EP1961949B1 - Injecteur doté d'une servo-vanne supplémentaire - Google Patents

Injecteur doté d'une servo-vanne supplémentaire Download PDF

Info

Publication number
EP1961949B1
EP1961949B1 EP08100356A EP08100356A EP1961949B1 EP 1961949 B1 EP1961949 B1 EP 1961949B1 EP 08100356 A EP08100356 A EP 08100356A EP 08100356 A EP08100356 A EP 08100356A EP 1961949 B1 EP1961949 B1 EP 1961949B1
Authority
EP
European Patent Office
Prior art keywords
fuel
valve
injector
pressure
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP08100356A
Other languages
German (de)
English (en)
Other versions
EP1961949A3 (fr
EP1961949A2 (fr
Inventor
Dirk Vahle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1961949A2 publication Critical patent/EP1961949A2/fr
Publication of EP1961949A3 publication Critical patent/EP1961949A3/fr
Application granted granted Critical
Publication of EP1961949B1 publication Critical patent/EP1961949B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular a common rail injector according to the preamble of claim 1.
  • One from the DE 102 07 227 A1 known common rail injector comprises a means of an electromagnetic actuator operated control valve for blocking and opening a fuel drain path from a control chamber which is supplied via an inlet throttle with fuel from a high-pressure fuel storage.
  • the control valve By means of the control valve, the fuel pressure can be influenced within the control chamber.
  • a valve element By varying the fuel pressure within the control chamber, a valve element (nozzle needle) is moved axially between an open position and a closed position, wherein the nozzle needle releases the fuel flow into the combustion chamber of an internal combustion engine in its open position.
  • a disadvantage of the known injectors, in which the electromagnetically operated control valve with a non-pressure balanced Ball seat is provided is provided is that the maximum by means of the control valve switchable control pressure (with reasonable space and recoverable power requirements) is limited.
  • US 2004/000600 A shows an injector with a hydraulically controlled servo valve.
  • the invention has for its object to provide an injector, by means of which injection pressures beyond 2000 bar, preferably injection pressures of 3000 bar or above, can be realized.
  • the invention is based on the idea of providing a servo valve in addition to the control valve, which is preferably operated by means of an electromagnetic actuator, wherein the pressure within a control chamber assigned to the servo valve can be varied by means of the actuator-operated control valve, whereby the servo valve can in turn be switched.
  • the servo valve itself in turn controls the pressure in a second control chamber associated with the actual injection valve, such that a one-piece or multi-part nozzle needle is adjustable between a closed position and an open position releasing the fuel flow through a nozzle hole arrangement into a combustion chamber of an internal combustion engine.
  • the first control chamber of the control valve in particular via an inlet throttle, is supplied with control fluid flowing from a first high-pressure port of the injector, while an additional second high-pressure port is provided for supplying the second control chamber of the servo valve.
  • the fuel flowing in through the second high-pressure connection is fed, in particular via an inlet throttle, to the second control chamber of the servo valve.
  • the injector is preferably also supplied with the fuel volume to be injected through the nozzle hole arrangement via the second high-pressure connection.
  • the actuator of the injector is designed as a piezoelectric actuator. It is advantageous, however, if the actuator is designed as an electromagnetic actuator due to its greater travel.
  • the control valve is preferably designed as a 2/2-way valve, in particular with a ball / conical seat, by means of which the control fluid pressure level at the servo valve (in the first control chamber) is controlled. Since the servo valve is designed with the pressure difference between the two control chambers with an individually adapted excess force, the injection valve can be acted upon with the optimum for the injection into the combustion chamber pressure level.
  • control valve To open the injector (lifting the one-piece or multi-part nozzle needle from its needle seat), the control valve is first opened by means of, in particular electromagnetic actuator, whereby control fluid from the first control chamber can flow through a fuel drain path in a low pressure region of the injector.
  • the inlet to the first control chamber and the outflow of control fluid through the fuel drain path out of the first control chamber are matched to one another such that when the control valve is open, a net outflow from the first control chamber results.
