EP1416152B1 - Soupape pour le contrôle des fluides avec alimentation d'un fluide sous pression - Google Patents

Soupape pour le contrôle des fluides avec alimentation d'un fluide sous pression Download PDF

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Publication number
EP1416152B1
EP1416152B1 EP20030021080 EP03021080A EP1416152B1 EP 1416152 B1 EP1416152 B1 EP 1416152B1 EP 20030021080 EP20030021080 EP 20030021080 EP 03021080 A EP03021080 A EP 03021080A EP 1416152 B1 EP1416152 B1 EP 1416152B1
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EP
European Patent Office
Prior art keywords
valve
pressure
control space
piston
valve according
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
EP20030021080
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German (de)
English (en)
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EP1416152A1 (fr
Inventor
Wolfgang Stoecklein
Dietmar Schmieder
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • F02M57/026—Construction details of pressure amplifiers, e.g. fuel passages or check valves arranged in the intensifier piston or head, particular diameter relationships, stop members, arrangement of ports or conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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

Definitions

  • the invention relates to a valve for controlling fluids with a pressure medium supply according to the closer defined in the preamble of claim 1.
  • Valves of the aforementioned type are known in practice and have a pressure booster for compressing fuel from a supply pressure to an injection pressure.
  • the pressure transmission is carried out with pressure-translated chambers, which are combined with other components for pressure transmission and for injecting fuel into a combustion chamber of an internal combustion engine.
  • a valve of a pressure fluid reservoir or a pressure medium source in particular a common rail area, fuel with a supply pressure or a rail pressure over fed to a pressure medium supply.
  • the supplied with feed pressure fuel is compressed to a high pressure and injected with the valve open with the high pressure in the combustion chamber of an internal combustion engine.
  • the pressure intensification has a piston system which can be actuated via a control valve and with which the high pressure or injection pressure is generated as required.
  • the high pressure is in the region of an injection nozzle of the valve.
  • a control of the control valve is preferably carried out via a piezoelectric actuator, which forms part of an actuator of the valve.
  • the injection nozzle and the pressure ratio of the valve are spatially separated and must be connected via holes and channels in the valve housing with each other in order to lead the high-pressure fuel from the pressure ratio to the injector can.
  • the holes and channels are phased with the compressed to high pressure fuel, so that the valve body and other the channels and holes having components of the valve must be designed high-strength, which disadvantageously requires higher component wall thicknesses and also causes a high sealing effort between individual components of the valve ,
  • the valve according to the invention for controlling fluids with the features of claim 1 has the advantage that on the holes used in practice and channels for guiding the compressed at high pressure or injection pressure fuel from a pressure intensification in an area from which the Fuel is injected into a combustion chamber of an internal combustion engine through the nozzle body through the valve, can be largely dispensed with.
  • the function of the injection nozzle and the high pressure generating pressure ratio is combined in a structurally compact unit, so that leakage, which have a negative effect on the injection behavior of a valve for controlling fluids, are minimized.
  • FIG. 1 a first embodiment of a valve 1 for controlling fluids with a pressure medium supply 2 and a valve element 3 for controlling a pressure in a high-pressure region 4 is shown.
  • the valve element 3 is arranged in a control chamber 5, which has two valve seats 6, 7 cooperating with the valve element 3.
  • the control chamber 5 is separated from a low-pressure region 8 of the valve 1.
  • This position of the valve element 3 is in the FIG. 1 illustrated, wherein the valve element 3 then rests against the first valve seat 6, when an actuation of the valve element 3 is omitted by the designed as a piezoelectric actuator control and the valve element 3 is pressed by a spring force of a spring 9 against the first valve seat 6.
  • the control element which may for example also be embodied as an electromagnetic drive system, is arranged on the side of the first valve seat 6 facing away from the control chamber 5.
  • the valve element 3 When the control element is energized, the valve element 3 is lifted off the first valve seat 6, as a result of which the control chamber 5 is connected to the low-pressure region 8. Furthermore, the valve member 3 is sealingly pressed against the second valve seat 7, so that the control chamber 5 is separated from a valve control chamber 10. Since the control chamber 5 is connected to the pressure medium supply 2, the valve control chamber 10 is also separated from the pressure medium supply 2 when the valve element 3 rests against the second valve seat 7.
  • the first valve seat 6 is in the present case designed as a conical seat, and cooperating with the first valve seat 6 sealing surface 11 of the valve element 3 is designed spherical or spherical segment, so that upon contact of the valve element 3 to the first valve seat 6 between the first valve seat 6 and the Sealing surface 11 is a line contact.
  • the second valve seat 7 is designed as a flat surface of a control chamber 5 limiting member 42 which cooperates with a likewise flat surface or end face 12 of the valve member 3.
