EP4107386A1 - Soupape d'injection de carburant pour des moteurs à combustion interne - Google Patents

Soupape d'injection de carburant pour des moteurs à combustion interne

Info

Publication number
EP4107386A1
EP4107386A1 EP21706532.5A EP21706532A EP4107386A1 EP 4107386 A1 EP4107386 A1 EP 4107386A1 EP 21706532 A EP21706532 A EP 21706532A EP 4107386 A1 EP4107386 A1 EP 4107386A1
Authority
EP
European Patent Office
Prior art keywords
valve member
head
intermediate part
chamber
shaft
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.)
Pending
Application number
EP21706532.5A
Other languages
German (de)
English (en)
Inventor
Marco Ganser
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.)
Ganser Hydromag AG
Original Assignee
Ganser Hydromag AG
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 Ganser Hydromag AG filed Critical Ganser Hydromag AG
Publication of EP4107386A1 publication Critical patent/EP4107386A1/fr
Pending 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/025—Hydraulically 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
    • 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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • 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
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035—Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • 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
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
    • 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
    • F02M63/0077—Valve seat details
    • 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
    • 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
    • F02M2200/07—Fuel-injection apparatus having means for avoiding sticking of valve or armature, e.g. preventing hydraulic or magnetic sticking of parts

Definitions

  • the present invention relates to a fuel injector for intermittent
  • a fuel injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine is described, for example, in the document WO 2016/041739 A1. It has a hydraulic control device for controlling the axial movement of an injection valve member by changing the pressure in a control chamber.
  • An intermediate valve of the hydraulic control device has a mushroom-shaped intermediate valve member, the shaft of which is guided with a tight sliding fit in a guide recess extending through an intermediate part.
  • a head of the intermediate valve member is with its sealing surface running at a radial distance around the shaft - in the closed position of the intermediate valve member - on an annular formed on the intermediate part
  • Intermediate valve seat close-fitting.
  • An annular space that is delimited by the intermediate part, the shaft and the head and has an inner annular space running around the shaft is permanently connected to a high pressure via a fuel passing through the intermediate part Housing of the fuel injector formed fuel high-pressure inlet connected.
  • the intermediate valve with the shaft guided in a tight sliding fit on the intermediate part permanently separates the control chamber from a valve chamber, except for a throttle passage of precise size formed on the intermediate valve member, which permanently connects the control chamber with the valve chamber.
  • the intermediate valve In the closed position of the intermediate valve member, the intermediate valve separates the fuel high pressure allowance and the annular space from the control chamber, and when the intermediate valve member is moved away from the closed position, the intermediate valve releases a connection between the annular space and the fuel high pressure allowance and the control chamber.
  • the valve chamber can be connected to and separated from a low-pressure fuel return.
  • the valve chamber is connected to the low-pressure fuel return by means of the actuator arrangement, after which fuel flows from the control chamber into the valve chamber through the throttle passage in the intermediate valve element and, as a result of the associated pressure drop in the control chamber, the injection valve element is lifted from the injection valve seat located on the housing.
  • Another fuel injector is described in document EP 1 991 773 B1.
  • control chamber and a valve chamber are permanently connected to one another via a precise throttle passage
  • an intermediate valve also permanently separates these two chambers from one another.
  • the throttle passage is arranged directly adjacent to the control room.
  • Injection valve member as well as a rapid one
  • the invention relates to a fuel injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine, with a housing defining a longitudinal axis, the one
  • a high-pressure chamber which runs from the high-pressure fuel inlet to the injection valve seat, is arranged in the housing. Also in the housing is one that interacts with the injection valve seat
  • Injection valve member arranged adjustable in the direction of the longitudinal axis.
  • the fuel injection valve further comprises a compression spring which acts on the injection valve member with a closing force directed in the direction against the injection valve seat and which is preferably supported on the one hand on the injection valve member and on the other hand is supported in a stationary manner relative to the housing; a guide part in which a control piston of the injection valve member is guided in a sliding fit; an intermediate part which, together with the guide part and the control piston, delimits a control space; and a hydraulic control device for controlling the axial movement of the injection valve member by changing the pressure in the control chamber.
  • the hydraulic control device comprises an intermediate valve with a mushroom-shaped intermediate valve member which has a shaft and which is guided in a guide recess of the intermediate part has a head, and an intermediate valve seat which is formed on a side of the intermediate part facing the head and cooperates with the head.
  • the intermediate valve member releases a connection between a high-pressure fuel inlet connected to the high-pressure chamber and the control chamber. This interrupts in a closed position
  • High-pressure fuel admission and the control room and separates the control room - with the exception of a throttle passage - from a valve chamber.
  • the fuel injection valve further comprises an electrically operated actuator arrangement for connecting the valve chamber to a low-pressure fuel return and for separating the valve chamber from the low-pressure fuel return.
  • the head is in the closed position of the
  • the guide part and the intermediate part can be used as be designed as independent components. However, it is also possible for the guide part and the intermediate part to be formed integrally as a one-piece component.
  • the throttle passage is preferably formed on the intermediate valve member, particularly preferably on the head of the intermediate valve member.
  • the throttle passage can, however, also be formed on the intermediate part.
  • the throttle passage can be formed between the intermediate valve member and another component, for example through a gap between the intermediate part or the guide part.
  • the throttle passage formed on the intermediate valve member can open on the side facing away from the control chamber into a blind hole that is recessed on the intermediate valve member and belonging to the valve chamber.
  • the throttle passage is preferably formed in the intermediate valve member adjacent to the control chamber.
  • the throttle passage and the blind hole are preferably formed centrally to the longitudinal axis.
  • the first sealing surface and the second are preferably
  • the first sealing surface can be formed on the head, ie on the side of the head facing the intermediate part, or on the intermediate part, ie on the side of the intermediate part facing the head.
  • the second sealing surface can in turn, depending on the configuration, on the head, ie on the side of the head facing the intermediate part, or on the intermediate part, ie on the side of the intermediate part facing the head.
  • the fact that the head rests against the intermediate valve seat in the closed position of the intermediate valve member forming a first and a second ring sealing surface makes it possible to improve the fluidic interruption of the connection between the high-pressure fuel inlet and the control chamber in the closed position of the intermediate valve member.
  • the separation of the control chamber from the valve chamber, which exists in the closed position of the intermediate valve member except for the throttle passage can be improved, which enables more precise control of the axial movement of the injection valve member by coordinating the dimensions of the throttle passage and thus the injection process.
  • the sealing properties of the intermediate valve can be improved while limiting or minimizing adhesive forces between the intermediate part and the intermediate valve member, since the ring sealing surfaces are small compared to the facing surfaces of the head and the intermediate part.
  • an intermediate space preferably a split ring space
  • the annular sealing surfaces seal the gap both with respect to the valve chamber and with respect to the control chamber away.
  • the ring sealing surfaces seal off the intermediate space from the high-pressure fuel inlet.
  • the split ring space measured in the direction of the longitudinal axis, has a gap width of less than 1 mm, or less than 0.5 mm, or less than 0.1 mm, or less than 0.05 mm. In one embodiment, the
  • High-pressure fuel allowance in the intermediate part in such a way that the high-pressure fuel allowance in the closed position of the intermediate valve member opens into a split ring space which, in the closed position of the intermediate valve member, is formed between the intermediate part and the head and is radially delimited by the first and second ring sealing surfaces.
