Actuating magnet

Description

[0001] The invention relates to an actuating magnet having the features in the preamble of claim 1.

[0002] Such actuating magnets are also known in technical terms as proportional or switching magnets, and are freely available on the market in a wide variety of designs.

[0003] In particular, such actuating magnets serve to control the respective valve piston of a hydraulic or pneumatic valve for the purpose of regulating a corresponding media flow between connections of a valve housing in which the valve piston is guided for longitudinal movement. As an example, reference is made here to a proportional pressure control valve according to DE 10 2011 018 873 A1, comprising a valve housing in which the valve piston is guided for axial movement in a guide and, under the action of an energizable actuating magnet for the valve piston and a spring-loaded return device acting on the valve piston counter to the applied magnetic force of the actuating magnet, regulates a media flow at least between two media connections incorporated in the valve housing.

[0004] By activating the actuating magnet, i.e., by energizing its coil arrangement, the valve piston establishes the media-carrying connection between the aforementioned ports, taking into account the prevailing forces based on the prevailing pressures multiplied by the respective pressure-effective areas, the spring force, the flow forces, and the magnetic force. The media pressure applied to at least one of the media ports in the valve housing, multiplied by a pressure-effective area on the valve piston, is in equilibrium with the prevailing actuating force of the actuating magnet, so that a more or less balanced force-displacement characteristic curve for the actuating magnet can be specified via the desired equilibrium.

[0005] DE 10 2013 010 833 A1 discloses an actuating magnet, particularly in the form of a proportional magnet or switching magnet, comprising a magnet armature that is guided axially movably in a pole sleeve at least partially surrounded by a coil winding as part of a pole tube. A pole core or pole piece is connected to the pole sleeve as a further part of the pole tube via a separating region that forms a magnetic decoupling and can also be filled with a non-magnetic material. When the coil winding is energized, a magnetic force acts on the armature, which moves it within a displacement space as part of an armature space in the sense of a "pushing magnet" toward the pole piece. The known solution is characterized in that, for a desired shortening of the axial length of this displacement space, at least one, preferably annular, insert made of ferromagnetic material of a predetermined axial thickness can be inserted between the armature and the pole piece.If necessary, several such inserts, even in different thicknesses, can be inserted into the anchor space.

[0006] The respective insert mentioned is inserted into the relevant armature chamber as a control means for influencing the force-displacement characteristic curve for the actuating magnet or its armature, with the result that, compared to a solution without such an insert, the force increase occurs with a progressively increasing characteristic curve, i.e. in the direction of the full deflection of the armature, there is an increased force on an actuating tappet of the valve piston, as shown in DE 10 2011 018 873 A1 for a proportional pressure control valve, so that increased actuating forces act on the valve.

[0007] The known solution in which the control means for influencing the force-displacement characteristic curve is introduced in the form of the respective insert in the armature chamber in which the magnet armature is guided so as to be longitudinally movable, shortens the free actuating path for the magnet armature and thus simultaneously reduces the maximum possible displacement path for the valve piston of a valve connected to the actuating magnet with its media or fluid connections.

[0008] Particularly when multiple inserts are arranged one behind the other in the armature chamber, a significantly maximized force increase occurs at the end of the solenoid armature's actuation travel. Consequently, high spring forces are required as a counterforce in the valve, which leads to excessively large compression springs and thus to large valve designs. Furthermore, the actuating magnet and the connected valve respond sluggishly, which impairs the valve's control dynamics.

[0009] DE 10 2006 021 927 A1 discloses an actuating magnet with an energizable coil device for moving a magnet armature within a pole tube in at least one direction, wherein the magnet armature has at least one control means for influencing a force-displacement characteristic curve, at least in the sense of a force reduction at the end of its working stroke, wherein the respective control means is introduced into the outer contour of the magnet armature and is formed from a control groove which runs at least partially in the magnet armature and is formed by a circumferential annular groove in the magnet armature, and wherein the pole tube is formed from a pole sleeve which is connected to a pole piece via a separating ring which helps to limit a magnetic separation between the pole sleeve and the pole piece.

[0010] US 2010 / 0301978 A1, EP 1 818 951 A1, US 2006 / 001513 A1, US 2020 / 0096130 A1 and DE 36 35 551 A1 disclose further actuating magnets.

[0011] Based on this prior art, the invention is therefore based on the object of further improving known valve designs to enable a meaningful influence on the force-displacement characteristic curve for the magnet armature, with a fast-responding actuation behavior of the respective magnet armature and a compact design. This object is achieved by an actuating magnet having the features of patent claim 1 in its entirety.