  • This configuration of the two valve seats 6, 7 and the sealing surfaces 11, 12 of the valve element 3 ensures that a production-related axial offset of the first valve seat 6 against a the control chamber 5 and the valve control chamber 10 connecting channel 13 does not affect the sealing effect of the valve element 3. Furthermore, it is ensured that at a successful in the axial direction of the valve 1 actuation of the valve element 3, an offset of the valve member 3 transversely to the direction of movement of the valve element 3 between the two valve seats 6 and 7 is omitted, so that a delay-free control of the valve 1 is ensured ,
  • the valve control chamber 10 is delimited by a valve plate 14 and a piston 15 of a pressure transmission, wherein the piston 15 rests with its valve plate 14 facing end face 16 on the valve plate 14.
  • the end face 16 of the piston 15 is designed in such a spherical shape that the channel 13, which represents the connection between the valve control chamber 10 and the control chamber 5, is not closed by the piston 15 when it rests against the valve plate 14.
  • the piston 15 is in this case made in two parts and consists of a first with a larger diameter partial piston 17 and a second executed with a smaller diameter partial piston 18.
  • the first partial piston 17 is designed with a central blind hole 19, in which the second partial piston 18 is inserted , Furthermore, the second part piston 18 is inserted into a spacer sleeve 20 which is pressed against a nozzle needle 23 of the valve 1 via a second spring 22 arranged between a collar 21 of the second part piston 18 and the spacer sleeve 20.
  • the collar 21 is formed at that end of the second piston 18, which is pressed by the second spring 22 against the bottom of the blind hole 19 of the first part piston 17. With its end facing away from the collar 21 of the second part of piston 18 is guided axially movable in a guide bore 24 of the nozzle needle 23.
  • the second partial piston 18 is formed with a central through-bore 25 which is closed at the end of the collar 21 by the first partial piston 17 and at the end remote from the first partial piston 17 of the second partial piston 18 opens into the guide bore 24.
  • the guide bore 24 is adjoined by a connecting channel 26 formed coaxially with the latter in the nozzle needle 23 on, which is connected via a tap hole 27 with an annular space 28.
  • the annular space 28 is delimited by a nozzle body 29 and the nozzle needle 23.
  • the nozzle needle 23 bears against a sealing seat 30 of the nozzle body 29, so that several injection openings 31 of the nozzle body 29 distributed over the circumference of the nozzle body 29 are closed by the nozzle needle 23.
  • the nozzle needle 23 is axially longitudinally movable and sealingly guided in the nozzle body 29 via a first guide region 32 and a second guide region 33, wherein a needle control chamber 34 defined by the nozzle needle 23 and the nozzle body 29 is formed between the first guide region 32 and the second guide region 33.
  • the needle control chamber 34 is connected via a in the nozzle body 29, a valve body 35 and the valve plate 14 extending connecting line 36 with the pressure medium supply 2.
  • the needle control chamber 34 is sealed via the first guide region 32 with respect to a longitudinal bore 37 of the valve body 35, in which the first sub-piston 17 and the second sub-piston 18 are arranged.
  • the needle control chamber 34 is sealed via the second guide region 33 with respect to the annular space 28, wherein depending on the existing pressure conditions in the valve 1 leakage flows from the needle control chamber 34 in the direction of the annular space 28 and the longitudinal bore 37 or in the opposite direction.
  • the longitudinal bore 37 of the valve body 35 is permanently connected via a in the nozzle body 35, the valve plate 14 and a valve housing 38 extending further connecting channel 39 with the control chamber 5.
  • connection between the pressure medium supply 2 and the control chamber 5 is designed with an inlet throttle 40 and an outlet throttle 41, wherein the connecting line 36 branches off in the direction of the needle control chamber 34 between the inlet throttle 40 and the outlet throttle 41.
  • a pressure of the control chamber 5 adjusts itself as a function of the throttling action of the outlet throttle 41, which in turn is smaller than the intermediate pressure level. It follows that the pressure in the valve control chamber 10 and the pressure in the longitudinal bore 37 at installation of the valve element 3 at the first valve seat 6 is the same size, whereas the pressure in the needle control chamber 34 due to the branch of the connecting line 36 before the outlet throttle 41 is greater than the pressure in the valve control chamber 10 is.
  • FIG. 1 illustrated embodiment when using the inventive Valve described in a fuel injection valve 1 for internal combustion engines of motor vehicles, wherein the fuel injection valve 1 is designed in the present embodiment as a common rail injector.
  • the valve element 3 is actuated via the control designed as a piezoelectric actuator, which is arranged on the valve control chamber and combustion chamber side facing away from the valve element 3.
  • the piezoelectric actuator not shown, is constructed in a conventional manner of several ceramic layers and has on its valve member 3 side facing an actuator head and on its side facing away from the valve element 3 an actuator, which is located on a wall of the valve housing 38th supported.
