EP1654453A1 - Injector for fuel injection systems of combustion engines, particularly direct injection diesel engines - Google Patents

Injector for fuel injection systems of combustion engines, particularly direct injection diesel engines

Info

Publication number
EP1654453A1
EP1654453A1 EP20040738750 EP04738750A EP1654453A1 EP 1654453 A1 EP1654453 A1 EP 1654453A1 EP 20040738750 EP20040738750 EP 20040738750 EP 04738750 A EP04738750 A EP 04738750A EP 1654453 A1 EP1654453 A1 EP 1654453A1
Authority
EP
European Patent Office
Prior art keywords
nozzle needle
nozzle
injector
piezo actuator
needle
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.)
Withdrawn
Application number
EP20040738750
Other languages
German (de)
French (fr)
Inventor
Sebastian Kanne
Godehard Nentwig
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
Priority to DE10336327.0A priority Critical patent/DE10336327B4/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to PCT/DE2004/001301 priority patent/WO2005014995A1/en
Publication of EP1654453A1 publication Critical patent/EP1654453A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02Fuel-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
    • F02M45/04Fuel-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
    • F02M45/08Injectors peculiar thereto
    • F02M45/086Having more than one injection-valve controlling discharge orifices
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603Injectors peculiar thereto with means directly operating the valve needle using piezo-electric or magnetostrictive operating means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21Fuel-injection apparatus with piezo-electric or magnetostrictive elements
    • F02M2200/215Piezo-electric or magnetostrictive elements being able to tilt in its housing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46Valves, e.g. injectors, with concentric valve bodies
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/704Linkage 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

Abstract

An injector for fuel injection systems of combustion engines, particularly direct injection diesel engines, comprises a piezo actuator (16), which is placed inside an injector body (10) and which, via first spring means (35), is held in contact with the injector (10) and with a sleeve-like intensifier plunger (33). In addition, a nozzle body (20) is provided, which is connected to the injector body (10), has at least one nozzle discharge opening (26, 27), and inside of which a graduated (first) nozzle needle (21) is guided in an axially displaceable manner, and (second) spring means (54) are provided, which are placed inside the intensifier plunger (33) and which, together with the injection pressure acting on the rear side on the (first) nozzle needle (21), hold the (first) nozzle needle (21) in the closed position. In addition, the injector comprises an (outer) control space (47), which is formed at the nozzle needle-side end of the intensifier plunger (33), and which is connected, via at least one leakage gap, to a fuel supply (18) that is under injection pressure. The (first) nozzle needle (21) is displaced in the opening direction (36) by the fuel located inside the control space (47).

Description


   <Desc / Clms Page number 1>
 



   INJECTOR FOR FUEL INJECTION SYSTEMS FROM
INTERNAL COMBUSTION ENGINES, ESPECIALLY FROM
DIRECT INJECTING DIESEL ENGINES
State of the art
The invention relates to an injector according to the preamble of
Claim 1.



   An injector of the aforementioned type is the subject of (not previously published) DE ... (R. 305 558). Advantages of this known injector are in its comp. uncomplicated construction (few individual parts) and direct control of the nozzle needle by the piezo actuator. The speed of the nozzle needle movement can be set via the voltage curve of the piezo actuator. In addition, the well-known injector is characterized by the fact that it does not require a fuel return.



  Advantages of the invention The object of the present invention is to compare with simple means to create a way to gradually control and actuate the nozzle outlet.



  According to the invention the object is achieved in an injector of the type described in the introduction by the characterizing features of patent claim 1.

 <Desc / Clms Page number 2>

 



   Advantageous embodiments of the basic idea of the invention are contained in claims 2-9.



   The invention advantageously makes it possible to actuate the nozzle outlet in stages by actuating the two nozzle needles one after the other by appropriate voltage application of the piezo actuator. The system according to the invention also has the advantage without
Get along return.



  drawing
In the drawing, an embodiment of the invention is shown, which is described in detail below. It shows (each schematically):
1 shows an embodiment of a directly controlled common
Rail injector with piezo actuator, in vertical longitudinal section,
Fig. 2 shows a lower portion of the injector of FIG. 1, in an enlarged view compared to FIG. 1, and
FIG. 3-in diagram representation - the force exerted by the piezo actuator on the converter disks, plotted over the stroke of the piezo actuator.



