EP3008327B1 - Mengenbegrenzungsventil - Google Patents

Mengenbegrenzungsventil Download PDF

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Publication number
EP3008327B1
EP3008327B1 EP14729857.4A EP14729857A EP3008327B1 EP 3008327 B1 EP3008327 B1 EP 3008327B1 EP 14729857 A EP14729857 A EP 14729857A EP 3008327 B1 EP3008327 B1 EP 3008327B1
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EP
European Patent Office
Prior art keywords
piston
stop
limiting valve
face
extending
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
EP14729857.4A
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German (de)
English (en)
French (fr)
Other versions
EP3008327A1 (de
Inventor
Robby Gerbeth
Michael Walder
Andreas Mehr
Markus Staudt
Frank MLICKI
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.)
Rolls Royce Solutions GmbH
Original Assignee
MTU Friedrichshafen GmbH
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Filing date
Publication date
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Publication of EP3008327A1 publication Critical patent/EP3008327A1/de
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Publication of EP3008327B1 publication Critical patent/EP3008327B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—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
    • F02M61/042—The valves being provided 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
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0205—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine
    • F02M63/0215—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively for cutting-out pumps or injectors in case of abnormal operation of the engine or the injection apparatus, e.g. over-speed, break-down of fuel pumps or injectors ; for cutting-out pumps for stopping the engine by draining or closing fuel conduits
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the invention relates to a quantity limiting valve for an injection system of an internal combustion engine according to the preamble of claim 1.
  • a quantity limiting valve is provided in a line connection between a high-pressure source and an injector in order to limit an amount of fuel that can be supplied to the injector during an opening cycle and thus be injected into a combustion chamber of the internal combustion engine. In this way, damage to the internal combustion engine can be prevented by an excessive amount of injected fuel, for example, when the injector has a defect, so that it no longer or no longer completely closes.
  • a quantity limiting valve usually has an inflow region and an outflow region. It also comprises a piston which is displaceably guided in a cylinder.
  • the inflow region is separated from the outflow region, wherein a fluid connection exists between the inflow region and the outflow region via an overflow channel passing through the piston in regions and a flow path arranged between a peripheral surface of the piston and an inner surface of the cylinder.
  • the piston is biased in a first functional position with an end face against a stop surface of a stop element.
  • the quantity limiting valve is - as seen in the flow direction - arranged between the high pressure source and the injector or integrated upstream of an actual injection device in the injector. As long as the injector is closed, wherein a fluid connection to a combustion chamber assigned to the injector is blocked, the quantity limiting valve is arranged in its first functional position.
  • the inflow region is fluidically separated from the outflow region or at least from an outflow region of the injector from which fuel flows into the combustion chamber. It can then no longer get fuel from the inflow into the outflow. This therefore runs in the combustion chamber empty, which at the same time maximizes the pressure difference across the piston to the inflow region.
  • the piston is therefore permanently urged by the pressure prevailing in the inflow region pressure against the sealing surface, so that no fuel can get into the combustion chamber.
  • the internal combustion engine is effectively protected from being damaged by an excessive amount of fuel.
  • a disadvantage of a known quantity limiting valve is that the piston is delayed at the beginning of an injection with respect to the start of injection and abruptly released from its seat in the first functional position.
  • the sudden release of the piston leads to a pressure waveform superimposed opening shaft, namely a temporally local pressure increase, which leads to a mis-evaluation of the pressure curve and thus to a faulty determination the injection begins.
  • the course of the opening wave typically changes over the life of the quantity limiting valve. Accordingly, erroneous evaluations of the pressure signal detected in the single memory are unavoidable.
  • a mass flow control valve for an injection system of an internal combustion engine in which in addition to the previous description in a contact area of the end face with the abutment surface in the first functional position, an underflow structure is formed, which comprises at least one intermediate space between the piston and the stop element, which with the inflow region is in fluid communication.
  • the invention has for its object to provide a flow control valve, which does not have the disadvantages mentioned.
