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
• • 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

Definitions

• the present invention relates to an injection nozzle for an internal combustion engine, in particular in a motor vehicle, having the features of the preamble of the claim
• Such an injection nozzle is known for example from DE 103 26 046 A1 and comprises a nozzle body which has at least one injection hole.
• a nozzle needle is mounted adjustable in stroke, with which an injection of fuel through the at least one injection hole is controllable.
• a booster piston is provided, which is drive-coupled with an actuator and having a translator surface.
• the nozzle needle has a hydraulically coupled to the translator surface control surface.
• the known injection nozzle works with a direct needle control.
• the nozzle needle or a needle assembly comprising the nozzle needle has at least one pressure stage, which is hydraulically coupled to a feed path which supplies the fuel under injection pressure to the at least one injection hole. While on the at least one pressure ⁇ f ⁇ hungs disclosed in the nozzle needle or in the
• Locking forces can be introduced into the nozzle needle or the needle assembly on the control surface.
• the closing forces predominate.
• To open the nozzle needle of the pressure acting on the control surface pressure is lowered, whereby the closing forces are reduced, so that the ⁇ f ⁇ hungs feature predominate.
• the nozzle needle lifts and opens at least one Injection port.
• the pressure reduction at the control surface is achieved by an actuation of the actuator and thus by a stroke of the booster piston.
• a hydraulic space bounded by both the translator surface and the control surface is increased by the stroke of the intensifier piston, thereby decreasing the pressure therein.
• a large gear ratio results in the actuation of the actuator to a fast ⁇ f ⁇ hungsdoch the nozzle needle and a large opening stroke, which is advantageous for the realization of large injection quantities with short injection times.
• a small gear ratio results in the actuation of the actuator to a correspondingly slower opening movement of the nozzle needle and a correspondingly smaller ⁇ f ⁇ hungshub. This is advantageous for the realization of precisely dimensioned, small injection quantities with short injection times.
• Known injection nozzles, with which both small injection quantities and large injection quantities to be realized, thus have a mean transmission ratio as a compromise.
• the actuator in order to still be able to realize a large opening stroke with a comparatively small gear ratio, the actuator must be designed to carry out a correspondingly large stroke on the booster piston. This has the consequence that the actuator builds relatively large volume.
• the available installation space is limited in internal combustion engines.
• the injector according to the invention with the features of the independent claim has the advantage over that two different depending on the needle stroke Translation ratios are effective.
• the gear ratio is constant in known injectors.
• a bypass piston is provided. In a small ⁇ ffhungshub the nozzle needle of the bypass piston remains at its stop, so that the stroke of the booster piston moves only the translator surface. According to the ratio of control surface to
• Translator surface follows the nozzle needle to the stroke of the booster piston.
• the nozzle needle acting on the alternate surface of the bypass piston forces are greater than the forces acting on the storage surface of the bypass piston forces.
• Gear ratio is significantly greater than the first gear ratio, so that the nozzle needle then opens faster and can perform a relatively large ⁇ ffhungshub.
• the injection nozzle according to the invention can thus in the region of the first
• Translation ratio control the nozzle needle to perform small needle strokes, so as to realize accurate and small injection quantities with short injection times.
• the injection nozzle according to the invention by the second ratio, the nozzle needle so control that in comparatively short times large needle strokes and thus large injection quantities can be realized.
• the large second gear ratio leads to the fact that the actuator only has to realize a relatively small stroke and accordingly can be built comparatively small.
• the storage space can be subdivided into a first storage subspace and into a second storage subspace. Furthermore, one is
• Throttle piston provided, which is drive-coupled with the bypass piston at least for the transmission of compressive forces, which is mounted in a stroke-adjustable manner in the booster piston and which contains a throttle path which hydraulically couples the two storage subspaces.
• the storage area is in a first storage subspace limiting, for example, formed directly on the bypass piston first memory sub-area and in a second - A -
• Booster piston, bypass piston and nozzle needle The injection process is thus more stable and has a reproducible accuracy. Furthermore, a sudden, "popping" of the nozzle needle, so an uncontrolled high speed increase in the transition from the first gear ratio to the second gear ratio is avoided.In this way, the larger needle strokes are still relatively accurately controlled.
• FIG. 1 is a greatly simplified, schematic representation of an injection nozzle according to the invention in longitudinal section
• Fig. 2 is a view as in Fig. 1 to a detail of the invention
• FIG. 3 to 7 views as in Fig. 2, but in further different
• an injection nozzle 1 according to the invention comprises a nozzle body 2 which has at least one injection hole 3.
