EP0937203B1 - Injecteur de carburant - Google Patents

Injecteur de carburant Download PDF

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Publication number
EP0937203B1
EP0937203B1 EP98916807A EP98916807A EP0937203B1 EP 0937203 B1 EP0937203 B1 EP 0937203B1 EP 98916807 A EP98916807 A EP 98916807A EP 98916807 A EP98916807 A EP 98916807A EP 0937203 B1 EP0937203 B1 EP 0937203B1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
valve member
space
injection valve
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.)
Expired - Lifetime
Application number
EP98916807A
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German (de)
English (en)
Other versions
EP0937203A1 (fr
Inventor
Detlev Potz
Stephan Haas
Thomas Kuegler
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
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Filing date
Publication date
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Publication of EP0937203A1 publication Critical patent/EP0937203A1/fr
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Publication of EP0937203B1 publication Critical patent/EP0937203B1/fr
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • F02M61/045—The valves being provided with fuel discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/304—Fuel-injection apparatus having mechanical parts, the movement of which is damped using hydraulic means

Definitions

  • the invention relates to a fuel injection valve for Internal combustion engines according to the preamble of claim 1 out.
  • known fuel injector is in a bore of the a piston-shaped valve body projecting into the combustion chamber Valve member axially outwards against a return spring displaceable.
  • the valve member points to his end of the combustion chamber protruding from the bore Valve closing member forming the closing head on its a valve sealing surface facing the valve body having.
  • the valve member acts with this valve sealing surface with one on the combustion chamber end face of the valve body arranged valve seat surface together.
  • a first touch is here with its lower end constantly with the discharge line connected while the second bevel with its lower Boundary edge only after passing through a certain one Opening stroke movement in the overlap with the relief line dips.
  • the known Fuel injector a two-stage hydraulic Blocking of the valve member is reached, a first Control position on the damping chamber the opening of the first Row of spray holes corresponds while the final hydraulically blocked end position of the valve member Open both rows of spray holes and thus opening the corresponds to the entire injection cross section.
  • the known fuel injection valve the disadvantage that the recesses on the valve member very much need to be manufactured exactly to the precise arrangement the precise control of the spray hole rows due to the many control edges to ensure.
  • the known fuel injection valve the injection pressure dependent Blocking of the valve member in intermediate positions not set operationally, which is expensive Geometric adjustment work of the hydraulic stroke stops has the consequence.
  • the for so-called vario register nozzles necessary control of a multi-stage opening stroke of the valve member in Dependence on the fuel injection pressure at the valve manufacturing technology only very complex realize.
  • the fuel injection valve for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that the second opening stroke phase of the valve member is adjustable and controllable via a valve inserted into the relief line.
  • a third control edge which controls the start of the second opening stroke phase, can be dispensed with, so that the manufacturing outlay of the recesses on the valve member can be greatly reduced compared to the known solution.
  • the reduction in the control edges furthermore results in a stable long-term operating behavior due to the lower influenceability as a result of geometric inaccuracies in the control recesses.
  • the configuration of the recesses according to the invention also has the advantage that both control edges are each arranged at the upper end of the recesses and can therefore be easily manufactured.
  • the time of the beginning of the second opening stroke phase of the valve member can be set in a simple manner by designing the bore diameter of the relief line and the valve design, for example the design of the valve spring strength of the valve in the relief line.
  • the pressure valve can advantageously be controlled directly by an electrical actuator, which can be designed, for example, as a piezo actuator.
  • valve member of the pressure valve to the armature in a current-carrying coil (solenoid valve), the basic settings being able to be made in each case via a spring.
  • direct control of the pressure valve in the relief line is hydraulically possible, with a regulated hydraulic back pressure being applied to the back of the pressure valve, by means of which the pressure valve can be opened or closed as a result of the pressure difference between the pressure in front of the pressure valve and the back pressure behind it.
  • Another advantageous setting option of the valve in the relief line is the map-controllable adjustment of the spring preload of the valve spring of the pressure valve.
  • the spring preload can be continuously adjusted by means of an adjustable spring support surface, which can be axially displaced, for example, electrically by a piezo actuator or the armature in a magnetic coil or hydraulically by a piston in a working area.
  • an adjustable spring support surface which can be axially displaced, for example, electrically by a piezo actuator or the armature in a magnetic coil or hydraulically by a piston in a working area.