  • the pressure of the valve control chamber 10 corresponds approximately to the pressure in the longitudinal bore 37 and the spring force of the second Spring 22 and the pressure and the area ratios of the needle control chamber 34, the annular space 28, the piston 15 and the nozzle needle 23 are matched to each other, the fuel injection valve 1 is closed, and the piston 15 and the first part piston 17 abuts with its end face 16 the valve plate 14 at.
  • the high-pressure area 4 bounded by the annular space 28, the tap hole 27, the connecting channel 26, the guide bore 24 and the through-bore 25 of the second partial piston 18 has its largest volume.
  • the high-pressure region 4 is filled with fuel, which has approximately the pressure level of the longitudinal bore 37.
  • valve element 3 is lifted from the first valve seat 6 and pressed sealingly against the second valve seat 7. In this position of the valve element 3rd is the pressure medium supply 2, the needle control chamber 34 and the longitudinal bore 37 connected via the control chamber 5 with the low pressure region 8. At the same time the valve control chamber 10 is closed due to the system of the valve element 3 to the second valve seat 7 relative to the control chamber 5, so that in the valve control chamber 10 is still approximately the pressure level of the control chamber 5 before opening the first valve seat 6. This results in a pressure gradient between the valve control chamber 10 and the longitudinal bore 37.
  • An area ratio between the end face 16 and on the side facing away from the end face 16 of the first part piston 17 effective surfaces of the piston 15 leads in combination with the pressure gradient between the valve control 10 and the longitudinal bore 37 to a lifting of the first part piston 17 of the valve plate 14 in the direction This in turn results in a displacement of the second part piston 18 in the direction of the nozzle needle 23, which leads to a reduction in the volume of the high-pressure region 4.
  • the fuel located in the high pressure area 4 is compressed to a defined high pressure.
  • the high pressure is applied to a further active surface 43 of the nozzle needle 23 and, together with the pressure of the needle control chamber 34, which also acts in the opening direction of the nozzle needle 23 to open the valve 1. That is, from reaching the defined high pressure in the high-pressure region 4 or in the annular space 28, the nozzle needle 23 is lifted from the sealing seat 30.
  • fuel is injected via the injection openings 31 in a combustion chamber, not shown, of an internal combustion engine and reduced the high pressure in the high pressure region 4.
  • the energization of the piezoelectric actuator is interrupted and the elongation of the piezoelectric ceramic is formed back.
  • the valve element 3 lifts off from the second valve seat 7 and is pressed sealingly against the first valve seat 6.
  • the pressure level of the longitudinal bore 37 increases such that the piston 15 is pressed against the valve plate 14 again.
  • the nozzle needle 23 is pressed against the sealing seat 30 due to the force relationships.
  • the needle control chamber 34 is emptied via the inlet throttle 40 and the outlet throttle 41, whereby a fast needle closure is ensured.
  • the arrangement of the inlet throttle 40 and the outlet throttle 41 it is possible, depending on the throttling action of the two throttles 40, 41 tune a Nadelhubverlauf so that the nozzle needle 23 opens under high pressure or injection pressure at a defined speed and then quickly closes. For a precise injection with an exactly adjustable injection amount of fuel is feasible.
  • a closing speed of the nozzle needle is essentially determined by the throttling action of both throttles, wherein an increasing throttling action reduces the closing speed.
  • valve according to the invention results in a reduction in the volume of the high-pressure region of the fuel injection valve, which advantageously counteracts strength problems.
  • the fuel injection valve according to the invention has the advantages of a fuel injection valve with pressure transmission, namely that a supply pressure can be substantially smaller than the injection pressure generated only in the valve itself, whereby a pressure medium supply must not be performed with the same strength as the pressure translation system itself.
  • FIGS. 2 . 3 and 4 represent three further embodiments of the valve according to the invention Figures 2 . 3 and 4 illustrated embodiments of the in FIG. 1 illustrated embodiment in each case only in some areas, which is why in the following description and in the FIGS. 2 to 4 for identically constructed and functionally identical components, the same reference numerals are used.
  • FIG. 2 illustrated embodiment of the fuel injection valve 1 differs from the in FIG. 1 illustrated embodiment of the fuel injection valve 1 by a arranged in the region of the contact surface between the first partial piston 17 and the second partial piston 18 filling valve 44, which is to ensure a filling of the high-pressure region 4 with fuel safely.
  • the filling should be ensured even if a theoretically sufficient pressure gradient between the high pressure region 4 and the longitudinal bore 37 of the valve body 35 should not lead to a sufficient filling of the high pressure region 4 starting from the longitudinal bore 37.
  • the filling valve 44 opens from a certain Pressure gradient between the valve control chamber 10 and the high pressure area 4 and remains open until a closing pressure in the high pressure area 4 is reached.
  • the filling valve 44 embodied as a check valve blocks the high-pressure region 4 with respect to the valve control chamber 10, so that the above-described pressure build-up in the high-pressure region is reliably ensured by displacement of the piston 15 in the direction of the nozzle needle 23.