  • the pressure in the first control chamber whereby the operatively connected to the first control valve servo valve opens, in particular by a servo piston lifts from its sealing seat and thus releases the fuel flow from the actual injection valve (nozzle needle) associated second control chamber, wherein the inlet for and the outflow of fuel from the second control chamber are matched to one another such that when the servo valve is open, a net outflow of fuel from the second control chamber results.
  • a sufficiently large pressure gradient lifts the nozzle needle from its needle seat and are the nozzle hole arrangement for under high pressure, in particular about 3000 bar, stagnant fuel, which preferably flows through the second high pressure port, released into the combustion chamber of an internal combustion engine.
  • the control valve of the actuator is closed, whereby the pressure in the first control chamber increases, which causes the servo valve closes and thereby the pressure in the second control chamber increases. This in turn causes the nozzle needle to be moved axially into its needle seat.
  • the pressure level of the control fluid flowing in from the first high-pressure port is lower than the pressure level of the fuel flowing in from the second high-pressure port, which is supplied via the nozzle hole arrangement to the combustion chamber of an internal combustion engine.
  • the actuator only controls the comparatively low pressure level of the control fluid, while the servo valve controls the fuel which is under (maximum) high pressure (injection pressure) and which is to be injected.
  • electromagnetic actuators whose travel is advantageously greater than that of piezoelectric actuators, use at injection pressures beyond the 2000 bar limit.
  • two separate high-pressure accumulators for the control fluid and the fuel to be injected can be provided, for example, which are supplied with control fluid or fuel with differently sized high-pressure pumps.
  • the pressure level of the first high-pressure port and the pressure level of the second high-pressure port are approximately equal.
  • the actuator control valve in particular designed as a 2/2-way valve solenoid control valve, preferably with a ball / cone valve seat or a flat / flat valve seat is formed.
  • These valves have the advantage over pressure-balanced valves that (almost) no leakage occurs in the closed position.
  • the servo valve is preferably a servo piston valve with a ball / cone valve seat or a flat / flat valve seat.
  • each of the two control chambers are associated with an inlet throttle and an outlet throttle, wherein the respective cooperating throttles are dimensioned such that when the control valve is open or when the servo valve open a net outflow from the respective control chamber results.
  • the injector is provided with two separate return ports for the different control amounts.
  • the injector is provided with two separate return ports for the different control amounts.
  • the control fluid is fuel, to supply both control quantities to a common return connection.
  • the separate return ports may be configured to operate at a different pressure level.
  • the fuel drainage path From the second control chamber first opens into an intermediate chamber and fuel flows from there via at least one throttle to the low pressure region of the injector.
  • the control fluid drain path also advantageously opens out of the first control chamber, so that only a single return connection has to be provided.
  • the servo valve In order to avoid a double (axially spaced) guide a servo piston of the servo valve, it is advantageous to form the servo valve as a so-called.
  • Flip-flop valve wherein the particular spherical valve element between two, in particular opposite sealing seats is adjustable.
  • the valve element In the first sealing seat, the valve element obstructs the fuel drain path from the first control chamber into the intermediate chamber (valve chamber), while the valve element in the second sealing seat blocks a, in particular throttle-free, connecting channel in the direction of the low-pressure region of the injector, so that fuel is only via a throttle channel can flow out of the intermediate chamber in the direction of the low pressure region.
  • control fluid which is connected to the actuator-operated control valve, for example, water, oil or air.
  • control fluid is also fuel, in particular at a low pressure level than the fuel flowing in via the second high-pressure port.
  • This embodiment allows the provision of only a single return port.