[0012] According to the characterized part of patent claim 1, it is provided that the annular groove is introduced into the outer circumference of the magnet armature and that in the fully deflected position of the magnet armature, when the required actuating force is applied, the circumferential annular groove of the magnet armature maintains an axial distance from the separating ring.

[0013] A groove on the outer circumference of the magnet armature not only further reduces the force in the area of ​​the final stroke, but also results in a longer working stroke distance in the area of ​​the working stroke with an essentially horizontal force-displacement characteristic curve.

[0014] Because the respective control means is incorporated into the outer contour of the magnet armature, the control means is arranged in a space-saving manner according to the invention in a component in the form of the magnet armature that is absolutely necessary for the function of the actuating magnet.

[0015] The control grooves can be easily and cost-effectively introduced into the magnet armature using methods known from the state of the art, for example by milling or laser cutting.

[0016] Since it is further provided that the magnet armature has at least one control means for influencing the mentioned force-displacement characteristic curve, at least in the sense of a force reduction at the end of a working stroke, the control means are relocated from the armature space into the magnet armature in a space-saving manner, as shown in the prior art.

[0017] It is surprising for an average person skilled in the art in the field of such magnetic systems that by moving the control means into the magnet armature over its actuation path, a uniform force-displacement curve is achieved and that, in particular at the end of the working or actuation stroke of the magnet armature, there is a reduction in the actuation force, which is sufficient to be able to move the valve piston of a valve connected to the actuating magnet safely into its positions blocking or releasing the respective fluid connections.Since the applied actuating force is reduced overall at the end of the armature stroke, the actuating magnet and its coil body can be correspondingly reduced in size and thus designed to save space. Since only low actuating forces, particularly via the return spring of the connected valve, are to be controlled, an extremely fast, dynamic switching behavior is achieved for the actuating magnet according to the invention. This has no equivalent in the prior art.

[0018] The control means of the armature can be optimized in such a way that the armature reaches its reset position even before its front end has struck the pole core or an anti-stick disc arranged on the pole core, thus protecting the latter or even eliminating the need for it. This allows for highly force-balanced movements of the armature, which benefits the switching dynamics. Instead of a compression spring as the return force source for the armature, a second, appropriately polarized coil device can also initiate a return movement of the armature to its non-actuated neutral position.

[0019] Particularly advantageous is the provision of at least one circumferential annular groove on the outer circumference and on the end face of the magnet armature. Compared to the exclusive provision of the axial groove, this results in a further reduction in force in the final stroke and working stroke of the magnet armature. As a result, the difference between the maximum and minimum force of the force-displacement characteristic curve in the working stroke is particularly small, so that a particularly long working stroke distance with an essentially horizontal force-displacement characteristic curve can be generated in the working stroke. The force-stroke behavior of the actuating magnet is essentially the same in the actuation direction and in the return direction of the magnet armature, differing only by a force of up to approximately 12 Newtons in a specific stroke position of the magnet armature.

[0020] The groove on the outer circumference and / or on the end face of the magnet armature can be segmented, so that it has at least one interruption. The groove profile can be at least partially annular and / or partially thread-shaped. Furthermore, the groove can be filled with any type of non-magnetizable material, thereby increasing the rigidity and strength of the magnet armature.

[0021] Several grooves can be provided on the outer circumference and / or on the end face of the magnet armature, arranged concentrically to the longitudinal axis of the magnet armature. At least one of the grooves on the outer circumference and / or on the end face of the magnet armature can differ in depth from the at least one other groove on the outer circumference or on the end face of the magnet armature, depending on the desired force-displacement characteristic.

[0022] The pole sleeve can be made of magnetizable steel, which is connected, in particular welded, to a pole piece made of magnetizable steel via a separating ring. In the fully deflected position of the magnet armature, with the required actuation force applied, the circumferential annular groove of the magnet armature maintains an axial distance from the separating ring, which preferably corresponds approximately to one to three times, particularly preferably twice, the base width of the annular groove.

