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EP2307697B1 - Injecteur de carburant avec induit en deux pièces - Google Patents

Injecteur de carburant avec induit en deux pièces Download PDF

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Publication number
EP2307697B1
EP2307697B1 EP09769057A EP09769057A EP2307697B1 EP 2307697 B1 EP2307697 B1 EP 2307697B1 EP 09769057 A EP09769057 A EP 09769057A EP 09769057 A EP09769057 A EP 09769057A EP 2307697 B1 EP2307697 B1 EP 2307697B1
Authority
EP
European Patent Office
Prior art keywords
armature
fuel injector
valve
control chamber
anchor
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.)
Active
Application number
EP09769057A
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German (de)
English (en)
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EP2307697A1 (fr
Inventor
Andreas Rettich
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
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Filing date
Publication date
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Publication of EP2307697A1 publication Critical patent/EP2307697A1/fr
Application granted granted Critical
Publication of EP2307697B1 publication Critical patent/EP2307697B1/fr
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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
    • 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
    • F02M63/0024—Valves characterised by the valve actuating means electrical, e.g. using solenoid in combination with permanent magnet
    • 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
    • F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift

Definitions

  • both pressure-controlled and stroke-controlled injection systems can be used.
  • fuel injection systems so-called accumulator injection systems are used in the pump-nozzle units, pump-line-nozzle units.
  • high pressure fuel eg, fuel at over 1000 bar
  • common rail injectors make it possible in an advantageous manner to adapt the injection pressure to the load and the speed of the internal combustion engine.
  • the following invention relates in particular to common rail fuel injectors, but is basically also applicable to other types of fuel injectors.
  • an actuator is generally used for opening the fuel injector, that is to say for starting the injection process, and for subsequently closing the fuel injector.
  • an actuator is generally used for opening the fuel injector, that is to say for starting the injection process, and for subsequently closing the fuel injector.
  • magnetic actuators or piezoactuators can be used here, the invention described below starting from the use of magnetic actuators.
  • Hydraulic valves with magnetic actuators in particular a pressure balance of the hydraulic valves is sought.
  • the very small solenoid valve strokes which may for example be about 50% smaller than, for example, the strokes of fuel injectors with comparable ball valves, increase the stability of fuel injectors with pressure balanced hydraulic solenoid valves significantly.
  • a problem with such fuel injectors is the bouncing of the solenoid valve anchor when closing the valve. Due to this bounce, the minimum time interval between switching operations is typically limited to 200 to 250 ⁇ s. This is due in particular to the fact that small changes in the bounce behavior over the runtime can lead to a significant injection quantity drift if the armature closing bounce is not completed when a follow-up injection, for example the second injection, is triggered. In many cases, however, spray intervals, ie distances between individual switching operations of the hydraulic valve, of about 100 microseconds are required.
  • a fuel injector for injecting fuel into the combustion chamber of an internal combustion engine, which at least largely avoids the disadvantages of known fuel injectors described above.
  • the fuel injector can be used in particular for use in accumulator injection systems, in particular in self-igniting internal combustion engines, although other uses are also conceivable.
  • the advantages of pressure balanced hydraulic valves can be maintained.
  • a basic idea of the present invention is that armature closing bouncing can be prevented by decoupling the anchor bolt and the anchor plate. As a result, the advantages of a pressure balanced valve can be further optimized, and in particular very small temporal spray clearances can be realized.
