EP3990770A1 - 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
EP3990770A1
EP3990770A1 EP20734891.3A EP20734891A EP3990770A1 EP 3990770 A1 EP3990770 A1 EP 3990770A1 EP 20734891 A EP20734891 A EP 20734891A EP 3990770 A1 EP3990770 A1 EP 3990770A1
Authority
EP
European Patent Office
Prior art keywords
valve member
chamber
injection valve
pressure
pressure 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.)
Pending
Application number
EP20734891.3A
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 EP3990770A1 publication Critical patent/EP3990770A1/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
    • 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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the present invention relates to a
  • a fuel injector of this type is known, for example, from 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 in a sliding fit in a guide recess extending through an intermediate part.
  • An annular space bounded by the intermediate part, shaft and head and having an inner annular space running around the shaft is permanently connected to a high-pressure fuel inlet formed on a housing of the fuel injection valve via a high-pressure fuel inlet running through the intermediate part.
  • Intermediate valve member separates a control chamber from a valve chamber, apart from a throttle passage formed on the intermediate valve member.
  • closed position of the intermediate valve element separates the intermediate valve of the high-pressure fuel inlet and the annular space from the control chamber and when the intermediate valve element is moved away from the closed position, the intermediate valve releases a connection between the annular space and the high-pressure fuel inlet and the control chamber.
  • the valve chamber is also continuously connected to the valve via a throttle admission formed on the intermediate part
  • valve chamber can be connected to and separated from a low-pressure fuel return.
  • 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 on the housing. Since the opening movement of the injection valve member depends essentially solely on the throttle passage, this must be designed very precisely in order to be the same with a large number of fuel injection valves
  • the throttle admission can be manufactured with a slightly larger tolerance than the throttle passage, since the low pressure
  • Fuel return separated valve chamber only a small amount of fuel flowing through the throttle admission into the valve chamber leads to the opening of the intermediate valve member. The resulting rapid pressure increase in the control room moves that Injection valve member towards the injection valve seat, whereby the injection process is ended.
  • Fuel injector with a piezoelectric actuator This controls the connection between one
  • Valve chamber and a low-pressure fuel return A control piston of an injection valve member is guided in a sliding fit in a cup-shaped guide part.
  • the guide part and the control piston delimit a control chamber which is connected to the valve chamber on the one hand by a throttle passage formed in the bottom of the guide part and on the other hand is connected to the high-pressure chamber via a throttle inlet formed in the jacket of the guide part.
  • a valve closing element controlled by means of the piezoelectric actuator is arranged in the valve chamber, which separates the valve chamber from the low-pressure fuel return when it is in contact with a first valve seat and, when it is in contact with a second valve seat formed on the guide part, shuts off the throttle passage, thereby separating the control chamber from the valve chamber and also the guide part lifts off from a valve body area and thereby connects the valve chamber with the high pressure chamber.
  • a channel is connected to a return line during an injection by means of a solenoid valve.
  • a non-return valve designed as a plate with a throttle bore is located between the channel and the control chamber. During the opening movement of the injection valve member, the control chamber can only empty into the channel via the throttle bore of the check valve plate, which means that the opening movement of the can be controlled
  • Injection valve member leads. This opens when the injection valve member closes
  • Injection valve member similar to the fuel injector according to document DE 3700687 A1, can be determined by designing a throttle bore.
  • the piezo actuator of a pilot valve has to expand, which means that a high pressure channel connected to the high pressure inlet is released on a control body.
  • the released, relatively large cross-section causes a large fuel inflow into the control chamber and thus a particularly rapid closing process of the injection valve member.
  • a transmission pin is pressed onto the end face of the control body by a pilot valve pin of the actuator.
  • Injection valve member must expand. In this state, the piezo actuator is energized. Since the injection duration is only about 5% or less of the duration between two successive injections, the piezo actuator is almost constantly under electrical voltage. Furthermore, in this known solution, the position of the throttle bore, which determines the opening movement of the injection valve member, is unfavorable because it is located far away from the control chamber.
  • valve chamber in the injection valves known from the document EP 1 991 773 B1 is also via a throttle admission, which on Guide part is formed, connected to the high pressure chamber.
  • a high-pressure fuel inlet which is connected to the high-pressure chamber and opens into a throttle gap formed by the head of the mushroom-shaped injection valve member and the guide part, also leads through the guide part.
  • the control chamber is connected to the valve chamber via a throttle passage formed on the intermediate valve member.
  • a valve back pressure chamber is provided to exert a back pressure of a first valve needle. Also is a
  • Hydraulic passage provided so that it extends through the valve back pressure chamber.
  • a valve body is provided on a second valve needle and is driven in order to connect the hydraulic pressure passage to a fuel tank or to separate it therefrom and in order to thereby drive the first valve needle.
  • the second valve needle is driven by hydraulic pressure generated by an actuator.
  • Fuel injection valve, the control chamber is bounded on the one hand by the piston of the injection valve member, on the other hand by a slide valve body and on the circumferential side by a sleeve. Both the double-acting piston and the slide valve body are guided in a tight sliding fit on the sleeve.
  • a throttle passage runs through the slide valve body, which is connected to a control passage in the Control body is permanently connected to the flow.
  • a throttle inlet leads from the high pressure chamber into the control passage. This one is on the dem
  • the slide valve body then rests against the control body in a sealing manner again.
  • the slide valve body has a further throttle passage opening into the control chamber.
  • a device for controlling an injector is known from WO 2019/016399 A1, in which the shaft of a mushroom-shaped intermediate valve member is guided in a guide part with a sliding fit.
  • the passage-free intermediate valve element separates a control chamber from a valve chamber.
