Piston slide valve having a two-part actuator

Abstract

The invention relates to an electromagnetically actuated piston slide valve (1), comprising a magnetic actuator (10) - having an armature (12) with a central bore (12a) and - having a tappet (13), which is designed as a non-cylindrical tappet in an insertion region (11a). The invention further relates to a shock absorber having such a piston slide valve.

Description

[0001] Piston valve with two-piece actuator

[0002] FIELD OF THE INVENTION

[0003] The present invention relates to a piston slide valve, in particular a proportional valve, and a shock absorber for a vehicle with such a piston slide valve.

[0004] BACKGROUND OF THE INVENTION

[0005] Adjustable or controllable valves, or valves with adjustable flow resistance, are used in vehicle shock absorbers as damper valves to control or regulate the flow of a working fluid, such as hydraulic oil, between the damper chambers of a shock absorber and thus adjust its damping characteristics (e.g., "hard" or "soft"). Examples of valves used are electromagnetically actuated piston slide valves designed as proportional valves or throttles. In such piston slide valves, an axially movable valve slide or piston slide moves in or on a guide cylinder, in particular on a guide pin, with radial fluid passages, which enables a targeted change in the free flow cross-section for the working fluid, independent of auxiliary variables.A proportional characteristic can be achieved by suitable coordination and dimensioning of the components of the electromagnetic drive and / or the valve, whereby, for example, the stroke of the magnet armature and / or the free cross-section of the fluid passage openings changes at least approximately proportionally to the drive current or to the displacement of the piston slide.

[0006] In such directly controlled and pressure-balanced valves, the magnetic force, or rather the valve efficiency, is a key quality parameter. Crucial to high valve performance is keeping mechanical and electromagnetic losses as low as possible during valve operation. At the same time, component and manufacturing costs should be kept low.

[0007] SUMMARY OF THE INVENTION

[0008] The object of the present invention is to provide a simple and compact piston valve with increased valve efficiency, as well as a corresponding shock absorber. This object is achieved by the independent claims. Advantageous embodiments and further developments are specified in the dependent claims.

[0009] The present invention provides an electromagnetically actuated piston spool valve comprising a piston spool or valve assembly and a magnetic actuator, i.e., a magnetic linear actuator. The magnetic actuator comprises an actuator that can be moved along a central or valve axis of the piston spool valve, i.e., along a linear travel path. The travel path is accordingly a straight line between a front, energized end point, which forms the maximum deflection of the actuator, and a rear, deenergized end point, which forms the minimum deflection of the actuator.

[0010] The actuator comprises a magnet armature made of a magnetically conductive or ferromagnetic material with a central bore on a central axis of the magnet armature that coincides with the valve axis. Preferably, the magnet armature is a cylinder or has at least one cylindrical, radial outer side and / or is a closed and / or annular body surrounding the central bore. The central bore is a through-opening or continuous opening for the flow of a working fluid, in particular a hydraulic oil, during operation or when the magnet armature or the actuator is moved along the travel path. The central bore connects the two opposite axial or front and rear ends or end faces of the magnet armature, i.e., the (axial) front and rear of the magnet armature.The piston valve is therefore a pressure-balanced valve in which the same pressure generally prevails on the front and rear sides of the armature. The central bore is preferably cylindrical in sections or continuously, i.e., across the entire axial length of the armature or from the front to the rear end, and / or has a circular cross-section at every point with a diameter that remains constant in sections or continuously along the central axis.

