EP1656498B1 - Soupape d'injection de carburant commandee par une soupape pilote - Google Patents

Soupape d'injection de carburant commandee par une soupape pilote Download PDF

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Publication number
EP1656498B1
EP1656498B1 EP04738118A EP04738118A EP1656498B1 EP 1656498 B1 EP1656498 B1 EP 1656498B1 EP 04738118 A EP04738118 A EP 04738118A EP 04738118 A EP04738118 A EP 04738118A EP 1656498 B1 EP1656498 B1 EP 1656498B1
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EP
European Patent Office
Prior art keywords
control
space
injection valve
fuel injection
pilot valve
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EP04738118A
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German (de)
English (en)
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EP1656498A1 (fr
Inventor
Marco Ganser
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Ganser Hydromag AG
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Ganser Hydromag AG
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Publication of EP1656498A1 publication Critical patent/EP1656498A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • 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
    • F02M47/025—Hydraulically 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
    • 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

Definitions

  • the present invention relates to a fuel injection valve for intermittent fuel injection into the combustion chamber of an internal combustion engine according to the patent claim 1.
  • a fuel injection valve is for example in the EP-A-1476652 described.
  • a hollow cylindrical housing is fixed to the housing a designated in the document as a control body drain body formed with a control passage.
  • control sleeve on the one hand operatively connected to an injection valve member control piston and on the other hand arranged as a slide valve body control body slidably disposed in a close sliding fit.
  • the control piston defines downwardly a control chamber, which is bounded above by the control body and laterally by the control sleeve.
  • a throttle restriction having throttle passages are formed, of which a throttle passage is connected via the throttle restriction with the control passage in Abiserraumoasa and with the control chamber in flow communication.
  • a throttle inlet formed in the control body opens into this control passage on the control chamber side, which is in flow communication with a high-pressure chamber via a cavity formed in the control sleeve, a slot in the control sleeve, and a flow gap formed between the sleeve and the housing, in which high-pressure fuel pressure prevails.
  • the control chamber is constantly via the throttle inlet directly to the high-pressure chamber in a flow connection.
  • Another fuel injection valve is in the EP-A-1273791 disclosed.
  • the control chamber of this fuel injection valve is bounded on the one hand by a piston of the injection valve member, on the other hand by a control body designated as a slide valve body and peripherally by a control sleeve. Both the double-acting piston and the control body are guided in a tight sliding fit on the control sleeve.
  • a throttle passage which is permanently connected to a control passage in a designated as a control body discharge space body flow-connected.
  • the discharge space body is partially supported on the control sleeve. From the high-pressure chamber, the throttle inlet leads into the control passage.
  • EP-A-0 426 205 Further fuel injection valves are in EP-A-0 426 205 .
  • EP-A-1 273 791 disclosed. They have a controlled by an electromagnetic actuator Pilotvantistatt which separates in the closed position provided with a throttle restriction outlet channel of a control chamber of a low-pressure outlet.
  • Pilotvantiux When the pilot valve pin is lifted from the pilot valve seat, fuel from the exhaust passage flows directly to the low pressure outlet.
  • an injection process is initiated and closing the pilot valve causes the closing movement of the injection valve member to terminate the injection process.
  • a fuel injection valve of this kind is in DE 101 00390 A disclosed. It comprises a nozzle module which has a valve control piston which cooperates with a nozzle needle and a valve control chamber delimited by a spring plate and an end face of the valve control piston which communicates with a high-pressure feed line via an inlet channel and which is actuated via a discharge channel with a piezoelectric actuator unit
  • Valve-shaped valve control module is in operative connection.
  • the valve control module has a arranged in a valve chamber and cooperating with two valve seats valve closing member, wherein the nozzle needle is opened via a caused by the valve control module pressure reduction in the valve control chamber via the flow channel and is closed by a filling of the valve control chamber.
  • the injection valve has means for filling the valve control chamber via the inlet channel and the outlet channel.
  • the throttle passage may be formed by a sliding fit for the pilot valve pin, but preferably the pilot valve pin is guided in a tight sliding fit and the relief space is connected to the low pressure outlet via a separately formed throttle passage.
  • the behavior of the fuel injector upon opening, that is, at the beginning of an injection event, may be very similar to that of known fuel injectors in which the exhaust port is provided with a throttle restriction.