  • Fig. 1 Based on Fig. 1 the principle of operation of an injector 1 designed as a common-rail injector is explained below. All embodiments have in common that the injector 1 is supplied via a first high-pressure port 2 and a second high-pressure port 3. About the first high pressure port 2 flows as a control fluid serving to fuel, while on the second high-pressure port 3, inter alia, the fuel volume flows, which is injected into the combustion chamber, not shown, of an internal combustion engine. Furthermore, all embodiments have in common that the injector 1 is provided with a single return port 4, via the fuel to a fuel reservoir and from there, for example via two different sized high-pressure pumps, not shown, two different high-pressure fuel storage 5, 6 is supplied. In particular, in the event that fuel is not supplied as the control fluid via the first high-pressure port 2, the injector 1 can also be provided with two separate return ports 4.
  • a one-piece nozzle needle 7 is received, which in the area of a needle tip 8 is provided with a closing surface 9 is, with which it can be brought into tight contact with a needle seat 10.
  • the nozzle needle 7 is biased by a closing spring 13, which is arranged in a pressure chamber 14 of the injector 1 and at one end on a component 15 and the other end on a peripheral collar 16 of the nozzle needle 7, biased toward its closed position.
  • the injector 1 is equipped with a designed as a 2/2-way solenoid valve 17 actuator control valve 17.
  • the actuator control valve 17 is a Steuerfluid- (fuel) drain path 18 from a disposed within an injector body 19 first control chamber 20 in a low pressure region 21 of the injector 1 can be unlocked and blocked.
  • the control fluid drainage path 18 is provided with a first outlet throttle 22.
  • the first control chamber 20 is supplied via the first high-pressure port 2 with under high pressure (p1) standing fuel (control fluid).
  • the first outlet throttle 22 and the first inlet throttle 23 are matched to one another such that when the actuator control valve 17 is open, a net outflow from the control chamber 20 into the low-pressure region 21 of the injector 1 and from there into the return port 4 results.
  • a servo piston 24 of a servo valve 31 moves with its in the drawing plane upper end face 25, the first control chamber 20, from the illustrated closed position in the drawing plane upwards into an open position in which he a fuel drain path 26 with a second outlet throttle 27 from a second control chamber 28 releases.
  • the second control chamber 28 is bounded radially outwardly by the component 15 and in the drawing plane below by an upper end face 29 of the nozzle needle 7.
  • the second control chamber 28 is supplied via an inlet throttle 30 with under high pressure (p2), in particular injection pressure, stagnant fuel from the pressure chamber 14, which in turn is supplied directly with fuel via the second high pressure port 3 from the second high pressure fuel reservoir 6.
  • the flow cross sections of the second outlet throttle 27 and the inlet throttle 30 are matched to one another such that when the servo valve 31 is opened, ie when the servo piston 24 moves upward in the drawing plane, a net outflow of fuel from the second control chamber 28 results, whereby the pressure within the second control chamber 28 drops and the nozzle needle 7 lifts off from its needle seat 10 and thus releases the flow of fuel from the nozzle hole assembly 11.
  • the actuator control valve 17 When the actuator control valve 17 is closed, the pressure in the first control chamber 20 increases due to the fuel flowing through the inlet throttle 23 (control fluid) again, whereby the force acting on the servo piston 24 Pressure force increases, which in turn the servo piston 24 is moved in the plane of the drawing down on its valve seat 32 and thereby blocks the fuel drain path 26 from the second control chamber 28. As a result, the pressure in the second control chamber 28 increases (by the fuel flowing in through the inlet throttle 30), whereby the nozzle needle 7 is moved in the drawing plane down into its needle seat 10, which in turn terminates the injection process.
  • the pressure level p1 of the first high-pressure accumulator 2 is lower than the pressure level p2 of the second high-pressure accumulator 3.
  • the pressure level p2 corresponds to the injection pressure level.
  • the valve seat 32 of the servo valve 31 is formed as a flat / flat seat. With the servo piston 24 raised, high-pressure fuel (p2) flows into a valve chamber 33 of the servo valve 31 and from there via a connecting line 24 within the injector body 19 to the low-pressure region 21 of the injector 1 and thence to the return port 4.
  • p2 high-pressure fuel
  • the design has the advantage that by means of the actuator control valve 17, the injection pressure level does not have to be switched, but that by means of the actuator control valve 17 preferably pressures of up to 2000 bar must be switched, whereas the actual injection pressure of the means of the actuator control valve 17th actuated servo valve 31 is switched.
