VALVE OF A FUEL INJECTOR

Abstract

The present invention relates to a valve of a fuel injector for selectively disconnecting a high pressure region from a low pressure region of a fuel, comprising an opening in a seat plate, an armature which is designed to close the opening of the seat plate, a spring element which prestresses the armature in the direction of a position which closes the opening, and an electromagnet for lifting the armature out of the position which closes the opening into a position which releases the opening, characterized by an elastically compressible damping element for limiting an armature stroke in the case of the armature being lifted from the seat plate into the releasing position.

Claims

1. A valve (1) of a fuel injector for a selective separation of a high pressure region from a low pressure region of a fuel comprising: an opening (2) in a seat plate (3); an armature (4) that is configured to close the opening (2) of the seat plate (3); a spring element (5) that preloads the armature (4) in the direction of a position closing the opening (2); and an electromagnet (6) for raising the armature (4) from the position closing the opening (2) into a position releasing the opening (2), wherein an elastically compressible damping element (7) to bound an armature stroke on the raising of the armature (4) from the seat plate (3) into the releasing position.

2. A valve (1) in accordance with claim 1, wherein the damping element (7) is a soft-elastic damping element (7).

3. A valve (1) in accordance with claim 1, wherein the stiffness of the damping element (7) is smaller than the stiffness of the armature (4).

4. A valve (1) in accordance with claim 1, wherein the damping element (7) is a damping pin having a substantially cylindrical shape that preferably has a cross-sectional reduction (12) between its two end surfaces.

5. A valve (1) In accordance with claim 1, wherein the damping element (7) has a spherical section (8) at its contact surface to the armature (4) to minimize a contact surface with the armature (4).

6. A valve (1) in accordance with claim 1, wherein the poles (9) of the electromagnet (6) and an end side of the damping element (7) contacting the armature (4) are disposed in a common plane in a relaxed state of the damping element (7).

7. A valve (1) in accordance with claim 1, wherein the damping element (7) is separate from a housing (10) of a fuel injector.

8. A valve (1) in accordance with claim 1, wherein the preload force of the spring element (5) can be set, preferably via setting plates (11) to change the position of the spring element (5) with respect to the damping element (7) and/or the armature (4).

9. A valve (1) in accordance with claim 1, wherein the end side of the damping element (7) remote from the armature (4) is designed as a flat seat.

10. A valve (1) in accordance with claim 1, wherein the armature (4) has an elevated portion (13) in its surface facing the damping element (7) at which the armature (4) impacts the damping element (7).

11. A valve (1) in accordance with claim 1, wherein the armature (4) is designed in multiple parts and comprises an armature part and a seat part.

12. A valve (1) in accordance with claim 1, wherein the spring element (5) is a spiral spring that extends in a spiral manner around the damping element (7).

13. A valve (1) in accordance with claim 1, wherein the armature (4) only comes into contact with the damping element (7) on the transition from the position closing the opening (2) into the position releasing the opening (2).

14. A valve (1) in accordance with claim 1, wherein the design of the valve (1) is rotationally symmetrical to an axis of rotation (13) that is identical to an axis of rotation of the damping element (7).

15. A fuel injector having a valve (1) in accordance with claim 1, in particular a diesel fuel injector.

16. A valve (1) in accordance with claim 2, wherein the stiffness of the damping element (7) is smaller than the stiffness of the armature (4).

17. A valve (1) in accordance with claim 16, wherein the damping element (7) is a damping pin having a substantially cylindrical shape that preferably has a cross-sectional reduction (12) between its two end surfaces.

18. A valve (1) in accordance with claim 3, wherein the damping element (7) is a damping pin having a substantially cylindrical shape that preferably has a cross-sectional reduction (12) between its two end surfaces.

19. A valve (1) in accordance with claim 2, wherein the damping element (7) is a damping pin having a substantially cylindrical shape that preferably has a cross-sectional reduction (12) between its two end surfaces.

20. A valve (1) In accordance with claim 17, wherein the damping element (7) has a spherical section (8) at its contact surface to the armature (4) to minimize a contact surface with the armature (4).