[0023] The annular groove running around the outer circumference of the magnet armature can be essentially U-shaped in cross-section with straight walls. The depth of the annular groove running around the outer circumference of the magnet armature can essentially correspond to the width of the annular groove. The separating ring can, starting from a cylindrical base section, transition into two inclined boundary walls towards the outside, one of which faces the pole sleeve with a greater inclination and the other, with a lesser inclination, the free end of the actuating plunger. The annular groove running around the outer circumference of the magnet armature can remain behind the separating ring in any travel position of the magnet armature in its force-exerting actuation position. The annular groove, which serves as a control groove and is provided on the front side of the magnet armature, can enclose the actuating plunger and be provided in the area of ​​the outer third of the free end face of the magnet armature, which faces the actuating plunger.The cross-section of the front-side annular groove can, starting from a base surface running parallel to the front side of the magnet armature, have a straight wall section that is perpendicular to the base surface and an inclined wall section that runs diagonally in the direction of the actuating axis of the magnet armature, preferably forming an angle of approximately 30° to 60°, particularly preferably 45°, with the armature. By simply changing one of the aforementioned parameters of the actuating magnet, the course of the force-displacement characteristic curve can be adapted to specific applications of the actuating magnet.

[0024] Further preferred embodiments of the invention are specified in the subclaims.

[0025] In the following, an actuating magnet according to the invention is explained in more detail with reference to the drawing. The drawing is not to scale and shows Fig. 1 shows a schematically simplified longitudinal section of an actuating magnet according to the invention; Fig. 1A, 1B each an enlarged view of a Fig. 1 with A or B; Fig. 2 partially in a schematically simplified longitudinal section the actuating magnet from Fig. 1 ; and Fig. 3 a force-displacement characteristic curve of the actuating magnet from Fig. 1 and 2 in a Cartesian coordinate system in which the stroke of the magnet armature is plotted along the abscissa and the force along the ordinate.

[0026] Actuating magnets known from the prior art serve, for example, to control a valve for the purpose of regulating a media flow between connections provided in the valve housing. With regard to the structure and function of such a combination of an actuating magnet and a valve known from the prior art, reference is made to a proportional pressure control valve according to DE 10 2011 018 873 A1 as an example.

[0027] In Fig. 1 and 21 shows an actuating magnet 10 according to the invention, which has a pole tube 12 in which a magnet armature 14 is guided for axial movement in an armature chamber 16. The pole tube 12 has a pole sleeve 18 and a pole piece 20, each made of magnetizable material, in particular steel, and which are connected to one another via a separating ring 22, which helps to define a magnetic separation between the pole sleeve 18 and the pole piece 20, formed as a recess in the pole tube 12. To improve the strength and rigidity of the pole tube, the recess can be filled with a non-magnetizable material (not shown in the figures). The armature chamber 16 is defined by parts of the pole sleeve 18, by the separating ring 22, by parts of the pole piece 20, and by a cylindrical connecting piece 24, which, received by the free end 26 of the pole sleeve 18, closes off the armature chamber 16 to the outside.

[0028] To move the magnet armature 14 ( Fig. 1 and 2 ) within the pole tube 12, at least in the direction of the pole piece 20, the actuating magnet 10 has a coil device 28 with a coil winding 30, which is arranged on the pole tube 12 and can be energized for an actuation process. The coil device 28 is at least partially enclosed by a housing 32, which has an annular pole plate 34 surrounding the pole piece 20.

[0029] At one end of the magnet armature 14, a rod-like actuating part in the form of an actuating plunger 38 is fastened, in particular screwed into the magnet armature 14, which extends through a through-bore 40 in the pole piece 20, so that the free end 42 of the actuating plunger 38 facing away from the magnet armature 14 is accessible for actuating a device not shown in the figures, for example a valve (see DE 10 2011 018 873 A1).

[0030] As in the Fig. 1, 1A and 2 shown, where the Fig. 1A an enlarged view of the Fig. 1 As shown in the figure of the circular section marked A, the magnet armature 14 has a force-displacement characteristic curve 44, 46, 48 ( Fig. 3 ) a tax resource 50 ( Fig. 1A ) in the form of an annular control groove 54 introduced into its outer circumference 52, which is referred to below as annular groove 54.

[0031] As in Fig. 1A As can best be seen, the annular groove 54 introduced into the outer circumference 52 of the magnet armature 14 is, when viewed in cross-section, essentially U-shaped, namely with walls 58 running perpendicular to the longitudinal axis 56 of the actuating magnet 10 and arranged parallel to one another, which extend from an annular base surface 60 arranged coaxially to the longitudinal axis 56 of the actuating magnet 10, wherein the depth of the annular groove 54 essentially corresponds to the width of the annular groove 54. The annular groove 54 is introduced into the magnet armature 14 in a region which, starting from an end face 62 of the magnet armature 14 with the actuating plunger 38, extends between one fifth and one third of the total axial length of the magnet armature 14.