  • the pilot valve pin is moved into the discharge chamber at high speed until it bears against the pilot valve seat. Since the throttle passage prevents rapid escape of the fuel from the discharge space, the said movement of the pilot valve pin and the associated displacement of fuel is followed by a very rapid increase in pressure in the discharge space and in a discharge space adjoining the latter upstream of the pilot valve seat, which results in a very rapid closing movement of the Injector valve member causes. This closing movement can be further supported be used that the movement of the pilot valve pin is mechanically utilized.
  • Fig. 1 shows in longitudinal section an inventive fuel injection valve 10 having a substantially cylindrical, a lateral high-pressure inlet 12 having valve housing 14.
  • This has a running in the direction of the longitudinal axis 16, continuous, stepped bore 17, in which an electric controlled actuator 18, a controlled by this control device 20 and a needle-shaped injection valve member 22 are arranged with a closing spring 24.
  • the injection valve member 22 is held by means of the closing spring 24 to an injection valve seat 26 in abutment, which is formed on an injection valve seat body 28.
  • This is substantially rotationally symmetrical to the longitudinal axis 16, is located on the front side of the valve housing 14 and is held by a cap nut 30 sealingly on the valve housing 14.
  • injection valve nozzles 32 are formed in a known manner, through which fuel is injected under very high pressure in a combustion chamber, not shown, of an internal combustion engine, when the injection valve member 22 by means of the actuated by the actuator 18 hydraulic control device 20 in the direction the longitudinal axis 16 is lifted from the injection valve seat 26.
  • the injection valve seat 26 delimits a high-pressure space 34 in which the injection valve member 22 is arranged and which, on the other hand, is delimited by the control device 20 and peripherally by the injection valve seat body 28 and valve housing 14.
  • the high-pressure chamber 34 is connected to the high-pressure inlet 12, through which fuel is supplied under very high pressure of up to 1000 bar or even 1800 bar or more to the high-pressure chamber 34 for injection into the combustion chamber of the internal combustion engine and for controlling the injection valve member 22.
  • the injection valve member 22 delimits, with its end region facing away from the injection valve seat 26, a control chamber 36, on the other hand, from a control body 38 is limited, in which concentric to the longitudinal axis 16 is formed with a throttle restriction 40 'Auslraw barnlass 40 is formed; see in particular also Fig. 2 , which a section of the fuel injection valve 10 of Fig. 1 with the control device 20 shows enlarged.
  • the control body 38 With its end face 42 facing away from the control chamber 36, the control body 38, with the assistance of a compression spring 44 which is supported on the control body 38 and on the injection valve member 22, seals against a face 46 'of a mushroom-shaped discharge space body 46 facing it.
  • a discharge space 48 is formed by a longitudinal bore 16 coaxial longitudinal bore, without throttling constriction - which is aligned with the outlet passage 40 and with this flow directly connected.
  • the substantially circular cylindrical control body 38 is slidably mounted with a radial play of about 0.02 mm to 0.1 mm or 0.2 mm in a control sleeve 50 in the direction of the longitudinal axis 16 and forms a valve member together with the discharge chamber body 46, whose end face 46 'acts as a valve seat, an intermediate valve 52.
  • the control sleeve 50 at whose the injection valve seat 26 facing the end of the closing spring 24 is supported, is held by the force of this closing spring 24 on Abpoundraum stresses 46 in sealing engagement.
  • the injection valve member 22 is guided in close sliding fit with a game of about 2 microns to 10 microns.
  • the mushroom-shaped discharge space body 46 is sealingly against a by a, in an internal thread on the valve housing 14 einindeten retaining nut 54 with its hat part against a Ablageschulter 56 of the valve housing 14 pressed. Furthermore, the retaining nut 54 and the drainage space body 46 lie flat against one another in a sealing manner.
  • the stem part of the mushroom-shaped discharge chamber body 46 distributed in the circumferential direction, at least 2 high-pressure channels 58 are formed, on the one hand with a valve housing 14, the stem and the head portion of Ab Wegraum stressess 46 and the control sleeve 50 limited annular space 60 in fluid communication and the other on the other the valve seat of the intermediate valve 52 forming end face 46 'open.
  • the annular space 60 is connected to the high-pressure chamber 34 and thus to the high-pressure inlet 12 by a longitudinal groove 62, which extends in the axial direction and is integrally formed on the radially outer side of the control sleeve 50.
  • the high pressure channels 58 may, as in Fig. 1 and Fig. 2 shown to the right of the longitudinal axis 16, by oblique holes in the discharge chamber body 46 or, as in Fig. 2 shown to the left of the longitudinal axis 16, be generated by angular holes.
  • a recess 64 may be formed on the drainage space body 46, which ensures that the contact surface extends as a relatively narrow band-shaped area along the outer circumference of the control body 38 and around the mouths of the high-pressure channels 58.
  • corresponding recesses may be formed on the control body 38.
  • a pilot valve pin 66 slidably mounted in close sliding fit of about 2 microns to 10 microns in the direction of the longitudinal axis 16.
  • the drainage space body 46 forms an annular pilot valve seat 68, which forms a pilot valve 70 together with the pilot valve pin 66 as a valve member around the mouth side opening of the drainage space 48.
  • the pilot valve seat 68 is designed as a flat seat.