  • a check valve is also advantageously used in an inlet line of the damping chamber, which on the other hand is connected to the low-pressure fuel circuit, preferably the spring chamber of the injection valve is. This check valve also avoids the creation of a negative pressure in the damping chamber and thus cavitation damage and unintentional reverberation of the injection valve member when closing.
  • valve in the discharge line represents its execution as Alternative pistons.
  • This gives as an alternative piston trained valve member of the valve in the Relief line during its opening stroke movement Defined escape volume through which the pressure in the Damping space of the injection valve drops and so the allows second opening stroke.
  • the control volume when Closing stroke of the injection valve member from the Alternative volume is refilled in a simple form. moreover the pressure drop in the damping chamber can be limited exactly, whereby when the damping space is finally closed when the end stroke position of the injection valve member is reached Pressure builds up faster, which is the stopping distance of the Valve element of the injection valve shortened.
  • Another The advantage of this variant is that the sealing function from the alternative volume to the leak oil chamber (e.g. spring chamber) the outer surface of the evasive piston and of the Relief line to the escape volume through a cone seat is guaranteed.
  • valve spring is designed to be block-proof.
  • Another advantage is the arrangement of the damping space in an washer between the valve body and achieved a valve holding body, which makes manufacturing or manufacture of the damping space and relief channel is relatively easy.
  • the damping or control room is on his End face of the valve body facing away from one piston axially displaceable with the valve member, which advantageously by means of a valve member Pressed sealing ring is formed.
  • This one on the Valve member attached seal slides with his The outer circumference seals in one that forms the damping space Hole in the washer.
  • the sealing ring is there advantageously as open to the damping space U-shaped sealing ring, which is preferably made of a PTFE material is made.
  • a spring is inserted for basic sealing, due to the U-shaped hollow profile sealing the sealing ring towards the wall of the washer with increasing Hydraulic pressure in the damping chamber is increased.
  • a den Damping space relief channel is also in advantageously integrated into the washer, wherein also the pressure valve controlling this relief channel in the washer is provided.
  • This pressure valve is preferably designed as a piston check valve, being about the design of the pressure valve spring Opening pressure or the opening time as the start of the second valve member opening stroke phase is adjustable. there is also a throttle point in an advantageous manner Pressure valve upstream.
  • the stroke of the Piston in the pressure valve limited to the minimum necessary stroke and the piston is also made of light materials, to wear and vibrations on the pressure valve as possible to keep low.
  • This anti-rotation device is advantageous Way in a low traffic area, preferably between the upper valve guide and the Fuel injector spring or between this spring and the valve member end arranged. That points to Valve member recesses, preferably an even number of cuts on the one in the valve body holder arranged fitting with complementary formations intervenes.
  • This fitting can be easily with the Assemble the fuel injector to the actual one Adjust the position of the valve member and thus enables one small distance between the valve member and the Rotation fixation, so that a very precise guidance with little wear on the valve member is possible. It is this fitting is particularly advantageous in the washer between the valve body and valve holding body integrate.
  • Fuel injection valves for internal combustion engines are in of the drawing and are shown in the following Description explained in more detail.
  • Figures 1 and 2 show a known fuel injection valve the vario register nozzle design in different Sectional views
  • the figures 3 and 4 enlarged Excerpts from a first embodiment of the Fuel injection valve according to Figure 1 in the area of Damping chamber with a valve in the relief line, wherein the sectional view of Figure 4 by 90 ° from the 3 is rotated
  • FIG. 5 and 6 an anti-rotation device on the valve member of the Fuel injection valve in two views
  • FIG 7 a second embodiment analogous to the representation of the Figure 3, in which the valve in the relief line over a piezo actuator is directly controlled, the figure 8 a third embodiment in which the valve member by a solenoid valve is actuated, Figure 9 a fourth Embodiment in which the opening of the valve in the Relief line using a hydraulic back pressure is adjustable on the pressure valve, Figure 10 is a fifth Embodiment in which the adjustment of the Spring preload force of the valve in the relief line 11 is a sixth via a piezo actuator Embodiment in which the adjustment of the Spring preload of the relief valve via a Magnetic armature takes place, the figure 12 a seventh Embodiment in which the adjustment of the Spring preload of the relief valve via a hydraulic actuating piston takes place, Figures 13 and 14 eighth embodiment in two views, in which a additional check valve in an inlet line of the Damping space is used and Figure 15 is a ninth Embodiment in which the valve member of the valve in the relief line is designed as an escape piston.
  • FIGS. 1 and 2 show a known fuel injection valve of the outwardly opening type with two rows of spray holes which can be opened one after the other (vario register nozzle), on which the control of the valve member stroke according to the invention is realized.