  • the servo piston 24 cooperates with a valve element designed as a valve ball 35, which can be brought into tight contact with a conical valve seat 36.
  • the valve ball / conical seat (FIG. Fig. 2 ) Manufacturing tolerances can be compensated improved, whereby leaks are avoided.
  • the embodiment corresponds to Fig. 2 the embodiment according to Fig. 1 ,
  • the fuel drain path 26 with second outlet throttle 27 in the embodiment according to Fig. 3 first in a valve seat 32 of the servo valve 31 containing intermediate chamber 37, from where the fuel via another throttle 38 whose flow cross-section is preferably greater than the flow area of the second outlet throttle 27 in the limited by a shoulder of the servo piston 24 valve chamber 33 and from there from via the, in particular throttle-free connection line 34 to the low pressure region of the injector 1.
  • the first outlet throttle 26 of the embodiments according to the Fig. 1 and Fig. 2 was in the injector 1 according to Fig. 3 in other words, divided to the second outlet throttle 26 and the additional throttle 38. This is advantageous because the pressure and temperature load of the throttle 26 is reduced by those from the throttle 38.
  • the servo piston 24 is on the one hand on the lateral surface of its large diameter portion 39 and in the region of its small diameter portion 40 out.
  • the servo valve 31 is designed as a so-called flip-flop valve.
  • the servo piston 24 also acts in this embodiment, as in the embodiment according to Fig. 2 , with a designed as a valve ball valve element 35 together, which in turn can be brought into close contact with two opposite conical seats 36, 41.
  • the valve element 35 is housed in the intermediate chamber 37.
  • the valve element 35 is in close contact with the lower in the plane of the cone seat 36, the fuel drain path 26 is locked from the second control chamber 28 into the intermediate chamber 37.
  • the connecting channel 42 annular channel formed radially between the small diameter section 40 of the servo piston 24 and the injector body 19 or a disk component is axially interposed the intermediate chamber 37 and the valve chamber 33 is blocked, so that the fuel flow from the second control chamber 28 via the fuel drain path 26 and the intermediate chamber 37 via the additional throttle 38 to the valve chamber 33 and from there via the connecting line 34 in the low pressure region and can flow out there to the return port 4.
  • designed as a flip-flop valve servo valve 31 is compared to the embodiment according to Fig. 3 advantageous that the servo piston 24 must be performed only in the region of its large diameter portion 39.
  • injector 1 has a nozzle body 43 and an injector body 44, wherein the nozzle body 43 is braced against the injector body 44 by means of a union nut 45, which is penetrated by the nozzle body 43 in the axial direction.
  • the nozzle needle 7 is arranged in a nozzle chamber 46 within the nozzle body 43 and is spring-loaded by means of the closing spring 13 in the direction of the needle seat 10.
  • the nozzle chamber 46 is supplied via the second high pressure port 3 with under high pressure (injection pressure) of about 3000 bar standing fuel.
  • the second control chamber 28 is supplied with fuel from the nozzle chamber 46.
  • the second inlet throttle 30 is integrated. It can be seen that the conical seat 36 of the valve ball formed as a valve member 35 of the servo valve 31 is received in the plate member 48.
  • the servo piston 24 is received in a stepped bore in the injector body 44. Between the servo piston 24 and the injector body 44, an annular space 49 is formed, which serves as a low-pressure region 21 of the injector 1 and into which the integrated into the plate member 48 second outlet throttle 27 of the second control chamber 28 opens. The low pressure region 21 is connected to the return port 4.
  • the servo piston 24 is spring-loaded by means of a compression spring 50 which is supported on a retaining ring 51 held on the servo piston 24 and on a position-fixed component 52 in the direction of the conical seat 36.
  • the servo piston 24 limited with its upper surface in the plane of the drawing 25, the first control chamber 20, the over the first inlet throttle 23 is supplied with fuel at high pressure (p1, p1 ⁇ p2) from an annular space 53.
  • the annular space 53 is connected directly to the first high-pressure port 2 and is formed between the component 52 and the injector body 44.
  • the first outlet throttle 22 opening out of the first control chamber 20 is opened or closed by the actuator control valve 17.
  • the actuator control valve 17 has a cooperating with a valve ball 54 piston 55 of the actuator control valve 17 in its upper in the plane of the drawing an armature 56 which cooperates with electromagnets 57.