[0032] Additionally or alternatively, the magnet armature 14, like the Fig. 1 und 1B can be seen, whereby the Fig. 1B an enlarged view of the Fig. 1 with B, also to influence the force-displacement characteristic ( Fig. 3 ) a tax means 64 ( Fig. 1B ) in the form of an annular control groove 66 introduced into the end face 62 of the magnet armature 14 with the actuating plunger 38, which is referred to below as a further annular groove 66.

[0033] As in Fig. 1B As can best be seen, the cross-section of the further annular groove 66 introduced into the end face 62 of the magnet armature 14, starting from a bottom surface 68 running parallel to the end face 62 of the magnet armature 14, has a straight wall section 70 which is perpendicular to the bottom surface 68, and an oblique wall section 72 which is designed to run obliquely in the direction of the actuating axis 56 of the magnet armature 14. The angle between the oblique wall section 72 and the actuating axis 56 is approximately 45 degrees. The further annular groove 66 is provided in the region of the outer third of the free end face 62 of the magnet armature 14.

[0034] The annular groove 54 formed in the outer circumference 52 of the magnet armature 14 and / or the further annular groove 66 formed in the front side of the magnet armature 14 each coaxially surround the actuating plunger 38.

[0035] Seen in cross section, the separating ring 22 ( Fig. 1 and 2 ), starting from a cylindrical base part 74, into two obliquely running, annular boundary walls 76, 78 towards the outside, of which one 76 faces the pole sleeve 18 with a greater inclination and the other 78, with a smaller inclination, faces the free end 42 of the actuating plunger 38. In each stroke position of the magnet armature 14, in particular in the end stroke position, i.e. in the fully deflected stroke position, the annular groove 54 introduced into the magnet armature 14 on the outer circumference 52 in the direction of the end 80 of the magnet armature 14 facing away from the actuating tappet 38 and the further annular groove 66 introduced into the magnet armature 14 on the front side in the direction of the end 62 of the magnet armature 14 having the actuating tappet 38 each maintains an at least slight axial distance from the base part 74 of the separating ring 22, the width of which corresponds approximately to 2.5 times the base width of the annular groove 54 in the outer circumference 52 of the magnet armature 14.

[0036] In Fig. 3 is in a coordinate system a force-displacement characteristic curve 82 of a control-means-free magnet armature known from the prior art and force-displacement characteristic curves 44, 46, 48 of the Fig. 1 and 2 shown magnet armature 14, which has the annular grooves 54, 66 introduced into its outer circumference 52 and / or into its end face 62.

[0037] In the coordinate system ( Fig. 3 ), in which the stroke s of the magnet armature 14 is plotted on the x-axis in millimeters and the force F on the y-axis in Newtons, the force-displacement characteristic curve of the control-means-free magnet armature is shown by means of a solid, dark characteristic curve 82, the force-displacement characteristic curve of a magnet armature 14 with only one groove 54 introduced on its outer circumference 52 is shown by means of a dashed characteristic curve 44, the force-displacement characteristic curve of a magnet armature 14 with only one end-face groove 66 is shown by means of a dotted characteristic curve 46 and the force-displacement characteristic curve of a magnet armature 14 which has a groove 54 introduced on its outer circumference 52 and a end-face groove 66 is shown by means of a solid, light characteristic curve 48.

[0038] How Fig. 3 As can be seen, a groove 66 (characteristic curve 46) introduced on the end face 62 of the magnet armature 14 essentially causes a reduction in force, in particular of the maximum force, in the area of ​​the final stroke of the magnet armature 14 compared to a control means-free magnet armature, whereas a groove 54 (characteristic curve 44) introduced on the outer circumference 52, in addition to a further reduction in force in the area of ​​the final stroke, causes a longer working stroke distance with a substantially horizontal force-displacement characteristic curve 44 in the area of ​​the working stroke.

[0039] Particularly advantageously, at least one circumferential annular groove 54, 66 (characteristic curve 48) is provided on the outer circumference 52 and on the end face 62 of the magnet armature 14. Compared to the exclusive provision of the groove 54 provided on the outer circumference 52, these grooves result in a further reduction in force in the region of the final stroke and the working stroke of the magnet armature 14, whereby the difference between the maximum and minimum force of the force-displacement characteristic curve 48 in the region of the working stroke is particularly small, so that a particularly long working stroke distance with a substantially horizontal force-displacement characteristic curve 48 can be generated in the region of the working stroke.