[0011] The actuator further comprises a plunger which is inserted, preferably pressed, into an axial insertion area on the front side of the magnet armature in the central bore and which protrudes beyond the front end of the magnet armature and serves to actuate a (front-side) valve element, in particular a piston slide in the valve arrangement. The (elongated) plunger, which is thus firmly connected to the magnet armature, is preferably arranged on the valve axis and / or preferably has a central axis which particularly preferably coincides with the valve axis. A rear end of the plunger is preferably arranged within the magnet armature so that the plunger does not protrude beyond a rear end of the magnet armature. The insertion area thus comprises the front end of the magnet armature or the central bore and the rear end of the plunger.The insertion area preferably comprises between 5% and 100% of the (length of the) central bore along the valve axis, for example 5%, 10%, 20%, 30%, 50%, 70%, 90% or 100%, whereby each of the mentioned values ​​can also represent an upper or lower limit of the mentioned value range.

[0012] According to the invention, the plunger has a non-cylindrical radial outer side or outer surface, at least in the axial insertion region or along its entire length, i.e., completely. The plunger is thus designed in sections or entirely as a non-cylindrical or non-solid-walled plunger. Accordingly, the central bore of the magnet armature is not closed by the plunger, i.e., not completely or only partially. Rather, there is an axially continuous passage opening for the working fluid in the central bore, even in the insertion region, so that communication of the working fluid between the front and rear of the magnet armature can take place on the outside of the plunger and / or past the plunger.

[0013] Thus, in the region in which the tappet is designed as a non-cylindrical tappet, for example on an otherwise cylindrical or radial outer side, the diameter of which corresponds to the diameter of the central bore, it has recesses or depressions which run along, preferably parallel to, its central axis and are each continuous. In other words, the non-cylindrical tappet has, in a cross-section perpendicular to the central axis of the tappet, an outer or peripheral area whose diameter corresponds to the diameter of the central bore in the insertion area. The points or sections on the radial or circumferential outer side of the tappet which span the peripheral area or lie on it then engage with an (inner) wall of the central bore, i.e. they touch it and / or form pressing surfaces. The space lying between these points or sectionsThe remaining surface of the plunger is spaced from the circumference, which, by definition, only occurs radially inward. Preferably, the diameter of the central bore and the circumference of the plunger remain constant throughout the entire insertion area.

[0014] The inventive provision of a non-cylindrical outer surface of the tappet allows the use of a through-hole both for fastening the tappet and for fluid communication, so that the through-hole can be a central hole. This can be manufactured with little effort, thus avoiding eccentric through-holes, which require complex manufacturing steps.

[0015] The magnetic actuator comprises, in a conventional manner, a stationary pole tube, the design of which not only influences the stroke-force characteristic of the magnetic actuator, but also mechanically guides the magnetic armature along its travel path. The pole tube usually provides very precise mechanical guidance with only minimal play, which then advantageously applies to the entire actuator and thus also the tappet, without the need for additional bearings or guidance of the tappet. Axial guidance along the valve axis is generally achieved by a rear pole pot and a front-side pole arrangement, each of which surrounds the magnetic armature radially and usually also axially. The front-side pole arrangement comprises or consists of a pole stage and a pole part.

[0016] In this case, the pole stage refers to the section of the front-side pole arrangement that is arranged radially (exclusively) outside the magnet armature and has an opening or through-hole corresponding to the magnet armature, into which the magnet armature dips with increasing deflection or current flow. The pole stage can be designed as a separate, preferably one-piece component that is firmly connected to the front-side pole arrangement of the pole tube. Typically, the magnet armature has a cylindrical, radial outer surface, and the pole stage is an annular section or an annular (closed) component of the pole tube or the front-side pole arrangement, with a cylindrical or circular opening or through-hole for the magnet armature.

[0017] In this case, the term pole piece or pole core refers to that section of the front-side pole arrangement which is arranged axially (exclusively or along the entire travel path) at the front of the magnet armature and preferably has an outer shape congruent with the magnet armature (as viewed in the direction of the valve axis). The pole piece can be designed as a separate, preferably one-piece component which is firmly connected to the front-side pole arrangement of the pole tube. The pole piece, which has a through-opening for the plunger, is generally an annular section or an annular (closed) component of the pole tube or the front-side pole arrangement, preferably a cylinder with a (cylindrical or circular) through-opening for the plunger. The rear end face of the pole piece preferably corresponds to the front end face of the magnet armature.Particularly preferably, the rear end face of the pole piece and the front end face of the magnet armature are completely flat or planar. The pole tube, i.e., the pole pot and pole arrangement or the pole stage and pole piece, consists entirely or partially of a magnetically conductive material. The magnetic actuator further comprises a magnetic coil, usually arranged on the outside of the pole tube, so that when the magnetic coil is energized, the magnet armature is forced toward the pole piece.