  • the fuel injection valve has a valve body 1, which projects with its lower free end into the combustion chamber of the internal combustion engine to be supplied.
  • the valve body 1 has an axial through bore 3, in which a piston-shaped valve member 5 is axially displaceably guided.
  • the valve member 5 has a closing head 7 protruding from the bore 3 and enlarged in cross section, which forms a valve closing member. This closing head 7, shown enlarged in FIG.
  • valve sealing face 9 which cooperates with a stationary valve seat face 11, which is formed on the end face of the valve body 1 on the combustion chamber side, surrounding the bore 3.
  • the valve sealing surface 9 and the valve seat surface 11 that result in a sealing cross section are conical, the cone angles of the two contact surfaces 9, 11 differing slightly from one another, so that a defined sealing edge is formed.
  • annular pressure chamber 13 is formed, which on the combustion chamber side is enlarged by a diameter extension of the valve member 5 forming an annular shoulder 15 at its transition into the closing head 7 and on the other hand by a cross-sectional expansion 17 of the valve member 5 the bore 3 is limited.
  • This pressure chamber 13 can be filled with high-pressure fuel via a pressure channel 19, for which purpose the pressure channel 19 is connected in a manner not shown to an injection line of an injection pump.
  • Injection channels 21 lead from the annular shoulder 15 delimiting the pressure chamber 13 and are initially designed as a longitudinal bore in the closing head 7 of the valve member 5 and from which control bores are then discharged at the level of the sealing edge.
  • the outlet openings 23 (injection holes) of the injection channels (21) are arranged above the valve sealing surface 9 on the lateral surface of the closing head 7 in such a way that they are covered by the wall of the bore 3 in the closed position of the injection valve, that is to say when the valve member 5 is in contact with the valve seat 11, and can only be opened during the outward opening stroke of the valve member 5 by emerging from the bore 3 of the valve body 1.
  • two rows of rows (spray hole rows) of outlet openings 23, which are arranged one above the other in the axial direction of the valve member 5, are preferably provided and are opened in succession during the valve member opening stroke movement.
  • valve member 5 protrudes with its stem part facing away from the combustion chamber from the valve body 1 into a bore which forms a spring chamber 25 and is enlarged in cross section in a valve holding body 27 which is clamped axially against the valve body 1 by means of a clamping nut 29.
  • a valve closing spring 31 is clamped in the spring chamber 25 in such a way that it is supported with its end near the combustion chamber against the valve body 1 and acts with its end remote from the combustion chamber on a valve plate 33 on the valve member 5 and thus holds the valve member 5 in contact against the valve seat 11.
  • the valve holding body 27 is axially penetrated by the pressure channel 19, a fuel filter 35 being inserted into the pressure channel 19 at the upper end of the valve holding body 27.
  • valve member 5 To limit the outward opening stroke movement of the valve member 5 instructs the valve member 5 its combustion chamber facing away from the valve body 1 in the Valve holding body 27 projecting end radially from Valve member projecting piston 37 on one hydraulic damping space 39 limited.
  • an intermediate plate 41 the axially between a face 43 remote from the combustion chamber Valve body 1 and the end face of the combustion chamber Valve holding body 27 is clamped.
  • the washer 41 has a part of the pressure channel 19 in the form of an axial Through hole on.
  • the Intermediate disc 41 has a central through opening 45, through which the stem of the valve member 5 projects and which limits the damping space 39 radially outward. axial becomes the damping space 39 in the washer 41st on the one hand from the end face 43 of the valve body 1 and on the other hand limited by the valve member piston 37.
  • This Piston 37 is by one on the shaft of the Valve member 5 pressed sealing ring formed as U-sealing ring 47 open to the damping space 39 is formed. There is one in this U-sealing ring 47 for basic sealing Spring 49 inserted.
  • the damping chamber 39 is filled and relieved via the fuel channels shown in FIGS. 3 and 4, to the low pressure circuit of the injection system are connected and the fuel injector to explain them in Figure 4 compared to the representation in 3 is rotated by 90 °.
  • the damping chamber 39 is filled and relieved via two cuts on the valve member 5, which the damping space 39 via relief channels with a low pressure chamber, preferably connect the fuel-filled spring chamber 25.
  • a first bevel 51 on valve member 5 is like this arranged so that when the injector is closed, i.e. with valve member 5 resting on the valve seat 11 with its protrudes into the damping space 39 while its lower end opens into an annular groove 53 on the valve member 5.
  • This annular groove 53 sweeps more precisely as in FIG. 4 shown the mouth of a first relief channel 55, the valve body 1, the intermediate plate 41 and the Valve holding body 27 penetrating into the spring chamber 25 opens.
  • the upper end of the first, away from the combustion chamber Bevel 51 forms with its upper boundary edge a first control edge 57, which is connected to the end face 43 of the valve body 1 cooperates.
  • the valve member 5 has a second bevel 59 on, whose upper combustion chamber distant boundary edge forms second control edge 61.
