阅读说明：本技术 用于计量流体的阀 (Valve for metering a fluid ) 是由 S·塞尔尼 M·乌恰尔 J·罗泽 A·格拉泽 M·伯尔 A·海因施泰因 N·赫尔曼 M 于 2018-05-03 设计创作，主要内容包括：本发明涉及一种用于计量流体的阀(1),尤其是用于内燃机的燃料喷射阀,所述阀具有电磁促动器(10),所述电磁促动器具有布置在衔铁室(16)中的衔铁(6),并且具有被所述促动器(10)借助所述衔铁(6)能够操纵的阀针(5),其中,所述衔铁(6)在所述阀针(5)上被导向,其中,在所述阀针(5)上布置有在运行中与所述衔铁(6)的第一端侧(22)共同作用的第一止挡元件(7)和在运行中与所述衔铁(6)的第二端侧(23)共同作用的第二止挡元件(8),所述第一止挡元件和第二止挡元件限制所述衔铁(6)相对于所述阀针(5)的运动,并且其中,所述衔铁(6)具有朝向所述衔铁(6)的第一端侧(22)敞开的弹簧接收部(25),在所述弹簧接收部中放入支撑在所述止挡元件(7)上的弹簧(27)。所述阀(1)在此这样地构型,使得所述衔铁(6)具有至少一个流体通道(15),所述流体通道能够在运行中实现引导流体在所述衔铁室(16)的邻接到所述衔铁(6)的第一端侧(22)上的第一区域(17)和所述衔铁室(16)的邻接到所述衔铁(6)的所述第二端侧(23)上的第二区域(18)之间通过,所述流体通道(15)至少部分地包含所述弹簧接收部(25)并且所述流体通道(15)沿着从所述第一端侧(22)朝向所述第二端侧(23)取向并且相对于纵轴线(4)的同轴方向(19)至少区段地径向向外延伸。(The invention relates to a valve (1) for metering a fluid, in particular a fuel injection valve for an internal combustion engine, having an electromagnetic actuator (10) having an armature (6) arranged in an armature chamber (16) and having a valve needle (5) which can be actuated by the actuator (10) by means of the armature (6), wherein the armature (6) is guided on the valve needle (5), wherein a first stop element (7) which interacts in operation with a first end face (22) of the armature (6) and a second stop element (8) which interacts in operation with a second end face (23) of the armature (6) are arranged on the valve needle (5), wherein the first and second stop elements limit a movement of the armature (6) relative to the valve needle (5), the armature (6) has a spring receptacle (25) which is open toward a first end face (22) of the armature (6) and in which a spring (27) supported on the stop element (7) is inserted. The valve (1) is designed in such a way that the armature (6) has at least one fluid channel (15) which, during operation, enables a fluid to be conducted between a first region (17) of the armature chamber (16) adjoining a first end face (22) of the armature (6) and a second region (18) of the armature chamber (16) adjoining a second end face (23) of the armature (6), the fluid channel (15) at least partially containing the spring receptacle (25) and the fluid channel (15) extending radially outward at least in sections in a coaxial direction (19) from the first end face (22) to the second end face (23) and relative to the longitudinal axis (4).)

1. A valve (1) for metering a fluid, in particular a fuel injection valve for an internal combustion engine, having an electromagnetic actuator (10) having an armature (6) arranged in an armature chamber (16) and having a valve needle (5) which can be actuated by the actuator (10) by means of the armature (6), wherein the armature (6) is guided on the valve needle (5), wherein a first stop element (7) which interacts in operation with a first end face (22) of the armature (6) and a second stop element (8) which interacts in operation with a second end face (23) of the armature (6) are arranged on the valve needle (5), which limit a movement of the armature (6) relative to the valve needle (5), and wherein the armature (6) has a spring receptacle(s) (10) which is open toward the first end face (22) of the armature (6) 25) A spring (27) supported on the stop element (7) is inserted into the spring receptacle,

it is characterized in that the preparation method is characterized in that,

the armature (6) has at least one fluid channel (15) which, during operation, enables a fluid to be conducted between a first region (17) of the armature chamber (16) adjoining a first end face (22) of the armature (6) and a second region (18) of the armature chamber (16) adjoining a second end face (23) of the armature (6), the fluid channel (15) at least partially containing the spring receptacle (25) and the fluid channel (15) extending radially outward at least in sections along a coaxial direction (19) from the first end face (22) to the second end face (23) and relative to the longitudinal axis (4).