  • An annular relief chamber 72 directly adjoins the pilot valve seat 68 on the low-pressure side, which is formed on the retaining nut 54 serving as a relief space body as a recess running around the pilot valve pin 66.
  • This otherwise closed relief space 72 is permanently connected via a throttle passage 74 to a low-pressure outlet 76 of the valve housing 14. Fuel flowing out through the low-pressure outlet 76 is returned to a fuel storage container in a known manner.
  • Fig. 2 is shown in solid lines that the throttle passage 74 as an oblique bore in the pilot valve pin 66 or, as indicated by dashed lines, may be formed on the retaining nut 54.
  • the diameter of the throttle body 74 'of the otherwise larger diameter throttle passage 74 is for example about ten times smaller than the diameter of the pilot valve pin 66 and about five times smaller than the clear diameter of the discharge space 48. However, these ratios may be different. From Another advantage is that the pilot valve pin 66, when lifted from the pilot valve seat 68, very quickly releases a substantially larger flow cross-section than it is defined by the throttle point 74 '.
  • the pilot valve pin 66 is held in abutment with the pilot valve seat 68 by means of the actuator 18.
  • an actuator shaft 78 lies with its ball-shaped end on the pilot valve seat 68 facing away from the end face of the pilot valve pin 66 at this.
  • the actuator 18 is a piezoelectric or magnetostrictive actuator.
  • Such actuators 18 allow only a relatively small stroke of the Aktuatorschafts 78 and thus the pilot valve pin 66, for example, 0.03 mm. However, they have the advantage that they move the pilot valve pin 66 with great speed and great force.
  • the actuator 18 is arranged in an actuator housing 80, which projects into the valve housing 14 and is fastened thereto by means of a fastening screw 82.
  • the clearance between the control body 38 and the control sleeve 50 ensures that through this clearance and the outlet passage 40 the control chamber 36 is filled with fuel very quickly as soon as - to terminate an injection process by closing the pilot valve 70 - the control body 38 is out of its installation is moved away from the drainage space body 46.
  • the closing spring 24 bears against an intermediate disk 86, which in turn bears against a support disk 86 'which is supported on a shoulder of the injection valve member 22.
  • the intermediate disc 86 is replaceable in order to tune the behavior of the Brennstöffeinspritzventils 10 by selecting the desired thickness.
  • FIGS. 3 to 6 are used for the training according to FIGS. 1 and 2 corresponding parts use the same reference numerals as in FIG. 1 and FIG. 2 , In the following, only the differences between the embodiment shown in the relevant figure and those according to the FIGS. 1 and 2 explained.
  • the high-pressure passage 58 opens, as in the in the Fig. 2 and 3 shown embodiment, in the annular space 60, which is connected to the high-pressure chamber 34.
  • the recess 64 in the drainage space body 46 is annular formed so that radially inside a running around the mouth of the high-pressure passage 58 sealing surface and radially outside an annular sealing surface for cooperation with the control body 38 remains.
  • the outlet passage 40 extends obliquely with respect to the longitudinal axis 16 so that it opens into the annular space formed by the recess 64.
  • the discharge space 48 is formed by a bore oblique with respect to the longitudinal axis 16 through the discharge space body 46, the discharge space 48 opening into the recess 64 on the one hand and the mouth of the discharge space 48 being arranged on the side of the pilot valve 70 centric to the longitudinal axis 16.
  • the pilot valve pin 76 is in turn in the retaining nut 54, in which the discharge chamber 72 is excluded, mounted in close sliding fit.
  • the throttle passage 74 is formed on the pilot valve pin 66 by a blind hole from the actuator side, which - instead of a single throttle 94 '- by means of a radial first throttle bore 90 with the relief space 72 and a radial second throttle bore 90' with the low pressure outlet 76 in Flow connection is.
  • the diameter of these two throttle bores 90, 90 ' in comparison to the single throttle restriction 74' in the throttle passage 74 according to FIG. 1 and 2 , are slightly larger and therefore somewhat inaccurate, in order to achieve a corresponding throttle effect.
  • the cooperating with the pilot valve pin 66 end face of Aktuatorschafts 78 is flat to To seal the blind hole in the pilot valve pin 68.
  • control body 38 is similar to that according to Fig. 2 however, the throttle restriction 40 'of the outlet passage 40 is located in the end region facing the outflow chamber 48.
  • the otherwise circular-cylindrical outlet passage 40 has in its control-chamber-side end region a conical shape, in which the counter-shaped end portion of the injection valve member 22 engages when the injection valve member 22 is in the maximum open position. This leads to a very good sealing of the outlet passage 40 and contributes at the end of the injection process a very rapid lifting of the control body 38 from the injection valve body 28 and thus a very fast closing movement of the injection valve member 22 at.
  • FIG. 4 left or right of the longitudinal axis 16, two other possible embodiments for the high-pressure passage 58 shown. These are formed by bores in the discharge space body 46, which extend obliquely to the longitudinal axis 16 and communicate with the annular space 60, and by bores, which are in flow communication with the former and parallel or oblique to the longitudinal axis 16, but in that region on the front side 46 'open, which acts as a valve seat of the intermediate valve 52.