  • both the valve space and the control space in the closed position of the intermediate valve element can be removed from the high-pressure fuel inlet or the
  • the high-pressure chamber can be fluidically separated. This offers the advantage that, in the closed position of the intermediate valve member, the entry of fuel from the high pressure chamber through the high pressure fuel inlet into the valve chamber or the control chamber can be minimized or avoided, thereby improving the precision of the control of the injection process.
  • the height of the shaft in the axial direction, ie along the longitudinal axis, can also be reduced, since the guide of the shaft in the guide recess no longer has to take on an additional function of fluidic sealing. This advantageously allows a more compact design. Furthermore, due to the increased play during an opening movement of the intermediate valve member to end an injection process the valve chamber can be flooded more quickly by fuel flowing through between the shaft and the guide recess, as a result of which the termination of the injection process can be accelerated.
  • the gap ring space measured in the direction of the longitudinal axis, can have a gap width of less than 1 mm, or less than 0.5 mm, or less than 0.1 mm, or less than 0.05 mm.
  • the high-pressure fuel inlet can comprise a bore that is horizontal with respect to the longitudinal axis and a vertical bore, the vertical bore opening into the split ring space in the closed position of the intermediate valve member.
  • the shaft can be guided in a sliding fit in the guide recess of the intermediate part in such a way that there is a clearance of at least 10 pm, preferably between 20 pm and 50 pm, in the radial direction between the shaft and the guide recess.
  • the intermediate valve member has an inlet, which with a first end into the The valve chamber opens and a second end opens onto an outside of the intermediate valve member in such a way that the second end is in the closed position of the
  • Intermediate valve member is arranged at a radially smaller distance from the shaft than the second ring sealing surface.
  • valve chamber can be flooded more quickly with fuel from the high-pressure chamber via the inlet when the valve chamber is removed from the valve chamber by the actuator arrangement to end an injection process
  • one of the guide recess of the is under the outside of the intermediate valve member
  • Front side formed a blind hole, which preferably protrudes into the head and forms part of the valve chamber.
  • the first end of the admission can open into the blind hole.
  • an inner annular space is formed which adjoins the shaft and the second annular sealing surface, the admission in the closed position of the
  • Intermediate valve member connects the inner annular space with the valve space.
  • the admission can open with the second end on an outside of the shaft or the head.
  • the second end of the inlet is arranged on a line at which the shaft connects to the head.
  • the admission can be designed as an inclined or horizontal bore with respect to the longitudinal axis.
  • the admission has a larger diameter than the smallest diameter of the low-pressure fuel return.
  • the diameter of the inlet By dimensioning the diameter of the inlet, rapid flooding of the valve chamber can be achieved, which has a positive effect on the opening process of the intermediate valve.
  • the large dimensions of the inlet can be made possible without generating additional leakages, since the inlet can be fluidically separated from the high-pressure chamber in the closed position of the intermediate valve member due to the arrangement of the second end.
  • the shaft has at least one circumferential ring projection, over which at least one circumferential ring projection the shaft is guided in the guide recess.
  • a throttle passage extending around the shaft in the axial direction can be formed between the shaft and the guide recess.
  • the throttle passage formed by the annular projection offers the advantage that a turbulent flow instead of a laminar flow can be achieved for the fluid flowing through in the longitudinal direction in the space between the shaft and the guide recess.
  • the range of permissible radial play between the shaft and the guide recess to be further enlarged.
  • the shaft has two annular projections which are spaced apart from one another in the longitudinal direction of the shaft. Due to the two circumferential ring projections spaced apart from one another in the longitudinal direction of the shaft, two throttle passages, which are connected in series along the longitudinal axis and circumferential around the shaft, can be formed in the longitudinal direction. As a result, the formation of eddies and the turbulent flow of the fluid flowing through the space between the shaft and the guide recess can be further promoted.
  • the play in the radial direction between the shaft and the guide recess can also be increased further by acting as series-connected throttle passages.
  • the shaft can be in such a way
  • the guide recess of the intermediate part can be guided so that there is a clearance of at least 50 pm, preferably between 70 pm and 100 pm, in the radial direction between the shaft and the guide recess.
  • the intermediate valve member has a valve chamber passage which is connected to the valve chamber and which runs in the intermediate valve member in such a way that the valve chamber passage in the closed position of the
  • Intermediate valve member opens into a split ring space, which in the closed position of the intermediate valve member is formed between the intermediate part and the head and is delimited radially by the first and the second ring sealing surface.
  • valve chamber passage can advantageously be sealed in the closed position of the intermediate valve member with respect to the control chamber and the high-pressure fuel inlet. This advantageously allows the diameter of the
  • valve chamber passage large compared to, for example, the diameter of the throttle passage, without thereby promoting leaks from the control chamber or the high-pressure fuel inlet into the valve chamber passage or the valve chamber in the closed position of the intermediate valve member.
  • a large dimensioning of the valve chamber passage offers the advantage that the valve chamber can be quickly flooded through the valve chamber passage when the intermediate valve member is moved away from the closed position, which enables an injection process to be terminated quickly.
  • the fuel injection valve has an annular space which is delimited by the intermediate part, shaft and head in the closed position of the intermediate valve member and into which the high-pressure fuel inlet opens.
  • the annular space preferably has an inner annular space which runs around the shaft and is delimited in the radial direction by the shaft and intermediate part, which is preferably excluded on the shaft itself, the high-pressure fuel inlet preferably opening into the inner annular space.
  • the annular space preferably has a split ring space adjoining the inner annular space, which in the closed position of the intermediate valve member is formed by a circumferential gap between the intermediate part and the head of the intermediate valve member.
  • the split ring space can have an at least approximately constant gap width.
  • the gap width is preferably at least five times smaller than the inner annular space, measured in each case in the direction of the longitudinal axis.
  • the inner ring space on the shaft of the intermediate valve member is preferably formed by a circumferential ring groove that is open to the outside in the radial direction and which, viewed in the direction of the longitudinal axis, preferably has such a dimension that the mouth of the fuel high pressure allowance is always at least almost completely in the area of the ring groove .
  • the annular groove preferably adjoins the head directly. This advantageously enables a simple design of the intermediate part.
  • the entire mouth of the high-pressure fuel inlet is preferably located in the area of the inner ring space. This means that any inclined bores that might otherwise be required on the intermediate part can be avoided.
  • the annular groove preferably has a trapezoidal cross-section, the oblique side being the Head is turned away. With this side, when the intermediate valve member is open, the through the
  • Intermediate valve member has a valve chamber passage connected to the valve chamber, which in the
  • the shaft In the closed position of the intermediate valve member opens into the split ring space and the high-pressure fuel inlet opens into the annular space delimited by the intermediate part, shaft and head, the shaft is preferably guided in a tight sliding fit in the guide recess of the intermediate part, so that leakage of the high-pressure fuel inlet into the valve space via the guide of the shaft can be prevented or minimized.
  • a secondary passage is formed on the intermediate valve member, preferably on the shaft, which the high-pressure fuel admission or the
  • a secondary passage can be formed on the intermediate part.
  • the secondary passage preferably opens through a straight one that runs in the radial direction
  • Throttle bore in the valve chamber preferably in the blind bore of the shaft.
  • the secondary passage is via the in the closed position of the intermediate valve member from
  • the secondary passage can extend into the valve chamber from the annular groove, preferably from its radially inner base and preferably in the radial direction with respect to the longitudinal axis.
