Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
  • F02M63/0012—Valves
  • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
  • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
• • 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
  • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
  • F02M63/0012—Valves
  • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
  • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member

Definitions

• the invention relates to an injection valve for an internal combustion engine with an electromagnetically actuated control valve, which alternatively closes or releases a fluid passage opening assigned to a sealing surface by means of a valve actuator and thereby controls the pressure in a control pressure chamber connected to the passage opening.
• valve actuator is firmly connected to the armature of the electromagnet and is pressed onto a sealing surface by spring force, so that the passage opening to the control pressure chamber is closed.
• Such injection valves are usually used in accumulator injection systems, where very high control pressures of the order of several 100 bar occur.
• the valve actuator connected to the magnet armature is raised against the spring force, so that the passage opening is opened and the high pressure can thus be reduced in the control pressure chamber.
• the pressure drop in the control pressure chamber then triggers the injection in the injection valve.
• valve actuator When the solenoid current is switched off, the magnet armature and with it the valve actuator, which is usually designed as a cylindrical bolt, strikes the sealing surface with its end face under the spring force and thereby closes the passage opening.
• a good sealing effect of the valve actuator against the very high pressure in the control pressure chamber is achieved by the smallest possible cross-sectional area and thus small diameter of the valve actuator.
• the smallest possible diameter of the valve actuator is therefore also desirable so that angular errors, i. H. Deviations in the alignment of the end face of the valve actuator from the associated sealing seat surface, which result from manufacturing inaccuracies, do not lead to leakage gaps.
• a third reason for the smallest possible diameter of the valve actuator is a high sealing seat pressure to be aimed at and thus a more precise control.
• a disadvantage of a small diameter of the valve actuator is, however, that a small diameter and thus a small end face may result in an inadmissibility high seat angle at the valve opening results.
• Another disadvantage of a small diameter of the valve actuator is the fact that the closing movement of the magnet armature and the valve actuator, which together form a considerable inert mass, are decelerated to zero with little damping and rebound effects occur. For a damping braking of the valve actuator, the largest possible diameter and thus a correspondingly large end face would be desirable.
• the object of the present invention is to design an injection valve of the aforementioned type in such a way that the conflict of objectives outlined above is resolved and thereby both great accuracy of the control valve is achieved even at extremely high pressures and at the same time inadmissibly high wear and tear is prevented by the impact movement of the valve actuator.
• the object is achieved in that the valve actuator actuated by the electromagnet has, in addition to an actuator sealing surface which interacts with the sealing surface of the fluid passage opening, an actuator stop surface which is arranged at a distance from the actuator sealing surface.
• the actuator stop surface is significantly larger than the actuator sealing surface.
• the locally separate design of the actuator stop surface and the actuator sealing surface also has the advantage that high fluid pressures, such as occur in the area of the fluid passage opening and thus the actuator sealing surface, can be moved locally away from the electromagnet and the electromagnet is protected from high hydraulic pressure.
• the electromagnet can also be better protected against impairment by the physical or chemical properties of the control fluid.
• the actuator sealing surface is the end face of a valve rod formed by the valve actuator.
• the valve actuator comprises a spherical valve body, which rests on the end face of the valve rod and interacts with conical sealing surfaces of the passage opening.
• the length of the valve rod is essentially determined by the distance that the actuator sealing surface or the valve body stop of the valve rod is from the actuator stop surface. It is advantageous if the valve actuator is essentially mushroom-shaped, the mushroom stem forming the valve rod and the actuator stop surface being an annular collar concentrically surrounding the valve rod in the region of the mushroom cap. Such a valve actuator can be manufactured with little effort in terms of production technology.
• the length of the valve rod is a minimal amount greater than the distance between the sealing surface of the fluid passage opening or the valve body stop of the valve rod from the reference stop for the actuator stop surface.
• valve actuator is divided in a parting line into an actuator stop having the actuator stop surface and a valve rod which is operatively connected to the actuator sealing surface and the actuator stop.