  • the invention can be combined with respect to the production, including assembly with fuel injectors with one-piece anchor, so that for example the fuel injector according to the invention with multi-part anchor can be offered as an option on customer request.
  • the manufacture of the armature is significantly simplified compared to conventional armature.
  • it can be separated by the decoupling of anchor bolt and anchor plate Optimize materials.
  • Different materials can be used for the anchor bolt and the anchor plate.
  • the anchor plate with respect to the magnetic properties and the geometry can be optimally designed, as well as the separately formed anchor bolt can be optimized, for example, optimal closure properties and the lowest possible wear.
  • no consideration must be given to wear on the valve seat with regard to the selection of materials and the geometric design of the anchor plate.
  • both material and geometry can be reduced for minimal wear and optimum sealing properties.
  • eliminates the need for using a spring plate since, for example, setting rings for an elevation can be used as a measure group.
  • the assembly of the proposed fuel injector can be carried out using an armature designed as an assembly.
  • this assembly can comprise an anchor plate, an anchor sleeve, an adjusting ring, in particular a sickle disc.
  • This assembly can be preassembled outside the actual assembly of the fuel injector, for example, and delivered as a ready-preassembled assembly to the assembly of the actual fuel injector.
  • the fuel injector comprises an injection valve member movably mounted in an injector body of the fuel injector for closing or releasing at least one injection opening.
  • the injection valve member may be designed in one or more members.
  • the proposed fuel injector comprises at least one hydraulic valve, which is set up to control a stroke of the injection valve via at least one control chamber.
  • the hydraulic valve can be designed as a pressure-balanced valve, that is, as a valve to which even in the closed state, no high pressure of the fuel, so for example, no rail pressure acts. This can take place, for example, in that the hydraulic valve does not provide a hydraulic surface acting on the fuel in an opening or closing direction of the hydraulic valve, for example, no surface or surface component oriented perpendicularly to the opening of a drainage bore to be closed.
  • the hydraulic valve has at least one magnetic actuator with at least one magnetic coil and at least one magnet armature.
  • the magnet armature in turn comprises at least one armature plate interacting with the magnet actuator and at least one movably mounted relative to the armature plate and controlling a pressure in the control chamber Anchor bolt on.
  • This anchor bolt is preferably designed to release or close at least one outlet throttle of the control chamber, in accordance with the control of the magnetic actuator.
  • An anchor bolt is thus to be understood as a fundamentally arbitrarily shaped closing element, which can be designed, for example, as an elongate closing element with an arbitrary cross-section, for example in the form of a solid bolt. Also, a hollow cross-section may be present, which is explained in more detail below using the example of a preferred sleeve shape.
  • the anchor bolt is mounted within the anchor plate or the anchor plate surrounding, so that the anchor bolt and the anchor plate are displaceable relative to each other in the closing direction.
  • the anchor bolt is mounted relative to the anchor plate such that a movement of the anchor plate in an opening direction against the closing direction, at least from a certain minimum stroke, entrains the anchor bolt, so that the hydraulic valve opens. This can be done for example via appropriate shoulders and / or other entrainment devices on the anchor bolt and / or on the anchor plate.
  • the anchor bolt according to the invention should be sleeve-shaped and thus comprise an anchor sleeve or designed as an anchor sleeve.
  • the anchor sleeve in the axial direction is slidably mounted on the anchor plate, in particular within the anchor plate.
  • the sleeve shape of the anchor bolt in the form of an anchor sleeve is advantageous for the design of a pressure balanced hydraulic valve, according to the above definition, since an anchor sleeve can be used to provide as possible no hydraulic surface against the closing direction of the fuel. All hydraulic forces on the anchor sleeve can then act in the radial direction without affecting a position of the anchor sleeve in the axial direction or exert a hydraulic force on this anchor sleeve.