  • the shaft of the intermediate valve member can have a preferably groove-shaped pocket recess proceeding from the annular groove, from which the secondary passage extends into the valve chamber, preferably also with respect to the longitudinal axis in the radial direction. In the embodiment with one pocket recess, two diametrically opposite one another are preferred
  • valve chamber passage has a bore in the head which is parallel to the longitudinal axis or inclined with respect to the longitudinal axis and which opens into the split ring chamber in the closed position of the intermediate valve member.
  • the valve chamber passage preferably also has a horizontal bore in the head, which connects the bore, which is parallel to the longitudinal axis or inclined with respect to the longitudinal axis, to the blind bore.
  • the intermediate valve member can also have two or more valve chamber passages which each open into the split ring chamber.
  • several parallel or inclined bores belonging to the respective valve chamber passages can be present in the head, each of which opens into the split ring chamber.
  • a first annular sealing bead is formed with a first end face which forms the first sealing face.
  • the sealing bead offers the advantage that a reliable fluidic seal can be provided with the formation of an annular sealing surface, while at the same time adhesion forces between the intermediate part and the intermediate valve member can be reduced or minimized.
  • a second annular sealing bead with a second end face, which forms the second sealing face, is preferably formed on the side of the head facing the intermediate part or on the side of the intermediate part facing the head. In configurations in which the sealing bead is formed on the head, a flat surface of the intermediate part opposite the sealing bead generally forms the intermediate valve seat. In configurations in which the sealing bead is formed on the intermediate part, the end face of the sealing bead generally forms both the
  • the first sealing bead and the second are preferably Sealing bead both formed on the head or both on the intermediate part.
  • one of the sealing beads is formed on the head and the other of the sealing beads is formed on the intermediate part.
  • the intermediate part has at least one step in the radial direction on the side facing the head and the head has at least one step in the radial direction on the side facing the intermediate part, with edges of the steps of the intermediate part and the head offset from one another in the closed position of the intermediate valve member each limit the first and / or the second ring sealing surface radially.
  • the gradation of the intermediate part or of the head is generally designed to run around the shaft or the guide recess.
  • the gradation of the intermediate part or of the head can be formed by an undercut or a projection.
  • the gradation of the intermediate part and / or the head can have vertical and horizontal surfaces.
  • the gradation can also have a chamfered or curved surface.
  • a step which is formed by an edge of the head or of the intermediate part can in particular also fall under gradation in this context.
  • the dimensions of the first and / or second ring sealing surface can advantageously be matched by suitable dimensioning of the gradations.
  • gradations and / or combination with one or more sealing beads in the closed position of the intermediate valve member one or more several intermediate spaces, in particular split ring spaces, into which one or more passages such as valve chamber passages, high-pressure fuel inlets, etc. can open.
  • a gradation of the intermediate part forms an inner annular space, which in
  • the shaft is preferably continuously guided in the guide recess of the intermediate part.
  • the housing of the fuel injector preferably has a housing body with the high-pressure fuel inlet and a nozzle body on which the injector seat is formed.
  • the intermediate part and thus the intermediate valve are preferably arranged in the nozzle body. This advantageously enables, viewed in the longitudinal direction, a short design of the housing body and also of the injection valve member.
  • the housing has a housing body with the high-pressure fuel inlet and a nozzle body on which the injection valve seat is formed, but the intermediate part and thus the intermediate valve being arranged between the housing body and the nozzle body. This advantageously allows a slim design of the nozzle body.
  • the guide recess (open in the direction of the control chamber) is designed like a blind hole, one from the guide recess, preferably from its bottom, to the low-pressure fuel return
  • Outlet bore is formed on the intermediate part. This outlet bore is preferably designed to taper in a step-like manner, as seen from the guide recess.
  • two-part solutions can also be used, as shown, for example, in FIGS. 2 to 4,
  • an intermediate element can be connected above the intermediate part, wherein the outlet bore can be formed in the intermediate element and the outlet bore can be formed in the intermediate part
  • Guide recess can be designed as a continuous bore.
  • the intermediate element is preferably designed in the form of a plate.
  • the valve chamber usually includes the from
  • the mouth of the outlet bore facing the low-pressure fuel return preferably forms the low-pressure outlet.
  • the housing has a
  • the intermediate body preferably has a receiving recess which is open in the direction of the nozzle body and connected to the high-pressure chamber and in which the intermediate part is arranged.
  • the intermediate body can be part of the actuator arrangement.
  • a plunger of the actuator arrangement preferably runs through a corresponding passage in the intermediate body in order to close or open the low-pressure outlet formed on the intermediate part.
  • the intermediate body preferably forms a guide element for the plunger.
  • the housing body preferably rests on one end face of the intermediate body and the nozzle body rests in a sealing manner on the opposite end face of the intermediate body.
  • the guide recess is delimited on the side facing the control chamber by a shoulder formed on the intermediate part and set back with respect to the end face facing the nozzle body, this shoulder being able to have the intermediate valve seat.
  • a head space can be formed between this shoulder and the end face of the intermediate part facing the nozzle body, in which the head of the intermediate valve member can be accommodated.
  • This embodiment makes it possible to design the guide part in a simple manner, since its end facing the intermediate part can form a stop for limiting the stroke of the intermediate valve member.
  • the guide part is preferably formed by a circular cylindrical guide sleeve on which the compression spring is supported, the compression spring thereby pressing the guide sleeve against the intermediate part in a sealing manner.
  • the throttle passage must be temporarily closed in order to reduce fuel loss. On the one hand, this can be the case as set out in the following paragraph. On the other hand, there is also the possibility of temporarily closing the throttle passage with a shut-off valve, as is known, for example, from WO 2018/162747 A1 and DE 19516 565 A1.
  • control piston of the injection valve member has a cam-shaped projection on its side facing the intermediate valve, which can close the throttle passage when it is in contact with the intermediate valve member.
  • the invention further relates to a
  • Fuel fine injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine, with a housing defining a longitudinal axis, the one
  • High-pressure fuel inlet and an injection valve seat a high-pressure chamber which is arranged in the housing and runs from the high-pressure fuel inlet to the injection valve seat, an injection valve member which is adjustable in the direction of the longitudinal axis and which interacts with the injection valve seat, a compression spring which pushes the injection valve member towards the injection valve seat directional closing force acted upon, a guide part in which a control piston of the injection valve member is guided in a sliding fit, an intermediate part which, together with the guide part and the control piston, delimits a control chamber, a hydraulic control device for controlling the axial movement of the injection valve member by changing the pressure in the control chamber, with a Intermediate valve comprising a mushroom-shaped intermediate valve member which has a shaft guided in a guide recess of the intermediate part and a head, and an intermediate valve seat which is formed on a side of the intermediate part facing the head and interacts with the head, the intermediate valve member in an open position having a first connection between a with the high-pressure chamber connected to the high-pressure fuel
  • the valve chamber can be filled with fuel via the second connection, which enables a more rapid opening movement of the intermediate valve member.
  • the second connection improves the filling of the valve chamber in comparison to a fuel injection valve in which the valve chamber is filled, for example, solely from the control chamber via a throttle passage.
  • the valve chamber can therefore advantageously be filled via the second connection even with a small opening movement of the intermediate valve member.
  • the throttle passage it is advantageously sufficient if the flow of fuel from the control chamber into the valve chamber through the throttle passage causes the initially small opening movement of the intermediate valve member, since the valve chamber can then be filled with a large amount of fuel via the second connection.
  • the fuel can also be supplied during the injection process, i.e. in the closed position of the intermediate valve member
