KR102401612B1 - Assembly having a valve for metering a fluid - Google Patents

Abstract

The invention relates to an assembly (1) comprising a valve (2) used for metering a fluid. The valve 2 comprises an electromagnetic actuator 5 and a valve needle 15 which can be actuated by the actuator 5 . The electromagnetic actuator comprises a magnetic coil 6 and an armature 8 which is arranged on the valve needle 15 and can be actuated by the magnetic coil 6 in the course of operation. The valve needle 15 is used to actuate the valve closing body 16 which interacts with the valve seat face 19 to form a sealing seat. In this case, at least one stop surface 32 , 33 against which the armature 8 strikes in the course of operation is provided. In addition, a measuring device 3 is provided which is electrically connected to the magnetic coil 6 at least in the course of operation. The armature 8 , the stop surfaces 32 , 33 and the valve needle 15 are formed so that, in the course of operation, the armature vibration of the armature 8 is generated after the sealing seat is closed. Further, the measuring device 3 is configured such that, in the course of operation, the armature vibration generated after the closing of the sealing sheet is detected in the form of vibration generated in the coil voltage of the magnetic coil 6 .

Description

Assemblies with valves for metering fluids {ASSEMBLY HAVING A VALVE FOR METERING A FLUID}

The present invention relates in particular to an assembly comprising a valve for metering a fluid, used as a fuel injection valve for an internal combustion engine. In particular, the invention relates to the field of injectors for fuel injection systems for automobiles, preferably in which direct injection of fuel into the combustion chambers of an internal combustion engine is carried out.

From DE 199 50 761 A1 is known a fuel injection valve for a fuel injection system comprising a valve needle which interacts with a valve seat face to form a seal seat. The fuel injection valve includes an armature secured to a valve needle, which is movably guided on the valve needle and is cushioned by an elastomeric ring made of an elastomeric polymer. The cushioning is achieved by means of an elastomeric ring. Therefore, the rebound of the valve needle from the valve seat surface when closing the fuel injection valve can be prevented, because the inertial mass of the valve needle and the inertial mass of the armature are separated and a cushioning is achieved between them. .

SUMMARY OF THE INVENTION It is an object of the present invention to provide an assembly which enables improved construction and special functions.

An assembly according to the invention with the features of claim 1 has the advantage that improved construction and in particular special functions are possible. By means of the measures presented in the dependent claims, advantageous improvements of the assembly presented in claim 1 are possible.

In implementations of the valve, buffering at the time of closing may be desirable to prevent needle bounce pulses, or undesirable reopening of the sealing seat via a bouncing armature. In this regard, it may also be desirable to partition the mass of the armature and provide a buffer between the individual masses so that a corresponding separation is achieved.

On the other hand, detection of operating points may be desirable or even required for actuation of the fuel injection valve. Precise closing of the valve at any point in time, in particular to compensate for dynamic behavior variations and thus for injection quantity variations and/or to reduce wear and/or noise emissions of the valve by way of re-regulation in the case of a closed valve It is important to know the timing. By re-controlling the closing valve, to some extent a braking pulse can be generated. In this case, detection of the time of closure is usually required to be accurate to a few milliseconds. By means of the detection of the generated armature vibrations in the form of vibrations generated in the coil voltage of the magnetic coil, this can be done here by means of an evaluation of the measured voltage and/or the measured current in a desirable manner without further complex sensor devices.

Accordingly, in a particularly advantageous manner, the respective dynamic behavior of the valve can be taken into account. That is, it has been shown that, for example, the dynamic behavior of fuel injection valves varies from valve to valve and varies with operating conditions and with wear. Significant changes with respect to operating conditions were noted, particularly with regard to temperature, fuel, in particular fuel quality or fuel composition, fuel pressure, combustion chamber pressure and control duration. Changes in dynamic behavior can now be compensated for in a desirable manner, even during operation of the valve and/or over the useful life of the valve.