  • the second bevel 59 continuously covers the mouth a second relief channel 63, which is also characterized by the valve body 1, the washer 41 and the Valve holding body 27 extends to the spring chamber 25.
  • the second control edge 61 has a greater distance from it Face 43 of the valve body 1 than the first Control edge 57.
  • Driving over the second control edge 61 over the end face 43 corresponds to the opening stroke position of the valve member 5, in which both rows of spray holes on Injection cross-section are controlled, whereby after Driving over the second control edge 61 over the end face 43 the damping chamber 39 is finally closed hydraulically and thus the maximum opening stroke position of the valve member certainly.
  • valve 65 in the second Relief line 63 used in the first Embodiment is designed as a check valve.
  • This in the part running in the intermediate disc 41 of the second relief channel 63 has inserted valve 65 an axially displaceable, piston-shaped valve member 67 on that facing the second bevel 59 End has a conical sealing surface 69 with which it a valve seat surface 71 cooperates.
  • the valve member 67 acts a valve spring 72 which on the other hand is supported on the valve holding body 27 in a stationary manner and the design of the opening pressure at valve 65 is adjustable.
  • valve member 5 independently avoid and thus the connection between the bevels 51, 59 and the inlet opening to the relief channels 55, 63 must also be reliably ensured on valve member 5 an anti-rotation device is provided.
  • This anti-rotation is here as in the two views in FIGS. 5 and 6 shown, as a profile 73 on the valve member 5 formed with which the valve member 5 in a complementary recess 75 protrudes in the intermediate plate 41.
  • the fuel injection valve according to the invention works in following way. Holds in the injector closed position the valve spring 31, the valve member 5 with its valve sealing surface 9 in contact with the valve seat 11, the damping space 39 limiting piston 37 is in its starting position and Damping chamber 39 is over the first bevel 51, the Annular groove 53 and the first relief channel 55 with the fuel-filled spring chamber 25 (low pressure chamber) connected and filled with this by fuel, which is called hydraulic Working fluid is used.
  • This first opening stroke phase is ended by driving over the first control edge 57 on the first bevel 51 over the end face 43 of the valve body 1, the damping chamber 39 being closed briefly when the first bevel 51 is completely immersed in the valve body 1 and thereby acting as a hydraulic damper, which blocks a further opening stroke movement of the valve member 5.
  • the valve member 5 In this position, which opens a partial opening cross section on the injection valve, the valve member 5 remains in a first operating mode of the injection valve, which corresponds to the idling range and a partial load range of the internal combustion engine to be supplied. If the entire opening cross-section on the injection valve is to be opened at higher load or speed of the internal combustion engine, the second operating mode is selected on the injection valve.
  • valve member 5 remains only briefly in the intermediate position with a simultaneously increasing fuel injection pressure in the pressure chamber 13 of the injection valve.
  • a second opening pressure limit value in the pressure chamber 13 is exceeded, the force acting on the annular shoulder 15 in the opening direction on the valve member 5 or, proportionally, the pressure in the damping chamber 39 exceeds the locking force on the valve 65 in the second relief channel 63, which was previously constantly connected to the damping chamber 39.
  • the valve 65 is opened, part of the pressure medium is relieved again from the damping chamber 39 via the second bevel 59 and the second relief channel 63 into the spring chamber 25, so that the valve member 5 continues the opening stroke movement in a second opening stroke phase.
  • the upper outlet openings 23B of the injection channels 21 are now opened, so that both rows of spray holes and thus the entire injection cross section are opened.
  • the fuel flowing out via the second bevel 59 is throttled in front of the valve 65 in the second relief channel 63.
  • the opening stroke movement of the valve member 5 is ended when the second control edge 61 is passed over on the second bevel 59 over the end face 43 of the valve body 1, the damping chamber 39 now being finally closed hydraulically and thus limiting the opening stroke movement of the valve member.
  • This reaching the maximum opening stroke stop is advantageously damped, the degree of damping on the valve member being dependent on the modulus of elasticity of the fuel.
  • the arrangement according to the invention of a valve in the second relief channel allows the pause between the two opening stroke phases and the second opening stroke phase of the valve member to be set very precisely, with at least one injection taking place between the two operating modes of the injection valve (half injection cross section - total opening cross section).
  • additional hydraulic stops further intermediate positions of the opening stroke position of the valve member are possible.
  • Valve member 67 has a piston rod 77 which is connected to an actuator 79 of a piezo actuator is attached, which is in Supported closing direction of the valve member 67 fixed to the housing.
  • the valve spring 72 acts on the piezo actuator 79, pretensions this and holds the valve member 67 in contact with the Valve seat.
  • the electrical control of the piezo actuator 79 takes place depending on a map of the to be supplied Internal combustion engine and depending on the current point in time Injection, even during an injection process an adjustment is possible.