  • the intermediate valve is also designed to provide a direct connection between the To create high-pressure chamber and the control chamber when the pressure level in the valve chamber is equal to or greater than a predetermined value.
  • Fuel injector the realization of multiple injections with a very short time interval can be achieved without problems. This object is achieved with a fuel injection valve according to claim 1 and claim 20.
  • the fuel injector according to the invention for the intermittent injection of fuel into the combustion chamber of an internal combustion engine has a housing which defines a longitudinal axis and which has a high-pressure fuel inlet on the one hand and an injection valve seat on the other.
  • the housing there is a high pressure chamber which runs from the high pressure fuel inlet to the injection valve seat.
  • an injection valve member cooperating with the injection valve seat is arranged in the housing so as to be movable in the direction of the longitudinal axis.
  • a compression spring is supported on the injection valve member and acts on it with a closing force directed in the direction against the injection valve seat.
  • the compression spring is preferably supported in a stationary manner relative to the housing.
  • a control chamber is delimited by the control piston, the guide part and an intermediate part and is thereby separated from the high-pressure chamber.
  • the guide part and the intermediate part can be designed as independent components. However, it is also possible that these two parts are integrally formed in one piece on a single component.
  • a hydraulic control device for controlling the axial movement of the injection valve member by changing the pressure in the control chamber has an intermediate valve, the mushroom-shaped intermediate valve member of which has a shaft guided in a guide recess of the intermediate part with a preferably close sliding fit and a head, which with its preferably in a radial distance around the shaft extending sealing surface - in the closed position of the intermediate valve member - on a preferably annular formed on the intermediate part
  • the intermediate valve seat rests in a sealing manner.
  • the intermediate part, the shaft and the head delimit an annular space in which one with the high-pressure space and thus with the high-pressure fuel inlet is preferably continuous connected fuel high pressure admission 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 admission preferably opens into the inner ring space.
  • An electrically operated actuator arrangement is intended to connect a valve chamber to a low-pressure fuel return or to separate it from it.
  • the valve chamber is preferably permanently connected to the high-pressure chamber and thus to the high-pressure inlet via a throttle inlet.
  • the intermediate valve member preferably permanently separates the control chamber from the valve chamber apart from a throttle passage formed on the intermediate valve member. This separates in the closed position of the intermediate valve member
  • the intermediate valve member When the intermediate valve member is moved away from the closed position, the intermediate valve provides a connection between the annular space and the
  • the throttle admission which preferably permanently connects the valve chamber to the high-pressure fuel inlet is formed on the intermediate valve member.
  • the throttle admission as well as the throttle passage which is to be formed extremely precisely for the initiation of an injection process is formed on a single workpiece, namely the intermediate valve member.
  • the throttle admission preferably opens into the valve chamber.
  • the throttle admission preferably runs from an outer side of the shaft facing the annular space into the valve space.
  • the throttle passage preferably opens into the control chamber at a preferably flat end face of the head facing the control piston.
  • the throttle passage preferably runs from the end face of the head facing the control piston into the valve chamber.
  • the throttle admission is preferably connected via the annular space to the high-pressure space and thus to the high-pressure fuel inlet. This enables a particularly simple training.
  • the annular space preferably has a split ring space adjoining the inner annular space. In the closed position of the intermediate valve member, this split ring space 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 ring space, measured in each case in the direction of the longitudinal axis.
  • Embodiments for the intermediate valve are also disclosed in the document WO 2016/041739 A1 and in the two documents mentioned above.
  • the inner annular space on the shaft of the intermediate valve member is preferably formed by a circumferential annular groove that is open in the radial direction to the outside and, viewed in the direction of the longitudinal axis, has such a dimension that the mouth of the high-pressure inlet is always at least almost completely in the area of the annular groove. Furthermore, the annular groove preferably adjoins the head directly. This also enables a simple design of the intermediate part.
  • the entire mouth of the is preferably located
  • the annular groove preferably has a trapezoidal one
  • the throttle admission preferably extends from the annular groove, preferably from its radially inner base and preferably in the radial direction with respect to the longitudinal axis into the valve chamber.
  • the shaft of the intermediate valve member can have a preferably groove-shaped pocket recess proceeding from the annular groove, from which the throttle admission extends into the valve chamber, preferably also with respect to the longitudinal axis in the radial direction.
  • the throttle admission has a short length and its inlet opening is connected to the annular groove in an at least approximately unthrottled manner.
  • the rotational position of the intermediate valve member does not play a role, since the throttle inlet is always connected to the high-pressure chamber via the circumferential annular groove.
  • two diametrically opposite pocket recesses are preferably formed on the shaft in order to achieve symmetrical pressure conditions.
  • the throttle passage formed on the intermediate valve member preferably opens 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, into which the throttle admission also opens.
  • the throttle passage in the intermediate valve member is preferably formed adjacent to the control chamber.
  • the throttle passage and the blind hole are preferably designed centrally to the longitudinal axis.
  • the housing preferably has a housing body with the high-pressure fuel inlet and a nozzle body on which the injection valve seat is formed.
  • the intermediate part and thus the intermediate valve are preferably arranged in the nozzle body. As seen in the longitudinal direction, this enables a short design of the housing body and also of the injection valve member.
  • the housing also has a housing body with the
  • the guide recess (open in the direction of the control chamber) is designed in the manner of a blind hole, an outlet bore being formed on the intermediate part of the guide recess, preferably from its bottom, to the low-pressure fuel return.
  • 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 disclosed for example in FIGS. 2 to 4, 8 and 9 of WO 2016/041739 A1 and in FIGS. 2, 4, 5, 7 and 8 of WO 2007/098621 A1 .
