EP1381774B1 - Dispositif d'injection de carburant comprenant deux elements de soupape coaxiaux - Google Patents

Dispositif d'injection de carburant comprenant deux elements de soupape coaxiaux Download PDF

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Publication number
EP1381774B1
EP1381774B1 EP02729851A EP02729851A EP1381774B1 EP 1381774 B1 EP1381774 B1 EP 1381774B1 EP 02729851 A EP02729851 A EP 02729851A EP 02729851 A EP02729851 A EP 02729851A EP 1381774 B1 EP1381774 B1 EP 1381774B1
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EP
European Patent Office
Prior art keywords
valve element
injection device
fuel injection
valve
pressure
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.)
Expired - Lifetime
Application number
EP02729851A
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German (de)
English (en)
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EP1381774A1 (fr
Inventor
Detlev Potz
Gerhard Mack
Thomas Kuegler
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1381774A1 publication Critical patent/EP1381774A1/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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • a fuel injection nozzle is shown in the elongated housing two mutually coaxial valve needles are guided. At the injection end, the housing is closed and includes two axially spaced rows of circumferentially spaced spray holes. There is a separating sleeve between the valve needles and the valve needles can be operated independently via separate fuel supply lines. Such fuel injectors are used for direct-injection internal combustion engines.
  • the purpose of the two valve needles lies in the adjustment of the injection characteristic to the operating load, what u.a. is important for the emission behavior of the internal combustion engine.
  • DE 32 14 040 A1 discloses a fuel injection device with two coaxial valve elements, which are at least temporarily in operative connection via a stop.
  • valve elements are no longer moved independently. Instead, the movement of the one valve element is coupled to a movement of the other valve element. This makes it possible to dispense with a separate control of the two valve elements. In this way, the fuel injection device can build smaller. Furthermore, the inventive design no mechanical means are required to effect a movement of the other valve element. This fuel injection device thus operates wear-free and therefore has a particularly long life.
  • the inner valve element opens first and causes a movement of the outer valve element in a movement after a certain way. It is particularly preferred if in the other valve element at least one opening is present, which covers the access to the flow channel from the fuel inlet by a distance in the closed state of the injection device.
  • a switchable stroke limiter is provided, by means of which the stroke of the first opening valve element can be limited so that the driver connection between the two valve elements does not yet engage.
  • the stroke limitation works hydraulically. In this case, it is possible to dispense with electrical components in the region of the fuel injection device. This increases the reliability of the fuel injection device.
  • first-opening valve may be connected to a first pressure surface defining a control chamber, and the control chamber may be fluidically closable.
  • the control chamber When the control chamber is fluidically closed, the fluid volume trapped in the control chamber, due to its low compressibility, acts like a mechanical stop against which the first pressure surface bears. In this way, the stroke of the first opening valve element is limited.
  • the first opening valve element may be connected to a second pressure surface, which causes an opening movement of the valve element when pressurized, wherein the first pressure surface is greater than the second pressure surface. This makes it possible to keep the pressure in the control room as low as possible.
  • a drain opening is present and that a control element is connected to the first opening valve element, which is spaced in the closed state of the fuel injection device from the drain opening and in the course of movement of the valve element, the drain opening sealing covered.
  • the fluidic closure of the control chamber can be canceled in a simple manner in that the fuel injection device has a switchable valve, via which the control chamber can be connected to an outlet.
  • a lifting of the fluidic Closure of the control chamber lifts the stroke limiter, so that the first opening valve element can cover the full opening travel while taking the second valve element.
  • valve is hydraulically switchable.
  • the later-opening valve element is connected to a third pressure surface, which presses the valve element onto the valve seat when the pressure is applied. This ensures that when the first opening valve element lifts from the valve seat and, for example, the stroke limiter is turned on, the other valve element is still pressed onto the valve seat.
  • the invention further relates to a fuel system for an internal combustion engine and an internal combustion engine.