As a result, the particular characteristics of the valve and, in some cases, the particular difficulties associated with these characteristics can also be taken into account. These characteristics and difficulties apply, for example, to solenoid valves comprising an armature separated from the valve needle in which a so-called armature free path is preset. In this case, in the armature free path, the closing process is not detected as a maximum in the current profile, but as an inflection point in the voltage. In this case, the inflection point occurs by hydraulic sticking of the armature and sudden different accelerations before and after separation from the stop surfaces on the valve needle. However, this targeted detection is problematic, as hydraulic sticking is determined by viscosity. The object of the detection is the fuel, in particular the quality and composition of the fuel, the fuel temperature, and the microgeometry and roughness of the relevant surfaces between the armature and the valve needle. The matching detection is therefore complex, since a particularly complex evaluation and in some cases additional sensor devices are required to reliably and accurately determine the time of closure while taking all of the above influencing variables into account.

With the proposed assembly, a simple evaluation can be carried out in a desirable manner in order to reliably detect the closing point of the valve. The generated armature vibrations can be detected even with small deflections, in particular as micro-movements, directly, for example as vibrations in the measured coil voltage. These oscillations can again be evaluated reliably by simple means, in particular as mechanically excited armature oscillations substantially independent of the medium used, in particular the fluid being metered, and in particular the actual state of said fluid which characterizes its temperature. can be evaluated.

The improvement according to claim 2 has the advantage that a reliable adjustment of the coil voltage is possible, and the magnetic circuit provided for the operation of the armature can be used without substantial structural changes.

The refinement according to claim 3 provides advantageous possibilities for generating armature vibrations. In this case, after the intermittent change of the armature speed, after tilting of the armature due to friction and lateral forces, a uniform acceleration along the guide again can appear. Therefore, it is possible to accurately detect a signal.

In the case of a refinement according to claim 4, a different hydraulic fixation over the circumference can be created or strengthened, whereby armature vibrations can likewise be generated. Preferred possibilities for forming the armature geometry are specified in claims 5, 6 and 7. Accordingly, armature oscillations can be caused by asymmetric stop geometry. In this case, suitable matching is possible by a combination of individual measures and/or by overlapping formation of specific measures at different peripheral positions of the stop geometry.

An improvement according to claim 8 makes it possible in particular to generate a signal without movement of the wobbling type of the armature. As a result, damping of the motion pulses, which occurs in particular when generating a oscillating motion of the armature, can be prevented. Preferred embodiments of such a spring/mass system are given in claims 9 and 10. According to claim 11 , the possibility is presented for exciting the spring/mass system, preferably via a single pulse.

Preferred embodiments of the present invention are described in more detail below with reference to the accompanying drawings and equation (1). Corresponding elements in the drawings are denoted by corresponding reference numerals.

1 is a schematic cross-sectional view showing an assembly including a valve according to a first embodiment of the present invention.
Fig. 2 is a schematic diagram showing an electrical circuit of the assembly shown in Fig. 1 of a first embodiment of the present invention;
Fig. 3 is an excerpted view of an armature guided on a valve needle of the assembly shown in Fig. 1 according to a second embodiment of the present invention in the course of operation;
Fig. 4 shows a stop member disposed on a valve needle of a valve of an assembly according to a third embodiment of the present invention;
5 is a view showing a stop member disposed on a valve needle of a valve of an assembly according to a fourth embodiment of the present invention; FIG.
6 is a view showing a stop member disposed on a valve needle of a valve of an assembly according to a fifth embodiment of the present invention;
7 is a view showing a stop member disposed on a valve needle of a valve of an assembly according to a sixth embodiment of the present invention;
8 is a view showing a stop member disposed on a valve needle of a valve of an assembly according to a seventh embodiment of the present invention;
9 is a view showing a stop member disposed on a valve needle of a valve of an assembly according to an eighth embodiment of the present invention; FIG.
10 is a view showing an armature disposed on a valve needle of a valve of an assembly according to a ninth embodiment of the present invention.
11 is a view showing an armature disposed on a valve needle of a valve of an assembly according to a tenth embodiment of the present invention;
12 is a view showing an armature disposed on a valve needle of a valve of an assembly according to an eleventh embodiment of the present invention.
13 is a view showing an armature disposed on a valve needle of a valve of an assembly according to a twelfth embodiment of the present invention;

1 , an assembly 1 comprising a valve 2 and a measuring device 3 according to a first embodiment is shown in a schematic cross-sectional view in an excerpt. The valve 2 is used for metering a fluid, and can in particular be used as a fuel injection valve 2 for an internal combustion engine. The valve 2 is suitable in principle for liquid and gaseous fluids. The measuring device 3 may be a component of the control device 3 . A preferred application case for the assembly 1 is that a plurality of fuel injection valves 2 , formed according to the valve 2 , are used as high-pressure injection valves 2 and fuel into each assigned combustion chamber 4 of an internal combustion engine. It is a fuel injection system used to directly inject

