EP1636484A1 - Injecteur pour moteurs a combustion interne - Google Patents

Injecteur pour moteurs a combustion interne

Info

Publication number
EP1636484A1
EP1636484A1 EP04729036A EP04729036A EP1636484A1 EP 1636484 A1 EP1636484 A1 EP 1636484A1 EP 04729036 A EP04729036 A EP 04729036A EP 04729036 A EP04729036 A EP 04729036A EP 1636484 A1 EP1636484 A1 EP 1636484A1
Authority
EP
European Patent Office
Prior art keywords
compensator
control
piston
chamber
pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04729036A
Other languages
German (de)
English (en)
Other versions
EP1636484B1 (fr
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
Publication of EP1636484A1 publication Critical patent/EP1636484A1/fr
Application granted granted Critical
Publication of EP1636484B1 publication Critical patent/EP1636484B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • F02M2200/706—Valves for filling or emptying hydraulic chamber

Definitions

  • the present invention relates to an injection nozzle for internal combustion engines with the features of the preamble of claim 1.
  • Such an injector is for example from the
  • nozzle body which has at least one spray hole.
  • the nozzle body also contains a needle guide in which a nozzle needle is guided.
  • the injection of fuel through the at least one spray hole can be controlled with the nozzle needle.
  • the at least one spray hole are under high pressure
  • a control valve is arranged, with which the fuel supply can be controlled through the supply line to the at least one spray hole.
  • This control valve is drive-coupled to its actuation with an actuator.
  • the nozzle needle At its end facing away from the at least one spray hole, the nozzle needle carries a control piston which is guided in a stroke-adjustable manner in a control chamber.
  • this control room communicates with the supply line which can be controlled by the control valve.
  • an appropriately throttled goes from the control room Drain line that leads to a leakage oil chamber and that can be controlled with a slide. This slide forms part of the control valve and is thus actuated together with the control valve by the actuator.
  • the nozzle needle At its end facing the at least one spray hole, the nozzle needle has a pressure stage which, when pressurized, acts in the opening direction of the nozzle needle.
  • control valve closes the feed line and the slide opens the drain line.
  • the nozzle needle is then biased into its closed position by spring force; the at least one spray hole is thus closed.
  • the control valve When the actuator is partially activated, the control valve lifts off the associated seat, as a result of which the supply line is opened and the high fuel pressure can act on the pressure stage of the nozzle needle.
  • the high fuel pressure cannot build up in the control room because the drain line is still open. Accordingly, the opening forces on the nozzle needle predominate, so that the nozzle needle opens and an injection takes place.
  • the high fuel pressure can now also build up in the control chamber, so that the closing forces on the nozzle needle now predominate and drive it into the closed position.
  • the effort required to actuate the nozzle needle is relatively large.
  • the injection nozzle according to the invention with the features of the independent claim has the advantage that the nozzle needle can be controlled directly by operating the control piston. This is made possible by the fact that the high fuel pressure is present both on a compensator surface of the nozzle needle and on a control surface of the control piston, the control surface and the
  • Compensator surface are coupled together via a corresponding hydraulic path. This means that a pressure change on the control surface, which is triggered by actuation of the actuator, i.e. the control piston, is also effective directly on the compensator surface of the nozzle needle, as a result of which the balance of forces at the nozzle needle for opening or closing the nozzle needle changes directly , The effort to implement such a direct nozzle needle control is considerably reduced.
  • An embodiment is particularly advantageous in which the nozzle needle has a pressure stage which, according to the invention, is permanently connected hydraulically to the supply line. In this way, the nozzle needle always has a force component directed in the opening direction, which is directly available to support the opening movement of the nozzle needle.
  • the control piston can be actuated to open the nozzle needle in such a way that the applied pressure drops at the first compensator surface assigned to the nozzle needle.
  • the actuator drives the control piston in the direction in which the first control surface assigned to the control piston is biased anyway by the high fuel pressure applied to it.
  • the first control surface yields in the direction of the pressure forces acting on it.
  • the actuator does not have to generate any actuating forces, but only a sufficiently rapid adjustment of the control piston cause.
  • This embodiment is advantageous because in modern injection systems the fuel is now supplied to the at least one spray hole at very high pressures, for example 800 bar (???), via the supply line.
  • control piston is drive-coupled to the actuator via a drive rod, the actuator being designed as a hollow actuator through which the drive rod is guided centrally.