• the injection nozzle 1 is provided for a Brennkrafhnaschine, which may be arranged in particular in a motor vehicle, and is used for injecting fuel into an injection chamber 4, in which the injection nozzle 1 in the assembled state at least in the region of at least one
• Spray hole 3 protrudes into it.
• the injection nozzle 1 contains a nozzle needle 5, which may be part of a needle assembly 6 and with the aid of which an injection of fuel through the at least one injection hole 3 can be controlled.
• the nozzle needle 5 cooperates with its needle tip 7 with a needle seat 8. If the nozzle needle 5 is seated in its needle seat 8, the at least one injection hole 3 is blocked, that is to say that at least one injection hole 3 is separated from a supply path 9, supplied via the injection-pressure fuel, and supplied to the at least one injection hole 3.
• the feed path 9 is guided through the interior of the nozzle body 2, so that the components arranged in the nozzle body 2 virtually "float" in the fuel in the feed path 9. In principle, however, another guidance of the feed path 9 is also possible.
• the nozzle needle 5 or the needle assembly 6 is mounted in the nozzle body 2 in an adjustable stroke.
• This storage is realized here by a first bearing sleeve 10, in which the needle assembly 6 and the nozzle needle 5 is inserted at a distal end of the needle tip 7.
• the first bearing sleeve 10 is attached to an intermediate plate 11, which forms a part of the nozzle body 2.
• the intermediate plate 11 separates the injection nozzle 1 in a
• Needle needle 5 containing needle area and a translator piston 12 and an actuator 13 containing compiler area.
• the feed path 9 is passed through the intermediate plate 11.
• the needle needle 5 and the needle assembly 6 is connected to a closing pressure spring 15 in the
• the needle needle 5 or its needle assembly 6 has a control surface 17, specifically on a side remote from the at least one spray hole 3.
• the control surface 17 delimits a control chamber 18 axially, which is also axially limited relative to the control surface 17 of the intermediate plate 11.
• the control chamber 18 is also enclosed radially by the first bearing sleeve 10.
• the control chamber 18 may be hydraulically coupled to the feed path 9 via a control space path 19.
• This control space path 19 can be formed, for example, as here in the region of the bearing between the nozzle needle 5 or needle assembly 6 and first bearing sleeve 10, for example as a bearing clearance or as at least one longitudinal groove in the first bearing sleeve 10 and / or in the nozzle needle 5 or needle assembly 6 may be formed. It is also possible to control the control room path
• the injection nozzle 1 contains the booster piston 12, which is drive-coupled to the actuator 13.
• the booster piston 12 is mounted adjustable in height in the nozzle body 2.
• the booster piston 12 is inserted into a second bearing sleeve 20 which is fixedly connected to the intermediate plate 12.
• the drive coupling between the booster piston 12 and the actuator 13 causes a stroke adjustment of the actuator 13 inevitably produces an identical stroke adjustment of the booster piston 12.
• Actuator 13 is expediently designed as a piezoelectric actuator, which in the energized state in the stroke direction has a larger dimension than in a de-energized state.
• the booster piston 12 has a booster surface 21 which axially delimits a coupler space 22.
• the translator surface 21 is configured annular. Axially opposite
• the coupler space 22 of the intermediate plate 11 is axially limited. Furthermore, the coupler space 22 is bounded radially by the second bearing sleeve 20. The coupler space 22 is hydraulically coupled by a control path 23 with the control chamber 18.
• the control path 23 is realized here in the form of at least one bore, which penetrates the intermediate plate 11.
• the coupler space 22 can be hydraulically coupled to the feed path 9 via a coupler space path 24.
• the coupler space path 24 can be formed radially between the booster piston 12 and the second bearing sleeve 20, for example as a radial play or as at least one longitudinal groove in the second bearing sleeve 20 and / or in the It is also possible in principle to configure the coupler space path 24 by a transverse bore which penetrates the second bearing sleeve 20 and connects the coupler space 22 with the feed path 9.
• the coupler space path 24 is throttled.
• the injection nozzle 1 is also equipped with an evasive piston 25, which is mounted in a stroke-adjustable manner in the booster piston 12.
• the booster piston 12 is designed as a hollow piston open on one side.
• the bypass piston 25 protrudes into the coupler space 22 and has there an evasion surface 26, which likewise limits the coupler space 22 accordingly.
• the bypass piston 25 On the side facing away from the escape surface 26, the bypass piston 25 also has a storage surface 27, which defines a storage space 28 which is formed in the booster piston 12.
• the booster piston 12 can optionally have at least one throttle 29, which hydraulically couples the storage space 28 to the feed path 9.