The valve 2 comprises an actuator 5 , which comprises a magnetic coil 6 , an internal pole 7 and an armature 8 . Upon supply of current to the magnetic coil 6 , the magnetic circuit 9 is closed via the inner pole 7 , whereby actuation of the armature 8 in the opening direction 10 is carried out. In this case, the magnetic circuit 9 is schematically illustrated by closed lines of magnetic force 11 , 12 .

The valve 2 comprises a valve needle 15 and a valve closing body 16 actuable by means of the valve needle 15 . In this case, the valve closing body 16 may also be formed integrally with the valve needle 15 . The valve needle 15 extends through the nozzle body 17 to the valve seat body 18 connected with the nozzle body 17 . A valve seat face 19 is formed on the valve seat body 18 , and the valve closing body 16 interacts with the valve seat face 19 to form a sealing seat. In addition, injection holes 20 and 21 are formed on the valve seat body 18 .

The nozzle body 17 is connected to the housing member 22 . In this case, the magnetic circuit 9 can be closed via the nozzle body 17 and/or the housing element 22 , whereby the nozzle body and the housing element are preferably at least partially made of a suitable material, in particular a ferromagnetic material. is formed with

The magnetic coil 6 is connected to the measuring device 3 via electrical lines 23 , 24 . In this case, depending on the respective embodiment of the assembly 1 , an interface 25 can be provided which enables the connection of the valve 2 and the measuring device 3 , for example via a suitable connector. Of course, it is also possible for the measuring device 3 to be integrated in the valve 2 . In this case, the corresponding measuring signal can be guided, for example, to a separate control device. It is also possible for the functions provided for the measuring device 3 to be realized locally separately.

Accordingly, an embodiment of the assembly 1 also includes a case in which the measuring device 3 is integrated in the valve 2 .

Stop members 30 , 31 are provided on the valve needle 15 , which are fixedly connected with this valve needle 15 and are thus arranged in a fixed position on the valve needle 15 . The stop member 30 includes a stop surface 32 . The stop member 31 comprises a stop face 33 . End faces 34 , 35 are formed on the armature 8 . In addition, the armature 8 is a through formed such that, in this embodiment, the armature 8 is guided on the valve needle 15 with a predetermined play that allows tilting of the armature 8 with respect to the longitudinal axis 37 of the valve needle. and a bore 36 . Between the stop surfaces 32 , 33 the armature 8 is cantilever supported in the present embodiment. In this case, the armature 8 is urged by a spring 38 in a direction opposite to the opening direction 10 to the starting position shown in FIG. 1 . In the starting position, the end face 35 of the armature 8 abuts the stop face 33 . Also provided is a return spring 39 that biases the valve needle 15 to the starting position shown in FIG. 1 in which the sealing seat between the valve closing body 16 and the valve seat face 19 is closed.

When current is supplied to the magnetic coil 6 , an opening force is applied to the armature 8 via the magnetic circuit 9 , whereby the armature 8 first passes through the armature free path 40 while the sealing sheet still remain closed. Following this, the armature 8 strikes on the stop face 32 of the stop member 30 , whereby an opening pulse is transmitted to the valve needle 15 and the sealing seat is opened. As a result, fuel is injected from the inner chamber 41 through the injection holes 20 and 21 into the combustion chamber 4 .

The opening movement of the armature 8 is limited by a stop face 42 on the inner pole 7 . If the armature 8 hits the stop face 42 , a certain oscillation of the valve needle 15 can still occur in the opening direction 10 and in the opposite direction.

Closing of the valve 2 is performed when the magnetic coil 6 is switched to the current-free state. The reason is that in this case the return spring 39 and the stop member 30 cause the return of the armature 8 as well as the valve needle 15 . As soon as the valve closing body 16 hits the valve seat face 19 when the armature and valve needle are retracted, the armature 8 is disengaged from the stop face 32 and then the stop face of the stop member 31 ( 33) is moved.