  • the mouth of the outlet bore facing the low-pressure fuel return preferably forms the
  • This embodiment also allows a simple and space-saving design of the
  • the housing has a housing body with the high-pressure fuel inlet and a nozzle body on which the injection valve seat is formed.
  • An intermediate element is arranged between the housing body and the nozzle body, the intermediate part being arranged in the intermediate element or being received by it.
  • the intermediate element 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 guide recess in the intermediate part is designed like a blind hole, with an outlet bore, preferably tapering in steps, being formed in the intermediate part from the guide recess to the low-pressure fuel return.
  • the space delimited by the guide recess and the intermediate valve member, the possibly existing blind hole in the intermediate valve member and the outlet bore belong to the valve chamber or form it.
  • the intermediate element is part of the actuator arrangement.
  • a plunger of the actuator arrangement preferably runs through a corresponding passage in the intermediate element in order to close or open the low-pressure outlet formed on the intermediate part.
  • the intermediate element preferably forms a guide element for the plunger.
  • the housing body preferably rests on one end face of the intermediate element and the nozzle body rests in a sealing manner on the opposite end face of the intermediate element.
  • the housing has a housing body with the high-pressure fuel inlet and a nozzle body on which the injection valve seat is formed.
  • An intermediate element is located between the housing body and the nozzle body, the intermediate part being arranged in a receiving recess of the intermediate element that is open in the direction of the nozzle body and connected to the high pressure chamber.
  • the intermediate valve member extends in the direction of the longitudinal axis through the intermediate part, an outlet bore being formed on the intermediate element from the guide recess to the low-pressure fuel return.
  • This outlet bore is preferably designed to taper in a step-like manner, the mouth facing the low-pressure fuel return forming the low-pressure outlet. That of the guide recess, the intermediate valve member and the outlet hole as well as the possibly existing blind hole in the
  • Intermediate valve member limited volume belongs to the valve chamber or forms it.
  • the intermediate valve seat is preferably formed on an at least approximately flat end face of the intermediate part. This also enables a simple design of the guide recess and the intermediate valve. Alternatively, however, it is also possible to use the
  • 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.
  • This embodiment is particularly simple and the compression spring fulfills a twofold task.
  • the throttle passage can be temporarily closed in order to further minimize fuel loss.
  • this can be the case as set out in the following paragraph.
  • a shut-off valve as is known, for example, from WO 2018/162747 A1 and DE 195 16 565 A1.
  • the control piston of the injection valve member preferably has a cam-shaped projection on its side facing the intermediate valve which closes the throttle passage when it rests against the intermediate valve member.
  • control chamber is permanently connected to the valve chamber via the throttle passage.
  • Another fuel injector according to the invention for the intermittent injection of fuel into the combustion chamber of an internal combustion engine likewise has a housing defining a longitudinal axis, which has a high-pressure fuel inlet on the one hand and an injection valve seat on the other. In the housing there is a high pressure chamber which runs from the high pressure fuel inlet to the injection valve seat.
  • an injection valve member which is movably guided in the direction of the longitudinal axis and which interacts with the injection valve seat.
  • a compression spring which is supported on the one hand against the injection valve member, acts on it with a closing force acting in the direction against the injection valve seat and, on the other hand, is preferably supported in a stationary manner relative to the housing, preferably on a guide part or a guide part designed as a guide sleeve.
  • a double-acting control piston of the injection valve member is guided in a tight sliding fit.
  • the fuel injector also has an intermediate part which, together with the guide part or the guide sleeve and the control piston, delimits a control chamber.
  • the intermediate part and the guide part can be designed as independent components. However, it is also possible to form the intermediate part and the guide part in one piece on a single component.
  • a hydraulic control device for controlling the axial movement of the injection valve member by changing the pressure in the control chamber is also arranged in the housing and has an intermediate valve whose mushroom-shaped intermediate valve member has a has a shaft and a head guided in a guide recess of the intermediate part in a preferably close sliding fit. With its sealing surface, which preferably runs at a radial distance around the shaft, the head rests in a sealing manner on an intermediate valve seat formed on the intermediate part in the closed position of the intermediate valve member.
  • An annular space is delimited by the intermediate part, shaft and head, in which a high-pressure fuel inlet, which is preferably permanently connected to the high-pressure fuel inlet for the sake of simplicity, opens.
  • an electrically operated actuator arrangement is arranged in the housing, which is intended to connect a valve chamber to and separate the valve chamber from a low-pressure fuel return.
  • the valve chamber is connected to the
  • a plunger of the actuator arrangement preferably runs through a corresponding passage in the intermediate element in order to close or open the low-pressure outlet formed on the intermediate part.
  • the intermediate element preferably forms a guide element for the plunger, i.e. the passage in the intermediate element preferably forms a guide for the plunger.
  • the intermediate valve member preferably permanently separates the control chamber from the valve chamber, except for one am Intermediate valve member formed throttle passage.
  • the intermediate valve In the closed position of the intermediate valve element, the intermediate valve separates the high-pressure fuel inlet and the annular space from the control chamber and when the intermediate valve element is moved away from the closed position, the intermediate valve releases a connection between the annular space and the high-pressure fuel inlet with the control chamber.
  • the throttle admission is preferably formed on the intermediate valve member.
  • the housing further has a housing body with the high-pressure fuel inlet and a nozzle body on which the injection valve seat is formed.
  • An intermediate element is arranged between the housing body and the nozzle body, the intermediate part being arranged in or received by the intermediate element.
  • the intermediate part is preferably received in a blind hole-like receiving section formed on the intermediate element.
  • the guide recess is preferably designed like a blind hole, an outlet bore being formed from the guide recess through the intermediate part to the low-pressure fuel return. This is preferably designed to taper in steps.