  • the high pressure area 4 in the in FIG. 1 described manner with respect to the longitudinal bore 37 sealed. The sealing effect at the contact point between the first partial piston 17 and the second partial piston 18 is achieved by a sufficiently high acting on the second partial piston 18 contact pressure.
  • FIG. 2 illustrated embodiment of the fuel injection valve 1 according to the invention be carried out to the effect that the piston 15 is a one-piece stepped piston.
  • the first sub-piston 17 and the second sub-piston 18 are integrally formed or firmly connected to each other, whereby a filling of the high-pressure region is not provided starting from the longitudinal bore of the valve body and the high-pressure region only starting from the valve control chamber by opening and closing the Filling valves is controlled.
  • fuel injection valve For further operation of the in FIG. 2 shown fuel injection valve is based on the description of Fuel injection valve according to FIG. 1 referred to, since this is the same except for the additional filling of the high pressure area 4 via the filling valve 44.
  • FIG. 3 illustrated embodiment of the fuel injection valve 1 differs essentially from the in FIG. 2 illustrated embodiment in that the filling valve 44 is not disposed on the abutment region between the first part piston 17 and the second part piston 18 facing the end of the first part piston 17, but that the filling valve 44 is integrated in the mouth region of the through hole 25 in the guide bore 24.
  • This measure results in that the volume of the high pressure area 4 in comparison to the embodiments according to FIG. 1 and FIG. 2 is reduced, whereby the above-described advantages of the fuel injection valve according to the invention are even more significant.
  • a valve closing member 45 of the filling valve 44 designed as a check valve and a closing spring 47 pressing the valve closing member 45 against a valve seat 46 are arranged in the through bore 25 and positioned by a disc 48 welded to the second partial piston 18 after assembly of the valve closing member 45 and the closing spring 47.
  • the disc 48 is provided with a central bore 49 for guiding fuel into the high pressure region 4.
  • the through-bore 25 of the second partial piston 18 is provided with a diameter constriction in the region of the valve-sealing seat 46, whereby pressure fluctuations in the longitudinal bore acting on the filling valve 44 37 and thus smoothed in the through hole 25.
  • the operation of the fuel injection valve 1 according to the in FIG. 3 illustrated embodiment corresponds substantially to the operation of the in FIG. 2 Therefore, to the description of the operation of the fuel injection valve to FIG. 1 and 2 is referenced.
  • FIG. 4 is a further embodiment of the fuel injection valve 1 is shown, the basic structural design substantially according to the embodiment according to FIG. 1 equivalent.
  • the fuel injection valve according to FIG. 4 However, without connection between the pressure medium supply 2 and the needle control chamber 34 and without in the FIGS. 1 . 2 and 3 illustrated throttles 40 and 41 executed.
  • the fuel injection valve 1 according Fig. 4 compared to the embodiments according to FIG. 1 . 2 and 3 a simplified embodiment, but the injection behavior is not adjustable in the differentiated manner, as in the embodiments of the FIGS. 1 to 3 the case is that the inlet throttle 40 and the outlet throttle 41 have. This results from the fact that the opening behavior of the fuel injection valve according FIG. 4 can only be influenced via a throttle effect of a breakthrough 50.
  • the aperture 50 is provided in the nozzle needle 23 to ensure delivery or discharge of fuel into the needle control chamber 34 and out of the needle control chamber 34, respectively, and provides communication between the needle control chamber 34 and the high pressure region 4 in the region of the connection channel 26 ago.
  • valve element 3 As shown in FIG. 4 is the valve element 3 at the first valve seat 6 and the nozzle needle 23 at the sealing seat 30 at. If the first valve seat 6 is released from the valve element 3 and the second valve seat 7 is closed by the valve element 3, the piston 15 is displaced in the direction of the nozzle needle 23, the fuel present in the high-pressure region 4 being compressed to high pressure. At the same time, the pressure in the needle control chamber 34 increases in accordance with the throttling effect of the opening 50.
  • the nozzle needle 23 lifts in the direction of the valve plate 14 from the sealing seat 30, and the fuel present in the high-pressure region 4 or in the annular space 28 is introduced into a combustion chamber via the injection openings 31 an internal combustion engine injected.
  • valve element 3 is in turn sealingly applied to the first valve seat 6, whereby the piston 15 is displaced back to the valve plate 14 in the manner described above.
  • the nozzle needle 23 is pressed sealingly against the sealing seat 30, wherein the volume of the needle control chamber 34 is reduced.
  • the excess fuel of the needle control chamber 34 is via the opening 50 in the high pressure area 4 pressed.
  • the closing speed of the nozzle needle 23 is therefore dependent on the throttling effect of the opening 50 and variable via a change in the throttle effect.
  • the high-pressure region 4 is thus filled after completion of the injection on the one hand via the longitudinal bore 37 and in addition with excess fuel of the needle control chamber 34 via the opening 50.
  • the fuel injection valve according to the in FIG. 4 illustrated embodiment with a filling valve in the in the Figures 2 and 3 to be provided in the manner described.
  • the filling valve in the in FIG. 2 or in FIG. 3 be shown positions or arranged in any intermediate positions.