  • the drive rod carries on a side of the actuator facing away from the control piston a drive piston which can be driven by the actuator, the actuator being designed and arranged such that when it is actuated it drives the drive piston in an opening stroke direction of the nozzle needle.
  • the proposed design makes it possible to drive the control piston in the opening direction of the nozzle needle, which can be advantageous for generating a pressure drop on the first control surface.
  • the first control surface and the first compensator surface can be arranged in a common conversion space, in which case the control piston and the compensator piston are guided coaxially into one another.
  • the first is
  • Hydraulic path extremely short, as it is still practically implemented within the transfer space.
  • the nozzle needle is thereby controlled particularly directly.
  • Fig. 1 to 5 each a greatly simplified principle- longitudinal section through an injection nozzle according to the invention, with different
  • Injection nozzle 1 a nozzle body 2, which is equipped with at least one spray hole 3. It is clear that the nozzle body 2 regularly has more than one spray hole 3. Through the at least one spray hole 3, the injection nozzle 1 can fuel into a combustion chamber or
  • the nozzle body 2 contains a single nozzle needle 5, which is guided in a stroke-adjustable manner in a nozzle guide 6 in the nozzle body 2.
  • the nozzle needle 5 cooperates on its nozzle tip 7 facing the at least one spray hole 3 with a sealing seat 8 which is formed in the nozzle body 2 and usually has a circular ring shape.
  • a feed line 9 is formed in the nozzle body 2, which leads in the nozzle body 2 to a nozzle chamber 10 and is supplied with fuel which is under high pressure.
  • the feed line 9 is usually connected to a high-pressure line common to a plurality of injection nozzles 1, the so-called “common rail principle” common high-pressure line is fed by means of a common high-pressure pump. It is also possible to supply the supply line 9 with fuel under high pressure in a different way.
  • the feed line 9 can be connected directly to a high-pressure pump.
  • the nozzle space 10 can be connected to the at least one injection hole 3 via an annular space 11, the sealing seat 8 being arranged between the annular space 11 and the at least one spray hole 3.
  • the nozzle needle 5 has a pressure stage 12 in the nozzle chamber 10 and in the annular chamber 11 which faces the at least one spray hole 3.
  • the pressure stage 12 is the difference from a guide surface 13 in the cross section of the needle guide 6 minus a sealing surface 14 in the sealing seat 8.
  • a first compensator surface 16 is assigned to the nozzle needle 5, which serves to introduce pressure forces into the nozzle needle 5.
  • the first compensator surface 16 is formed on the nozzle needle 5 itself, specifically on a side facing away from the at least one spray hole 3. Accordingly, when pressure is applied, the first compensator surface 16 acts in a closing direction 17 of the nozzle needle 5 symbolized by an arrow.
  • the first compensator surface 16 is larger here than the pressure stage 12, so that it is sufficient to close or keep the nozzle needle 5 at the first Compensator surface 16 to apply the high fuel pressure.
  • the injection nozzle 1 also contains a control piston 18 which is drive-coupled to an actuator 19.
  • the actuator or actuator 19 is used to adjust the control piston 18 and can be designed, for example, as a piezo actuator.
  • the actuator 19 drives a drive piston 39 which is fixedly connected to a drive rod 40 which in turn is fixedly connected to the control piston 18. In principle, however, other drive couplings between the actuator 19 and the control piston 18 can also be carried out.
  • the control piston 18 is mounted in a control piston guide 20 in a stroke-adjustable manner in the nozzle body 2 and has a first control surface 21.
  • a first hydraulic path 22 is formed in the nozzle body 2, which hydraulically couples the first control surface 21 to the first compensator surface 16.
  • a hydraulic coupling is understood to mean a pressure transmission path which can transmit the pressure applied to the first control surface 21 up to the first compensator surface 16 and vice versa.
  • the first control surface 21 is arranged in a first control chamber 23 and can be pressurized therein.
  • the first compensator surface 16 is also arranged in a first compensator chamber 24 and there with a
  • the first control room 21 communicates with the first compensator room 24 via a connecting line 25.
  • the first hydraulic path 22 thus leads through the first control room 23, the connecting line 25 and the first compensator room 24.
  • first compensator chamber 24 there is also a return spring 26, which is located at one end on the nozzle body 2 and at the other end on the first Compensator 16 supports and drives the nozzle needle 5 in its closing direction 17.
