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
  • F02M61/08—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 the valves opening in direction of fuel flow
• • 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
  • F02M61/042—The valves being provided with fuel passages
  • F02M61/045—The valves being provided with fuel discharge orifices
• • 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
  • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
  • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size

Definitions

• the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
• a valve member is axially displaceably guided in a bore in a valve body.
• the valve member has a valve head at its end protruding from the bore of the valve body on the combustion chamber side, the annular end surface of the valve facing away from the combustion chamber and delimiting a pressure chamber delimits the pressure chamber
• High pressure fuel can be applied.
• the high-pressure fuel acting on the pressure chamber moves the valve member outward against the restoring force of a valve spring into an opening stroke position.
• At least one injection channel is provided in the valve head, which, starting from the pressure chamber, opens into an outlet opening on the peripheral wall of the valve head, which is closed by the valve body in the closed position of the valve member and in the open stroke position of the valve body Valve member emerges from the overlap with the bore wall of the valve body, so that the fuel from the pressure chamber for injection into the combustion chamber of the internal combustion engine to be supplied.
• the injection bore is subdivided into at least two or more parallel channels, which are separated from one another by a partition and are released one after the other by the control edge on the valve body during the opening stroke of the valve member.
• This described channel geometry of the injection bore produces a relatively long concentrated injection jet which penetrates deep into the combustion chamber of the internal combustion engine to be supplied.
• a small stroke volume approximately 250-300 cm /
• the fuel injection valve for internal combustion engines according to the invention with the characterizing features of claim 1 has the advantage that the injection jet generated has a short depth of penetration and high atomization quality, so that it is well suited for combustion chambers of small diameter and small stroke volume.
• the spray geometry is advantageously designed so that the pressure conversion of the jet always takes place at the control edge of the valve body, which is still immersed in the outlet cross section of the injection bore even when the valve member is at its maximum opening stroke.
• the injection bores are arranged approximately at right angles to the valve member axis. Since the constant deflection of the jet path at the control edge is approximately 15 °, a jet cone of 150 ° is created with several injection openings over the circumference of the valve head.
• the described effect of a very short spray hole occurs particularly clearly when the outlet cross section of the injection bore is opened only slightly, at most up to 50%.
• injection channels or outlet or spray cross sections on the valve head of the valve member depends on the particular requirements of the internal combustion engine to be supplied, the outlet cross sections on the valve head advantageously being evenly distributed over the circumference of the valve head. Further advantages and advantageous configurations of the subject matter of the invention can be found in the description, the drawing and the claims.
• FIG. 1 shows a longitudinal section through the fuel injection valve in maximum
• FIG. 2 shows an enlarged section from FIG. 1 in the region of the valve member head
• FIG. 3 shows an enlarged representation of the injection cross section and the jet course of the injection jet.
• the fuel injection valve for internal combustion engines shown in FIG. 1 has a valve body 1 which is clamped to a valve holding body 5 by means of a union nut 3.
• a piston-shaped valve member 9 is axially displaceably guided in a bore 7 in the valve body 1 and has a valve head 11 acting as a closing head at its lower end, which projects into the combustion chamber of the internal combustion engine to be supplied.
• the valve head 11 shown enlarged in FIG. 2 has a conical valve sealing surface 13 facing the valve body 1, which in the exemplary embodiment is formed by an annular end surface of a seat ring 15 placed on the valve head 11 and which has a correspondingly conical valve seat surface 17 on the combustion chamber side end surface of the Valve body 1 interacts.
• the section of the valve head 11 projecting into a diameter-enlarged bore part 19 of the bore 7 of the valve body 1 is designed as a piston slide which is guided in the bore part 19 and with it the combustion chamber facing away from the annular end face 21 a pressure chamber 23 in the valve body 1.
• This pressure chamber 23 is connected via an annular gap 25 between the shaft 27 of the valve member 9 and the wall of the bore 7 to a collecting chamber 29, in which, on the other hand, the valve body 1 and the