  • a flow control valve which does not have the disadvantages mentioned.
  • the flow control valve a delayed and sudden release of the piston from its seat in the first functional position and thus the formation of an opening shaft to be avoided.
  • the possibility should be created of evaluating a pressure signal in a single memory, which is assigned to an injector, error-free and reproducible, wherein in particular an injection start can be reliably detected.
  • a flow control valve is provided with the features of claim 1.
  • the underflow structure comprises at least one projection extending toward the abutment surface, which projection has the end surface at least in regions, and / or at least one recess extending into the end surface.
  • the at least one intermediate space is preferably in fluid communication with the fluid connection, in particular with the flow path arranged between the peripheral surface of the piston and the inner surface of the cylinder, so that a small amount of fuel is already introduced from the inflow region into the opening immediately after the injector is opened Outflow region can flow, or an additional fluid path is opened from the inflow region to the outflow region via the piston.
  • a pressure profile which is preferably detected in a single memory of the injector, has no disturbance due to the response of the quantity limiting valve. He is thus easily error-free and reproducible evaluated. There is no variable lifetime response of the flow control valve.
  • the underflow structure comprises more than one projection, wherein on each projection a portion of the end surface is arranged.
  • the piston with the at least one projection is biased against the abutment surface, wherein the at least one projection adjacent, in particular - seen in the circumferential direction - between the projections, the at least one gap is formed in the fuel in the first functional position comes out of the inflow area.
  • the underflow structure comprises at least one recess extending into the end face.
  • the underflow structure has more than one recess.
  • the at least one intermediate space is formed by the recess, wherein in the first functional position fuel from the inflow region passes into the recess.
  • a quantity limiting valve is also preferred, which is characterized in that the underflow structure comprises at least one projection which extends to the end face and which has the stop face at least in regions.
  • the underflow structure is at least not exclusively provided on the piston, but also or possibly completely on the stop element, namely in the form of at least a projection on which the abutment surface is arranged at least partially.
  • more than one protrusion is provided on the abutment member, each protrusion having a portion of the abutment surface.
  • the at least one intermediate space is adjacent to the at least one projection and particularly preferably-seen in the circumferential direction-between the projections.
  • the underflow structure preferably comprises at least one recess extending into the abutment surface.
  • the at least one intermediate space is formed in this case by the at least one recess.
  • the underflow structure comprises at least one projection and / or at least one recess in the region of the piston, as well as at least one projection and / or at least one recess in the region of the stop element.
  • the stop element is designed as a stop sleeve, which engages partially in the cylinder.
  • the stop sleeve with a collar which runs along an outer circumference of the same, on a wall of the cylinder - seen in the axial direction - on.
  • the stop element is therefore preferably designed as a separate, separate from the cylinder component, which is advantageous in terms of easy processing of the stop surface.
  • the stop sleeve preferably protrudes into the cylinder, so that the contact area of the end face is arranged with the abutment surface in an interior of the cylinder. This ensures that the piston is guided safely in the cylinder at all times.
  • a mass limiting valve is also preferred, which is characterized in that the piston has at least one projection extending in the direction of the stop surface, on which the end face is arranged.
  • the piston has three such projections.
  • the piston preferably has at least one recess, preferably three recesses, which are provided in the end face or are introduced into the end face / are. The choice of three projections and / or three recesses results in a particularly position-stable contact between the piston on the one hand and the stop element on the other.
  • the stop sleeve at least one extending in the direction of the end face of the piston projection having the abutment surface, preferably three such projections, which together have the abutment surface, and / or at least one recess, preferably three recesses in the Has stop surface. This configuration also results in a particularly stable installation in the contact area.
  • the three projections are arranged symmetrically about a longitudinal axis of the quantity limiting valve, wherein they particularly preferably have an angular distance of 120 ° to each other.
  • the three recesses are preferably arranged symmetrically about the longitudinal axis of the flow control valve, wherein they particularly preferably have an angular distance of 120 ° to each other.