• Valve actuator consists in that the valve rod, which is significantly smaller in diameter, is easier to manufacture independently of the actuator stop. Another advantage is that different material can be used for the valve stem and actuator stop. With the split version of the valve actuator, it only has to be ensured that the opening movement of the valve rod, i. H. So the lifting from the sealing surface is guaranteed by the excess pressure from the fluid passage opening or by a supporting auxiliary spring. The slight excess length of the valve rod, based on the distance between the actuator sealing surface or valve body stop and the actuator stop surface (valve rod protrusion) can be absorbed during the closing movement by elastic deformation (shortening) of the valve rod.
• the actuator stop is essentially mushroom-shaped, the actuator stop surface being in the region of the mushroom foot on the valve rod striking face.
• this end face will be a circular area, the diameter of which is significantly larger than the diameter of the striking valve rod.
• a guide bushing be arranged at a short distance from the actuator sealing surface of the valve rod. In this way, bending vibrations of the free end of the valve rod with the actuator sealing surface are prevented, so that the actuator sealing surface only has to have a slightly larger diameter than that of the through bore.
• the length of the valve rod is preferably a multiple of its diameter.
• the actuator sealing surface is assigned to a one-part or two-part disk-shaped insert, the control pressure chamber connecting on the side facing away from the sealing surface.
• the corresponding insert part can be adapted to different stresses in terms of material with little effort, thereby improving the seal.
• FIG. 2 shows the area of the electromagnetic control valve of the injection valve according to FIG. 1 enlarged
• Fig. 3 is a again greatly enlarged compared to the representation in Fig. 2
• FIG. 4 shows a variant of the injection valve with an insert in the area of
• Fig. 6 shows a variant of an injection valve according to the invention in longitudinal section, the valve needle with its end facing away from the injection openings lying directly in the control pressure chamber.
• the injection valve of a high-pressure accumulator injection system for an internal combustion engine shown in FIG. 1 has a housing 1.
• a valve needle 20 is mounted, through the axial movement of which an injection hole 24 in relation to a high-pressure chamber 21 can be opened and thus an injection takes place.
• the high-pressure chamber 21 is connected to a high-pressure connection 22 via channels in the housing 1.
• the movement of the nozzle needle 20 is controlled via an electromagnet 10, the armature 11 of which is firmly connected to a valve actuator 12.
• the valve actuator 12 is part of a control valve which is actuated by the electromagnet 10. The function of this electromagnetically operated control valve is explained on the basis of the enlargement according to FIG. 2.
• valve actuator 12 is essentially mushroom-shaped, the mushroom stem as
• Valve rod 16 is formed, which extends from the area of the mushroom cap to a sealing surface 17, into which a fluid passage opening 14a opens out from a control pressure chamber 14.
• the diameter of the valve rod 16 is selected such that the end face just covers the fluid passage opening 14a and thus forms a sealing seat on the sealing face 17. It is easy to see that the length of the valve rod 16 is a multiple of its diameter.
• the control pressure chamber 14 is connected to the high-pressure duct system of the injection valve via a throttle bore.
• the valve actuator 12 is through the valve rod 16 in an upper guide sleeve 15o and a lower guide bush 15u axially displaceably mounted on the housing.
• the lower guide bush 15u is arranged such that there is only a small distance between the lower end of the valve rod 16, which is designed as an actuator sealing surface 16a, and the lower edge of the lower guide bush 15u.
• the resulting annular space 18 is connected to a low-pressure fluid connection 19 of the injection valve.
• the valve rod 16 closes off the fluid passage bore 14a with its actuator sealing surface 16a.
• An annular collar concentrically surrounding the valve rod 16 in the area of the mushroom cap of the actuator 12 is designed as an actuator stop surface 12a and rests on the upper flat surface of the sleeve 15o.
• the valve actuator 12 In the shown closed position of the electromagnetic control valve, the valve actuator 12 together with the magnet armature 1 1 is loaded by a compression spring, not shown, which presses the actuator 12 onto the sealing surface 17 and at the same time onto the top of the upper guide bush 15o, which acts as a reference stop for the actuator stop surface 12a of the actuator 12 is used. If the electromagnet 10 is energized, the magnet armature 1 1 pulls the valve actuator 12 upward against the force of the compression spring, so that the fluid passage bore 14a is opened and thus a pressure drop in the control pressure chamber 14 occurs, which causes the valve needle 20 to be raised and thus causes an injection , When the current is switched off, the valve actuator 12 strikes down together with the magnet armature 1 1 under the force of the compression spring.
• the actuator stop surface 12a of the actuator 12 which is much larger than the actuator sealing surface 16a of the valve rod 16, acts as a pure damping and impact surface for reducing the inertial forces of the armature and valve actuator.