  • FIGS. 1-3 the embodiment of a fuel injection device illustrated in FIGS. 1-3 will be explained. It comprises a housing 12 with an upper base section 14 in FIG. 1, a central section 16 and a nozzle body 18. Via an inlet 20, the fuel injection device 10 can be connected to a high-pressure fuel line (not shown). An outlet 22 may be connected to a low pressure region of a fuel system. Between the nozzle body 18 and the base portion 14, an intermediate disc 24 and a control disc 26 are arranged in the axial direction.
  • the fuel injector is for injecting fuel (gasoline or diesel) into the combustion chamber of an internal combustion engine (not shown).
  • the nozzle body 18 has, in its lower region in FIG. 1, an injection dome 28 which is provided with two axially spaced-apart rows of outlet openings 30 and 32 distributed over the circumference (see FIG. 3). Except for the outlet openings 30 and 32, the nozzle body 18 is thus closed at the lower end of sinem.
  • a recess 34 extending in its longitudinal direction is provided in the interior of the nozzle body 18.
  • the recess 34 has a bulbous extension 36, which via a flow channel 38 with the inlet 20 is connected (Fig. 2).
  • two formed as valve needles coaxial valve elements 40 and 42 are arranged in the recess 34.
  • the outer valve element 42 is tubular, the inner valve element 40 has a solid cross-section.
  • Both valve elements 40 and 42 have at their lower end sealing edges 44 and 46 which cooperate with corresponding valve seats (without reference numerals) between the outlet openings 30 and 32 and above the upper outlet openings 32.
  • annular space 48th From the injection tip 28 to the bulbous extension 36 extends between the outer valve member 42 and the inner wall (without reference numeral) of the recess 34, an annular space 48th
  • the outer diameter of the outer valve element 42 is greater in an upper region than in a lower region. In the transition between the two areas, approximately at the level of the extension 36, a pressure surface 50 is formed, their importance will be discussed in detail below.
  • an oblique shoulder 52 is formed on the inner circumferential surface (without reference numeral) of the outer valve member 42.
  • the outer valve element 42 extends beyond the upper side of the nozzle body 18 out into a central recess 54 in the intermediate disc 24. There, the upper end of the outer valve element 42 abuts against a control piston 56, which is slidably guided in the recess 54 in the intermediate disc 24 is.
  • the top of the control piston 56 forms a total of a first pressure surface 57. Its outer edge is pulled up in a ring.
  • a control pin 58 is supported, which extends almost completely through a central recess 60 in the control disk 26 therethrough.
  • At the top of the control pin 58 in turn supports the blunt tip of a conical Spring bolt 62 from.
  • At its base is located on a compression spring 64 which is received in a recess 66 in the base portion 14 of the housing 12.
  • the compression spring 64 is supported on an annular adjusting disk 68, which is arranged on the upper end of the recess 66 in the base portion 14 of the housing 12 in FIG.
  • the recess 66 is connected to the outlet 22 via a flow channel 70.
  • the inner valve element 40 is guided in the outer valve element 42.
  • a shoulder 72 is provided on the outer circumferential surface of the inner valve element 40.
  • the inner valve element 40 terminates shortly above the shoulder 72.
  • the upper end face of the inner valve element 40 is concave.
  • a recess 74 formed therethrough is connected via radially extending openings 76 and corresponding radially extending channels 78 in the wall of the outer valve member 42 with the bulbous extension 36 of the recess 34 and thereby through the flow channel 38 to the inlet 20.
  • the recess 74 also forms a pressure surface, whose importance will be discussed below.
  • a connecting pin 80 is supported, which is also supported on the control piston 56 with its upper end in the position of the valve elements 40 and 42 shown in FIGS. 1-3.
  • the control pin 58 which is arranged between the control piston 56 and the spring pin 62, has a circular cross section in a section 82 arranged at the bottom in FIG. 1, whereas in a top section 84 in FIG. 1 it has a bevel 86.