  • the piston and / or the stop element comprises / comprises less than three or more than three projections and / or recesses, these are preferably symmetrical, in particular at equal angular intervals, arranged around the longitudinal axis of the quantity limiting valve.
  • a longitudinal axis of the flow restrictor valve an axis extending in the direction is addressed, in which the piston displaced upon actuation of the flow control valve.
  • the corresponding longitudinal direction also corresponds to the flow direction of the fuel from the inflow region into the outflow region.
  • a circumferential direction is a direction concentrically surrounding the longitudinal direction.
  • a radial direction is a direction perpendicular to the longitudinal direction.
  • a flow control valve which is characterized in that at least one recess is formed as extending in the radial direction groove.
  • Such a groove is particularly easy to manufacture and has aerodynamic advantages.
  • a flow control valve which is characterized in that the stop sleeve has a - extending in the longitudinal direction - through hole, which forms at least partially the inflow region.
  • the through-bore is therefore preferably at least part of a fuel reservoir or serves to pass fuel to the injector.
  • it is preferably part of the high pressure line extending from the high pressure source to the injector.
  • a quantity limiting valve is preferred, which is characterized in that the at least one groove is in fluid communication with the inflow region on the one hand and with the flow path between the peripheral surface of the piston and the inner surface of the cylinder on the other hand.
  • the at least one groove forms not only a gap of the underflow structure, but at the same time a fluid path, via which fuel from the inflow region via the groove and the flow path in immediately upon opening of the injector can flow the outflow area.
  • the at least one groove contributes significantly to the fact that the piston is neither late nor abruptly released from its seat in the first functional position, but rather a gentle, continuous opening behavior of the flow control valve is realized, which in particular does not interfere with a pressure measurement in the range affects the injector associated with individual memory.
  • a gap arranged between two projections can also be regarded as a groove in the sense explained here, wherein the intermediate space preferably extends in the radial direction.
  • the gap is preferably in fluid communication with the inflow region on the one hand and with the flow path on the other hand, resulting in the same advantages that have been explained in connection with the groove.
  • the quantity limiting valve is preferably used in an injection system for an internal combustion engine, which has a common high-pressure accumulator, namely a so-called common rail, and which is accordingly designed as a common-rail injection system.
  • individual injectors of the internal combustion engine are in fluid communication with the common high-pressure accumulator.
  • the quantity limiting valve is used in conjunction with an injector which has an individual buffer as an additional buffer volume.
  • the quantity limiting valve is preferably integrated in the injector and particularly preferably arranged downstream of the individual accumulator, so that during an injection fuel flows from the individual accumulator into the inflow region.
  • the quantity limiting valve can be used for any fuels that can be injected by means of an injector in a combustion chamber of an internal combustion engine or by way of a single-point injection in a common intake manifold or in the way of a multi-point injection in individual combustion chambers associated intake manifold of the internal combustion engine.
  • Fluid fuels of the type relevant here include both liquid and gaseous fuels.
  • the quantity limiting valve is suitable for injecting gasoline, diesel, heavy oil, methanol, ethanol or higher alcohols, as well as methane-containing gases, in particular natural gas, lean gas or special gas, as well as any other suitable liquid or gaseous fuel.
  • Hydrogen or synthesis gas namely a mixture of hydrogen and carbon monoxide, can also be injected by means of the quantity limiting valve.
  • the quantity limiting valve is particularly preferably used in conjunction with liquid fuels under normal conditions.
  • An internal combustion engine in which the quantity limiting valve is used, is preferably designed as a reciprocating piston engine and can serve the propulsion of land, water or air vehicles.
  • these are heavy agricultural machinery, mining vehicles or large construction machinery.
  • motor vehicles serving the defense, such as tanks to be driven by the internal combustion engine.
  • the use of the internal combustion engine for driving trains, for example in railcars or locomotives, is possible.
  • a corresponding internal combustion engine to drive a ship.
  • Stationary applications in particular for energy generation, for example in a block heating power value, are possible.
  • the internal combustion engine can be used in particular as an emergency generator, for continuous load operation or peak load operation.