  • the fuel drain path 26 opens with second outlet throttle 27 in the valve chamber 33 of the servo valve 31 in the plane below the large diameter portion 39 of the servo piston 24.
  • This valve chamber 33 is connected via a transverse channel to an annular space 60, which directly with fuel from the second high pressure port 3 is supplied. So that when the servo piston 24 is lifted fuel can flow out of the second control chamber 28, the pressure level p1 of the fuel flowing in via the first high-pressure port 2 must be lower than the pressure level p2 of the fuel flowing in via the second high-pressure port 3.
  • the latter arrives in the pressure chamber 14 and from there via the second inlet throttle 30 into the second control chamber 28 or, when the nozzle needle 7 is raised from the needle seat 10, via the nozzle hole arrangement 11 into a combustion chamber of an internal combustion engine.
  • the following embodiments according to the FIGS. 7 to 10 have in common that the voltage applied to the first high-pressure port fuel pressure and the voltage applied to the second high-pressure port 3 fuel pressure p2, at least for some operating conditions or permanently be the same size. This is achieved in that the fuel flowing out of the second control chamber 28 from the second fuel drain path 26 with outflow throttle 27 flows into an injector region which is supplied with fuel flowing from the first high-pressure port 2, but the pressure in this injector region temporarily ceases an opening movement of the servo piston 24 drops below the pressure level p1 of the fuel flowing in through the first high-pressure port 2, whereby fuel can only flow out of the fuel drain path 26 in the first place.
  • the fuel drain path 26 opens into the valve chamber 33 below the large diameter portion 29 of the servo piston 24.
  • This valve chamber 33 is connected via a throttle 61 to the first high-pressure port 2.
  • the throttle 61 is located in a channel 62, which connects the valve chamber 33 with the first control chamber 20 and is fed into the fuel from the first high pressure port 2.
  • Fig. 8 shows an alternative embodiment in which the fuel drain path 26 with outlet throttle 27 also opens into the valve chamber 33 of the servo valve 31.
  • the valve chamber 33 is hydraulically connected via the throttle 61, which is introduced into the large diameter portion 39 of the servo piston 24, to the first control chamber 20, which is supplied with fuel from the first high-pressure port 2 directly via the first inlet throttle 23.
  • the throttle 61 ensures again that at a rapid opening movement of the servo piston 24 fuel flows slowly from the first high pressure port 2 and in this case from the first control chamber 20 into the valve chamber 33, whereby the pressure within the valve chamber 33 at least during the opening movement of the servo piston 24 below the pressure level p1 of the first High-pressure port 2 of incoming fuel drops, whereby fuel can escape via the fuel drain path 26 from the second control chamber 28.
  • the embodiment according to Fig. 9 essentially corresponds to the embodiment according to Fig. 8 with the only difference that the first inlet throttle 23 is incorporated to supply the first control chamber 20 in the large diameter portion 39 of the servo piston 24 and that the valve chamber 33 is supplied directly via the throttle 61 with high-pressure fuel from the first high-pressure port 2, so the first control chamber 20 is filled indirectly via the valve space 33.
  • the pressure in the valve chamber 33, so the injector, in which the fuel drain path 26 opens from the second control chamber 28 drops below the pressure p1 in the first high-pressure fuel storage, so that fuel with open servo valve 31 from the second control chamber 28 in the Valve chamber 33 and from there via the first inlet throttle 23 and the control fluid drain path 18 in the low pressure region 21 of the injector 1 and from there to the return port 4 can flow.
  • the embodiment according to Fig. 10 is characterized in that the fuel drain path 26 from the second control chamber 28 opens into the intermediate chamber 37 and from there via the additional throttle 38 in the actual valve chamber 33 below the large diameter portion 39 of the servo piston 24 of the servo valve 31.
  • This valve space 33rd is hydraulically connected to the first control chamber 20 via the integrated in the large diameter portion 39 throttle 21, which via the first directly connected to the first high pressure port 2 first Supply throttle 23 is supplied with fuel under high pressure (p1).
  • p1 fuel under high pressure
  • the throttle 61 prevents too rapid a pressure increase in the valve chamber 33 and the additional Throttle 38 additionally reduces the rate of pressure rise in the intermediate chamber 37, allowing fuel to flow out of the second control chamber 28 via the fuel drain path.

