EP3194757A1 - Injecteur de carburant pour moteurs à combustion interne - Google Patents

Injecteur de carburant pour moteurs à combustion interne

Info

Publication number
EP3194757A1
EP3194757A1 EP15762935.3A EP15762935A EP3194757A1 EP 3194757 A1 EP3194757 A1 EP 3194757A1 EP 15762935 A EP15762935 A EP 15762935A EP 3194757 A1 EP3194757 A1 EP 3194757A1
Authority
EP
European Patent Office
Prior art keywords
injection valve
intermediate part
housing
valve member
fuel
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
EP15762935.3A
Other languages
German (de)
English (en)
Other versions
EP3194757B1 (fr
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 Crs 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 Crs AG filed Critical Ganser Crs AG
Publication of EP3194757A1 publication Critical patent/EP3194757A1/fr
Application granted granted Critical
Publication of EP3194757B1 publication Critical patent/EP3194757B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0028—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
    • 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
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • 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
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F02M63/0042—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing combined with valve seats of the lift valve type

Definitions

  • the invention relates to a fuel injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine according to the preamble of claim 1.
  • the invention further relates to a fuel injection valve according to the preamble of claim 16.
  • Fuel injection valves of this type are known for example from WO 2007/098621 AI. Such fuel injectors allow with a minimum construction cost both the controllability of the opening movement of the injection valve member and a rapid closing of the injection valve member.
  • an intermediate valve moreover, permanently separates these two chambers from one another.
  • the intermediate valve opens quickly and gives the associated with the high-pressure chamber passage of large cross-section, causing a quick termination of the injection process.
  • the intermediate valve member of the intermediate valve is mushroom-shaped and has a, in a guide passage of an intermediate part guided in close sliding fit shaft and a head which is connected to a running around the shaft at a radial distance sealing surface
  • the sealing surface of the head and the sealing surface of the intermediate valve seat is inclined to each other so that they rest in the closed position of the intermediate valve, radially outwardly sealingly against each other and radially inward, an axially increasing throttle gap for the throttling of the high-pressure zulass in the direction of Form valve space. It is thus desirable to have an annular line seal between the valve member and the valve seat of the intermediate valve. The extremely precise for this solution production of the mushroom-shaped intermediate valve member and cooperating with this intermediate part is very delicate and very expensive.
  • embodiments of the fuel injection valve are disclosed, in which the intermediate part and an adjacent thereto on the side facing away from the guide member intermediate member are circular disc-shaped and arranged in an inner approximately completely circular cylindrical portion of the housing. They release a section of the high-pressure chamber between themselves and the housing. This section is connected on the one hand to the injection valve seat and on the other hand to the high-pressure fuel inlet.
  • the connection to the high-pressure inlet can for example take place in that the housing in the otherwise cylindrical portion in the radial direction against the outside and obliquely to the longitudinal axis extending recesses are formed. Such recesses weaken the stability of the housing, for example of the nozzle body in this area, which requires a correspondingly thicker design of the housing wall.
  • US 2011/0233309 Al discloses a fuel injection device in which a
  • the printing surface of the Pressure member is displaced or separated from the opening wall surface to open the inflow port of the opening wall surface to the pressure control chamber, when the connection between the discharge port and the return passage is interrupted by the pressure control valve.
  • the pressure surface of the pressure element or the opening wall surface of the control housing is provided with a lowered inflow portion and a lowered outflow portion, which are separated from each other.
  • a lowering dimension of the lowered inflow section is greater than the lowering dimension of the lowered outflow section.
  • the inventive fuel injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine has a housing which has at least one housing body and a nozzle body with an injection valve seat.
  • the housing is formed radially outwardly over its entire length at least approximately circular cylindrical, optionally with stepped outer diameter.
  • the housing has a high pressure space extending from a high pressure fuel inlet of the housing to the injector seat.
