WO2012130452A1 - Soupape d'injection - Google Patents

Soupape d'injection Download PDF

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Publication number
WO2012130452A1
WO2012130452A1 PCT/EP2012/001379 EP2012001379W WO2012130452A1 WO 2012130452 A1 WO2012130452 A1 WO 2012130452A1 EP 2012001379 W EP2012001379 W EP 2012001379W WO 2012130452 A1 WO2012130452 A1 WO 2012130452A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve member
coupling element
valve
injection
annular gap
Prior art date
Application number
PCT/EP2012/001379
Other languages
German (de)
English (en)
Inventor
Raphael FÜCHSLIN
Original Assignee
Fuechslin Raphael
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 Fuechslin Raphael filed Critical Fuechslin Raphael
Publication of WO2012130452A1 publication Critical patent/WO2012130452A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion

Definitions

  • the present invention relates to an injection valve for fuel injection in a combustion chamber of an internal combustion engine, for example a diesel engine.
  • Such injection valves are used in particular for the intermittent injection of a fuel present in liquid form, for example gasoline or diesel fuel, into a combustion chamber of an internal combustion engine.
  • the fuel is provided by a high-pressure pump at a high pressure and injected into the combustion chamber through the injection valve arranged on the combustion chamber, for example a cylinder of a diesel or gasoline engine.
  • the injection process is usually controlled by an electronic engine control.
  • Such an injection valve comprises a housing, which is usually elongated for reasons of the available installation space and in which an elongated valve member is displaceably arranged. By displacing the valve member, an injection port disposed in a valve seat member can be closed or opened. On the housing, a high-pressure fuel port is provided, which communicates via a bore in communication with the injection port. Furthermore, the injection valve comprises an actuator, via a control device, in particular
  • CONFIRMATION COPY the electronic engine control can be controlled, and a typically hydraulic control device, with which the activity of the actuator can be converted into a movement of the valve member.
  • actuators and control devices are known per se and described, for example, in EP 0 976 924 A2 or EP 0 228 578 A1.
  • An injection valve of the type mentioned is disclosed for example in WO 02/086309 AI.
  • the length of the valve member of such an injector is usually much larger than the diameter of the valve member.
  • the large ratio of length to diameter can lead to many disadvantages.
  • long, thin components are more difficult to produce than short, thick components, which leads to higher production costs.
  • an injection valve member is usually subjected to a heat treatment or curing during its processing, which can lead to a disadvantageous for the use delay of the valve member.
  • the needle and the piston rod are rigidly connected by a substantially triangular shaped connecting member in the axial direction, while relative sliding in the radial direction within a slot of the connecting member is possible to absorb misalignment of both axes. An angular error between the needle and the piston rod is not compensated.
  • DE 44 27 378 A1 proposes a common rail injector in which, despite an axial offset between a valve piece and a nozzle needle, a centric introduction of the closing force into the nozzle needle is achieved by an elongated valve piston being moved into a short valve piston and a pressure rod is split, which is tapered at its end facing the valve piston.
  • a fuel injector is described in which a connecting piece is firmly connected both with a valve piston and with a nozzle needle.
  • an injection valve for a fuel injection system of an internal combustion engine wherein in a valve housing, a multi-part valve body with a nozzle needle and a coaxially arranged on this lying overlying valve body part is slidably disposed.
  • the fuel passes from an inlet line via a laterally arranged in the valve housing bore in a nozzle needle adjacent pressure chamber.
  • a fuel-filled damping chamber is provided between the nozzle needle and the overlying valve body part.
  • An operative connection between the nozzle needle and the overlying valve body part can be imparted by a ring element into which the nozzle needle protrudes approximately free of play.
  • An articulated function is exercised by a ring element made of plastic, which is inserted over the two ends of the nozzle needle and the valve body part and together with these forms a tight fit.
  • the damping chamber can be connected via a throttle bore with the pressure chamber.
  • a plastic ring member is not satisfactory in durability due to the chemical, thermal and mechanical conditions prevailing in the injector.
  • a deformation of the ring element is necessary, whereby lateral forces are exerted on the nozzle needle and the overlying valve body part or the respective guides, which lead to friction and wear, which ultimately affects the function of the injection valve.
  • An injection valve according to the invention for fuel injection into a combustion chamber of an internal combustion engine for example an Otto or a diesel engine, comprises a valve housing and a valve member, which is arranged displaceably in the valve housing for opening and closing at least one injection opening in a longitudinal direction.
  • the injection opening can be arranged for injecting the fuel into the combustion chamber and is accompanied by For example, formed by a valve housing associated valve seat member.
  • the valve member is elongated in particular in the longitudinal direction and comprises a plurality of valve member elements arranged one after the other in the longitudinal direction, in particular likewise elongate.
  • at least one valve member element can be designed to open and close the injection opening;
  • at least one valve member element may be provided on which a drive of the valve member engages.
  • the valve member according to the invention further comprises a coupling element for coupling a first valve member element with a second valve member element.