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)

Claims (11)

  1. Injecteur pour l'injection de carburant dans une chambre de combustion d'un moteur à combustion interne, en particulier injecteur de rampe commune, comprenant un premier raccord haute pression (2) et une soupape de commande d'actionneur (17) avec laquelle une course d'écoulement de fluide de commande (18) peut être bloquée ou libérée d'une première chambre de commande (20) qui est alimentée en fluide de commande depuis le premier raccord haute pression (2), et comprenant une aiguille de buse (7) qui peut être réglée entre une position d'ouverture libérant le flux de carburant dans la chambre de combustion d'un moteur à combustion interne et une position de fermeture dans laquelle l'aiguille de buse (7) s'applique contre un siège d'aiguille (10),
    caractérisé en ce que
    la première chambre de commande (20) est connectée fonctionnellement à une servo-vanne (31) au moyen de laquelle une voie d'écoulement de carburant (26) hors d'une deuxième chambre de commande (28), qui est alimentée en carburant provenant d'un deuxième raccord haute pression (3), peut être libérée ou bloquée, et en ce que la deuxième chambre de commande (28) est connectée fonctionnellement à l'aiguille de buse (7) de telle sorte que l'aiguille de buse se soulève de son siège d'aiguille (10) lorsque la voie d'écoulement de carburant (26) est libérée par la servo-vanne (31).
  2. Injecteur selon la revendication 1, caractérisé en ce que le niveau de pression (p1) du fluide de commande affluant depuis le premier raccord haute pression (2) est inférieur ou égal au niveau de pression (p2) du carburant affluant depuis le deuxième raccord haute pression (3).
  3. Injecteur selon l'une quelconque des revendications 1 ou 2, caractérisé en ce que la soupape de commande d'actionneur (17) est une électrovanne de commande réalisée notamment sous forme de soupape à 2/2 voies.
  4. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que dans la course d'écoulement de fluide de commande (18) est prévu un premier étranglement d'écoulement (22) et en ce que la première chambre de commande (20) est alimentée en fluide de commande par le biais d'un premier étranglement d'alimentation (23) et en ce qu'un deuxième étranglement d'écoulement (27) est prévu dans la voie d'écoulement de carburant (26), et en ce que la deuxième chambre de commande (28) est alimentée en carburant par le biais d'un deuxième étranglement d'alimentation (30).
  5. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un raccord de retour commun (4) est prévu pour le fluide de commande s'écoulant depuis la voie d'écoulement de fluide de commande (18) et pour le carburant s'écoulant hors de la voie d'écoulement de carburant (26).
  6. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que le canal d'écoulement de carburant (26) débouche dans une chambre intermédiaire (37) qui est connectée par le biais d'un étranglement à une région basse pression (21) de l'injecteur (1).
  7. Injecteur selon la revendication 6, caractérisé en ce que la servo-vanne (31) est réalisée sous forme de soupape en bascule avec un élément de soupape (35) notamment en forme de bille, qui, dans une position d'étanchéité, bloque la course d'écoulement de carburant (26) dans la chambre intermédiaire (37), et dans une deuxième position d'étanchéité, libère la course d'écoulement de carburant(26) et bloque simultanément un canal de connexion sans étranglement (42) allant à une région basse pression (21) de l'injecteur (1).
  8. Injecteur selon l'une quelconque des revendications précédentes, caractérisé en ce que le fluide de commande est de l'eau, de l'huile ou de l'air.
  9. Injecteur selon l'une quelconque des revendications 1 à 7, caractérisé en ce que le fluide de commande est du carburant.
  10. Injecteur selon la revendication 9, caractérisé en ce que la course d'écoulement de carburant (26) de la deuxième chambre de commande (28) débouche dans une région d'injecteur, qui est sollicitée avec du carburant s'écoulant hors du premier raccord haute pression (2).
  11. Injecteur selon la revendication 10, caractérisé en ce que la région d'injecteur est alimentée en carburant depuis le premier raccord haute pression (2) par le biais d'un étranglement (61) et en ce que la pression de carburant dans la région d'injecteur tombe en dessous du niveau de pression (p1) du carburant dans le premier raccord haute pression (2) dans le cas d'un mouvement de réglage, de préférence dans le cas d'un mouvement d'ouverture d'un piston de servocommande (24) de la servo-vanne (31).
EP08100356A 2007-02-13 2008-01-11 Injecteur doté d'une servo-vanne supplémentaire Not-in-force EP1961949B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007006939A DE102007006939A1 (de) 2007-02-13 2007-02-13 Injektor mit zusätzlichem Servoventil

Publications (3)

Publication Number Publication Date
EP1961949A2 EP1961949A2 (fr) 2008-08-27
EP1961949A3 EP1961949A3 (fr) 2008-09-17
EP1961949B1 true EP1961949B1 (fr) 2009-11-18