[0040] Due to the reduction in force in the area of ​​the final stroke, the magnet armature 14 can, under the action of the annular grooves 54, 66, either abut against the pole piece 20 or against an anti-stick disc 84, if provided, with a reduced actuating force or even assume its final position before returning to the unactuated position while maintaining a gap-like axial distance therefrom.

[0041] Out of Fig. 3 It is further apparent that the force-stroke behavior of each magnet armature 14 having at least one annular groove 54, 66 is essentially the same in the actuation direction 86 and in the return direction 88, namely, in a specific stroke position of the magnet armature 14, it differs only by a force of up to approximately 12 Newtons, the force in the return direction 88 being greater in each stroke position than the force in the actuation direction 86.

[0042] How Fig. 1 and 2show, the magnet armature 14 is guided in the pole tube 12 by means of a guide sleeve 90, which is arranged in an annular circumferential recess 92 on the outer circumference 52 of the magnet armature 14 and which surrounds the magnet armature 14 at its end region facing away from the actuating plunger 38. For the longitudinally movable guidance of the actuating plunger 38 in the pole piece 20, a further guide sleeve 94 is provided, which is received in an annular circumferential recess 96 in the form of an inner diameter extension in the end region of the through-bore 40 of the pole piece 20 facing the magnet armature 14.

[0043] In the direction of the end face 62 of the magnet armature 14, to which the actuating plunger 38 is fastened, the annular circumferential recess 96 for the further guide sleeve 94 is adjoined by an annular circumferential recess 98 with a larger outer diameter, in which an anti-stick disc 84 surrounding the actuating plunger 38 is arranged.

[0044] Like the Fig. 1 and 2 As can also be seen, the pole piece 20, in particular in the respective image plane of the Fig. 1 and 2 two through-passage compensating bores 100 for pressure equalization, running parallel to the actuating axis 56, which connect the exterior of the actuating magnet 10 with the armature chamber 16, in which the magnet armature 14 is movably arranged. The two compensating bores 100 each open out of the pole piece 20 at the level of the further annular groove 66 formed in the front side of the magnet armature 14 in the direction of the magnet armature 14.

[0045] Connecting piece 24 is a plug part (not shown in the figures) for energizing coil device 28, which plug part is at least partially enclosed by pole sleeve 18. Pole piece 20 has a screw thread 104 on the outer circumference 52 of its free end 102 for screwing actuating magnet 10, for example, into a valve block not shown in the figures.

[0046] The Fig. 1 and 2 The actuating magnet 10 shown is designed as a so-called "pushing magnet" which, when the coil winding 30 is energized, moves from its initial stroke position in which it rests against the connecting piece 24 in the direction of the pole piece 20 until it reaches its final stroke position near the anti-stick disc 84 or in contact with the anti-stick disc 84.

[0047] To return the magnet armature 14 to its initial stroke position when the coil device 28 is partially or de-energized, a reset device (not shown in the figures) can be provided, which has an energy storage device in the form of a compression spring. The compression spring can be either part of the actuated device, for example in the form of the valve (see DE 10 2011 018 873 A1), or part of the actuating magnet 10, namely, it can be supported with one end on the magnet armature 14 and with its other end on the pole piece 20, with the actuating plunger 38 extending through the compression spring.

Claims

1. Actuating solenoid with an energisable coil device (28) for moving a solenoid armature (14) inside a pole tube (12) in at least one direction, the solenoid armature (14) comprising at least one control means (50) for influencing a force-displacement characteristic curve (44, 46, 48), at least in the sense of force reduction at the end of its operating stroke, the respective control means (50) being incorporated in the outer contour (52, 62) of the solenoid armature (14) and being formed by a control groove (54) running at least in sections in the solenoid armature (14), said control groove being formed by a circumferential annular groove (54) in the solenoid armature (14), and the pole tube (12) being formed by a pole sleeve (18) which is connected to a pole piece (20) via a separating ring (22), which co-delimits a magnetic separation between the pole sleeve (18) and the pole piece (20), characterised in that the annular groove (54) on the outer circumference (52) of the solenoid armature (14) is incorporated in said solenoid armature and in that, in the fully deflected position of the solenoid armature (14), by applying the required actuating force, the circumferential annular groove (54) of the solenoid armature (14) maintains an axial distance from the separating ring (22).