  • the drainage space body 46 is no longer mushroom-shaped but pill-shaped and pressed by means of the retaining nut 54 in sealing contact with the contact shoulder 56 of the valve housing 14. Further, the relief space 72 is disposed in the interior of the drain chamber body 46, on which also the pilot valve pin 66 is guided in close sliding fit. In this case, the drainage space body 46 also serves as a relief space body. The sealing of the high-pressure chamber 34 with respect to the low-pressure outlet 76 thus takes place by the sealing abutment of the discharge space body 46 on the abutment shoulder 56.
  • valve seats In addition to the valve seats, only these two interacting surfaces have to be designed with high precision, in contrast to the embodiments according to FIGS Figures 1 - 3 where also the abutting end faces of the discharge chamber body 46 and the retaining nut 54 are to be formed as sealing surfaces.
  • the pilot valve seat 68 When in the Fig. 4 training form shown is the pilot valve seat 68 and, thereafter, the relief chamber 72 by a conical extension - seen from the control body 38 forth - the drainage chamber 48 forming hole formed.
  • part of the pilot valve pin 66 Corresponding to the same the cooperating with the pilot valve seat 68 part of the pilot valve pin 66 is formed conically.
  • the relief space 72 in turn extends as an annular space around the pilot valve pin 66 around and the throttle passage 74 is formed as with respect to the longitudinal axis 16 oblique bore in the pilot valve pin 66, but now - in contrast to the embodiment according to the FIGS. 1 and 2 -
  • Throttle throat 74 ' located in the low pressure outlet 76 facing end portion of the throttle passage 44. Hydraulically, therefore, the volume of the throttle passage 74 upstream of the throttle restriction 74 'is part of the relief space 72.
  • the retaining nut 54 is formed to tighten with a hexagon socket, which at the same time surrounds the pilot valve pin 66 at a distance to form the flow connection between the throttle passage 74 and the low-pressure outlet 76.
  • Fig. 5 shows one of the Fig. 3 very similar form of training, the drainage space body 46 is no longer mushroom but pills shaped.
  • the annular space 60 extends around the overhead end region of the control sleeve 50.
  • the high-pressure channel 58 is formed by two bores running obliquely with respect to one another and with respect to the longitudinal axis 16. The one opens to the annular space 60 and the other in the middle of the end face 46 'of the discharge space body 46.
  • the throttle restriction 40 'of the outlet passage 40 at the recess 64 which is integrally formed on the control body 38.
  • non-inventive fuel injection valve 10 is the Outflow chamber 46 formed pills and centrally has the run-off in the axial direction of the drain chamber 48 but no high-pressure channel 58 on. With the drain space body 46, the pilot valve pin 66 cooperates, which as in Fig. 1 and Fig. 2 is shown formed.
  • the control body 38 is guided in the manner of a slide valve body in the control sleeve 50 in close sliding fit of about 2 microns to 10 microns.
  • the annular space 60 which is recessed radially on the inside of the control sleeve 50 extends around its end region facing the discharge space body 46 and is connected to the high-pressure space 34 via a radial passage and the longitudinal groove 62.
  • Concentric with the longitudinal axis 16 extends through the control body 38 through the outlet passage 40 with its throttle restriction 40 'at the control chamber 36 end facing. Parallel thereto, but offset radially with respect to the longitudinal axis 16, extends through the control body 38 through a connecting channel 94, which is closed when ab Wegraum Economics 46 Ab kgraum Economics control body 38.
  • connection channel 94 connects the control space 36 to the high-pressure space 34.
  • the connection channel 94 has the same function as in the embodiments shown above, the radial clearance between the control body 38 and the control sleeve 50th Next are on the control body 38, formed on the end face 42, inner and outer recesses 64, which serve to form the surface with which the control body 38 sealingly against the discharge chamber body 46, small in order to achieve a high surface pressure. Further, by a more or less large radially outer recess 64 the dynamic behavior of the control body 38 relative to lift-off from the installation on the discharge room body 46 can be varied.
  • Fig. 7 shows a non-inventive fuel injection valve 10, wherein the control body 38 is replaced by a leaf spring 96.
  • the leaf spring 96 is similar to that of EP-A-1 273 791 formed known leaf spring. From a disc of spring steel, a C- or U-shaped slot is excluded, which separates a radially inner leaf spring tongue 98 of a retaining ring 100.
  • the leaf spring 96 is held clamped with its retaining ring 100 between the control sleeve 50 and the drain chamber body 46. For radial alignment of the retaining ring 100 and the control sleeve 50 are jointly encompassed by a centering ring 102.
  • the throttle restriction 40 ' is formed on the leaf spring tongue 98, kozentrisch to the longitudinal axis 16 as a through hole.
  • the leaf spring tongue 98 closes when it concerns the discharge chamber body 46 both from the high-pressure passage 58 formed therein and from the discharge space 48 extending centrally with respect to the longitudinal axis 16.
  • a throttle admission 92 may be excluded, which connects the high-pressure chamber 34 with the discharge chamber 48.
  • the effect of this throttle admission 92 is the same as that of the throttle passage 92 of the embodiments according to Fig. 3 and 8th , namely In particular, when using an electromagnetic actuator 18 to support the rapid closing of the injection valve member for the completion of the injection process.