  • a preferably needle-shaped injection valve member is arranged to be adjustable in the direction of its longitudinal axis, which cooperates with the injection valve seat.
  • the injection valve member is lifted from the injection valve seat and brought to terminate the injection back to this plant.
  • a compression spring is present, which is supported with one end on the injection valve member and this acts with a directed towards the injection valve seat closing force.
  • the other end of the compression spring is supported stationary relative to the housing, preferably on a guide part, which is preferably designed as a guide sleeve.
  • the guide part is arranged in the housing in the high-pressure chamber, in which a control piston of the injection valve member is guided in preferably a narrow sliding fit.
  • a preferably plate-shaped intermediate part is present, which delimits a control space with respect to the high-pressure chamber and separates it from the latter together with the guide part and the control piston.
  • Control device for controlling the axial movement of the injection valve member by changing the pressure in the control chamber available.
  • the control device has a Intermediate valve, the mushroom-shaped intermediate valve member has a guided in a guide passage of the intermediate part in a preferably close sliding fit shaft and a head.
  • the head is facing the control chamber and lies with its at a radial distance around the shaft extending sealing surface, in the closed position of the intermediate valve member, on a formed on the intermediate part, annular
  • the annular sealing surface lies in a plane perpendicular to the axis of the shaft and thus of the intermediate valve member.
  • a high-pressure inlet formed on the intermediate part and permanently connected to the high-pressure inlet opens.
  • the intermediate valve separates, in the closed position of the intermediate valve member, the high-pressure admission and the annular space from the control chamber and, if the intermediate valve member is not in the closed position, there is the connection between the annulus and the high-pressure admission with the control room free.
  • the intermediate valve with the guided in preferably narrow sliding fit on the intermediate part shaft continuously separates the control chamber of a valve chamber, to a preferably formed on the intermediate valve member throttle passage of precise size, which connects the control chamber with the valve chamber permanently.
  • the fuel injector has an electrically actuated actuator assembly for connecting the valve space to and disconnecting the valve space from a low pressure fuel return.
  • the annular space further has an annular space immediately adjacent to the inner annular space
  • Spaltringraum which, in the closed position of the intermediate valve member, is formed by a gap between the intermediate part and the head of the intermediate valve member, wherein the measured in the longitudinal direction of the intermediate valve member gap width of
  • Spaltringraums is smaller than the inner annulus, preferably at least five times smaller.
  • the gap ring space allows a significant reduction of the ring sealing surface and thus the adhesion forces as well as an optimal placement of the ring sealing surface in the radial direction.
  • the annular sealing surface can be selected further outward in the radial direction or further inward.
  • the size of the active control piston surface of the injection valve member is adjustable in this simple manner, given space.
  • the split ring space, in the closed position of the intermediate valve member and in the longitudinal direction of the shaft and thus measured the intermediate valve member an at least approximately constant gap width.
  • the mouth of the high-pressure admission is completely in the region of the inner annular space.
  • This makes it possible to produce the high-pressure admission by means of a bore extending in the radial direction. Moreover, this prevents that the orifice is partially in the region of the split ring space, which the formation of the ring sealing surface at a shorter distance to the shaft, i. radially inward, allows.
  • the annular surface measured in the radial direction, a width between 0.1 mm and 1 mm.
  • the width is between 0.2 mm to 0.5 mm. This ensures a good seal on the one hand with a flat annular sealing surface and on the other hand a minimal adhesion.
  • the split-ring space In the closed position of the intermediate valve member, the split-ring space, measured in the longitudinal direction of the shaft, preferably has a gap width of 0.04 mm to 0.4 mm.
  • the gap ring space is designed to save space and on the other hand, it is sufficiently large to ensure during the transient processes the optimal loading of the surface of the head between the shaft and the sealing surface with fuel.
  • the gap width is at least approximately constant in the region of the entire gap ring space.