  • the first valve member element can be arranged on the nozzle side of the second or vice versa.
  • the coupling element may be sleeve-shaped and surrounds an end region of the first valve member element such that an annular gap is formed between an outer surface of the end region of the first valve element element and a first inner surface of the coupling element.
  • the coupling element may comprise further elements for connection to the first and the second valve member element.
  • the end region of the first valve member element and a region of the coupling element enclosing the latter can be approximately configured as full or hollow cylinders with a circular cross section, so that the outer surface of the end region of the first valve element element and the first inner surface of the coupling element are approximately circular cylindrical.
  • the annular gap can have a uniform or an uneven width along the circumference of the first valve member element.
  • the injection valve is designed such that the valve member, in particular the coupling element, can be at least partially surrounded by a pressurized fluid. In particular, the valve member is surrounded during operation of the injection valve in the region of the opening of the annular gap of the pressurized fluid.
  • the annular gap is thus dimensioned such that the kinematic coupling of the first and a second valve member element adjacent in the longitudinal direction is maintained at least for this period of time.
  • the annular gap can for this purpose have a width in the micrometer range, for example of a maximum of about 5 ⁇ .
  • the first and the second valve member element are at least as far surrounded by the pressure fluid, so that by the negative pressure in relation to the surrounding pressure of the pressure fluid and possibly taking into account other forces, such as a spring, a corresponding movement of the first and the second valve member is triggered.
  • an operative connection for transmitting the tensile force or the longitudinal movement of the valve member is created, which allows the compensation of the angular error without exerting substantial lateral forces. Due to the hydraulic coupling created in this way, a further connection between the first and the second valve member element is not necessary, in particular, no positive or frictional connection is necessary.
  • an annular gap is present between an outer surface of the end region of the first valve member element and a first inner surface of the coupling element, a compensation of an angular error between a longitudinal axis of the first valve member element and a longitudinal axis of the coupling element and thus in particular a longitudinal axis of the second valve member element is made possible.
  • the clearance ensured by the annular gap makes it possible to tilt the first valve element element relative to the coupling element, without having to apply a force for deforming the coupling element from the guides of the valve element. Since no deflection of the coupling element or the first valve member element necessary to compensate for the angular error are, they can be made of resistant materials of high rigidity, such as steel, in particular hardened steel. As a result, an operative connection between the first and the second valve member element is provided, which allows actuation of the valve member for opening and closing the injection port, however, for example, deformations and guiding errors of the valve member elements can be tolerated.
  • the length of the annular gap measured in the longitudinal direction and the width of the annular gap are dimensioned such that an angular error of at least approximately 2 '(2 arc minutes) can be compensated.
  • This corresponds to a deviation of, for example, about 0.01 mm to a length of 15 mm.
  • the pressure fluid can escape through the annular gap.
  • the pressure force acts for longer periods than the tensile force, it may be provided that the pressure fluid escapes so much from the interior of the coupling element, that the end portion of the first valve member element in contact with an end portion of the second valve member element or a correspondingly formed stop of the coupling element passes. As a result, a secure transmission of the pressure force is possible.
  • the valve member on all sides or practically on all sides of the pressurized fluid umber; at least during the injection process, the valve member is surrounded on all sides or practically on all sides by the pressurized fluid.
  • the valve member when the valve member is surrounded on all sides or practically on all sides by the pressurized fluid, occurs in the execution of an injection process, the situation that within the valve member a Traction acts.
  • the annular gap is dimensioned such that upon application of a tensile force to the valve member in the interior of the coupling element, a negative pressure is formed; the negative pressure is used to transmit the tensile force between the first and second valve member element.
  • valve member can be surrounded on all sides or practically on all sides by the pressure fluid, a particularly simple design is possible; In particular, no pressure-tight sealing of the valve member is required.
  • the first and second valve member members are hydraulic only in the longitudinal direction when a tensile force is applied, i. by the resulting negative pressure, coupled together.
  • a simple manufacture and assembly and an improved compensation of the angular errors are made possible.
  • the annular gap is dimensioned such that upon application of the tensile force to the valve member such a small amount of the pressurized fluid penetrates into the interior of the coupling element, that there is no significant damping of the movement of the valve member.
  • the movement of a nozzle-remote of the first or the second valve member element is thus transferred to a nozzle closer of the two interconnected valve member elements, without substantial relative movement of the two valve member element takes place underneath each other.
  • Such a relative movement would reduce the control of the injection process, in particular the control of the movement of a nozzle needle.
