EP0949415A2 - Dispositif d'injection de combustible pour moteurs à combustion interne - Google Patents

Dispositif d'injection de combustible pour moteurs à combustion interne Download PDF

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Publication number
EP0949415A2
EP0949415A2 EP98123745A EP98123745A EP0949415A2 EP 0949415 A2 EP0949415 A2 EP 0949415A2 EP 98123745 A EP98123745 A EP 98123745A EP 98123745 A EP98123745 A EP 98123745A EP 0949415 A2 EP0949415 A2 EP 0949415A2
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EP
European Patent Office
Prior art keywords
valve
valve member
fuel injection
control
injection device
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
EP98123745A
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German (de)
English (en)
Other versions
EP0949415B1 (fr
EP0949415A3 (fr
Inventor
Rudolf Dr. Heinz
Dieter Kienzler
Roger Potschin
Klaus-Peter Dr. Schmoll
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 EP0949415A2 publication Critical patent/EP0949415A2/fr
Publication of EP0949415A3 publication Critical patent/EP0949415A3/fr
Application granted granted Critical
Publication of EP0949415B1 publication Critical patent/EP0949415B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of the patent claim 1 off.
  • the known fuel injection device is the valve chamber in a first version without reducing the cross section connected to the control room.
  • the control valve contributes Actuation by the piezo actuator to the drain section Drain channel either completely or closes it.
  • Another version is the valve chamber over a Connection channel connected to the control room, this Connection channel coaxial to the valve seat on the side of the Drain channel is.
  • the amount of pre-injection is in the second described embodiment so that the Adjustment speed of the control valve member by the Piezo actuator and the geometrically defined path of the Control valve member determining quantities for the degree of Relieve the pressure in the control room.
  • the maximum relief cross section for both Relief for the pre-injection as well as for the Discharge for the main injection the same size, what for a fine tuning of the opening speed of the Injector in different operating conditions from Disadvantage is.
  • the fuel injection device with the characteristic features of claim 1 has against it the advantage that the control valve according to the invention sequentially two drain cross sections in succession are taxable.
  • a gradation of the Drain cross-section can be achieved depending on the stroke.
  • Especially for low relief of the control pressure in the Control room can have a first smaller discharge cross-section come into effect with which the Pre-injection can be set.
  • For the main injection is then a large drain cross section available for a quick movement of the Injector member allowed. It is advantageous thereby a sleeve-shaped according to claim 2 Drag valve member provided that a second Drainage cross section of the drainage channel controls if that Control valve member a first, relieving the control room Stroke.
  • the one before the opening of the second Outflow cross section through the drag valve member Pressure reduction in the valve room or control room facilitates a quick opening of the second Drain cross-section in succession to the opening of the first discharge cross section at the first movement of the Drag valve member. This can be particularly fast Opening the injection valve member at the beginning of Main injection can be achieved.
  • FIG. 1 shows a schematic representation of a Fuel injector with fuel supply off a high pressure fuel accumulator and one Fuel injection valve of a known type
  • FIG. 2 first embodiment of the invention with a Control valve member on which a drag valve member is arranged is that by a driver on the valve lifter of his Valve seat is moved away
  • Figure 3 shows a modification of the Embodiment of Figure 2 with a Control valve member having improved guidance
  • Figure 4 shows a third embodiment of the invention in Further development of the embodiment of Figure 2, wherein instead of a driver for taking the drag valve member a compression spring is provided
  • Figure 5 is a fourth Embodiment of the invention in the Drag valve member a third valve seat is provided
  • Figure 6 shows a fifth embodiment with a Control valve member that both the discharge cross section from Valve space to the drainage channel as well as the connecting channel controls between valve space and control space
  • Figure 7 sixth embodiment in which the control valve in analogous configuration to Figure 2, the pressure of a
  • a fuel injector with which at high Injection pressures a large variation with little effort the fuel injection with respect to the injection quantity and Injection time is possible is through a so-called Common Rail System implemented.