  • the mouth of the outlet bore facing the actuator arrangement forms a low-pressure outlet which can be closed or released by the actuator arrangement.
  • this fuel injector also has the advantages described above and can also, as described above, be embodied as specified in the relevant dependent claims.
  • FIG. 1 shows in longitudinal section a first embodiment of an injection valve according to the invention
  • FIG. 2 enlarged compared to FIG. 1, the part of the injection valve framed there by a rectangle labeled II;
  • FIG. 3 enlarged compared to FIG. 2, the one framed there with a rectangle labeled III
  • FIG. 4 shows a second embodiment of an injection valve according to the invention in longitudinal section;
  • FIG. 5, enlarged compared to FIG. 4, the part of the injection valve marked there with a rectangle labeled V;
  • FIG. 6, enlarged compared to FIG. 5, the part of the fuel injection valve with the control device framed by a rectangle labeled VI;
  • FIG. 7 shows a third embodiment of an injection valve according to the invention in longitudinal section;
  • FIG. 8 enlarged compared to FIG. 7, the part of the injection valve framed there by a rectangle labeled VIII;
  • FIG. 9, enlarged compared to FIG. 8, the part of the fuel injection valve with the control device framed by a rectangle labeled IX;
  • FIG. 10 shows the same representation as FIG. 9
  • FIG. 11 shows the same representation as FIG. 9
  • FIG. 12 shows a view of a mushroom-shaped intermediate valve member with an annular groove formed on the shaft and two pocket recesses emanating from the annular groove, the throttle inlets emanating from the pocket recesses;
  • FIG. 13 shows the intermediate valve member shown in FIG. 12 in a longitudinal section along the section line XIII-XIII in FIG. 12;
  • FIGS. 12 and 14 shows the intermediate valve member according to FIGS. 12 and
  • FIG. 15 shows the intermediate valve member according to FIGS. 12 to 14 in a perspective view of the head.
  • 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 of, for example, up to 200 bar or more.
  • the fuel injector 10 has a housing 12 defining a longitudinal axis L with a housing body 14, a nozzle body 16 on which an injector 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 takes 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 outer shape of the housing 12 is at least approximately circular cylindrical in a known manner.
  • a high-pressure fuel inlet 24 On the face of the housing body 14 facing away from the nozzle body 16 is a high-pressure fuel inlet 24 arranged, from which in the interior of 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 basket-like perforated filter 32 for holding back any foreign particles in the fuel.
  • the valve carrier 28 can also carry a check valve whose disc-shaped valve member, which interacts with a valve seat formed on the valve carrier 28, has a bypass bore.
  • the check valve allows fuel supplied via a high-pressure feed line to flow into the high-pressure chamber 26 practically without any obstacles, but prevents fuel from flowing out of the high-pressure chamber 26 into the high-pressure feed line with the exception of the bypass.
  • the structure and the mode of operation of the module designed as a cartridge with the valve carrier 28, the non-return valve that may be present and the perforated filter 32 are disclosed in detail in the document WO 2014/131497 A1.
  • the high-pressure fuel inlet 24 and the valve carrier 28 with check valve and perforated filter 32 can also be designed, as disclosed in the document WO 2013/117311 A1.
  • a possible embodiment of the high-pressure fuel inlet 24 and, if applicable, of the check valve, as well as a rod filter instead of the perforated filter 32 is known from document WO 2009/033304 A1.
  • the disclosure of the above documents applies through
  • the high-pressure chamber 26 Adjacent to the valve carrier 28, the high-pressure chamber 26 has a discrete storage chamber 34 formed on the housing body 14, which on the other hand communicates with the high-pressure chamber 26 via a flow channel 36
  • the discrete storage chamber 34 which is very long in terms of its cross-section, is arranged so as to run slightly obliquely with respect to the longitudinal axis L of the housing 12 and thus of the fuel injector 10.
  • an electrically operated actuator assembly 38 is received in a known manner, which is intended with its plunger 40, which is spring-loaded in one direction and movable in the other direction by means of an electromagnet of the actuator assembly 38, with its sealing element 41 to close a low-pressure outlet 42 in order to separate a valve chamber 44 from a low-pressure fuel return 46 (see FIGS. 2 and 3), and the
  • the longitudinal axis, denoted by 48, of the plunger 40 and thus of the actuator arrangement 38 runs parallel and eccentrically to the longitudinal axis L.
  • the plunger 40 extends through the base of the cup-shaped actuator receiving body 20, which forms a guide element 21 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 21 parallel to the longitudinal direction L.
  • the guide vanes form passages running in the longitudinal direction L through which the fuel can flow from the low-pressure outlet 42 to the low-pressure fuel return 46.
  • a channel 52 runs from an electrical connection 50 through the housing body 14 to the actuator arrangement 38, in which the electrical control line (not shown here) for controlling the actuator arrangement 38 is received.
  • the conical injection valve seat 18 is formed on the nozzle body 16 and is directly connected to the storage chamber 34 and thus the high-pressure fuel inlet 24 via the flow channel 36.
  • injection openings 54 are formed in a hemispherical free end region of the nozzle body 16 in a known manner, through which, when lifted from the injection valve seat 18 Injection valve member 56, the fuel under very high pressure into the combustion chamber of the
  • the injection valve member 56 is needle-shaped and interacts with the injection valve seat 18.
  • the injection valve member 56 is guided movably in the direction of the longitudinal axis L in a circular cylindrical guide bore 57 in the nozzle body 16, which is concentric to the longitudinal axis L and belongs to the high pressure chamber 26, with recesses on the injection valve member 56 running in the longitudinal direction, open to the outside in the radial direction and separated from one another by guide vanes the low-loss flow of fuel to the injection valve seat 18 and to the injection openings 54 is made possible.