  • connection between the piezo actuator 79 and the valve member 67, 77 also via transmission elements respectively.
  • the embodiment is controlled Valve member 67 of valve 65 in the second relief channel 63 via a solenoid valve, the rod 77 of the Pressure valve member 67 is connected to an armature 81, or forms part of this.
  • This anchor 81 protrudes a current-carrying coil 83 of the solenoid valve, so that through the controlled change of the adjacent electrical voltage, the position of the armature 81 and thus the Valve member 67 is adjustable.
  • the basic setting of the Valve can be an additional to the valve spring 72 Adjustment spring 85 are made.
  • Embodiments are set Opening time or the closing characteristic at the valve 65 in the second relief channel 63 via the map-dependent Adjustment of the spring preload of the valve spring 72nd
  • this adjustment of the spring pretensioning force takes place by means of a piezo actuator 89 which is inserted above the valve member 67 into the spring chamber of the valve 65 and which is pretensioned by the valve spring 72, the valve spring 72 being over a Shim 91 is supported directly on the piezo actuator 89.
  • a piezo actuator 89 which is inserted above the valve member 67 into the spring chamber of the valve 65 and which is pretensioned by the valve spring 72, the valve spring 72 being over a Shim 91 is supported directly on the piezo actuator 89.
  • the spring preload of the valve spring 72 of the valve 65 is set in the second relief channel 63 by a magnet armature 93, which is axially displaceably guided in a current-carrying coil 95.
  • the piston-shaped armature 93 forms with its valve-side end face a spring support surface on which the valve spring 72 is supported, which on the other hand engages an annular shoulder of the valve member 67.
  • the axial position of the armature 93 and thus the pretensioning force of the valve spring 72 can now be set by varying the electrical voltage of the coil 95
  • Figure 12 shows a seventh embodiment in which the axial adjustment of the spring support surface Valve spring 72 of valve 65 in the second relief channel 63 hydraulically.
  • the spring contact surface is on a piston 97 is provided, on one end face of which Valve spring 72 abuts and the other facing away Front a hydraulic working space 99 limited.
  • This work space 99 is from a control line 101 a hydraulic system with a pressurized one Hydraulic fluid can be filled, with the pressure supply depending on the operating map of the internal combustion engine is adjustable.
  • the axial displacement of the piston 97 and thus the adjustment of the biasing force of the valve spring 72 now takes place through the controlled pressure supply or relieve in work space 99.
  • the eighth exemplary embodiment shown in FIGS. 13 and 14 in two views has, in addition to the previous exemplary embodiments, a further inlet line 103 in the intermediate disk 41, which continuously opens into the damping chamber 39 starting from the spring chamber 25 filled with lower pressure fuel.
  • a check valve 105 which opens in the direction of the damping chamber 39 and whose valve member is designed as a stepped piston 107, is inserted into this inlet line 103.
  • the stepped piston 107 forms with its end face on the spring chamber side a sealing face 109 with which it is held in contact with a valve seat face 113 by a check valve spring 111.
  • the check valve spring 111 is supported in a stationary manner on the valve body 1 and acts on the stepped piston 107 on its end face facing away from the spring chamber 25.
  • the stepped piston 107 is designed such that it plunges into the smaller diameter of a stepped receiving bore 115 with its larger circumferential surface before the system is seated on the valve seat 113, so that the check valve 105 closes before it contacts the valve seat 113.
  • the biasing force of the check valve spring 111 is so small that the stepped piston 107 is only moved when the pressure between the spring chamber 25 and the damping chamber 39 in contact with the valve seat 113.
  • the check valve 105 thus opens as long as the pressure in the damping chamber 39 is lower than the leakage oil pressure in the spring chamber 39, so that a safe filling of the damping chamber 39 and avoiding negative pressure during the closing stroke movement of the valve member 5 of the injection valve is ensured. If there is pressure equalization between the spring chamber 25 and the damping chamber 39, the check valve 105 closes, the stepped piston being pressure-balanced at this point in time.
  • the valve member of the valve 65 in the second relief channel 63 is designed as an escape piston 117.
  • the valve seat of the valve 65 is designed as a conical protuberance 119, against which the evading piston 117 comes into contact with its flat end face in such a way that a residual volume remains in the valve chamber.
  • the evasive piston 117 is sealingly guided on its circumferential surface on the wall of a valve chamber 121 receiving the valve 65 and is acted upon in a known manner by the valve spring 72 in the closing direction, which is supported on an adjusting disk 91.
  • the evasive piston 117 releases an evasive volume in the valve chamber 121, through which the pressure in the damping chamber 39 drops in such a way that the second opening stroke phase can take place on the valve member 5 and the entire injection cross section of the injection valve is opened.
  • the evasive volume is now conveyed back into the damping space 39, so that the refilling of the damping space 39 is supported, with the evasive piston 117 also taking over the function of a check valve.