[0018] The inventive two-part design of the actuator further advantageously allows for different materials to be used for the plunger and the magnet armature. In a preferred embodiment, the plunger is made of a magnetically non-conductive material. The magnetic actuator comprises—as mentioned—a pole piece that is fixedly positioned opposite the front end of the magnet armature, in the direction of which the magnet armature is urged when energized, and that has a central axial through-opening for the plunger. The plunger extends through the through-opening of the pole piece to actuate a valve element of the valve arrangement arranged at the front of the pole piece.Particularly preferably, along the entire travel path of the actuator, only the magnetically non-conductive plunger is located within the through-opening of the pole part and / or the magnetically conductive magnet armature (or other magnetically conductive material) does not enter the through-opening of the pole part.

[0019] The use of a plunger made of a magnetically non-conductive material or the avoidance of magnetically conductive material within the through-hole of the pole piece allows radial magnetic force distributions in the pole piece and corresponding transverse forces to be suppressed, which increases the magnetic efficiency of the magnetic actuator and the valve efficiency. Thus, the magnetic actuator generates a greater magnetic force with the same energy input or current flow. This increased magnetic efficiency allows, for example, the provision of a larger axial air gap or working air gap between the pole piece and the magnet armature or the provision of a larger spacing between the pole piece and the magnet armature at maximum deflection, thereby achieving increased (mechanical) robustness of the magnetic actuator or the spool valve.The working air gap is preferably in the range between 200 and 3000 pm and is, for example, 200, 300, 400, 500, 700, 1000, 1200, 1500, 2000, 2500, or 3000 pm, whereby each of the stated values ​​can also represent an upper or lower limit of the stated value range. The stroke, i.e. the length of the travel path of the actuator or the magnet armature or the distance between minimum deflection and maximum deflection, is preferably in the range between 0.5 and 5 mm and is, for example, 0.5, 0.7, 1.0, 1.5, 2.0, 2.5, 3.0, 4.0, or 5.0 mm, whereby each of the stated values ​​can also represent an upper or lower limit of the stated value range.

[0020] Preferably, the magnet armature and plunger are each one-piece components, each made of the same material throughout (homogeneously). The actuator is preferably the only movable component of the magnetic actuator and / or consists of the magnet armature and plunger. Such a two-part actuator, which consists of exactly two firmly connected components that are not separated during intended use or operation or remain firmly connected, simplifies the design of the magnetic actuator, reduces the number of components, and minimizes manufacturing costs.

[0021] In a preferred embodiment, the plunger has a consistent cross-section perpendicular or transverse to the central axis along its entire axial length. This simplifies the manufacture of the plunger.

[0022] The plunger is preferably a cold-formed, particularly cold-extruded, component, which can be manufactured with minimal effort using a wire or rod pressed or forced through a die. Accordingly, the plunger is made of a cold-formable, preferably magnetically non-conductive or only slightly conductive material, such as the material "1.4567" from the manufacturer Saarstahl.

[0023] Preferably, the ram is a tool-free component, meaning that after cold forming in a forming tool, no further machining, for example, is performed in another tool or machine tool. This further simplifies production.

[0024] Preferably, the plunger is made of a solid material and, for example, has no internal cavities.