  • the invention is also in principle conventional fuel injection pumps can be used.
  • use with one is particularly advantageous Common rail injection system.
  • a high pressure fuel source High-pressure fuel accumulator 1 provided by a High-pressure fuel delivery pump 2 from one Fuel tank 4 is supplied with fuel.
  • the pressure in the high-pressure fuel reservoir 1 is determined by detects a pressure sensor 6 and an electrical one Control device 8 supplied via a Pressure control valve 5 the pressure in the high-pressure fuel reservoir controls.
  • the control device also controls this Opening and closing of high-pressure fuel injection valves 9, used to inject fuel from the high-pressure fuel accumulator be supplied.
  • This is in the executed example as an elongated valve needle trained that a conical at one end Has sealing surface 15 with an inner Valve seat cooperates on the valve housing, from which the Remove injection openings 12.
  • the valve needle is in one Longitudinal bore 13 at its upper, sealing surface 15 end facing away and is on the sealing surface 15th facing away from the longitudinal bore 13 end acted upon by a compression spring 18 in the closing direction.
  • valve needle 14 Between the guide in the longitudinal bore 13 and the The valve seat is the valve needle 14 from an annular space 19 surrounded, which opens into a pressure chamber 16, which in turn via a pressure line 17 in constant connection with the High-pressure fuel accumulator 1 stands.
  • the valve needle 14 In the area of this Pressure chamber, the valve needle 14 has a pressure shoulder 20 on, over which they oppose the pressure in the pressure chamber 16 Force of the spring 18 is applied in the sense of lifting the sealing surface 15 from the valve seat.
  • the valve needle continues to be driven by a plunger 21 applied, the valve needle 14 facing away End face 22 in a tappet guide bore 23 Control room 24 limited.
  • This is via an inlet channel 26, in which an inlet throttle 28 is provided, always with the pressure line 17 or the High-pressure fuel accumulator 1 connected.
  • the inlet channel opens into the control room 24 in a non-closable manner.
  • Connecting channel 29 from the one in a valve chamber 30 Control valve 31 opens.
  • In the connecting channel that also represents a drainage channel is one Diameter restriction, preferably in the form of a Drain throttle 32 is provided.
  • the detailed structure of the Control valve 31 is in the different Embodiments 2 to 7 shown in more detail.
  • Control valve 31 has a control valve member 34, consisting from a valve tappet 35 which is in a tappet bore 36 is guided, and a valve head 37 on the in the Valve chamber 30 protruding find the control valve member 34 the end of the valve lifter opposite the valve head 35, a spring plate 38 is provided, on which a Compression spring 39 supports, which strives to Bring control valve member into the closed position.
  • the control valve member 34th acted upon by a piston 40, which is part of a Piezo actuator 41 is and when the piezo is excited depending on the degree of excitation the control valve member in different Can bring opening positions.
  • the piston can be connected directly to the piezo of the piezo actuator or by means of a hydraulic or mechanical transmission be moved by this.
  • valve head 37 arranged at the end of the valve tappet 35 has a conical entry to the connecting channel 29 in the valve head sealing surface 51 facing away from the valve chamber 30, which with a valve seat 52 to form a Valve 58 cooperates.
  • This valve seat 52 is located at the transition to an inner through hole 53 of a sleeve-shaped drag valve member 54 that the Valve tappet surrounds at a distance.
  • the inner peripheral wall of the inner through hole 53 thus forms together with the Shell surface 55 of the valve lifter 35 a Passage cross section 56.
  • Spacer ribs 57 guided on the valve lifter 35 To determine the location of the sleeve-shaped towing member 54, this is over Spacer ribs 57 guided on the valve lifter 35. These ribs leave the adequately dimensioned passage cross section 56 free.
  • Valve member sealing surface 59 which is also conical is formed with a smaller cone tip angle than the cone tip angle of the conical valve seat 46 and with the valve seat 46 cooperates.