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

Claims (26)

  1. Injecteur de carburant pour un moteur à combustion interne, comprenant une aiguille (5) coulissant axialement vers l'extérieur dans un perçage (3) d'un corps d'injecteur (1) contre une force de rappel, l'extrémité de l'aiguille du côté de la chambre de combustion ayant une tête d'obturation formant un organe d'obturation de soupape, sortant du perçage (3), cette tète ayant sur sa face tournée vers le corps (1) de l'injecteur, une surface d'étanchéité de soupape (9) coopérant avec une surface formant siège de soupape (11) prévue sur la face frontale du corps (1) de l'injecteur, du côté de la chambre de combustion, et
    au moins une ouverture d'injection (21) partant d'une chambre de pression (13) dans la tête d'obturation (7) et dont l'orifice d'éjection (23) est couvert en position de fermeture de l'aiguille (5) par le corps (1) de l'injecteur et libéré par la course d'ouverture dirigée vers l'extérieur,
    ainsi qu'une butée hydraulique de course à deux étages limitant la course d'ouverture de l'aiguille (5), cette butée étant réalisée comme chambre d'amortissement hydraulique (39) avec une conduite de décharge commandée,
    la conduite de décharge pouvant être reliée par au moins deux cavités dans l'aiguille (5) à la chambre d'amortissement (39) en formant des liaisons hydrauliques qui sont commandées successivement en fermeture pendant le mouvement de la course d'ouverture de l'aiguille (5),
    caractérisé en ce qu'
    au moins l'une des cavités peut être reliée à une chambre basse pression par un canal de décharge (63) muni d'une soupape (65).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    les orifices d'éjection (23) des canaux d'injection (21) sont commandés à l'ouverture de manière variable pendant le mouvement de la course d'ouverture de l'aiguille (5) et de préférence sous la forme de deux rangées d'orifices d'éjection superposées axialement, réalisées dans l'aiguille (5) et parmi lesquelles, après le passage d'une première phase d'ouverture par l'aiguille (5), seulement la première rangée, inférieure d'orifices d'éjection (23A), proche de la chambre de combustion est commandée à l'ouverture alors que la seconde rangée, supérieure d'orifices d'éjection (23B) n'est commandée à l'ouverture qu'au cours d'une seconde phase de course d'ouverture par l'aiguille (5).
  3. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    les cavités de l'aiguille (5) sont réalisées sous la forme de parties meulées dont les extrémités supérieures, à l'opposé de la chambre de combustion forment des arêtes de commande coopérant avec une surface frontale (43) du corps d'injecteur (1), délimitant axialement la chambre d'amortissement (39).
  4. Injecteur de carburant selon la revendication 3,
    caractérisé en ce qu'
    une première partie meulée (51) est réalisée sous la forme d'une surface meulée inclinée, dont l'extrémité inférieure et plus profonde du côté de la chambre de combustion vient dans un volume annulaire (53), formé entre l'aiguille (5) et le perçage (3) et relié à la chambre basse pression, et dont l'extrémité axiale supérieure qui se termine à plat, débouche dans la chambre d'amortissement (39) lorsque l'aiguille (5) est appliquée contre le siège de soupape (11), l'arête de l'extrémité supérieure éloignée de la chambre de combustion, de la première parue meulée (51) formant une première arête de commande (57).
  5. Injecteur de carburant selon la revendication 3,
    caractérisé par
    une seconde partie meulée (59) dont l'extrémité axiale supérieure éloignée de la chambre de combustion forme une seconde arête de commande (61) et dont l'extrémité axiale inférieure, du côté de la chambre de combustion est reliée en permanence au canal de décharge (63) équipé d'une soupape (65).
  6. Injecteur de carburant selon l'une quelconque des revendications 4 et 5,
    caractérisé en ce que
    la première et la seconde arête de commande (57, 61) de l'aiguille (5) sont décalées axialement en hauteur l'une par rapport à l'autre pour que la première arête de commande (57) soit commandée à la fermeture après le passage d'une première phase de course d'ouverture par l'aiguille (5), alors que la seconde arête de commande (61) est fermée seulement après le passage d'une course d'ouverture complète de l'aiguille (5) par la surface frontale (43) du corps (1) de l'injecteur.
  7. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la chambre d'amortissement (39) est prévue dans un disque intermédiaire (41) serré entre le corps (1) de l'injecteur et un corps de support (27) pour l'injecteur.