  • the gap ring space measured in the radial direction, has a width of at least 0.2 mm. This allows a simple production on the one hand the sealing surface on the head and the other sealing surface of the intermediate valve seat.
  • the sealing surface on the head and the other sealing surface of the intermediate valve seat Preferably, on the head, on whose side facing the intermediate part projecting annular
  • Formed sealing bead whose free end face forms the sealing surface.
  • the control chamber facing end face of the intermediate part is flat. It forms the auxiliary valve seat with the part cooperating with the sealing surface of the head.
  • the sealing flange has an at least approximately square or rectangular cross section.
  • the head preferably has, on its side facing the intermediate part, a circular annular surface running radially outward around the sealing bead and lying at least approximately in the same plane as the annular surface between the shaft and the sealing bead.
  • the sealing bead has a cross section corresponding at least approximately to a rectangular trapezoid, the right angles being radially inward. The shorter of the two mutually parallel side of the trapezoid is thus in the sealing surface of the intermediate valve member and the oblique side extends away from this radially outward obliquely in the direction of the intermediate part.
  • the head seen in cross-section, a rectilinear extension of the radially outwardly inclined side of the trapezoid up to its radial outer edge out. This also allows a simple production of the intermediate valve member.
  • a radially inner and at the intermediate part a radially outer undercut may be integrally formed on the head, on whose side facing the intermediate part, wherein these undercuts limit the ring sealing surface in the abutting part of the intermediate valve member head. It would also be the reverse construction possible, namely, that at the top of a radially outer and the intermediate part a radially inner undercut are formed, these undercuts limit the annular surface.
  • an annular, preferably at least approximately square or rectangular sealing projection is integrally formed on the intermediate part, on whose side facing the head, whose free, head facing the end face forms the valve seat.
  • the sealing surface on the head can lie in the same plane as the surface between the shaft and the annular sealing surface.
  • the valve chamber is connected via a further throttle passage permanently connected to the high-pressure chamber.
  • This further throttle passage may be formed, for example, starting from high-pressure admission in the intermediate part. If the valve space is separated from the low-pressure fuel return by means of the actuator arrangement, a higher pressure is built up more quickly by this further throttle passage in the valve space, which leads to a faster opening of the intermediate valve member and thus to a more rapid termination of the injection process.
  • a preferably plate-shaped intermediate element Preferably lies on the intermediate part, on its side facing away from the guide part, a preferably plate-shaped intermediate element.
  • an outlet passage is formed, which defines the valve space together with the intermediate part and the intermediate valve member and which on the side facing away from the intermediate part of the intermediate member by means of a plunger of the actuator assembly lockable and releasable.
  • the valve chamber can thus be formed in a simple manner with the desired volume.
  • the end face of the intermediate element facing the actuator arrangement can be planar, on which the ram comes to rest for separating the valve space from low-pressure fuel return.
  • the guide part is formed by an annular annular guide sleeve in cross section, on which the compression spring is supported.
  • the compression spring presses the guide sleeve to the preferably plate-shaped intermediate part sealingly.
  • the fuel injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine also has a housing with at least one housing body and a nozzle body with an injection valve seat.
  • the housing has a high pressure space communicating with a high pressure fuel inlet and with the injector seat.
  • a preferably needle-shaped injection valve member is adjustably arranged, which cooperates with the injection valve seat.
  • a compression spring which is supported on the one hand on the injection valve member and this applied with a directed in the direction against the injection valve seat closing force, on the other hand supported stationary with respect to the housing.
  • an intermediate part which defines a control space together with the guide part and the control piston, and an electrically actuated actuator assembly for connecting the control chamber with and separating the control chamber from a low-pressure fuel return for controlling the axial Movement of the injection valve member by changing the pressure in the control room available.
  • the intermediate part is radially outside at least approximately circular cylindrical and arranged in an inner at least approximately circular cylindrical portion of the housing. He leaves between himself and the housing a section of the high-pressure chamber free.