  • the internal combustion engine stationary auxiliary or auxiliary units drives, such as fire pumps on an oil rig.
  • Fig. 1 shows a schematic representation of an embodiment of a quantity limiting valve 1 in longitudinal section.
  • the quantity limiting valve 1 is integrated here in an injector 3, wherein the injector 3 has a single memory 5.
  • the injector 3 is part of an injection system 6 of an internal combustion engine 8, wherein the injection system 6 has a common high-pressure accumulator.
  • the single memory 5 serves as an additional buffer volume.
  • the quantity limiting valve 1 has an inflow region 7 and an outflow region 9.
  • a cylinder 11 is a piston 13 - in the axial direction or in the longitudinal direction, namely in FIG. 1 guided in a displaceable manner in the vertical direction, the inflow region 7 being separated from the outflow region 9 by the piston.
  • the inflow region 7 there is a fluid connection between the inflow region 7 and the outflow region 9.
  • This comprises an overflow channel 15, which passes through the piston 13 at least in regions, and which extends diagonally in the illustrated embodiment.
  • the overflow channel 15 opens on the one hand into the inflow region 7 and on the other hand into a flow path 17 which is arranged between a circumferential surface 19 of the piston 13 and an inner surface 21 of the cylinder 11.
  • FIG. 1 the piston 13 is shown in its first functional position in which it bears with an end face 25 on a stop surface 27 of a stop element 29 under prestress.
  • the piston 13 is urged in the illustrated embodiment by a spring 31 under bias against the stop element 29.
  • the piston 13 remains in its first functional position as long as the injector 3 is closed. If the injector 3 is opened, fuel flows from the outflow region 9 through an outflow region 33 to an actual injection device, for example one Injection needle, the injector 3 down from. As a result, the pressure in the outflow region 9 falls. As long as the piston 13 is in the first functional position, only fuel from the inflow region 7 via the overflow 15 and on via the flow path 17, which - seen in the flow direction - connects to the overflow channel 15 , flow into the discharge area 9. Due to the resulting pressure difference between the inflow region 7 and the outflow region 9, a force acting on the piston 13, which finally exceeds the biasing force caused by the spring 31.
  • the piston 13 is then in the longitudinal direction of the outflow region 9 or in this in - in FIG. 1 down - relocated.
  • additional fuel can flow directly into the flow path 17, resulting in two fluid paths between the inflow region 7 and the outflow region 9, namely a fluid path in which the overflow channel 15 upstream of the Flow path 17 is provided, and another, in which the fuel flows directly from the inflow region 7 in the flow path 17.
  • the flow cross sections of these flow paths are dimensioned such that more and more fuel flows out of the outflow region 9 via the outflow region 33 than can flow in from the inflow region 7 via the fluid paths.
  • the pressure difference between the inflow region 7 and the outflow region 9 is thus retained, and the piston 13 continues to move into the outflow region 9, as seen in the longitudinal direction, as long as the injection continues.
  • the pressure difference initially remains, and fuel continues to flow via the fluid paths from the inflow region 7 into the outflow region 9, wherein, however, the pressure difference now continuously compensates because no more fuel flows out of the outflow region 9 via the outflow region 33 flows. Finally, the pressure difference reaches a limit, from which the biasing force exerted by the spring 31 on the piston 13 is greater than the force caused by the pressure difference, opposing force, so that the piston 13 reverses and moves back toward the stop member 29. Finally, it reaches - preferably before the next injection event - again its first functional position.
  • the injector 3 is defective, so that fuel permanently escapes from it, the pressure difference remains above the piston 13, so that it displaces as far as a sealing surface 35 at which it exits finally sealingly abuts with an axial end surface 37.
  • the piston 13 is then arranged in a second functional position.
  • the inflow region 7 is fluidically separated from the outflow region 9 downstream of the piston 13 or from the outflow region 33 upstream of the piston 13, so that no more fuel can flow from the inflow region 7 into the outflow region 9 or into the outflow region 33.