  • the coupling element is preferably designed such that it is deformed under the effect of the negative pressure, so that the width of the annular gap to maintain the negative pressure is reduced.
  • the coupling element can, at least in a partial region which surrounds the end region of the first valve element. limb member encloses, be formed thin-walled. Due to the prevailing in the interior of the coupling element negative pressure compared to the external pressure of the pressure fluid, the coupling element is compressed in the micrometer range, so that the width of the annular gap is reduced and the inflowing amount of the pressurized fluid is reduced. Due to the deformation, the coupling element can even enclose the end region of the first valve member element in a sealing manner under the effect of the negative pressure.
  • the pressurized fluid is pressurized liquid fuel or fuel that can be supplied via a high-pressure connection of the valve housing.
  • the fuel to be injected is used as the pressurized fluid for mediating the coupling between the first and the second valve member element, a particularly simple and safe execution of the injection process is achieved.
  • the injection valve according to the invention is designed as an injection valve of an injection system with a common high-pressure supply.
  • an injection system is characterized by a high-pressure pump which provides the fuel to be injected at a high pressure, for example 100 bar to over 2500 bar, of a plurality of injection valves via a common high-pressure line system.
  • a high-pressure pump which provides the fuel to be injected at a high pressure, for example 100 bar to over 2500 bar, of a plurality of injection valves via a common high-pressure line system.
  • Such injection systems are therefore also referred to as common rail systems.
  • the high-pressure supply of the injection valves in such an injection system is known per se.
  • the injectors effect an intermittent injection of the high pressure fuel into the combustion chamber of an internal combustion engine, the injections typically being controlled by an electronic engine controller.
  • valve member is guided in a central bore of the valve housing and the fuel from the high pressure port through the central bore can be fed to the Einspritzöffhung. Because of that, the fuel In the same space of the valve housing, in which the valve member is arranged, is guided to the injection port, can be ensured in a simple manner that the valve member, in particular the coupling element, is surrounded by pressurized fuel and thereby even when applying a tensile force an operative connection between consists of the first and the second valve member element due to the resulting in the interior of the coupling element due to the tensile force negative pressure.
  • the fact that the valve member and the fuel are guided in a central bore, a simple and inexpensive production is possible.
  • the first inner surface of the coupling element and / or the outer surface of the end region of the first valve member element seen in longitudinal section is formed crowned. Seen spatially, the first inner surface of the coupling element is thus spindle-shaped or the outer surface of the end region of the first valve member element is barrel-shaped.
  • the deviations from a cylindrical, in particular circular cylindrical shape can be dimensioned such that a compensation of angular errors to the desired extent, however, the width of the annular gap, in particular in a central region is sufficiently low to the inflow of pressurized fluid into the interior of the coupling element so far to limit that maintaining a sufficient negative pressure for a time sufficient for actuation of the valve member is ensured or that a sufficiently small amount of fluid penetrates into the interior, so that no significant damping occurs.
  • a compensation of larger angle errors while maintaining the operative connection between the first and a second valve member element can be made possible.
  • the first inner surface of the coupling element and / or the outer surface of the end region of the first valve member member may be formed frusto-conical.
  • a crown may be superimposed in the manner described. This can also equal larger angle error while maintaining the operative connection are made possible.
  • At least one spacer is arranged or can be arranged.
  • the at least one spacer is formed in particular for transmitting a compressive force between the first and the second valve member element.
  • the coupling element is fixedly connected to a second valve member element, for example shrunk or connected by soldering, or formed integrally with the second valve element element, i. integrated with this into a component.
  • the coupling element may enclose an end region of a second valve element element such that an annular gap for compensating an angular error between a longitudinal axis of the second valve element element and a longitudinal axis of the coupling element is formed between an outer surface of the end region of the second valve element element and a second inner surface of the coupling element.
  • the coupling element is connected according to this embodiment, in particular in a corresponding manner with the second valve member element as with the first valve member element.
  • the first and the second valve member element are coupled to each other such that both in the connection of the first and in the connection of the second valve member element with the coupling element, a compensation of an angle error is made possible. This can be compensated for a total of a larger angle error, it can but also a radial offset of the axes of the first and second valve member element are compensated.
  • the valve member comprises more than two valve member elements, which are operatively connected by a plurality of coupling elements.
  • the valve member may comprise a valve member formed as a nozzle needle, which is designed to open and close the injection opening.
  • the valve member has a control part, which can be driven via a control device which can be actuated by means of an actuator. The control part is thus displaced due to the action of the actuator and drives the valve member to its movement in the longitudinal direction.