  • the first control surface 21 is arranged on the control piston 18 on a side facing away from the at least one spray hole 3.
  • the control piston 18 is also equipped with a second control surface 27 which lies opposite the first control surface 21 and thus faces the at least one spray hole 3.
  • the second control surface 27 is arranged in a second control chamber 28 and can be pressurized there.
  • the second control chamber 28 communicates, so that in the second control chamber 28 of the Kraftstoffhochdru 'ck prevails to the supply line.
  • a second hydraulic path 29 is formed in the nozzle body 2, via which the first control chamber 23 is hydraulically coupled to the second control chamber 28 or to the feed line 9. This means that the high fuel pressure of the supply line 9 or of the second control chamber 28 also prevails in the first control chamber 23.
  • a control piston bypass 30 is formed radially between the control piston 18 and the control piston guide 20, which connects the first control chamber 23 to the second control chamber 28.
  • This control piston bypass 30 can be formed, for example, by an axial groove formed in the control piston 18 and / or in the control piston guide 20 or by a corresponding radial play between the control piston 18 and the control piston guide 20.
  • the control piston bypass 30 creates a throttled connection between the two control spaces 23 and 28.
  • the throttled control piston bypass 30 can only allow pressure equalization between the control spaces 23 and 28 to be significantly delayed.
  • the injection nozzle 1 according to the embodiment according to FIG. 1 works as follows:
  • the actuator 19 In an initial state shown in FIG. 1, the actuator 19 is not actuated, so that the control piston 18 is stationary.
  • the supply line 9 is subjected to the high fuel pressure, so that the high fuel pressure also prevails in the nozzle chamber 10, in the annular chamber 11 and in the second control chamber 28.
  • Hydraulic path 29 enable pressure equalization between the control rooms 23 and 28, so that the high fuel pressure also prevails in the first control room 23. The high fuel pressure then also prevails in the first via the first hydraulic path 22
  • Compensator chamber 24 On the one hand, the high fuel pressure cooperates with the first compensator surface 16 on the nozzle needle 5 in the closing direction 17. On the other hand, the high fuel pressure in the nozzle chamber 10 and in the annular chamber 11 interacts with the pressure stage 12 in the opening direction 15. Since the first compensator 16 is greater than the pressure stage 12 results in 'on the nozzle needle 5 in total effective in the closing direction 17 resulting force. In addition, the return spring 26 also acts on the nozzle needle 5 in the closing direction 17. Accordingly, the nozzle needle 15 is pressed at its needle tip 17 into the sealing seat 8. The nozzle needle 5 is thus closed and separates the at least one spray hole 3 from the annular space 11 or from the fuel supply 9.
  • the actuator 19 In order to generate a fuel injection through the at least one spray hole 3 into the combustion chamber 4, the actuator 19 is actuated, as a result of which it drives the control piston 18 to carry out an opening stroke 31 symbolized by an arrow.
  • the opening stroke 31, which is carried out at a relatively high actuating speed, on the one hand reduces the volume of the second control chamber 28. The fuel displaced thereby can escape into the supply line 9.
  • the opening stroke 31 increases the volume of the first control chamber 23. Since the second hydraulic path 29 allows no or only a delayed pressure compensation between the control chambers 23 and 28 during dynamic processes, there is consequently a pressure drop in the first control chamber 23.
  • This pressure drop propagates directly into the first compensator chamber 24 via the first hydraulic path 22, so that only a reduced pressure is effective on the first compensator surface 16.
  • the opening stroke 31 is selected such that the pressure drop at the first compensator surface 16 changes the balance of forces at the nozzle needle 5 to such an extent that a resulting force that is effective in the opening direction 15 now arises.
  • the high fuel pressure still effective at pressure stage 12 predominates at nozzle needle 5. Accordingly, the nozzle needle 5 lifts off the seat 8, that is, the nozzle needle 5 opens. Accordingly, fuel can now reach the at least one spray hole 3 under high pressure and inject it into the combustion chamber 4.
  • the actuator 19 is reset. Accordingly, the volume in the first control chamber 23 decreases, with the result that the pressure rises in the first control chamber 23. This increase in pressure propagates through the first hydraulic path 22 again to the first compensator surface 16. The one here The resulting pressure may well be higher than the high pressure fuel. Furthermore, the return spring 26 also supports the closing movement of the nozzle needle 5. Overall, a resultant force acting in the closing direction 17 results in any case on the nozzle needle 5.