Description

[0026] Further features, details and advantages of the invention will be explained with reference to the following description of the Figures. There are shown:

[0027] FIG. 1: a half-sectional view through the valve in accordance with the invention;

[0028] FIG. 2: a force diagram on the transition of the armature between its two positions; and

[0029] FIG. 3: a representation of the armature stroke in dependence on different elasticities of the damping element.

[0030] FIG. 1 here shows a partial longitudinal sectional view of the valve 1 in accordance with the invention. The seat plate 3 that separates the high pressure region (at the lower side) from a low pressure region (at the upper side) has an opening 2 that can connect a high pressure region and a low pressure region of fuel to one another. This opening 2 is here closed by an armature 4 whose sealing surface 15 seals the opening 2 in its closed state. The armature 4 can be raised from this position when the magnet 6 is activated and thus pulls the armature 4 from the opening 2. In a deactivated state of the magnet 6, a spiral spring 5 has the effect that the sealing surface 15 of the armature 4 is pressed toward the opening 2. The magnet 6 has a coil 61 and a coil jacket 62 so that a magnetic force can be produced by a flowing of current through the coil 61. In the space bounded by the spiral spring 5, a damping element 7 is arranged that corresponds to a damping pin in the representation shown. This damping pin 7 has a first end side 8 that faces the armature 4. The end side 8 is rounded in the present case or corresponds to a section of a sphere so that on an impact of the armature 4 on the damping element 7, only a contact region that is as small as possible is produced between the armature 4 and the damping element 7. It can further be recognized that the damping element 7 has a cutout 14 in its periphery that provides a smaller stiffness and thus a certain elasticity of the damping element 7. This cutout 14 can be provided as rounded here as can be seen at reference numeral 12. The damping element 7 can be held in the magnet 6 by a press fit. A setting plate 11 by which the spring can be moved in its position in the axial direction can further be provided to set the preload force of the spring element 5.

[0031] The armature 4 can here have an elevated portion at which the armature 4 impacts the contact surface 8 of the damping element 7.

[0032] An armature guide 16 is provided so that the armature is guided into the position releasing the opening 2 during a transition of its sealing position. A spacer ring 17 here screens the armature 4 from the housing 10 of a fuel injector. The magnet poles of the magnet 6 are marked by reference numeral 9.

[0033] The axis of symmetry 13 shows that the valve 1 is set up with mirror symmetry and/or rotational symmetry.

[0034] In a closed state, a magnetizable part, here the armature 4, is acted on in the armature guide 16 by means of the spring element 5 by a force, the preload force, definable via the setting plate 11 that closes the armature 4 in an axial direction away from the magnet 6 toward a sealing part of the seat plate 3. As stated, the seat plate 3 separates a high pressure region from a low pressure region of the fuel.

[0035] In an open state, the connection between the high pressure region and the low pressure region via the opening 2 in the seat plate 3 is released by an axial movement of the armature 4 in the direction of the magnet 6 so that fuel can flow from the high pressure region arranged at the bottom in FIG. 1 into the low pressure region that is arranged above the seat plate 3 in FIG. 1. At least one fuel inlet from the injector into the combustion chamber is released via a hydraulically mechanical event chain and fuel is supplied into the combustion space.

[0036] Current that flows through the windings of the coil 16 is produced by means of a voltage source to open the magnetic valve 1, that is the transition between a closed state and an open state. The windings of the coil 61 are surrounded by a coil jacket 62 that is in turn surrounded radially inwardly and outwardly by a ferromagnetic core 6 that serves for the reinforcement of the magnetic field induced by the current in the coil 61.

[0037] A force acts between the magnet pole 9 of the magnet 6 and the armature 4 due to the magnetic field. With a sufficiently strong power signal and a sufficiently long control duration, the attractive magnetic force between the magnet pole 9 and the armature 4 exceeds the opposite preload force of the spring 5. As a result, the armature is then drawn in the axial direction in the direction of the magnet 6 so that the opening 2 in the seat plate 3 is released.

