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
  • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
• • 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
  • F02M63/0012—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
  • F02M63/0019—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of electromagnets or fixed armatures
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
  • F02M2547/003—Valve inserts containing control chamber and valve piston
• • 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
• • 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
  • F02M63/008—Hollow valve members, e.g. members internally guided

Definitions

• the invention relates to a switching valve, in particular a solenoid valve for fuel injection valves, and a fuel injection valve with such a switching valve.
• the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
• a fuel injector with a pressure balanced control valve is known.
• an injection valve member which opens or closes an injection opening, is actuated by a control valve, the control valve releasing or closing a connection from a control chamber into a fuel return by placing or releasing a closing element in a seat.
• the hydraulic forces are minimized via a pressure compensation.
• the spring force can be reduced with less stroke and larger cross-sectional area. As a result, short switching times and advantageous dynamics are possible.
• the known from DE 10 2006 021 741 A1 fuel injector has the disadvantage that it may come to a seat leakage due to a misalignment of an anchor and a lack of centering due to a formed flat seat. Furthermore, the control valve is relatively sensitive to particles, since the support effect is limited. In addition, the seat limit can only be done via the anchor, with very small seat lengths consist of two functional edges, which also adversely affects the coating and particle impacts.
• the switching valve according to the invention with the features of claim 1 and the fuel injection valve according to the invention with the features of claim 12 have the advantage that an operation is improved. Specifically, there is the advantage that a robust switching valve can be created, which is also suitable for high pressures.
• the space into which the channel of the valve piece opens between the guide section and the sealing seat is formed at least partially in the guide opening.
• a puncture is provided on the valve piece between the guide portion and the valve seat surface, and that the space into which the channel of the valve piece opens between the guide portion and the sealing seat is at least substantially predetermined by the puncture, wherein an inner wall of the guide opening bounded by the recess space.
• the guide opening is designed as a guide bore, in particular as a continuous guide bore, and that at least the guide section of the valve piece is configured axially symmetrical to an axis of the guide bore.
• a guide between the valve piece and the valve closing body is ensured, so that a leak on the sealing seat is prevented by misalignment of the valve closing body.
• a relatively large guide play is predetermined between the guide section and the guide bore. In this way, a tensile load between the guide portion and the rest of the valve piece can be reduced. About the relatively large leadership game targeted leakage is possible.
• a lateral grinding is provided on the guide section, on which a leakage gap is formed between the guide section and the guide bore.
• About the leakage gap can also be a tensile load between the guide portion and the rest of the valve piece can be reduced.
• the channel which opens into the space between the guide portion and the sealing seat, designed as a throttled channel.
• the valve closing body has a sealing edge which faces the valve seat surface, that the sealing seat between the sealing edge and the valve seat surface is formed and that a predetermined by the sealing edge seat diameter of the sealing seat is at least approximately equal to a diameter of the guide portion of the valve piece. This allows a very small seat diameter can be realized, with a sufficient high-pressure resistance is possible. Due to the small seat diameter, a reliable tightness of the closed sealing seat can be ensured even at very high pressures.
• valve seat surface is designed as a conical valve seat surface and that an opening angle of the conical valve seat surface is selected from a range of about 80 ° to about 120 °.
• sealing edge is configured on a conical end face of the valve closing body and that an opening angle of the conical end face is greater than the opening angle of the conical valve seat face. This allows an advantageous centering effect of the valve closing body with respect to the valve seat surface of the valve piece. Thus, leakage at the sealing seat by misalignment or the like can be prevented.
• a seat limitation may be mounted in or on the valve piece.
• the seat diameter of the sealing seat is not greater than 2 mm, in particular approximately equal to 1, 8 mm.
• a relatively large leakage which may occur, for example, with a seat diameter of 2.5 mm, be prevented and a high pressure resistance for very high pressures, especially for pressures of more than 160 MPa (1600 bar), created.
• FIG. 1 shows a switching valve of a fuel injection valve in an excerptional, schematic sectional view according to an embodiment of the invention.
• Fig. 1 shows an embodiment of a fuel injection valve 1 with a switching valve 2 in a schematic, excerpt, axial sectional view.
• the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
• a preferred use of the fuel injection valve 1 is for a fuel injection system with a fuel rail, which leads diesel fuel under high pressure to a plurality of fuel injection valves 1.
• valve 1 and the switching valve 2 according to the invention are also suitable for other applications.
• the switching valve 2 has a valve piece 3 on which a valve seat surface 4 is formed. Furthermore, the switching valve 2 has a valve closing body 5, which cooperates with the valve seat surface 4 to a sealing seat.
• the valve closing body 5 is a part of an armature 6. In this case, the valve closing body 5 is formed integrally with the armature 6. However, the valve closing body 5 can also be connected to the armature 6.
