WO2004111430A1 - Injecteur pour moteurs a combustion interne - Google Patents

Injecteur pour moteurs a combustion interne Download PDF

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Publication number
WO2004111430A1
WO2004111430A1 PCT/DE2004/000847 DE2004000847W WO2004111430A1 WO 2004111430 A1 WO2004111430 A1 WO 2004111430A1 DE 2004000847 W DE2004000847 W DE 2004000847W WO 2004111430 A1 WO2004111430 A1 WO 2004111430A1
Authority
WO
WIPO (PCT)
Prior art keywords
nozzle needle
nozzle
needle
control chamber
leakage
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.)
Ceased
Application number
PCT/DE2004/000847
Other languages
German (de)
English (en)
Inventor
Friedrich Boecking
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
Priority to EP04729038A priority Critical patent/EP1636481A1/fr
Publication of WO2004111430A1 publication Critical patent/WO2004111430A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the present invention relates to an injection nozzle for internal combustion engines with the features of the preamble of claim 1.
  • Such an injection nozzle is known for example from DE 100 58 153 Al and has a nozzle body on which at least one first spray hole and at least one second spray hole are formed.
  • a first nozzle needle designed as a hollow needle is guided in a first needle guide of the nozzle body, with which the injection of fuel through the at least one first spray hole can be controlled.
  • a second needle guide is formed, in which a second nozzle needle is arranged coaxially with the first nozzle needle, with which the injection of fuel through the at least one second spray hole can be controlled.
  • the second nozzle needle is drive-connected to a drive piston which, in a control chamber, has a control surface which is effective when pressure is applied in the closing direction.
  • the second nozzle needle has a pressure stage, ie a cross-sectional area of a second one formed between the second nozzle needle and the nozzle body
  • the valve seat is smaller than a cross-sectional area of the second needle guide formed in the first nozzle needle for guiding the second nozzle needle.
  • the injection nozzle according to the invention with the features of the independent claim has the advantage over the fact that a first control chamber provided for direct control of the first nozzle needle can be arranged coaxially in a high-pressure chamber and is only separated from it by a control chamber sleeve.
  • the high-pressure chamber and the first control chamber can thus be arranged relatively close to one another in the nozzle body without requiring an excessive amount of installation space in the radial direction.
  • the axial height of the nozzle body can be considerably reduced by this design.
  • the control chamber sleeve is prestressed in an opening direction of the first nozzle needle, as a result of which it comes into sealing contact with a boundary wall of the first control chamber formed on the nozzle body and opposite a first control surface of the first nozzle needle or a first drive piston coupled to it.
  • the control chamber sleeve can be biased in the opening direction of the first nozzle needle with a biasing spring which is supported on one end on the control chamber sleeve and on the other end on the first nozzle needle or on the first drive piston.
  • the pressure in the high-pressure chamber is the same as in the first control chamber, so that the tight contact between the control chamber sleeve and the sealing body is not important.
  • the first nozzle needle is opened, however, there is a reduced pressure in the first control chamber, so that a pressure difference between the high-pressure chamber and the first control chamber arises, which is to be sealed with the aid of the control chamber sleeve.
  • the proposed arrangement of the prestressing spring increases its prestressing force when the first nozzle needle is opened, with the result that the sealing effect of the control chamber sleeve lying against the nozzle body also increases.
  • the first needle guide can advantageously communicate with a first leakage space which is connected to a leakage line.
  • the leakage system has a leakage pressure that is usually lower than the smallest operating pressure in the fuel that occurs during the correct operation of the injection nozzle. This ensures that fuel - if at all - gets into the leakage system from the high-pressure system in all operating states, not the other way around.
  • a further development is particularly advantageous in which the first leakage space is delimited radially on the outside by a leakage space sleeve which defines the first leakage space separates from the high-pressure chamber, is guided on the first nozzle needle or on the first drive piston and is prestressed in the closing direction of the first nozzle needle.
  • a leakage space sleeve which defines the first leakage space separates from the high-pressure chamber, is guided on the first nozzle needle or on the first drive piston and is prestressed in the closing direction of the first nozzle needle.
  • the leakage space sleeve is prestressed in the closing direction of the first nozzle needle against a wall of the nozzle body which delimits the first leakage space in the closing direction.