2. The valve as set forth in claim 1, wherein,

it is characterized in that the preparation method is characterized in that,

the point (61) of the first opening (55) of the fluid channel (15) which is disposed furthest in the radial direction from the longitudinal axis (4) is closer to the longitudinal axis (4) than the point (63) of the second opening (56) of the fluid channel (15) which is disposed furthest in the radial direction from the longitudinal axis (4).

3. The valve according to claim 1 or 2,

it is characterized in that the preparation method is characterized in that,

the fluid channel (15) protrudes on an outlet surface (80) of the armature (6) toward the second region (18) of the armature chamber (16) and an axis (81) of the fluid channel (15) is oriented perpendicular to the outlet surface (80), along which axis the fluid channel (15) protrudes on the outlet surface (80) of the armature (6).

4. The valve according to any one of claims 1 to 3,

it is characterized in that the preparation method is characterized in that,

the outlet surface (80) is located in an annular surface (82) that surrounds the longitudinal axis (4) and the annular surface (82) is formed as a partial surface (82) of a conical outer circumferential surface (83) that is rotationally symmetrical relative to the longitudinal axis (4) or as a partial surface (82) of a disk (84) that is oriented perpendicular to the longitudinal axis (4).

5. The valve according to any one of claims 1 to 4,

it is characterized in that the preparation method is characterized in that,

the fluid channel (15) extends continuously radially outwards along the coaxial direction (19).

6. The valve according to any one of claims 1 to 5,

it is characterized in that the preparation method is characterized in that,

the fluid channel (15) has at least one inclined bore (50) extending at least radially outwards along the coaxial direction (19).

7. The valve as set forth in claim 6,

it is characterized in that the preparation method is characterized in that,

the inclined bore (50) extends from a first end side (22) of the armature (6) to a second end side (23) of the armature (6).

8. The valve according to claim 6 or 7,

it is characterized in that the preparation method is characterized in that,

the inclined hole (50) intersects the spring receiving portion (25).

9. The valve according to any one of claims 1 to 8,

it is characterized in that the preparation method is characterized in that,

the inclined hole (50) and the spring receiving part (25) intersect in such a way that a bottom (26) of the spring receiving part (25) is cut open by the inclined hole (50).

10. The valve according to any one of claims 1 to 9,

it is characterized in that the preparation method is characterized in that,

the fluid channel (15) has a first coaxial blind hole (71) which extends from a first end face (22) of the armature (6) in the coaxial direction (19) and a second coaxial blind hole (72) which extends from a second end face (23) of the armature (6) counter to the coaxial direction (19), said blind holes intersecting in the armature (6), and the second blind hole (72) being located radially further to the outside than the first blind hole (71) with respect to the longitudinal axis (4).

Technical Field

The invention relates to a valve for metering a fluid, in particular a fuel injection valve for an internal combustion engine. The invention relates in particular to the field of injectors for motor vehicle fuel injection systems, in which fuel is preferably injected directly into the combustion chamber of an internal combustion engine.

Background

DE 102013222613 a1 discloses a valve for metering a fluid. The known valve has an electromagnet for operating a valve needle controlling the metering opening. The electromagnet is used to actuate an armature which can be moved on the valve needle. The armature has a bore adjoining the valve needle, which forms a spring receptacle for a pre-lift spring (vorubretainer).

Disclosure of Invention

The valve according to the invention with the features of claim 1 has the following advantages: improved configuration and operation can be achieved. In this case, improved guidance between the armature and the valve needle, in particular damping and stabilization of the armature, and at the same time advantageous guidance of the fluid through the armature chamber can be achieved.

Advantageous embodiments of the valve specified in claim 1 can be achieved by the measures specified in the dependent claims.

In valves for metering fluids, the armature, which acts as an electromagnet, is not fixedly connected to the valve needle, but rather is mounted movably between stops. Such a stop can be formed on a stop element, which can be realized as a stop sleeve and/or as a stop ring. However, the stop element can also be formed integrally with the valve needle. In the rest state, the armature is adjusted via a spring to a stop which is fixed in position relative to the valve needle, so that the armature rests there. Then, when the valve needle is actuated, the entire free travel of the armature can be used as an acceleration section, wherein the spring is shortened during the acceleration. The free travel of the armature can be predetermined by an axial play between the armature and the two stops.