  • the diameter of the portion 82 corresponds approximately to the diameter of the recess 60 in the control disk 26.
  • the height of the circular portion 82 of the control pin 58 is chosen so that it projects beyond a distance S3 over the upper edge of the control piston 56, but it is still spaced from the lower edge of the control disk 26 by a distance S4.
  • a control chamber 88 is formed between the upper side 57 of the control piston 56 and the underside of the intermediate disk 24. From the control chamber 88 extends obliquely outwardly a Abêtbohrung 90 to an inlet chamber 92 of a spring-loaded ball valve 94.
  • a control piston 96 of the ball valve 94 is guided in an eccentric longitudinal bore 98 in the washer 24. Via a low-pressure control pressure port 100, the control piston 96 can be acted upon, whereby the inlet chamber 92 of the ball valve 94 is connected to a leakage oil drain 102.
  • the fuel injection device 10 is operated as follows:
  • a pressure wave is generated in a manner not shown here, which reaches via the fuel inlet 20 and the flow channel 38 into the annular space 48.
  • the pressure wave leads to the pressure surface 50 on the outer circumferential surface of the outer valve member 42 to a axially directed away from the injection stud 28 force, through which the outer valve member 42 via the control piston 56, the control pin 58 and the spring pin 62 against the spring force of the compression spring 64th is moved upward.
  • the sealing edge 46 of the outer valve element 42 lifts off from the corresponding valve seat in the region of the injection tip 28 of the nozzle body 18, which ultimately connects the upper outlet openings 32 via the annular space 48 with the fuel inlet 20.
  • the sealing edge 44 of the inner valve element 40 remains in contact with the corresponding valve seat in the region of the injection tip 28 of the nozzle body 18, so that the lower outlet openings 30 remain separated from the fuel inlet 20. This is ensured by the fact that the pressure wave propagates through the radial channels 78 in the outer valve element 42 and the radial openings 76 in the inner valve element 40 into the concave recess 74 in the upper end face of the inner valve element 40. Characterized in that the resultant of the pressure surface forming concave recess 74 in the opposite direction to As a result of the pressure surface 50 extends, the inner valve element 40 is acted upon in the opposite direction to the outer valve element 42 and thus pressed with its sealing edge 44 against the corresponding seat in the nozzle body 18.
  • control pin 58 By the opening movement of the outer valve member 42 and the control piston 56 and with this the control pin 58 is pushed upwards.
  • the fuel located in the control chamber 88 can escape upwards into the recess 66 through the gap formed between the bevel 86 and the recess 60 in the control disk 26 and flow out to the outlet 22 via the flow channel 70.
  • the control pin 58 In the course of the movement of the control pin 58, however, penetrates the lower circular portion 82 of the control pin 58 in the recess 60 in the control disc 26 a. In this case, there is no longer any gap between the control bolt 58 and the recess 60 in the control disk 26. The fuel present in the control chamber 88 can thus no longer escape from the control chamber 88.
  • a back pressure thus builds up, which acts on the pressure surface 57 of the control piston 56. Since this pressure surface 57 on the control piston 56 is considerably larger than the pressure surface 50 on the outer valve element 42, a counterforce builds up even at a relatively low pressure in the control chamber 88, whereby the movement of the outer valve element 42 is stopped. Thus, limiting the stroke of the outer valve element 42 is achieved by the fuel trapped in the control chamber 88.
  • the distance S4 between the top of the circular portion 82 of the control pin 58 and the bottom of the control disk 26 in the closed state of the fuel injection device 10 is smaller than the distance S1 between the shoulder 52 on the outer valve member 42 and the shoulder 72 on the inner valve member 40. In this way it is ensured that the movement of the outer valve member 42 is stopped before the shoulder 72 of the inner valve member 40 on Paragraph 52 of the outer valve member 42 comes into abutment.
  • the low pressure pilot pressure port 100 in the intermediate disk 24 is pressurized.