  • the manufacturing effort for the construction of the nozzle body is considerably reduced.
  • FIG. 1 and 2 each show a greatly simplified principle - longitudinal section through an injection nozzle according to the invention, in different embodiments.
  • an injection nozzle 1 has a nozzle body 2 that is only partially shown.
  • the injection nozzle 1 is used to supply fuel to a cylinder of an internal combustion engine, particularly in a motor vehicle.
  • a nozzle tip 3 protrudes into a combustion chamber 4 or into a premixing chamber 4 of the respective cylinder, such that at least one first spray hole 5 and at least one second spray hole 6 inject fuel into the combustion chamber / premixing chamber 4 when the injection nozzle 1 is actuated accordingly can.
  • the injection nozzle 1 can have a plurality of first spray holes 5 and / or a plurality of second spray holes 6, which are then expediently each arranged in a ring, distributed in the circumferential direction along the nozzle tip 3.
  • the nozzle body 2 contains a first needle guide 7, in which a first nozzle needle 8 is mounted so as to be stroke-adjustable.
  • the first nozzle needle 8 is used to control the at least one first spray hole 5.
  • a first sealing seat 10 is formed between a first needle tip 9 of the first nozzle needle 8 facing the spray holes 5, 6 and the nozzle tip 3 at least one first spray hole 5 is arranged upstream of the at least one first spray hole 5.
  • the fuel supply to the spray holes 5, 6 takes place via a supply line 11 which is formed in the nozzle body 2, is supplied with fuel at high pressure on the inlet side and opens into a nozzle chamber 12 on the outlet side.
  • the supply line 11 can be supplied with fuel under high pressure
  • Supply line 11 can be connected to a high-pressure manifold, not shown here, which is fed by a high-pressure pump and to which the supply lines 11 of several injection nozzles 1 are connected (“common rail principle”). It is also possible to connect the supply line 11 directly to one to connect the corresponding high pressure pump.
  • the first nozzle needle 8 is designed as a hollow needle and contains a second needle guide 14, in which a second nozzle needle 15 is mounted in a stroke-adjustable manner coaxial with the first nozzle needle 8.
  • the second nozzle needle 15 is used to control the at least one second spray hole 6.
  • a second sealing seat 17 is formed, which is downstream of the at least one first spray hole 5 and upstream of the at least one second spray hole 6 is arranged.
  • the sealing seats 10, 17 each extend annularly and linearly in the circumferential direction.
  • both the at least one first spray hole 5 and the at least one second spray hole 6 are separated from the fuel supply.
  • ⁇ at least one first injection hole 5 communicates with the fuel supply, while this is closed off at least one second spray hole 6 from the fuel supply.
  • both nozzle needles 8, 15 are open, all spray holes 5, 6 communicate with the fuel supply.
  • the nozzle needles 8, 15 are actuated with the aid of hydraulic pressure forces acting on them for opening and closing.
  • An opening direction is the Nozzle needles 8, 15 symbolized by an arrow 18, while an arrow 19 represents the closing direction of the nozzle needles 8, 15.
  • the first nozzle needle 8 has a first pressure stage 20, which is arranged in the nozzle chamber 12 or in the annular chamber 13 and is therefore constantly subjected to high fuel pressure during operation of the injection nozzle 1.
  • the first pressure stage 20 faces the spray holes 5, 6, so that the pressure forces acting thereon act in the opening direction 18.
  • the first pressure stage 20 is realized in that a first sealing surface 21 in the first sealing seat 10 is selected to be smaller than a first guide surface 22 in the first needle guide 7.
  • a first control surface 23 is provided, which can basically be formed on the first nozzle needle 8.
  • the first control surface 23 is formed on a first drive piston 24, which is drive-coupled to the first nozzle needle 8. Since the first control surface 23 faces away from the spray holes 5, 6, it generates a pressure force which is effective in the closing direction 19 when pressure is applied.
  • the first drive piston 24 is supported directly on the first nozzle needle 8.
  • first drive piston 24 and the first nozzle needle 8 are permanently subjected to pressure forces which press the first drive piston 24 against the first nozzle needle 18, it is not absolutely necessary for the first nozzle needle 8 to be firmly connected to the first drive piston 24 is.