    Description of the exemplary embodiment In FIGS. 1 and 2, 10 denotes a cylindrical injector body with a continuous recess 11 that is cylindrical over the major part of its longitudinal extent. At its upper end, the recess 11 initially has a conically tapering section 12,

 <Desc / Clms Page number 3>

 the one that turns into a right-angled one that finally opens outwards
Section 13, 14 merges. Arranged in the cylindrical section of the recess 11, which is numbered 15, is a likewise cylindrical piezo actuator 16 with a comparatively large longitudinal extension, the diameter of which is smaller than the inside diameter of the recess section 15.



   This results in between the outer wall of the piezo actuator 16 and the
Inner wall of the injector body 10 is an annular space 17. For centering the piezo actuator 16 within the injector body
10 serves on the one hand the conical section 12 of the axial recess 11.



   On the other hand, if necessary in the annular space 17 in certain axial
Distances from each other that are permeable to fluid can be provided (not shown).



   The upper, angled section 13, 14 of the recess 11 functions as
Cable entry for the power supply of the piezo actuator 16.



   At the upper end of the injector body 10 is a fuel supply 18, for. B.



   High-pressure connection of a common rail system is provided, which is in hydraulic connection with the annular space 17 via a pressure channel 19.



  At the lower end of the injector body 10 and coaxially with it, there is a nozzle body 20, which receives a first nozzle needle 21. The nozzle body 20 is fastened to the injector body 10 by means of a union nut (clamping nut) 22 in such a way that it comes into sealing contact with a rear end face 23 on a lower end face 24 of the injector body 10.



  To accommodate the first nozzle needle 21, the nozzle body 20 has an interior 25, which is open at the top and has multiple steps, the one at the bottom

 <Desc / Clms Page number 4>

 in several nozzle outlet bores 26 to 29 opening conical
Valve seat 30 forms.



   At its upper end, the first nozzle needle 21 has a section 31 of larger diameter, which is fitted into a cylindrical interior 32 of a sleeve-shaped, downwardly open booster piston 33.



   The upper end of the booster piston 33 is formed by a collar 34. A helical compression spring 35, which is arranged in the annular space 17 — in this case enclosing the booster piston 33 — on the one hand on the end face 23 of the nozzle body 20 and on the other hand on the collar 34 of the booster piston 33, holds the booster piston 33 with the piezo actuator on the front
Investment. Due to the pressure acting on the piezo actuator 16 in the direction of arrow 36 from the compression spring 35 via the booster piston 33, the top side 37 of the piezo actuator 16 is sealed against the injector body 10, and the electrical connection (not shown) can thus be angled
Bores 13, 14 are guided out of the injector body 10.



   A special feature, which can be seen in particular from FIG. 2, is that the first nozzle needle 21 has a continuous, concentric axial recess 39, which is stepped by a shoulder 38 and in which a second nozzle needle 41, which is likewise stepped by a shoulder 40, is axially displaceably fitted.



  In the lower part of the nozzle body 20, as a component of the nozzle body interior 25, a cylindrical pressure chamber 42 is formed concentrically surrounding the first nozzle needle 21, which has bores 43, 44 in the nozzle body 20 and an annular space 45 formed between the nozzle body 20 and the clamping nut 22 is hydraulically connected to the annular space 17 of the injector body 10.

 <Desc / Clms Page number 5>

 



   The interior 25 of the nozzle body 20 has a stepped top
Diameter widening 46 in which the booster piston 33 is guided such that a first control chamber 47 formed in the widened interior part 46 below the booster piston 33 has a
Leakage gap 48 (see in particular FIG. 2) is in hydraulic connection with the annular space 17 of the injector body 10. A section 49 of the
Nozzle body interior 25 with a comparatively small diameter serves to guide the first nozzle needle 21 within the nozzle body 20.



   This guide fit 49 is also designed so that there is a leakage gap. The first control chamber 47 is thus hydraulically connected to the cylindrical chamber 42 via the second leakage gap 49, which in turn is connected via the
Recesses 43 to 45 are pressurized from the annular space 17 of the injector body 10. The interior 32 of the booster piston 33, which extends above the nozzle needle 21, is also hydraulically connected to the high-pressure pressurized annular space 17 of the injector body 10, specifically via a lateral bore 50 in the booster piston 33.



