EP0937203A1 - Injecteur de carburant - Google Patents

Injecteur de carburant

Info

Publication number
EP0937203A1
EP0937203A1 EP98916807A EP98916807A EP0937203A1 EP 0937203 A1 EP0937203 A1 EP 0937203A1 EP 98916807 A EP98916807 A EP 98916807A EP 98916807 A EP98916807 A EP 98916807A EP 0937203 A1 EP0937203 A1 EP 0937203A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
valve member
injection valve
chamber
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
EP98916807A
Other languages
German (de)
English (en)
Other versions
EP0937203B1 (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
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 EP0937203A1 publication Critical patent/EP0937203A1/fr
Application granted granted Critical
Publication of EP0937203B1 publication Critical patent/EP0937203B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—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 is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a piston-shaped valve member is axially displaceable outwardly against a return spring in a bore of the valve body projecting into the combustion chamber.
  • the valve member on its combustion chamber end has a closing head which projects from the bore and forms a valve closing member and which has a valve sealing surface on its side facing the valve body. With this valve sealing surface, the valve member interacts with a valve seat surface arranged on the end face of the valve body on the combustion chamber side.
  • the known fuel injection valve has a two-stage that limits the opening stroke of the valve member hydraulic stroke stop, which is designed as a hydraulic damping chamber with controllable relief.
  • the relief line can be connected to the damping chamber via two recesses on the valve member, this connection being able to be controlled in succession during the opening stroke movement of the valve member.
  • the recesses in the known fuel injection valve are designed as two surface grindings on the valve member which protrude with their upper ends into the damping space.
  • a first bevel is permanently connected to the relief line with its lower end, while the second bevel with its lower boundary edge only dips into the overlap with the relief line after a certain opening stroke movement has been completed.
  • the control position on the damping chamber corresponds to the opening of the first spray hole row
  • the final hydraulically blocked end position of the valve member corresponds to the opening of both spray hole rows and thus the opening of the entire injection cross section.
  • the known fuel injection valve has the disadvantage that the recesses on the valve member have to be made very precisely in order to ensure precise control of the rows of spray holes via the precise arrangement of the many control edges.
  • the injection pressure-dependent blocking of the valve member in intermediate positions cannot be adjusted for operational reasons, which requires complex geometric adaptation work on the hydraulic stroke strikes.
  • the control of a multi-stage opening stroke course of the valve member, which is necessary for the so-called vario register nozzles can only be implemented in a very complex manner in terms of production technology, depending on the fuel injection pressure applied to the valve.
  • 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 easily determined by designing the bore diameter of the relief line and the valve design, e.g. adjust the design of the valve spring strength of the valve in the relief line.
  • the opening time or the closing characteristic of the valve which is preferably designed as a pressure valve, in the relief line to be able to adjust as a function of the map during operation of the injection valve, in order to be able to continuously control the second opening stroke phase on the valve member of the injection valve.
  • the pressure valve can advantageously be controlled directly by an electrical actuator, which can be designed, for example, as a piezo actuator.
  • an electrical actuator which can be designed, for example, as a piezo actuator.
  • Another alternative to this is the direct connection of the 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.
  • 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 prevents the creation of a negative pressure in the damping chamber and thus cavitation damage and a unintentional reverberation of the injection valve member when closing.
  • valve in the relief line is its design as an evasive piston.
  • the valve member of the valve in the relief line designed as an evasive piston, releases a defined evasive volume during its opening stroke movement, by means of which the pressure in the damping space of the injection valve drops and thus the second Opening stroke path allows.
  • This embodiment variant has the advantage that the control volume is refilled in a simple form from the evasive volume during the closing stroke of the injection valve member.
  • the pressure drop in the damping chamber can be precisely limited, which means that when the damping chamber is finally closed when the injection valve member reaches the end stroke position, the pressure builds up faster, which shortens the stopping distance of the valve member of the injection valve.
  • Another advantage of this variant is that the sealing function from the escape volume to the leak oil chamber (e.g. spring chamber) is ensured by the outer surface of the escape piston and from the relief line to the escape volume by a conical seat.