  • the individual components first nozzle needle 8, first drive piston 24
  • the components 8, 24 mentioned form a functional unit which is completely adjustable in terms of stroke.
  • the first drive piston 24 is fixedly connected to the first nozzle needle 8, in particular the first drive piston 24 and the first nozzle needle 8 can also be formed in one piece.
  • the first control surface 23 is arranged in a first control chamber 25 and can be pressurized there. Opposite the first control surface 23, the first control chamber 25 is delimited by a first wall 26 which faces the spray holes 5, 6 and is formed on the nozzle body 2. Radially inside is the first control chamber 25 through a cylindrical guide pin 27 of the nozzle body
  • the first control chamber 25 is delimited by a control chamber sleeve 29, which is mounted on the outside on the first drive piston 24 so as to be stroke-adjustable.
  • the control chamber sleeve 29 is by means of a biasing spring
  • the biasing spring 30 thus simultaneously serves to drive the first drive piston 24 and thus the first nozzle needle 8 in the closing direction 19 thereof.
  • the control chamber sleeve 29 separates the first control chamber 25 from a high-pressure chamber 32, which drives the drive piston 24 at its end remote from the spray holes 5, 6 encased in a ring.
  • the high-pressure chamber 32 is connected to the supply line 11, so that the high-pressure fuel prevails in the high-pressure chamber 32 during operation of the injection nozzle 1.
  • the feed line is 11 so arranged in the nozzle body 2 that it is virtually passed through the high-pressure chamber 32. Accordingly, the nozzle body 2 can be made relatively simple, as a result of which it can be produced inexpensively. Furthermore, due to this arrangement, the nozzle body 2 is comparatively small in the radial direction, and at the same time a relatively small overall height can also be achieved in the axial direction.
  • the first control chamber 25 communicates with the supply line 11 via a first inflow line 33, so that the high fuel pressure can be set in the first control chamber 25.
  • the first inflow line 33 is throttled and for this purpose can contain a first inflow throttle 34 which throttles the volume flow through the first inflow line 33.
  • the first control chamber 25 is also connected to a first connection 36 of a 3/3 valve 37 by means of a first drain line 35. According to its designation “3/3”, the 3/3 valve 37 has three connections, namely the first connection 36, a second connection 38 and a third connection 39, as well as three switching positions, which are explained further below.
  • the first drain line 35 is also throttled, which is achieved here by means of a first drain throttle 40.
  • the first inflow line 33 is throttled more than the first outflow line 35, which is achieved by appropriate dimensioning of the first inflow throttle 34 and the first outflow throttle 40.
  • the first drive piston 24 is mounted in the nozzle body 2 in a first drive piston guide 41 in a stroke-adjustable manner.
  • This first drive piston guide 41 and the first needle guide 7 communicate with a first leakage space 42, to which a leakage line 43 is connected.
  • the Leakage line 43 usually leads to a relatively unpressurized reservoir, in particular a fuel tank.
  • a pressure control valve (not shown here) can expediently be arranged in the leakage line 43, which ensures that a predetermined leakage pressure prevails in the leakage system 43.
  • This leakage pressure is selected such that it is certainly smaller than the smallest operating pressure for the fuel that occurs during the correct operation of the injection nozzle 1.
  • a leak from the high-pressure chamber 32 can reach the first leakage chamber 42 along the first drive piston guide 41, as can a leak from the nozzle chamber 12 along the first needle guide 7.
  • the leakage volume can then be discharged via the leakage line 43.
  • a second pressure stage 44 In order to introduce pressure forces effective in the opening direction 18 into the second nozzle needle 15, the latter is equipped with a second pressure stage 44.
  • the second pressure stage 44 is also arranged in the annular space 13, but in a section which is arranged downstream of the first sealing seat 10. This means that the second pressure stage 44 is only acted upon by the high fuel pressure when the first nozzle needle 8 is open.
  • a second sealing surface 45 in the second sealing seat 17 is selected to be smaller than a second guide surface 46 in the second needle guide 14.
  • a second control surface 47 is provided for introducing pressure forces acting in the closing direction 19 into the second nozzle needle 15.
  • the second control surface 47 can be arranged directly on the second nozzle needle 15 on a side facing away from the spray holes 5, 6.