  • the ball valve 94 is lifted from its seat via the control piston 96, so that a fluid connection of the control chamber 88 via the spill port 90, the inlet chamber 92 and the eccentric longitudinal bore 98 to the drain hole 102 exists.
  • the outer valve member 42 is moved against the force of the compression spring 64 as described above.
  • the control chamber 88 is not fluidly closed even when the circular lower portion 82 of the control pin 58 is inserted into the recess 60 in the control disk 26. Instead, the fluid present in the control chamber 88 can flow to the drain outlet 90 via the spill port 90 in the manner described above to the drain outlet 102.
  • the movement of the outer valve element ends only when the annular edge of the control piston 56 rests against the underside of the control disk 26. In this case, the control piston 56 and with it the outer valve element 42 has covered the path S2.
  • the shoulder 52 comes in the course of the movement of the outer Valve element 42 in abutment against the shoulder 72, whereby the inner valve member 40 is entrained by the outer valve member 42.
  • the sealing edge 44 of the inner valve member 40 thus also lifts off from the corresponding valve seat in the injection tip 28 of the nozzle body 18, whereby the lower outlet openings 30 are also connected to the fuel inlet 20. If the pressure in the annular space 48 drops again, the inner valve element 40 is pressed via the connecting pin 80 and the outer valve element 42 by the compression spring 64 again with its sealing edges 44 and 46 against the corresponding valve seats in the injection tip 28 in the nozzle body 18.
  • the fundamental difference between the first and the second embodiment relates to the order of movements of the valve elements.
  • first opens the outer valve element 42.
  • the inner valve member 40 With the embodiment shown in FIGS. 4 to 6, however, first opens the inner valve member 40 and trailing, depending on the switching position of the ball valve 94, in the course of its opening movement, the outer valve element 42 with.
  • an additional spring 104 is provided, which the outer valve element 42 in its rest state with the sealing edge 46 against the corresponding valve seat in the injection tip 28 of the nozzle body 18th suppressed.
  • the outer valve element 42 is guided on the inner valve element 40, and the inner valve element 40 is again guided at least indirectly in the intermediate disc 24 with its end remote from the injection tip 28. In this way it is possible to make the extension 36 of the recess 34 in the nozzle body 18 accessible from the outside, so that it can be e.g. drilled and thus can be made very easily.
  • the outer valve element 42 is further guided by a constriction of the recess 34 in the nozzle body 18.
  • a sleeve 108 is additionally fastened to the inner valve element 40 at its upper end (compare, in particular, FIG. 5).
  • the attachment can be done for example by pressing.
  • a sleeve 108 offers the advantage of a larger pressure stage. By this is meant that the closing and the opening pressure are closer to each other, resulting in a faster closing of the inner valve member 40.
  • such a sleeve 108 allows a special choice of material for the guidance of the unit formed from sleeve 108 and inner valve element 40 in the intermediate disc 24th
  • the annular space 48 with which the fuel can reach the outlet openings 30 and 32, is provided between the inner valve element 40 and the outer valve element 42 in the embodiment illustrated in FIGS. 4-6.
  • FIGS. 4 and 6 show two possible embodiments of the injection tip 28.
  • the opening angle of the injection tip 28 is 60 °, whereas it is 90 ° on the right side of Figs. 4 and 6.
  • a smaller opening angle has advantages in terms of the size of the injection tip 28, whereas a larger angle has advantages in terms of tightness between the sealing edges and the corresponding valve seats ..
  • the injection angle has an influence on the combustion behavior of the injected fuel.
  • FIG. 7 shows a modification of the embodiment shown in FIGS. 4-6.
  • the sleeve 108 is dispensed with. Instead, the inner valve element 40 is guided directly in the intermediate disc 24. This is easier to manufacture.
  • FIGS. 8 and 9 show a fourth exemplary embodiment of a fuel injection device 10. Also in these two figures bear such elements and parts which have equivalent functions to parts and elements of Figs. 1-7, the same reference numerals. They are not explained again in detail.
