EP3055549B1 - Ensemble piston-conduit de fluide, en particulier ensemble piston de commande-alésage de commande - Google Patents

Ensemble piston-conduit de fluide, en particulier ensemble piston de commande-alésage de commande Download PDF

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Publication number
EP3055549B1
EP3055549B1 EP14777586.0A EP14777586A EP3055549B1 EP 3055549 B1 EP3055549 B1 EP 3055549B1 EP 14777586 A EP14777586 A EP 14777586A EP 3055549 B1 EP3055549 B1 EP 3055549B1
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EP
European Patent Office
Prior art keywords
piston
fluid
fluid line
control
geometry
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.)
Not-in-force
Application number
EP14777586.0A
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German (de)
English (en)
Other versions
EP3055549A1 (fr
Inventor
Willibald SCHÜRZ
Roman Etlender
Werner Reim
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.)
Continental Automotive GmbH
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Continental Automotive GmbH
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Publication date
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Publication of EP3055549A1 publication Critical patent/EP3055549A1/fr
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Publication of EP3055549B1 publication Critical patent/EP3055549B1/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
    • 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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8092—Fuel injection apparatus manufacture, repair or assembly adjusting or calibration

Definitions

  • the invention relates to a piston-fluid line arrangement, in particular a control piston control bore arrangement for an injector, in particular a fuel injector for a direct injection system of a motor vehicle. Furthermore, the invention relates to an injector, in particular a fuel injector for a direct injection system of an internal combustion engine.
  • the DE 10 2011 079 468 A1 discloses a piston fluid line arrangement, in particular a control piston control bore arrangement for an injector, in particular a fuel injector for a direct injection system of a motor vehicle, in which a piston of the piston-fluid line arrangement fitted or paired into a fluid line by means of a fluid passing through the fluid line hydraulically positioned sideways.
  • a deviation of an actual injection quantity-a so-called shot-from a desired injection quantity of the injector always has a negative effect on combustion, that is to say the resulting pollutant emissions, and usually also consumption of the internal combustion engine.
  • the object of the invention is by means of a piston-fluid line arrangement, in particular a control piston control bore arrangement for an injector, in particular a fuel injector for a direct injection system of a motor vehicle, according to claim 1; and by means of an injector, in particular a fuel injector for a direct injection system of an internal combustion engine, according to claim 11 solved.
  • the piston-fluid line arrangement comprises a piston fitted and / or paired into a fluid line which can be hydraulically positioned sideways by a fluid passing through the fluid line, wherein according to the invention a geometry of the piston and / or a geometry of the fluid line is configured or are that the piston is positioned eccentrically and / or positioned by the fluid in the fluid line.
  • the geometry of the piston is preferably a secondary geometry, wherein a primary geometry of the piston is preferably cylindrical.
  • the geometry of the fluid line is preferably a secondary geometry, wherein a primary geometry of the fluid line is also preferably cylindrical.
  • the injector according to the invention comprises a piston-fluid line arrangement according to the invention, in particular a control piston control bore arrangement according to the invention.
  • the preferred secondary geometry of the piston and / or the preferred secondary geometry of the fluid conduit is configured such that a centerline of the piston is positionable and / or positioned by the fluid substantially parallel to a centerline of the fluid conduit.
  • the geometry (s) may be selected such that a flow of the fluid between the piston and the fluid line (sealing gap) is greater than a flow in the case of a concentric position of the piston in the fluid line.
  • the piston assumes a substantially highly eccentric position relative to the fluid line.
  • Such an embodiment may be advantageous in some applications wherein a maximum minimum flow rate for a given fit or pairing is adjusted by the piston and the fluid line.
  • the preferred secondary geometry of the piston and / or the preferred secondary geometry of the fluid conduit is or are configured such that in a sealing gap between a lateral surface of the piston and an inner surface of the fluid line an asymmetric pressure distribution of the fluid is adjustable and / or is set.
  • the geometry (s) may be selected such that a fluid path is provided in the lateral surface of the piston and / or the inner surface of the fluid line, by means of which the asymmetrical pressure distribution of the fluid in the sealing gap is adjustable and / or adjusted.