  • the outer diameter of the intermediate part corresponds at least approximately to the clear width of the cylindrical portion of the housing and on the intermediate part is formed a through-going recess in the axial direction, which forms the portion bounded by the intermediate part and the housing of the high-pressure chamber.
  • the housing is thus not weakened in the relevant section by recesses for the guidance of the fuel from the high-pressure fuel inlet to the injection valve seat.
  • the recess for the guidance of the fuel is located exclusively on the intermediate part, which is not exposed to particularly high pressure loads.
  • the guide element is formed by an annular annular guide sleeve in cross-section, on which the compression spring is supported and thereby presses the guide sleeve to the intermediate part sealingly, which is preferably designed plate-like.
  • the control device has an intermediate valve whose intermediate valve member, in its open position, releases high-pressure admission into the control chamber and, in the closed position, interrupts the high-pressure admittance and permanently separates the control chamber from a valve chamber, the control chamber and the valve chamber constantly communicating with one another via a throttle passage are connected, which is preferably formed on the intermediate valve member.
  • the electrically actuated Akuatoran extract is intended to connect in its open position the valve chamber with the low-pressure fuel return and separate in its closed position, the valve chamber from the low-pressure fuel return.
  • the fuel injection valve just described is designed as defined in claims 1 to 15.
  • the cross section of the recess on the intermediate part preferably has the shape of a circular sector. This recess is particularly easy to produce.
  • an at least approximately circular cylindrical also arranged in the portion of the housing, preferably plate-shaped formed intermediate element.
  • Intermediate element at least approximately corresponds to the clear width of the circular cylindrical portion of the housing and the intermediate element is also formed in the axial direction a continuous recess which is aligned with the recess on the intermediate part. It continues the section of the high-pressure chamber delimited by the intermediate part and the housing, preferably with the same cross-section. For this purpose, it preferably also has the cross section of the circular sector.
  • FIG. 2 in comparison with FIG. 1, enlarges the part of the injection valve marked there with a rectangle labeled I I;
  • FIG. 3 is enlarged in comparison to FIG. 2, the one there with I I I
  • Fuel injection valve extending in a direction perpendicular to the local section plane
  • FIG. 6 shows a perspective view of an intermediate part for the mushroom-shaped
  • the fuel injection valve 10 shown in FIG. 1 is intended for the intermittent injection of fuel into the combustion chamber of an internal combustion engine.
  • the fuel is under very high pressure, for example, up to 2 ⁇ 000 or more bar.
  • the fuel injection valve has a housing 12 with a housing body 14, a nozzle body 16, on which an injection valve seat 18 is formed, and an actuator receiving body 20, which is arranged between the housing body 14 and the nozzle body 16.
  • a union nut 22 supported on the nozzle body 16 receives the actuator receiving body 20 and is threaded onto the housing body 14.
  • the housing body 14 and the Aktuatoruf broth stresses 20, and this and the nozzle body 16 are adjacent to each other at the front, are pressed sealingly against each other by means of the union nut 22 and aligned in the direction of the housing axis L to each other.
  • the outer shape of the housing 12 is at least approximately circular cylindrical in a known manner.
  • a high-pressure fuel inlet 24 is arranged, from which a high-pressure space 26 runs in the interior of the housing 12 as far as the injection valve seat 18.
  • the high fuel pressure inlet 24 is through a valve carrier 28 formed, which carries a check valve 30 and a basket-like hole filter 32 for retaining any foreign particles in the fuel.
  • the disc-shaped valve member of the check valve 30, which cooperates with a valve seat formed on the valve seat 28, has a bypass bore.
  • the check valve 30 can flow in a known manner via a high-pressure feed line supplied fuel in the high-pressure chamber 26 virtually obstacle-free, but prevents the escape of fuel from the high-pressure chamber 26 in the high-pressure feed line except through the bypass.
  • the structure and operation of the designed as a cartridge assembly with the valve carrier 28, the check valve 30 and the hole filter 32 are disclosed in detail in the earlier application PCT / EP2014 / 000447.
  • the high-pressure fuel inlet 24 and the valve carrier 28 with check valve 30 and hole filter 32 may also be formed, as disclosed in WO 2013/117311 AI.