  • upstream of this guide bore 57 is the interior space 58 of the nozzle body 16, which is part of the high pressure chamber 26 and is circular in cross section
  • Actuator receiving body 20 widening twice, then tapering to a receiving section 58 'and then widening again. Between the two extensions and between these and the taper to the receiving section 58 ', the nozzle body 16 has a hollow cylindrical first and second section 60, 60' on the inside.
  • a support ring is formed on the injection valve member 56, on which a compression spring 62 is supported with its one end. With its other end, the compression spring 62, in the area of the second section 60 ', is on one
  • the guide sleeve 64 'forming the guide part 64 is supported on the end face, the other end region facing away from the guide sleeve extending into the receiving section 58' and thus held in a centered manner.
  • 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 part 64 or the guide sleeve 64 'with its end face facing away from the compression spring 62 in sealing contact with a cylindrical intermediate part 66 which is received in the receiving section 58' and thus held centered.
  • the guide part 64 can be designed in another shape, as a sleeve, for example as a cuboid or ring body.
  • the compression spring 62 and the support ring can be fed to the injection openings 54 with as little loss as possible.
  • a double-acting control piston 68 molded onto the injection valve member 56 is guided in a tight escapement fit from approximately 3 ⁇ m to 5 ⁇ m in the direction of the longitudinal axis L.
  • the control piston 68, the guide part 64 or the guide sleeve 64 'and the intermediate part 66 delimit a control chamber 70 from the high-pressure chamber 26.
  • the intermediate part 66 is part of a hydraulic control device 72, which is also described with reference to FIG.
  • a circular cylindrical guide recess 74 runs in the intermediate part 66 from the flat end face facing the control chamber 70.
  • a shaft 76 of a mushroom-shaped intermediate valve member 78 is in this with a close sliding fit of approximately 3 ⁇ m to 10 ⁇ m guided.
  • a head 80 of the intermediate valve member 78 which is formed integrally with the shaft 76 is located in the control chamber 70 and, with its side facing the intermediate part 66, interacts with this intermediate part 66, the flat end face of which has an annular shape
  • the intermediate valve member 78 together with the intermediate valve seat 82 formed on the intermediate part 66, forms an intermediate valve 83.
  • a stop shoulder 84 is formed at a distance from the intermediate part 66, which limit the opening stroke Hl of the intermediate valve member 78.
  • the intermediate valve member 78 is in the open position and the head 80 rests against the stop shoulder 84.
  • a throttle passage 90 is formed on the intermediate valve member 78, which, on the other hand, is formed in one on the intermediate valve member 78 concentric to the
  • Longitudinal axis L recessed blind hole 92 opens.
  • the throttle passage 90 also opens into the control chamber 70 at the flat face 801 of the head 80 facing the control piston 68, so that the throttle passage 90 runs from the face 801 of the head 80 facing the control piston 68 into the valve chamber 44.
  • Throttle passage 90 on the end face 801 of the head 80 facilitates precise manufacture of the throttle passage 90.
  • the high-pressure fuel inlet 86 is in the
  • the embodiment according to FIGS. 1 to 3 is formed by a bore leading in the radial direction through the intermediate part 66 from the inclined bore belonging to the flow channel 36 to the guide passage 74.
  • the fuel high pressure admission 86 is permanent with the
  • High-pressure fuel inlet 24 and has a flow cross-section that is preferably much larger than the throttle passage 90.
  • a throttle admission 96 is provided on the intermediate valve member 78 through a bore running in the radial direction in the shaft 76 formed, which is permanently flow-connected to the high-pressure chamber 26 and thus to the high-pressure fuel inlet 24 and opens into the blind hole 92.
  • the mouth of the outlet bore 102 forms the low-pressure outlet 42.
  • the flow cross-section of this outlet bore 102 is at least the same size everywhere, but is preferably greater than the sum of the flow cross-sections of the throttle passage 90 and the throttle inlet 96.
  • the intermediate part 66 and the actuator receiving body 20 have aligned, facing, blind hole-like positioning bores 106 in which a common positioning pin 104 is inserted.
  • the intermediate valve 83 has the task, in the closed position of the intermediate valve member 78, to separate the high-pressure fuel inlet 86 and the inner annular space 108 from the control chamber 70 and, with the intermediate valve seat 82 lifted from the intermediate valve seat 82, the connection between the To release inner ring space 108 and high pressure admission 86 with the control chamber 70.
  • the shaft 76 of the intermediate valve member 78 has a circumferential annular groove 110 which is open towards the outside in the radial direction and which directly adjoins the head 80 to form the inner annular space 108.
  • the annular groove 110 Seen in the direction of the longitudinal axis L, the annular groove 110 has such a dimension that the mouth of the high pressure inlet 86 is always completely in the area of the annular groove 110, even when the intermediate valve member 78 is in the open position and is in contact with the stop shoulder 84 with the intermediate valve member 78 open, to allow the fuel flowing in through the high-pressure fuel inlet 86 to flow on to the control chamber 70 with little loss.
  • the annular groove 110 has a trapezoidal cross section, the inclined side facing away from the head 80 and serving to deflect the fuel with little loss.
  • the throttle admission 96 runs from the bottom of this annular groove 110 in the radial direction to the blind hole 92 and thus opens into the valve chamber 44.
  • a circumferential annular groove 110 ′ open to the inside in the radial direction is formed on the intermediate part 66.
  • the inner annular space 108 ' can then be formed by the annular groove 110 on the shaft 76 of the intermediate valve member 78 and the annular groove 110' on the intermediate part 66. It is also conceivable that in certain embodiments no annular groove is formed on the shaft 76 of the intermediate valve member 78 and the annular space 108 'is only formed by the annular groove 110' on the intermediate part 66.