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

Claims (14)

  1. Soupape (1) pour commander des liquides, avec une alimentation en fluide sous pression (2), avec un élément de soupape (3) pour commander une pression dans une région de haute pression (4), avec un élément de commande pour actionner l'élément de soupape (3) et avec une multiplication de pression au moyen de laquelle le fluide sous pression alimenté par le biais de l'alimentation en fluide sous pression (2) peut être comprimé d'une pression d'alimentation à une haute pression, la multiplication de pression présentant au moins un piston (15) disposé de manière déplaçable longitudinalement dans un corps de soupape (35), et la région de haute pression (4) étant limitée au moins en partie par un corps d'injecteur (29) et une aiguille d'injecteur (23) disposée de manière déplaçable longitudinalement dans celui-ci, qui ferme hermétiquement des ouvertures d'injection (31) du corps d'injecteur (29) lors de l'application contre un siège d'étanchéité (30), caractérisée en ce que le piston (15) de la multiplication de pression est guidé au moins en partie de manière déplaçable longitudinalement dans l'aiguille d'injecteur (23) et une partie de la région de haute pression (4) est limitée en outre à l'intérieur de l'aiguille d'injecteur (23) par celle-ci et par la partie du piston (15) qui est guidée dans l'aiguille d'injecteur (23).
  2. Soupape selon la revendication 1, caractérisée en ce que le piston (15) est réalisé sous forme de piston étagé.
  3. Soupape selon la revendication 1 ou 2, caractérisée en ce que le piston (15) est réalisé en deux parties.
  4. Soupape selon l'une quelconque des revendications 1 à 3, caractérisée en ce qu'un élément élastique (22) est disposé entre le piston (15) et l'aiguille d'injecteur (23).
  5. Soupape selon l'une quelconque des revendications 1 à 4, caractérisée en ce que l'élément de soupape (3) est disposé dans un espace de commande (5) qui présente deux sièges de soupape (6, 7) coopérant avec l'élément de soupape (3).
  6. Soupape selon la revendication 5, caractérisée en ce que l'espace de commande (5) est connecté à chaque fois à l'alimentation en fluide sous pression (2), à une région de basse pression (8) et à un espace de commande de soupape, la connexion de l'espace de commande (5) à la région de basse pression (8) étant fermée lors de l'application de l'élément de soupape (3) contre le premier siège de soupape (6), et les connexions de l'espace de commande à l'espace de commande de soupape (10) et à l'alimentation en fluide sous pression (2) étant ouvertes.
  7. Soupape selon la revendication 5 ou 6, caractérisée en ce que les connexions de l'espace de commande (5) à la région de basse pression (8) et à l'alimentation en fluide sous pression (2) sont ouvertes lors de l'application de l'élément de soupape (3) contre le deuxième siège de soupape (7) et la connexion de l'espace de commande (5) à l'espace de commande de soupape (10) est fermée.
  8. Soupape selon l'une quelconque des revendications 5 à 7, caractérisée en ce que l'espace de commande de soupape (10) est limité par une surface frontale (16) du piston (15) tournée vers l'espace de commande (5), par une plaque de soupape (14) et par le corps de soupape (35).