[0025] Furthermore, the plunger can have a star-shaped and / or multi-arm cross-section transverse to the central axis, whereby, for example, the mechanical requirements imposed by the pressing in and / or actuation of the valve element can be met with relatively little material expenditure. As already mentioned above, the plunger has (circumferential) points or sections on its outer side in cross-section transverse to the central axis, which span a circumference or engage the wall of the central bore of the magnet armature or form pressing surfaces. Preferably, the plunger has a concave section between each of these points or sections, i.e. a section with a negative radius of curvature (whereas a simple circle or the outer surface of a cylinder has a constant positive radius of curvature).Particularly preferably, the plunger is concave in cross-section at every point on the outer side that does not engage the wall of the central bore or form a pressing surface. This means that the plunger has a continuously concave section in cross-section between the points or sections located on a circumference or between the pressing surfaces. This allows for a large passage area for the working fluid in the insertion area.

[0026] In cross-section transverse to the central axis, the plunger preferably has an n-fold rotational symmetry with n > 2 and integer, where n is preferably 3, 4, 5, 6, 7, 8, 9, 10 or 12.

[0027] The plunger preferably has a length in the range between 1 and 10 cm, for example, 1, 2, 3, 5, 7, or 10 cm, whereby each of the specified values ​​can also represent an upper or lower limit of the specified value range. The plunger preferably has a diameter or circumferential diameter in the range between 2 and 20 mm, for example, 2, 3, 4, 5, 7, 10, 12, 15, or 20 mm, whereby each of the specified values ​​can also represent an upper or lower limit of the specified value range.

[0028] In a preferred embodiment, the magnetically conductive armature is rotationally symmetrical and / or cylindrical and / or has at least one cylindrical, radial outer surface. Preferably, the front and / or rear end face of the armature is completely flat or planar.

[0029] Preferably, the diameter of the central bore is constant or consistent throughout, i.e., along the entire length of the central bore or the magnet armature, or at least in the insertion area. For example, the central bore consists of several directly adjacent axial sections, each with a constant but different diameter. Particularly preferably, the central bore is designed as a blind hole with a front section with a first constant diameter, which forms or encompasses the insertion area, and with a directly adjoining rear section with a second constant and smaller diameter.The first diameter is then preferably selected such that a total passage area for the working fluid in the insertion area is greater than or equal to the area of ​​the central bore in the rear section and / or that the insertion area does not form the maximum fluid-dynamic resistance in the central bore of the magnet armature.

[0030] In the simplest case, the magnet armature has a constant cross-section perpendicular to the central axis along its entire axial length, which simplifies production.

[0031] The magnet armature is preferably a cold-formed, particularly cold-extruded, component, which can be manufactured with minimal effort using a wire or rod, which—if necessary—is pressed or forced through a die, and then provided with a central bore. Accordingly, the magnet armature is preferably made of a cold-formable, magnetically conductive material, such as C4C from the manufacturer Deutsche Edelstahlwerke. Alternatively, the magnet armature can also be a turned part or a turned component.

[0032] Preferably, the magnet armature is a tool-free component, meaning that after cold forming in a forming tool or turning in a turning tool and after the central bore has been created (which preferably takes place in the forming tool or turning tool or immediately thereafter), no further machining, for example, in another tool or machine tool, is performed. This further simplifies production.

[0033] In the simplest case, the magnet armature consists of a solid material apart from the central bore, with no other, particularly no eccentric, through-bores being present.

[0034] The magnet armature preferably has a length in the range between 1 and 10 cm, for example 1, 2, 3, 5, 7 or 10 cm, whereby each of the stated values ​​can also represent an upper or lower limit of the stated value range. The central bore or all sections of the central bore preferably each have a diameter in the range between 2 and 20 mm, for example 2, 3, 4, 5, 7, 10, 12, 15 or 20 mm, whereby each of the stated values ​​can also represent an upper or lower limit of the stated value range. The magnet armature preferably has an outer diameter in the range between 10 and 100 mm, for example 10, 15, 20, 30, 40, 50, 70 or 100 mm, whereby each of the stated values ​​can also represent an upper or lower limit of the stated value range.