  • the anchor bolt can be acted upon in particular by means of a valve spring element, for example a helical valve spring, with a force acting in a closing direction of the hydraulic valve first force.
  • the armature plate in turn can be acted upon in particular by means of at least one armature spring element, for example a helical armature spring, with a second force acting counter to the closing direction. In this case, this second force is preferably lower than the first force.
  • an anchor sleeve it is possible to receive a pressure pin for the hydraulic sealing of the interior of the anchor sleeve within the anchor sleeve, on the control chamber side facing the cavity within the anchor sleeve.
  • the interior the anchor sleeve can in particular be designed cylindrical, in particular as a circular cylinder and / or as a polygonal cylinder.
  • the outer diameter of the pressure pin can be adapted to the inner diameter or the inner dimensions of this inner space, so that the pressure pin is mounted, for example, sliding and sealing within the interior of the anchor sleeve.
  • the pressure pin, the anchor sleeve and a valve piece with an outlet throttle of the control chamber can then limit a valve space, wherein hydraulic forces act only on the pressure pin by the high pressure of the fuel within this valve space, but not on the anchor sleeve. In this way, a pressure balance can also be generated.
  • the fuel injector comprises a valve piece, within which at least one outlet throttle of the control chamber is accommodated.
  • an outlet throttle can generally be understood to mean an opening to the control chamber which, when the hydraulic valve is open, limits or controls the outflow of the fuel from the control chamber to a low-pressure drain.
  • valve piece has a, at least in the closed state of the hydraulic valve, projecting into the anchor sleeve approach, in particular a cylindrical approach.
  • This approach can be adapted at least in sections from its cross-section to the inner dimensions of the interior of the anchor sleeve, so at least in sections, for example, in turn, have a circular cross section, a polygonal cross section or the like.
  • the approach of the valve piece can also serve as a guide for the anchor sleeve, preferably a sealing guide is selected.
  • An orifice of the outlet throttle of the control chamber can be accommodated in particular in the approach.
  • This mouth can be arranged, for example, at a remote from the control chamber end of the approach.
  • the at least one orifice may also be received in a peripheral constriction of the neck.
  • the approach may initially comprise a first guide section, then the said constriction with the at least one mouth, and then a further guide section.
  • the at least one guide section can be adapted from its outer diameter preferably to the inner diameter of the interior of the anchor sleeve, so for example, in turn, have said circular and / or polygonal cross-section.
  • a changeable shim in particular a sickle disc
  • Such a shim which can be stored, for example, in different thicknesses, can be used to allow adjustment of the overstroke of the hydraulic valve. Under an overstroke is here after switching off the Magnetaktors, a distance referred to which, after the anchor bolt has reached its seat and thus its closed position, the anchor plate still further moves due to their own inertia.
  • a corresponding overstroke can be provided, in particular an adjustable overstroke.
  • This overstroke stop can also be set up as an exchangeable overstroke stop, for example once again in the form of a replaceable disc or a ring.
  • This overstroke stop can basically be provided between any part of the fuel injector, in particular the injector body, and the anchor plate.
  • the armature plate on its side facing away from the magnetic actuator side a guide extension, for example a cylindrical sleeve-shaped guide extension, wherein the fuel injector has a guide for receiving this guide extension.
  • the at least one overstroke stop can be arranged between this guide and the guide extension.
  • this guide which, for example, part of a valve piece, in which the above-described outlet throttle of the control chamber is added, may be, and the guide extension.
  • the at least one overstroke stop can be arranged.
  • it can be accommodated in the form of a replaceable disk between the guide and the guide extension.