  • the second connection runs between the high-pressure fuel inlet and a bore which runs through the shaft of the intermediate valve member and is part of the valve chamber.
  • the bore is preferably designed as a blind bore.
  • the head is in the closed position of the intermediate valve member with a side facing the intermediate part over a first radial distance around the shaft or the
  • first sealing surface with the formation of a first, in the circumferential direction closed ring sealing surface and a second sealing surface running at a second radial distance around the shaft or the guide recess to form a second, in the circumferential direction closed ring sealing surface on the intermediate valve seat, wherein the first radial distance is greater than the second radial distance.
  • a first annular sealing bead with a first end face, which forms the first sealing face, is formed on the side of the head facing the intermediate part or on the side of the intermediate part facing the head.
  • a second annular sealing bead with a second end face, which forms the second sealing face is formed on the side of the head facing the intermediate part or on the side of the intermediate part facing the head.
  • the intermediate part has at least one gradation on the side facing the head and the head has at least one gradation on the side facing the intermediate part, with edges of the gradations of the intermediate part and the head offset from one another in the closed position of the intermediate valve member each showing the first and / or or limit the second ring sealing surface radially.
  • a gradation of the intermediate part forms an inner annular space, which in
  • the closed position of the intermediate valve member is limited by the intermediate part, the shaft and the head.
  • Intermediate valve member opens into a split ring space which is formed between the intermediate part and the head in the closed position of the intermediate valve member and is limited radially by the first and the second ring sealing surface.
  • the second connection comprises an admission of the intermediate valve member, which opens with a first end into the valve chamber and with a second end opens on an outside of the intermediate valve member.
  • the valve chamber can advantageously be filled via the admission in order to support the opening movement of the intermediate valve member.
  • the first end of the inlet preferably opens into the blind hole which runs through the shaft and is part of the valve chamber.
  • the inlet opens with the second end on the outside of the intermediate valve member in such a way that the second end is arranged at a radially smaller distance from the shaft than the second ring sealing surface in the closed position of the intermediate valve member.
  • the second connection comprises a passage which is formed by a clearance in the radial direction between the shaft and the guide recess of at least 10 pm, preferably between 20 pm and 50 pm.
  • the shaft has two annular projections which are spaced apart from one another in the longitudinal direction of the shaft.
  • the ring projections each have at least one bevel in the circumferential direction
  • the second connection comprising a passage which from an intermediate space is formed between the at least one bevel and the guide recess.
  • the play between the shaft and the guide recess can be kept sufficiently small by the at least one bevel, which allows better centering of the shaft, ie avoiding or reducing an eccentric or inclined position of the shaft.
  • a sufficient passage formed by the space between the at least one chamfer and the guide recess, can be provided, which serves as a passage for the second connection.
  • the ring projections each have two or three chamfers in the circumferential direction.
  • the shaft has at least one bevel in the circumferential direction, the second connection comprising a passage which is formed by an interspace between the at least one bevel and the guide recess.
  • the play between the shaft and the guide recess can be kept sufficiently small by the at least one bevel, which allows better centering of the shaft, ie avoiding or reducing an eccentric or inclined position of the shaft.
  • a sufficient passage formed by the space between the at least one bevel and the guide recess, can be provided which serves as a passage for the second connection.
  • the shaft has two or three chamfers in the circumferential direction.
  • the second connection comprises a bore running through the head of the intermediate valve member, which at least partially forms a valve chamber passage connected to the valve chamber and opens with one end on a side of the head facing the intermediate part.
  • valve chamber passage runs in the intermediate valve member in such a way that the
  • valve chamber passage opens into a split ring chamber which, in the closed position of the intermediate valve member, is formed between the intermediate part and the head and is delimited radially by the first and the second ring sealing surface.
  • the fuel injection valve has an annular space which is delimited by the intermediate part, shaft and head in the closed position of the intermediate valve member and into which the high-pressure fuel inlet opens.
  • FIG. 1 shows, in longitudinal section, a representation of a fuel injection valve from the prior art
  • FIG. 2 enlarged compared to FIG. 1, the part of the fuel injection valve from the prior art, which is framed by a rectangle labeled II;
  • FIG. 3 shows a detail of a first embodiment of a fuel injection valve according to the invention in longitudinal section, the detail representing a region of the fuel injection valve which corresponds to the rectangle labeled III in FIG. 2;
  • FIG. 4 shows a section of a second embodiment of a fuel injection valve according to the invention in longitudinal section, the section representing a region of the fuel injection valve which corresponds to the rectangle designated by III in FIG. 2;
  • FIG. 5a shows a section of a third embodiment of a fuel injection valve according to the invention in longitudinal section, the section representing a region of the fuel injection valve which corresponds to the rectangle designated by III in FIG. 2;
  • FIG. 5b shows a detail of a horizontal cross-sectional representation of another Embodiment of an inventive
  • FIG. 6 shows a detail of a fourth embodiment of a fuel injection valve according to the invention in longitudinal section, the detail representing a region of the fuel injection valve which corresponds to the rectangle labeled III in FIG. 2;
  • FIG. 7 shows a section of a fifth embodiment of a fuel injection valve according to the invention in longitudinal section, the section representing a region of the fuel injection valve which corresponds to the rectangle labeled III in FIG. Description of exemplary embodiments
  • Figure 1 shows a fuel injection valve 10 'according to WO2016 / 041739 A1 for the intermittent injection of
  • the fuel is under very high pressure of, for example, up to 200 bar or more.
  • the fuel injector 10 ' has a housing 12' which defines a longitudinal axis L and has a
  • a union nut 22 'supported on the nozzle body 16' receives the actuator receiving body 20 'and is wound onto the housing body 14'.
  • the housing body 14 'and the actuator receiving body 20', as well as this and the nozzle body 16 'abut one another at the front, are pressed against one another in a sealing manner by means of the union nut 22' and aligned with one another in the direction of the longitudinal axis L.
  • the external shape of the housing 12 ' is at least approximately circular-cylindrical in a known manner.
  • a high-pressure fuel inlet 24 ' On the end face of the housing body 14 'facing away from the nozzle body 16' there is a high-pressure fuel inlet 24 ', from which inside the housing 12' - through the housing body 14 ', the actuator receiving body 20' and the nozzle body 16 '- to the injection valve seat 18'. a high pressure chamber 26 'runs.
  • the high-pressure fuel inlet 24 ' is formed by a valve carrier 28', which carries a check valve 30 'and a basket-like perforated filter 32' for holding back any foreign particles in the fuel.
  • the disc-shaped valve member of the check valve 30 ' which interacts with a valve seat formed on the valve carrier 28', has a bypass bore.
  • the check valve 30 allows fuel supplied via a high-pressure feed line to flow into the high-pressure chamber 26' practically without any obstacles in the known manner, but prevents the outflow of the fuel Fuel from the high pressure chamber 26 'into the
  • High-pressure fuel inlet 24 'and the valve carrier 28' with check valve 30 'and perforated filter 32' can also be designed, as disclosed in document WO2013 / 117311 A1.
  • One possible embodiment of the high-pressure fuel inlet 24 'and the check valve 30', as well as a rod filter instead of the perforated filter 32 ', is known from document WO2009 / 033304 A1. The corresponding disclosure of the above-mentioned documents is deemed to be incorporated into the present disclosure by reference.
  • High-pressure chamber 26 ' has a discrete storage chamber 34' which is formed on the housing body 14 'and which, on the other hand, is connected to the injection valve seat 18' via a flow channel 36 'of the high-pressure chamber 26'.
  • a stationary immovable throttle can also be provided in certain embodiments.
  • an electrically operated actuator assembly 38' is received in a known manner, which is intended with its spring-loaded in one direction and in the other direction by means of an electromagnet of the actuator assembly 38 'movable plunger 40' to a
  • the longitudinal axis of the plunger 40 ' denoted by 48', and thus of the actuator arrangement 38 ', runs parallel and eccentrically to the longitudinal axis L.