  • the geometry (s) may be selected such that the fluid path is provided in the lateral surface of the piston and / or the inner surface of the fluid line such that a lateral force can be exerted and / or exerted on the piston by means of the fluid.
  • the asymmetric pressure distribution of the fluid in the sealing gap has the lateral force of the fluid to the piston result, the side force to attack on the piston so, ie the asymmetric pressure distribution on the piston should be set up so that the center line of the piston with respect to the center line of the fluid line is set up parallel and parallel.
  • the fluid path can be designed in such a way that the piston is permanently securely positioned in an eccentric position over relevant operating states and the flow of the fluid through the sealing gap is comparatively small.
  • the piston For a given pressure difference on the piston, it is primarily desired to have a flow that is as constant as possible and, secondarily, the lowest possible flow of fluid through the sealing gap.
  • a larger eccentricity of the piston also means a larger flow of fluid through the sealing gap, therefore, it is preferable to aim for a safe eccentric position, in which the flow of the fluid through the resulting sealing gap is comparatively small. Ie. it is a comparatively small, but over time geometrically constant eccentric position of the piston in the fluid line sought.
  • the fluid path can be provided on / in the piston and / or on / in the fluid line.
  • the following explanations relate mainly to the piston and are, where appropriate, also applicable to the fluid line.
  • the fluid path on / in the piston can be arranged such that it can be brought into fluid communication with a high-pressure side or a low-pressure side of the piston.
  • the fluid in the fluid path pushes the piston away from an opening of the fluid path on / in the piston, or the fluid in the sealing gap presses the piston toward an opening of the fluid path on / in the piston.
  • Under the low pressure side should be understood an end region of the piston, in which there is a lower fluid pressure than on the high pressure side of the piston. This pressure difference can be only a few bar, which can certainly prevail on the low pressure side, a fluid high pressure.
  • Fluid path pushes the piston away from the opening of the fluid path in the direction of a radially opposite region of the inner surface of the fluid line.
  • the fluid in the sealing gap presses the piston in the direction of the opening of the fluid path to a region of the inner surface of the fluid line directly opposite the opening.
  • the fluid path can have a recess on / in the piston, wherein the recess is in particular a groove or facet, which extends in sections in the circumferential direction and / or in sections in the longitudinal direction of the piston.
  • a bottom of the recess may be flat or curved, d. H. the bottom of the recess has z. B. a radius.
  • the fluid path can have a fluid connection from an interior and an exterior of the piston, wherein the fluid connection is in particular a bore, preferably a through-bore, and / or an intersection, preferably an inner and outer recess of the piston.
  • the fluid path outside the piston may have the opening, a circumferential groove, a circumferential facet, a longitudinal groove and / or a longitudinal facet.
  • the fluid path may include at least one bore from an outside of the piston to a piston interior.
  • the fluid path can have an intersection of an outer recess with an inner recess and / or a recess on a longitudinal end portion of the piston.
  • the piston may be formed as a control piston, a pin, a control pin or a leakage pin.
  • the fluid is preferably a diesel or gasoline fuel.
  • a fluid pressure in a fluid space by means of a reproducible piston position in a fluid line.
  • This will be a position of Pistons set in the fluid line by means of a geometry of the piston and / or the fluid line.
  • the invention is well applicable to injectors, in particular fuel injectors, wherein a fluid pressure in a control chamber of the injector is well adjustable or can be maintained during an injection pause. Ie. it improves the shot / shot scattering of the injector.
  • a dispersion in a mass production based on an injector function is reduced, and a proportion of those injectors that do not meet required tolerances in their injection quantities, can be reduced.
  • an expense of necessary rework can be reduced. This affects individually and in total in a reduction of the manufacturing costs.
  • FIG. 1 a longitudinal side view of an injector according to the invention for a common rail injection system of an internal combustion engine, which is shown centrally and centrally cut below; the Fig. 2 a centrally cut, broken away top and bottom, detailed longitudinal side view of a control assembly of the injector Fig. 1 , with a hydraulic direct drive of a nozzle needle; and the Fig. 3 to 5 a first, the Fig. 6 to 8 a second, the Fig. 9 to 11 a third, the Fig. 12 to 14 a fourth, the 15 to 17 a fifth, the Fig. 18 to 20 a sixth, and the Fig.
  • FIGS. 24 and 25 two embodiments of an application of the invention to a fluid line.
  • the invention is explained in more detail below with reference to a piezoelectrically operated common rail diesel injector 1 for an internal combustion engine (see FIG. Fig. 1 ).