  • a further advantage is achieved by the oblique formation of the upper ends of the surface grindings in the valve member, which cause the opening cross-section to gradually decrease towards the damping chamber and thus avoid pressure vibrations and the resulting vibrations on the valve member.
  • the valve spring is designed to be block-proof in order to ensure that the damping chamber has emergency running shadow on the fuel injection valve for the first filling.
  • a further advantage is achieved by arranging the damping space in an intermediate disk between the valve body and a valve holding body, as a result of which the manufacture or manufacture of the damping space and relief channel is relatively simple.
  • the damping or control chamber is bounded on its side facing away from the end face of the valve body by a piston which can be displaced axially with the valve member and which is advantageously formed by a sealing ring pressed onto the valve member.
  • This sealing ring attached to the valve member slides sealingly with its outer circumference in a bore in the intermediate disk which forms the damping space.
  • the sealing ring is advantageously open to the damping chamber
  • U-shaped sealing ring which is preferably made of a PTFE material.
  • a spring for basic sealing is inserted into this sealing ring, the sealing of the sealing ring against the wall of the intermediate disk increasing with increasing due to the U-shaped hollow profile
  • Hydraulic pressure in the damping chamber is increased.
  • a relief channel which relieves the damping space is likewise advantageously integrated into the intermediate disk, the pressure valve controlling this relief channel also being provided in the intermediate disk.
  • This pressure valve is preferably designed as a piston check valve, the opening pressure or the opening time being adjustable as the start of the second valve member opening stroke phase via the design of the pressure valve spring.
  • a throttle point is also advantageously connected upstream of the pressure valve.
  • the stroke of the piston in the pressure valve is advantageously limited to the minimum necessary stroke and the piston is also made of light materials in order to keep wear and vibrations on the pressure valve as low as possible. In order to ensure a secure connection between the ground bevels and the relief duct, it is necessary to secure the valve member against unintentional twisting.
  • This anti-rotation device is advantageously arranged in a lightly loaded area, preferably between the upper valve member guide and the fuel injection valve spring or between this spring and the valve member end.
  • the valve member has recesses, preferably an even number of cuts, which engages in a molded part arranged in the valve body holder with complementary formations.
  • This fitting can be easily adapted to the actual position of the valve member during assembly of the fuel injection valve and thus enables a small distance between the valve member and the rotational position fixing, so that very precise guidance with little wear on the valve member is possible. It is particularly advantageous to integrate this fitting into the intermediate disc between the valve body and the valve holding body.
  • FIGS. 1 and 2 show a known fuel injection valve of the vario-register nozzle type in various Sectional views, Figures 3 and 4 enlarged sections of a first embodiment of the fuel injection valve of Figure 1 in the area of the damping chamber with a valve in the relief line, the sectional view of Figure 4 by 90 ° from the
  • FIGS. 5 and 6 an anti-rotation device on the valve member of the fuel injection valve in two views
  • FIG. 7 shows a second exemplary embodiment analogous to the representation of FIG. 3, in which the valve in the relief line is directly controlled via a piezo actuator
  • FIG. 8 shows a third exemplary embodiment in which the valve member is actuated by a solenoid valve
  • FIG. 9 shows a fourth exemplary embodiment in which the opening of the valve in the relief line can be adjusted by means of a hydraulic counterpressure on the pressure valve
  • FIG. 10 shows a fifth exemplary embodiment 11, in which the spring pretensioning force of the valve in the relief line is adjusted via a piezo actuator
  • FIG. 11 shows a sixth exemplary embodiment in which the adjustment of the
  • FIG. 12 shows a seventh exemplary embodiment in which the spring preload force of the relief valve is adjusted via a hydraulic actuating piston
  • FIGS. 13 and 14 show an eighth exemplary embodiment in two views, in which an additional check valve is fed into an inlet line of the Damping chamber is used
  • Figure 15 is a ninth embodiment in which the valve member of the valve in the relief line is designed as an escape piston.
  • Figures 1 and 2 show a known fuel injection valve of the outward opening type with two successively controllable rows of spray holes (vario register nozzle) on which the control of the valve member stroke according to the invention is implemented.
  • 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, which projects out of the bore 3 and has an enlarged cross section, which forms a valve closing member.
  • This closing head 7, shown enlarged in FIG. 2 forms with its annular end face facing the valve body 1 a 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.
  • 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 widening of the diameter 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 space 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 located at the level of the sealing edge dissipate.