In this embodiment, for the stop face 32 of the stop member 30 , an angle 43 , which may be referred to as an inclination angle or an inclination angle 43 , is preset. The stop surface 32 is formed planar in this embodiment, and the normal vector 57 ( FIG. 6 ) of the stop surface 32 forms an angle 43 with the longitudinal axis 37 .

If the end face 34 of the armature 8 abuts planarly on the stop face 32 , then the tilt of the armature 8 by an angle 43 with respect to the longitudinal axis 37 , or its starting position shown in FIG. 1 . This happens. Therefore, due to the dynamic behavior of the valve 2 , a tilting or swinging motion of the armature 8 occurs after closing of the valve 2 . This changes the working gap 44 between the armature 8 and the inner pole 7 .

In Fig. 2 there is shown a schematic diagram of an electrical circuit 50 of the assembly shown in Fig. 1 in a first embodiment. In this case, the measuring device 3 and the magnetic circuit 9 are included in the electric circuit 50 . In the idealized figure, the working gap 44 may be represented as a working air gap having a length x. In this case, the influence of the medium in the working gap 44 can be taken into account by means of a corresponding variable, in particular a multiplication factor for the length x. Here the magnetic circuit 9 is characterized by a length l. Also presented is a cross-section A characterizing the magnetic circuit 9 . Also, the magnetic permeability (μ _R ) is presented. In the magnetic circuit 9 , a magnetic flux ? is generated from the current i flowing through the magnetic coil 6 . In this case, the magnetic coil 6 is also used as a measuring coil, and the current i also includes a measuring signal. The current i arises from the voltage U _n applied to the n windings of the magnetic coil 6 , which voltage is, according to the model, a decreasing voltage U _R in the ohmic resistance R and the magnetic coil 6 ) is divided by the decreasing voltage (U _i ) at the inductive resistance.

For example, the voltage U _n detected as a measurement signal by the measurement device 3 can be expressed according to equation (1). To close the valve 2 , for example, starting from a holding current level which appears at a voltage U _n , eg of 60 V applied to the magnetic coil, the current i is rapidly dissipated and then the current i = 0 is applied. can be Then, in the phase of the current supply, via the terminal voltage U _n , in particular the armature speed of the armature 8 , or the amount of change in the working gap 44 between the armature 8 and the inner pole 7 , is to be measured. can In this case, as shown in Equation (1), the voltage drop (U _R = Ri) approaches almost zero. And the amount of change of current also approaches almost zero after rapid current dissipation and application of current (i = 0), whereby the time derivative of current i is at least almost extinct. Accordingly, on the right side of the equation shown in Equation (1), only the third term remains, which is determined by the amount of change in the length x of the working gap 44 with respect to time t.

In this phase, that is to say, when a current i=0 is applied, closing of the valve 2 is also carried out, wherein the valve closing body 16 strikes the valve seat face 19 and the armature 8 first It continues to fly as a separate mass. By means of the structural measures described according to FIG. 1 , for example in which the armature 8 is tilted, a modulation of the armature speed or a modulation of the length x appears. This modulation results in a relatively higher order quotient, ie a non-constant velocity term (dx/dt). The non-uniform armature velocity during valve closure may represent an abrupt amount of change repeated by the average value of the oscillations, or other relatively higher order fluctuations. Accordingly, the modulation differs from the normal effects on the armature motion caused by the springs 38 , 39 or by the flow resistance. Modulation of the armature speed can be detected directly as oscillations in the measured current (i) or the measured voltage (U _n ) even with very small deflections, especially micro-motion. Thus, the oscillations of the armature speed can be evaluated reliably by simple means and in particular as armature oscillations that are mechanically excited, irrespective of the medium used and the actual state of the medium, for example the temperature of the medium. .

The generation of the armature vibrations described according to FIG. 1 can also be carried out in other ways. The generation of mechanical armature vibrations of the armature 8 during closing can therefore be carried out in different ways, further possibilities are described in detail below. The measures described may be realized individually or in combination.

3 shows an excerpted view of the armature 8 guided on the valve needle 15 of the valve 2 of the assembly 1 shown in FIG. 1 according to a second embodiment in the course of operation. In this embodiment, an inclination of the stop face 33 of the stop member 31 with respect to the longitudinal axis 37 is provided. Thus, during the closing process, when the end face 35 of the armature 8 collides with the stop face 33 , a tilting of the armature 8 followed by a tilting or wobbling motion of the armature 8 occurs. In this case, a certain rebound of the armature 8 in the opening direction 10 can also be carried out.