  • Parallel to the discrete storage chamber 34' which is eccentrically arranged with respect to the longitudinal axis L of the housing 12 'and thus of the fuel injector 10', runs from an electrical connection 50 'through the housing body 14' to the actuator assembly 38 'a channel 52' in which the electrical control line for controlling the
  • Actuator assembly 38 ' is added.
  • the plunger 40 ' extends through the bottom of the cup-shaped actuator receiving body 20', which forms a guide element for the plunger 40 '.
  • the plunger 40 ' has guide wings protruding in the radial direction, with which it is slidably guided on the guide element parallel to the longitudinal direction L.
  • the guide vanes form passages extending in the longitudinal direction L through which the fuel can flow from the low-pressure outlet 42 'to the low-pressure fuel return 46'.
  • FIG. 2 shows an enlarged section of the fuel injector from FIG. 1 in the area of the rectangle labeled II.
  • the conical injection valve seat 18 ' is formed on the nozzle body 16', which via the flow channel 36 'with the
  • High fuel pressure inlet 24 ' is directly connected.
  • injection openings 54' are formed in a hemispherical free end region of the nozzle body 16 'in a known manner, through which, when the injection valve member 56' is lifted from the injection valve seat 18 ', the fuel is under very high pressure is injected into the combustion chamber of the internal combustion engine.
  • the injection valve member 56 ' is needle-shaped and interacts with the injection valve seat 18'.
  • the injection valve member 56 ' is in a guide bore 57' in the nozzle body which is concentric to the longitudinal axis L and belongs to the high-pressure chamber 26 'in the direction of the
  • the interior space 58' of the nozzle body 16 'belonging to the high-pressure chamber 26' is designed to widen twice towards the actuator receiving body 20 ', the approximately in the longitudinal center of the nozzle body 16 'up to its end face of the interior 58' facing the actuator receiving body 20 'defines an internally circular cylindrical portion 60' of the nozzle body 16 'with a constant cross section.
  • a support ring is formed on the injection valve member 56 ', on which a compression spring 62' is supported at one end.
  • the compression spring 62 ' is supported at the end on a guide sleeve 64 "forming a guide part 64'.
  • the compression spring 62 ' acts on the injection valve member 56' with a closing force acting in the direction of the injection valve seat 18 ' Guide part 64 'or the guide sleeve 64 "with its the
  • the guide part 64 ' can be in a form other than a sleeve, for example as
  • Cuboid or ring body be formed.
  • a double-acting control piston 68 'formed on the injection valve member 56' is guided displaceably in the direction of the longitudinal axis L.
  • the intermediate part 66 ' is part of a hydraulic control device 72'.
  • FIG. 3 shows a section of a first embodiment of one according to the invention Fuel injector 10 in longitudinal section.
  • Fuel injection valve 10 which corresponds to the rectangle labeled III in FIG.
  • Fuel injection valve 10 differs from fuel injection valve 10 ′ shown in FIG. 2 according to WO2016 / 041739 A1, in particular with regard to hydraulic control device 72, and is described below with reference to FIG.
  • the remaining area of the first embodiment of the fuel injector 10 outside the rectangle labeled III essentially corresponds to the fuel injector 10 ′ shown in FIGS. 1 and 2. This also applies accordingly to the sections of the further embodiments of the invention
  • Fuel fine injection valve 10 which are shown in Figures 4-7.
  • a circular cylindrical guide recess 74 extends through an intermediate part 66 from the flat end face facing the control chamber 70 to the likewise flat end face facing away from the control chamber 70.
  • a shaft 76 of a mushroom-shaped intermediate valve member 78 is guided in this.
  • a head 80 of the intermediate valve member 78 formed integrally with the shaft 76 is located in the control chamber 70 and, with its side facing the intermediate part 66, interacts with the intermediate part 66, the flat end face of which forms an annular intermediate valve seat 82.
  • the intermediate valve member 78 forms together with the intermediate valve seat 82 formed on the intermediate part 66
  • a first annular sealing bead 111 running at a first radial distance rl around the shaft 76 is formed, with a first end face 111.1 which forms the first sealing face 111.2.
  • a second annular sealing bead 112 running around the shaft 76 at a second radial distance r2 is formed, with a second end face 112.1 which forms the second sealing face 112.2.
  • the intermediate valve member 78 is in the closed position in which the head 80 with its
  • the ring sealing surface 122 rests on the intermediate valve seat 82.
  • the first radial distance rl is greater than the second radial distance r2 from the shaft 76.
  • a high-pressure fuel inlet 86 which is connected to the high-pressure chamber 26 and comprises a horizontal bore 861 and a vertical bore 862, runs in the intermediate part 66.
  • the vertical bore 862 opens into a split ring space 118 which is formed between the intermediate part 66 and the head 80 and radially from the first and the second ring sealing surface 121, 122 is limited.
  • several high-pressure fuel inlets 86 can be provided.
  • the game can also be smaller, e.g. between 3 and 10 pm. In further embodiments, the play can be greater and, for example, have a value between 20 p and 50 pm.
  • the second radial distance r2 of the second ring sealing surface 122 from the shaft 76 is greater (e.g. several 1/10 mm) than the play. Due to the sealing of the high-pressure fuel inlet 86 in the closed position of the intermediate valve member 78 by the annular sealing surfaces 121, 122, the possibility of additional leakages into the valve chamber 44 generated by the play between the shaft 76 and the guide recess 74 is minimized or negligible.
  • the shaft 76 can be made shorter along the longitudinal axis L compared to the prior art, such as in the fuel injection valve of WO2016 / 041739 A1. Furthermore, the intermediate part 66 can also be made shorter in the direction of the longitudinal axis L, so that a more compact design is made possible.
  • an intermediate element 98 is subsequently arranged above the intermediate part 66, through which an outlet bore 102 which tapers in steps and which is connected at one end to the guide recess 74 and at the other end forms the low-pressure outlet 42.
  • the outlet bore 102 is arranged eccentrically with respect to the longitudinal axis L.
  • the intermediate element 98 is formed integrally with the intermediate part 66 as a one-piece intermediate part in which the
  • Guide recess is designed as a blind hole (see e.g. Figure 5a).
  • the length of the shaft 76 in the direction of the longitudinal axis L is dimensioned in comparison to the guide recess 74 such that in the closed position of the
  • the intermediate valve member 78 has an inlet 96, which opens with a first end into a blind hole 92 running through the shaft 76, which is part of the valve chamber 44, and with a second end at the
  • the outside of the intermediate valve member 78 opens onto a line on which the shaft 76 adjoins the head 80.
  • Annular space 117 is formed which adjoins the shaft 76 and the second annular sealing surface 122, the inlet 96 connecting the inner annular space 117 to the blind hole 92 and the valve space 44 in the closed position of the intermediate valve member 78.
  • the blind hole 92 runs through the shaft 76 and protrudes into the head 80.
  • the admission 96 is designed as a bore which is inclined with respect to the longitudinal axis L.
  • the admission 96 can, however, also be designed as a horizontal bore in further embodiments.
  • a throttle passage 90 is formed on the head 80, which extends from the end face of the head 80 facing the control piston 68 to the blind hole 92 and connects the valve chamber 44 with the control chamber 70.
  • the permit 96 has a larger diameter than that of the
  • Throttle passage 90 on.
  • the diameter of the inlet 96 can also be larger than the smallest diameter of the stepped outlet bore 102.
  • the intermediate valve member 78 releases a second connection between the high-pressure fuel allowance 86 and the valve chamber 44 through the inlet 96, so that the valve chamber 44 or the blind hole 92 can be flooded with fuel. Even with a small movement of the intermediate valve member 78 away from the intermediate part 66, fuel can flow from the high-pressure fuel inlet 86 via the split ring space 118 and the inner annular space 117 through the inlet 96 into the blind hole 92 and support the opening movement of the intermediate valve member 78.
  • the control piston 68 has on its side facing the head 80 a cam-like projection 561 with a preferably circular cross section, which serves as a stroke limiter for the stroke of the injection valve member 56 and can rest on the intermediate valve member 78.
  • the cam-like projection 561 has a recess 5611 extending perpendicular to the plane of the drawing, through which, even when the cam-like projection 561 is in contact with the intermediate valve member 78, fuel can flow from the control chamber 70 via the throttle passage 90 into the valve chamber 44 or into the blind hole 92.
  • the recess 5611 is therefore designed to be open in the radial direction (or in the shown FIG. 3 in the direction perpendicular to the plane of the drawing) towards the control chamber 70.
  • a stop shoulder 84 is formed at a distance from the intermediate part 66 and limits the opening stroke of the intermediate valve member 78.
  • the side facing the stop shoulder 84 has wedge-like flow grooves which allow the fuel to flow from the gap to the control piston 68 with little loss when the intermediate valve member 78 is in the open position and the head 80 rests against the stop shoulder 84.