  • the outlet openings 23 (spray holes) of the injection channels (21) are arranged above the valve sealing surface 9 on the lateral surface of the closing head 7 so 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 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, which are opened one after the other during the valve member opening stroke movement.
  • longitudinal slots are also possible as injection openings, the cross-section of which is then opened analogously in at least two stages.
  • the piston-shaped 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 its end near the combustion chamber is supported against the valve body 1 and with its end remote from the combustion chamber it acts on a valve plate 33 on the valve member 5 and the valve member 5 is thus pressed against the valve seat 11 in contact holds.
  • 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 In order to limit the outward opening stroke movement of the valve member 5, the valve member 5 points out of the valve body 1 into the valve body 1 facing away from the combustion chamber Valve holding body 27 projecting end a piston 37 projecting radially from the valve member shaft, which delimits a hydraulic damping space 39.
  • Embodiment shown in Figures 3 and 4 provided according to the invention in an intermediate plate 41 which is clamped axially between an end surface 43 of the valve body 1 remote from the combustion chamber and the end surface of the valve holding body 27 on the combustion chamber side.
  • the washer is provided according to the invention in an intermediate plate 41 which is clamped axially between an end surface 43 of the valve body 1 remote from the combustion chamber and the end surface of the valve holding body 27 on the combustion chamber side.
  • the intermediate disk 41 has a part of the pressure channel 19 in the form of an axial through hole. Furthermore, the intermediate disk 41 has a central through opening 45, through which the stem of the valve member 5 projects and which delimits the damping space 39 radially outward.
  • the damping space 39 in the intermediate disk 41 is axially delimited on the one hand by the end face 43 of the valve body 1 and on the other hand by the valve member piston 37.
  • This piston 37 is formed by a sealing ring pressed onto the stem of the valve member 5, which is designed as a U-sealing ring 47 that is open to the damping chamber 39.
  • a spring 49 is inserted in this U-sealing ring 47 for basic sealing.
  • the damping chamber 39 is filled and relieved via the fuel channels shown in FIGS. 3 and 4, which are connected to the low-pressure circuit of the injection system and for the explanation of which the fuel injection valve in FIG. 4 is rotated by 90 ° in relation to the illustration in FIG. 3.
  • the damping chamber 39 is filled and relieved via two cuts on the valve member 5, which connect the damping chamber 39 to a low-pressure chamber, preferably the fuel-filled spring chamber 25, via relief channels.
  • a first bevel 51 is arranged on the valve member 5 so that when the injection valve is closed, that is to say when the valve member 5 is in contact with the valve seat 11, its upper end projects into the damping chamber 39, while its lower end opens into an annular groove 53 on the valve member 5. As shown in more detail in FIG. 4, this annular groove 53 sweeps over the mouth of a first relief channel 55, which opens into the spring chamber 25 and penetrates the valve body 1, the intermediate disk 41 and the valve holding body 27. The upper end of the first, away from the combustion chamber
  • the bevel 51 forms with its upper boundary edge a first control edge 57 which interacts with the end face 43 of the valve body 1. Passing over the first control edge 57 over the end face 43 corresponds to a valve member opening stroke position in which the first row of spray holes located below is opened, so that the distance between the control edge 57 and the end face 43 corresponds to a first opening stroke path in a first opening stroke phase of the valve member 5.
  • the first bevel 51 runs obliquely in the direction of the first control edge 57.
  • the valve member 5 Offset to the first bevel 51, has a second bevel 59, the upper boundary edge remote from the combustion chamber forming a second control edge 61.
  • the second bevel 59 With its lower end facing the combustion chamber of the internal combustion engine to be supplied, the second bevel 59 continuously covers the mouth of a second relief channel 63, which also extends through the valve body 1, the intermediate disk 41 and the valve holding body 27 to the spring chamber 25.
  • the second control edge 61 is at a greater distance from the end face 43 of the valve body 1 than the first control edge 57.
  • the passage of 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 are controlled at the injection cross section, whereby to Driving over the second control edge 61 over the end face 43 of the damping chamber 39 is finally closed hydraulically and thus determines the maximum opening stroke position of the valve member.
  • a valve 65 is inserted into the second relief line 63, which in the first exemplary embodiment is designed as a check valve.
  • This valve 65 which is inserted in the part of the second relief channel 63 that runs in the intermediate disk 41, has an axially displaceable, piston-shaped valve member 67, which has a conical sealing surface 69 at its end facing the second ground section 59, with which it cooperates with a valve seat surface 71 .
  • a valve spring 72 acts on the rear side of the valve member 67, which on the other hand is supported in a stationary manner on the valve holding body 27 and by means of the design of which the opening pressure on the valve 65 can be adjusted.