  • the outer valve element 42 opens in front of the inner valve element 40.
  • the pressure surfaces on the outer valve element 42, which cause an axial opening movement of the outer valve element 42 at a pressure wave introduced via the inlet 20 and the flow channel 38 are present in two places of the outer valve element 42:
  • the outer surface of the outer carries Valve element 42 in the region of the confluence of the flow channel 38 a constriction 110.
  • the diameter of the outer valve element 42 above this constriction 110 is greater than the diameter below the constriction 110.
  • annular space 48 is present between the region of the outer valve element 42 below the constriction 110 and the recess 34 in the nozzle body 18, through which the pressure wave faces the injection point 28 up to a conical taper 112. Tip of the outer valve member 42 propagates (Fig. 9).
  • the region of the conical taper 112 up to the sealing edge 46 acts as a pressure surface on which a resultant force is set in a pressure wave, by means of which the outer valve element 42 with the sealing edge 46 lifts off from the corresponding valve seat.
  • the pressure chamber 36 is completely created by the constriction 106 in the outer valve member, the production of the recess 34 in the nozzle body 18 is considerably simplified and thereby the manufacturing cost of the fuel injection device 10 are lowered.
  • the inner valve element 40 is received in a blind hole 114 in the outer valve element 42.
  • the blind hole 114 extends coaxially with the longitudinal axis of the outer valve element 42 and is introduced into the outer valve element 42 from the injection tip 28 facing the end.
  • the inner valve element 40 also has a constriction 72 in its upper region.
  • each of the openings 116 each have a ball 118 is received, whose diameter is greater than the wall thickness of the outer valve member 42 in the region of the blind hole 114.
  • the openings 116 and the balls 52 are dimensioned and positioned so that when the fuel injection device 10 is closed the balls 52 have a distance S1 from the upper flank of the constriction 72 in the inner valve element 40 in FIGS. 8 and 9.
  • the balls 52, the openings 116 and the constriction 72 together form a driver connection, through which the inner valve element 40 is entrained during a movement of the outer valve element 42 by a distance which is greater than S1.
  • the injection pressure is transmitted via the annular space 48 to radial openings 118 in the peripheral wall of the outer valve element 42 delimiting the blind hole 114.
  • a pressure chamber 120 is fluidically connected to the annular space 48.
  • the pressure chamber 120 is formed between the end face 74 remote from the injection tip 28 and the bottom of the blind hole 114.
  • a spring 104 is tensioned between the end face 74 of the inner valve member 40 and the bottom of the blind hole 114.
  • the spring 104 provides a basic force that pushes the inner valve member 40 in the unpressurized state with its sealing edge 44 against the corresponding seat in the injection head 28.
  • the advantage of the embodiment shown in FIGS. 8 and 9 is its simpler and therefore more cost-effective production and the execution of a particularly low-friction driver connection with the balls 52.
  • FIGS. 10 and 11 A fifth embodiment of a fuel injection device 10 is shown in FIGS. 10 and 11. Again, such parts and elements which have equivalent functions to parts and elements of the preceding figures bear the same reference numerals. They too are not explained again in detail.
  • the fuel injector shown in FIGS. 10 and 11 is again configured such that the outer valve member 42 opens first.
  • the end of the outer end facing the injection tip 28 is the end of the injection tip 28 Valve element 42 ago introduced into this one to the longitudinal axis of the outer valve member 42 coaxial bore 114.
  • this is not formed as a blind hole, but connected via a throttle channel 122 with a relatively small cross-section with a discharge space 124, which in turn extends to the top in Figs. 10 and 11 of the outer valve member 42.
  • the inner valve member 40 is different from that of the last-described embodiment:
  • annular groove 128 is introduced into the outer circumferential surface of the inner valve member 40.
  • the inner valve element 40 is penetrated by a transverse bore 130.
  • a longitudinal bore 132 extends to the transverse bore 130.