  8. Injecteur de carburant selon l'une quelconque des revendications 3 et 7,
    caractérisé en ce que
    la chambre d'amortissement (39) est délimitée à son extrémité axiale à l'opposé de la surface frontale (43) du corps (1) de l'injecteur par un piston (37) fixé à l'aiguille (5) et dont la périphérie extérieure coulisse de manière étanche contre la paroi de la chambre d'amortissement (39).
  9. Injecteur de carburant selon la revendication 8,
    caractérisé en ce que
    le piston (37) est réalisé sous la forme d'un joint d'étanchéité à section en U (47), ouvert vers la chambre d'amortissement (39), ce joint étant pressé sur le corps de l'aiguille (5).
  10. Injecteur de carburant selon la revendication 9,
    caractérisé en ce qu'
    un ressort (49) est prévu dans le joint annulaire d'étanchéité à section en U (47).
  11. Injecteur de carburant selon la revendication 7,
    caractérisé en ce que
    la soupape (65) est installée dans le disque intermédiaire (41).
  12. Injecteur de carburant selon la revendication 5,
    caractérisé en ce que
    la soupape (65) du canal de décharge (63) est précédée par un point d'étranglement.
  13. Injecteur de carburant selon la revendication 1,
    caractérisé par
    un moyen de blocage en rotation de l'aiguille (5) de l'injecteur pour éviter sa rotation automatique.
  14. Injecteur de carburant selon la revendication 13,
    caractérisé en ce que
    le moyen de blocage en rotation est constitué par une forme profilée (73) de l'aiguille (5) et une cavité (75) complémentaire du boítier, de préférence dans le disque intermédiaire (41).
  15. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la soupape (65) du canal de décharge (63) est réglable à l'aide d'un organe de réglage électrique.
  16. Injecteur de carburant selon la revendication 15,
    caractérisé en ce que
    l'organe de réglage est un actionneur piézo-électrique (79).
  17. Injecteur de carburant selon la revendication 15,
    caractérisé en ce que
    l'organe de réglage est une électrovanne reliée à l'organe de soupape (67) de la soupape de pression (65) avec un induit (81) pénétrant dans une bobine (83) traversée par du courant.
  18. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'ouverture de la soupape (65) dans le canal de décharge (63) est commandée par une pression antagoniste hydraulique, réglable du côté opposé à la chambre d'amortissement (39) d'un organe (67) de la soupape (65).
  19. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la pression d'ouverture de la soupape (65) du canal de décharge (63) est réglable en continu par le réglage de la force de précontrainte d'un ressort de soupape (72).
  20. Injecteur de carburant selon la revendication 19,
    caractérisé en ce que
    le réglage de la force de précontrainte du ressort appliquée à la soupape (65) se fait par le déplacement axial d'une surface d'appui de ressort.
  21. Injecteur de carburant selon la revendication 20,
    caractérisé en ce que
    la surface d'appui de ressort se déplace à l'aide d'un actionneur piézo-électrique (89).
  22. Injecteur de carburant selon la revendication 20,
    caractérisé en ce que
    la surface d'appui de ressort est déplacée à l'aide d'un induit d'électro-aimant (93) placé dans une bobine (95).
  23. Injecteur de carburant selon la revendication 20,
    caractérisé en ce que
    la surface d'appui du ressort est déplacée à l'aide d'un piston hydraulique (97).
  24. Injecteur de carburant selon la revendication 1,
    caractérisé par
    une soupape antiretour (105) s'ouvrant en direction de la chambre d'amortissement (39), installée dans une conduite d'alimentation (103) partant de la chambre basse pression de la chambre d'amortissement (39).
  25. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    l'organe d'obturation de la soupape (65) du canal de décharge (63) est réalisé en forme de piston d'échappement (117) qui libère un volume de compensation déterminé dans la chambre de soupape (121) de la soupape (65) par sa course d'ouverture.
  26. Injecteur de carburant selon la revendication 25,
    caractérisé en ce qu'
    une surface de siège de soupape du piston d'échappement guidée de manière étanche dans la chambre de soupape (121) a une forme de partie rabattue conique (119).
EP98916807A 1997-09-11 1998-02-27 Injecteur de carburant Expired - Lifetime EP0937203B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19739905 1997-09-11
DE19739905A DE19739905A1 (de) 1997-09-11 1997-09-11 Kraftstoffeinspritzventil
PCT/DE1998/000575 WO1999013214A1 (fr) 1997-09-11 1998-02-27 Injecteur de carburant