  • FIG. 1 a first embodiment of a fuel injector 110 according to the invention is shown in a sectional view with a cutting direction parallel to a Injektorachse 112 in a partial view.
  • the fuel injector 110 comprises an injector body 114, which in FIG. 1 is shown only slightly.
  • an injection valve member 116 is slidably mounted in the axial direction, of which in the sectional illustration according to FIG FIG. 1 only one valve piston 118 is shown.
  • the injection valve member 116 may be formed one or more members and serves to open or close at least one injection port, which in FIG. 1 not shown.
  • valve piston 118 At its upper end, the valve piston 118 is mounted in a sleeve extension 120 of a valve piece 122, so that a control chamber 124 is formed between the upper side of the valve piston 118 and the valve piece 122.
  • This control chamber can be acted upon by an inlet throttle 126 with high-pressure fuel, so that the pressure in the control chamber 124 controls a position of the valve piston 118 and thus a position of the injection valve member 116.
  • the valve piece 122 furthermore has an at least partially cylindrically configured valve body 128, which is supported on the injector body 114 downwards, that is to say in a closing direction of the injection valve member 116.
  • a conical sealing shoulder 130 and, subsequent to the sealing shoulder 130, a cylindrical projection 132 of the valve body 128 are first received on this valve body 128.
  • a discharge throttle 134 of the control chamber 124 is arranged in the valve piece 122.
  • This outlet throttle 134 starting from the control chamber 124, initially comprises an axial bore 136, followed by two throttle bores 138 running obliquely to the injector axis 112 in this exemplary embodiment.
  • These throttle bores 138 each open into openings 140 which are provided in a peripheral constriction 142 of the attachment 132 , Above the constriction 142, the projection 132 is widened again and has a guide section 144.
  • the outlet throttle 134 can the control chamber 124 with a (in FIG. 1 not shown) connect low-pressure drain, so that a pressure in the control chamber 124 and thus a position of the injection valve member 116 can be controlled by opening or closing the drain throttle 134.
  • a hydraulic valve 146 is provided in the fuel injector 110, which is designed as a solenoid valve.
  • the hydraulic valve 146 includes a magnetic actuator 148 having a solenoid 150 and a magnetic core 152 which are arranged axially symmetrically.
  • Magnetic actuator 154 further comprises a magnetic armature 154.
  • Magnetic armature 154 is acted upon by a force in the closing direction by means of a valve spring 158 mounted in a central cavity 156 of magnetic core 152.
  • the armature 154 is acted upon by an armature spring 160, which is supported on the valve body 128 with a force opposite to the closing direction.
  • the armature 154 is designed in two parts in the illustrated embodiment and includes an anchor plate 162 and an anchor bolt 164th
  • the armature plate 162 At its end facing the magnetic core 152, the armature plate 162 has an armature plate 166 in the form of an axially symmetrical annular disk. In the closing direction, a cylinder sleeve-shaped guide extension 168 adjoins this anchor plate 166.
  • the armature plate 162 cooperates with the magnetic coil 150 and can accordingly be made of a material optimized for magnetic actuation.
  • the anchor bolt 164 is slidably mounted in this embodiment.
  • This anchor bolt 164 has an anchor sleeve 170 in the illustrated embodiment.
  • This anchor sleeve 170 comprises a cylindrical inner space 172, in which the guide portion 144 of the projection 132 is slidably and sealingly mounted.
  • the anchor sleeve 170 has a sealing edge 174, which in the in FIG. 1 illustrated closed state of the hydraulic valve 146 is seated on the sealing shoulder 130 of the valve member 122 and forms a sealing seat.
  • the outlet throttle 134 is closed, so that in the control chamber 124 high pressure is applied and the injection valve member 116 in its in FIG. 1 Not shown valve seat is pressed and closes the at least one injection port.
  • hydraulic valve 146 configured as a pressure-balanced valve, as can act on the hydraulic valve 146, in particular the anchor bolt 164, in the axial direction no hydraulic forces.
  • the pressure, which is out the control chamber 124 transmits via the outlet throttle 134 in the constriction 142 can act only in the radial direction on the inner walls of the anchor sleeve 170.