  • the invention is not limited to such diesel injectors 1, but can, for. B. also be applied to pump-nozzle injectors or gasoline injectors with a single or multi-part nozzle needle.
  • gasoline injectors typical names can be found in the list of reference numerals.
  • An injectable fluid may be a fuel, it is of course possible by means of an injector 1 according to the invention, another fluid such. Water, an oil or any other process fluid; ie the injector 1 according to the invention is not limited to the automotive industry.
  • the Fig. 1 shows the injector 1 substantially in a sectional view, wherein the injector 1 comprises a nozzle assembly 10 and an injector assembly 50.
  • the nozzle assembly 10 and the Injektorbaueria 50 are fluid-tight by means of a nozzle lock nut 60 together.
  • the injector assembly 50 has an injector body 500, in which an actuator 510 is provided, which is preferably designed as a piezoelectric actuator 510.
  • an electromagnetic actuator is also applicable.
  • the piezoactuator 510 drives a one-piece, preferably integral, nozzle needle 110 hydraulically directly (see also FIG Fig. 2 ).
  • the nozzle needle 110 may also be formed in two or more parts and / or be configured to open outwardly in the injector 1.
  • the injector body 500 has a high-pressure-side fluid connection (not illustrated) for the fuel to be injected, the fluid connection being in fluid communication with a high-pressure bore 502 formed in the injector body 500.
  • the injector 1 is hydraulically connectable to a high-pressure fluid circuit (not shown).
  • the high-pressure bore 502 supplies the nozzle assembly 10 and thus a nozzle chamber 102 of the injector 1 with fuel under high pressure, z. B. a so-called rail pressure (common rail system).
  • rail pressure common rail system
  • the nozzle assembly 10 has a nozzle body 100 with at least one spray hole (not shown) in its nozzle 104 and the nozzle chamber 102, wherein the nozzle needle 110 is arranged displaceably in the nozzle chamber 102 and stored in sections.
  • the nozzle needle 110 is pressed via an energy storage 114, preferably a nozzle needle spring 114, in the direction of its nozzle needle seat inside in the nozzle 104 in order to be securely closed even in an electrically non-energized state of the piezoelectric actuator 510.
  • the nozzle needle 110 is either pressed into its nozzle needle seat or moves away from the nozzle needle seat, whereby fuel can be injected.
  • the nozzle assembly 10 further accommodates a control assembly 20 located between the nozzle body 100 and the injector assembly 50 for actuating the nozzle needle 110 based on elongation of the piezoactuator 510 in response to its energy or charge, that is, an electrical voltage applied thereto.
  • the Fig. 2 shows the components of the control assembly 20 for a direct hydraulic coupling by an elongation movement of the piezoelectric actuator 510 and thereby caused movement of the nozzle needle 110.
  • the piezoelectric actuator 510 has for this purpose a bottom plate 512 with a preferably one-piece Betsch Trentsfortsatz in direct mechanical contact with a transmission pin 214 is fitted and / or paired with a very small clearance in a pin bore 212 of an intermediate plate 210 of the control assembly 20.
  • a mating clearance of the transmission pin 214 in the pin bore 212 is chosen to be so small, e.g. B. about 1 micron, that even at a high Rail pressure of up to over 2,500 bar only a small fuel leakage at the transfer pin 214 occurs.
  • the pin bore 212 connects a first control chamber 22, which is also referred to as a piston control chamber 22 and in which a slightly lower fuel pressure than the actual rail pressure prevails, with a leakage chamber 52 of the injector 1, which is preferably in an ambient pressure in permanent fluid communication.
  • the leakage chamber 52 is preferably in fluid communication with a leakage connection 504 of the injector 1.
  • the first control chamber 22 communicates through a connecting bore 14 in a section of the control assembly 20 with a second control chamber 12, the so-called needle control chamber 12, preferably in permanent fluid communication.
  • a slightly lower fuel pressure prevails than the rail pressure, wherein the pressures in the control chambers 12, 22 are substantially the same, at least when the injector 1 is closed.
  • a fluid throttle (not shown) may be provided, which is preferably formed in a separate plate 230 of the control module 20.
  • a stroke (elongation) of the piezoelectric actuator 510 is transmitted by means of the transmission pin 214, which is also referred to as leakage pin 214, to a control piston 300, which is fitted and / or paired into a control bore 400 of a control plate 220 of the control module 20.
  • the transmission pin 212 engages on / in the first control chamber 22 at an upper end face of the control piston 300, wherein the control piston 300 is supported on an inner end face by an energy storage device 224, preferably designed as a spiral spring 224.
  • At the inner end face and an underside of the control piston 300 there is preferably substantially rail pressure, this area preferably is in permanent fluid communication through a communication bore 232 with the nozzle space 102.