  • the injection nozzle 1 according to FIG. 1 is characterized by a particularly simple construction, which also enables direct control of the nozzle needle 5 via the control piston 8. It is important that the high fuel pressure is effective at its pressure stage 12 even when the nozzle needle 5 is closed. It is also advantageous in this embodiment that the first compensator surface 16 at a
  • Pressurization in the closing direction 17 acts, so that only a pressure reduction on the first compensator surface 16 is required to open the nozzle needle 5.
  • the forces required to generate a pressure drop are comparatively small, so that overall very short positioning times can be achieved.
  • FIG. 2 shows a second exemplary embodiment of an injection nozzle 1 according to the invention, wherein, because of the correspondence with the first exemplary embodiment according to FIG. 1, with regard to components and functions, reference is made to what has been said about FIG. 1 and essentially only the differences are explained below.
  • the first compensator surface 16 is formed on a compensator piston 32 which is guided in a stroke-adjustable manner in a compensator piston guide 33 in the nozzle body 2 and which is drive-coupled to the nozzle needle 5.
  • the compensating piston 32 is preferably fixedly connected to the nozzle needle 5 and can in particular be produced in one piece or in one piece with the latter.
  • nozzle needle 5 and compensator piston 32 are also fundamentally possible to arrange the nozzle needle 5 and compensator piston 32 in such a way that they abut one another on the end face without being firmly connected to one another.
  • the prevailing pressure conditions can cause the nozzle needle 5 and compensator piston 32 to move together, whereby forces always act which press the two components against one another at their end faces.
  • the first compensator surface 16 faces the at least one spray hole 3 and thus acts in the opening direction 15 when pressure is applied.
  • the compensator piston 32 has a second compensator surface 34 on a side facing away from the at least one spray hole 3, which correspondingly lies opposite the first compensator surface 16.
  • the second compensator surface 34 is arranged in a second compensator chamber 35 and can be pressurized there.
  • the second compensator chamber 35 communicates with the supply line 9, so that the high fuel pressure is permanently present in the second compensator chamber 35.
  • the high fuel pressure acting on the second compensator surface 34 generates a force acting in the closing direction 17 on the unit consisting of compensator piston 32 and nozzle needle 5.
  • the first hydraulic path 22 again leads from the first compensator surface 16 through the first compensator chamber 24, through the connecting line 25 and through the first control chamber 23 to the first control surface 21.
  • the second hydraulic path 29 couples the first control surface 21 to the feed line 9, in this embodiment it leads through a feed line 36 into which
  • Feed valve 37 is arranged.
  • the feed valve 37 is designed here as a non-return check valve which blocks towards the feed line 9 and opens towards the first control chamber 23 and which is also spring-loaded in its blocking direction.
  • a further spring 38 is shown in this embodiment, which serves to reset the control piston 18 and is supported on the one hand on the nozzle body 2 and on the other hand on the drive piston 39.
  • the embodiment of the injection nozzle 1 according to the invention shown in FIG. 2 works as follows:
  • Nozzle needle 5 closed ie the needle tip 7 is seated in the sealing seat 8 and thereby separates the at least one spray hole 3 from the feed line 5.
  • the feed line 36 enables pressure equalization between the feed line 9 and the first control chamber 23, so that in the first control chamber 23 there is essentially high fuel pressure.
  • the high fuel pressure is also present on the first compensator surface 16 via the first hydraulic path 22.
  • the compensator surfaces 16, 34 and the pressure stage 12 are matched to one another in such a way that, in the initial state, a resultant result is produced on the nozzle needle 5 or on the unit composed of compensator piston 32 and nozzle needle 5 Sets force that acts in the closing direction 17. Accordingly, the nozzle needle 5 is pressed with its needle tip 7 against the sealing seat 8. In addition, the return spring 26 also acts in the closing direction and exerts an additional closing force on the nozzle needle 5.
  • the actuator 19 is now actuated such that the control piston 18 again executes an opening stroke 31.
  • the control piston 18 penetrates deeper into the first control chamber 23 with its first control surface 21, as a result of which the volume of the first control chamber 23 decreases. This creates a pressure increase in the first control chamber 23, which on the one hand blocks the feed valve 37 and thereby causes the fuel to escape from the first control chamber 23 through the
  • the increasing pressure propagates directly from the first control chamber 23 into the first compensator chamber 24. Accordingly, the pressure on the first compensator surface 16 also rises, so that the forces acting in the opening direction 15 on the unit composed of compensator piston 32 and nozzle needle 5 increase.