  • the conical Valve seat 46 a main valve seat of a main valve 61 represents a much larger passage cross-section limited from the valve space 30 to the annular space 48 than that Passage cross section between the valve head 37 and The valve seat 52 of the valve 58 is limited.
  • the piezo actuator is used to initiate an injection controlled by the control valve member by one Opening stroke adjusted.
  • the pilot valve 58 opened by the valve head 37 from the valve seat 52 takes off.
  • the great advantage of a piezo drive is the fact that a actuated control valve member according to the Excitation of the actuator can be brought into defined positions can. This makes it easy and exact Injections into a pre and a main injection divide. A pre-injection is required for the above featured fuel injector design only a slight relief of the control room 24 so that the Injector valve member only a short opening Injection openings 12 causes. For a main injection on the other hand, to carry out a large, fast stroke of the injection valve member 14, the control chamber 24 quickly and be effectively relieved. The faster the injector can open or close, the more precise the Injection phase can be determined.
  • the inlet 26 Includes inlet throttle 28 and this is smaller than that Cross section on the outflow side of the control chamber 24, in particular the cross section of the discharge throttle 32, the effective relief of the control room can be achieved.
  • the final control of the cross-section to the drain channel 49 takes over the control valve. This must first against the high pressure in the control room 24 or in Work on valve chamber 30. But now the cross section of the drain at the pre-valve 58 is small in relation to the main valve 61, will do a relatively minor job of opening the Valve 58 required.
  • By opening the pilot valve the pressure in the valve chamber 30 is already significantly reduced, so that when a larger pressure in the valve chamber 30th wall must be adjusted against this pressure, the force to be applied is already lower.
  • the control of the control valve can take place so that the opening of the valve 58 of the Pressure in the control room 24 is already lowered so that a short opening stroke of the injection valve member 14 allows is.
  • the control valve member 35 be moved again and over the drag valve member 54 open the larger discharge cross-section in order to with the then following rapid discharge the opening of the Injection valve member 14 for the main injection initiate.
  • the completion of the main injection is through Closing the control valve controlled and thus the Injection quantity.
  • the pressure after Opening the valve should only be relieved to the extent that Injection valve member 14 remains closed, but one only little further relief opening it causes.
  • By subsequently adjusting the Valve tappet 35 can then by increasing the Degree of opening of the pilot valve and / or by dragging Opening the drag valve member a short further relief the pressure in the control chamber 24 or valve chamber 30 be made to generate a pre-injection and then by taking back the valve lifter stroke Termination of the same. This is followed by a larger one Valve tappet stroke in which the drag valve member 54 again a complete relief of the control room 24 Performing the main injection is effected.
  • the Front side can be designed with a crown radial passage cross sections. Limiting the Drain cross-section through the drain throttle 32 which in executed example is arranged in the connecting channel 29, can follow in another place, for example in Drain channel 49 or by dimensioning a maximum Flow cross section 56 therebetween.
  • Figures 8a to 8c are the control processes of this Control valve.
  • Figure 8a the stroke of the Injection valve member 14 on the angle of rotation of the Internal combustion engine or the time applied.
  • Man recognizes the smaller forward stroke V of the injection valve needle 14 to carry out the pre-injection, the intermediate one Pause P at which the control valve is fully or as far it is concluded that the injection valve member pressure in the control chamber 24 that brings it back into the closed position sets, and the subsequent stroke H, via the Duration the main injection is defined. Is triggered this is shown by the sequence shown below Strokes of the control valve member.
  • the diagram 8c below shows the pressure curve shown in the control room 24 with corresponding Pressure drops if, according to diagram 8b, the Control valve member h1 has opened.