  • annular sealing bead 112 protruding from the remaining area of this side of the head 80 is formed on the head 80, the free end face 114 of which the sealing surface 116 of the
  • Embodiment located in a plane which runs at right angles to the longitudinal axis L.
  • the sealing surface 116 also lies in a plane which runs at right angles to the longitudinal axis L
  • the flat end face of the intermediate part 66 forming the intermediate valve seat 82 also lies in a plane which runs at right angles to the longitudinal axis L.
  • sealing bead 112 can also be provided further out in the radial direction. This enables an optimal adaptation of the intermediate valve 83 to the desired ones
  • the adhesion between the intermediate part 66 and the intermediate valve member 78 is minimized in that the annular sealing surface 112, which is formed by the sealing surface 116 and the intermediate valve seat 82, is minimized.
  • the throttle admission 96 also supports a rapid opening movement of the intermediate valve member 78.
  • the opening movement of the injection valve member 56 is determined practically exclusively by the throttle passage 90. This is therefore very precisely machined with small tolerances.
  • the valve chamber 44 delimited from the control chamber 70 by the intermediate valve member 78 is formed by the blind hole 92, the outlet hole 102 and the volume between the shaft 76 and the bottom of the guide recess 76.
  • the head 88 of the intermediate valve member 78 and the end face of the intermediate part 66 cooperating with it are preferably designed according to one of the embodiments disclosed in the document WO 2016/041739 A1.
  • Alternative possible shapes of the sealing surfaces are disclosed in the documents WO 2010/088781 A1, WO 2007/098621 A1 and WO 2016/041739 A1.
  • the injection valve member 56 has on its
  • the side facing the intermediate valve 83 has a cam-like projection 56 ', which serves as a stroke limiter for the stroke H2 of the injection valve member 56 and thereby closes the throttle passage 96 by resting against the intermediate valve member 78.
  • Fuel return 46 flows out than can flow through the throttle passage 90 and the throttle inlet 96 into the valve chamber 44. This reduces the pressure in the valve chamber 44, with the result that on the one hand the intermediate valve member 78 is pressed with great force against the intermediate part 66 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 injection process results in that the injection valve member 56 is quickly moved towards the injection valve seat 18 and comes to rest against it.
  • This mode of operation also applies to the further embodiments shown in the figures and to be described below.
  • the intermediate part 66 is designed as a one-piece body. It is also possible to realize the intermediate part 66 from two workpieces that lie against one another in a sealing manner. A possible dividing line 66 ′ of the intermediate part 66 into the two workpieces is shown in FIG. 3. This separation takes place preferably at the bottom of the blind hole-like
  • the intermediate part 66 for receiving the head 80 of the intermediate valve member 78 has a head space 128 with shoulder 126, like this 7 to 11 and is described in connection with these figures.
  • the embodiment of the fuel injector 10 shown in FIGS. 4 to 6 again has a housing 12 with a housing body 14 on the one hand and a nozzle body 16 on which the injector seat 18 is formed on the other hand.
  • an intermediate element 122 rests on the front side of the housing body 14, the outer contour of which essentially corresponds to that of the housing body 14.
  • an intermediate body 124 is between the intermediate element 122 and the Nozzle body 16.
  • the intermediate element 122 and the intermediate body 124 are received in the union nut 22, which is supported on the nozzle body 16 and at the other end is wound onto the housing body 14, so that the intermediate element 122 on the one hand on the housing body 14 and on the other hand on the intermediate body 124 and this in turn bear against the nozzle body 14 at the end in a sealing manner.
  • these workpieces are also kept aligned with one another in the direction of the longitudinal axis L.
  • the intermediate part 66 for receiving the head 80 of the intermediate valve member 78 has a head space 128 with a shoulder 126, as shown in FIGS. 7 to 11 and described in connection with these figures.
  • the high-pressure fuel inlet 24 is arranged, from which inside the housing 12 - through the housing body 14, the intermediate element 122, the intermediate body 124 and the nozzle body 16 - to
  • Injection valve seat 18 of high pressure chamber 26 runs. In the embodiment shown is the
  • High-pressure fuel inlet 24 molded directly onto the housing body 14.
  • valve support 128 with a perforated filter 32.
  • the high pressure chamber 26 does not have a discrete storage chamber 34, although such a chamber can be provided in accordance with FIG. 1.
  • Flow channel 36 runs in the housing 12 from
  • the flow channel 36 runs through the intermediate element 122.
  • An actuator receiving body 20 is not provided in the present embodiment.
  • a blind hole-like recess facing the intermediate element 122 is formed on the housing body 14, in which the electrically operated actuator arrangement 38 is received.
  • the plunger 40 of the actuator arrangement 38 is in turn spring-loaded in one direction and movable in the other direction by means of the electromagnet of the actuator arrangement 38 and is intended, together with the sealing element 41, to close the low-pressure outlet 42 in order to separate the valve chamber 44 from the low-pressure fuel return 46, and to release the low-pressure outlet 42 on the intermediate part 66 in order to connect the valve chamber 44 and the low-pressure fuel return 46 to one another.
  • the longitudinal axis, denoted by 48, of the plunger 40 and thus of the actuator arrangement 38 is parallel and eccentric to the longitudinal axis L of the housing 12.
  • the intermediate element 122 forms the guide element 21 for the plunger 40, which is designed the same as above in connection with the embodiment according to FIG Figures 1 to 3 described.
  • Actuator assembly 38 runs.
  • the conical injection valve seat 18 and the injection openings 54 are formed on the nozzle body 16.