  • the pressure in the second compensator chamber 35 remains constant, so that the forces acting in the closing direction on the unit comprising compensator piston 32 and nozzle needle 5 remain constant.
  • the pressure increase caused by the opening stroke 31 is so high that the balance of forces on the unit comprising the compensating piston 32 and the nozzle needle 5 changes in such a way that a resultant force which is effective in the opening direction 15 now arises.
  • the nozzle needle 5 lifts off its sealing seat 8 and the at least one spray hole 3 communicates with the supply line 9. Accordingly, fuel is injected into the combustion chamber 4 through the at least one spray hole 3.
  • the actuator 19 is actuated to reset the control piston 18, the return movement of the control piston 18 being supported by the spring 38.
  • the volume of the first control chamber 23 is increased again, so that the pressure in the first control chamber 23 also drops to a corresponding extent. This pressure drop propagates again via the first hydraulic path 22 to the first compensator chamber 24.
  • the associated drop in pressure at the first compensator surface 16 subsequently leads again to a change in the balance of forces on the unit comprising the compensator piston 32 and the nozzle needle 5, in such a way that a resulting force that is effective in the closing direction 17 again arises.
  • the resulting pressure force thus drives the unit out, assisted by the return spring 26
  • Compensator piston 32 and nozzle needle 5 in the closed position of the nozzle needle 5. As soon as the needle tip 7 moves back into its sealing seat 8, the at least one spray hole 3 is again separated from the feed line 9, so that the injection process is ended.
  • FIG. 2 is also characterized by a particularly simple construction and works with direct control of the nozzle needle 5.
  • FIG. 2 is also characterized by a particularly simple construction and works with direct control of the nozzle needle 5.
  • FIG. 3 shows a third embodiment of an injection nozzle 1 according to the invention, being because of the similarities with the previous ones
  • FIGS. 1 and 2 with regard to components and functions refer to what has been said regarding FIGS. 1 and 2 and essentially only the differences are explained below.
  • the first compensator surface 16 is arranged on the compensator piston 32 on a side facing away from the at least one spray hole 3, so that it acts in the closing direction 17 when pressure is applied. Accordingly, the opposite second compensator surface 34 acts in the opening direction 15.
  • the return spring 26 is accordingly arranged in the first compensator chamber 24 and is supported on the nozzle body 2 and on the first compensator surface 16.
  • the feed valve 37 is constructed in such a way that it blocks in the event of a pressure drop in the first control chamber 23 and thereby prevents fuel from flowing in from the supply line 9 into the first control chamber 23.
  • Infeed valve 37 ensures that the infeed valve 37 can still open when the pressure drop is less pronounced, in order to enable pressure equalization between the first control chamber 23 and the feed line 9.
  • the feed line 36 could also contain a throttle point, which, according to the throttled control piston bypass 30 of the variant shown in FIG. 1, virtually blocks the second hydraulic path 29 during dynamic processes and one Pressure equalization is possible when there are quasi-static conditions.
  • the actuator 19 is designed as a hollow actuator, which is a central one
  • the third embodiment of the injection nozzle 1 according to the invention shown in FIG. 3 works as follows:
  • the nozzle needle 5 is closed, ie its needle tip 7 blocks the at least one spray hole 3.
  • the high pressure fuel is present at the pressure stage 12.
  • High fuel pressure also prevails in the second compensator chamber 35.
  • the second hydraulic path 29 is active, so that pressure equalization between the feed line 9 and the first control chamber 23 can take place. Accordingly, the high fuel pressure also prevails in the first control chamber 23.
  • the high fuel pressure consequently also prevails in the first compensator chamber 24 via the first hydraulic path 22.
  • the closing force predominates, so that the balance of forces on the unit consisting of compensator piston 32 and nozzle needle 5 results in a resulting force effective in the closing direction 17.
  • the return spring 26 acting in the closing direction.
  • the actuator 19 is actuated so that it drives the control piston 18 to carry out the opening stroke 31.
  • the opening stroke 31 acting in the opening direction 15 causes the first control chamber 23 to be enlarged, with the result that the pressure in the first control chamber 23 drops sharply and rapidly.