  • FIG. 3 A modification of the control valve according to FIG. 2 is shown in Figure 3 shown. As far as this configuration with Figure 2 matches, the same reference numbers are used. Reference is made to the corresponding description for FIG. 2 referred. Deviates from the embodiment according to FIG. 2 in Figure 3 in the area in which in Figure 2 the Valve tappet 135 is guided in the tappet bore 36, a Sleeve 166 arranged on the plunger 135. In Figure 3 is this sleeve axially between a stop 167 and one Holding disc 168 fixed on the plunger. The attack is made by a shoulder of the plunger formed at the end of the from the sleeve-shaped drag link 54 protruding spacing ribs 57 is provided.
  • the holding disc can, for example, as Snap ring in an annular groove 69 of the plunger on its from the Ram bore 136 protruding end can be realized.
  • the sleeve can also be placed on the plunger 135 be pressed on.
  • the stroke is also h1 defines, from which the plunger, which is together with the Sleeve 166 moves to rest on the sleeve-shaped Towing member 54 arrives.
  • the sleeve 166 also has their lower end facing the drag valve member 54 Reduction in diameter with which in replacement for the annular space 48 an annular space 148 is again formed here from FIG. 2, who is constantly in communication with the drain channel 49.
  • the Towing member 54 is as in the previous embodiment 2 designed on its end face so that a Overflow cross section is released in the Magnitude of the passage cross section 56 is.
  • This configuration has the advantage that the Guide surface within the tappet bore 136 is larger and thus the control valve member is guided more precisely. Since the Tappet 135 for assembly by the inner one Through hole 53 must be passed, would be one Enlargement of the ram guide diameter in the area the plunger bore according to FIG. 2 is actually a limit set. By adding the sleeve 166 can still the guide surface can be enlarged, the sleeve subsequently after threading the drag valve member 54 on the valve lifter is installed. The outside diameter of the The sleeve is larger than the diameter of the inner one Through hole 53 of the drag valve member and smaller than the diameter of the valve space 30.
  • FIG. 4 Another variant of a control valve in a modification to The exemplary embodiment according to FIG. 2 is shown in FIG. 4 reproduced.
  • two are different Drainage cross-sections of the drainage channel in succession steered on.
  • the one from limited the plunger 21 of the injection valve member 14 Control chamber 24 is provided, through which the throttle 32nd contained connection channel 29 with the valve chamber 30th connected is.
  • the tappet 235 also projects into this valve space the valve head 237 and the valve head sealing surface 251, which in Closed state of the control valve in contact with the valve seat 52 of the sleeve-shaped drag valve member 54 is below Formation of the pilot valve 58.
  • Via the valve head 237 this additionally with its valve member sealing surface 59 in System held on the main valve seat 46 of the main valve 61.
  • valve seat 46 Beyond this valve seat 46 is again the Annulus 48, which is penetrated by the plunger 235 and in permanent connection with the drain channel 49.
  • sleeve-shaped drag valve member 54 on its outer circumference over longitudinal ribs 60, which are formed by grooves between them are formed on the peripheral wall 45 of the valve chamber 30 guided. These longitudinal ribs leave the flow cross section to the main valve 61 free.
  • the inner through hole 53 of the drag valve member 54 is from the valve lifter 35 spaced so that starting from the pilot valve corresponding flow cross section 56 to the annular space 48 or drainage channel 49.
  • the connecting channel 29 lies coaxially with the valve head 237 opposite and ends there in an axial boundary wall 270 of the valve chamber 30.
  • the axial boundary wall is thus as the valve seat of a third valve 279 with the Valve head 237 designed as a valve member.
  • valve tappet 235 is actuated so that to realize a pre-injection Valve head 237 in one go from its installation on Valve seat 52 is moved away until it touches Sealing surface 271 on the valve seat 270 of the third valve 279 or on the axial boundary wall 270 the valve head is relieved for a short time of the valve chamber 30 and the control chamber 24, which at appropriate dimensioning is sufficient, an opening of the Injection valve member 14 for performing a To effect pre-injection.