  • the second control surface 47 is formed on a second drive piston 48, which is drive-coupled to the second nozzle needle 15.
  • the second control surface 47 is in a second control room
  • the second control chamber 49 arranged and pressurized there.
  • the second control chamber 49 communicates through a second inlet line 50 with the inlet line 11, here indirectly via the high-pressure chamber 32, to which the second inlet line
  • the second inflow line 50 is connected.
  • the second inflow line 50 is throttled, which is expedient by means of a second
  • the second inflow line 50 comprises an annular groove 52 which is formed radially on the inside of the first drive piston 24.
  • the second drive piston 48 is mounted in a second drive piston guide 53 in a stroke-adjustable manner in the first drive piston 24, which is designed as a hollow piston for this purpose.
  • the two drive pistons 24 and 48 like the two nozzle needles 8 ' , 15, are arranged coaxially one inside the other.
  • the second control chamber 49 is connected to the second connection 38 of the 3/3 valve 37 via a second drain line 54.
  • the second drain line 54 is throttled, which z. B. is achieved by means of a second discharge throttle 55.
  • the second inflow line 50 is throttled more than the second outflow line 54, which by appropriately dimensioning the second
  • Inlet throttle 51 and the second outlet throttle 55 is reached.
  • a second leakage space 56 is formed in the interior of the first drive piston 24, which surrounds the mutually facing end sections of the second nozzle needle 15 and the second drive piston 48 in a ring shape.
  • the second leakage space 56 takes up leakages that pass from the second control space 49 along the second drive piston guide 53 and, when the first nozzle needle 8 is open, from the annular space 13 along the second needle guide 14 into the second leakage space 56.
  • the first drive piston 24 contains at least one transverse bore 57 through which the two leakage spaces 42 and 56 communicate with one another. In this way, the second leakage space 56 is also connected to the leakage line 43 through the transverse bore 57 and the first leakage space 42.
  • the second leakage space 56 there is also a return spring 58, which is supported on the one hand via a step 59 formed on the first drive piston 24 on the first drive piston 24 and on the other hand via a disk 60 on a shoulder 61 formed on the second nozzle needle 15.
  • the return spring 58 thus drives the second nozzle needle 15 in its closing direction 19.
  • the disk 60 is designed to be permeable to leakage, which can be achieved by a corresponding radial play or by corresponding axial openings.
  • a relief line 62 is connected to the third connection 39 of the 3/3 valve 37, which can expediently be connected to the leakage line 43.
  • a check valve 63 here arranged, which blocks to the third terminal 39 and opens to the leakage line 43 against the force of a closing spring 64.
  • the 3/3 valve 37 here comprises a valve body 65 which interacts with a first valve seat 66 and with a second valve seat 67. Furthermore, the 3/3 valve 37 contains a spring 68, which drives the valve body 65 into the first valve seat 66.
  • the valve body 65 is drive-connected via a drive rod 69 to an actuator or actuator 70, which can in particular be designed as a piezo actuator.
  • the actuator 70 can drive the valve body 65 in accordance with a double arrow for performing actuating strokes 71.
  • the control chamber sleeve 29 is tapered at its end 72 modified from the spray holes 5, 6. This results in an increased contact force in the contact zone between the control chamber sleeve 29 and the first wall 26, which increases the sealing effect of the control chamber sleeve 29 for sealing the high-pressure chamber 32 with respect to the first control chamber 25.
  • the pointed end 72 is formed in that the control chamber sleeve 29 is beveled conically on the radially outside.
  • the control chamber sleeve 29 thus has a chamfer 73 at its pointed end 72, which is exposed to the high pressure chamber 32. Due to the selected shape of the control chamber sleeve 29, the supply line 11 can be brought relatively close to the high pressure chamber (32) in relation to the radial direction of the first control chamber 25.
  • the nozzle body 2 can thus be extremely compact in the radial direction.
  • the embodiment of the injection valve 1 according to the invention shown in FIG. 1 works as follows: In the initial state shown in FIG. 1, both nozzle needles 8, 15 are closed, so that the first nozzle needle 8 sits in the first sealing seat 10, while the second nozzle needle 15 sits in the second sealing seat 17.