  • a possible embodiment of the high-pressure fuel inlet 24 and the check valve 30, as well as a rod filter instead of the hole filter 32 is known from WO 2009/033304 AI.
  • the high-pressure chamber 26 has a discrete storage chamber 34 formed on the housing body 14, which on the other hand is connected to the injection valve seat 18 via a flow channel 36 of the high-pressure chamber 26.
  • the dimensioning and operation of the discrete storage chamber 34 together with the check valve 30 with bypass is disclosed in detail in WO 2007/009279 AI; this disclosure is incorporated by reference into the present disclosure.
  • an electrically actuated actuator 38 is received in a known manner, which is determined with its in one direction spring-loaded and movable in the other direction by means of an electromagnet of the actuator assembly 38 ram 40 to close a low-pressure outlet 42, to separate a valve space 44 from a low pressure fuel return 46 (see FIGS. 2 and 3) and release the low pressure outlet 42 to interconnect the valve space 44 and the low pressure fuel return 46.
  • the designated 48 longitudinal axis of the plunger 40 and thus the actuator assembly 38 is parallel and eccentric to the longitudinal axis L. Parallel to the longitudinal axis L of the housing 12 and thus the fuel injector 10 eccentrically arranged discrete storage chamber 34 extends from an electrical connection 50 through the housing body 14 Actuator 38, a channel 52, in which the electrical control line for controlling the
  • Actuator 38 is included.
  • the conical injector seat 18 is integrally formed on the nozzle body 16, which is directly connected via the flow channel 36 to the storage chamber 34 and thus to the high-pressure fuel inlet 24.
  • injection openings 54 are formed in a hemispherical free end portion of the nozzle body 16 in a known manner through which, at the injection valve member 56 lifted from the injection valve seat 56, the under very high pressure fuel in the combustion chamber
  • the injection valve member 56 is needle-shaped and cooperates with the injection valve seat 18.
  • the injection valve member 56 is guided in a direction of the longitudinal axis L in a concentric with the longitudinal axis L, the high pressure chamber 26 associated guide bore 57 in the longitudinal direction, extending through longitudinally extending in the radial direction outwardly open recesses on the injection valve member 56, the low-loss flow of fuel to the injector seat 18 and to the injection openings 54 is made possible.
  • the interior space 58 of the nozzle body 16 leading to the high-pressure chamber 26 is twice widening toward the actuator receiving body 20, the section of the actuator body 20 facing toward the longitudinal center of the nozzle body 16 extending to its end face facing the actuator receiving body 20
  • Interior 58 defines an inner circular cylindrical portion 60 of the nozzle body 16 with a constant cross section and thus of the housing 12.
  • a support ring is integrally formed on the injection valve member 56, to which a compression spring 62 with its one end supported. At its other end, the compression spring 62 is supported on a guide sleeve 64 forming a guide sleeve 64 ⁇ frontally.
  • 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.
  • the compression spring 62 holds the guide member 64 and the guide sleeve 64 ⁇ with its end facing away from the compression spring 62 in sealing engagement with a disc-shaped intermediate part 66.
  • the guide sleeve 64 ⁇ is in close Zuleitpassung of about 3 ym to 5 ym on the injection valve member 56 integrally formed control piston 68 slidably guided in the direction of the longitudinal axis L.
  • the control piston 68, the guide sleeve 64 ⁇ and the intermediate part 66 define a control chamber 70 relative to the high-pressure chamber 26 from.
  • the intermediate part 66 is part of a control device 72, which will also be described with reference to FIG.
  • a circular-cylindrical guide passage 74 runs through the intermediate part 66 from the flat end face facing the control chamber 70 to the control chamber 70, which is also flat.
  • An integrally formed with the shaft 76 head 80 of the intermediate valve member 78 is located in the control chamber 70 and acts with its, the intermediate part 66 facing side with the guide member 64 together, the flat end face forms an annular intermediate valve seat 82.
  • the intermediate valve member 78 forms an intermediate valve together with the intermediate valve seat 82 formed on the intermediate part 66.
  • a stop shoulder 84 is formed at a distance from the intermediate part 66, which limits the opening stroke of the intermediate valve member 78.
  • a throttle passage 90 is formed on the intermediate valve member 78, on the other hand opens into a blind hole 92 recessed on the intermediate valve member 78 concentric with the longitudinal axis L.
  • the Brennstoffzulass 86 is in the embodiment according to the figures 1 to 3 by two diametrically opposite, in the radial direction passing through the intermediate part 66 and in the
  • High-pressure fuel inlet 24 is connected and has over the throttle passage 90 to a much larger flow cross-section.