  • the radial bores 134 lie approximately at the level of the annular groove 128 at a distance S1 between axially opposite edges of the bores 134 and the annular groove 128.
  • the fuel injector 10 shown in Figs. 10 and 11 operates as follows:
  • the ball valve 94 is held accordingly in the closed state.
  • the hydraulic stop formed in this way is designed such that the outer valve element 42 can only move a distance, which is smaller than S1.
  • the pressure wave via the annular space 48, the radial bores 134, the annular groove 128, the transverse bore 130 and the longitudinal bore 132 continues into the pressure chamber 120. Due to the small flow cross section of the throttle channel 122, the pressure in the pressure chamber 120 is largely retained and presses the inner valve element 40 with its sealing edge 44 against the corresponding valve seat in the injection tip 28 of the nozzle body 18 via the pressure surface 74.
  • the advantage of the fuel injection device 10 shown in FIGS. 10 and 11 is that no mechanical parts for the driver connection between the inner valve element 40 and the outer valve element 42 are required. Thus, no wear can occur at this point, what the reliability of this Fuel injection device 10 improved.
  • the transverse bore 130 is arranged approximately at half the length of the inner valve element 40. This ensures that the pressure wave arrives at approximately the same time at the conical taper 112 of the outer valve element 42 and in the pressure chamber 120, so that on the one hand acting on the outer valve member 42 opening force and the other acting on the inner valve member 40 closing force occur simultaneously.
  • top and bottom refer only to the representations in the figures. The actual mounting positions may differ from this.

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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)

Claims (12)

  1. Dispositif d'injection de carburant (10) pour moteurs à combustion interne, comprenant
    - un boîtier longitudinal (12) avec une extrémité d'injection fermée (28),
    - une cavité (34) dans le boîtier (12) s'étendant dans sa direction longitudinale et qui peut être reliée à une admission de carburant (20),
    - au moins deux orifices de sortie (30, 32) écartés l'un de l'autre sur l'extrémité d'injection (28),
    - au moins deux éléments de soupape coaxiaux mobiles axialement (40, 42) et disposés au moins par zones dans la cavité (34) et qui coopèrent avec des sièges de soupape au niveau des orifices de sortie (30, 32),
    - les éléments de soupape (40, 42) coopérant de sorte qu'un élément de soupape (40 ; 42) entraîne un déplacement de l'autre élément de soupape (42 ; 40) lorsqu'il se déplace selon une trajectoire définie (S1),
    caractérisé en ce qu'
    une chambre de pression (120), prévue à l'extrémité d'un élément de soupape (40) qui part de l'extrémité d'injection (28), est reliée d'une part à une zone de basse pression (102) par un étrangleur d'écoulement (122) et peut être reliée d'autre part à l'admission de carburant (20) par l'intermédiaire d'un canal d'écoulement (130) qui s'étend transversalement, et la liaison entre la chambre de pression (120) et l'admission de carburant (20) est interrompue par l'autre élément de soupape (42) lorsque celui-ci s'est déplacé d'une certaine distance (S1).
  2. Dispositif d'injection de carburant (10) selon la revendication 1,
    caractérisé en ce que
    les orifices de sortie (30, 32) écartés axialement les uns des autres sont reliés fluidiquement entre eux lorsque les deux éléments de soupape (40, 42) sont relevés des sièges de soupape correspondants.
  3. Dispositif d'injection de carburant (10) selon l'une quelconque des revendications 1 ou 2,
    caractérisé en ce que
    l'élément de soupape intérieur (40) s'ouvre d'abord et, lorsqu'il se déplace sur une trajectoire définie (S1), entraîne un déplacement de l'élément de soupape extérieur (42).
  4. Dispositif d'injection de carburant (10) selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    au moins une ouverture (134), prévue dans l'autre élément de soupape, recouvre l'accès au canal d'écoulement (130) depuis l'admission de carburant d'une trajectoire (S1) lorsque le dispositif d'injection (10) est à l'état fermé.