• the bypass piston 25 may include a throttle 30 which hydraulically couples the reservoir 28 to the coupler chamber 22.
• a throttle 30 may also be formed radially between bypass piston 25 and booster piston 12, e.g. in the form of a corresponding radial clearance and / or in the form of at least one longitudinal groove in the booster piston 12 and / or in the bypass piston 25.
• the bypass piston 25 is axially biased by a return spring 31 against a stop 32.
• the restoring spring 31 is supported on the one hand on the booster piston 12 and on the other hand on the bypass piston 25, namely on the storage surface 27.
• the stop 32 is arranged stationary with respect to the nozzle body 2. In the present case, the stop 32 is formed on the intermediate plate 11. The contact between
• Evasive piston 25 and stop 32 is advantageously carried out so that the escape surface 26 is as large as possible.
• the contacting is quasi punctiform, which is achieved by a convex shaping of the bypass piston 25 in the region of its escape surface 26.
• the booster piston 12 is biased with an opening compression spring 33 in its opening direction.
• the opening compression spring 33 is supported on the one hand on the second bearing sleeve 20 and on the other hand on a collar 34 of the booster piston 12 from.
• the volume of the storage space 28 is expediently greater than the common volume of the coupler space 22 and the control space 18.
• coupler space 22 and control chamber 18 form separate spaces that are interconnected by the control path 23
• control chamber 18 and coupler space 22 coincide in a common space.
• the injection nozzle 1 operates as follows:
• the nozzle needle 5 is in the needle seat 8. Accordingly, the at least one injection hole 3 is locked.
• the control surface 17 has its greatest distance from the intermediate plate 11.
• the control chamber 18 thus has its largest volume.
• the actuator 13 is energized and thus has its greatest extent. Accordingly, the booster piston 12 is maximally in the direction
• the coupler space 22 thus has its smallest volume. Furthermore, the bypass piston 25 abuts against the stop 32. In the storage space 28, in the coupler space 22 and in the control chamber 18, the same pressure prevails as in the feed path 9, that is, the injection pressure.
• the actuator 13 In order to carry out an injection of fuel through the at least one spray hole 3 into the injection space 4, the actuator 13 is discharged, that is, the energization of the actuator 13 is interrupted. The actuator 13 is thus operated inversely. This means that the actuator 13 must be energized to close the at least one injection hole 3.
• the storage space 28 - as explained above - at least in the initial state has a larger volume than the total volume of the coupler chamber 22 and the control chamber 18, the pressure in the storage chamber 28 decreases slower than in the coupler chamber 22 and the control chamber 18. Accordingly, the effective on the storage surface 27 Pressure forces greater than the pressure acting on the alternate surface 26 pressure forces. As a result, the bypass piston 25 initially remains biased against its stop 32.
• the opening forces acting on the nozzle needle 5 or on the needle dressing 6 are then greater than the effective closing forces. Accordingly, the nozzle needle 5 lifts off from the needle seat 8. As a result, the at least one spray hole 3 communicates with the feed path 9. The injection process begins.
• the nozzle needle 5 and the needle assembly 6 is equipped with at least one pressure stage 36 and 37, which is permanently coupled hydraulically to the feed path 9 /.
• This first booster ratio is at least initially defined by the ratio of the control surface 17 to the translator surface 21.
• Transmission ratio is comparatively small, so that a small stroke of the booster piston 12 also causes a comparatively small stroke of the nozzle needle 5, which may already be greater than the stroke of the booster piston 12. If only a small injection quantity to be realized can now within this first Phase, during which the first ratio is present, the actuator 13 are energized again to stop the initiated opening movement and reverse. While the opening movement of the booster piston 12 is intensively supported by the ⁇ ffiiungstikfeder 33, the closing pressure spring 15 supports the closing movement of the nozzle needle. 5 However, if a larger injection quantity to be realized, the outflow of the actuator 13 is maintained longer, so that the booster piston 12 can move further away from the intermediate plate 11. Accordingly, the nozzle needle 5 can continue to stand out from its needle seat 8.
• the bypass piston 25 lifts off from the stop 32 and in particular enters the storage space 28.
• the new, second transmission ratio is defined by the ratio of the control surface 17 to the total area of translator surface 21 and alternate surface 26.
• the stroke of the booster piston 12 together with the stroke of the Ausweichkolbens 25 thus produce a relatively large stroke adjustment of the nozzle needle 5.
• results for the nozzle needle 5 a particularly high opening speed, wherein in addition a comparatively large opening stroke can be realized.