[0035] In a preferred embodiment, the magnetic actuator comprises a rear, preferably one-piece pole pot, which—as already mentioned—is part of the pole tube and directly surrounds the magnet armature axially and radially on its rear side. The pole pot has a (rear) axial stop for the magnet armature on a front side of a rear axial wall facing the magnet armature, which is opposite the preferably completely flat or planar rear axial end face of the magnet armature. This provides a remanence distance for the magnet armature at minimal deflection, i.e., generally in the de-energized position, and thus prevents magnetic and / or hydraulic sticking of the magnet armature in the de-energized position.Preferably, the axial stop creating the remanence distance is formed by a plurality of n preferably point-shaped, cold-formed and / or identical stop elevations on the front side of the rear wall, with n > 2 and an integer, where n is preferably 2, 3, 4, 5, or 6. The stop elevations are preferably arranged regularly around a central axis of the pole pot and spaced from this, and / or the pole pot preferably has an n-fold rotational symmetry.

[0036] The pole pot is preferably a cold-formed component, and the stop elevations are particularly preferably also created by cold forming. For example, these are formed by pressing a die having corresponding recesses onto the front side of the rear wall. The pole pot is a pot-shaped and preferably one-piece and / or closed component, i.e., it preferably has a continuously closed surface without through-openings. The remanence distance or the height of the stop elevations is preferably in the range between 200 and 2000 μm and is, for example, 200, 300, 400, 500, 700, 1000, 1200, 1500, or 2000 μm, whereby each of the stated values ​​can also represent an upper or lower limit of the stated value range.

[0037] This stop geometry in the form of two or more elevations on the front of the rear wall

[0038] - minimizes the area of ​​the axial stop in order to keep the negative, axially conductive magnetic force in this direction as small as possible,

[0039] - can be created with little effort through the manufacturing process of forming technology or cold forming, and

[0040] - avoids additional components. The piston slide valve further comprises a valve or piston slide arrangement arranged in a valve housing, which is preferably designed as follows: The valve arrangement comprises an axially displaceable valve or piston slide as a movable valve element, which is actuated by the tappet of the actuator. The piston slide moves along a travel path linearly along a stationary guide cylinder, in particular on the outside of a (cylindrical) guide pin or on the inside of a hollow cylinder. The guide cylinder and the piston slide each have a longitudinal or central axis that coincides with the valve axis, so that the piston slide moves on or along the valve axis. The piston slide is guided by the guide cylinder and corresponds to the guide cylinder.Piston valves and guide cylinders typically have a circular cross-section and corresponding diameters. However, other cross-sections are also conceivable, such as triangular, square, hexagonal, or octagonal cross-sections.

[0041] Along its travel path, the piston slide changes the free flow cross-section of a fluid channel, which is formed, for example, by radial fluid passage openings in the guide cylinder, and thus closes or opens the piston slide valve.

[0042] In this preferred embodiment, the valve arrangement further comprises a spring element that urges the piston slide into a rearward, open position in which the fluid channel is (fully or maximally) open. The piston slide valve is thus an NO valve (normally open) that is fully open when de-energized. The plunger is particularly preferably only in contact with the piston slide. To actuate the piston slide, the plunger advantageously only abuts the piston slide with its front side or axial end face, in particular against a rear side of the piston slide, and is not rigidly connected to the piston slide. This avoids mechanical transverse forces and thus increases valve efficiency.