• a solenoid 8 is arranged, which serves to generate a magnetic field for actuating the valve closing body 5 of the armature 6 by means of the magnetic core 7. As a result, the sealing seat formed between the valve closing body 5 and the valve seat surface 4 can be opened and closed.
• the armature 6 is in this case guided on a pressure pin 9, which is supported on a support element 10. Further, a Ventilfe- 11 is provided, which is arranged between the support member 10 and the armature 6, to bias the armature 6 against a magnetic attraction of the magnetic core 7, which is controllable by a current through the magnetic coil 8. In this case, the force of the valve spring 11 influences the contact force of an edge 12 of the valve closing body 5 against the valve seat surface 4 when the sealing seat is closed.
• valve piece 3 is inserted into a further housing part 13 of the fuel injection valve 1.
• the valve member 3 is supported on a shoulder 14 of the housing part 13.
• the valve piece 3 has a bore 15 in which a control chamber 16 is delimited by a valve piston 17.
• In the control chamber 16 performs an inlet throttle 18, which connects the control chamber 16 with a high-pressure chamber 19 in the interior of the housing part 13.
• the switching valve 2 has an axis 25, on which the armature 6 and the valve piece 3 are aligned.
• the armature 6 is configured axially symmetrical with respect to the axis 25.
• the valve piece 3 is designed substantially axially symmetrical to the axis 25.
• the valve piece 3 has a guide portion 26 which is guided in a guide bore 27 of the armature 6.
• the guide bore 27 is configured here as a continuous guide bore 27.
• In the guide bore 27 also extends the pressure pin 9 to guide the armature 6 on the pressure pin 9.
• a recess 28 is provided on the valve piece 3.
• a fuel chamber 29 is formed, which is bounded by an inner wall 30 of the guide bore 27 of the armature 6. The fuel room 29 is thus formed between the guide portion 26 and the valve seat surface 4.
• the valve piece 3 has an axial blind bore 31, from which a channel 32 and a channel 33 branch off. About the blind bore 31 and the channels 32, 33 of the control chamber 16 is connected to the fuel chamber 29.
• the channels 32, 33 are designed as throttled channels 32, 33.
• the channels 32, 33 both open into the fuel chamber 29 between the guide portion 26 and the sealing seat, which is formed at the edge 12 between the valve closing body 5 and the valve seat surface 4.
• the fuel cavity 29 is formed in the guide bore 27.
• the edge 12 of the valve closing body 5 is designed as a sealing edge on which the sealing seat between the valve closing body 5 and the valve seat surface 4 comes about.
• the sealing edge 12 faces the valve seat surface 4.
• a diameter 34 of the sealing edge 12 is at least approximately the same size as a diameter 35 of the guide portion 26. This is in relation to the fuel chamber 29, a pressure equalization allows.
• the diameter 34 is very small, so that a seat diameter of the sealing seat is also very small.
• the diameter 34 and thus the seat diameter at the sealing edge 12 can not be greater than 2 mm, in particular approximately equal to 1, 8 mm.
• the armature 6 has an end face 36 which faces the valve seat surface 4 of the valve piece 3.
• the sealing edge 12 is formed between the end face 36 and the inner wall 30 of the guide bore 27.
• the conical valve seat surface 4 for example, has an opening angle which is equal to 90 °.
• An opening angle of the conical end face 36 of the valve closing body 5 is greater than the opening angle of the conical valve seat surface 4, that is, in this embodiment, greater than 90 ° selected.
• the opening angle of the conical valve seat surface 4 is determined by the required centering and may be in a range of less than 120 °. It is particularly advantageous if it is in a range of about 80 ° to about 120 °.
• the opening The angle of the conical end face 36 of the valve closing body 5 is then selected to be greater than the opening angle of the conical valve seat surface 4.
• the valve seat surface 4 is limited by a step 37. In this way, a maximum diameter 38 of the valve seat surface 4 can be predetermined for seat limitation.
• the seat limitation can be attached to the valve member 3 through the step 37 or in other ways.
• the guide section 26 is preferably relatively short along the axis 25. This short guide section 26 essentially serves for centering during assembly. The leadership of the armature 6 via the pressure pin 9. The pressure forces from the seat diameter are preferably absorbed by the pressure pin 9. About the support member 10 thus takes place a support to a magnet group. In this case, the guide section 26 does not seal against the high pressure in the fuel chamber 29. This ensures that the valve member 3 in the region of the recess 28 and in particular at the mouths of the channels 32, 33 is not loaded on train and thus in this area no or only very small tensile stresses in the valve piece 3 occur. Here it is possible to provide a further strain relief.
• a bevel 39 may be provided on one side of the guide section 26, which forms a leakage gap between the guide section 26 and the inner wall 30 of the guide bore 27.
• the guide portion 26 in which no bevel 39 or the like is provided.
• the guide section 26 is designed to be axially symmetrical with respect to the axis 25. In this way, a certain amount of guidance can be achieved in order to achieve a reliable closing of the sealing seat between the sealing edge 12 and the valve seat surface 4. Specifically, a tilting between the valve closing body 5 and the valve member 3 is prevented or at least reduced, whereby a self-centering of the sealing edge 12 is supported on the conical valve seat surface 4.

Landscapes

• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Electromagnetism (AREA)
• Fuel-Injection Apparatus (AREA)
• Magnetically Actuated Valves (AREA)
• Lift Valve (AREA)

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

Family

ID=42313859

Family Applications (1)

Country Status (4)

Families Citing this family (2)

Citations (5)

Family Cites Families (1)

• 2009
  • 2009-06-05 DE DE200910026774 patent/DE102009026774A1/de not_active Withdrawn
• 2010
  • 2010-04-13 CN CN201080024570.4A patent/CN102803704B/zh active Active
  • 2010-04-13 WO PCT/EP2010/054810 patent/WO2010139501A1/de active Application Filing
  • 2010-04-13 EP EP10713929.7A patent/EP2438288B1/de active Active

Patent Citations (5)

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