  • the connecting channel 29 is completely closed, so the pressure in the valve chamber can continue to relax, meanwhile the pressure in the control room 24 via the inlet 26 is rebuilding what a closing the Injector needle 14 follows.
  • the pressure relief in the valve chamber 30 in turn leads to the Return forces arranged in the annular space 48 Compression spring 272, which is between the housing and the end face of the drag valve member 54 on the annulus side supports, predominates and the drag valve member 54 of the Adjustment of the valve head 237 up to the turn tight system on the valve head sealing surface 251. If then by controlling the Piezo actuator the valve head in an intermediate position between the valve seats 270 and 46 is moved, the control room 24 over the valve chamber 30 and the large opening cross section of the main valve 61 very quickly to the fullest extent possible be relieved, so that here to carry out a Main injection a maximum, quick adjustment of the Injection valve member can take place in the opening direction.
  • the Decoupling the control room 24 from the pressure source 1 via the Inlet throttle 28 allows relief to almost full relief pressure, favored by the large Outflow cross section on the outer circumference of the drag valve member.
  • the valve head returned together with the drag valve member 54, with tight sealing of the valve 58 and the Main valve 61.
  • the great advantage of this design is that to perform the pre-injection only a single movement of the control valve member in one Direction is required and to carry out the Main injection continues to only move back in shape a partial stroke in the direction of the starting position and one itself subsequent final repatriation.
  • FIGS. 2 and 3 While in the exemplary embodiments FIGS. 2 and 3 only two valves each in connection with the Control valve member and the drag valve member realized were in the above-described embodiment 4 realized a total of three valves, the valve 58 with the valve seat 52, the main valve 61 with the Main valve seat 46 and the third valve 279 with the Valve seat 270.
  • three valves are also implemented here. This execution however, builds on the configuration according to FIG. 3. As in 3, the valve chamber 30 is again provided here, in the coaxial to the valve lifter 35 of the connecting channel 29 Coming from the control room 24, flows out.
  • the sleeve 366 has now in their area overlapping the annular groove 374 on the front side a conical sealing surface 375, which at corresponding movement of the valve lifter 335 to the system a conical valve seat 376 on the front of the Drag valve member 354 can be brought.
  • This valve seat 376 thus forms 375 together with the conical sealing surface a third valve 379.
  • the tapered valve seat is 376 thereby to the inside of the inner through hole 53 of the Drag valve member 354 inclined, so in the opposite direction the inclination of the valve member sealing surface 59 of the main valve 61.
  • This stroke h5 is brief Relief of the valve chamber 30 and the control chamber 24, the is sufficient, the injection valve member 14 in a Pre-injection position to move.
  • the advantage in this embodiment is that by a staged energization of the piezo actuator for the pre and Main injection can be switched in one direction got to. This results in very short switching times in particular by switching through the one Valve seat 52 to the other valve seat 376 a very short Relief and thus a very small pre-injection quantity feasible. To end the injection, the Tappet returned to the starting position shown. For there is a separate injection process Relief cross-section available to match the corresponding Can be adapted to requirements.
  • FIG. 6 A fifth exemplary embodiment of the invention is shown in FIG. 6 shown that a further development of Representing embodiment of Figure 4.
  • the mouth opens again Connection channel 29 coaxial to the valve lifter 435 in the Valve chamber 30 a.
  • the valve head 437 carries the Valve head sealing surface 51, which with the valve seat 52 on Transition from the front of the drag valve member 454 to its inner through hole 53 to form the Valve 58 cooperates.
  • the drag valve member 454 carries a conical Valve member sealing surface 459 that mates with the main valve seat 46 at the transition from the valve chamber 30 to the annular chamber 48 Formation of the main valve 61 cooperates.
  • the drag valve member 454 by a compression spring 472 in the direction of opening the Main valve 61 loaded.
  • the spring 472 overrides a thrust washer 477 on a neck-shaped extension 478 of the drag valve member 54.