  • suitable actuators or control devices are known per se.
  • the actuator may have a control unit, such as an electronic engine control, electromagnetically operable valve that controls the flow of pressurized fluid from a control room.
  • the control part When the pressurized fluid flows out of the control chamber, the control part follows, so that the valve member releases the injection opening; On the other hand, when the pressurized fluid fills the control space, the valve member is moved in the reverse direction by a spring for closing the injection port.
  • the valve member may comprise only two valve member elements, namely the valve member element designed as a nozzle needle and the control part, wherein these two valve member elements are in operative connection via a coupling element described above; However, the valve member may also have more than two Ventilgliedele- elements, more than one coupling element of the type described may be present.
  • the coupling element or the coupling elements can or can NEN also integrated into a valve member element, ie be integrally formed with this.
  • FIG. 1 shows a longitudinal section of an embodiment of an injection valve according to the invention.
  • Fig. 2 is an enlarged detail of Fig. 1;
  • FIG. 3 shows an enlarged view in longitudinal section of the geometric relationships on a coupling element according to the embodiment shown in Figures 1 and 2 in a misalignment ..;
  • Fig. 4 is a cross-sectional view taken along the plane D-D shown in Fig. 3;
  • FIG. 5 shows a coupling element according to a further embodiment of the invention in longitudinal section
  • FIG. 6 shows a coupling element according to a further embodiment of the invention, also in longitudinal section; 7 shows a coupling element according to a further embodiment of the invention in longitudinal section; Fig. 8 is a coupling element according to a further embodiment of the invention in longitudinal section.
  • an injection valve comprises a valve housing 18, a valve housing 18 associated with this and a holding member 16 fixedly connected valve seat member 13 and an actuator 1.
  • the valve seat member 13 has an injection port 14; There may also be several injection openings.
  • the injection opening 14 can be closed by a seat part 12a of a valve member El arranged inside the valve housing 18.
  • the valve member El is formed thin and elongated and at least partially disposed in a central bore 17 of the valve housing 18, wherein it is slidably guided in its longitudinal direction; For this purpose, suitable guides may be present (not shown).
  • the valve member El comprises, in addition to the seat part 12a, a spacer part 11a and a control part 8, which are coupled to one another via coupling elements 9a, 9b.
  • the valve housing 18 has a high-pressure fuel connection 10 through which liquid fuel under high pressure is supplied.
  • the high-pressure fuel connection 10 is connected to the central bore 17, through which the fuel reaches the injection opening 14.
  • the valve member El is thus largely surrounded by the fuel under high pressure.
  • actuator 1 is arranged, which may for example comprise an electromagnet.
  • the actuator 1 together with a sealing seat 2, an outlet throttle 3, a control chamber 4, an inlet throttle 5, a spring 6 and an associated spring plate 7, a control device Sl.
  • the end face 21 of the control part 8 limits the effective area of the control chamber 4.
  • the actuator 1 can be caused via an unillustrated control unit to release the sealing seat 2. It can now escape under pressure fuel through the outlet throttle 3 from the control chamber 4, which can flow virtually pressure-free via a symbolically illustrated return line back into a tank 22.
  • control chamber 4 Since the control chamber 4 is connected to the fuel high-pressure connection 10 only via an inlet throttle 5, the pressure in the control chamber 4 drops until the injection valve member E 1, comprising the control part 8, spacer part 11a, seat part 12a and the two coupling elements 9a, 9b, moved out of his seat 15. This fuel is injected into a combustion chamber, not shown in Fig. 1. If the injection is to be terminated, the actuator 1 is caused by the control unit to close the sealing seat 2. Thus, no fuel can escape through the outlet throttle 3 more and the pressure in the control chamber 4 increases. With the help of the spring 6, which is supported with its spring plate 7 on the injection valve member El, this is pressed into its seat 15 and the injection is stopped.
  • the operation of the actuator 1 or the control device Sl is described here only by way of example. There are also known other embodiments of the actuator 1 and the control device Sl for controlling the movement of the valve member El, which can also be used in the context of the present invention.
  • Fig. 2 shows a coupling element 9b, whereby the spacer 1 la and the seat part 12a are operatively connected.
  • the coupling element 9b is at least as firmly connected to the spacer 1 la, that the function of mediating the movement of the spacer I Ia is guaranteed to the seat part 12a.
  • the coupling element 9b could, for example, be shrunk, pressed or soldered onto the spacer part 11a, although other types of connection are also conceivable.
  • the coupling element 9b On the side of the Seat part 12a, the coupling element 9b has an inner surface which is formed as a substantially circular cylindrical annular surface 19a and which encloses with a clearance fit the seat part 12a at its end portion having a substantially circular cylindrical outer surface 24a.
  • annular gap 26 is present between the outer surface 24a and the annular surface 19a thus an annular gap 26 is present.
  • the clearance fit is sufficiently tight or the annular gap 26 sufficiently narrow that at a stroke in the opposite direction to the seat 15 (see Fig. 1) in the interior 20 of the coupling element 9a at least one such negative pressure sets that with the resulting force and if necessary, with a frictional force acting between annular surface 19a and outer surface 24a, the seat part 12a is pulled out of its seat 15.