  • the magnetic core 152 facing end of the anchor bolt 164 has a shim 176 which is inserted into a circumferential groove of the anchor sleeve 170.
  • This shim 176 is configured in the illustrated embodiment, for example, as a sickle plate 178, such as from a top view of the armature 154 in FIG. 2 evident.
  • the residual air gap disk 184 is not shown in this figure.
  • the anchor sleeve 170 has at its lower end, as in FIG. 1 can be seen, a shoulder 180, which limits the movement of the armature plate 162 down and which thus acts as an overstroke stop 182.
  • the armature sleeve 170 can first be inserted from below into the guide extension 168, whereupon the sickle disk 178 can be pushed into the groove in the armature sleeve 170 at the upper end.
  • the valve spring 158 is supported in the illustrated embodiment on the sickle plate 178, but may alternatively be supported on other parts of the anchor bolt 164, for example, the anchor sleeve 170.
  • the armature spring 160 is supported at its upper end on the armature plate 166.
  • the sliding support of the anchor sleeve 170 in the anchor plate 162 allows for relative movement between the anchor plate 162 and the anchor bolt 164, which is bounded upwardly by the sickle disc 178 and down through the shoulder 180.
  • a residual air gap disk 184 may be provided in the form of one or more annular disks, which may set a gap between the magnetic core 152 and the magnet armature 154.
  • the residual air gap between the magnetic core 152 and the magnet armature 154 may also be designed as an air gap.
  • a stop for the anchor bolt 164 or the anchor sleeve 170 of the anchor bolt 164 also take place in a different form than by the use of a disc.
  • the solenoid actuator 148 is turned off or the magnetic force is reduced, so that, driven by the valve spring 158, the anchor bolt 164 is pressed back into its seat and again in the control chamber 124 can build up a high pressure.
  • the injection valve member 116 then closes again.
  • the residual air gap disc 184 may preferably be clamped under the sickle disc 178 so that the residual air disc 184 may be held in a defined position by the sickle disc 178.
  • the anchor plate 162 is held between the injections by means of the armature spring 160 in a defined position or brought into such a defined position.
  • the spring force of the armature spring 160 should be chosen as small as possible, preferably at a maximum of 3 to 4 Newtons.
  • the armature plate 162 will continue to move downwardly due to its inertia , This way is also referred to as overstroke and is in FIG. 1 denoted by a.
  • Other sizes x (thickness of the sickle plate 178), z (axial length of the anchor plate 162) and y (distance between the upper edge of the sickle plate 178 and the underside of the anchor plate 162) are also in FIG. 1 Are defined.
  • the overstroke a is limited by the overstroke stop 182, which in this case is formed by the shoulder 180 at the top of a collar 186 of the anchor sleeve 170.
  • the excess stroke a should preferably not be greater than 10 microns. If, in individual cases, the tolerances of the individual parts of the dimensions relevant to the overstroke are greater than the overtravel tolerance requires, it is possible to set the overstroke a via an adjusting ring (measuring groups). In this case, the dimensions marked y and z in FIG. 1 are measured and then a corresponding dial 176 (dimension x in FIG. 1 ) to be selected.
  • FIG. 3 a second embodiment of a fuel injector 110 according to the invention is shown.
  • the fuel injector 110 comprises an injector body 114, in which an injection valve member 116 is mounted with a valve piston 118.
  • a control chamber 124 is formed in a valve piece 122, which can be acted upon by an inlet throttle 126 with high pressure.
  • the control chamber 124 is again pressure relieved, the Outflow throttle 134 in the in FIG. 3 illustrated embodiment, in contrast to the embodiment according to FIG. 1 , only an axial bore 136 includes.
  • This axial bore 136 opens into the interior of a cylindrical sleeve-shaped guide 188 of the valve piece 122 and can be closed or released by the hydraulic valve 146.
  • the hydraulic valve 146 is basically similar to that in FIG FIG. 1 shown hydraulic valve 146 shown. It is in the illustration according to FIG. 3 the magnetic actuator 148 is shown only partially, with only part of the magnetic core 152 being depicted.
  • the magnetic coil 150 which, for example, analogous to FIG. 1 can be designed, is in FIG. 1 Not shown.
  • the magnetic actuator 148 in the embodiment of FIG. 3 a magnet armature 154 with an anchor plate 162 and an anchor bolt 164.