  • control piston 300 is designed as a sleeve 300 which is closed on the upper side (side of the first control chamber 22) and in the interior 340 of which the spring element 224 for returning the control piston 300 protrudes. It is of course possible to form the control piston 300 as a solid cylinder, in which case the spring element 224 acts on an underside of the control piston 300, and the spring element 224 z. B. may be stored in a bore in the plate 230. Mixed forms between the illustrated sleeve-shaped control piston 300 and a control piston 300 as a solid cylinder are of course possible.
  • the second control chamber 12 is formed by an end face of an upper longitudinal end portion 112 of the nozzle needle 110, the so-called needle piston 112, a wall of a needle bore 122 in an upper guide 120 of the nozzle needle 110, preferably a nozzle needle sleeve 120, and a lower end face of the plate 230.
  • the needle piston 112 of the nozzle needle 110 is facing away from a nozzle needle tip of the nozzle needle 110 or the nozzle 104 of the nozzle body 100.
  • a pressure drop is generated in the first control chamber 22, which via the connection bore 14 and possibly delayed by the optional fluid throttle in the plate 230 on the upper end face of the nozzle needle 110 is transmitted in the second control room 12. If this pressure drop exceeds a certain value, the nozzle needle 110 opens and there is an injection of fuel (shot).
  • a stroke of the nozzle needle 110 can be controlled or regulated by opening the nozzle needle 110 via a variation of the stroke of the piezoactuator 510.
  • the stroke of the piezo actuator 510 can be changed by a variation of its intrinsic electrical energy.
  • the aim of the invention is to ensure the lowest possible shot / shot scattering of the injections.
  • An influence on a self-adjusting fluid pressure in the control chamber 12, 22 have to a large extent the control piston 300 (in general: piston 300) and the control bore 400 (in general: fluid line 400).
  • Possible positions of the control piston 300 in the control bore 400 are substantially a concentric, an eccentric and a tilted position. Due to these different positions of the control piston 300, the flow resistances in the control bore 400 change due to a position resulting from the respective position Gap geometry significant.
  • the flow of fluid through the sealing gap 222 at a maximum eccentric position of the control piston 300 is increased by a factor of about 2.5 in comparison to its concentric position. At a maximum tilted position of the control piston 300, this factor is only about 0.5. Ie.
  • a fivefold amount of fluid per unit of time can flow than at a maximum tilted position (in the case of an injector 1). This has a significant effect on the adjusting in the injection pauses pressures in the control chambers 12, 22, in particular the first control chamber 22nd
  • the solution according to the invention for this problem consists in using a geometry of the control piston 300 (cf. Fig. 3 to 23 ) and / or a geometry of the control bore 400 (see. FIGS. 24 and 25 ) to influence a position of the control piston 300 in the control bore 400 influence. This is preferably done in such a way that primarily a safe eccentric and no concentric and no tilted position of the control piston 300 in the control bore 400 is sought. Secondarily, in this safe eccentric position, a flow of the fluid (here: fuel) through a self-adjusting sealing gap 222 should be comparatively low.
  • the corresponding geometry or the corresponding geometries are chosen such that a center line 302 of the control piston 300 is set parallel to a center line 402 of the control bore 400, wherein the two center lines 302, 402 are not aligned, but spaced from each other, in particular not maximum spaced from each other, are.
  • control piston 300 is modified on its lateral surface 304 and / or the control bore 400 on its inner surface 404 such that a resultant lateral force on the control piston 300, which ensures an eccentric preferred position of the control piston 300 in the control bore 400.
  • a modification is preferably performed by a fluid path 310, 410 on / in the control piston 300 and / or on / in the control bore 400 which opens on the control piston 300 (opening 312, 412).
  • the fluid path 310, 410 can be a groove, z. B. a circumferential groove and / or a longitudinal groove, a facet, z. B. a peripheral facet and / or a Leksfacette, a WegNeillung and / or a fluid connection, such as a bore, a through-bore and / or an intersection, etc., or any combination thereof. All of these terms are to be subsumed in accordance with this specification under the term recess, in the sense of deviation from a primary geometry of the control piston 300 and the control bore 400.
  • the primary geometry of the control bore 400 and the control piston 300 is the shape of a (hollow) cylinder or a (hollow) cone.
  • the control piston 300 may be a part or section of another component, for. B. a needle piston 112 of a nozzle needle 110, a valve body or a part or portion thereof, etc. This applies analogously to the control bore 400, which does not necessarily have to be set up in the control plate 220.