The guide length between the armature and the valve needle can be increased by: the spring receiving portion is configured by an annular groove that does not abut on the valve needle. In this case, the spring receptacle can still be advantageously formed close to the longitudinal axis, i.e. at a small radial distance from the longitudinal axis, in order to be able to achieve an advantageous introduction of fluid from the first region of the armature chamber into the spring receptacle with a corresponding formation of the valve.

In the combination of an armature having a through-flow opening and a stop arranged on the valve needle and having a large outer diameter, it is conceivable to: an overlap occurs between the throughflow holes and a stop surface (stop) formed on the respective stop element. As a result, a part of the damping surface between the armature and the stop element associated therewith is lost. Furthermore, the free flow cross section is also reduced at the stop element in the region of the end position of the armature.

The resulting situation, while having the advantage of a low adhesion effect during actuation when the armature is disengaged from the respective stop element, also results in a reduction of the damping required for damping a crash or for stabilizing the armature. Specifically, when the valve is closed, this can result in an excessively long time being required for the armature to be sufficiently stable in terms of the desired actuation time. Therefore, the through-flow opening through the armature, which is close to the valve needle configuration, has a significant disadvantage in terms of a pause time which can be very short, for example less than 1.2ms, as can be desirable in the case of multiple injections.

The proposed fluid channel advantageously enables a fluid to be guided through the armature chamber and at the same time reduces the impairment of the damping behavior, which is advantageous in particular for the stabilization of the armature when the valve is closed. The desired damping can thus also be predetermined or adjusted by the design of the stop surface on the stop element in such a way that the fluid is guided through the armature without being influenced at least to a large extent.

In one embodiment, the point of the first opening of the fluid channel which is furthest radially outside the longitudinal axis is closer to the longitudinal axis than the point of the second opening of the fluid channel which is furthest radially outside the longitudinal axis, which has the following advantages: in an advantageous manner, the fluid can be introduced into the fluid channel close to the longitudinal axis on the first end side of the armature, while the opening of the fluid channel can be displaced into a region further away from the valve needle on the second end side of the armature. The following advantages are achieved in particular in the embodiment according to claim 2: the overlap of the opening of the fluid channel on the second end side of the armature with the stop surface on the second stop element can be reduced or completely avoided. In particular, the point of the fluid channel which is disposed furthest inside the second opening can be located radially in the stop surface of the second stop element. A corresponding advantage can be achieved in this embodiment in that the center of gravity of the area of the first opening of the fluid channel is closer to the longitudinal axis than the center of gravity of the area of the second opening of the fluid channel.

Furthermore, the embodiment according to claim 3 has the following advantages: the manufacturability of the fluid channel can be achieved or improved by means of the holes. Advantageous measures for this are given in claim 4.

The embodiment according to claim 5 has the following advantages: on the one hand, a fluidically advantageous configuration of the fluid channel can be achieved. On the other hand, if necessary, a production-technically advantageous configuration of the fluid channel can be achieved, as is possible in particular according to the embodiment of claim 6. In this case, according to the embodiment of claim 7, an optimization with respect to the angle of inclination, at which the axis of the inclined bore is inclined relative to the longitudinal axis, can be advantageously achieved, wherein the angle of inclination can be kept optimally small, for example given the provisions for the opening on the second end side of the armature. The cross section available for the fluid to be conducted can thereby also be increased along the coaxial direction over the entire path through the armature due to the configuration of the inclined bore, if this is relevant in the case of the respective application.

In the embodiment according to claim 8, the remaining space, which may be left when the spring (armature free-stroke spring) is inserted, can advantageously be used together for guiding the fluid. In this case, the embodiment according to claim 9 makes it possible in particular to use the spring receptacle along its entire extent along the longitudinal axis.

In the embodiment according to claim 10, the fluid channel can be advantageously formed by a coaxial blind hole to be realized simply in terms of manufacturing technology.

In an advantageous manner, a combination of an armature free-travel spring in an armature having a radially outwardly extending fluid channel, in particular an inclined bore, and an armature can thus be realized. This combination makes it possible to achieve a maximum damping surface between the stop element and the armature. In this case, a reduction of the damping surface due to an overlap with the respective opening can be avoided exclusively. Since a plurality of fluid channels are preferably provided in the design of the valve, which fluid channels are preferably realized in place of conventional through-openings, a significant influence on the operating mode of the valve, in particular a significantly improved damping, can be achieved. For example, two to ten fluid channels, in particular two to six fluid channels, can be realized. Here, such fluid channels may at least partially jointly contain a spring receptacle. This also improves the throughflow performance. In principle, however, it is also possible to consider a combination with only one fluid channel or with at least one proposed fluid channel with at least one conventional through-opening.