  • the 3/3 valve 37 assumes its first switching position shown here, in which the valve body 65 is seated in its first valve seat 66. Accordingly, the third port 39 is blocked, while the first port 36 communicates with the second port 38, since the valve body 65 is lifted from its second valve seat 67.
  • the communicating connection of the first connection 36 to the second connection 38 is not absolutely necessary for the function of the 3/3 valve 37 or for the control of the nozzle needles 8, 15. (???)
  • the high fuel pressure is established in the first control chamber 25 via the first inflow line 33. Likewise, the high fuel pressure is established in the second control chamber 49 via the second inflow line 50.
  • the first nozzle needle 8 In order to carry out fuel injection through the at least one first spray hole 5, the first nozzle needle 8 must be opened.
  • the actuator 70 is actuated to adjust the stroke of the valve body 65.
  • a second switching position of the 3/3 valve 37 is set. In this second switching position, the valve body 65 is seated in its second valve seat 67, while it is lifted off its first valve seat 66. Accordingly communicates in the second switching position, the first connection 36 with the third connection 39. This means that fuel can now flow out of the first control chamber 25 through the expansion line 62 via the expansion line 62. At the same time, fuel flows into the control chamber 25 via the first inflow line 33.
  • first inflow line 33 is throttled more than the first outflow line 35, more fuel flows out of the first control chamber 25 than can continue to flow. Accordingly, there is a pressure drop in the first control chamber 25. This pressure drop changes the effective force balance on the unit formed by the first drive piston 24 and the first nozzle needle 8 in such a way that a resulting force now acts in the opening direction. Consequently, the first nozzle needle 8 lifts off its first sealing seat 10 and the at least one first spray hole 5 can be supplied with the high-pressure fuel. As a result, fuel is injected into the combustion chamber 4 through the at least one first spray hole 5.
  • the actuator 70 is actuated to return the valve body 5 to the first switching position.
  • High fuel pressure can then build up again in the first ' control chamber 25 via the first inflow line 33, since no more fuel flows out of the first control chamber 25 via the first outflow line 35 in the first switching position of the 3/3 valve 37.
  • the balance of forces is changed again to generate a resultant force acting in the closing direction 19.
  • the biasing spring 30 supports the closing movement of the first drive piston 24 or the first nozzle needle 8.
  • the two nozzle needles 8, 15 can be opened conventionally one after the other, so that initially only the first nozzle needle 8 is opened and then also the second nozzle needle 15.
  • the two nozzle needles 8, 15 can also be opened virtually simultaneously with the injection nozzle 1 according to the invention become.
  • the procedure for opening the outer nozzle needle 8 is as above, in which the second switching position is set on the 3/3 valve 37.
  • the fuel high pressure is essentially present at the second pressure stage 44 of the first nozzle needle 15. Nevertheless, in the balance of forces on the common stroke-adjustable unit comprising the second nozzle needle 15 and the second drive piston 48, the pressure and spring forces effective in the closing direction 19 predominate.
  • the second nozzle needle 15 can now be opened in that the 3/3 valve 37 is adjusted to its third switching position by a corresponding actuation of the actuator 70.
  • the valve body 65 In the third switching position, the valve body 65 is located between the two valve seats 66, 67, so that the valve body 65 is lifted off both valve seats 66, 67.
  • both the first connection 36 and the second connection 38 are thus connected to the third connection 39.
  • Fuel can thus flow out of the second control chamber 49 into the expansion line 62 via the second drain line 54.
  • the second. inflow line 50 fuel into the second control chamber 49. Due to the selected dimensioning of the second throttles 51, 55, the fuel can flow out of the second control chamber 49 faster than it can flow.
  • both nozzle needles 8, 15 are to be opened quasi in parallel, that is to say almost simultaneously, the 3/3 valve 37 can be adjusted from its first switching position directly into its third switching position by a corresponding actuation of the actuator 70, as a result of which As a result, the pressure in the first control chamber 25 and the pressure in the second control chamber 49 drop simultaneously. As soon as the first nozzle needle 8 then lifts off its first sealing seat 10, there is essentially high fuel pressure at the second pressure stage 44 of the second nozzle needle 15, so that the second nozzle needle 15 can then also open immediately.
  • both nozzle needles 8, 15 can be closed simultaneously.