  5. Dispositif d'injection de carburant (10) selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    une limitation de course commutable (94) permet de limiter la course de l'élément de soupape qui s'ouvre en premier (40 ; 42) de telle sorte que la liaison d'entraînement (52, 72) entre les deux éléments de soupape (40 ; 42) ne s'engage pas encore.
  6. Dispositif d'injection de carburant (10) selon la revendication 5,
    caractérisé en ce que
    la limitation de course fonctionne hydrauliquement.
  7. Dispositif d'injection de carburant (10) selon la revendication 6,
    caractérisé en ce que
    l'élément de soupape qui s'ouvre en premier (40 ; 42) est relié à une première surface de pression (57) qui délimite une chambre de commande (88), et cette chambre de commande (88) peut être fermée fluidiquement.
  8. Dispositif d'injection de carburant (10) selon la revendication 7,
    caractérisé en ce que
    l'élément de soupape qui s'ouvre en premier (40 ; 42) est relié à une deuxième surface de pression (50) qui entraîne, lors d'une pressurisation, un mouvement d'ouverture de l'élément de soupape (40 ; 42), et la première surface de pression est plus grande que la deuxième surface de pression.
  9. Dispositif d'injection de carburant (10) selon la revendication 7,
    caractérisé en ce qu'
    un orifice d'écoulement (60) est prévu dans la paroi de la chambre de commande (88) et un élément de commande (82) est relié à l'élément de soupape qui s'ouvre en premier (40 ; 42), lequel est écarté (54) de l'orifice d'écoulement (60) lorsque le dispositif d'injection de carburant (10) est à l'état fermé et recouvre de manière étanche l'orifice d'écoulement (60) au cours d'un déplacement de l'élément de soupape (40 ; 42).
  10. Dispositif d'injection de carburant (10) selon l'une quelconque des revendications 7 à 9,
    caractérisé en ce qu'
    une soupape commutable (94) permet de relier la chambre de commande (88) à une sortie (102).
  11. Dispositif d'injection de carburant (10) selon la revendication 10,
    caractérisé en ce que
    la soupape (94) peut être commutée hydrauliquement (100).
  12. Dispositif d'injection de carburant (10) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'élément de soupape qui s'ouvre ensuite (42 ; 40) est relié à une troisième surface de pression (74) qui appuie sur le siège de soupape lors de la pressurisation de l'élément de soupape (42 ; 40).
EP02729851A 2001-04-17 2002-04-04 Dispositif d'injection de carburant comprenant deux elements de soupape coaxiaux Expired - Lifetime EP1381774B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10118699 2001-04-17
DE2001118699 DE10118699A1 (de) 2001-04-17 2001-04-17 Kraftstoff-Einspritzvorrichtung und Kraftstoffsystem für Brennkraftmaschinen, sowie Brennkraftmaschine
PCT/DE2002/001234 WO2002084110A1 (fr) 2001-04-17 2002-04-04 Dispositif d'injection de carburant comprenant deux elements de soupape coaxiaux, systeme de carburant pour moteurs a combustion interne et moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1381774A1 EP1381774A1 (fr) 2004-01-21
EP1381774B1 true EP1381774B1 (fr) 2006-07-05

Family

ID=7681665

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02729851A Expired - Lifetime EP1381774B1 (fr) 2001-04-17 2002-04-04 Dispositif d'injection de carburant comprenant deux elements de soupape coaxiaux

Country Status (6)

Country Link
EP (1) EP1381774B1 (fr)
JP (1) JP4076142B2 (fr)
BR (1) BR0204830A (fr)
DE (2) DE10118699A1 (fr)
PL (1) PL358121A1 (fr)
WO (1) WO2002084110A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1482165A1 (fr) * 2003-05-26 2004-12-01 Siemens Aktiengesellschaft Injecteur avec plusieurs orifices pour moteur à combustion interne et prcédé d'utilisation d'un injecteur avec plusieurs orifices
DE10326044A1 (de) * 2003-06-10 2004-12-30 Robert Bosch Gmbh Einspritzdüse für Brennkraftmaschinen
DE10341452A1 (de) * 2003-09-09 2005-03-31 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10348978A1 (de) * 2003-10-22 2005-05-25 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, insbesondere für eine Brennkraftmaschine mit Direkteinspritzung
DE102004015361A1 (de) * 2004-03-30 2005-10-20 Bosch Gmbh Robert Ventil zum Einspritzen von Kraftstoff
US7243862B2 (en) 2004-04-07 2007-07-17 Delphi Technologies, Inc. Apparatus and method for mode-switching fuel injector nozzle
DE102004020550A1 (de) * 2004-04-27 2005-11-24 Robert Bosch Gmbh Einspritzdüse
TR200402048A1 (tr) * 2004-08-18 2006-03-21 Robert Bosch Gmbh Hidrolik kontrollü değişken kesitli enjektör memesi.