[0043] The piston spool valve is particularly preferably a proportional valve that adjusts the travel of the actuator and / or piston spool and / or the pressure drop proportional to the current supply or current strength in the solenoid coil. The piston spool valve is thus a directly controlled valve in which the actuating force of the magnetic actuator is transmitted directly and immediately to the actuating or piston spool of the valve arrangement via the tappet. The present invention further comprises a shock absorber with exactly one, two or more of the piston spool valves described above. In the simplest case, the shock absorber comprises a pressure cylinder in which an axially movable piston divides the volume of the pressure cylinder into two pressure chambers. The two pressure chambers are then hydraulically connected via a piston spool valve as described above.Alternatively, a separate piston slide valve can be provided for each flow direction, for example to be able to adjust the rebound and compression stages of the shock absorber separately, so that two piston slide valves are provided on the shock absorber.

[0044] SHORT DESCRIPTION OF THE CHARACTERS

[0045] Further advantages of the invention are described below with reference to the exemplary embodiment illustrated in the accompanying figures. This exemplary embodiment represents a preferred embodiment that does not limit the invention in any way. The figures shown are schematic representations that do not necessarily reflect actual proportions, but serve to improve the clarity of the exemplary embodiment. In detail, the figures show:

[0046] Figure 1 shows a longitudinal section of an embodiment of a piston valve in the open state,

[0047] Figure 2 shows a cross section of a tappet, and

[0048] Figure 3 is a schematic view of a shock absorber.

[0049] FIGURE DESCRIPTION

[0050] Figure 1 shows an embodiment of a piston slide valve 1 according to the invention for a shock absorber 30 of a motor vehicle in the open state. The electromagnetically actuated piston slide valve 1 comprises a magnetic actuator 10 and a valve assembly 20, each of which has a central axis coinciding with the valve axis 1a of the piston slide valve 1.

[0051] The magnetic actuator 10 comprises an actuator 11 consisting of a magnetic armature 12 and a non-magnetic or non-magnetizable tappet 13. The magnetic armature 12 has a central bore 12a that is rotationally symmetrical with respect to the valve axis 1a. The tappet 13 is designed entirely, i.e., along its entire length, as a non-cylindrical tappet and has the cross-section shown in Figure 2 along its entire length. In an insertion area 1a on the front side of the magnetic armature 12, the tappet 13 is inserted with its rear end into the central bore 12a and pressed there.In the illustrated embodiment, the central bore is designed as a blind hole with a front section having a first constant diameter, which in this case also forms the insertion area 11a, and with a directly adjoining rear section having a second constant diameter, which in this case is smaller than the first diameter. In an embodiment not shown, the central bore 12a is a simple through-hole with exactly one constant diameter along the entire axial length of the magnet armature 12. Apart from the central bore 12a, the magnet armature 12 is a solid cylinder with a cylindrical outer side with an outer diameter that remains constant along the entire axial length of the magnet armature 12 and flat or level axial end faces.

[0052] The magnetic actuator 10 further comprises a pole tube 14, in which the magnetic armature 12 or the actuator 11 can be moved along the valve axis 1a. The pole tube 14 comprises a closed rear pole pot 15 and a front pole arrangement 16, comprising or consisting of a pole step 17, into which the magnetic armature dips along its travel path, and a pole part 18, toward which the magnetic armature moves when the magnetic actuator is energized. The magnetic actuator 10 further comprises a magnetic coil 19, which is arranged on the outside of the pole tube 14 and is electrically supplied via an electrical connection in the form of a plug 19a.

[0053] In Figure 2, the insertion area 11a is shown in cross-section perpendicular to the valve axis 1a. The non-cylindrical tappet 13 has a three-fold rotational symmetry and is a three-armed tappet which is pressed onto the central bore of the magnet armature 12 at three circumferential sections 13a, so that these sections form pressing surfaces 13a which span a circumference which coincides with the central bore 12a in the insertion area 11a, i.e. has the same diameter. Between these pressing surfaces 13a, the radial surface of the tappet is spaced apart in cross-section from the central bore 12a or the spanned circumference and is essentially concave, so that in the insertion area 11a, fluid passage openings 11b are present between each two adjacent pressing surfaces 13a, which allow the passage of a working fluid from the front to the back of the magnet armature 12.The pole piece 18 of the pole tube 14 has a central through-opening 18a for the plunger 13. The rear axial end face of the pole piece and the front axial end face of the magnet armature 12 are flat, so that the magnet armature 12 does not penetrate into the pole piece 18 during the entire travel path of the actuator 11, and in particular, the through-opening 18a of the pole piece 18 contains exclusively the plunger 13, which is made of a magnetically non-conductive material, at any point along the travel path of the actuator 11.