  • the annular gap 26 may initially be slightly wider than is necessary for a sufficiently long maintenance of the negative pressure.
  • the pressure drop occurring at the beginning of the stroke movement in the interior 20 may be sufficient to deform the coupling element 9b such that the clearance is reduced or the annular gap 26 becomes narrower.
  • the clearance can be sufficiently sealed, so that a sufficient negative pressure is maintained long enough to pull the seat part 12a out of the seat 15 (see Fig. 1).
  • the coupling element 9b is preferably made thin-walled at least in the region of its annular surface 19a.
  • the clearance must be at least so tight that at the start of the stroke movement sufficient for the deformation pressure drop comes about. In Fig.
  • the ideal case is shown, in which the longitudinal axes of the seat part 12a and spacer I Ia match and form a common longitudinal axis 23;
  • the coupling element 9b may also be rotationally symmetrical, so that a longitudinal axis of the coupling element 9b also coincides with the longitudinal axis 23.
  • deviations may arise between the individual axes, which are compensated according to the invention. This will be explained below with reference to FIGS. 3 and 4.
  • Fig. 3 the lower part of the coupling element 9b and the end portion of the seat part 12a, which has the outer surface 24a shown.
  • the spacer 1 la is not shown in Fig. 3.
  • the longitudinal axis of the seat part 12a can be tilted by an angle W1 relative to the longitudinal axis of the coupling element 9b, which here coincides with that of the spacer part 1a.
  • the diameter D1 of the annular surface 19a, ie the inner diameter of the coupling element 9b, and the diameter DO of the outer surface 24a of the end region of the seat part 12a are dimensioned such that an annular gap 26 is formed between the annular surface 19a and the outer surface 24a consists.
  • the width of the annular gap is in a symmetrical arrangement ' ⁇ (Dl -DO).
  • the angular error Wl which can be compensated by the connection between coupling element 9a and seat part 12a, is greater, the greater the width of the annular gap 26 and the shorter the length LI of the clearance between the substantially circular cylindrical annular surface 19a and the outer surface 24a , If the length LI of the annular surface 19a is increased in FIG. 3 for a given diameter DO and given angular error Wl, then the diameter D1 of the annular surface 19a and thus the width of the annular gap 26 must increase in order to obtain the angular error W1 without deformation of the coupling element 9b or 9b of the seat part 12a compensate.
  • Fig. 4 the situation shown in Fig. 3 is shown as a cross section in the plane D-D.
  • the annular gap 26 is unevenly wide over the circumference of the end region of the seat part 12a.
  • S2, S3 measured at two opposing positions (see also Fig. 3):
  • the quantity should in particular be so small that no appreciable damping takes place by means of a liquid cushion formed between the end region of the seat part 12a and the spacer part 11a. This should also apply in particular to the reverse movement following the stroke movement, ie when a pressure force is exerted in the valve member El for closing the injection nozzle 14.
  • the amount of pressure fluid flowing through the annular gap into the inner space 20 of the coupling element 9b per unit of time is approximately proportional to the cube of the width of the annular gap and inversely proportional to the length LI of the clearance fit for a given pressure difference in the simplest case.
  • the combination of the diameter DO, Dl and the length LI is therefore to be chosen so that on the one hand the clearance is tight enough, on the other hand, a compensation of the angular error Wl via an inclined position of the end portion of the seat portion 12a in the annular gap 26 and not or not to a substantial Part of a deformation of the coupling element 9b and the end portion of the seat part 12a, since such a deformation would lead to high side forces on the injection valve member El, which would be problematic for its function.
  • the width of the annular gap 26 and the length LI of the annular surface 19a are selected such that an angular error Wl of at least approximately 2 'is permissible.
  • the coupling element 9b can also be designed such that the coupling element 9b is deformed by the negative pressure arising in the interior 20 during a lifting movement and the width of the annular gap 26 is reduced; With an inner diameter D1 of approximately 4 mm, a wall thickness in the relevant region of the coupling element 9b of approximately 0.4 mm may be suitable for this purpose when using non-hardened steel.
  • the same considerations apply if the coupling element 9b is firmly connected to the seat part 12a and the spacer part 1a is enclosed by the coupling element 9b to form an annular gap.
  • the spacer 1 la may be operatively connected in the same way by a coupling element 9 a with the control part 8, as shown in Figures 3 and 4 for the connection between the seat part 12 a and spacer 1 la.
  • the injection valve member El comprises more than one coupling element, as a whole, a radial offset of the axes of the interconnected elements can be compensated.
  • the coupling element is designed in one piece with a spacer part Ib.
  • the annular surface 19b is therefore formed by the spacer part Ib.
  • a coupling element 9c has two inner surfaces which are each designed as annular surfaces 19c, 19d.
  • the seat part 12a and the spacer 1 lc are articulated with the head pelelement 9c and connected to each other.
  • a larger angle error or a radial offset can be compensated.
  • a spacer 25 can be provided between the spacer part 11a and the seat part 12a, which is enclosed by the coupling element 9b.
  • the spacer may for example consist of hardened steel.
  • FIG. 8 shows a simplified embodiment.
  • the annular surface 19e simultaneously forms the receptacle for the spacer part ld, so that the coupling element 9d has only a single inner diameter.
  • the outer surface 24 b of the end portion of the seat portion 12 b is adapted to the corresponding diameter to form an annular gap 26.