  • An opening 312, 412 of the fluid path 310, 410 constituted by one or a plurality of recesses 320, 322; 422, 426, is designed such that the center lines 302, 402 of the control piston 300 and the control bore 400 are substantially parallel to each other.
  • the lateral force generated by the fluid passing through the opening 312, 412 acts on the control piston 300 substantially longitudinally on the control piston 300, so that substantially no tilting moment on Control piston 300 is created.
  • This can have the consequence that the opening 312, 412 itself is not provided centrally on the control piston 300 (see. Fig. 5 ), since the pressure conditions in the sealing gap 222 change from the high to the low pressure side, wherein the sealing gap 222 acts as a fluid throttle.
  • the fluid path 310, 410 of the control piston 300 and / or the control bore 400 with the high-pressure side (FIG. 3 to 24 ) or with the low-pressure side ( Fig. 25 ) are in fluid communication.
  • the fluid communication of the fluid path 310, 410 with the low pressure side is a hydraulic reversal of the fluid communication of the fluid path 310, 410 with the high pressure side.
  • an overpressure at the opening 312, 412 on the control piston 300 ensures a parallel offset of the control piston 300 relative to the control bore 400.
  • An essential design feature is that on / in the lateral surface 304 of the control piston 300 on one side one or a plurality of recesses 320 - fluid path 310 or a portion thereof - are introduced in possibly different geometries. These recesses 320 lead to the asymmetrical pressure distribution in the sealing gap 222, so that the resulting lateral force arises, which brings the control piston 300 in its eccentric preferred position. - Since a piston interior 340 and a bottom of the control piston 300 with substantially the rail pressure of the injector 1, a pressure prevails in the fluid path 310 substantially at a level of the rail pressure.
  • a width (circumferential direction of the control piston 300) and height (longitudinal direction of the control piston 300) and an axial position of the opening 312 determine the hydraulic lateral force on the control piston 300.
  • An advantageous and possibly 'optimal' design for the injector 1 provides a hydraulic lateral force which permanently positions eccentrically the control piston 300 (the side force is higher than a sum of possible 'disturbing' forces, such as a lateral force from the spring element 224), whereby the lateral force on the control piston 301 is preferably comparatively small. especially minimal, is or remains.
  • first embodiment of the invention as a recess 320 in the circumferential and longitudinal direction of the control piston 300 extending groove 324 in the lateral surface 304 of the control piston 300 is introduced (outer recess 320).
  • the circumferential groove 324 passes through a fluid connection 330, in particular a through-bore 332, in fluid communication with the piston interior 340, which preferably radially connects a bottom of the circumferential groove 324 with the piston interior 340.
  • the bottom of the circumferential groove 324 may, as in Fig. 4 to see, have a radius of z. B. is greater than that of the control piston 300.
  • the floor can also be level (cf. Fig. 13 ).
  • a boundary of the circumferential groove 324 on the lateral surface 304 forms the opening 312 of the fluid path 310.
  • two fluid connections 330 in particular two through holes 332, in a wall of the control piston 300, preferably in the radial direction, introduced.
  • the through holes 332 are located on one side of the control piston 300, and an angle of their center lines is preferably less than 120 °, in particular less than 90 ° and particularly preferably less than 45 °.
  • the boundaries of the through-bores 332 on the lateral surface 304 together form the opening 312 of the fluid path 310. It is, of course, possible to provide only one or a plurality of through-bores through the wall of the control piston 300.
  • the fluid path 310 comprises an outer recess 320 which is formed as a longitudinal facet 326 or longitudinal groove 326.
  • a surface 326 is ground or introduced to the control piston 300 over a certain length and width (circumferential direction of the control piston 300), which to the side of the rail pressure but z. B. also to the side of the first control chamber 22 (not shown, see FIG. Fig. 25 ) is open.
  • a bottom of the longitudinal facet 326 or longitudinal groove 326 may, as in Fig. 10 to see, to be just, but also a radius analogous to Fig. 4 can be applied.
  • a boundary of the longitudinal groove 326 or longitudinal facet 326 on the lateral surface 304 forms the opening 312 of the fluid path 310.
  • the fluid path 310 in each case from the side of the rail pressure of the control piston 300 has a narrow outer recess 320 which is formed as a L Lucasstheticsnut 326 in the lateral surface 304 of the control piston 300.
  • the respective longitudinal connection groove 326 opens into an outer recess 320 which is designed in each case as a circumferential groove 324.
  • the fourth embodiment is characterized in that a bottom of the circumferential groove 324 is flat ( Fig. 13 ), whereas in the fifth embodiment, a bottom of the circumferential groove 324 has a radius ( Fig. 16 ), which in turn may be larger than that of the control piston 300.