[0054] The valve arrangement 20 of the piston slide valve 1 comprises a piston slide 21, which, in the illustrated embodiment, is movable along the valve axis 1a on a guide cylinder 22 designed as a guide pin and is actuated by the tappet 13. The valve arrangement 20 further comprises a spring element 23 arranged on the valve axis 1a, which is supported on the piston slide 21 and the guide pin 22 and accordingly urges the piston slide 21 and thus the actuator 11 into a rearward position. To actuate the valve arrangement 20, the tappet 13 abuts with its front end against a rearward end of the piston slide 21 and is not rigidly connected to it, which avoids mechanical transverse forces.The valve arrangement 20 further comprises an axial and a radial fluid connection 24a, 24b with an intermediate fluid channel 25, which is designed as a radial opening in the guide pin 22 and whose free cross section is closed or opened by the piston slide 21 along its travel path.

[0055] In the present piston valve 1, a front stop or the maximum deflection of the actuator 11 is determined by the valve arrangement 20, so that at maximum deflection of the magnet armature 12, a working air gap remains between its front side and the rear side of the pole piece 18, which increases the robustness of the piston valve 1. In the illustrated embodiment, two stop elevations 15a are provided on the inside of the pole pot 15 as a rear axial stop for the magnet armature 12. This ensures a remanence distance for the magnet armature 12, which prevents hydraulic and magnetic sticking of the magnet armature 12 in the de-energized position or at minimum deflection. The stop elevations 15a are arranged on the front side of the rear axial wall of the pole pot 15. In the illustrated embodiment, two identical stop elevations 15a are provided, which are spaced apart from the valve axis 1a.In an embodiment not shown, more than two, for example three, four, or six, stop elevations 15a are provided, which are then preferably arranged symmetrically or regularly around the valve axis 1a. The pole pot 15 is a cold-formed component, and the stop elevations are also created by cold forming.

[0056] Furthermore, all components of the pole tube 14 as well as the magnet armature 12 and the plunger 13 of the actuator are cold-formed or cold-extruded components.

[0057] In an embodiment not shown, the non-cylindrical plunger 13 has a five-fold rotational symmetry and is a five-armed plunger which is pressed onto the central bore of the magnet armature 12 at five circumferential sections or pressing surfaces 13a.

[0058] Figure 3 shows a shock absorber 30 with a pressure cylinder 31 in which an axially movable cylinder piston 32 divides the volume of the pressure cylinder 31 into two pressure chambers 33. A piston slide valve 1 according to the invention is mounted on the shock absorber 30 and connected to the shock absorber 30 and the two pressure chambers 33 via an axial fluid connection 24a and a radial fluid connection 24b. The piston slide valve 1 is the only throttle between the two pressure chambers 33 of the shock absorber 30.