  • the outflow area 9 and the outflow area 33 are empty, whereby the pressure difference to the inflow area 7 is maximized.
  • the piston is thus permanently urged against the bias of the spring 31 in its second functional position and held in this. It can no longer flow fuel through the injector 3 in the combustion chamber, so that the internal combustion engine is effectively protected from damage due to excessive fuel supply.
  • the problem is that the piston of such a constructed, conventional flow control valve at an opening of the injector, thus at the start of injection, delays and abruptly from its first functional position. This creates a so-called opening wave, namely a temporally local pressure increase in a detected in the region of the individual memory 5 pressure signal.
  • an underflow structure 39 is formed here, wherein at least one intermediate space 41 between the piston 13 and the stop element 29 is arranged.
  • the intermediate space 41 is in fluid communication with the inflow region 7.
  • fuel flows from the inflow region 7 into the intermediate space 41 and thus flows under the contact area between the end face 25 and the abutment surface 27, so that a larger surface area of the piston 13 is acted upon by the high pressure in the inflow region 7 , as is the case with a conventional flow control valve. Therefore, the piston 13 moves at the start of injection more quickly, thus not late, out of its first functional position.
  • a fluid connection to the flow path 17 is opened via the intermediate space 41, in particular because the projections 23 do not extend along the entire circumference of the piston 13.
  • fuel can also flow into the flow path 17 via the intermediate space 41 directly at the start of the injection. This results in a further fluid path, whereby the response of the flow control valve 1 is positively influenced, and wherein the piston 13th in particular no longer abruptly, but rather gently and continuously releases from its first functional position.
  • the underflow structure 39 is disposed completely on the stop element 29, wherein in particular projections 43 are provided, which extend in the direction of the end face 25, and on which partially the abutment surface 27 is arranged. Between the projections 43, of which in FIG. 1 only one is shown, the spaces 41 are formed, of which in FIG. 1 also only one is shown. Alternatively, it is possible that in the stop surface 27 recesses, in particular grooves are introduced, which act as gaps 41.
  • Fig. 2A shows a schematic view of the stop element 29 according to FIG. 1 from underneath.
  • the projections 43 can be seen, wherein the stop element 29, which is designed here as a stop sleeve 48, three projections 43 which - seen in the circumferential direction - are arranged symmetrically and in particular at an angular distance of 120 ° to each other. Between the projections 43 - seen in the circumferential direction - the gaps 41 are arranged.
  • the interstices 41 to interpret as recesses 44, which are provided in the abutment surface 27. It also appears that the abutment surface 27 is arranged on the projections 43 and is interrupted by the recesses 44 or the intermediate spaces 41.
  • the stop element 29 has a through hole 45 extending in the longitudinal direction, which is also in FIG. 1 is shown.
  • the through-bore 45 forms the inflow region 7 in regions.
  • Fig. 2B shows a schematic side view of the embodiment of a stop element 29 according to FIG. 2A , Identical and functionally identical elements are provided with the same reference numerals, so that reference is made to the preceding description.
  • the stop element 29 preferably has a circumferential collar 47 extending along an outer circumference 47, which is also in FIG. 1 is shown. This shows in FIG. 1 in that the stop sleeve 48 or the stop element 29 rests with the collar 49 on a wall 51 of the cylinder 11.
  • the effective flow cross-section of the fluid connection between the inflow region 7 and the outflow region 9 via the piston 13 is smaller than the flow cross-section downstream of the outflow region 9. Accordingly, the projections 43 have a small height h. This is preferably from at least a few tenths mm to a maximum of 2 mm, more preferably a few tenths mm, more preferably five tenths mm.
  • FIG. 3 shows a schematic, three-dimensional representation of a second embodiment of a flow control valve 1.
  • the same and functionally identical elements are provided with the same reference numerals, so reference is made in this respect to the preceding description.
  • the representation according to FIG. 3 corresponds to a schematic exploded view, with only selected parts of the flow limiting valve 1 are shown.
  • stop member 29 is shown with the collar 49.