  • the opening pressure at valve 65 can be used to set the point in time at which the second opening stroke phase is to begin at valve member 5, during which the complete opening cross section is opened at the injection valve. Furthermore, the second relief channel 63 between the valve 65 and the second bevel 59 is at least partially designed as a throttle cross section.
  • a rotation lock is also provided on the valve member 5.
  • This anti-rotation device is, as shown in the two views in FIGS. 5 and 6, formed as a profile 73 on the valve member 5, with which the valve member 5 projects into a complementary recess 75 in the intermediate disk 41.
  • the fuel injection valve according to the invention works in the following way.
  • valve spring 31 holds the valve member 5 with its valve sealing surface 9 in contact with the valve seat 11, the piston 37 delimiting the damping chamber 39 is in its starting position and the damping chamber 39 is via the first bevel 51, the annular groove 53 and the first relief channel 55 connected to the fuel-filled spring chamber 25 (low pressure chamber) and filled by this with fuel that serves as a hydraulic working fluid.
  • 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 cross-section on the injection valve, the valve member 5 remains in a first operating mode of the injection valve, which is the idling range and corresponds to a partial load range of the internal combustion engine to be supplied.
  • the second operating mode is selected on the injection valve.
  • the 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 has so far been constantly connected to the damping chamber 39.
  • valve 65 When 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 takes place in an advantageous manner damped, the degree of damping on the valve member depending 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).
  • further intermediate positions of the opening stroke position of the valve member are possible by providing further hydraulic stops.
  • the second exemplary embodiment shown in FIG. 7, analogous to the representation in FIG. 3, differs from the first exemplary embodiment by the direct control of the valve 65 in the relief channel 63
  • Valve member 67 has a piston rod 77, which is fastened to an actuator 79 of a piezo actuator, which is supported in the housing valve in the closing direction of the valve member 67.
  • the valve spring 72 acts on the piezo actuator 79, prestresses it and holds the valve member 67 in contact with the valve seat.
  • the electrical actuation of the piezo actuator 79 takes place as a function of a characteristic diagram of the internal combustion engine to be supplied and as a function of the instantaneous injection, an adjustment being possible even during an injection process.
  • the connection between the piezo actuator 79 and the valve member 67, 77 can also be made via transmission elements.
  • valve member 67 of the valve 65 is actuated in the second relief channel 63 via a solenoid valve, the rod 77 of the pressure valve member 67 being connected to an armature 81 or forming part of it.
  • This armature 81 projects into a current-carrying coil 83 of the solenoid valve, so that the position of the armature 81 and thus of the valve member 67 can be adjusted by the controlled change in the applied electrical voltage.
  • the basic setting of the valve can be carried out by an additional adjusting spring 85 in addition to the valve spring 72.
  • Valve 65 in the second relief channel 63 by the application of an adjustable hydraulic counterpressure to the spring-side rear side of the valve member 67.
  • this pressure which counteracts the pressure in the damping chamber 39, is built up in an additional hydraulic system in a manner not shown, and the valve 65 via the control line 87 fed.
  • the opening movement of the valve member 67 can thus be adjusted by the pressure difference between the damping chamber 39 and the back pressure in the control line 87 in addition to the force of the valve spring 72.
  • the opening time or the closing characteristic is set on the valve 65 in the second relief channel 63 via the characteristic map. dependent adjustment of the spring preload force of the valve spring 72.
  • 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 Adjusting washer 91 is supported directly on 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
  • FIG. 12 shows a seventh exemplary embodiment in which the axial adjustment of the spring contact surface of the valve spring 72 of the valve 65 in the second relief channel 63 is carried out hydraulically.
  • the spring support surface is provided on a piston 97, on one end face of which the valve spring 72 rests and the other end face of which limits a hydraulic working space 99.
  • This work space 99 is from a control line 101 a hydraulic system can be filled with a pressurized hydraulic fluid, the pressure supply being adjustable depending on the operating map of the internal combustion engine.
  • the axial adjustment 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 relief in the working 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.
  • Check valve spring 111 is supported in a stationary manner on valve body 1 and acts on stepped piston 107 on its end face facing away from spring chamber 25.
  • the stepped piston 107 is designed so that it is already in contact with the valve seat 113 with its larger one
  • Step piston 107 is only moved when the pressure between the spring chamber 25 and the damping chamber 39 is 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 avoidance of 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 escape 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.