  • the retaining nut 54 with the relief space 72 and the pilot valve pin 66 with the first and second throttle bore 90, 90 ', and the actuator 18 with its actuator shaft 78 are formed the same as in the embodiment according to the Fig. 3 ,
  • the control body 38 is now mushroom-shaped and its trunk is slidably guided in a blind hole-like recess of the injection valve member 22 in the direction of the longitudinal axis 16.
  • the compression spring 44 is supported on the one hand at the bottom of this blind hole and on the other hand on the trunk of the control body 38.
  • the control sleeve 50 limits the control chamber 36, engages around the hat of the control body 38 with a radial distance and lies with its end face sealingly against the end face 46 'of the discharge space body 46.
  • the throttle restriction 40 ' is formed. It communicates with the annular recess 64 on the discharge chamber body 46 and thus communicates with the discharge space 48 in fluid communication.
  • a radial clearance is present between the stem of the mushroom-shaped control body 38 and the injection valve member 22, a radial clearance is present to achieve a rapid pressure equalization between the control chamber 36 and the space in which the compression spring 44 is arranged.
  • the actuator 18 pulls the actuator shaft 78 in the axial direction upwards, that is, in the direction away from the pilot valve seat 68. Since there is high pressure in the discharge space 48, the pilot valve pin .66 is lifted off the pilot valve seat 68 in accordance with the movement of the actuator shaft 78. This leads to a very rapid increase in pressure in the relief space 72 and a correspondingly rapid pressure reduction in the discharge space 48 and in the outlet passage 40 downstream of the throttle restriction 40 '. From the discharge space 72, the fuel flows through the throttle passage 74 attenuated to the low-pressure outlet 76. The throttle restriction 40 'attenuates the flow of fuel out of the control chamber 36. This leads to a pressure reduction in the control chamber 36, whereby the injection valve member 22 in a known manner is lifted from the injection valve seat 26.
  • the pilot valve pin 66 is moved very quickly by means of the actuator 18 down into abutment with the pilot valve pin 66, thereby closing the pilot valve 70. Since the pilot valve seat 68 very quickly dives deeper into the relief space 72, an increase in pressure generated, which propagates through the drainage chamber 48 and leads to the lifting of the control body 38, or the leaf spring tongue 98, from the drain chamber body 46, since a rapid pressure equalization in the control chamber 36 due to the throttle restriction 40 'can not be done. By lifting off the control body 38 immediately the entire end face 42 of the control body 38 is acted upon by fuel under high pressure, since the high pressure passage 58 and the high pressure passages 58 are released.
  • the fuel injection valve 10 comprises a pilot valve 70
  • the fuel losses caused thereby are small since, during the period in which the pilot valve 70 is open, in the embodiment according to FIGS Fig, 1 . 2 . 4 . 5 and 6 no hydraulic connection between the drainage chamber 48 and the high-pressure chamber 34 is made.
  • a throttle passage 92 is present; however, because of the very small cross-section, the throttle passage 92 prevents rapid outflow of a larger amount of fuel.
  • Piezoelectric and magnetostrictive actuators are therefore particularly suitable for fuel injectors 10 according to the invention because they can apply very large forces, so that said pressure increase practically does not delay the movement of the pilot valve pin 66.
  • the aforementioned actuators 18 have a faster switching behavior than electromagnets, such can be used.
  • Fig. 9 shown embodiment has, in addition to those in the context of the embodiments according to Fig. 1 to 8 shown benefits, increased ability for multiple injections in very short time intervals.
  • Fig. 9 the same reference numerals as used in connection with the Fig. 1 to 8 ,
  • the discharge space 72 is formed by a recess on the retaining nut 54 and it is through the throttle body 74 'and the throttle passage 74 in the retaining nut 54 permanently connected to the low-pressure chamber, in the same manner as in the Fig. 2 indicated by dashed lines.
  • the retaining nut 54 of the pill-shaped drainage chamber body 46 On the front side of the retaining nut 54 of the pill-shaped drainage chamber body 46 is sealingly. It has an axial passage centrally, which forms the discharge space 48.
  • the pilot valve pin 66 and the pilot valve seat 68 form the pilot valve 70 controlled by an actuator 18, which in the closed state separates the discharge chamber 48 from the discharge chamber 72 ,
  • the discharge space 48 is formed by a central bore which widens in the direction of the control body 38 in a funnel shape. This discharge space 48 is penetrated by a transfer pin 104 whose diameter is smaller than the diameter of the cylindrical portion of the discharge space 48 and whose length is greater than the measured in the direction of the longitudinal axis 16 thickness of Abpoundraum stressess 46.
  • the pilot valve 70 is closed thus the transfer pin 104 via the drainage space body 46 on the side facing away from the retaining nut 54 and the control body 38 side facing.
  • the high-pressure channel 58 is formed on the drainage space body 46, which is formed by a radial blind bore and one of the end face 46 'of the drainage space body 46 in FIG axial direction in the blind hole leading through hole is formed.