  • the actuator 70 is controlled in such a way that it adjusts the 3/3 valve 37 directly into its first switching position.
  • the fuel outflow from the control rooms 25, 49 through the end lines 35, 54 is thereby stopped, so that the pressure in the control rooms 25, 49 rises again to the high-pressure fuel via the inflow lines 33, 50.
  • the force balances for the nozzle needles 8, 15 are reversed in such a way that the resultant forces acting in the closing direction 19 now arise on both nozzle needles 8, 15.
  • both nozzle needles 8, 15 can enter their sealing seats 10, 17 virtually simultaneously.
  • the pressure effective in the opening direction collapses at the second pressure stage 44, so that the second nozzle needle 15 also closes automatically at the latest then.
  • the actuator 70 is first actuated in such a way that it switches the 3/3 valve 37 from the third switching position into its second switching position, so that the fuel outflow from the second control chamber 49 through the second Drain line 54 is blocked. Accordingly, fuel flows in via the second inflow line 50, so that the high fuel pressure is restored in the second control chamber 49. As a result, the balance of forces for the second nozzle needle 15 is reversed, so that a resulting force arises in the closing direction 19. The second nozzle needle 15 then moves into its second sealing seat 17. The at least one second spray hole 6 is thus separated from the fuel supply, while the at least a first spray hole 5 still takes place fuel injection into the combustion chamber 4. By switching the 3/3 valve 37 back into its third switching position, the second nozzle needle 15 can be opened again.
  • the first nozzle needle 8 To close the first nozzle needle 8 and the switching of the 3/3-valve 37 in the first switching position and the fuel discharge from the first control chamber 25 by 'the first discharge line 35 is now stopped, so that the inflowing through the first inlet duct 33 fuel in first control chamber 25 increases the pressure up to the high fuel pressure. As a result, the balance of forces is also reversed for the first nozzle needle 8, so that a resultant effective in the closing direction 19 is produced. Accordingly, the first nozzle needle 8 also moves into the first sealing seat 10. Then the at least one first spray hole 5 is also separated from the fuel supply.
  • the injection nozzle 1 according to the invention is distinguished by a comparatively simple construction and enables direct control of the two nozzle needles 8, 15, the second nozzle needle 15 being able to be opened and closed independently when the nozzle needle 8 is open.
  • FIG. 2 shows a second exemplary embodiment of the injection nozzle 1 according to the invention, reference being made to what has been said regarding FIG. 1 with regard to components and functions because of the correspondences with the first exemplary embodiment according to FIG. 1 and only the differences are explained below.
  • the first leakage space 42 is delimited radially on the outside by a leakage space sleeve 74.
  • the leakage space sleeve 74 is in the Closure direction 19 of the first nozzle needle 8 biased.
  • the leakage space sleeve 74 comes to bear axially on a second wall 75 of the nozzle body 2, which delimits the first leakage space 42 on a side facing the spray holes 5, 6.
  • the leakage space sleeve 74 is also mounted on the first drive piston 24 so as to be stroke-adjustable radially on the outside.
  • the axial prestressing of the leakage space sleeve 74 is achieved in the embodiment according to FIG.
  • the biasing spring 30 is supported on the one hand on the control chamber sleeve 29 and on the other hand on the leakage sleeve 74.
  • the biasing forces of the sleeves 29, 74 are constant and in particular independent of the relative position of the first drive piston 24.
  • the leakage space sleeve 74 is also tapered at its end 76 preceding in the pretensioning direction, that is to say here in the closing direction 19, a conical shape also being selected here which produces a chamfer 77 radially on the outside.
  • the pointed end 76 also causes an increase in the contact pressure and thus the sealing effect in the contact zone between the leakage space sleeve 74 and the second wall 75.
  • the special design of the tip 76 by means of the chamfer 77 also enables a construction in which the supply line 11 on the Spray holes 5, 6 facing the side of the high-pressure chamber 32 can be brought relatively close to the first leakage chamber 42 in relation to the radial direction to the high-pressure chamber 32. Accordingly, a construction that is relatively compact in the radial direction is also supported here.
  • the leakage line 43 is connected to the second leakage space 56, so that the first Leakage space 42 is connected to the leakage line 43 through the transverse bores 57 and through the second leakage space 56.