  • the anchor plate 162 is again configured with an anchor plate 166 and a guide extension 168.
  • the guide extension 168 has at its lower end a constriction 190, which is cylindrical and corresponds to the inner diameter of the guide 188 from its outer diameter forth. The guide extension 168 is thus guided in the guide 188 of the valve piece 122.
  • the anchor sleeve 170 is in turn designed tubular and has at its lower end a seat edge 192, for example, a biting edge, a flat seat or a conical seat, which in the in FIG. 3 shown closed state on a sealing seat 194 in the interior of the guide 188 of the valve seat 122 is seated and a mouth 140 of the outlet throttle 134 seals.
  • a cylindrical pressure pin 196 added inside the tubular anchor sleeve 170 is in the in FIG. 1 illustrated embodiment.
  • This cylindrical pressure pin is supported at its upper end on the magnetic core 152 or another part of the magnetic actuator 148. From its outer diameter, the pressure pin 196 corresponds to the inner diameter of the tubular anchor sleeve 170, so that the anchor sleeve 170 is slidably mounted on this pressure pin 196, the pressure pin 196, however, ensures a pressure-tight seal of the control chamber 124. Due to the hydraulic pressure in the control chamber 124, which transmits through the outlet throttle 134 on the pressure pin 196, this pressure pin 196 is pressed up against the magnetic core 152.
  • this covenant can turn be configured as a dial 176 or a sickle disc 178 and, for example, in turn, be positively connected to the anchor sleeve 170.
  • the collar can also be configured in other ways, for example as part of the anchor sleeve 170 itself. Under the sickle plate 178, in turn, a residual air gap disc 184 can be arranged.
  • the hydraulic valve 146 used is a pressure compensated valve because no hydraulic forces are acting on the armature 154 in the axial direction.
  • the magnetic actuator 148 is energized, the armature plate 162 is attracted by the magnetic coil 150 and moved upward. Due to the collar in the form of the sickle plate 178 on the anchor bolt 164 and the anchor bolt 164 is pulled by the anchor plate 162 with up. The entrapment of the residual air gap disc 184 again serves to hold it in a defined position.
  • the anchor plate 162 is guided in the described upward movement by the guide 188 on the guide extension 168.
  • the anchor plate 162 is positioned in a defined position.
  • the spring force of the armature spring 160 should be as small as possible, for example, again at a maximum of 3 to 4 Newtons.
  • the solenoid actuator 148 can be switched off or switched to a lower current.
  • the valve spring 158 pushes the anchor bolt 164 back into its seat. Once the anchor bolt has reached the seat, the mouth 140 is closed, and the control chamber 124 is again acted upon by the inlet throttle 126 with high pressure, so that the injection valve member 116 back down moves and closes the at least one injection port.
  • This overstroke a is limited by an overstroke stop 182.
  • This overstroke stop 182 is formed by the upper edge of the guide 188 in the illustrated embodiment.
  • a replaceable overstroke stop 182 may be provided in the form of an adjusting ring 200, as shown in FIG FIG. 3 is indicated.
  • This adjusting ring 200 may in particular be configured as a replaceable adjusting ring, so that the overstroke stop 182 may be configured as a replaceable overstroke stop 182.
  • the overstroke stop 182 is conceivable, for example in that the shoulder 180 is not formed on the guide extension 168 of the anchor plate 162, but for example on the guide 188.
  • Other types of overstroke stop or combinations of such overstroke stops are conceivable.
  • the excess lift a should preferably again be no greater than 10 microns.
  • the minimum overtravel a is limited by the maximum wear or the resulting anchor stroke drift in the valve seat.
  • the wear or the Ankerhubdrift is less than 4 microns, so that the lower limit of the excess stroke a can be about 5 microns.
  • the tolerances of the individual parts of the dimensions relevant to the overstroke a should in each case be greater than necessary in each case, so it is again possible to adjust the overstroke a via an additional adjusting ring, such as, for example, the adjusting ring 182, 200. In this case, before the assembly would have to turn into the FIG. 3 Measured with y and z dimensions are measured so that the adjustment ring 200 can be selected with the dimension x accordingly.