  • this nozzle-shaped extension 478 becomes the drag valve member 454 tightly on the outer jacket 455 of the valve lifter 435 guided so that between the valve head 437 and the Drag valve member 454 has an annular recess 480 which is included through a by the Throttle bore 481 in constant trailing valve member Connection to the annular space 48 is.
  • Deviating from the embodiment according to FIG. 4 offers itself here the possibility of a targeted use of chokes to determine the relief dynamics of the control room 24.
  • the discharge is used to carry out the pilot injection determined by the throttle bore 481 and at The main injection is the relief of the control room 24 determined by the larger discharge throttle 32, which is smaller than the outflow cross section of the main valve 61. Together with the inlet throttle 29 then turns to the definition of Main injection in the desired gradation of pressure in the Control room 24 a.
  • the main injection will eventually by moving plunger 435 back into the one shown Starting position achieved in Figure 6, in which the pilot valve 58 and the main valve 61 are closed and the third Valve 479 is open.
  • the cross sections can be used for the pre and Main injection can be customized.
  • Figure 9a to 9c is recorded as the Motions of the injector needle 14, the Valve head 437 and the drag valve member 454 formed are.
  • FIG 9a is about the stroke and the Time the movement of the injector needle is recorded, with a small stroke for pre-injection V, one intermediate pause P in which the injector is closed and a subsequent main injection H.
  • the pilot injection is triggered according to the underlying diagram 9b by adjusting the Valve head 437.
  • the valve head is moved through by the valve seat 52 up to the valve seat 470 of the third valve, which in represented by the number 470 on the ordinate is.
  • FIG. 7 can such a valve is also designed as a 3/2 valve be, with a in a first position of the valve Connection from the high-pressure fuel reservoir from the control room is manufactured with the simultaneous closure of the Drain channel and in a second position of the valve Connection between high-pressure fuel accumulator 1 and Control room can be prevented, producing the Connection of the control room to the relief channel.
  • Figure 7 shows a very similar one in this context Design as Figure 2 with the difference that the Valve chamber 530 in permanent connection channel 529 Connection with the control room not shown here stands. This connecting channel branches from the peripheral wall of the cylindrical valve space 530.
  • valve chamber 530 The inflow of high pressure fuel takes place here on the axial End wall 570 of valve chamber 530, this inlet 526 coaxial to the axis of the valve chamber 530 or the Ram 535 opens.
  • the end face 570 forms in Mouth area of the inlet 526 a valve seat with an end sealing surface 571 on the valve head 537 in analogous configuration to FIG. 4 as third valve 479, but here in a different function, interacts.
  • Valve tappet 535 in a tappet bore 36 and penetrates the annular space 48, which in turn over the Main valve seat 46 the valve chamber larger in diameter 530 passes.
  • Valve member sealing surface 59 is conical, analogous to that conical transition between valve space 530 and annular space 48 and at one end of the sleeve-shaped drag valve member 54 is inclined to the outer periphery.
  • a conical valve seat 52 which with a Valve head sealing surface 551, which is also conical is formed, cooperates on the valve head 537.
  • the valve lifter 535 also has one Driver 563, for example as a snap ring in a Ring groove 583 of the valve lifter can be clipped.
  • the valve head is in contact with the valve seat 52 of the valve 58 and the valve member sealing surface 59 in System on the main valve seat 46 of the main valve 61, is the Driver 563 by a stroke h1 from an end face 564 of the Drag valve member spaced. Even when the Driver 563 on the end face 564 remains sufficient Cross-section free to allow fuel flow from valve compartment 530 when the pilot valve is open through the between valve tappet 535 and the inner through hole Passage cross section 56 can flow to the annular space 48 and from there via the drainage channel to the discharge side.
  • valve lifter 535 When the valve lifter 535 is actuated by the actuator this is lifted from the valve seat 52 with the valve head be so that with simultaneous inflow of fuel via the inlet channel 536 and outflow of fuel via the Passage cross section 56 to the drain channel 49 in the Control room sets an average pressure that is sufficient is to pre-injection by opening the Injector member 14 to effect.