  • the intermediate part 66 On the front side facing away from the control chamber 70, the intermediate part 66 has a U-shaped depression 94, which opens into the guide passage 74 on the one hand and permanently with the high-pressure chamber 26 and thus via a further throttle passage 96 recessed at the intermediate part 66 the fuel high pressure inlet 24 is fluidly connected.
  • Concentric to the longitudinal axis 48 passes through the intermediate member 98 through a step-like tapered outlet bore 102, which opens on the one hand in the flow gap 100 and the recess 94 and on the other hand forms the low-pressure outlet 42.
  • the intermediate element 98 is likewise arranged in the section 60 of the nozzle body 16 and, with its flat end facing away from the intermediate part 66, bears sealingly against the corresponding end face of the actuator receiving body 20.
  • Figure 4 shows the longitudinal section in this plane, wherein now the two positioning pins 104 are shown pulled out.
  • Other positioning pins 104 which are inserted in corresponding positioning holes in the nozzle body 16 and in the Aktuatorage Economics 20, define the position of these two bodies to each other.
  • the intermediate part 66 together with the shaft 76 and head 80 of the intermediate valve member 78 define an approximately hollow-cylindrical inner annular space 108 which runs around the shaft 76 and into which the high-pressure inlet 86 continuously discharges.
  • Embodiments of the control device 72 are the same educated.
  • the intermediate valve 83 has the task, in the closed position of the intermediate valve member 78, the high-pressure inlet 86 and the inner annulus 108 separate from the control chamber 70 and lifted at the intermediate part 66 formed between the intermediate valve seat 82 head 80, the connection between the inner annulus 108 and Hochdruckzulass 86 with the Control room 70 release.
  • the shaft 76 of the intermediate valve member 78 has a circumferential annular groove 110 which is open in the radial direction and which adjoins the head 80 directly. Seen in the direction of the longitudinal axis L, the annular groove 110 has a dimension such that the mouth of the high-pressure inlet 86 is always located completely in the region of the annular groove 110, even if the intermediate valve member 78 is in the open position and abuts against the stop shoulder 84.
  • the annular groove 110 has a trapezoidal cross-section, wherein the inclined side facing away from the head 80 and serves to deflect the loss of fuel flowing through the two holes of the high-pressure inlet 86 with open intermediate valve member 78.
  • annular sealing bead 112 is formed, the free end face 114, the sealing surface 116 of
  • Intermediate valve member 78 forms. Opposite this sealing surface 116, the head 80, on the side facing the intermediate part 66, radially inward and radially outside an undercut 118, wherein the surfaces of these undercuts 118, in the shown
  • Embodiment are in a plane which is perpendicular to the longitudinal axis L.
  • the sealing surface 116 is also in a plane which is perpendicular to the longitudinal axis L, and is the intermediate valve seat 82 forming flat end face of the intermediate part 66 also in a plane which is perpendicular to the longitudinal axis L.
  • the guide passage 74 extends in a circular cylindrical shape with the same cross section through the entire intermediate part 66.
  • a split ring space 118 which radially outside of the sealing bead 112 is limited and radially inwardly with the inner annulus 108 together forms an annular space 120 which is bounded by the intermediate valve member 78 and the intermediate part 66.
  • the width of the annular sealing surface 122, measured in the radial direction, is in the illustrated embodiment between 0.1 mm to 1.0 mm. Further, in the illustrated embodiment, the gap ring space 118 has a width measured in the radial direction of about 0.5 mm.
  • the sealing bead 112 can also be provided further outwards in the radial direction. This allows an optimal adaptation of the intermediate valve 83 to the desired injection characteristics. Is the active area of the formed as a double-acting piston intermediate valve member 78 increases, the intermediate valve 83 opens to terminate an injection process faster than if this active area is chosen smaller.
  • the adhesion between the intermediate portion 66 and the intermediate valve member 78 is minimized by minimizing the annular sealing surface 112 formed by the sealing surface 116 and the intermediate valve seat 82.
  • the further throttle passage 96 supports the movement of the intermediate valve member 78, but it can also be dispensed with depending on the specific requirements.
  • valve space 44 is formed by the blind hole 92, the flow gap 100, the recess 94 and the outlet bore 102.
  • the sealing bead 112 which is approximately rectangular in Figure 3, now trapezoidal, the right angle is radially inward lying and the oblique side is radially outward lying.
  • the oblique side has a, seen in cross-section, rectilinear extension to the radial outer edge 124 on the head 80.