DE102004046899A1 (de) * 2004-09-28 2006-03-30 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
TR200504275A1 (tr) * 2005-10-26 2007-10-22 Robert Bosch Gmbh Konik yakıt kanallı enjektör sistemi.
DE102006012842A1 (de) * 2006-03-21 2007-09-27 Robert Bosch Gmbh Kraftstoffeinspritzventile für Brennkraftmaschinen
DE102010040309A1 (de) 2010-09-07 2012-03-08 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102010040307A1 (de) 2010-09-07 2012-03-08 Robert Bosch Gmbh Brennstoffeinspritzventil
CN116044628A (zh) * 2023-01-03 2023-05-02 哈尔滨工程大学 一种机油润滑式甲醇燃料共轨式喷油器

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
DE2710138A1 (de) * 1977-03-09 1978-09-14 Maschf Augsburg Nuernberg Ag Mehrloch-einspritzduese
DE3036583A1 (de) * 1980-09-27 1982-05-13 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzduese
DE3214040A1 (de) * 1982-04-16 1983-10-20 Volkswagenwerk Ag, 3180 Wolfsburg Kraftstoffeinspritzduese, insbesondere fuer einen schnellaufenden fahrzeug-dieselmotor
EP0267203A1 (fr) * 1986-04-25 1988-05-18 VOEST-ALPINE AUTOMOTIVE Gesellschaft m.b.H. Injecteur pour moteurs a combustion interne
DE4115457A1 (de) * 1990-05-17 1991-11-21 Avl Verbrennungskraft Messtech Einspritzduese fuer eine brennkraftmaschine
DE4023223A1 (de) * 1990-07-21 1992-01-23 Bosch Gmbh Robert Kraftstoff-einspritzduese fuer brennkraftmaschinen
DE19739905A1 (de) * 1997-09-11 1999-03-18 Bosch Gmbh Robert Kraftstoffeinspritzventil
EP0967382B1 (fr) * 1998-06-24 2004-11-24 Delphi Technologies, Inc. Injecteur de carburant
GB9914642D0 (en) * 1999-06-24 1999-08-25 Lucas Ind Plc Fuel injector
ATE391232T1 (de) * 1999-10-06 2008-04-15 Delphi Tech Inc Kraftstoffeinspritzventil
DE10034444A1 (de) * 2000-07-15 2002-01-24 Bosch Gmbh Robert Brennstoffeinspritzventil

Also Published As

Publication number Publication date
JP4076142B2 (ja) 2008-04-16
BR0204830A (pt) 2003-04-29
DE50207439D1 (de) 2006-08-17
DE10118699A1 (de) 2002-10-31
JP2004518907A (ja) 2004-06-24
PL358121A1 (en) 2004-08-09
WO2002084110A1 (fr) 2002-10-24
EP1381774A1 (fr) 2004-01-21

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