  • the high-pressure passage 58 opens at the end face 46 'at a distance from the discharge space 48, so that the control body 38, when resting against the end face 46', closes the mouth of the high-pressure passage 58.
  • the discharge space body 46 forms with its end face 46 'and the control body 38, in turn, an intermediate valve 52nd
  • an intermediate body 50' in the central passage of the control body 38 in the direction of the longitudinal axis 16 is slidably disposed. Between the control body 48 and the intermediate body 50 ', an annular gap is present.
  • the intermediate body 50 ' is cup-shaped, wherein the bottom of the discharge chamber body 46 faces, and in the interior of the control body 38 is a compression spring 44 which holds the control body 38 - with open pilot valve 70 - with the bottom of the transfer pin 104 in abutment.
  • Through the bottom of the control body 38 passes through the outlet passage 40, which is formed without throttle restriction 40 'and communicates with at the end face 46' fitting control body 38 with the discharge chamber 48. If the control body 38 is located on the front side 46 ', it closes the mouth of the high-pressure channel 58.
  • the bottom of the control body 38 is at a distance from the end face 46 'which is given by the difference in length between the transmission pin 104 and the thickness of the discharge space body 46.
  • the stroke of the pilot valve pin. 66 is at least as large, but preferably greater than this distance.
  • the compression spring 44 is supported with its end facing away from the bottom of the control body 38 at an end face of a control chamber body 50 '' from which sealingly bears with its end face on the intermediate body 50 '.
  • the control chamber body 50 '' circumferentially bounded the control chamber 36, which is also bounded by the injection valve member 22, which is guided on the control chamber body 50 '' in close sliding fit.
  • the injection valve member 22 is desaxsiert with respect to the common longitudinal axis 16.
  • the control space 36 is continuously throttled in flow communication with the interior of the cup-shaped control body 38 and the drainage space 48.
  • control chamber body 50 "and the retaining nut 54 are clamped against each other so that the retaining nut 54 on Abpoundraum stresses 46, this on the other hand on the intermediate body 50 ', and this in turn on the other hand control chamber body 50' 'sealingly.
  • the intermediate body 50 'and control chamber body 50 may be integrally formed in one piece, similar to the control sleeve 50. It is also conceivable to form the control chamber body 50" in one piece together with the injection valve seat body 28 or the valve housing 14.
  • Ableraumelasticity 46 may be an open towards the end 46 'annular groove 106 may be formed, in which the high pressure channel 58 opens and which is closed at the front side 46' abutting control body 38 of this.
  • control body 38 viewed in the direction of the longitudinal axis 16, shorter form, so that the shell portion of the cup protrudes only slightly above the bottom of the control body 38 to the end of the Comprise compression spring 44.
  • the control body 38 is formed as a disc with an outlet passage 40 and the spring formed as a compression spring 44 replaced by a plate spring or wave spring.
  • a coaxial arrangement of the injection valve member 22 with the longitudinal axis 16 is conceivable, wherein the compression spring 44 is supported for example on the end face of the control chamber body 50 '' or on a supporting shoulder formed thereon.
  • pilot valve pin 66 may have a shoulder cooperating with the retaining nut 54 to limit the stroke of the pilot valve pin 66 in the opening direction of the pilot valve 70.
  • fuel injector 10 operates as follows.
  • the pilot valve 70 is closed.
  • the control body 38 is lifted off the front side 46 'of the discharge space body 46, whereby the discharge space 48 and the control space 46 are connected to the high-pressure inlet 12 via the high-pressure passage 58.
  • the injection valve member 22 is in contact with the injection valve seat 26 in the closed position; see also Fig. 1 .
  • the actuator 18 retracts the actuator shaft 78, thereby moving the pilot valve pin 66 away from the pilot valve seat 68 and connecting the drain chamber 48 and thus the control chamber 36 to the discharge chamber 72.
  • the extremely fast movement of the pilot valve pin 66 follows the transmission pin 104 and the control body 38, with the result that the intermediate valve 52 is closed very quickly and a subsequent flow of fuel through the high-pressure passage 58 is prevented.
  • the pressure drop in the control chamber 36 and thus a lifting of the injection valve member 22 from the injection valve seat 26 are made very quickly.
  • the pilot valve pin 66 is brought into contact with the pilot valve seat 68 by means of the actuator 18 in a known manner.
  • the transmission pin 104 is moved in the direction against the control body 38 which inevitably lifts off the end face 46 '.
  • the intermediate valve 52 opens and is formed by the high-pressure passage 58, a connection between the control chamber 36 and the high-pressure inlet 12. Further, this pressure increase is supported by the movement of the pilot valve pin 66 into the discharge chamber 72 inside.
  • the injection valve member 22 is thus very quickly brought into abutment with the injection valve seat 26 whereby the injection process is completed.
  • control body 38 moves with the transmission pin 104 and thus with the pilot valve pin 66, the high-pressure passage 58 is closed or opened very quickly by the control body 38, which results in several Injections in short to very short time intervals is of great advantage.