  • This dynamic behavior leads on the one hand to the fact that the feed valve 37 blocks and prevents fuel from flowing in from the supply line 9 into the first control chamber 23.
  • the pressure drop that forms in the first control chamber 23 propagates into the first compensator chamber 24 via the first hydraulic path 22. Accordingly, the force acting on the first compensator surface 16 in the closing direction 17 is reduced.
  • the pressure stage 12 and the second compensator surface 34 still prevail
  • This embodiment is also distinguished by a comparatively simple structure, it allowing direct actuation of the nozzle needle 5. Like the variant according to FIG. 1, a drop in pressure is also generated in this embodiment for opening the nozzle needle 5 on the first compensator surface 16.
  • FIG. 4 shows a fourth exemplary embodiment of an injection nozzle 1 according to the invention, whereby, because of the correspondences with the previously described exemplary embodiments according to FIGS. 1 to 3, with regard to components and functions, reference is made to what has been said regarding FIGS. 1 to 3 and essentially only the following Differences are explained.
  • the first control surface 21 and the first compensator surface 16 are arranged in a common conversion space 43 and can be pressurized. This conversion space 43 thus forms both the first control space 23 and the first compensator space 24. With this construction, the first hydraulic path 22 is virtually formed within the conversion space 43.
  • control piston 18 and compensating piston 32 are guided coaxially one inside the other, so that it is possible to arrange the first control surface 21 and the first compensating surface 16 radially next to one another.
  • the control piston 18 is designed as a hollow piston which has the compensator piston guide 33 in its interior, so that the compensator piston 32 is guided in a stroke-adjustable manner in the interior of the control piston.
  • the second compensator chamber 35 is also formed in the interior of the control piston 18, in which the return spring 26 is arranged here and which is delimited in the direction of the at least one spray hole 3 by the second compensator surface 34.
  • the return spring 26 is supported in the second compensator chamber 35 on the one hand on the control piston 18 and on the other hand on the compensator piston 32 and in this way generates a prestress acting in the closing direction 17 on the unit formed from the compensator piston 32 and nozzle needle 5 and a prestress acting in the opening direction 15 on the control piston 18 ,
  • the control piston 18 contains at least one transverse bore 44, which connects the second compensator chamber 35 with an annular groove 45.
  • This annular groove 45 communicates via a Connecting line 46 with the supply line 9. Accordingly, the high fuel pressure always prevails in the second compensator chamber 35.
  • the second hydraulic path 29 can again be formed by a control piston bypass 30 which is arranged between the control piston 18 and the control piston guide 20 and in this case connects the annular groove 45 to the conversion space 43 in a communicating manner. Additionally or alternatively, a control piston bypass 30 which is arranged between the control piston 18 and the control piston guide 20 and in this case connects the annular groove 45 to the conversion space 43 in a communicating manner. Additionally or alternatively, a control piston bypass 30 which is arranged between the control piston 18 and the control piston guide 20 and in this case connects the annular groove 45 to the conversion space 43 in a communicating manner. Additionally or alternatively, a control piston bypass 30 which is arranged between the control piston 18 and the control piston guide 20 and in this case connects the annular groove 45 to the conversion space 43 in a communicating manner. Additionally or alternatively, a control piston bypass 30 which is arranged between the control piston 18 and the control piston guide 20 and in this case connects the annular groove 45 to the conversion space 43 in a communicating manner. Additionally or alternatively, a control piston
  • Compensator piston bypass 47 may be provided, which is formed radially between the compensator piston 32 and the compensator piston guide 33 and which communicatively connects the second compensator chamber 35 to the transfer chamber 43.
  • the control piston bypass 30 or the compensating piston 47 is / are each throttled, so that pressure compensation between the conversion chamber 43 on the one hand and the second compensator chamber 35 and / or the annular groove 45 takes place only in quasi-static states, while the respective bypass is carried out in dynamic states 30, 47 is virtually blocked.
  • the compensator piston 32 is connected to the nozzle needle 5 via a piston rod 48.
  • Piston rod 48 and nozzle needle 5 are formed in a first leakage space 49, which leads via a leakage line 50 to a relatively depressurized reservoir, in particular a fuel tank.
  • a leakage line 50 to a relatively depressurized reservoir, in particular a fuel tank.