Accordingly, the vibration of the armature 8 is tilted around the guide according to each embodiment, the armature 8 being separated from the stop surfaces 32 and 33 on the valve needle 15 on one side as intended and on the guide. It can be created in a slightly twisted manner. Then, the armature 8 is delayed and separated also on the opposite side and tilted in the other direction. As a result, the armature speed fluctuates intermittently until the armature 8 has a uniform acceleration along the guide or comes to rest due to friction and lateral forces. In this case, the embodiments described according to FIGS. 1 and 3 of suitable stop surfaces 32 , 33 can also be realized in combination, and tilting of the armature 8 in the opposite direction is also possible.

Said behavior can also be created or enhanced by different hydraulic fixings across the circumference. Embodiments in this regard are exemplarily described below according to FIGS. 4 to 9 . In this case, the above embodiments can be realized individually or in combination on the stop member 30 and/or on the stop member 31 . 4 , there is shown a stop member 30 , 31 arranged on the valve needle 15 of the valve 2 of the assembly 1 according to a third embodiment. In this case, radial grooves 55 are formed on the stop surfaces 32 , 33 . The stop surfaces 32 , 33 are thus realized non-planar and asymmetrically conical.

In this case, the groove 55 is a possible configuration of the recess 55 . In this case, a plurality of recesses 55 , in particular radial grooves 55 , may be provided. Furthermore, the groove 55 may extend in another way, ie in a non-radial direction.

5, stop members 30 and 31 corresponding to a fourth embodiment are shown. In this embodiment, a slope 56 is formed on the stop surfaces 32 , 33 . As a result, the stop surfaces 32 and 33 are partially inclined.

6 , stop elements 30 , 31 corresponding to a fifth embodiment are shown. In this embodiment, the stop surfaces 32, 33 are tilted with respect to the longitudinal axis 37, so that the normal vector 57 of the stop faces 32, 33 is the tilt angle or tilt angle ( 43) to form an angle 43. This corresponds to a situation as described according to FIG. 1 or FIG. 3 .

7, stop members 30 and 31 corresponding to the sixth embodiment are shown. In this embodiment, a step 58 is provided on the stop surfaces 32 , 33 .

8, stop members 30 and 31 corresponding to the seventh embodiment are shown. In this embodiment, the stop surfaces 32 , 33 comprise a non-circular rim 59 . Particularly in the case of this embodiment, the projection 60 is provided on the stop surfaces 32 , 33 .

In Fig. 9, stop members 30, 31 corresponding to the eighth embodiment are shown. In the case of this embodiment, a depression 61 is provided here realized by a straight section 61 on the rim 59 .

In the case of the embodiments described according to FIGS. 8 and 9 , the geometry of the rim 59 is based on a correspondingly deformed circular rim. However, other geometries for the rim 59 may be realized.

In addition, different microstructures and roughnesses can also be realized on the stop surfaces 32 , 33 in order to realize hydraulic properties different from the configuration of radial symmetry, in particular hydraulic fixing properties. As a result, depending on the respective embodiment of the valve 2 , vibration of the armature 8 can be caused or intensified.

The rotationally asymmetric geometry of the stop surfaces 32 , 33 is therefore, in a preferred manner, causing a mechanical vibration of the armature 8 which results in a change in the length x of the working gap 44 of a relatively higher order. Structures may be realized. In particular, variations in the length x of a second or higher order than the second order can be achieved.

10 shows an armature 8 arranged on a valve needle 15 of a valve 2 of an assembly 1 corresponding to a ninth embodiment. In this embodiment, the armature 8 and the valve needle 15 are formed correspondingly to a system comprising two masses 64 , 65 connected via a spring member 63 . In this case, the armature 8 is fixedly connected to the valve needle 15 . The valve needle 15 is divided into a first needle section 66 and a second needle section 67 in this embodiment. The needle sections 66 , 67 are connected to each other via a connecting sleeve 68 . The armature 8 is in fixed connection with the first needle section 66 . The first needle section (66) is formed to enable oscillation of the elastic mechanical structure along the longitudinal axis (37). In this case, it should be noted that the first needle section 66 contributes not only to the realization of the spring member 63 according to the model, but also partially to the realization of the mass 64 . When the valve closing body 16 hits the valve seat face 19 when it is closed, vibration of the armature 8 occurs inside the spring/mass system 62 . In this case, suitable matching is possible.