   The upper (thickened) section 31 of the first nozzle needle 21 is guided in the booster piston 33 such that a (further) leakage gap 51 (see FIG. 2) results. There is therefore also a hydraulic one via this (third) leakage gap 51
Connection between the first control chamber 47 and the pressurized annular space 17 of the injector body 10 is established.



   Another special feature is that a (second) inner control chamber 52 is formed within the axial recess 39 - between its shoulder 38 and the shoulder 40 of the second nozzle needle 41 - which is in hydraulic connection with the first (outer) control chamber 47. The second (inner) control space 52 has a smaller volume than the first (outer) control space 47. The hydraulic connection of the two control spaces is carried out through a bore 53 which penetrates the first nozzle needle 21 obliquely in the area of its shoulder 38.

 <Desc / Clms Page number 6>

 



   As can further be seen in particular from FIG. 2, there is in the interior
32 of the booster piston 33 a (second) helical compression spring 54 is arranged which on the first nozzle needle 21 in the closing direction (arrow
55) exerts directed force. The (second) compression spring 54 becomes the first
Nozzle needle 21 kept closed during the breaks between the injection processes and when the vehicle is at a standstill. 1 and 2, the opening position of the two nozzle needles 21 and 41 is shown. In this
Position takes place an injection process on which all
Outlet openings - in the example shown, the bores 26 to
29 are involved.

   In this case, the cylindrical pressure chamber 42 comes out
Fuel through the outlet bores 26 to 29 into the cylinder combustion chamber (not shown) of the internal combustion engine.



   The first formed at the lower end of the translator piston 33
Control chamber 47 is used for hydraulic length compensation and as a hydraulic translator for the expansion movement of piezo actuator 16 with respect to first nozzle needle 21.



  1 and 2 (in particular FIG. 2) also make it clear that the (upper) end of the second nozzle needle 41 on the piezo actuator side is acted upon by third spring means 56 arranged in the interior of the booster piston 33 in the direction of the closed position (arrow 55). The third spring means 56 is a helical compression spring which is arranged concentrically with and encompassed by the second spring means (helical compression spring 54) and is supported on the one hand on the second nozzle needle 41 and on the other hand on the (upper) end of the translator piston interior 32 on the piezo actuator side , For this purpose, a shoulder 57 is formed at the (upper) end of the second nozzle needle 41 on the piezo actuator side, to which a pin part 58 with a smaller diameter is connected, on which the helical compression spring 56 is arranged.

 <Desc / Clms Page number 7>

 



   As can further be seen in particular from FIG. 2, the axial recess 39 through which the second nozzle needle 41 extends has the first
Nozzle needle 21 in its (lower) area on the nozzle outlet side
Diameter expansion on. This creates an annular cylindrical cavity 59 surrounding the (lower) area of the second nozzle needle 41 on the nozzle outlet side. A radial bore 60 is machined into the first nozzle needle 21 and hydraulically connects the cylindrical pressure chamber 42 to the annular cylindrical cavity 59.



   Another special feature is that the nozzle
Exit regions 26 to 29 containing (lower) end region 61 of the
Nozzle body 20 and the - each acting as a closing body -
End sections 62, 63 of the two nozzle needles 21 and 41 are conical, so that the end sections 62, 63 of the nozzle needles 21 and 41 are in a common closing or Add the open position (Fig. 1 and 2) to a uniform conical surface.

   The dimensions or position of the nozzle outlet openings 26 to 29 and the conical end sections 62, 63 of the two nozzle needles 21 and 41 are matched to one another in such a way that the two radially inner nozzle outlet openings 26, 27 extend from the conical end section 63 second nozzle needle 41 are actuated and the two radially outer nozzle outlet openings 28, 29 cooperate with the conical end section 62 of the first nozzle needle 21.



  The injector described above works as follows: The piezo actuator 16 is deenergized during spray breaks. If the piezo actuator 16 is now electrically actuated, it expands and moves the booster piston 33 downward (in the direction of arrow 55) against the force of the springs 35, 54 and 56. The volume of the control rooms 47 and 52 decreases and the pressure in the control rooms 47, 52 increases. Thereby

 <Desc / Clms Page number 8>

 a force in the opening direction (arrow 36) is exerted on the two nozzle needles 21 and 41. Once the opening force the closing pressure and
Exceeds the spring force, the nozzle needle that requires less opening force moves in the opening direction (arrow 36). In the embodiment shown in FIGS. 1 and 2, this is the second (inner)
Nozzle needle 41.