  • This variant is particularly suitable when the sealing bead 112 is located far outward of the head 80 in the radial direction.
  • the width of the annular sealing surface 122, and thus the free end face 114 of the sealing bead 112 0.1 mm to 1 mm, preferably 0.2 mm - 0.5 mm.
  • the shaft 76 of the intermediate valve member 78 has a circular cylindrical shape with a constant diameter up to the head 80, to avoid large stresses of course, the transition from the shaft 76 to the head 80 is rounded.
  • a cylindrical annular recess 126 is at the intermediate part 66, of which the head 80 facing the end side except fro, which ring lift 126 extends to the opposite end of the mouth of the high-pressure inlet 86. The this side end of the annular recess 126 is rounded.
  • the annular sealing bead 112 is formed on the intermediate part 66. It has an approximately rectangular cross-sectional shape and its head 80 facing the end face 114 ⁇ forms the annular intermediate valve seat 82nd
  • the sealing bead 112 may be formed on the intermediate part 66 by means of undercuts which lie radially inwards and radially outward relative to the latter.
  • the intermediate part 66 facing side of the head 80 may be formed as a flat annular surface, of which a annular portion forms the sealing surface 116, which cooperates with the intermediate valve seat 82.
  • the gap annular space 118 of the annular space 120 which also has the inner annular space 108, is formed by the radially inner undercut.
  • an undercut 128 is formed on the head 80 with respect to the planar side, which otherwise faces the intermediate part 66, radially inward.
  • the guide passage 74 extends through the intermediate part 66 with a constant cross section.
  • the annular sealing surface 120 is thus bounded radially inwardly by the undercut 128 and radially outwardly by the further undercut 130.
  • the distance between the two undercuts 128 and 130 is between 0.1 mm to 1 mm, preferably 0.2 mm to 0.5 mm.
  • annular space 120 is formed by the split annular space 118 and the formed by the annular groove 110 on the shaft 76 inner annular space 108; see also Figure 3.
  • Nozzle body 16 is formed, the intermediate part 66 and the intermediate element 98 are arranged. These are, as can also be seen in FIGS. 6 and 7, disc-shaped and are radially outwardly annular in shape, with the exception of one seen in plan view, sector-shaped recess 132.
  • the outer diameter of the circular cylindrical part substantially corresponds to the clear width of section 60 ,
  • the intermediate part 66 and the intermediate element 98 are inserted into the section 60, wherein the recesses 132 on the intermediate part 66 and intermediate member 98 are aligned with each other and formed by the circular sector recesses 132, planar sides of the intermediate part 66 and intermediate member 98 together with the inner wall of the housing 12 in section 60 define a portion of the high-pressure chamber 26 and the flow channel 36.
  • This section allows the low-loss flow of fuel from the high-pressure fuel inlet 24 to the injection valve seat 18, wherein the relevant part of the housing 12 does not need to be weakened and its wall may have the same wall thickness all round.
  • the plunger 40 is lifted off the intermediate element 98 for injection by means of the electromagnet of the actuator arrangement 38, as a result of which the low-pressure outlet 42 is released.
  • This has the consequence that flows from the valve chamber 44 per unit time, a larger amount of fuel in the low-pressure fuel return 46, as can flow into the valve chamber 44 through the throttle passage 90 and the possibly existing further throttle passage 96.
  • the pressure in the valve chamber 44 drops, with the result that on the one hand the intermediate valve member 78 is pressed with great force to the intermediate part 66 to keep the intermediate valve 83 securely closed and on the other hand, the pressure in the control chamber 70 drops.
  • This has the consequence that the injection valve member 56 is lifted from the injection valve seat 18 by the action of the double-acting control piston 68 against the force of the compression spring 62, whereby an injection of fuel into the combustion chamber of the internal combustion engine is started.
  • the plunger 40 is brought to the intermediate element 98 for conditioning, whereby the low-pressure outlet 42 is closed.
  • the pressure in the Valve chamber 44 rises through the throttle passage 90 and any existing additional throttle passage 96 incoming fuel, which causes a movement of the intermediate valve member 78 from the intermediate valve seat 82 away. This movement is further assisted by the double piston action of the intermediate valve member 78 embodied according to the present invention, wherein the adhesion opposing this opening movement of the intermediate valve member 78 is minimized.
  • the intermediate part 66 and the intermediate element 98 are each formed as a one-piece body. It is also possible to realize the intermediate part 66 and the intermediate element 98 from a single workpiece.