  • the circumferential groove 324 of the fifth embodiment covers a larger area outside of the control piston 300 than the circumferential groove 324 of the fourth embodiment. In the first case, the circumferential groove 324 covers approximately 90 ° and in the second case approximately 30-45 °. Further, the Lijnstheticsnut 326 may not be as deep, equal deep or deeper worked into the wall of the control piston 300 as the circumferential groove 324 in the adjacent area.
  • the fluid path 310 includes an outer recess 320, which is formed as a circumferential groove 324.
  • a bottom of the circumferential groove 324 in turn has a radius (see above), but in turn may be flat.
  • the bottom of the circumferential groove 324 is in fluid communication with the piston interior 340 via an intersection 334 formed as a fluid connection 330.
  • the intersection 334 is produced by a longitudinal groove 322, which is constituted as an internal recess 322, in the piston interior 340.
  • the fluid communication 330 of the rail side circumferential groove 324 is made by the intersection 324 with the longitudinal groove 322 in the longitudinal direction of the spool 300 on an inner side of the spool 300.
  • a boundary of the circumferential groove 324 on the lateral surface 304 forms the opening 312 of the fluid path 310.
  • the fluid path 310 comprises a recess 328 or a recess 328 of a wall of the control piston 300, ie a piston shaft of the control piston 300 is shortened on one side over a specific circular segment.
  • a limitation of Wegappelung 328 on the lateral surface 304 forms the opening 312 of the fluid path 310th
  • control pistons 300 which are not hollow drilled. In such a case, if necessary, a preferably small bore must be introduced into the control piston 300.
  • these features can be applied to other mating and / or mating games in the injector 1, z. B. on the transmission pin 214 in the pin bore 212, to the nozzle needle 110 in the nozzle needle sleeve 120, etc., are applied, which in particular a leakage balance (inflow equal inflowing) and thus also affect a resulting pressure in the control chamber 12, 22.
  • the invention is generally applicable to hydraulic coupling elements 300, i. H. the control piston 300 is formed as a hydraulic coupling element 300.
  • the fluid path 410 of the control bore 400 comprises an inner recess 422, which is formed as a longitudinal facet 426 or longitudinal groove 426.
  • a surface 426 or recess 426 is ground or introduced into the inner surface 404 of the control bore 400 over a certain length and width (circumferential direction of the control bore 400), which is open to the side of the rail pressure.
  • this can also be to the side of the first control chamber 22 (not shown, cf. Fig. 25 ) be open.
  • a bottom of the longitudinal facet 426 or longitudinal groove 426 may be as shown in FIG Fig. 10 to see, to be just, but also a radius analogous to Fig. 4 can be applied, wherein the radius is preferably smaller than that of the control bore 400.
  • a boundary of the longitudinal facet 426 or longitudinal groove 426 on the inner surface 404 forms the opening 412 of the fluid path 410 of the control bore 400 on the control piston 300.
  • the fluid path 410 of the control bore 400, an inner recess 422, which is formed as a narrow longitudinal groove 426 and the side of the first control chamber 22 is open.
  • a limitation of the longitudinal groove 426 on the inner surface 404 essentially forms the opening 412 of the fluid path 410 of the control bore 400 on the control piston 300.
  • Inner recess 422 is in such a way, in particular in the longitudinal direction of the control bore 400 running established that results in an asymmetric pressure distribution of the fluid on the control piston 300, wherein the control piston 300 is sucked in the direction of the opening 412 of the fluid path 410 or from one of these opposite side of the fluid pressure is pressed in the sealing gap 222.
  • Such hydraulically reversed embodiments of the invention are generally applicable.
  • the pressure conditions on the control piston 300 in the radial direction of the control piston 300 at least qualitatively reverse. Ie. a pressure and a suction side on the control piston 300 change positions.
  • this means that the fluid path 310 of the control piston 300 is open to the low pressure side and opens in the sealing gap 222 on the control piston.
  • a fluid connection to the piston interior 340 is to be avoided.
  • a simple, not shown embodiment of the invention is a pressure channel through a solid cylinder designed as a control piston 300.
  • z. B two in the control piston 300 blind holes arranged. One bore extends axially from the low pressure side into the control piston 300 and the other radially extends toward and intersects this first bore within the control piston 300.
  • the injector 1 a pressure channel from the low pressure side on one side in / on the sealing gap 222 between the control piston 300 and the control bore 400.
  • This embodiment is of course hydraulically reversible, the first blind hole instead of coming from the low pressure side, now from the High pressure side is set in the control piston 300. In a fully rotationally symmetrical control piston 300, this can simply be turned over to get from this embodiment to the other embodiment.