Landscapes

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

Abstract

L'invention concerne un injecteur de carburant pour moteurs à combustion interne, comportant un élément soupape (5) émergeant du corps de soupape (1). Cet élément soupape (5) présente au moins deux rangées superposées d'orifices d'injection (23), dont l'ouverture successive peut être commandée lors de la course d'ouverture de l'élément soupape (5) dirigée vers l'extérieur. Cet élément soupape (5) présente également une butée de course hydraulique à deux étages limitant la course d'ouverture dudit élément soupape (5). Cette butée se présente sous la forme d'une chambre d'amortissement hydraulique (39) à décharge, dont la fermeture peut être commandée. Cette décharge s'effectue par l'intermédiaire d'au moins deux parties réalisées par meulage (51, 59) au niveau de l'élément soupape (5), dont la fermeture successive peut être commandée pendant la course d'ouverture de l'élément soupape (5). Au moins une des parties réalisées par meulage peut être mise en communication avec une chambre basse pression par l'intermédiaire d'un canal de décharge (63) contenant une soupape (65).
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 true EP0937203A1 (fr) 1999-08-25
EP0937203B1 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)

Families Citing this family (16)

* 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
US6691935B1 (en) * 2000-02-07 2004-02-17 Robert Bosch Gmbh Injection nozzle
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 Maschinenfabrik GmbH, 59302 Oelde 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
US10731614B2 (en) * 2015-10-15 2020-08-04 Continental Automotive Gmbh Fuel injection valve with an anti bounce device
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

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2762654A (en) * 1952-07-01 1956-09-11 Gen Motors Corp Fuel injection device
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
DE19618698A1 (de) * 1996-05-09 1997-11-13 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19642440A1 (de) 1996-10-15 1998-04-16 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9913214A1 *

Also Published As

Publication number Publication date
WO1999013214A1 (fr) 1999-03-18
US6105879A (en) 2000-08-22
DE19739905A1 (de) 1999-03-18
DE59804130D1 (de) 2002-06-20
JP2001504915A (ja) 2001-04-10
EP0937203B1 (fr) 2002-05-15

Similar Documents

Publication Publication Date Title
EP0898650B1 (fr) Dispositif d'injection de carburant pour moteurs a combustion interne
EP0937203B1 (fr) Injecteur de carburant
DE4311627A1 (de) Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE19816316A1 (de) Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE19709794A1 (de) Ventil zum Steuern von Flüssigkeiten
DE19546033A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19618698A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10100390A1 (de) Einspritzventil
DE19716226C2 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10205218A1 (de) Ventil zur Steuerung einer Verbindung in einem Hochdruckflüssigkeitssystem, insbesondere einer Kraftstoffeinspitzeinrichtung für eine Brennkraftmaschine
DE10210927A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
EP2458194B1 (fr) Soupape d'injection de carburant pour moteurs à combustion interne
DE102007010498A1 (de) Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Brennkraftmaschine
DE102006050042A1 (de) Injektor zur Einspritzung von Kraftstoff in Brennräume von Brennkraftmaschinen
DE102012224398A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19642440A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1961953A1 (fr) Soupape à plusieurs voies
EP1290340A1 (fr) Dispositif d'injection de carburant pour moteurs a combustion interne
DE4315436A1 (de) Vorrichtung zur Regelung der Leerlaufdrehzahl einer Brennkraftmaschine
DE19747092A1 (de) Durchflußbegrenzungsvorrichtung für Brennkraftmaschinen
DE19623759A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
EP1339974A1 (fr) Systeme d'injection de carburant
DE4041878C2 (de) Kraftstoff-Einspritzventil für einen Dieselmotor
DE10032924A1 (de) Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
DE102005005713A1 (de) Düsenbaugruppe und Einspritzventil

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB

17P Request for examination filed

Effective date: 19990920

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 20010516

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 59804130

Country of ref document: DE

Date of ref document: 20020620

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20020801

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20030127

Year of fee payment: 6

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20030218

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20040218

Year of fee payment: 7

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20040227

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20040414

Year of fee payment: 7

GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20051031

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20051031