[0059] LIST OF REFERENCE SYMBOLS

[0060] 1 piston valve la valve axis, central axis

[0061] 10 Magnetic actuator

[0062] 11 Actuator

[0063] 11a Insertion area

[0064] 11b Fluid passage opening

[0065] 12 magnet armatures

[0066] 12a Central bore

[0067] 13 plungers

[0068] 13a Pressing surface

[0069] 14 Pole tube

[0070] 15 Poltopf

[0071] 15a stop elevation, stop

[0072] 16 pole arrangement

[0073] 17 pole stage

[0074] 18 Pole piece, pole core

[0075] 18a passage opening

[0076] 19 Solenoid coil

[0077] 19a plug

[0078] 20 Valve arrangement

[0079] 21 piston valves

[0080] 22 Guide cylinder, guide pin

[0081] 23 Spring element

[0082] 24a axial fluid connection

[0083] 24b radial fluid connection

[0084] 25 Fluid channel

[0085] 30 shock absorbers

[0086] 31 printing cylinders

[0087] 32 cylinder pistons

[0088] 33 pressure chamber

Claims

PATENT CLAIMS 1. Piston slide valve (1) comprising a magnetic actuator (10) with an actuator (11) movable along a linear travel path, having - a magnet armature (12) with a central bore (12a), and - a plunger (13), - which is inserted or pressed into the central bore in an axial insertion area (11a) on a front side of the magnet armature, and - which is designed as a non-cylindrical tappet at least in the insertion area or entirely.

2. Piston slide valve (1) according to claim 1, characterized in - that the magnetic actuator (10) further comprises a pole part (18) which has a central through-opening (18a) for the plunger (13), and - that the plunger consists of a magnetically non-conductive material and extends through the through-opening of the pole part, preferably along the entire travel path - only the plunger is located within the through hole of the pole piece and / or - the magnet armature (12) does not enter the through hole of the pole piece.

3. Piston slide valve (1) according to one of the preceding claims, characterized in that the magnet armature (12) and tappet (13) are each one-piece components and / or the actuator (11) consists of a magnet armature and tappet.

4. Piston slide valve (1) according to one of the preceding claims, characterized in that the tappet (13) - has a constant cross-section perpendicular to a central axis (la), and / or - is a cold-formed, in particular cold-extruded component, and / or - is a tool-cutting component, and / or - consists of a solid material, and / or - has a star-shaped and / or multi-armed cross-section, and / or - in cross-section between pressing surfaces (13a) lying on a circumference, each has a concave section, and / or - has an n-fold rotational symmetry in cross-section with n > 2 and integer, where n is preferably 3, 4, 5, 6, 7, 8, 9, 10 or 12.

5. Piston slide valve (1) according to one of the preceding claims, characterized in that - the magnet armature (12) is rotationally symmetrical and / or designed as a cylinder and / or has a cylindrical, radial outer side, and / or - the diameter of the central bore (12a) is constant throughout or at least in the insertion area, and / or - the magnet armature has a constant cross-section perpendicular to a central axis (la), and / or - the magnet armature is a cold-formed, in particular cold-extruded component or a turned component, and / or - the magnet armature is a tool-related component, and / or - the magnet armature is made of solid material except for the central bore, and / or - the magnet armature moves in a pole tube (14) which comprises a pole step (17) into which the magnet armature dips when energized or deflected.

6. Piston slide valve (1) according to one of the preceding claims, characterized in that the magnetic actuator (10) has a rear pole pot (15) which surrounds the magnet armature axially and radially and / or has a stop (15a) for the magnet armature on a rear wall, wherein the stop is preferably formed by a plurality of preferably point-shaped and / or cold-formed stop elevations (15a) on the rear wall.

7. Piston slide valve (1) according to claim 6, characterized in that the pole tube (14) consists of exactly the pole pot (15), the pole step (17) and the pole part (18), which are particularly preferably each one-piece components, and / or consist exclusively of magnetically conductive materials.

8. Piston slide valve (1) according to one of the preceding claims, further comprising a valve arrangement (20) with a piston slide (21) which moves linearly along a guide cylinder (22), preferably on a guide pin, and with a spring element (23) which urges the piston slide into a rearward opening position, wherein preferably - the tappet (13) is in contact with the piston slide, and / or - the piston valve is a proportional valve.

9. Shock absorber (30) for a vehicle, comprising one, preferably exactly one piston slide valve (1) according to one of the preceding claims, wherein the shock absorber has two damper chambers (33) separated by a piston (32) and wherein preferably the piston slide valve is the only throttle between the damper chambers of the shock absorber.

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