  • the needle-shaped injection valve member 56 is guided in the circular cylindrical guide bore 57 in the nozzle body 16 belonging to the high-pressure chamber 26 so as to be movable in the direction of the longitudinal axis L with its guide vanes, as described in connection with FIGS. 1 and 2.
  • the inner space 58 belonging to the high pressure chamber 26 and having a circular cross section is formed over a short length on the nozzle body 16 and over the entire length of the intermediate body 124 on the latter.
  • the interior space 58 has a first expansion in the nozzle body 16 and a second conical expansion on the intermediate body 124, with between this expansion and the
  • Intermediate element 122 of intermediate body 124 is designed in the shape of a hollow cylinder on the inside and forms section 60.
  • the compression spring 62 is supported in a known manner on the injection valve member 56, which with its other end on the Guide part 64 forming guide sleeve 64 s is supported on the end face.
  • 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 part 64 or the guide sleeve 64 'with its end face facing away from the compression spring 62 in sealing contact with the intermediate part 66, which is received and centered in the receiving section 58' formed on the intermediate element 122.
  • Receiving section 58 ′ is formed by a blind hole-like recess open in the direction of the intermediate body 124 and thus the nozzle body 16.
  • the intermediate part 66 is held in sealing contact with the bottom of the receiving section 58 'via the compression spring 62.
  • the guide recess 74 is designed in the manner of a blind hole, an outlet bore 102 tapering in a step-like manner being formed in the intermediate part 66 from the guide recess 74 to the low-pressure outlet 42.
  • the flow channel 36 opens radially outside the intermediate part 66 into the receiving section 58 ', whereby the fuel supplied through the flow channel 36 between the intermediate element 122 and the intermediate part 66 and between the guide sleeve 64' and the intermediate body 124 into the interior 58 and to the injection valve seat 18 can flow with little loss.
  • the intermediate part 66 can be positioned in the intermediate element 122 by means of positioning pins 104, as shown in FIG. 3.
  • the control piston 68 of the injection valve member 56 is guided displaceably in the direction of the longitudinal axis L.
  • the control piston 68, the guide part 64 or the guide sleeve 64 ′′ and the intermediate part 66 delimit the control chamber 70.
  • the intermediate part 66 is part of the hydraulic control device 72 and, together with the intermediate valve member 78, is embodied in the same way as described above, in particular in connection with FIG. 3.
  • a throttle inlet 96 is formed on the intermediate valve member 78 through a bore running in the radial direction in the shaft 76, which is flow-connected to the high-pressure chamber 26 and thus to the high-pressure fuel inlet 24 and opens into the blind hole 92.
  • the housing 12 is essentially designed in the same way as shown and described in connection with FIGS. 4 to 6.
  • the actuator assembly 38 is designed in the same way as described above, but the recess has in
  • the flow channel 36 runs through the guide part 64 and opens into the interior 58 between the intermediate body 124 and the guide part 64 or the guide sleeve 64 ′′.
  • the circular cylindrical intermediate part 66 which corresponds with its outer contour to the outer contour of the housing body 14, is part of the hydraulic control device 72, which is shown enlarged in Figures 8 and 9.
  • the guide recess 74 is again designed like a blind hole and is open in the direction of the control chamber 70. It is delimited by a shoulder 126 formed on the intermediate part 66 and forming the intermediate valve seat 82. From this shoulder 126 to the intermediate body 124 and thus the end face facing the nozzle body 16, a head space 128 is cut out on the intermediate part 66, in which the head 80 of the mushroom-shaped intermediate valve member 78 is located. This is designed in the same way as in connection with the embodiments disclosed above.
  • the stop shoulder 84 (Fig. 3) corresponding stroke limitation for the intermediate valve member 78 is in the present embodiment by the Intermediate part 66 facing end face of the guide part 64 or the guide sleeve 64 ′′ is formed.
  • the fuel inlet 86 in the intermediate part 66 is formed by a blind hole 130 that runs parallel to the longitudinal axis L and extends from the end face facing the intermediate body 124 and thus the nozzle body 16, is connected to the high pressure chamber 26 and a radial hole 132 that crosses this blind hole 130 and which, as in the embodiments according to FIGS. 1 to 6, opens into the inner annular space 108.
  • the radial bore 132 is closed radially on the outside by means of a sealing screw 134.
  • FIG. 10 corresponds to that according to FIGS. 7 to 9, only the fuel inlet 86 being designed differently.
  • the blind hole 130 now no longer runs parallel to the longitudinal axis L, but rather its longitudinal direction includes an acute angle with the longitudinal axis L.
  • Another blind hole 136, into which the blind hole 130 opens, runs from the guide recess 74.
  • the further blind hole 136 in turn opens into the inner annular space 108.
  • the fuel inlet 86 in an arc shape with a curvature instead of by means of straight bores; this for example by producing the intermediate part 66 by means of a 3D printing process. In this way, flow losses can be kept small and, in the embodiment according to FIGS. 7 to 10, the Sealing screw is omitted.
  • intermediate body 124 in one piece integrally.
  • the embodiment according to FIG. 11 has, in the same way as that according to FIGS. 4 to 6, an intermediate element 122 which is arranged between the housing body 14 and guide element 21 on the one hand and the intermediate body 124 on the other.
  • the intermediate part 66 is sleeve-shaped, the
  • the guide part 64 designed as a guide sleeve 64 is held in contact with the intermediate part 66 in a sealing manner by means of the compression spring 62, the guide sleeve 64 'in turn forms the stroke limitation for the intermediate valve member 78.
  • the intermediate valve 83 and thus the intermediate part 66 and the intermediate valve member 78 are in one of the
  • a receiving section 58 'forming the receiving recess 122' of the intermediate element 122 was added.