  • FIG. 3 In the lower area of FIG. 3 the cylinder 11 with the displaceably guided therein piston 13 are shown. It turns out that the peripheral surface 19 of the piston 13 is not tight against the inner surface 21 everywhere, but rather has recesses, which ultimately form the flow path 17. In FIG. 3 the viewer is facing such a recess 53. In the area of peripheral surface 19 is flattened, so that there is a gap between it and the inner surface 21.
  • this has the projections 23, of which at least one side of the recess 53 facing the viewer is shown here.
  • FIG. 3 shown is the overflow channel 15, which opens on the one hand in a central region 55 of the piston 13, wherein the central region 55 in FIG. 1 on the other hand, in the region of a recess 53 opens, the here in FIG. 3 The viewer is arranged facing away.
  • three recesses 56 are introduced in the form of grooves 57 in the end face 25 of the piston 13, which are formed as radial grooves.
  • the grooves 57 form spaces 41, which are underflowed by fuel, wherein the grooves 57 provide a fluid connection between the inflow region 7 and the flow path 17.
  • a delayed response of the piston 13 and a sudden release from the first functional position is effectively avoided.
  • the remaining between the grooves 57 webs on which the end face 25 is arranged can be considered in the illustrated embodiment, as projections 59 on which the end face 25 is arranged in regions.
  • the first embodiment according to the Figures 1 and 2 and the second embodiment according to FIG. 3 to combine with each other.
  • 25 projections 59 and / or recesses 56 are provided both in the region of the end face, as well as in the region of the stop surface 27th
  • the proposed here quantity limiting valve 1 opens gently, punctually and continuously.
  • the pressure measurement in the region of the individual memory 5 is not adversely affected so that a correct and reproducible determination of the start of injection from the pressure curve measured in the region of the individual memory 5 is possible.
  • the quantity limiting valve 1 is preferably used in conjunction with injectors 3, which are provided for the direct injection of fuel into combustion chambers of the internal combustion engine 8.
  • the quantity limiting valve 1 in connection with a single-point injector for injecting fuel into a common intake manifold of the internal combustion engine 8, or in connection with multipoint injectors for injecting fuel into the combustion chambers of the internal combustion engine 8 individually assigned intake manifold.
  • the concrete use does not change the principle of operation of the quantity limiting valve 1 described here.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP14729857.4A 2013-06-12 2014-06-03 Mengenbegrenzungsventil Active EP3008327B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013210983.0A DE102013210983B4 (de) 2013-06-12 2013-06-12 Mengenbegrenzungsventil
PCT/EP2014/001490 WO2014198387A1 (de) 2013-06-12 2014-06-03 Mengenbegrenzungsventil

Publications (2)

Publication Number Publication Date
EP3008327A1 EP3008327A1 (de) 2016-04-20
EP3008327B1 true EP3008327B1 (de) 2018-05-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP14729857.4A Active EP3008327B1 (de) 2013-06-12 2014-06-03 Mengenbegrenzungsventil

Country Status (7)

Country Link
US (1) US9909547B2 (zh)
EP (1) EP3008327B1 (zh)
JP (1) JP2016520767A (zh)
CN (1) CN105264216B (zh)
DE (1) DE102013210983B4 (zh)
HK (1) HK1220243A1 (zh)
WO (1) WO2014198387A1 (zh)

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DE102019121156A1 (de) * 2019-08-06 2021-02-11 Woodward L'orange Gmbh Einsatz für ein Mengenbegrenzungsventil

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CN105264216B (zh) 2017-11-17
DE102013210983B4 (de) 2021-04-29
US20160084210A1 (en) 2016-03-24
JP2016520767A (ja) 2016-07-14
DE102013210983A1 (de) 2014-12-18
HK1220243A1 (zh) 2017-04-28
WO2014198387A1 (de) 2014-12-18
US9909547B2 (en) 2018-03-06
EP3008327A1 (de) 2016-04-20
CN105264216A (zh) 2016-01-20

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