The oscillation of the armature 8 or the system 62 comprising masses which continue to move upon and after closing may be carried out about itself, ie about the center of gravity of the system 62 . In order for the vibration to produce a measurable rate of change in the axial magnetic actuation gap 44 , the center of gravity should be positioned as far away from the effective end face 34 of the armature 8 as possible, the vibrating system 62 . The natural frequency shall not exceed 50 kHz. This means that, in the case of an outwardly open valve which requires a corresponding deformation of the internally open valve 2 shown in FIG. 1 , the armature 8 first continues to move as an elastically oscillating mass after closing the valve. This can be achieved by being in fixed connection with the needle section 63 which causes an elastic mechanical structural vibration of the needle section 66 .

11 shows an armature 8 arranged on a valve needle 15 of a valve 2 of an assembly 1 corresponding to a tenth embodiment. In the case of this embodiment, the armature 8 is arranged on the valve needle 15 as a flying armature 8 . The armature 8 of the internally or externally open valve 2 is in this embodiment a first armature member 69 and a second armature member 70 and an elastic provided between the armature members 69, 70 made up of polymers. The first armature member 69 is a first mass 64 of the system 62 , which is formed by a second armature member 70 via an elastomer 61 used as a spring 63 . It is connected to the second mass 65 that becomes of vibration of the spring/mass system 62 when the armature 8 strikes the stop surfaces 32 , 33 or when the armature 8 disengages from the stop surfaces 32 , 33 of the stop members 30 , 31 . Here it happens.

Furthermore, the armature members 69 , 70 can be connected to each other via a spring 63 , in particular a helical spring member 63 , formed in a different way.

12 shows an armature 8 arranged on a valve needle 15 of a valve 2 of an assembly 1 corresponding to an eleventh embodiment. In the case of this embodiment, the armature 8 is arranged as a floating armature 8 on the first needle section 66 . Therefore, instead of the mass body 64 as shown in Fig. 10, division is realized into two mass bodies 64A and 64B. In this case, the mass 64B is braked by intermittent contact with at least one other mass 64A. In the case of this embodiment, the first needle section 66 strikes the armature 8 and thus causes intermittent armature motion. Thereby, vibration of the multi-member system 62 including masses 64A, 64B that are not fixedly connected and that are still floating can be realized.

13 shows an armature 8 arranged on a valve needle 15 of a valve 2 of an assembly 1 corresponding to a twelfth embodiment. In the case of this embodiment, the armature 8 is arranged on the valve needle 15 as a floating armature 8 . The armature 8 is, in this embodiment, at least one recess 73 , 74 , and at least one fixed in this at least one recess 73 , 74 along the valve needle 15 with play along the valve needle 15 . and a body (72) having a body (75, 76) of In this case, the armature vibration is generated through the collision of the body 72 of the armature 8 itself and the bodies 75 and 76 fixed with play. The fixing of the bodies 75 , 76 is realized in this embodiment by means of a plate connected to the body 72 , for example the plate welded to the body 72 .

Accordingly, by means of structural measures, a magnetic valve 2 comprising a plurality of movable masses 64 , 65 can be realized, which generates or amplifies a signal to be easily detected in the voltage profile, said Through the signal, the closing time of the valve 2 can be detected simply and accurately. In this case, at least substantial independence from the fuel used, in particular the quality and composition of the fuel, the fuel temperature and the ambient temperature is achieved. This enables reliable and simple implementation. This also enables a wide range of use. In particular, the armature 8 can be formed as a plate-shaped or plunger-shaped armature 8 . A preferred use is for injection of gasoline.

The invention is not limited to the described embodiments.