  • the control valve member For the Main injection is the control valve member with the Valve head 537 switched through until the Sealing surface 571 on valve seat 570 or closing of the third valve 579. The inflow of High pressure fuel in the valve compartment and thus also in the Control room prevented and the control room can to Drain channel 49 are completely relieved.

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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)
EP98123745A 1998-04-11 1998-12-14 Dispositif d'injection de combustible pour moteurs à combustion interne Expired - Lifetime EP0949415B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19816316A DE19816316A1 (de) 1998-04-11 1998-04-11 Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19816316 1998-04-11

Publications (3)

Publication Number Publication Date
EP0949415A2 true EP0949415A2 (fr) 1999-10-13
EP0949415A3 EP0949415A3 (fr) 2002-06-12
EP0949415B1 EP0949415B1 (fr) 2004-10-13

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EP98123745A Expired - Lifetime EP0949415B1 (fr) 1998-04-11 1998-12-14 Dispositif d'injection de combustible pour moteurs à combustion interne

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US (1) US6085719A (fr)
EP (1) EP0949415B1 (fr)
JP (1) JPH11324848A (fr)
DE (2) DE19816316A1 (fr)

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EP1016783A2 (fr) * 1998-12-28 2000-07-05 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs à combustion
WO2000050761A1 (fr) * 1999-02-22 2000-08-31 Siemens Aktiengesellschaft Injecteur pour dispositif d'injection de moteur a combustion interne
WO2002008598A1 (fr) * 2000-07-22 2002-01-31 Robert Bosch Gmbh Procede de commande d'une soupape d'injection destinee a l'injection de carburant dans un moteur thermique
EP1041272A3 (fr) * 1999-04-01 2002-09-18 Delphi Technologies, Inc. Injecteur de combustible
WO2004079180A1 (fr) * 2003-03-04 2004-09-16 Siemens Aktiengesellschaft Soupape comportant un element ressort, conçue pour un injecteur de carburant
WO2005095787A1 (fr) * 2004-03-23 2005-10-13 Siemens Aktiengesellschaft Servo-soupape et soupape d'injection
EP1640604A1 (fr) * 2004-09-23 2006-03-29 Siemens Aktiengesellschaft Servovalve et soupape d'injection
EP1781932A1 (fr) * 2004-08-24 2007-05-09 Robert Bosch Gmbh Soupape de commande pour injecteur

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DE19940292B4 (de) * 1999-08-25 2008-03-06 Robert Bosch Gmbh Steuerventil für ein Kraftstoffeinspritzventil
DE19940300A1 (de) * 1999-08-25 2001-03-01 Bosch Gmbh Robert Steuerventil für einen Injektor
DE60014813T2 (de) * 1999-08-31 2006-03-09 Denso Corp., Kariya Kraftstoffeinspritzvorrichtung
DE19941463A1 (de) * 1999-09-01 2001-03-15 Bosch Gmbh Robert Magnet-Injektor für Kraftstoff-Speichereinspritzsysteme
US20030155021A1 (en) * 2000-01-22 2003-08-21 Friedrich Boecking Valve for the control of fluids
DE10015268A1 (de) * 2000-03-28 2001-10-04 Siemens Ag Einspritzventil mit Bypaßdrossel
DE10031582A1 (de) * 2000-06-29 2002-01-17 Bosch Gmbh Robert Druckgesteuerter Injektor mit gesteuerter Düsennadel
DE10031580A1 (de) * 2000-06-29 2002-01-17 Bosch Gmbh Robert Druckgesteuertes Steuerteil für Common-Rail-Injektoren
DE10031579A1 (de) * 2000-06-29 2002-01-17 Bosch Gmbh Robert Druckgesteuerter Injektor mit Vario-Register-Einspritzdüse
DE10046823B4 (de) * 2000-09-20 2004-07-15 L'orange Gmbh Servosteuerventil für Einspritzinjektoren
US6764028B2 (en) 2001-04-04 2004-07-20 Synerject, Llc Fuel injector nozzles
US6634339B2 (en) 2001-10-31 2003-10-21 Caterpillar Inc Front end rate shaping valve concept for a fuel injection system
DE10154802A1 (de) * 2001-11-08 2003-05-22 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
DE10335059A1 (de) * 2003-07-31 2005-02-17 Robert Bosch Gmbh Schaltventil für einen Kraftstoffinjektor mit Druckübersetzer
US7124744B2 (en) * 2003-07-31 2006-10-24 Caterpillar Inc. Variable control orifice member and fuel injector using same
ES2277229T3 (es) 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni Servovalvula para controlar el inyector de combustible de un motor de combustion interna.