In particular, it is thus possible to realize a configuration in which, in respect of the stop face on the associated stop element, no overlap occurs between the associated opening or openings of the at least one fluid channel and the stop face on the stop element. Thereby providing a maximum damping surface.

Drawings

In the following description preferred embodiments of the invention are explained in detail with reference to the drawings, in which corresponding elements are provided with corresponding reference numerals. The figures show:

fig. 1 is a schematic cross-sectional view of a part of a valve corresponding to the first embodiment;

FIG. 2 corresponds to a schematic cross-sectional view of a portion of a valve of a second embodiment;

FIG. 3 is a schematic cross-sectional view of a portion of a valve corresponding to a third embodiment; and

fig. 4 corresponds to a schematic sectional view of a part of a valve of a fourth embodiment.

Detailed Description

Fig. 1 shows a valve 1 for metering a fluid according to a first exemplary embodiment in a partially schematic sectional illustration. The valve 1 can be designed in particular as a fuel injection valve 1. A preferred application is a fuel injection system in which such a fuel injection valve 1 is designed as a high-pressure injection valve 1 and is used to inject fuel directly into an associated combustion chamber of an internal combustion engine. Liquid or gaseous fuels can be used as fuel. Accordingly, the valve 1 is suitable for metering liquid or gaseous fluids.

The valve 1 has a housing (valve housing) 2 in which an inner pole 3 is arranged in a stationary manner. In this exemplary embodiment, the valve needle 5 arranged in the housing 2 is guided along the longitudinal axis 4 relative to the housing 2.

An armature (magnetic armature) 6 is arranged on the valve needle 5. Furthermore, a stop element 7 and a further stop element 8 are arranged on the valve needle 5. Stop surfaces 7',8' are formed on the stop elements 7, 8. When actuated, the armature 6 is moved along the longitudinal axis 4 relative to the valve needle 5 between the stop elements 7,8, wherein the armature free travel 9 is predetermined. The longitudinal axis 4 may be referred to herein as the longitudinal axis 4 of the valve needle 5 or the longitudinal axis 4 of the armature 5. The armature 6, the inner pole 3 and a not shown electromagnetic coil are components of the electromagnetic actuator 10. Valve closing body 11 is formed on valve needle 5, which valve closing body cooperates with valve seat surface 12 to form a sealing seat. When the armature 6 is actuated, it is accelerated in the direction of the inner pole 3. When the armature 6 comes to rest against the stop 7' of the stop element 7 and the valve needle 5 is actuated as a result, fuel can be injected into a chamber, in particular a combustion chamber, via the open sealing seat and the at least one nozzle opening 13.

The valve 1 has a return spring 14, which displaces the valve needle 5 by means of the stop element 7 into its initial position, in which the sealing seat is closed.

The armature 6 is based on a cylindrical basic shape 20 with a through-opening 21, wherein the armature 6 is guided on the valve needle 5 at the through-opening 21. The basic shape 20 of the armature 6 has a length 24 between a first end side 22 of the armature 6 facing the inner pole 3 and a second end side 23 of the armature 6 facing away from the inner pole 3. The armature 6 is arranged in the armature chamber 16. The first end side 22 adjoins the first region 17 of the armature chamber 16. Furthermore, the second end side 23 adjoins the second region 18 of the armature chamber 16. In operation, fuel can be conducted through the armature over at least a portion of the armature length 24 via at least one fluid channel 15.

The armature 6 has a spring receiving portion 25. Here, the fluid channel 15 contains a spring receiving portion 25. Thus, the fluid channel 15 is guided at least via a portion of the spring receptacle 25. The spring receptacle 25 is open on the end side 22 of the armature 6. The spring support surface 26 is formed by the base 26 of the spring receptacle 25, on which the spring 27 is supported, which is arranged partially in the spring receptacle 25. Furthermore, the spring 27 is also supported on the stop face 7' of the stop 7. When the armature 6 is actuated, the spring 27 is shortened relative to its initial length, wherein it can be completely inserted into the spring receptacle 25.

In addition, in this exemplary embodiment, the spring 27 is also formed with ground spring ends 43, 44. Thereby also obtaining a better support. Furthermore, reduced wear and a more uniform introduction of force into the magnet armature 6 are achieved on the one hand at the spring support surface 26 and on the other hand at the stop 7' of the stop element 7.