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

Abstract

L'invention concerne une soupape d'injection destinée à injecter du carburant dans une chambre de combustion d'un moteur à combustion interne. Ladite soupape comprend un carter (18) et un obturateur (E1) monté mobile dans un sens longitudinal dans ledit carter pour ouvrir et fermer au moins une ouverture d'injection (14). Ledit obturateur comprend une pluralité d'éléments d'obturateur (8, 11a, 11b, 11c, 12a, 12b) disposés les uns derrière les autres dans le sens longitudinal et au moins un élément d'accouplement (9a, 9b, 9c, 9d). L'élément d'accouplement (9a, 9b, 9c, 9d) entoure une zone d'extrémité d'un premier élément d'obturateur, de telle sorte qu'une fente annulaire (26) destinée à compenser une erreur angulaire (W1) entre un axe longitudinal du premier élément d'obturateur et un axe longitudinal de l'élément d'accouplement (9a, 9b, 9c, 9d) subsiste entre une surface extérieure (24a, 24b) de la zone d'extrémité du premier élément d'obturateur et une première surface intérieure de l'élément d'accouplement (9a, 9b, 9c, 9d). L'obturateur (E1), en particulier l'élément d'accouplement (9a, 9b, 9c, 9d), peut être entouré au moins en partie par un fluide sous pression et la fente annulaire (26) est dimensionnée de telle sorte que lorsqu'une force de traction est appliquée sur l'obturateur (E1) dans un espace intérieur (20) de l'élément d'accouplement (9a, 9b, 9c, 9d), une dépression destinée à l'accouplement cinématique du premier et d'un second élément d'obturateur soit formée.
PCT/EP2012/001379 2011-03-31 2012-03-29 Soupape d'injection WO2012130452A1 (fr)