• the much smaller actuator sealing surface 16a at the lower end of the valve rod 16 takes over the function of the sealing seat, which is done with great accuracy and without the risk of leakage due to the small surfaces even at extremely high control pressures.
• FIG. 3 This danger is shown on the basis of the greatly enlarged illustration according to FIG. 3 in a conventional injection valve.
• a conventional injection valve Such a valve is constructed similarly to that shown in FIGS. 1 and 2, but with the difference that the fluid passage opening 14a, which is in communication with the control pressure chamber 14, up to a housing surface which functions as a stop and sealing surface 13 is performed.
• the valve actuator 12 is again mushroom-shaped, but does not have the invention Valve rod 16.
• the diameter e of the sealing seat and impact surface is chosen to be significantly larger than the diameter of the fluid passage bore 14a. The risk must be taken into account here that as a result of an angular error f, ie a deviation of the sealing and stop surface from the exactly right angle relative to the
• a minimal gap s remains in the longitudinal axis of the valve actuator 12, even when the valve actuator 12 is struck, which causes a permanent pressure drop in the high-pressure region 14.
• FIG. 4 shows a region of an injection valve corresponding to FIG. 2, which is modified in the region of the actuator sealing surface.
• the valve rod 16 acts, as shown enlarged in FIG. 4, on a valve body 30 which is designed as a ball.
• the valve body 30 bears against a conically shaped sealing surface 17 of the fluid passage opening 14a.
• the fluid passage opening 14a contains a discharge throttle 33.
• the use of a separate valve body 30, which can also have a shape other than spherical, has the advantage that the seal is improved.
• a further improvement in the sealing results from the use of an insert part in the form of a disk-shaped part 37 which contains the discharge throttle 33. This part 37 can in terms of material and
• Throttle bore can be optimally matched to different stress situations in a simple manner.
• insert parts with throttle bores of different sizes, it is also possible to change the injection characteristics by simply replacing them.
• second parts 34 with different inlet throttles 36 in order to adjust the injection characteristics by simply exchanging them.
• This procedure of changing the injection quantity and the injection course by replacing first and second insert parts with different throttles is known per se from EP 0 844 385 A1.
• the part 37 is connected by a centering and holding clip 39 to a sleeve 38 in which the valve rod 16 is received with its guide bushings 15o and 15u.
• FIG. 5 shows an injection valve according to the invention, which likewise contains a disk-shaped insert 32.
• the control pressure chamber 14 directly adjoins the side of the insert 32 facing away from the sealing surface 17.
• the rear end of the nozzle needle 20 lies directly in the control pressure chamber 14.
• the insert 32 is installed between the nozzle holder and the injection nozzle 40. Injection nozzle 40 and insert 32 are pressed against the nozzle holder by a nozzle nut, so that the high-pressure areas are connected to one another.
• the insert 32 has a central bore as a fluid passage opening 14a to the control pressure chamber 14 and in the area opposite the valve rod 16 a calibrated discharge throttle 33.
• the insert also contains a high-pressure duct 41, which forwards the fuel under injection pressure from a high-pressure connection 22 to a high-pressure duct in the injection nozzle ,
• the high-pressure duct 41 in the insert part 32 has a line connection to the central bore in the insert part 32 and in this line connection there is a calibrated inlet throttle 36.
• the insert part 32 preferably has a conical sealing surface 17 in which a spherical valve body 30 provides the seal.
• a corresponding embodiment is known per se from US 5,832,899.
• the injector corresponds to the injector described under FIG. 1 or FIG. 2. Due to the design with the two sides of the insert directly assigned
• the seal is essentially reduced to this area that can be easily controlled.
• suitable insert parts it is possible in a simple manner to react to different stress cases and requirements for the injection quantity and injection process.

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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)
• Electromagnetism (AREA)
• Fuel-Injection Apparatus (AREA)
• Magnetically Actuated Valves (AREA)
• Valve-Gear Or Valve Arrangements (AREA)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (1)

Family

ID=7918638

Family Applications (1)

Country Status (5)

Cited By (3)

Families Citing this family (1)

Citations (8)

Family Cites Families (6)

• 1999
  • 1999-08-17 DE DE19938921A patent/DE19938921B4/de not_active Expired - Fee Related
• 2000
  • 2000-05-26 JP JP2001517048A patent/JP3754649B2/ja not_active Expired - Lifetime
  • 2000-05-26 WO PCT/EP2000/004815 patent/WO2001012981A1/de not_active Ceased
  • 2000-05-26 DE DE50009929T patent/DE50009929D1/de not_active Expired - Lifetime
  • 2000-05-26 EP EP00936814A patent/EP1208297B1/de not_active Expired - Lifetime
  • 2000-05-26 AT AT00936814T patent/ATE292239T1/de active

Patent Citations (8)

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