In this exemplary embodiment, a guide projection 28 is formed on the armature 6. The guide length of the armature 6 on the valve needle 5 is thus equal to the length 24 of the armature 6 between its end sides 22, 23.

In this exemplary embodiment, the guidance of the valve needle 5 relative to the longitudinal axis 4 or relative to the housing 2 is produced by means of a stop element 7. The stop element 7 is guided in the guide region 30 at an inner bore 31 of the inner pole 3. In a modified embodiment, the guidance of the valve needle 5 can additionally or alternatively also be achieved by the armature 6. The outer side 32 of the armature 6 reaches at least partially on the inner side 33 of the housing 2. In this configuration, instead of the guide region 30, an annular gap can be realized between the stop element 7 and the inner pole 3.

In this embodiment, the fluid passage 15 has an inclined hole 50. In this case, the fluid channel 15 preferably has exactly one inclined opening 50. The fluid channel 15 is guided via the inclined bore 50 and at least a portion 51 of the spring receiving portion 25.

In this exemplary embodiment, a direction 19 coaxial to longitudinal axis 4 is produced in an opposite orientation to opening direction 52, in which valve needle 5 is actuated when valve 1 is open, which direction is oriented from first end side 22 toward second end side 23.

The angled bore 50 is formed in the armature 6 in such a way that it extends radially outward along the coaxial direction 19, i.e. away from the longitudinal axis 4, wherein an angle of inclination 54 is produced in the plane of the drawing between the coaxial direction 19 and an axis 53 of the angled bore 50. However, the configuration of the inclined bore 50 is not limited to the axis 53 lying in the same plane as the longitudinal axis 4 of the valve needle 5, as is the case in the embodiment shown with the plane given by the plane of the drawing.

Furthermore, in this embodiment, the inclined bore 50 also extends from the first end side 22 of the armature 6 to the second end side 23 of the armature 6. In this case, a first opening 55 of the fluid channel 15 adjoining the first region 17 is located in the end side 22, while a second opening 56 adjoining the second region 18 is located in the second end side 23. An advantageous hydraulic connection between the first region 17 and the second region 18 can be achieved by an inclined bore 50 which extends from the first end side 22 to the second end side 23 of the armature 6. The positioning of the first opening 55 close to the longitudinal axis 4 can be used to achieve an advantageous flow of fluid, in particular fuel, from the inner bore 31 of the inner pole 3 into the fluid channel 15. Due to the arrangement of the second opening 56 of the fluid channel 15 away from the axis relative to the longitudinal axis 4, the inner part 57 of the second end face 23, on which the armature 6 interacts with the second stop surface 8', is sufficiently large in correspondence with the predetermined, possibly large, second stop surface 8', while the second opening 56 is not located in this inner part 57 or the fluid channel 15 does not cut through this inner part 57 of the second end face 23. A large damping surface can thereby be realized between the second stop surface 8' and the second end side 23.

Since the inclined bore 50 intersects the spring receptacle 25 along the longitudinal axis 4 over the entire length 58 of the spring receptacle 25 in an advantageous manner, advantageous flow properties and a further enlarged first opening 55 of the fluid channel 15 relative to the spring receptacle 25 are obtained. In this case, the point 60 is also located exclusively outside the spring receptacle 25, at which point the first opening 55 is spaced maximally apart from the longitudinal axis 4 in the radial direction. Conversely, point 61 is also located on the edge of spring receptacle 55, at which point first opening 55 has the smallest distance from longitudinal axis 4. Furthermore, points 62, 63 are also produced at the second opening 56, point 62 being located on the edge of the second opening 56 at a distance from the longitudinal axis 4, and point 63 being located on the edge of the second opening 56 at a distance from the longitudinal axis 4. Point 62 is further from longitudinal axis 4, viewed radially, than point 60. Furthermore, the point 63 of the second opening 56 is further from the longitudinal axis 4, viewed radially, than the point 61 on the edge of the first opening 55. Furthermore, the center of gravity 64 of the first opening 55 is radially closer to the longitudinal axis 4 than the center of gravity 65 of the second opening.

Furthermore, in this exemplary embodiment, the angled opening 50 is also configured in such a way that the base 26 of the spring receptacle 25 is cut open by the angled opening 50. The spring receptacle 25 can thus be used in an advantageous manner for guiding the fuel and is integrated over its entire length 58 into the fluid channel 15.