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DE201110015753 DE102011015753A1 (de) 2011-03-31 2011-03-31 Einspritzventil
DE102011015753.0 2011-03-31

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11506162B2 (en) 2020-11-17 2022-11-22 Caterpillar Inc. Trapped volume split check assembly in fuel injector

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0228578A1 (fr) 1985-12-02 1987-07-15 Marco Alfredo Ganser Dispositif d'injection de combustible pour moteur à combustion interne
EP0685645A2 (fr) * 1994-05-02 1995-12-06 Mathis, Christian, Dipl.Masch.Ing. ETH Soupape d'injection pour un système d'injection de combustible d'un moteur à combustion interne, en particulier d'un moteur diesel
DE4427378A1 (de) 1994-08-03 1996-02-08 Bosch Robert Gmbh & Co Kg Magnetventilgesteuerter Injektor zur Kraftstoffeinspritzung in den Brennraum einer Dieselbrennkraftmaschine
DE19815892A1 (de) 1997-04-17 1998-10-22 Nippon Soken Kraftstoffeinspritzdüse
EP0976924A2 (fr) 1998-07-31 2000-02-02 Siemens Aktiengesellschaft Servovalve pour un injecteur et injecteur
DE10020867A1 (de) 2000-04-28 2001-10-31 Bosch Gmbh Robert Common-Rail-Injektor
WO2002086309A1 (fr) 2001-04-24 2002-10-31 Crt Common Rail Technologies Ag Soupape d'injection de carburant destinee a des machines a combustion interne
DE102007005573A1 (de) * 2007-02-05 2008-08-07 Robert Bosch Gmbh Injektor mit mehrteiligem Ventilelement
US20100065020A1 (en) 2007-04-09 2010-03-18 Kenichi Kubo Fuel injector
EP2206912A2 (fr) * 2009-01-13 2010-07-14 Robert Bosch GmbH Injecteur de carburant

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0228578A1 (fr) 1985-12-02 1987-07-15 Marco Alfredo Ganser Dispositif d'injection de combustible pour moteur à combustion interne
EP0685645A2 (fr) * 1994-05-02 1995-12-06 Mathis, Christian, Dipl.Masch.Ing. ETH Soupape d'injection pour un système d'injection de combustible d'un moteur à combustion interne, en particulier d'un moteur diesel
EP0685645B1 (fr) 1994-05-02 2001-06-06 Mathis, Christian, Dipl.Masch.Ing. ETH Soupape d'injection pour un système d'injection de combustible d'un moteur à combustion interne, en particulier d'un moteur diesel
DE4427378A1 (de) 1994-08-03 1996-02-08 Bosch Robert Gmbh & Co Kg Magnetventilgesteuerter Injektor zur Kraftstoffeinspritzung in den Brennraum einer Dieselbrennkraftmaschine
DE19815892A1 (de) 1997-04-17 1998-10-22 Nippon Soken Kraftstoffeinspritzdüse
EP0976924A2 (fr) 1998-07-31 2000-02-02 Siemens Aktiengesellschaft Servovalve pour un injecteur et injecteur
DE10020867A1 (de) 2000-04-28 2001-10-31 Bosch Gmbh Robert Common-Rail-Injektor
WO2002086309A1 (fr) 2001-04-24 2002-10-31 Crt Common Rail Technologies Ag Soupape d'injection de carburant destinee a des machines a combustion interne
DE102007005573A1 (de) * 2007-02-05 2008-08-07 Robert Bosch Gmbh Injektor mit mehrteiligem Ventilelement
US20100065020A1 (en) 2007-04-09 2010-03-18 Kenichi Kubo Fuel injector
EP2206912A2 (fr) * 2009-01-13 2010-07-14 Robert Bosch GmbH Injecteur de carburant

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11506162B2 (en) 2020-11-17 2022-11-22 Caterpillar Inc. Trapped volume split check assembly in fuel injector

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