  • the guide part 64 or the guide sleeve 641 can, in certain embodiments, be integral with the
  • Intermediate part 66 can be designed as a one-piece component.
  • the intermediate valve 83 has the task of separating the high-pressure fuel inlet 86 from the control chamber 70 and from the valve chamber 44 in the closed position of the intermediate valve member 78 and, in the open position of the intermediate valve member
  • the intermediate element 98 is arranged in the nozzle body 16 and with its flat end face facing away from the intermediate part 66 rests against the corresponding end face of the actuator receiving body 20.
  • Actuator arrangement 38 have both the intermediate element 98 and the actuator receiving body 20 aligned, facing, blind hole-like
  • Positioning bores 106 in which a common positioning pin 104 is inserted.
  • aligned, blind-hole-like positioning bores are provided on these components, in which a positioning pin 1041 is also inserted. These positioning bores lie outside the plane of the drawing in FIG. 3, which is why the positioning pin 1041 is shown in dashed lines.
  • At least two positioning bores are attached to each component, each of which is aligned in pairs with positioning bores of adjacent components, so that two adjacent components are held in position relative to one another by at least two positioning pins.
  • FIG. 4 shows a section of a second embodiment of one according to the invention
  • the cutout represents an area of the
  • Fuel fine injection valve 10 which corresponds to the rectangle labeled III in FIG.
  • the second embodiment of the fuel injector according to the invention shown in FIG. 4 corresponds essentially to the first embodiment shown in FIG Intermediate part 66 are formed.
  • the first annular sealing bead 111 running at a first radial distance rl around the guide recess 74 is formed on the side of the intermediate part 66 facing the head 80, with a first end face 111.1 which forms the first sealing face 111.2.
  • the second annular sealing bead 112 running at a second radial distance r2 around the guide recess 74 is also formed on the side of the intermediate part 66 facing the head 80, with a second end face 112.1 which forms the second sealing face 112.2.
  • the first and the second end face 111.1, 112.1 at the same time form the
  • the intermediate valve seat 82 therefore comprises both the first end face 111.1 of the first sealing bead 111 and the second end face 112.1 of the second sealing bead 112. As shown in FIG.
  • two diametrically opposite, mutually corresponding high-pressure fuel inlets 86 are formed in the intermediate part 66. Further high-pressure fuel inlets can be formed in the intermediate part 66, for example on a plane which is vertical to the plane of the drawing and which runs through the longitudinal axis L.
  • the shaft 76 has an undercut adjoining the head 80, which undercut forms an inner annular space 108 which runs around the shaft 76 and is delimited in the radial direction by the shaft 76 and intermediate part 66.
  • An inner annular space 117 adjoins the inner annular space 108 and adjoins the shaft 76 and the second annular sealing surface 122.
  • a further admission (not shown in FIG. 4), for example designed as a horizontal bore, can be arranged in the shaft 76, which connects the blind bore 92 with the inner annular space 108 and is designed to support the opening process of the intermediate valve member 78.
  • FIG. 4 for example designed as a horizontal bore
  • the clearance between the shaft 76 and the guide recess 74 serves as the passage of the second connection which the intermediate valve member 78 releases in the open position between the high-pressure fuel inlet 86 and the valve chamber 44 4, does not have an allowance (such as the allowance 96 in FIG. 3) as part of the second connection, the play between the shaft 76 and the guide recess 74 is preferably greater than in an embodiment with allowance, ie, for example, the play between the shaft and the guide recess in FIG. 3.
  • the second sealing bead 112 or the second annular sealing surface 122 interrupts the second connection between the high-pressure fuel inlet 86 and the valve chamber 44.
  • a compression spring 63 is arranged between the control piston 68 and the head 80 centered about the longitudinal axis L.
  • the compression spring 63 serves to hold the intermediate valve member 78 in the closed position when the low-pressure outlet 42 is released by the raised plunger 40, in that the head 80 is pressed against the intermediate part 66, which is particularly effective at low system pressure of approx. 200 to 300 bar when the engine is idling.
  • FIG. 5a shows a detail of a third embodiment of a fuel injection valve 10 according to the invention in longitudinal section.
  • the cutout represents an area of the
  • Fuel injection valve 10 which corresponds to the rectangle labeled III in FIG.
  • Control device 72 differentiates. Similar to the embodiment of the fuel fine injection valve shown in Figure 3, the head 80 of the intermediate valve member 78 on the side of the head 80 facing the intermediate part 66 has a first sealing bead 111 running at a first radial distance rl around the shaft 76, with a first end face 111.1 , which forms the first sealing surface 111.2.
  • the second sealing surface is not formed by a sealing bead, but by a step 127 on the
  • the intermediate part 66 in the direction of the side of the head 80 facing the longitudinal axis L, which extends around the shaft 76 at a second radial distance r2.
  • the intermediate part 66 also has on the side facing the head 80 a step 125 running around the guide recess 74, wherein, in the shown closed position of the intermediate valve member 78, the mutually offset edges 125.1 and 127.1 of the steps 125 and 127 delimit the second annular sealing surface 122 radially.
  • the gradation 127 of the head 80 is formed by an undercut, which at the same time forms the split ring space 118 into which the high-pressure fuel inlet 86 opens.
  • the step 127 has a horizontal surface, which forms the second sealing surface 112.2, which in the closed position of the intermediate valve member 78 on a head 80 facing in the direction of the longitudinal axis L
  • the gradation 125 of the intermediate part 66 is formed by an annular recess 126 which has a rectangular cross-sectional profile in the circumferential direction.
  • the annular recess 126 can have a chamfered cross-sectional profile or a curved cross-sectional profile in the circumferential direction.
  • the annular recess 126 forms an inner annular space which, in the closed position of the intermediate valve member 78, is delimited by the intermediate part 66, the shaft 76 and the head 80. It can also be seen in Figure 5a that the
  • Outlet bore 102 runs in intermediate part 66.
  • the intermediate part 66 is received in a blind hole-like receiving recess 151 of an intermediate body 15, which as the actuator receiving body 20 of
  • Actuator assembly 38 is used. In contrast to the embodiments of FIGS. 3 and 4, therefore, a separate intermediate part and a separate intermediate element are not provided, but these two components are formed integrally as a one-piece intermediate part 66.
  • the outlet bore 102 has an inclined bore section which connects a blind hole-like guide recess 74 of the intermediate part 66 with the eccentrically arranged low-pressure outlet 42.
  • a blind hole-like guide recess 74 of the intermediate part 66 connects a blind hole-like guide recess 74 of the intermediate part 66 with the eccentrically arranged low-pressure outlet 42.
  • both the shaft 76 and the head 80 can be received.
  • the guide recess 74 is widened in its area facing the control piston 68 into a head space 128 in which the head 80 can be received.
  • the end face 84 of the guide sleeve 641 facing the intermediate part 66 and adjoining it serves as a stop shoulder for the head 80 in the open position of the intermediate valve member 78.
  • intermediate part 66 instead of the one-piece intermediate part 66, however, as in FIG. 3 or 4, a separate intermediate element and a separate intermediate part could be provided. It is also conceivable that the intermediate part and the guide sleeve are designed in one piece. Furthermore, it is also conceivable that the intermediate element shown in Figure 3 or 4 and Intermediate part are formed in one piece as an integral component.
  • the shaft 76 has two annular projections 761 and 762 which are spaced apart from one another in the longitudinal direction L of the shaft 76 and which encircle the shaft 76 (illustrated in FIG.
  • the annular projections 761 and 762 form two throttle passages, which are connected in series along the longitudinal axis L and run around the shaft 76, in the longitudinal direction L. This promotes the formation of eddies and a turbulent flow of the fluid flowing through the space between the shaft 76 and the guide recess 74.
  • the play can each have a value between 70 pm and 100 pm. Due to the radial play, the radial expansion of the second ring sealing surface 122 can, depending on the current radial position of the shaft 76 in the
  • Guide recess 74 vary. In order to ensure the sealing function of the intermediate valve, the maximum radial extension of the second annular sealing surface 122 is greater than the play. In the embodiment shown in Figure 5a, the clearance between the shaft 76 and the guide recess 74 serves as the passage of the second connection, which the intermediate valve member 78 releases in the open position between the fuel high pressure allowance 86 and the valve chamber 44 Intermediate valve member 78, the second annular sealing surface 122 interrupts the second connection between the high-pressure fuel inlet 86 and the valve chamber 44.