  • the return spring 58 is arranged here in the second leakage space 56 and, unlike in the variant according to FIG. 1, is supported on the one hand on the guide pin 27, which has a corresponding step 78 for this purpose, and on the other hand directly on the first nozzle needle 8. Accordingly, the return spring 58 is used here to reset the first nozzle needle 8 and not, as in the embodiment according to FIG. 1, to reset the second nozzle needle 15.
  • a spring for resetting the second nozzle needle 15 can be dispensed with here, since when the first nozzle needle is closed 8, no hydraulic pressure can act on the second pressure stage 44 in the opening direction 18, so that the balance of forces on the second nozzle needle 15 always produces a force that effectively results in the closing direction 19 and is sufficient to close the second nozzle needle 15.
  • the injection nozzle 1 according to the second embodiment shown in FIG. 2 operates in the same way as the embodiment shown in FIG. 1, so that what is said there can be referred to in terms of the mode of operation ,

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un injecteur (1) destiné à un moteur à combustion interne, présentant, dans un corps d'injecteur, des premiers et deuxièmes orifices d'injection (5, 6), dont l'ouverture et la fermeture peuvent être commandées au moyen d'une première aiguille d'injecteur (8) et d'une deuxième aiguille d'injecteur (15) guidée coaxialement dans la première. L'objectif de l'invention est de permettre de créer un injecteur (1) conçu de manière compacte. A cet effet, une première chambre de commande (25) est délimitée extérieurement dans le sens radial par une douille (29) qui sépare la première chambre de commande (25) d'une chambre haute pression (32), est guidée sur un premier piston d'entraînement (24) accouplé à la première aiguille d'injecteur (8) de façon à entraîner cette dernière, et est sollicitée dans le sens d'ouverture (19) de la première aiguille d'injecteur (8). La chambre haute pression (32) communique avec une conduite d'alimentation (11) qui achemine du carburant à haute pression aux orifices d'injection (5, 6).
PCT/DE2004/000847 2003-06-10 2004-04-23 Injecteur pour moteurs a combustion interne Ceased WO2004111430A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP04729038A EP1636481A1 (fr) 2003-06-10 2004-04-23 Injecteur pour moteurs a combustion interne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003126043 DE10326043A1 (de) 2003-06-10 2003-06-10 Einspritzdüse für Brennkraftmaschinen
DE10326043.9 2003-06-10

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008061400A1 (de) 2008-12-10 2010-06-17 Man Diesel Se Kraftstoff-Einspritzventil für eine Brennkraftmaschine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002090754A1 (fr) * 2001-05-08 2002-11-14 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion
DE10158337C1 (de) * 2001-11-28 2003-05-22 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung, insbesondere Injektor für Brennkraftmaschinen mit Direkteinspritzung, sowie Kraftstoffsystem und Brennkraftmaschine
US6568368B1 (en) * 1999-07-16 2003-05-27 Robert Bosch Gmbh Common rail injector
WO2004033890A1 (fr) * 2002-10-09 2004-04-22 Robert Bosch Gmbh Dispositif d'injection de carburant destine a un moteur a combustion interne

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6568368B1 (en) * 1999-07-16 2003-05-27 Robert Bosch Gmbh Common rail injector
WO2002090754A1 (fr) * 2001-05-08 2002-11-14 Robert Bosch Gmbh Soupape d'injection de carburant pour moteurs a combustion
DE10158337C1 (de) * 2001-11-28 2003-05-22 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung, insbesondere Injektor für Brennkraftmaschinen mit Direkteinspritzung, sowie Kraftstoffsystem und Brennkraftmaschine
WO2004033890A1 (fr) * 2002-10-09 2004-04-22 Robert Bosch Gmbh Dispositif d'injection de carburant destine a un moteur a combustion interne

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008061400A1 (de) 2008-12-10 2010-06-17 Man Diesel Se Kraftstoff-Einspritzventil für eine Brennkraftmaschine
JP2010138894A (ja) * 2008-12-10 2010-06-24 Man Diesel Se 内燃機関用燃料噴射弁

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DE10326043A1 (de) 2004-12-30
EP1636481A1 (fr) 2006-03-22

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