• the required stroke of the actuator 13 can remain relatively small due to the large second opening ratio, so that the actuator 13 and thus the injection nozzle 1 can build comparatively small.
• the injection nozzle 1 are thus control surface 17, translator 21, alternate surface 26, memory surface 27, the maximum possible Aktorhub and the maximum possible Düsennadelhub coordinated so that when Hubver ein of the actuator 13 to open the nozzle needle 5, the described two-phase or two-stage stroke adjustment for the nozzle needle 5 sets.
• the bypass piston 25 bears against its stop 32.
• the gear ratio is relatively small.
• the bypass piston 25 moves away from its stop 32 during the second phase or second stage.
• the associated gear ratio is relatively large.
• the storage space 28 is subdivided into a first storage subspace 40 and into a second storage subspace 41 for this purpose.
• a throttle piston 42 is provided, which is drive-coupled with the bypass piston 25 at least for the transmission of compressive forces.
• the throttle piston 42 is also mounted in a stroke-adjustable manner in the booster piston 12 and contains a throttle path 43 which hydraulically couples the two storage subspaces 40 and 41 throttled.
• the throttle path 43 expediently has a throttle 44, which is arranged between a longitudinal bore 45, which opens into the second storage subspace 41, and a transverse bore 46, which opens into the first storage subspace 40.
• the throttle piston 42 is fixedly connected to the bypass piston 25.
• the storage area 27 is subdivided into a first storage subarea 47 and a second storage subarea 48.
• the first memory sub-area 47 is at least in the variants of FIGS. 2 and 3 formed directly on the bypass piston 25 and limits the first storage part space 40.
• the second memory sub-area 28 is formed on the throttle piston 42 and limits the second memory sub-area 41st
• the retraction of the bypass piston 25 into the storage space 28 is throttled by the fact that, for this purpose, fuel has to be displaced from the second storage subspace 41 through the throttle path 43 into the first storage subspace 40.
• the embodiment according to FIG. 3 differs from that according to FIG. 2 in that the throttle path 43 has its path end radially on the throttle piston 42.
• the throttle 44 forms this path end here.
• the throttle piston 42 includes a bypass path 49, here through a connecting bore 50 between the longitudinal bore
• bypass path 49 thus bypasses the throttle path 43 and is here also equipped with a non-return valve 51, which blocks when retracting the throttle piston 42 into the second storage subspace 41.
• the throttle path 43 is also controlled as a function of the throttle piston stroke.
• the fuel volume is first displaced from the second storage subspace 41 through the throttle path 43 into the first storage subspace 40.
• the check valve 51 locks in this movement, the connecting hole 50. From a certain retraction stroke passes over a control edge 52 of the booster piston 12 said path end, so here the throttle 44, whereby the throttle path 43 is locked.
• the embodiment according to FIG. 4 also has a throttle path 43 controlled by the throttle piston stroke and a bypass path 49 with a check valve 51.
• the embodiment according to FIG. 4 differs from those according to FIGS. 2 and 3 in that the throttle piston 42 and the bypass piston 25 separate components are only loosely abut each other.
• the return spring 31 drives the
• the bypass path 49 here has an axial mouth end 53, which is closed at an axial contact between the escape piston 25 and throttle piston 42.
• the bypass path 49 is closed, the throttle path 43 is active and the retraction of the bypass piston 25 is throttled.
• To extend the bypass piston 25 can lift off the throttle piston 42, whereby the bypass path 49 is opened.
• the bypass piston 25 can thereby extend relatively quickly and relatively undamped and occupy its starting position with abutment against the stop 32.
• Throttle piston 42 follows, driven by the return spring 31.
• a further throttle 54 may be arranged.
• the non-return valve 51 is formed by the interaction of bypass piston 25 and throttle piston 42.
• the first memory sub-area 47 is configured on the bypass piston 25 per se. Depending on the tightness of a supported on the bypass piston 25 head 55 of the throttle piston 42, this first memory sub-area 47 may also be formed on this head 55.
• the injection nozzle 1 can also be equipped with an escape path 56 in the region of the bypass piston 25.
• This escape path 56 is formed in the embodiments shown here by an escape passage 57 which penetrates the bypass piston 25 from the storage surface 27 to the escape surface 26 and is arranged in particular coaxially in this.
• the escape path 56 and the escape passage 57 may also have any other shape and arrangement.
• the escape path 56 may be formed by a deflection channel 57 arranged obliquely in the bypass piston 25.
• the escape path 56 is designed so that it is adjacent to the stop 32 Evasive piston 25 is locked.