  • the receiving recess 122 has an extension running around the intermediate part 66 into which the
  • Flow channel 36 opens out, the intermediate part 66 having guide vanes radially on the outside in order to be held centered in the intermediate element 122 and to permit a low-loss flow of fuel in the direction of the injection valve seat 18.
  • valve chamber 44 is through the blind hole 92 in the shaft 76 of the intermediate valve member 78, the likewise stepped outlet bore 102 in the intermediate element 122 and the volume between the
  • the mouth of the outlet bore 102 forms the low-pressure outlet 42, which is formed on the intermediate element 122 in the present example. He is by means of the
  • Sealing element 41 of the plunger 40 of the actuator assembly 38 closable in order to separate the valve chamber 44 from the low-pressure fuel return 46, or releasable in order to connect the valve chamber 44 with the low-pressure fuel return. To connect fuel return 46.
  • the intermediate valve 83 is designed the same as in all other embodiments.
  • the intermediate valve member 78 is mushroom-shaped, with the shaft 76 on which the inner annular space 108 is formed through the annular groove 110 is formed, and the head 80, on which the flow grooves 88 are formed.
  • the throttle passage 96 no longer extends from the bottom of the annular groove 110, but rather two diametrically opposed pocket recesses 138 on the shaft 76, starting from the annular groove 110.

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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

La soupape d'injection de carburant (10) selon l'invention présente un dispositif de commande hydraulique (72) pour commander le déplacement axial de l'organe de soupape d'injection (56). La tige (76) de l'organe de soupape intermédiaire (78), réalisé en forme de champignon, de la soupape intermédiaire (83), est guidée avec ajustement par glissement dans l'évidement de guidage (74) de la pièce intermédiaire (66). L'organe de soupape intermédiaire (78) sépare l'espace de commande (70) de l'espace de soupape (44) jusqu'au passage d'étranglement (90) réalisé au niveau de l'organe de soupape intermédiaire. L'admission d'étranglement (96) est en outre réalisée au niveau de l'organe de soupape intermédiaire (78) et est reliée à l'espace haute pression (26).
EP20734891.3A 2019-06-25 2020-06-23 Soupape d'injection de carburant pour des moteurs à combustion interne Pending EP3990770A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH8512019 2019-06-25
PCT/EP2020/067509 WO2020260285A1 (fr) 2019-06-25 2020-06-23 Soupape d'injection de carburant pour des moteurs à combustion interne

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Publication Number Publication Date
EP3990770A1 true EP3990770A1 (fr) 2022-05-04

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WO (1) WO2020260285A1 (fr)

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Publication number Priority date Publication date Assignee Title
KR20220134652A (ko) * 2020-02-17 2022-10-05 간제르-히드로막 아게 내연기관용 연료 분사 밸브
WO2023073140A1 (fr) 2021-10-29 2023-05-04 Ganser Crs Ag Soupape d'injection de carburant pour moteurs à combustion interne
CN114109683B (zh) * 2021-11-30 2023-02-10 中船动力研究院有限公司 一种低碳燃料喷射装置及发动机
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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Publication number Priority date Publication date Assignee Title
CH668621A5 (de) 1986-01-22 1989-01-13 Dereco Dieselmotoren Forschung Kraftstoffeinspritzanlage fuer eine brennkraftmaschine.
DE19516565C2 (de) 1995-05-05 1998-07-30 Orange Gmbh Einspritzventil einer Brennkraftmaschine
DE10100390A1 (de) 2001-01-05 2002-07-25 Bosch Gmbh Robert Einspritzventil
EP1273791A3 (fr) 2001-07-03 2003-03-12 CRT Common Rail Technologies AG Soupape d'injection de combustible pour moteurs à combustion interne
EP1656498B1 (fr) 2003-08-22 2008-11-26 Ganser-Hydromag Ag Soupape d'injection de carburant commandee par une soupape pilote
JP2006257874A (ja) 2004-04-30 2006-09-28 Denso Corp インジェクタ
US7603984B2 (en) 2005-07-18 2009-10-20 Ganser-Hydromag Ag Accumulator injection system for an internal combustion engine
RU2438035C2 (ru) 2006-03-03 2011-12-27 Ганзер-Хюдромаг Аг Инжекторный клапан для топлива для двигателя внутреннего сгорания (варианты)
EP2188516B1 (fr) 2007-09-13 2011-10-26 Ganser-Hydromag AG Dispositif d'injection de carburant
CH700396A1 (de) 2009-02-09 2010-08-13 Ganser Hydromag Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
CN104093968B (zh) 2012-02-07 2016-10-12 甘瑟-许德罗玛格股份公司 燃料喷射阀和用于喷射燃料的装置
DE102012223166A1 (de) * 2012-12-14 2014-06-18 Robert Bosch Gmbh Kraftstoffinjektor
WO2014131497A1 (fr) 2013-03-01 2014-09-04 Ganser-Hydromag Ag Dispositif permettant d'injecter un carburant dans la chambre de combustion d'un moteur à combustion interne
GB201414669D0 (en) * 2014-08-19 2014-10-01 Delphi International Operations Luxembourg S.�.R.L. Control valve arrangement
CH710127A1 (de) 2014-09-17 2016-03-31 Ganser Crs Ag Brennstoffeinspritzventil für Verbrennungskraftmaschinen.
FR3027350B1 (fr) * 2014-10-20 2019-10-04 Delphi Technologies Ip Limited Injecteur de carburant
DE102017002366A1 (de) 2017-03-10 2018-09-13 Liebherr-Components Deggendorf Gmbh Kraftstoffeinspritzventil
DE102017116367A1 (de) 2017-07-20 2019-01-24 Liebherr-Components Deggendorf Gmbh Vorrichtung zum Steuern eines Injektors

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