  • FIG. 5b shows a detail of a horizontal cross-sectional illustration of a further embodiment of a fuel injection valve according to the invention, this embodiment of the fuel injection valve being designed in accordance with the embodiment shown in FIG. 5a.
  • the line AA along which the cross section shown in FIG. 5b was taken, is shown in FIG. 5a.
  • FIG. 5b therefore shows an embodiment of the embodiment of a fuel injector shown in FIG. 5a.
  • FIG Gaps between the shaft 76 or the annular projection 762 and the guide recess 74 is formed.
  • the first ring projection 761 also has corresponding chamfers in the circumferential direction.
  • the chamfers 762.1-3 of the second annular projection 762 (and the chamfers of the first annular projection) provide a passage, formed by the intermediate space 119 between the chamfers and the guide recess 74, which serves as a passage for the second connection. Furthermore, due to the bevels 762.1-3 (and the bevels of the first ring projection) and the passage of the second connection provided thereby, the play between the shaft 76 and the guide recess 74 can be kept smaller than in the embodiment described for FIG. 5a which leads to better centering of the shaft.
  • the three chamfers 762.1-3 (and the chamfers of the first annular projection) are arranged at an angle of 120 ° to one another. However, other arrangements are also conceivable, in particular embodiments with one bevel per annular projection or two bevels per annular projection or a larger number of bevels are conceivable.
  • the shaft can also have at least one bevel, or two or three bevels in the circumferential direction, without ring projections, i.e. e.g. in certain embodiments of the embodiments of the fuel injector shown in FIG. 3 or 4, so that again through the
  • a passage for the second connection is formed between the chamfer or chamfers and the guide recess.
  • Figure 6 shows a section of a fourth
  • the intermediate valve member 78 has a valve chamber passage 441 connected to the valve chamber 44, which has a bore 441.1 parallel to the longitudinal axis L and a includes horizontal bore 441.2.
  • the valve chamber passage 441 connects a blind hole 92 of the intermediate valve member 78 connected to the valve chamber 44 with a split ring chamber 118 which, in the shown closed position of the intermediate valve member 78, is formed between the intermediate part 66 and the head 80 and radially from the first and second ring sealing surfaces 121, 122 is limited.
  • the bore 441.1 parallel to the longitudinal axis L opens with a first end into the split ring space 118 and with a second end into the horizontal bore
  • the horizontal bore 441.2 in turn opens with a first end into the blind bore 92. As can be seen in FIG. 5a, a second end of the horizontal bore 441.2 is closed with a plug 441.3.
  • the horizontal bore 441.2 in turn opens with a first end into the blind bore 92. As can be seen in FIG. 5a, a second end of the horizontal bore 441.2 is closed with a plug 441.3.
  • Intermediate valve member 78 or head 80 has a further valve chamber passage 441, which is shown in dashed lines in FIG. 5a.
  • the dashed horizontal bore 441.2 of the further valve chamber passage 441 is not closed separately with a plug, since the dashed horizontal bore 441.2 can be drilled together with the horizontal bore 441.2 shown on the left with solid lines.
  • the intermediate valve member 78 in the open position through the bore 441.1 releases a second connection between the Brennstof fhoch strigzulass 86 and the blind bore 92 or the valve chamber 44 so that the blind bore 92 or the valve chamber 44 can be flooded with fuel.
  • the second ring sealing surface 122 interrupts the second Connection between the high-pressure fuel inlet 86 and the valve chamber 44.
  • the high-pressure fuel inlet 86 in contrast to the embodiments shown in FIGS. 3-5, opens into an annular space 120 delimited by the intermediate part 66, the shaft 76 and the head 80 in the closed position of the intermediate valve member 78 in the
  • the closed position of the intermediate valve member 78 adjoins the second ring sealing surface 122 and is arranged radially closer to the shaft 76 than the second ring sealing surface 122.
  • the annular space 120 has an inner annular space 108 which runs around the shaft 76 and is delimited in the radial direction by the shaft 76 and intermediate part 66 and which is excluded on the shaft 76 itself.
  • the Brennstof frochrikzulass 86 opens into the inner ring space 108.
  • the ring space 120 further has a split ring space 117 adjoining the inner ring space 108, which in the closed position of the intermediate valve member 78 is formed by a circumferential gap between the intermediate part 66 and the head 80 and radially to the second Ring sealing surface 122 adjoins.
  • the inner annular space 108 is formed by a circumferential annular groove which is open to the outside in the radial direction and which has a trapezoidal cross-section, the inclined side facing away from the head 80.
  • the shaft 76 is guided in the guide recess 74 with a close sliding fit of approximately 3 mha to 10 ⁇ m.
  • the diameter of the vertical bore 441.1 of the valve chamber passage 441 is larger than the diameter of the throttle passage 90 and enables rapid flooding of the blind hole 92 and the valve chamber 44 when the intermediate valve member 78 is moved away from the closed position.
  • an intermediate part 66 is formed with a secondary passage 97, as shown in FIG. 6 with dashed lines.
  • the secondary passage 97 connects the high pressure chamber 26 with the valve chamber 44 and supports the opening process of the intermediate valve member 78 when the plunger 40 closes the low pressure outlet 42 and separates the valve chamber 44 from the low pressure fuel return 46.
  • Figure 7 shows a section of a fifth
  • the cutout represents an area of the
  • Fuel fine injection valve 10 which corresponds to the rectangle labeled III in FIG.
  • valve chamber passage 441 has a bore 441.1 inclined with respect to the longitudinal axis L. Thanks to the inclined bore 441.1, it is possible to place the first sealing bead 111 radially further away from the fourth embodiment according to FIG To arrange shaft 76 without the plug 441.3 having to be reduced in size.
  • the valve chamber passage 441 opens with the inclined bore 441.1 into the
  • split ring space 118 which is delimited by the head 80, the intermediate part 66 and the first and second ring sealing surfaces 121, 122.
  • one end of the horizontal bore 441.2 opens into the blind bore 92.
  • the inner annular space 108 of the annular space 120 is delimited both by a recess on the shaft 76 and by a recess on the intermediate part 66.
  • a split ring space 117 adjoins the inner ring space 108, which in the closed position of the intermediate valve member 78 through a circumferential gap between the intermediate part
  • An optional secondary passage 97 is shown with dashed lines, which is formed on the shaft 76 by a straight, horizontal bore and connects the high-pressure chamber 26 or the high-pressure fuel inlet 86 via the annular chamber 120 to the blind hole 92.
  • the first and the second sealing bead 111, 112 are formed higher in the longitudinal direction L, so that the
  • Split ring space 118 has a greater depth in the longitudinal direction L.
  • the intermediate part 66 is designed as a one-piece component in which, similar to FIG. 5a, the Outlet bore 102 comprising an inclined bore extends.
  • the one-piece intermediate part 66 instead of the one-piece intermediate part 66, however, as in FIG. 6, a separate intermediate element and a separate intermediate part could be provided.
  • the intermediate element and the intermediate part in FIG. 6 are designed in one piece as an integral component.
  • Valve chamber passage may be provided, which is shown in the right area of the head 80 with dashed lines.
  • the shaft 76 is guided in the guide recess 74 with a close sliding fit from approximately 3 pm to 10 pm.
  • the diameter of the inclined bore 441.1 of the valve chamber passage 441 is larger than the diameter of the throttle passage 90 and enables a rapid
  • the intermediate valve member 78 is in the open position through the bore 441.1 a second connection between the
  • the closed position of the intermediate valve 83 is for a Injection by means of the electromagnet of the
  • Actuator arrangement 38 of tappets 40 lifted from intermediate element 98 or intermediate part 66, whereby low-pressure outlet 42 is released. This has the consequence that a larger amount of fuel per unit of time from the valve chamber 44 into the low-pressure
  • Fuel return 46 flows out than through the
  • Throttle passage 90 and the possibly existing secondary passage 97 can flow into the valve chamber 44.
  • the pressure in the valve chamber 44 drops, with the result that, on the one hand, the intermediate valve member 78 is pressed against the intermediate part 66 with the resulting pressure force in order to keep the intermediate valve 83 securely closed and, on the other hand, the pressure in the control chamber 70 drops.
  • This in turn has the consequence that the effect of the double-acting control piston 68 against the force of the compression spring 62 'lifts the injection valve member 56 from the injection valve seat 18', thereby starting an injection of fuel into the combustion chamber of the internal combustion engine.
  • the plunger 40 is brought into contact with the intermediate element 98 or the intermediate part 66, as a result of which the low-pressure outlet 42 is closed.
  • the pressure in the valve chamber 44 rises by means of the fuel flowing in through the throttle passage 90 and the secondary passage 97 which may be present, which leads to a movement of the intermediate valve member 78 from
  • valve chamber passage 441 opens into the split ring chamber 118
  • the valve chamber can