• the blocking effect of Ausweichpfads 56 in the initial state of the bypass piston 25, ie in abutting the stop 32 Ausweichkolben 25 is achieved in the preferred embodiments shown here, characterized in that the bypass piston 25 at its
• Dodge surface 26 has an annular sealing zone 58.
• This sealing zone 58 encloses an opening 59 of the escape channel 57, which is associated with the escape surface 26 and lies in this.
• the bypass piston 25 abuts against the stop 32 with its sealing zone 58.
• the sealing zone 58 thereby separates the escape path 56 from the coupler space 22 tightly.
• Deviating from the central arrangement of Evasive channels 57 in FIGS. 5 to 7 can be designed in another embodiment Ausweichkolben 25 and / or intermediate plate 11 such that the sealing surface 58 is on any other diameter, for example on the outer diameter of the bypass piston 25.
• the escape path 56 can be throttled.
• the throttle path 56 contains a throttle 60 for this purpose.
• the throttle 60 is arranged in the escape passage 57.
• the escape path 56 can optionally be configured so that it is blocked at a predetermined or a predetermined deviation stroke of the bypass piston 25, in which the bypass piston 25 moves into the storage space 28.
• This is achieved here, for example, by means of a storage space check valve 61, which blocks the escape path 56, here the escape channel 57 when the predetermined deviation stroke is reached.
• the storage space valve 61 comprises, for example
• Valve member 62 which cooperates with a circular valve seat 63.
• the valve seat 63 is formed on the bypass piston 25, specifically on the storage area 27 thereof.
• the valve seat 63 encloses an opening 64 of the bypass channel 57, which is assigned to the storage area 27, ie lies in the latter.
• the valve member 62 moves into its valve seat 63 and blocks said
• the valve member 62 is here exemplarily equipped with a flat end face; the valve seat 63 is shaped to be complementary. Alternatively, the valve member 62 may also have any other suitable shape, e.g. a conical shape or a spherical shape; the valve seat 63 is then formed in each case complementary.
• the pressure in the coupler chamber 22 increases so far that the bypass piston 25 lifts off the stop 32, although the actuator 13 is not yet driven to perform an opening stroke , This is, for example, the relative compressibility of the comparatively large Memory space 28 trapped hydraulic volume due.
• the injection nozzle 1 is actuated to carry out an injection process in the case of the bypass piston 25 lifted off from the stop 32, the second gear ratio is present at the opening stroke of the booster piston 12 from which the booster piston 12 is withdrawn from the actuator 13 at high speed but with little force.
• the bypass piston 25 could move in the opposite direction due to the changing pressure conditions, whereby the required pressure drop in the coupler chamber 22 does not occur or only delayed. In extreme cases, the nozzle needle 5 remains closed.
• the alternative path 56 provided in the embodiments of FIGS. 5 to 7 provides a remedy. For as soon as the rising in corresponding transient operating conditions in the coupler chamber 22 pressure lifts the bypass piston 25 from the stop 32, takes place via the escape path 56, a pressure equalization between the storage space 28 and
• Coupler space 22 The return spring 31 can then move the bypass piston 25 back to the starting position in which it rests against the stop 32. This ensures that during an opening operation of the actuator 13, the bypass piston 25 initially bears against the stop 32, so that at the beginning of the opening operation, the first gear ratio is present, in which the booster piston 12 is withdrawn slowly, but with great force from the actuator 13.
• the throttle 60 and the throttling of the alternate path 56 serves to ensure that in the desired switching from the first ratio to the second ratio, the pressure balance between the coupler chamber 22 and storage space
• the storage space check valve 61 for the second phase or second stage of the needle opening can ensure that the pressure compensation between the coupler space 22 and the storage space 28 is terminated when the escape stroke of the escape piston 25 is reached. This also makes it possible to avoid premature return of the bypass piston 25 against its stop 32.

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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)

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• 2005
  • 2005-06-09 DE DE102005026514A patent/DE102005026514B4/de not_active Expired - Fee Related
  • 2005-12-21 WO PCT/EP2005/057047 patent/WO2006087046A1/fr not_active Ceased
  • 2005-12-21 JP JP2007555465A patent/JP2008530438A/ja not_active Withdrawn
  • 2005-12-21 US US11/813,794 patent/US20080093484A1/en not_active Abandoned
  • 2005-12-21 DE DE502005006031T patent/DE502005006031D1/de not_active Expired - Lifetime
  • 2005-12-21 AT AT05825330T patent/ATE414848T1/de not_active IP Right Cessation
  • 2005-12-21 EP EP05825330A patent/EP1853813B1/fr not_active Expired - Lifetime

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