  9. Soupape selon l'une quelconque des revendications 5 à 8, caractérisée en ce que le corps de soupape (35) présente un alésage longitudinal (37) connecté à l'espace de commande (5), dans lequel est disposé le piston (15).
  10. Soupape selon la revendication 9, caractérisée en ce que l'alimentation en fluide sous pression (2) est connectée par le biais de l'espace de commande (5) à l'alésage longitudinal (37).
  11. Soupape selon l'une quelconque des revendications 6 à 10, caractérisée en ce que la connexion entre l'espace de commande (5) et l'alimentation en fluide sous pression (2) est pourvue d'un étranglement d'entrée (40).
  12. Soupape selon l'une quelconque des revendications 6 à 11, caractérisée en ce que la connexion entre l'alimentation en fluide sous pression (2) et l'espace de commande (5) est pourvue d'un étranglement de sortie (41).
  13. Soupape selon l'une quelconque des revendications 5 à 12, caractérisée en ce que l'espace de commande (5) est connecté par le biais d'une conduite de connexion (36) à un espace de commande d'aiguille (34), la conduite de connexion (36) partant de la connexion entre l'alimentation en fluide sous pression (2) et l'espace de commande (5) entre l'étranglement d'entrée (40) et l'étranglement de sortie (41) dans la direction de l'espace de commande d'aiguille (34).
  14. Soupape selon l'une quelconque des revendications 1 à 10, caractérisée en ce que la région haute pression (4) est connectée par le biais d'un perçage (50) dans l'aiguille d'injecteur (23) à un espace de commande d'aiguille (34).
EP20030021080 2002-10-31 2003-09-18 Soupape pour le contrôle des fluides avec alimentation d'un fluide sous pression Expired - Lifetime EP1416152B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10250722 2002-10-31
DE2002150722 DE10250722A1 (de) 2002-10-31 2002-10-31 Ventil zum Steuern von Flüssigkeiten mit einer Druckmittelzuführung

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EP1416152A1 EP1416152A1 (fr) 2004-05-06
EP1416152B1 true EP1416152B1 (fr) 2009-06-17

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DE (2) DE10250722A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10346212A1 (de) * 2003-10-06 2005-04-21 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1793120A1 (fr) * 2005-12-02 2007-06-06 Siemens Aktiengesellschaft Soupape d'un injecteur
DE102006047133A1 (de) * 2006-10-05 2008-04-10 Robert Bosch Gmbh Injektor für eine Kraftstoffeinspritzanlage
DE102007023384A1 (de) * 2007-05-18 2008-11-20 Robert Bosch Gmbh Injektor für eine Kraftstoffeinspritzanlage
JP4734351B2 (ja) * 2008-01-28 2011-07-27 日立オートモティブシステムズ株式会社 燃料噴射弁及び内燃機関

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2118624B (en) * 1982-04-13 1985-05-30 British Internal Combust Eng I.c. engine liquid fuel injector
US4509691A (en) * 1982-07-15 1985-04-09 Lucas Industries Public Limited Company Fuel injection nozzles
US5884848A (en) * 1997-05-09 1999-03-23 Cummins Engine Company, Inc. Fuel injector with piezoelectric and hydraulically actuated needle valve
US6454189B1 (en) * 2000-07-03 2002-09-24 Caterpillar Inc. Reverse acting nozzle valve and fuel injector using same

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DE10250722A1 (de) 2004-05-13
EP1416152A1 (fr) 2004-05-06
DE50311603D1 (de) 2009-07-30

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