[0038] The armature 4 is constantly further accelerated by the attractive magnetic force increasing as the distance reduces until it comes to abutment of the armature 4 at the damping element 7. In so doing, the armature 4 impacts a contact surface 8 of the damping element 7 that is configured by a pin in the above.

[0039] The damping pin 7 acts like a very hard spring, but has a comparatively small stiffness in comparison with the armature 4. Provision can be made here that the stiffness of the damping pin or of the damping element is smaller than 70%, preferably smaller than 50%, and more preferably smaller than 30%, of the stiffness of the armature 4. The damping pin 7 completely brakes the armature 4, with the damping pin 7 being elastically compressed. In so doing, there is a no further mechanical contact between the armature 4 and the magnet 6 except for the contact between the armature 4 and the pin 7.

[0040] After a maximum compression of the pin 7, the restoring force of the spring 5 and of the pin 7 effects an expansion of the pin 7 in the direction of the opening 2 of the seat plate 3. In an oscillating process, a deformation of the pin 7 is adopted to a degree at which the sum of the forces acting on the armature 4 (the attractive magnetic force and the repelling restoring force due to the spring 5 and the pin deformation) cancel each other out in force equilibrium.

[0041] The electrical current and the magnetic field are reduced again on a switching off of the voltage source. The magnetic force attracting the armature 4 thereby decreases very rapidly and can no longer overcome the restoring force of the spring. The armature is thereupon urged back into the closed state by the spring 5 so that the opening 2 in the seat plate 3 is closed by the armature 4 and the high pressure space (below the seat plate 3) is again separated from the low pressure space (above the seat plate 3) so that one or more fuel inlets from the injector into the combustion space are closed again via the hydraulically mechanical event chain and fuel is no longer introduced into the combustion space.

[0042] As FIG. 2 shows, the implementation of the abutment of the armature 4 at the damping element 7, that is relatively soft-elastic, produces a very advantageous behavior of the armature 4. If the armature 4 impacts the damping element 7, it only oscillates at a very small oscillation amplitude for a manageable time period.

[0043] FIG. 3 shows this oscillation behavior of the armature with reference to the armature stroke h in comparison with different elasticities of the damping element 7. Here, a hard elasticity is shown by a continuous line whereas a soft elasticity of the damping element 7 is shown in a dashed embodiment. It can be recognized that the oscillation amplitude of the soft-elastic embodiment Δh.sub.we is smaller in the hard elastic embodiment Δh.sub.he. This is due to the fact that the deformation of the damping element 7 on the impact of the armature has the result that the distance between the magnet 6 and the armature 4 is first further reduced to a distance that is smaller than that distance that would be adopted in a static equilibrium of forces. This has the result that the magnetic force F.sub.Mag between the armature 4 and the magnet 6 that attracts the armature 4 increases disproportionately in comparison with a linearly increased restoring force F.sub.Rück, caused by the spring and damping element 7. The disproportionate force increase greatly damps the resilient effect of the damping element 7 so that the bumping of the armature on the abutment of the magnet is reduced.

[0044] This is shown graphically in FIG. 3 in which the continuous line represents the amount of the magnetic force F.sub.Mag and the dashed line represents the amount of the restoring force F.sub.Rück. If the armature 4 is now only attracted up to the distance x.sub.A1 in an embodiment with a hard-elastic damping element due to the magnetic force, the resulting magnetic force F.sub.A1 is here substantially smaller than that magnetic force F.sub.A2, that is reached on the attraction of the armature 4 up to and into the position X.sub.A2 that results with a soft-elastic damping element embodiment.

[0045] Since, however, in the embodiment with a soft-elastic damping element, a greater force acts on the armature 4 overall than would be the case with the hard-elastic embodiment, the oscillating behavior of the armature 4 is considerably reduced that lasts for so long until a static equilibrium of forces has been adopted. A more stable regulation of the injection amount can thereby be achieved which results in an improvement of a fuel injector overall.