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

Abstract

L'invention concerne un injecteur de carburant (110), destiné à injecter du carburant dans la chambre de combustion d'un moteur à combustion interne, en particulier pour l'utilisation dans des systèmes d'injection à accumulateur. L'injecteur de carburant (110) comprend au moins un organe de vanne d'injection (116) monté mobile dans le corps d'injecteur (114) de l'injecteur de carburant (110) et destiné à obturer ou libérer au moins une ouverture d'injection. Par ailleurs, l'injecteur de carburant (110) comprend au moins une vanne hydraulique (146). La vanne hydraulique (146) est conçue pour commander une course de l'organe de vanne d'injection (116) via au moins une chambre de commande (124). La vanne hydraulique (146) possède un actionneur magnétique (148) avec au moins une bobine (150) et au moins un induit (154). L'induit (154) possède au moins une plaque d'induit (162) coopérant avec l'actionneur magnétique (148) et au moins un goujon d'induit (164) monté mobile par rapport à la plaque d'induit (162) et commandant une pression dans la chambre de commande (124).

Claims (11)

  1. Injecteur de carburant (110) pour l'injection de carburant dans la chambre de combustion d'un moteur à combustion interne, en particulier pour l'utilisation dans des système d'injection à accumulateur, comprenant au moins un organe de soupape d'injection (116) monté mobile dans un corps d'injecteur (114) de l'injecteur de carburant (110), pour fermer ou ouvrir au moins une ouverture d'injection, comprenant en outre au moins une soupape hydraulique (146), la soupape hydraulique (146) étant prévue pour commander par le biais d'au moins un espace de commande (124) une course de l'organe de soupape d'injection (116), la soupape hydraulique (146) comprenant un actionneur magnétique (148) avec au moins une bobine magnétique (150) et au moins une armature magnétique (154), l'armature magnétique (154) comprenant au moins une plaque d'armature (162) coopérant avec l'actionneur magnétique (148) et au moins un boulon d'armature (164) monté mobile par rapport à la plaque d'armature (162) et commandant une pression dans l'espace de commande (124), caractérisé en ce que le boulon d'armature (164) est réalisé sous forme de douille d'armature (170) et en ce que la douille d'armature (170) est montée sur la plaque d'armature (162) de manière à pouvoir coulisser dans la direction axiale.
  2. Injecteur de carburant (110) selon la revendication 1, dans lequel le boulon d'armature (164) est sollicité au moyen d'un élément de ressort de soupape (158) avec une première force agissant dans la direction de fermeture, la plaque d'armature (162) étant sollicitée au moyen d'un élément de ressort d'armature (160) avec une deuxième force agissant dans le sens inverse de la direction de fermeture, la deuxième force étant inférieure à la première force.
  3. Injecteur de carburant (110) selon la revendication 1, dans lequel une goupille de pression (196) montée coulissante dans la douille d'armature (170) est reçue sur le côté opposé à l'espace de commande (124) en vue de réaliser l'étanchéité de la douille d'armature (170).
  4. Injecteur de carburant (110) selon la revendication 1, comprenant en outre un organe de soupape (122), l'organe de soupape (122) comprenant un étranglement de sortie (134) de l'espace de commande (124), l'organe de soupape (122) présentant un insert (132) saillant à l'intérieur de la douille d'armature (170), en particulier un insert (132) au moins en partie cylindrique.
  5. Injecteur de carburant (110) selon la revendication 4, dans lequel une embouchure (140) de l'étranglement de sortie (134) est reçue dans l'insert (132).
  6. Injecteur de carburant (110) selon l'une quelconque des revendications 4 ou 5, dans lequel l'embouchure (140) est reçue dans un rétrécissement (142) du côté périphérique de l'insert (132).
  7. Injecteur de carburant (110) selon l'une quelconque des revendications 4, 5 ou 6, dans lequel l'insert (132) comprend sur le côté du rétrécissement (142) opposé à l'espace de commande (124) une portion de guidage (144), le diamètre extérieur de la portion de guidage (144) étant adapté au diamètre intérieur de la douille d'armature (170).
  8. Injecteur de carburant (110) selon la revendication 1, dans lequel le boulon d'armature (164) est entouré au niveau d'un côté opposé à l'espace de commande (124) au moins en partie par un disque d'ajustement (176) interchangeable, en particulier un disque en croissant (178), afin de permettre un ajustement d'une surcourse de la soupape hydraulique (146).
  9. Injecteur de carburant (110) selon l'une quelconque des revendications précédentes, dans lequel une butée de surcourse (182), en particulier une butée de surcourse interchangeable (182), est prévue sur le côté de la plaque d'armature (162) opposé à l'actionneur magnétique (148), pour limiter une surcourse de la soupape hydraulique (146).
  10. Injecteur de carburant (110) selon la revendication précédente, dans lequel la plaque d'armature (162) présente sur son côté opposé à l'actionneur magnétique (148) une saillie de guidage (168), l'injecteur de carburant (110) présentant un guidage (188) pour recevoir la saillie de guidage (168), l'au moins une butée de surcourse (182) étant disposée entre le guidage (188) et la saillie de guidage (168).
  11. Injecteur de carburant (110) selon la revendication précédente, dans lequel le guidage (188) est réalisé sous forme de partie d'un organe de soupape (122), l'organe de soupape (122) comprenant au moins un étranglement de sortie (134) de l'espace de commande (124).
EP09769057A 2008-06-27 2009-04-27 Injecteur de carburant avec induit en deux pièces Active EP2307697B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200810002717 DE102008002717A1 (de) 2008-06-27 2008-06-27 Kraftstoffinjektor mit zweiteiligem Magnetanker
PCT/EP2009/055019 WO2009156208A1 (fr) 2008-06-27 2009-04-27 Injecteur de carburant avec induit en deux pièces