Fig. 2 shows a valve 1 according to a second exemplary embodiment in a partially schematic sectional view. In this exemplary embodiment, the second opening 56 or a partial surface 56' on the second end side 23 of the armature 6, in which the second opening 56 is located, is oriented perpendicularly to the axis 53 of the angled bore 50. In this case, the partial surface 56' of the armature 6 can be formed by a circumferential groove 85 or individual counterbores. Specifically, the partial surface 56' can be formed first on the second end face 23 of the armature 6, and then the angled bore 50 can be drilled starting from the second end face 23. This makes it possible for the drill tip to come into contact at right angles with the partial surface 56' of the armature 6. Thus, a variant optimized with respect to production is obtained in particular with respect to the first exemplary embodiment illustrated in fig. 1, which variant serves in particular for improving the drilling. This also prevents the drill from breaking, since the drilling does not take place obliquely to the surface.

In this case, it is particularly advantageous for the oblique bores to be realized on the armature 6, which correspond to the oblique bores 50, to be formed in particular by a groove-shaped partial surface 56' which runs around the longitudinal axis 4, from which groove the oblique bores 50 run distributed over the circumference.

Fig. 3 shows a valve 1 according to a third exemplary embodiment in a partially schematic sectional illustration. In this exemplary embodiment, a chamfer 66 is formed on the armature 6, which chamfer cuts off the second end face 23 at its outer diameter 42. The chamfer 66 is then located between the second end side 23 and the outer side 32 of the armature 6. Preferably, the chamfer 66 is configured at a right angle with respect to the axis 53 of the angled bore 50. This configuration has the following advantages on the one hand: an optimization in terms of production is achieved as is correspondingly explained with reference to fig. 2. Furthermore, the inner portion 57 of the second end side 23, on which the armature 6 interacts with the stop surface 8', can be maximally configured. This results in a particularly large degree of freedom in the design of the structure. In the corresponding application case, therefore, very large hydraulic damping can be achieved.

Fig. 4 shows a valve 1 according to a fourth exemplary embodiment in a partially schematic sectional view. In this embodiment, the fluid passage 15 has a first coaxial blind hole 71 and a second coaxial blind hole 72. The first coaxial blind hole 71 extends from the first end side 22 in the coaxial direction 19. The second coaxial blind hole 72 extends from the second end face 23 opposite the coaxial direction 19. Within the armature 6, the two blind holes 71, 72 intersect one another. The intersection region 73 can be arranged close to the base 26 of the spring receptacle 25, as viewed along the longitudinal axis 4. Thereby resulting in advantageous flow properties. The blind holes 71, 72 and at least a portion 51 of the spring receiving portion 25 may be utilized in directing fluid through the armature 6. In this embodiment, the spring receptacle 25 can thus also be integrated at least partially into the fluid channel 15 in an advantageous manner. In the intersection region 73, the fluid is directed radially outward along the longitudinal axis 4, viewed in the coaxial direction 19. This also results in a favorable introduction of fluid into the fluid channel 15 starting from the inner bore 31 of the inner pole 3 and simultaneously in a favorable damping at the second stop element 8.

It is therefore particularly advantageous if the point 60 of the first opening 55 of the fluid channel 15 which is furthest radially outside the longitudinal axis 4 is located closer to the longitudinal axis 4 than the point 62 of the second opening 56 of the fluid channel 15 which is furthest radially outside the longitudinal axis 4. It is also advantageous if the center of gravity 64 of the area of the first opening 55 of the fluid channel 15 is closer to the longitudinal axis 4 than the center of gravity 65 of the area of the second opening 56 of the fluid channel 15.

In the preceding exemplary embodiments, which are described in particular with reference to fig. 2 to 4, it can be advantageously achieved that: the fluid channel 15 exits at an outlet face 80 of the armature 6 toward the second region 18 of the armature chamber 16, wherein an axis 81 of the fluid channel 15, along which the fluid channel 15 exits at the outlet face 80 of the armature 6, is oriented perpendicular to the outlet face 80. Furthermore, it is possible to design the fluid channel 15 from this side with a bore which can be machined into the armature perpendicular to the outlet face 80, which improves the manufacturability. The outlet face 80 can be located in an annular face 82 which surrounds the longitudinal axis 4, the annular face 82 being formed as a partial face 82 of a cone outer circumferential face 83 which is rotationally symmetrical with respect to the longitudinal axis 4, or as a partial face 82 of a disk 84 which is oriented perpendicularly to the longitudinal axis 4. This is possible, for example, by forming circumferential grooves 85 or chamfers 66.

The invention is not limited to the illustrated embodiments.