Publications (2)

Publication Number Publication Date
EP0937203A1 EP0937203A1 (fr) 1999-08-25
EP0937203B1 true EP0937203B1 (fr) 2002-05-15

Family

ID=7841992

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98916807A Expired - Lifetime EP0937203B1 (fr) 1997-09-11 1998-02-27 Injecteur de carburant

Country Status (5)

Country Link
US (1) US6105879A (fr)
EP (1) EP0937203B1 (fr)
JP (1) JP2001504915A (fr)
DE (2) DE19739905A1 (fr)
WO (1) WO1999013214A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19900037A1 (de) * 1999-01-02 2000-07-06 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE19947196A1 (de) 1999-10-01 2001-04-05 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
JP2003522882A (ja) * 2000-02-07 2003-07-29 ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング 噴射ノズル
DE10031579A1 (de) * 2000-06-29 2002-01-17 Bosch Gmbh Robert Druckgesteuerter Injektor mit Vario-Register-Einspritzdüse
DE20020281U1 (de) * 2000-11-30 2001-03-01 Hammelmann Paul Maschf Drehantrieb für ein hydraulisches Werkzeug
DE10111293B4 (de) * 2001-03-09 2008-11-20 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10115396A1 (de) * 2001-03-29 2002-10-10 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE10118699A1 (de) * 2001-04-17 2002-10-31 Bosch Gmbh Robert Kraftstoff-Einspritzvorrichtung und Kraftstoffsystem für Brennkraftmaschinen, sowie Brennkraftmaschine
DE10133167A1 (de) * 2001-07-07 2003-01-23 Bosch Gmbh Robert Kraftstoffhochdruckvorrichtung
DE10231583A1 (de) * 2002-07-11 2004-01-29 Daimlerchrysler Ag Kraftstoffeinspritzdüse einer Brennkraftmaschine mit Direkteinspritzdüse
DE10232693A1 (de) * 2002-07-18 2004-02-05 Siemens Ag Einspritzventil
DE10248379A1 (de) * 2002-10-17 2004-04-29 Robert Bosch Gmbh Kraftstoff-Einspritzvorrichtung für eine Brennkraftmaschine
US7520269B2 (en) * 2005-06-28 2009-04-21 Advanced Global Equities And Intellectual Properties Fuel injector nozzle assembly
WO2017063977A1 (fr) * 2015-10-15 2017-04-20 Continental Automotive Gmbh Soupape d'injection de carburant comprenant un dispositif antirebond, moteur à combustion interne et véhicule
DE102018208857A1 (de) * 2018-06-06 2019-12-12 Robert Bosch Gmbh Injektor für gasförmige und flüssige Brennstoffe
US11906067B2 (en) 2022-01-21 2024-02-20 Hamilton Sundstrand Corporation Active valve shimming

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US4182492A (en) * 1978-01-16 1980-01-08 Combustion Research & Technology, Inc. Hydraulically operated pressure amplification system for fuel injectors
DE3405161A1 (de) * 1984-02-14 1985-08-22 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzduese fuer brennkraftmaschinen
US4750675A (en) * 1987-10-05 1988-06-14 General Motors Corporation Damped opening poppet covered orifice fuel injection nozzle
US5275337A (en) * 1992-06-15 1994-01-04 Cummins Engine Company, Inc. High pressure limiting valve with fast response and fuel injector equipped therewith
DE4444363A1 (de) * 1994-12-14 1996-06-20 Bosch Gmbh Robert Mehrstrahl-Kraftstoffeinspritzdüse
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DE19642440A1 (de) 1996-10-15 1998-04-16 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Also Published As

Publication number Publication date
WO1999013214A1 (fr) 1999-03-18
EP0937203A1 (fr) 1999-08-25
DE59804130D1 (de) 2002-06-20
US6105879A (en) 2000-08-22
DE19739905A1 (de) 1999-03-18
JP2001504915A (ja) 2001-04-10

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