Landscapes

  • 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

Injecteur de carburant (10) qui comporte une soupape intermédiaire dont l'obturateur (78) présente une forme de champignon. La tige (76) de l'obturateur (78) de soupape intermédiaire est guidée dans le passage de guidage (74) d'une partie intermédiaire (66) selon un ajustement serré de coulissement. La tige (76) et la tête (80) de l'obturateur (78) de soupape intermédiaire, ainsi que la partie intermédiaire (66) délimitent un espace annulaire (120) dans lequel débouche un orifice d'entrée (86) pour fluide sous haute pression, et qui est formé par un espace annulaire interne (108) et par un espace annulaire (118) en forme de fente. L'espace annulaire (118) en forme de fente est délimité par la tête (80) et la partie intermédiaire (66), ainsi que radialement vers l'extérieur par un bourrelet d'étanchéité (112). La force d'adhésion entre l'obturateur (78) de soupape intermédiaire et la partie intermédiaire (66), qui agit à l'encontre du mouvement d'ouverture de l'obturateur (56) d'injecteur est ainsi réduite à un minimum.
EP15762935.3A 2014-09-17 2015-08-24 Injecteur de carburant pour moteurs à combustion interne Active EP3194757B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH01407/14A CH710127A1 (de) 2014-09-17 2014-09-17 Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
PCT/EP2015/069346 WO2016041739A1 (fr) 2014-09-17 2015-08-24 Injecteur de carburant pour moteurs à combustion interne

Publications (2)

Publication Number Publication Date
EP3194757A1 true EP3194757A1 (fr) 2017-07-26
EP3194757B1 EP3194757B1 (fr) 2020-04-15

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Application Number Title Priority Date Filing Date
EP15762935.3A Active EP3194757B1 (fr) 2014-09-17 2015-08-24 Injecteur de carburant pour moteurs à combustion interne

Country Status (9)

Country Link
US (1) US10557447B2 (fr)
EP (1) EP3194757B1 (fr)
JP (1) JP6557729B2 (fr)
KR (1) KR102033646B1 (fr)
CN (1) CN107076088B (fr)
BR (1) BR112017005206A2 (fr)
CH (1) CH710127A1 (fr)
RU (1) RU2673947C2 (fr)
WO (1) WO2016041739A1 (fr)

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DE102017002366A1 (de) 2017-03-10 2018-09-13 Liebherr-Components Deggendorf Gmbh Kraftstoffeinspritzventil
US10544771B2 (en) * 2017-06-14 2020-01-28 Caterpillar Inc. Fuel injector body with counterbore insert
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DE102018107238A1 (de) * 2018-03-27 2019-10-02 Liebherr-Components Deggendorf Gmbh Injektor zum Einspritzen von Kraftstoff
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WO2020260285A1 (fr) 2019-06-25 2020-12-30 Ganser Hydromag Ag Soupape d'injection de carburant pour des moteurs à combustion interne
CN110529317A (zh) * 2019-08-23 2019-12-03 一汽解放汽车有限公司 一种燃料喷射阀阀套总成
JP2023513634A (ja) * 2020-02-17 2023-03-31 ガンサー－ハイドロマグ アーゲー 内燃機関用燃料噴射弁
DE102020113608A1 (de) * 2020-03-31 2021-09-30 Liebherr-Components Deggendorf Gmbh Kraftstoffinjektorgehäuse und Injektor mit einem solchen Gehäuse
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WO2023166139A1 (fr) 2022-03-03 2023-09-07 Ganser-Hydromag Ag Soupape d'injection de carburant pour moteurs à combustion interne

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Also Published As

Publication number Publication date
JP6557729B2 (ja) 2019-08-07
CN107076088B (zh) 2020-06-26
BR112017005206A2 (pt) 2017-12-12
JP2017532502A (ja) 2017-11-02
CH710127A1 (de) 2016-03-31
RU2673947C2 (ru) 2018-12-03
RU2017108886A3 (fr) 2018-10-17
RU2017108886A (ru) 2018-10-17
US20170298888A1 (en) 2017-10-19
WO2016041739A1 (fr) 2016-03-24
KR20170056638A (ko) 2017-05-23
US10557447B2 (en) 2020-02-11
CN107076088A (zh) 2017-08-18
KR102033646B1 (ko) 2019-10-17
EP3194757B1 (fr) 2020-04-15

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