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