Landscapes

  • 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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (11)

  1. Ensemble piston-conduit de fluide, en particulier ensemble piston de commande-alésage de commande (300/400) pour un injecteur (1), en particulier un injecteur de carburant (1) pour un système d'injection directe d'un véhicule automobile, dans lequel
    un piston (300) de l'ensemble piston-conduit de fluide (300/400) ajusté ou combiné dans un conduit de fluide (400) peut être positionné hydrauliquement vers le côté au moyen d'un fluide circulant à travers le conduit de fluide (400), caractérisé en ce qu'une géométrie du piston (300) et/ou une géométrie du conduit de fluide (400) est configurée de telle manière que le piston (300) puisse être ou soit positionné de façon excentrique par le fluide dans le conduit de fluide (400).
  2. Ensemble piston-conduit de fluide selon la revendication 1, caractérisé en ce que la géométrie du piston (300) et/ou la géométrie du conduit de fluide (400) est configurée de telle manière que
    une ligne centrale (302) du piston (300) puisse être et soit positionnée par le fluide de façon essentiellement parallèle par rapport à une ligne centrale (402) du conduit de fluide (400); et/ou
    un débit de fluide entre le piston (300) et le conduit de fluide (400) soit plus grand qu'un débit avec une position centrale du piston (300) dans le conduit de fluide (400).
  3. Ensemble piston-conduit de fluide selon la revendication 1 ou 2, caractérisé en ce que la géométrie du piston (300) et/ou la géométrie du conduit de fluide (400) est configurée de telle manière que
    une distribution de pression asymétrique puisse être et soit réglée dans une fente d'étanchéité (222) entre une surface extérieure (304) du piston (300) et une surface intérieure (404) du conduit de fluide (400);
    il soit prévu dans la surface extérieure (304) du piston (300) et/ou la surface intérieure (404) du conduit de fluide (400) un chemin de fluide (310), au moyen duquel la répartition de pression asymétrique dans la fente d'étanchéité (222) peut être et est réglée; et/ou
    le chemin de fluide (310) soit prévu dans la surface extérieure (304) du piston (300) et/ou la surface intérieure (404) du conduit de fluide (400) de telle manière qu'une force latérale puisse être et soit exercée sur le piston (300) au moyen du fluide.
  4. Ensemble piston-conduit de fluide selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le chemin de fluide (310) est configuré de telle manière que le piston (300) soit positionné de façon fixe dans une position excentrique et que le débit du fluide à travers la fente d'étanchéité (222) soit de ce fait relativement faible.
  5. Ensemble piston-conduit de fluide selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le chemin de fluide (310) sur/dans le piston (300) est réalisé de telle manière qu'il puisse être mis en communication fluidique avec un côté haute pression ou un côté basse pression du piston (300); dans lequel
    le fluide dans le chemin de fluide (310) écarte le piston (300) d'une ouverture (312) du chemin de fluide (310) sur/dans le piston (300) ou le fluide dans la fente d'étanchéité (222) pousse le piston (300) sur une ouverture (312) du chemin de fluide (310) sur/dans le piston (300).
  6. Ensemble piston-conduit de fluide selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le chemin de fluide (310) présente un évidement (320, 322) sur/dans le piston (300), dans lequel l'évidement (320, 322) sur/dans le piston (300) est en particulier une rainure (324, 326) ou une facette (324, 326), qui s'étend en direction périphérique et/ou en direction longitudinale du piston (300).
  7. Ensemble piston-conduit de fluide selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le chemin de fluide (310) présente une communication fluidique (330) entre un intérieur et un extérieur du piston (300), dans lequel la communication fluidique (330) est en particulier un alésage (332), de préférence un alésage de passage (332), et/ou une découpe (334), de préférence d'un évidement intérieur (322) et extérieur (320).
  8. Ensemble piston-conduit de fluide selon l'une quelconque des revendications 1 à 7, caractérisé en ce que le chemin de fluide (310):
    • présente l'ouverture (312) extérieurement sur le piston (300) ;
    • comprend extérieurement sur le piston (300) une rainure périphérique (324) et/ou une facette périphérique (324);
    • présente extérieurement sur le piston (300) une rainure longitudinale (326) et/ou une facette longitudinale (326);
    • comprend au moins un alésage (332) depuis un côté extérieur du piston (300) jusqu'à un espace intérieur du piston (340);
    • présente une découpe (334) d'un évidement extérieur (320) avec un évidement intérieur (322); et/ou
    • comprend un évidement (328) à une partie d'extrémité longitudinale du piston (300).
  9. Ensemble piston-conduit de fluide selon l'une quelconque des revendications 5 à 8, caractérisé en ce que le chemin de fluide (310) est réalisé dans le conduit de fluide (400) de façon analogue au piston (300).
  10. Ensemble piston-conduit de fluide selon l'une quelconque des revendications 1 à 9, caractérisé en ce que:
    • le piston (300) est réalisé sous forme de piston de commande (300), de broche, de broche de commande ou de broche antifuite (214);
    • un fond de l'évidement (320, 322) est plan ou courbe;
    • la géométrie du piston (300) est une géométrie secondaire du piston (300);
    • une géométrie primaire du piston (300) est une forme cylindrique;
    • la géométrie du conduit de fluide (400) est une géométrie secondaire du conduit de fluide (400);
    • une géométrie primaire du conduit de fluide (400) est une forme cylindrique; et/ou
    • le piston (300) est réalisé sous la forme d'un élément de couplage hydraulique.
  11. Injecteur, en particulier injecteur de carburant (1) pour un système d'injection directe d'un moteur à combustion interne, caractérisé en ce que l'injecteur (1) présente un ensemble piston-conduit de fluide (300/400), en particulier un ensemble piston de commande/alésage de commande (300/400), selon l'une quelconque des revendications précédentes.
EP14777586.0A 2013-10-11 2014-09-29 Ensemble piston-conduit de fluide, en particulier ensemble piston de commande-alésage de commande Not-in-force EP3055549B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013220547.3A DE102013220547B4 (de) 2013-10-11 2013-10-11 Kolben-Fluidleitung-Anordnung, insbesondere Steuerkolben-Steuerbohrung-Anordnung
PCT/EP2014/070829 WO2015052032A1 (fr) 2013-10-11 2014-09-29 Ensemble piston-conduit de fluide, en particulier ensemble piston de commande-alésage de commande