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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)

Abstract

L'invention concerne une soupape d'injection de carburant (10) présentant un dispositif de commande (72) hydraulique destiné à commander le déplacement axial de l'organe de soupape d'injection (56). La tige (76) de l'organe de soupape intermédiaire (78) en forme de champignon de la soupape intermédiaire (83) est guidée dans la cavité de guidage (74) de la pièce intermédiaire (66). L'organe de soupape intermédiaire (78) libère en position d'ouverture une seconde liaison (118, 117, 96) entre une admission haute pression de carburant (86) et un espace de soupape (44) et interrompt, en position de fermeture, la seconde liaison (118, 117, 96) entre l'admission haute pression de carburant (86) et l'espace de soupape (44). La tête (80) de l'organe de soupape intermédiaire (80) repose en position de fermeture de l'organe de soupape intermédiaire (78) par une face tournée vers le pièce intermédiaire (66) sur le siège de soupape intermédiaire (82) par l'intermédiaire d'une première surface d'étanchéité (111.2) s'étendant à une première distance radiale (r1) autour de la tige (76) ou de la cavité de guidage (74), de manière à former une première surface d'étanchéité annulaire (121) fermée en soi dans la direction périphérique et par l'intermédiaire d'une seconde surface d'étanchéité (112.2) s'étendant à une seconde distance radiale (r2) autour de la tige (76) ou de la cavité de guidage (74), de manière à former une seconde surface d'étanchéité annulaire (122) fermée en soi dans la direction périphérique, la première distance radiale (r1) étant supérieure à la seconde distance radiale (r2).
EP21706532.5A 2020-02-17 2021-02-16 Soupape d'injection de carburant pour des moteurs à combustion interne Pending EP4107386A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1732020 2020-02-17
PCT/EP2021/053797 WO2021165275A1 (fr) 2020-02-17 2021-02-16 Soupape d'injection de carburant pour des moteurs à combustion interne

Publications (1)

Publication Number Publication Date
EP4107386A1 true EP4107386A1 (fr) 2022-12-28

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EP21706532.5A Pending EP4107386A1 (fr) 2020-02-17 2021-02-16 Soupape d'injection de carburant pour des moteurs à combustion interne

Country Status (6)

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US (1) US20230045640A1 (fr)
EP (1) EP4107386A1 (fr)
JP (1) JP2023513634A (fr)
KR (1) KR20220134652A (fr)
CN (1) CN115087802A (fr)
WO (1) WO2021165275A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023073140A1 (fr) 2021-10-29 2023-05-04 Ganser Crs Ag Soupape d'injection de carburant pour moteurs à combustion interne
WO2023166139A1 (fr) 2022-03-03 2023-09-07 Ganser-Hydromag Ag Soupape d'injection de carburant pour moteurs à combustion interne

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19516565C2 (de) 1995-05-05 1998-07-30 Orange Gmbh Einspritzventil einer Brennkraftmaschine
ATE488690T1 (de) 2005-07-18 2010-12-15 Ganser Hydromag Speichereinspritzsystem für brennkraftmaschine
CN101395366B (zh) 2006-03-03 2012-09-12 甘瑟-许德罗玛格股份公司 内燃机的燃料喷射阀
EP1985840B1 (fr) * 2007-04-23 2011-09-07 C.R.F. Società Consortile per Azioni Injecteur de carburant avec une soupape de contrôle et de dosage équilibrée pour un moteur à combustion interne
ATE500416T1 (de) * 2007-07-30 2011-03-15 Fiat Ricerche Druckausgeglichenes servoventil für ein brennstoffeinspritzventil einer verbrennungskraftmaschine
WO2009033304A1 (fr) 2007-09-13 2009-03-19 Ganser-Hydromag Ag Dispositif d'injection de carburant
JP5493966B2 (ja) * 2009-06-02 2014-05-14 株式会社デンソー 燃料噴射装置
JP5321496B2 (ja) * 2010-02-18 2013-10-23 株式会社デンソー 燃料噴射装置
JP5549293B2 (ja) * 2010-03-15 2014-07-16 株式会社デンソー 燃料噴射装置
JP6141328B2 (ja) 2012-02-07 2017-06-07 ガンサー−ハイドロマグ アーゲーＧａｎｓｅｒ−Ｈｙｄｒｏｍａｇ Ａｇ 燃料噴射バルブ及び燃料噴射装置
JP6441824B2 (ja) 2013-03-01 2018-12-19 ガンサー−ハイドロマグ アーゲーＧａｎｓｅｒ−Ｈｙｄｒｏｍａｇ Ａｇ 内燃機関の燃焼チャンバに燃料を噴射するための装置
CH710127A1 (de) * 2014-09-17 2016-03-31 Ganser Crs Ag Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
DE102017002366A1 (de) 2017-03-10 2018-09-13 Liebherr-Components Deggendorf Gmbh Kraftstoffeinspritzventil
WO2019078881A1 (fr) * 2017-10-20 2019-04-25 Cummins Inc. Injecteur de carburant avec élément flexible
WO2020260285A1 (fr) * 2019-06-25 2020-12-30 Ganser Hydromag Ag Soupape d'injection de carburant pour des moteurs à combustion interne

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JP2023513634A (ja) 2023-03-31
US20230045640A1 (en) 2023-02-09
KR20220134652A (ko) 2022-10-05
CN115087802A (zh) 2022-09-20
WO2021165275A1 (fr) 2021-08-26

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