• Ventilhaitek ⁇ rper 5 penetrating inlet line 31 opens, which can be connected to a fuel injection pump, through which the pressure chamber 23 is alternately acted upon by high fuel pressure.
• a valve spring 33 is inserted into a spring chamber 35 in the valve holding body 5, which is supported via a ring insert 37 and a slotted stop ring 39 on the end face of the valve body 1 facing away from the combustion chamber and which via an end facing away from the combustion chamber
• Valve member 9 arranged retaining ring 41 and a shim 43 acts on the valve member 9.
• the stem of the valve member 9 has a stop collar 45 at the level of the stop ring 39
• the closed position of the valve member 9 has a certain distance from the stop ring 39 which determines the total opening stroke and with which the valve member 9 comes into contact with the stop ring 39 after reaching the maximum opening stroke position.
• valve head 11 of the valve member 9 For injecting the fuel under high pressure into the combustion chamber (not shown) of the internal combustion engine to be supplied, in the valve head 11 of the valve member 9 there is at least one (in the exemplary embodiment three) discharge channel 47 leading away from the pressure chamber 23 and having an outlet cross section 49 on the peripheral wall of the valve head 11 forms, which is arranged so that it is completely closed when the valve member 9 the bore wall 19 of the valve body 1 is covered and during the outward opening stroke of the valve member 9 is opened by a lower control edge 51 arranged at the combustion chamber end of the valve body 1.
• This control edge 51 on the valve body 1, shown enlarged in FIGS. 2 and 3, is formed by the ring edge between the valve seat surface 17 and the wall of the bore 19 in the valve body 1.
• the injection channel 47 in the valve head 11 is formed by an inlet bore 53 starting from the upper annular end face 21 of the valve head 11, which is arranged inclined to the valve member axis, and an injection bore 55 leading radially away from this, which on the other hand opens onto the peripheral wall of the valve head 11 and there Exit cross section 49 forms.
• Injection bore 55 is perpendicular to the valve member axis and has a rectangular cross-sectional shape.
• the axial extent of the outlet opening at the outlet cross section 49 is dimensioned such that the valve sealing surface 13 on the support ring 15 is at a certain axial distance from the lower edge of the outlet cross section 49 on the combustion chamber side.
• the fuel injection valve according to the invention works in the following way.
• the valve spring 33 holds the valve member 9 with its valve sealing surface 13 in contact with the valve seat surface 17 on the valve body 1, the outlet cross section 49 of the injection channel 47 being in this closed position completely from the bore wall of the valve body 1 is closed.
• the pump delivered by the high-pressure injection pump gets under high-pressure fuel via the inlet line 31, the collecting chamber 29 and the annular gap 25 into the pressure chamber 23. There, the high-pressure fuel acts on the annular end face 21 and thus displaces the valve member 9 against the restoring force of the valve spring 33 from the valve seat 17.
• the outlet cross section 49 emerges of the injection channel 47 after passing through a short forward stroke from the overlap with the bore wall of the valve body 1, so that the outlet cross section 49 is opened by the control edge 51 of the valve body 1 and the fuel for injection reaches the combustion chamber of the internal combustion engine.
• the outlet cross-section 49 is only partially opened, as shown in FIG. 3, up to a maximum of 50%.
• the pressure conversion of the injection jet always takes place at the control edge 51, so that the effect of an extremely short spray hole length occurs.
• the beam deflection of 15 ° is provided at the control edge 51 in such a way that a beam cone angle ⁇ of approximately 150 ° is created over the evenly distributed multiple outlet cross sections 49.
• a maximum opening height of 50% of the total opening cross section at the outlet cross section 49 is ensured by the fixed distance between the stop collar 45 on the valve member 9 and the stop ring 39 in the closed position of the injection valve. The end of the high pressure injection takes place through the

Landscapes

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

Priority Applications (3)

Applications Claiming Priority (2)

Publications (1)

Family

ID=7783646

Family Applications (1)

Country Status (5)

Cited By (1)

Families Citing this family (1)

Citations (3)

• 1996
  • 1996-01-25 DE DE19602615A patent/DE19602615A1/de not_active Withdrawn
  • 1996-09-26 WO PCT/DE1996/001875 patent/WO1997027397A1/de not_active Application Discontinuation
  • 1996-09-26 KR KR1019970706625A patent/KR19980703221A/ko not_active Application Discontinuation
  • 1996-09-26 DE DE59608504T patent/DE59608504D1/de not_active Expired - Fee Related
  • 1996-09-26 JP JP9526396A patent/JPH11502587A/ja active Pending
  • 1996-09-26 EP EP96942256A patent/EP0817915B1/de not_active Expired - Lifetime

Patent Citations (3)

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