Publications (2)

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EP2307697A1 EP2307697A1 (fr) 2011-04-13
EP2307697B1 true EP2307697B1 (fr) 2012-06-20

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CN (1) CN102076950A (fr)
DE (1) DE102008002717A1 (fr)
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WO (1) WO2009156208A1 (fr)

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DE102010030393A1 (de) 2010-06-23 2011-12-29 Robert Bosch Gmbh Ankerelement sowie Einspritzventil mit einem solchen Ankerelement
DE102014225323A1 (de) * 2014-12-09 2016-06-09 Robert Bosch Gmbh Schalt- oder Druckregelventil für ein Karftstoffeinspritzsystem
DE102015213141A1 (de) * 2015-07-14 2017-01-19 Robert Bosch Gmbh Schaltventil für einen Kraftstoffinjektor sowie Kraftstoffinjektor
CN106050499B (zh) * 2016-05-31 2017-05-24 清华大学 控制阀自锁紧的电控高压喷油器
CN106014740B (zh) * 2016-07-25 2018-12-11 成都威特电喷有限责任公司 消除阀杆轴向力的控制阀
DE102016219881B3 (de) 2016-10-12 2017-11-23 Continental Automotive Gmbh Betreiben eines Kraftstoffinjektors mit hydraulischem Anschlag
CN106837640B (zh) * 2017-01-25 2019-04-26 中国第一汽车股份有限公司 针阀运动速度可控的共轨喷油器
CN110573261B (zh) * 2017-04-10 2022-06-21 天幸星科技有限公司 燃料雾化器和用于雾化燃料的方法
JP2023037746A (ja) * 2021-09-06 2023-03-16 ロベルト・ボッシュ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 燃料噴射装置

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RU2029129C1 (ru) * 1989-05-10 1995-02-20 Семенов Владимир Григорьевич Управляемая форсунка для двигателя внутреннего сгорания
IT239878Y1 (it) * 1996-12-23 2001-03-13 Elasis Sistema Ricerca Fiat Perfezionamenti ad una valvola di dosaggio a comando elettromagneticoper un iniettore di combustibile.
RU2136949C1 (ru) * 1998-02-16 1999-09-10 Коростышевский Исаак Матвеевич Электромагнитная топливная форсунка
DE19816315A1 (de) * 1998-04-11 1999-10-14 Bosch Gmbh Robert Brennstoffeinspritzventil
DE102004050992A1 (de) * 2004-10-20 2006-04-27 Robert Bosch Gmbh Magnetventilbetätigter Kraftstoffinjektor mit hydraulischem Überhubanschlag
DE102006050042A1 (de) * 2006-10-24 2008-04-30 Robert Bosch Gmbh Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen
DE102006057935A1 (de) * 2006-12-08 2008-06-12 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen

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RU2011102820A (ru) 2012-08-10
CN102076950A (zh) 2011-05-25
WO2009156208A1 (fr) 2009-12-30
RU2517518C2 (ru) 2014-05-27
DE102008002717A1 (de) 2010-01-14
EP2307697A1 (fr) 2011-04-13

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