  • the injection nozzle 1 also contains a second leakage space 51, which is also connected to the leakage line 50 and is arranged on the opposite side of the control piston 18 from the transfer space 43 in the nozzle body 2. Leakages that come from the annular groove 45 along the control piston 18 into the second leakage space 51 can be safely discharged for the actuator 19.
  • the fourth embodiment of the injection nozzle 1 according to the invention shown in FIG. 4 works as follows:
  • the nozzle needle 5 is closed, i.e. its needle tip 7 sits in the sealing seat 8 and thus blocks the at least one spray hole 3 from the feed line 9.
  • the pressure stage 12 is subjected to the high fuel pressure.
  • high fuel pressure also prevails in the second compensator chamber 25.
  • the second hydraulic path 29 that is to say via the control piston bypass 30 and / or via the compensator piston bypass 47, the high fuel pressure is thus also established in the conversion space 43.
  • the force balance on the unit formed from compensator piston 32, nozzle needle 5 and piston rod 48 leads to a resultant force acting in the closing direction 17. Accordingly, the nozzle needle 5 is pressed into its sealing seat 8 with a corresponding closing force.
  • the actuator 19 is now actuated such that it drives the control piston 18 to carry out the opening stroke 31.
  • the opening stroke 31 is again oriented in the direction of the at least one spray hole 3, ie the control piston 18 penetrates into the conversion space 43 with its first control surface 21.
  • a pressure increase occurs in the conversion space 43, which acts directly on the first compensator surface 16.
  • the rise in pressure in the transfer chamber 43 therefore has the consequence that the balance of forces at the unit comprising the nozzle needle 5 changes such that a resulting force is now effective in the opening direction 15. Accordingly, the nozzle needle 5 lifts off its sealing seat 8. Consequently, the fuel under high pressure can be at least one
  • Spray hole 3 reach and can be injected into the combustion chamber 4 through this.
  • the actuator 19 is actuated to reset the control piston 18, which accordingly moves back out of the conversion space 43.
  • the pressure in the conversion space 43 drops rapidly.
  • the dynamics of the pressure drop here also prevent pressure equalization via the throttled second hydraulic path 29, so that the pressure drop is also effective directly on the first compensator surface 16.
  • the balance of forces on the unit comprising the nozzle needle 5 changes again in such a way that a resulting force acting in the closing direction 17 again arises.
  • the nozzle needle 5 then moves back into its sealing seat 8 and blocks the at least one spray hole 3.
  • This embodiment also enables direct control of the nozzle needle 5, the effort required for this being kept relatively low.
  • FIG. 5 shows a fifth exemplary embodiment of an injection nozzle 1 according to the invention, with the components and functions relating to FIGS. 1 and 4 being the same as the previously described exemplary embodiments according to FIGS. 1 to 4 to 4 said and essentially only the differences are explained below.
  • a common conversion space 43 is again provided for the first control surface 21 and for the first compensator surface 16, which serves simultaneously as the first control space 23 and the first compensator space 24 and essentially forms the first hydraulic path 22.
  • the control piston 18 in the variant according to FIG. 5 it is not the control piston 18 but the compensator piston 32 that is designed as a hollow piston, so that the control piston 18 is guided in a centrally adjustable manner in the compensator piston 32. Accordingly, the control piston guide 20 is formed on the inside of the compensator piston 32.
  • Compensator piston 32 is also again arranged a first leakage space 54, in which the return spring 26 is supported on the one hand on the control piston 18 and on the other hand on an extension 52 of the nozzle needle 5.
  • This extension 52 has a number of longitudinal grooves 53 distributed over the circumference, via which the first leakage space 54 communicates with a second leakage space 55, which is connected to a leakage line 56.
  • the leakage line 56 leads, as before, into a relatively unpressurized reservoir.
  • the compensator piston 32 is drive-coupled to the nozzle needle 5 via pins 57.
  • the compensating piston 32 is drive-coupled to the nozzle needle 5 in such a way that only compressive forces can be transmitted.
  • the compensating piston 32 bears axially against the pin 57 and these bears axially against the nozzle needle 5. It is also useful to have the individual components together stroke-adjustable unit consisting of compensating piston 32, pin 57 and nozzle needle 5 to be attached to each other.
  • the second hydraulic path 29 is guided through the compensator piston bypass 47, which the
  • Moving space 43 communicates with the annular groove 45, the hydraulic coupling also being throttled via the second hydraulic path 29.