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)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Claims (13)

  1. Soupape d'injection de carburant pour l'injection intermittente de carburant dans la chambre de combustion d'un moteur à combustion interne, comprenant un boîtier de soupape (14) présentant un alésage (17) s'étendant dans la direction de son axe longitudinal (16) et comprenant un siège de soupape d'injection (26), qui limite une chambre haute pression (34) connectée à une entrée haute pression (12) du boîtier de soupape (14), la chambre haute pression étant d'autre part limitée par un dispositif de commande hydraulique (20) disposé dans l'alésage (17) et commandé par un actionneur, et, du côté périphérique, par le boîtier de soupape (14), et comprenant également un organe de soupape d'injection (22) disposé dans la chambre haute pression (34), en forme d'aiguille; coopérant avec le siège de soupape d'injection (26), le dispositif de commande (20) présentant un manchon de commande (50) qui sépare hermétiquement, du côté périphérique, une chambre de commande (36) de la chambre haute pression (34) et dans lequel l'organe de soupape d'injection (22) est guidé avec ajustement glissant serré, avec sa région d'extrémité opposée au siège de soupape d'injection (22), en limitant la chambre de commande (36), le manchon de commande (50) étant maintenu sur un corps de la chambre d'évacuation (46) en appui hermétique, un corps de commande (38) limitant la chambre de commande (36) étant monté dans le manchon de commande (50) de manière à pouvoir coulisser avec un jeu radial dans la direction axiale, le jeu radial formant une connexion fluidique entre l'entrée haute pression (12) et la chambre de commande (36), et le corps de commande (38) formant, en tant qu'organe de soupape, conjointement avec le corps de la chambre d'évacuation (46), dont le côté frontal (46') sert de siège de soupape, une soupape intermédiaire (52) du dispositif de commande (20), afin de fermer, de manière libérable, au moins un canal haute pression (58) s'étendant à travers le corps de la chambre d'évacuation (46).
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce qu'une chambre d'évacuation (48) en liaison avec la chambre de commande (36) et conduisant à un siège de soupape pilote (68) d'une soupape pilote (70) est formée dans le corps de la chambre d'évacuation (46).
  3. Soupape d'injection de carburant selon la revendication 2, caractérisée en ce que la chambre de commande (36) est en connexion fluidique avec la chambre d'évacuation (48) par le biais d'un étranglement (40') dans le corps de commande (38).
  4. Soupape d'injection de carburant selon la revendication 3, caractérisée en ce que le corps de commande (38) présente un passage de sortie (40) qui est muni de l'étranglement (40').
  5. Soupape d'injection de carburant selon la revendication 4, caractérisée en ce que l'étranglement (40') du passage de sortie (40) est réalisé soit dans une région d'extrémité du côté du corps de la chambre d'évacuation soit dans une région d'extrémité du côté de la chambre de commande du corps de commande (38).
  6. Soupape d'injection de carburant selon la revendication 4 ou 5, caractérisée en ce que le passage de sortie (40) et la chambre d'évacuation (48) sont réalisés en forme de cylindre et leurs axes de cylindre sont orientés soit tous les deux coaxialement soit tous les deux obliquement par rapport à l'axe longitudinal (16).
  7. Soupape d'injection de carburant selon l'une quelconque des revendications 2 à 6, caractérisée par une entrée étranglée (92), qui relie la chambre d'évacuation (48) à l'entrée haute pression (12).
  8. Soupape d'injection de carburant selon l'une quelconque des revendications 2 à 7, caractérisée en ce que du côté du corps de commande, au niveau de la chambre d'évacuation (48) du corps de la chambre d'évacuation (46), ou du côté du corps de la chambre d'évacuation au niveau du passage de sortie (40) du corps de commande (38) est façonné un évidement (64).
  9. Soupape d'injection de carburant selon l'une quelconque des revendications 2 à 8, caractérisée en ce que lorsque la soupape intermédiaire (52) est ouverte, le jeu radial du corps de commande (38) dans le manchon de commande (50) forme la connexion fluidique entre l'entrée haute pression (12) et la chambre de commande (36).
  10. Soupape d'injection de carburant selon l'une quelconque des revendications 2 à 9, caractérisée en ce que le manchon de commande (50) présente un épaulement de limitation de course (84) pour le corps de commande (38).
  11. Soupape d'injection de carburant selon l'une quelconque des revendications 2 à 10, caractérisée en ce qu'un ressort de pression (44) maintient en appui de manière soulevable le corps de commande (38) contre le corps de la chambre d'évacuation (46).
  12. Soupape d'injection de carburant selon l'une quelconque des revendications 2 à 11, caractérisée en ce que la soupape pilote (70) présente une tige de soupape pilote (66) coopérant d'une part avec un actionneur (18) commandé électriquement et d'autre part avec le siège de soupape pilote (68), la tige de soupape pilote (66) séparant dans la position de fermeture, la chambre de commande (36) du dispositif de commande (20) d'une sortie basse pression (76), et en ce qu'une chambre de décharge fermée (72) se raccorde au niveau du siège de soupape pilote (68), sur son côté tourné vers la sortie basse pression (76), cette chambre de décharge (72) étant connectée de manière durable à la sortie basse pression (76) au moyen d'un passage étranglé (74) et pénétrant dans la tige de soupape pilote (66).
  13. Soupape d'injection de carburant selon la revendication 12, caractérisée en ce que la tige de soupape pilote (66) est guidée, dans le corps de limitation (54) en ajustement glissant, de préférence suivant un ajustement glissant serré.
EP04738118A 2003-08-22 2004-07-30 Soupape d'injection de carburant commandee par une soupape pilote Active EP1656498B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH14422003 2003-08-22
PCT/CH2004/000478 WO2005019637A1 (fr) 2003-08-22 2004-07-30 Soupape d'injection de carburant commandee par une soupape pilote