   Because this is the combustion chamber of the
Pressure area facing the internal combustion engine is smaller than that of the first (outer) nozzle needle 21. As soon as the second (inner) nozzle needle 41 opens, the pressure in the control spaces 47, 52 does not decrease any further. After a short while
Stroke (approx. 0.1 mm, depending on the hydraulic flow) beats the second
Nozzle needle 41 at its upper stop, the pin part 58 coming into contact with the inner (upper) end face of the booster piston 33. In order to now also move the first (outer) nozzle needle 21 into its open position (FIGS. 1 and 2), a (further) increase in the electrical voltage applied to the piezo actuator 16 is required.

   The piezo actuator 16 expands again in the axial direction (arrow 55) to such an extent that the first nozzle needle 21 now also moves into the open position (FIGS. 1 and 2) and opens the nozzle outlet openings 28, 29. As a result of the path translation effected by the translator piston 33, the first nozzle needle 21 is able to carry out a maximum stroke which is clearly above the stroke of the piezo actuator 16. (Since the first nozzle needle 21 is supplied with fuel from the inside and outside, the stroke can be significantly less than 200 μm.) As soon as the nozzle needles 21, 41 have left the stroke region of the seat throttle, they are pressure-balanced.

   The piezo actuator 16 then only has to keep the pressure in the control spaces 47, 52 above the high pressure (rail pressure) of the fuel supplied at 18 (FIG. 1) via the booster piston 33 so that the resistances of the springs 35, 54 and

 <Desc / Clms Page number 9>

 
56 can be overcome. The longest possible activation period is determined by the
Leakage determined from the control rooms 47.52. Does the pressure drop in the
Control rooms 47.52 on the rail pressure, so close the nozzle needles
21.41. To actively close the nozzle needles 21, 41, the
Piezo actuator 16 applied electrical voltage can be reduced to zero.



   The piezo actuator 16 then contracts and the pressure in the
Control rooms 47.52 drops below the rail pressure. Thereby they experience
Nozzle needles 21, 41 closing forces, move in the direction of arrow 55 and close the nozzle outlet openings 26 to 29. The first (outer)
Compression spring 35 prevents the piezo actuator 16 from moving away from the booster piston
33 separates.



   In the exemplary embodiment shown in FIGS. 1 and 2, these are
Volumes of the control chambers 47, 52 and the surfaces of the nozzle needles 21, 41 acted upon by the control chamber pressures or by the pressure of the fuel supply 18, 19 or by the spring mean pressure so that the two nozzle needles 21, 41 change by changing the
Open the piezo actuator 16 of the applied electrical voltage one after the other and let it close at the same time by removing the voltage from the piezo actuator 16.



  In the following, a simple calculation example shows what forces and what powers are required to carry out the functions described: With an outer diameter of the second (inner) nozzle needle 41 of 1.7 mm (seat diameter: 1.6 mm), at 1600 bar Rail pressure 321 N is required to move the second nozzle needle 41 into the open position (FIGS. 1 and 2). With a stroke ratio of 4: 1 for the second nozzle needle 41, this corresponds to 1284 N piezo force, plus the spring forces. As soon as the

 <Desc / Clms Page number 10>

 second nozzle needle 41 is opened a few micrometers, the necessary (further) opening force decreases very sharply since the pressure on the underside of the needle increases.

   When the second nozzle needle 41 has reached its full stroke - 0.08 mm is sufficient because the radially inner nozzle
Outlet openings 26, 27 in this example the smaller hydraulic
Have flow, the piezo actuator 16 has been extended by 0.02 mm (neglecting the leakage losses and the compressibility). In order to open the first (outer) nozzle needle 21 with an inner diameter (= inner seat diameter) of 2.0 mm and an outer diameter of 2.8 mm, a force of 482, 54 N is required. At a
Stroke ratio of 1: 3, this corresponds to a force of 1450 N am
Piezo actuator 16. This force is higher than the opening force of the second (inner) nozzle needle 41.