  • the embodiment of the injection nozzle 1 according to the invention shown in FIG. 5 operates as follows:
  • the nozzle needle 5 closes the at least one spray hole 3, in which the needle tip 7 is seated in the sealing seat 8. Since the at least one spray hole 3 is arranged downstream of the sealing seat 8, it is thus separated from the feed line 9.
  • the pressure stage 12 is permanently subjected to the high fuel pressure, which also prevails in the annular groove 45 via the connecting line 46. Since the initial state is static, the second hydraulic path 29 is active, so that the throttled compensator piston bypass 47 compensates for pressure between the annular groove 45 and the conversion space 43. Accordingly, the high fuel pressure also prevails in the conversion space 43. Consequently, the
  • Nozzle needle 5 stroke-adjustable unit a balance of forces that leads to a resulting force acting in the closing direction 17.
  • the nozzle needle 5 is thus biased into its sealing seat 8.
  • the actuator 19 is now actuated such that the control piston 18 carries out the opening stroke 31.
  • the control piston 18 thus dips deeper into the compensator piston 32, with the result that the first control surface 21 moves in the direction of the opening stroke 31 adjusted.
  • a pressure drop occurs in the conversion space 43. Since the opening stroke 31 is carried out with high dynamics, the
  • Compensator piston bypass 47 insufficient pressure compensation take place, so that the second hydraulic path 29 is virtually blocked. Accordingly, the pressure drop forming in the conversion space 43 can be transferred directly to the first compensator surface 16. As a result, the balance of forces on the stroke-adjustable unit containing the nozzle needle 5 changes in such a way that one in
  • Opening direction 15 sets effective resulting force. Accordingly, the nozzle needle 5 lifts off its sealing seat 8.
  • the at least one spray hole 3 is thus connected to the feed line 9, so that the fuel under high pressure jets into the combustion chamber 4 through the at least one spray hole 3.
  • the actuator 19 is actuated correspondingly to retract the control piston 18. This results in a conversion space 43 again

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention concerne un injecteur (1) destiné à un moteur à combustion interne, notamment d'un véhicule automobile, qui comporte un corps d'injecteur (2), présentant au moins un orifice d'injection (3), et au moins une aiguille d'injecteur (5) qui est guidée dans un élément de guidage d'aiguille (6) et qui permet de commander l'injection de carburant à travers l'orifice d'injection (3). L'objectif de l'invention est de créer un injecteur (1) conçu de manière particulièrement simple. A cet effet, un piston de commande (18), accouplé à un actionneur (19) de manière à entraîner ce dernier, présente une première surface de commande (21); l'aiguille d'injecteur (5) présente une surface de compensation (16) qui est couplée hydrauliquement à la première surface de commande (21) par l'intermédiaire d'une première voie hydraulique (22); et la première surface de commande (21) peut être couplée hydrauliquement, par l'intermédiaire d'une deuxième voie hydraulique (29), à une conduite d'alimentation qui achemine du carburant à haute pression à l'orifice d'injection (3).
EP04729036A 2003-06-10 2004-04-23 Injecteur pour moteurs a combustion interne Expired - Lifetime EP1636484B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10326046A DE10326046A1 (de) 2003-06-10 2003-06-10 Einspritzdüse für Brennkraftmaschinen
PCT/DE2004/000848 WO2004111433A1 (fr) 2003-06-10 2004-04-23 Injecteur pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1636484A1 true EP1636484A1 (fr) 2006-03-22
EP1636484B1 EP1636484B1 (fr) 2007-09-12

Family

ID=33482739

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Application Number Title Priority Date Filing Date
EP04729036A Expired - Lifetime EP1636484B1 (fr) 2003-06-10 2004-04-23 Injecteur pour moteurs a combustion interne

Country Status (6)

Country Link
US (1) US20060032940A1 (fr)
EP (1) EP1636484B1 (fr)
JP (1) JP2006514216A (fr)
KR (1) KR20060021356A (fr)
DE (2) DE10326046A1 (fr)
WO (1) WO2004111433A1 (fr)

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Also Published As

Publication number Publication date
WO2004111433A1 (fr) 2004-12-23
KR20060021356A (ko) 2006-03-07
US20060032940A1 (en) 2006-02-16
DE502004004964D1 (de) 2007-10-25
JP2006514216A (ja) 2006-04-27
DE10326046A1 (de) 2004-12-30
EP1636484B1 (fr) 2007-09-12

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