Publications (2)

Publication Number Publication Date
EP1656498A1 EP1656498A1 (fr) 2006-05-17
EP1656498B1 true EP1656498B1 (fr) 2008-11-26

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EP04738118A Active EP1656498B1 (fr) 2003-08-22 2004-07-30 Soupape d'injection de carburant commandee par une soupape pilote

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Country Link
EP (1) EP1656498B1 (fr)
AT (1) ATE415554T1 (fr)
DE (1) DE502004008540D1 (fr)
WO (1) WO2005019637A1 (fr)

Cited By (5)

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Publication number Priority date Publication date Assignee Title
WO2011122051A1 (fr) * 2010-03-31 2011-10-06 株式会社デンソー Dispositif d'injection de carburant
JP2011226458A (ja) * 2010-03-31 2011-11-10 Denso Corp 燃料噴射装置
US20120152206A1 (en) * 2010-12-17 2012-06-21 Denso Corporation Fuel injection device
JP2012127329A (ja) * 2010-12-17 2012-07-05 Denso Corp 燃料噴射装置
DE102012100020A1 (de) 2011-01-07 2012-07-12 Denso Corporation Kraftstoffeinspritzvorrichtung

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DE102005026967B4 (de) * 2005-06-10 2014-09-25 Siemens Aktiengesellschaft Ventil, insbesondere Servoventil
CH697562B1 (de) * 2005-08-09 2008-11-28 Ganser Hydromag Brennstoffeinspritzventil.
JP5110321B2 (ja) * 2006-03-03 2012-12-26 ガンサー−ハイドロマグ アーゲー 内燃機関用燃料噴射バルブ
JP5493966B2 (ja) * 2009-06-02 2014-05-14 株式会社デンソー 燃料噴射装置
DE102009039609A1 (de) * 2009-09-01 2011-03-03 Continental Automotive Gmbh Injektorbaugruppe mit Drosselelement
JP5152220B2 (ja) 2010-02-18 2013-02-27 株式会社デンソー 燃料噴射装置
JP5327117B2 (ja) * 2010-03-24 2013-10-30 株式会社デンソー 燃料噴射装置
DE102011078399A1 (de) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Kraftstoffinjektor
DE102012202546A1 (de) * 2012-02-20 2013-08-22 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102012202549A1 (de) * 2012-02-20 2013-08-22 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102012010614B4 (de) * 2012-05-30 2014-07-03 L'orange Gmbh Injektor
DE102012212614A1 (de) * 2012-07-18 2014-01-23 Continental Automotive Gmbh Piezoinjektor mit hydraulisch gekoppelter Düsennadelbewegung
DE102012222509A1 (de) 2012-12-07 2014-06-12 Continental Automotive Gmbh Piezoinjektor
DE102012223934B4 (de) 2012-12-20 2015-10-15 Continental Automotive Gmbh Piezoinjektor
EP2961977B1 (fr) 2013-03-01 2017-06-21 Ganser-Hydromag AG Dispositif pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion
WO2016208130A1 (fr) * 2015-06-26 2016-12-29 株式会社デンソー Injecteur
JP6256440B2 (ja) * 2015-06-26 2018-01-10 株式会社デンソー インジェクタ
US11255306B2 (en) 2017-10-20 2022-02-22 Cummins Inc. Fuel injector with flexible member
DE102018107238A1 (de) * 2018-03-27 2019-10-02 Liebherr-Components Deggendorf Gmbh Injektor zum Einspritzen von Kraftstoff
DE102018109206A1 (de) 2018-04-18 2019-10-24 Liebherr-Components Deggendorf Gmbh Injektor zum Einspritzen von Kraftstoff
WO2020260285A1 (fr) 2019-06-25 2020-12-30 Ganser Hydromag Ag Soupape d'injection de carburant pour des moteurs à combustion interne
JP2023504727A (ja) * 2019-12-03 2023-02-06 ガンサー－ハイドロマグ アーゲー 内燃機関用スライド弁を有する燃料噴射弁

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DE10100390A1 (de) * 2001-01-05 2002-07-25 Bosch Gmbh Robert Einspritzventil
EP1273791A3 (fr) * 2001-07-03 2003-03-12 CRT Common Rail Technologies AG Soupape d'injection de combustible pour moteurs à combustion interne

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Publication number Priority date Publication date Assignee Title
WO2011122051A1 (fr) * 2010-03-31 2011-10-06 株式会社デンソー Dispositif d'injection de carburant
JP2011226459A (ja) * 2010-03-31 2011-11-10 Denso Corp 燃料噴射装置
JP2011226458A (ja) * 2010-03-31 2011-11-10 Denso Corp 燃料噴射装置
CN102472211A (zh) * 2010-03-31 2012-05-23 株式会社电装 燃料喷射设备
DE102011001563A1 (de) 2010-03-31 2014-03-06 Denso Corporation Kraftstoffeinspritzvorrichtung
CN102472211B (zh) * 2010-03-31 2014-10-01 株式会社电装 燃料喷射设备
US20120152206A1 (en) * 2010-12-17 2012-06-21 Denso Corporation Fuel injection device
DE102011056406A1 (de) 2010-12-17 2012-06-21 Denso Corporation Brennstoffeinspritzvorrichtung
JP2012127329A (ja) * 2010-12-17 2012-07-05 Denso Corp 燃料噴射装置
US9109556B2 (en) * 2010-12-17 2015-08-18 Denso Corporation Fuel injection device
DE102012100020A1 (de) 2011-01-07 2012-07-12 Denso Corporation Kraftstoffeinspritzvorrichtung

Also Published As

Publication number Publication date
ATE415554T1 (de) 2008-12-15
EP1656498A1 (fr) 2006-05-17
WO2005019637A1 (fr) 2005-03-03
DE502004008540D1 (de) 2009-01-08

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