Publications (2)

Publication Number Publication Date
EP3055549A1 EP3055549A1 (fr) 2016-08-17
EP3055549B1 true EP3055549B1 (fr) 2018-04-18

Family

ID=51655722

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14777586.0A Not-in-force EP3055549B1 (fr) 2013-10-11 2014-09-29 Ensemble piston-conduit de fluide, en particulier ensemble piston de commande-alésage de commande

Country Status (5)

Country Link
US (1) US20160230728A1 (fr)
EP (1) EP3055549B1 (fr)
CN (1) CN105658945B (fr)
DE (1) DE102013220547B4 (fr)
WO (1) WO2015052032A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016208255B3 (de) * 2016-05-13 2017-06-08 Continental Automotive Gmbh Verfahren und Vorrichtung zum Betreiben eines Fluidinjektors für ein Kraftfahrzeug
JP6922558B2 (ja) * 2017-08-29 2021-08-18 株式会社デンソー 燃料噴射装置
CN109141760B (zh) * 2018-11-01 2024-05-28 三江开源有限公司 水压试验机
DE102019130674A1 (de) * 2019-11-13 2021-05-20 Svm Schultz Verwaltungs-Gmbh & Co. Kg Verfahren zur Bildung einer Ventileinheit, Ventileinheit

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
US4826081A (en) * 1987-08-20 1989-05-02 Zwick Eugene B Unit type fuel injector for low lubricity, low viscosity fuels
GB9920144D0 (en) * 1999-08-26 1999-10-27 Lucas Industries Ltd Fuel injector
DE19947772A1 (de) * 1999-10-05 2001-04-19 Hermann Golle Einspritzventil, insb. für Common-Rail-Einspritzsysteme
WO2003071122A1 (fr) * 2002-02-22 2003-08-28 Crt Common Rail Technologies Ag Soupape d'injection de carburant pour moteurs a combustion interne
JP4007202B2 (ja) * 2003-01-23 2007-11-14 株式会社デンソー 軸部材の摺動構造およびインジェクタ
CH697562B1 (de) * 2005-08-09 2008-11-28 Ganser Hydromag Brennstoffeinspritzventil.
DE102008002416A1 (de) * 2008-06-13 2009-12-17 Robert Bosch Gmbh Kraftstoffinjektor
DE102010042688A1 (de) * 2010-10-20 2012-04-26 Robert Bosch Gmbh Kraftstoffinjektor
DE102010042668A1 (de) * 2010-10-20 2012-04-26 Zf Friedrichshafen Ag Mehrstufengetriebe
DE102011079468A1 (de) * 2011-07-20 2013-01-24 Continental Automotive Gmbh Piezoinjektor
DE102012222509A1 (de) * 2012-12-07 2014-06-12 Continental Automotive Gmbh Piezoinjektor

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Title
None *

Also Published As

Publication number Publication date
EP3055549A1 (fr) 2016-08-17
US20160230728A1 (en) 2016-08-11
DE102013220547A1 (de) 2015-04-16
CN105658945B (zh) 2019-01-29
WO2015052032A1 (fr) 2015-04-16
CN105658945A (zh) 2016-06-08
DE102013220547B4 (de) 2017-05-04

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