Family

ID=39472735

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08100356A Not-in-force EP1961949B1 (fr) 2007-02-13 2008-01-11 Injecteur doté d'une servo-vanne supplémentaire

Country Status (3)

Country Link
EP (1) EP1961949B1 (fr)
AT (1) ATE449250T1 (fr)
DE (2) DE102007006939A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015114716A1 (de) * 2015-09-03 2017-03-09 Denso Corporation Kraftstoff-Injektor mit zwei Kraftstoffeinlässen
DE102018208859A1 (de) * 2018-06-06 2019-12-12 Robert Bosch Gmbh Verfahren zum Betreiben eines Kraftstoffinjektors, Kraftstoffinjektor

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2351773B (en) * 1997-02-26 2001-02-21 Caterpillar Inc Hydraulically actuated fuel injection system
DE19744723A1 (de) 1997-10-10 1999-04-15 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung
DE10207227A1 (de) 2002-02-21 2003-09-04 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
US6824081B2 (en) * 2002-06-28 2004-11-30 Cummins Inc. Needle controlled fuel injector with two control valves
DE10305303A1 (de) * 2003-02-10 2004-08-19 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung, insbesondere für Brennkraftmaschinen mit Kraftstoff-Direkteinspritzung
DE10333692B3 (de) * 2003-07-24 2004-09-30 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
ES2277229T3 (es) 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni Servovalvula para controlar el inyector de combustible de un motor de combustion interna.

Also Published As

Publication number Publication date
DE502008000183D1 (de) 2009-12-31
EP1961949A3 (fr) 2008-09-17
DE102007006939A1 (de) 2008-08-14
EP1961949A2 (fr) 2008-08-27
ATE449250T1 (de) 2009-12-15

Similar Documents

Publication Publication Date Title
EP2235354B1 (fr) Injecteur de carburant dont l'élément soupape de commande présente une zone d'appui
EP2102486B1 (fr) Injecteur avec une soupape de commande à compensation de pression axiale
WO2008049699A1 (fr) Injecteur de carburant
DE102007043538A1 (de) Injektor mit hydraulischem Dämpfer
EP2011995B1 (fr) Injecteur doté d'un élément d'aération s'ouvrant vers l'extérieur
DE102004024527A1 (de) Kraftstoffeinspritzeinrichtung
EP1961949B1 (fr) Injecteur doté d'une servo-vanne supplémentaire
EP1939441A2 (fr) Injecteur de carburant
EP2123898B1 (fr) Injecteur de carburant
EP2275666B1 (fr) Injecteur de carburant doté d'une soupape de distribution à pression compensée
DE102007005382A1 (de) Leckagefreier Injektor
EP2195523B1 (fr) Injecteur à manchon de soupape de commande
WO2008049668A1 (fr) Injecteur d'injection de carburant dans des chambres de combustion de moteurs à combustion interne
DE10357873A1 (de) Einspritzventil
EP2019198B1 (fr) Injecteur
EP2138709B1 (fr) Injecteur de carburant actionné directement
EP2195522B1 (fr) Injecteur avec un élément de soupape de commande en forme de manchon
DE102007034319A1 (de) Injektor
DE102006050033A1 (de) Injektor, insbesondere Common-Rail-Injektor
DE102007001365A1 (de) Injektor mit Steuer- und Schaltkammer
WO2008125537A1 (fr) Injecteur
EP2204570B1 (fr) Injecteur de carburant
DE19947196A1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE102008044043A1 (de) Kraftstoffinjektor
DE102019215119A1 (de) Kraftstoffinjektor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA MK RS

17P Request for examination filed

Effective date: 20090317

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 502008000183

Country of ref document: DE

Date of ref document: 20091231

Kind code of ref document: P

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20091118

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20091118

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100228

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100218

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100318

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100218

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

BERE Be: lapsed

Owner name: ROBERT BOSCH G.M.B.H.

Effective date: 20100131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100131

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20100819

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100219

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20120126

Year of fee payment: 5

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20120111

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100519

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100111

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100418

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120131

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120111

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20091118

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120131

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20130326

Year of fee payment: 6

Ref country code: FR

Payment date: 20130207

Year of fee payment: 6

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 449250

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130111

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130111

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502008000183

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502008000183

Country of ref document: DE

Effective date: 20140801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140801

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140111