2. Actuating solenoid according to claim 1, characterised in that a further, end-face control groove is formed in the solenoid armature (14) by a circumferential annular groove (66) incorporated on one end face (62) of the solenoid armature (14).

3. Actuating solenoid according to either claim 1 or claim 2, characterised in that the axial distance from the separating ring (22) approximately corresponds to one to three times, more preferably to twice the bottom width of the annular groove (54, 66).

4. Actuating solenoid according to any of the preceding claims, characterised in that the annular groove (54) running around the outer circumference (52) of the solenoid armature (14), viewed in cross-section, is formed such that it is substantially U-shaped with straight walls (58).

5. Actuating solenoid according to any of the preceding claims, characterised in that the depth of the annular groove (54) running around the outer circumference (52) of the solenoid armature (14) substantially corresponds to the width of the annular groove (54).

6. Actuating solenoid according to any of the preceding claims, characterised in that the solenoid armature (14) acts on an actuating plunger (38), which passes through the pole piece (20), and which preferably, by means of an energy accumulator, with the coil device (28) partially energised or de-energised, moves the solenoid armature (14) back in its unactuated position.

7. Actuating solenoid according to claim 6, characterised in that the separating ring (22), starting from a cylindrical bottom part (74), transitions outwards into two obliquely extending delimiting walls (76, 78), one (76) of said walls, with a greater inclination, facing the pole sleeve (18), and the other (78), with a correspondingly smaller inclination, facing the free end (42) of the actuating plunger (38).

8. Actuating solenoid according to any of the preceding claims, characterised in that the annular grove (54), running around the outer circumference (52) of the solenoid armature (14), remains behind the separating ring (22) in each displacement position of the solenoid armature (14) in its force-exerting actuating position.

9. Actuating solenoid according to any of claims 6 to 8, provided that these are dependent on claim 2, characterised in that the end-face control groove (66) surrounds the actuating plunger (38) and is incorporated in the region of the outer third of the free end face (62) of the solenoid armature (14) which faces the actuating plunger (38).

10. Actuating solenoid according to any of claims 2 or 3 to 9, provided that these are dependent on claim 2, characterised in that the cross-section of the end-face control groove (66), starting from a bottom surface (68) running parallel with the end face (62) of the solenoid armature (14), has a straight wall section (70), which is perpendicular to the bottom surface (68), and an oblique wall section (72), which runs obliquely in the direction of the actuating axis (56) of the solenoid armature (14), preferably enclosing an angle of approximately 30° to 60°, more preferably 45°, with said solenoid armature.

11. Actuating solenoid according to any of claims 6 to 10, characterised in that an anti-adhesion disc (84) surrounding the actuating plunger (38) is arranged in an annular recess (98) of the pole piece (20), said recess facing the solenoid armature (14).

12. Actuating solenoid according to any of the preceding claims, characterised in that, under the influence of the respective control means (50, 64) formed by the respective control groove (54, 66), the solenoid armature (14) comes into contact with the pole piece (20) or the anti-adhesion disc (84) respectively with a reduced actuating force or preferably assumes its end position while maintaining a gap-shaped axial distance before resetting into the unactuated position.

13. Actuating solenoid according to any of claims 6 to 12, characterised in that the solenoid armature (14) is surrounded at its end region facing away from the actuating plunger (38) by a guide sleeve (90), which serves to guide the solenoid armature (14) in the pole sleeve (18).

14. Actuating solenoid according to any of claims 6 to 13, characterised in that the actuating plunger (38) is guided in the pole piece (20) in a longitudinally displaceable manner by means of a further guide sleeve (94).

15. Actuating solenoid according to any of claims 2 or 3 to 14, provided that these are dependent on claim 2, characterised in that the pole piece (20) has at least one continuous compensating hole (100) running parallel with the actuating axis (56) and emerging from the pole piece (20) in the direction of the solenoid armature (14) at the level of the annular groove (66) incorporated in the solenoid armature (14) on the end face thereof.

16. Actuating solenoid according to any of the preceding claims, characterised in that the coil device (28) is at least partially surrounded on the outside by a housing (32), which has a pole plate (34) that surrounds the pole piece (20).

17. Actuating solenoid according to any of the preceding claims, characterised in that the free end (26) of the pole tube (12) receives a connecting piece (24) that terminates the armature housing (16) for the solenoid armature (14) towards the outside and against which a plug part for energising the coil device (28) abuts, said plug part being at least partially surrounded by the pole sleeve (18).