   (With a correspondingly different selection of the stroke ratio. For the first and the second nozzle needle (21 or 41), if necessary, it can also be achieved that first the first (outer) nozzle needle (21) and only then the second (inner) nozzle needle (41) opens.)
In order to achieve the necessary opening stroke of the first nozzle needle (21) of 0.15 mm - more is not necessary, since the first nozzle needle (21) is supplied with fuel from the inside and outside - the piezo actuator (16) must be turned again by 0 .05 mm long. In this example, this results in a necessary total stroke of the piezo actuator (16) of approximately 0.075 mm, plus losses of leakage and compressibility.

   Assuming that a total of a further 0.025 mm piezo actuator stroke is required to compensate for the losses, a piezo actuator which fulfills the force-displacement curve shown in FIG. 3 and labeled 64 can be used.

 <Desc / Clms Page number 11>

 



   With an enlargement of the seat angle and a little tighter
Designing the necessary strokes of the first and second nozzle needles (21 and 41) can also achieve significantly smaller values for maximum force and stroke. For example, with a seat angle of 90 (in the exemplary embodiment shown in FIGS. 1 and 2, the seat angles are somewhat smaller than 90), the second (inner) nozzle needle 41 would only have a stroke of 60 μm and the first (outer) nozzle needle 21 only still need a stroke of 100 µm. This would result in a significantly smaller maximum stroke of the piezo actuator 16 of only 80 for the same transmission ratios and the same surcharge for leakage (see curve 65 in FIG. 3).