1: Assembly
2: valve
3: Measuring device
4: combustion chamber
5: Actuator
6: Magnetic coil
7: inner pole
8: Armature
9: Magnetic circuit
10: open direction
11: magnetic field lines
12: magnetic field lines
15: valve needle
16: valve closing body
17: nozzle body
18: valve seat body
19: valve seat surface
20: injection hole
21: injection hole
23: electric line
24: electric line
25: interface
30: stop member
31: stop member
32: stop surface
33: stop surface
34: end face
35: end face
36: through bore
37: breeder
38: spring
39: return spring
40: armature free path
41: inner chamber
42: stop surface
43: angle, tilt or tilt angle
44: working clearance
50: electrical circuit
55: groove, recess
56: inclined part
57: normal vector
58: step part
59: border
60: protrusion
61: depression, straight section
62: spring/mass system
63: spring member, spring, spiral spring member
64: first mass
65: second mass
66: first needle section
67: second needle section
68: connecting sleeve
69: first armature member
70: second armature member
71: elastomer
72: body
73: recess
74: recess
75: body
76: body

Claims (11)

An assembly (1) comprising a valve (2) for metering a fluid, said valve (2) comprising an electromagnetic actuator (5) and a valve needle (15) actuable by said actuator (5) , the electromagnetic actuator (5) comprises a magnetic coil (6) and an armature (8) disposed on the valve needle (15) and capable of being actuated by the magnetic coil (6) in the course of operation, the valve A needle (15) is used to actuate a valve closure body (16) which interacts with a valve seat surface (19) to form a sealing seat, provided with at least one stop surface (32, 33), said stop surface (32, 33) being provided At (32, 33) the armature (8) strikes in the course of operation, in the assembly,
A measuring device (3) is provided in electrical connection with the magnetic coil (6) at least in the course of operation, the armature (8) and/or the stop surfaces (32, 33) and/or the valve needle (15) being actuated It is formed so that the armature vibration of the armature 8 is generated after closing of the sealing sheet in the process, and the measuring device 3 is configured to measure the armature vibration generated after closing of the sealing sheet in the operation process to the magnetic coil 6 Formed to detect in the form of vibrations generated from the coil voltage (U _n ) of
The armature (8) is disposed on the valve needle (15) so as to enable tilting of the armature (8) with respect to the valve needle (15), the armature (8) and the stop surfaces (32, 33) ), which is configured to tilt relative to the valve needle (15) when the armature (8) hits or separates from the stop surface (32, 33). The armature (8) and the inner pole (7) of the electromagnetic actuator (5) according to claim 1, wherein the vibration produced in the coil voltage (U _n ) of the magnetic coil (6) is caused by armature vibration. at least substantially created by a change in the working clearance (44) of delete 3. The armature (8) according to claim 1 or 2, wherein the end face (34, 35) and/or the stop face (32, 33) of the armature (8) is such that the stop face (32, 33) of the armature (8) is configured. Assembly characterized in that in the region impinging on it, it is formed with a stop geometry which is rotationally asymmetric with respect to the longitudinal axis (37). 5. A stop geometry according to claim 4, wherein the stop geometry of the end face (34, 35) of the armature (8) or the stop geometry of the stop face (32, 33) is at least one recess (55) and/or Assembly characterized in that it comprises at least one groove (55) and/or at least one radial groove (55) and/or at least one step (58) and/or at least one slope (56). Assembly according to claim 4, characterized in that the stop geometry on the armature (8) or the stop surface (32, 33) comprises a non-circular rim (59). 7. The armature (8) or the stop geometry on the stop surface (32, 33) according to claim 6, characterized in that at least one protrusion (60) and/or at least one depression (60) on the rim (59). 61) and/or at least one substantially straight section (61). System ( 62), characterized in that the assembly is formed. 9. The armature (8) according to claim 8, comprising a first mass (64) in the form of a first armature member (69) and at least one second mass (65) in the form of a second armature member (70); , the second mass 65 and the first in the form of an elastic polymer 71 and/or a helical spring member 63 provided between the first armature member 69 and the second armature member 70 . An assembly comprising a spring (63) connecting the mass (64). 3. The valve needle (15) according to claim 1 or 2, wherein the valve needle (15) comprises a first needle section (66) and a second needle section (67) in which the armature (8) is arranged in a fixed or floating manner. and the first needle section (66) and the second needle section (67) are connected to each other, and the first needle section (66) is formed to enable an elastic mechanical structural vibration. 3. The armature (8) according to claim 1 or 2, wherein the armature (8) has at least one recess (73, 74) and play along the valve needle (15) in the at least one recess (73, 74). assembly comprising a body (72) having at least one body (75, 76) secured thereto.

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