EP1621764B1 (fr) * 2004-06-30 2007-11-07 C.R.F. Società Consortile per Azioni Injecteur d'un moteur à combustion interne
DE102006021741A1 (de) * 2006-05-10 2007-11-15 Robert Bosch Gmbh Kraftstoffinjektor mit druckausgeglichenem Steuerventil
ATE445777T1 (de) * 2007-07-30 2009-10-15 Fiat Ricerche Einspritzdüse mit ausgeglichenem messservoventil für einen verbrennungsmotor
DE102008032385B4 (de) * 2008-07-09 2018-03-29 Audi Ag Hochdruckeinspritzanordnung für eine direkteinspritzende Brennkraftmaschine
DE102009001003B4 (de) * 2009-02-19 2017-11-30 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102011017217A1 (de) 2011-04-15 2012-10-18 Mühlbauer Ag Vorrichtung und Verfahren zum Ablegen von bogenförmigen Produkten
CH710127A1 (de) * 2014-09-17 2016-03-31 Ganser Crs Ag Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
JP6645663B2 (ja) 2014-12-11 2020-02-14 デルフィ・インターナショナル・オペレーションズ・ルクセンブルク・エス・アー・エール・エル 制御バルブアセンブリ
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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1016783A2 (fr) * 1998-12-28 2000-07-05 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs à combustion
EP1016783A3 (fr) * 1998-12-28 2002-10-23 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs à combustion
WO2000050761A1 (fr) * 1999-02-22 2000-08-31 Siemens Aktiengesellschaft Injecteur pour dispositif d'injection de moteur a combustion interne
US6561435B2 (en) 1999-02-22 2003-05-13 Siemens Aktiengesellschaft Injector for an injection system of an internal combustion engine
EP1041272A3 (fr) * 1999-04-01 2002-09-18 Delphi Technologies, Inc. Injecteur de combustible
WO2002008598A1 (fr) * 2000-07-22 2002-01-31 Robert Bosch Gmbh Procede de commande d'une soupape d'injection destinee a l'injection de carburant dans un moteur thermique
WO2004079180A1 (fr) * 2003-03-04 2004-09-16 Siemens Aktiengesellschaft Soupape comportant un element ressort, conçue pour un injecteur de carburant
WO2005095787A1 (fr) * 2004-03-23 2005-10-13 Siemens Aktiengesellschaft Servo-soupape et soupape d'injection
EP1781932A1 (fr) * 2004-08-24 2007-05-09 Robert Bosch Gmbh Soupape de commande pour injecteur
EP1640604A1 (fr) * 2004-09-23 2006-03-29 Siemens Aktiengesellschaft Servovalve et soupape d'injection

Also Published As

Publication number Publication date
DE19816316A1 (de) 1999-10-14
DE59812121D1 (de) 2004-11-18
US6085719A (en) 2000-07-11
JPH11324848A (ja) 1999-11-26
EP0949415B1 (fr) 2004-10-13
EP0949415A3 (fr) 2002-06-12

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