Claims

PATENT CLAIMS 1. Injector for fuel injection systems of internal combustion engines, in particular of direct-injection diesel engines, with a piezo actuator (16) arranged in an injector body (10), which acts on the first Spring means (35) on the one hand is held in contact with the injector body (10), on the other hand with a sleeve-like booster piston (33), with at least one nozzle connected to the injector body (10). Nozzle body (20) having an outlet opening (26-29), in which a stepped (first) nozzle needle (21) is guided axially displaceably, with second spring means (54) arranged inside the booster piston (33),
   which - together with the injection pressure acting on the back of the (first) nozzle needle (21) - the (first) nozzle needle (21) in Hold the closed position and with an (outer) control chamber (47) formed at the nozzle needle end of the booster piston (33) and which is connected via at least one leakage gap to a fuel supply (18) under injection pressure, the (first) Nozzle needle (21) through the one located in the (outer) control chamber (47) Fuel is acted upon in the opening direction (55), and the (first) Nozzle needle (21) with a rear area (31), the larger one Has a diameter as a region on the nozzle outlet side of the (first) Nozzle needle (21), into the interior (32) of the booster piston (33)
 is fitted, characterized in that the first nozzle needle (21) a  <Desc / Clms Page number 13>  has a continuous, concentric axial recess (39) stepped by a shoulder (38), in which a second nozzle needle (41) likewise stepped by a shoulder (40) is axially displaceably fitted, within the axial recess (39) - between its shoulder (38) and the shoulder (40) of the second nozzle needle (41) - a (second) inner control chamber (52) is formed, which is in hydraulic connection with the outer (first) control chamber (47), and that the control chamber volumes and the from the control room pressures or from the Fuel supply pressure (18, 19) or
 surfaces of the nozzle needles (21, 41) acted upon by the spring mean pressure are matched to one another in such a way that the two nozzle needles (21, 41) pass through Have the change in the electrical voltage applied to the piezo actuator (16) opened one after the other.
2. Injector according to claim 1, characterized in that the liquid pressurized Surfaces of the second nozzle needle (41) in relation to the surfaces of the first nozzle needle (21) pressurized with liquid are designed such that the second nozzle needle (41) is already at a vgiw. low control chamber pressure (cf. low piezo actuator voltage), the first nozzle needle (21), however, only when cf. high Control room pressure (cf. high piezo actuator voltage) can be opened.
3. Injector according to claim 1 or 2, characterized in that the two control spaces (47, 52) are hydraulically connected to one another by a bore (53) penetrating the first nozzle needle (21).  <Desc / Clms Page number 14>  
4. Injector according to one or more of the preceding claims, wherein the interior (32) of the booster piston (33) with the Fuel supply (18) is hydraulically connected, characterized in that the (upper) end of the second nozzle needle (41) on the piezo actuator side of third spring means (56) arranged in the interior of the booster piston (33) in the direction of the closed position (arrow 55) is applied.
5. The injector of claim 4, wherein as the first nozzle needle (21) in Spring direction acting on the closing direction (arrow 55) Helical compression spring (54) is used, which is arranged coaxially to the first nozzle needle (21) and on the one hand on the rear end face, on the other hand on the piezo actuator side (upper) end of the booster piston Interior (32) supports, characterized in that the third spring means a Helical compression spring (56), which are concentric with the second Spring means (helical compression spring 54) is arranged and enclosed by this and on the one hand on the second nozzle needle (41) on the other hand on the piezo actuator side (upper) end of the booster piston Interior (32) supports.
6. Injector according to claim 5, characterized in that on the piezo actuator-side (upper) end of the second nozzle needle (41) a shoulder (57) is formed, to which one Connects pin part (58) with a smaller diameter, and that the helical compression spring (56) acting as the third spring means on the Pin part (58) is arranged.  <Desc / Clms Page number 15>  
7. The injector according to one or more of the preceding claims, wherein in the region of the nozzle body (20) on the nozzle outlet side, the first Nozzle needle (21) concentrically surrounding cylindrical pressure chamber (42) is formed, which is under the injection pressure (high pressure) Fuel supply (18) is hydraulically connected, characterized in that the axial recess (39) of the first nozzle needle (21) penetrated by the second nozzle needle (41) has a diameter widening in its (lower) area on the nozzle outlet side, in such a way that one on the nozzle outlet side (lower one) ) Area of the second nozzle needle (41) surrounding annular cylindrical cavity (59), and that in the first nozzle needle (21) at least one Radial bore (60) is incorporated, which the cylindrical pressure chamber (42)
 connects hydraulically with the annular cylindrical cavity (59).
8. Injector according to one or more of the preceding claims, characterized in that the nozzle outlet (61) of the nozzle body (20) one or more radially outer, from the first (outer) Nozzle needle (21) actuated nozzle outlet openings (28,29) and one or more radially inner nozzle outlet openings (26, 27) which can be actuated by the second (inner) nozzle needle (41).
9. Injector according to one or more of the preceding claims, characterized in that the (lower) end region (61) of the nozzle body (20) containing the nozzle outlet openings (26-29) and the end sections (622 63 each functioning as closing bodies) ) of the two nozzle needles (21 or 41) are conical, the end sections (62, 63) of the nozzle needles (21 or 41) being in common Locking or. Complement the opening position to a uniform cone surface.
EP20040738750 2003-08-07 2004-06-22 Injector for fuel injection systems of combustion engines, particularly direct injection diesel engines Withdrawn EP1654453A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE10336327.0A DE10336327B4 (en) 2003-08-07 2003-08-07 Injector for fuel injection systems of internal combustion engines, in particular direct injection diesel engines
PCT/DE2004/001301 WO2005014995A1 (en) 2003-08-07 2004-06-22 Injector for fuel injection systems of combustion engines, particularly direct injection diesel engines

Publications (1)

Publication Number Publication Date
EP1654453A1 true EP1654453A1 (en) 2006-05-10

Family

ID=34112016

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20040738750 Withdrawn EP1654453A1 (en) 2003-08-07 2004-06-22 Injector for fuel injection systems of combustion engines, particularly direct injection diesel engines

Country Status (6)

Country Link
US (1) US20080163852A1 (en)
EP (1) EP1654453A1 (en)
JP (1) JP2007506897A (en)
KR (1) KR20060060675A (en)
DE (1) DE10336327B4 (en)
WO (1) WO2005014995A1 (en)

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DE102004010183A1 (en) * 2004-03-02 2005-09-29 Siemens Ag Injector
DE102004031790A1 (en) * 2004-07-01 2006-01-26 Robert Bosch Gmbh Common rail injector
DE102004060550A1 (en) * 2004-12-16 2006-07-06 Robert Bosch Gmbh fuel Injector
DE102005015731A1 (en) * 2005-04-06 2006-10-12 Robert Bosch Gmbh Fuel injector with piezo actuator
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US20080163852A1 (en) 2008-07-10
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KR20060060675A (en) 2006-06-05
DE10336327A1 (en) 2005-03-03

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