WO2017005496A1 - Hydraulic valve, in particular hydraulic transmission valve - Google Patents

Abstract

The invention relates to a hydraulic valve (1), in particular a hydraulic transmission valve, comprising an electromagnet part (3) having a magnetisable housing (4) which surrounds a magnet coil (7) on an outer periphery (50) and on at least one end face (52), and also a pole tube (6) which is arranged in the interior of the magnet coil (7) and in which an armature (10) is provided so as to be axially movable in an armature space (56), further comprising a hydraulic part (2) having a hydraulic piston (16) which is guided so as to be axially movable in a valve bushing (5) and by means of which at least one working connection (A) can be connected selectively to at least one supply connection (P) and at least one tank connection (T). The armature (10) is provided in order to drive the hydraulic piston (16). The valve bushing (5) is arranged along a longitudinal axis (L) in an extension of the pole tube (6). According to the invention, a fork plug (35) is integrated into a coil body (8).

Description

 Hydraulic valve, in particular hydraulic transmission valve

Technical area

The invention relates to a hydraulic valve, in particular a hydraulic transmission valve of a hydraulic fluid-carrying device, in particular the mechatronics of a hydraulic control of a transmission of a motor vehicle.

State of the art

In order to nevertheless be fail-safe in the case of large gear oil change intervals, in extreme cases with so-called lifetime fillings, the gear valve must have a high degree of robustness. High robustness can indeed be achieved with a great play on the parts to be moved. However, this is at the expense of the control quality.

From DE 10 201 1 053 023 A1 a hydraulic valve is known, which has both a high robustness and a high control quality. The high robustness is achieved by dirt particles in the operating medium can not get stuck to jamming of the transmission valve, since the anchor can muster so high axial forces that it can always break loose. The high control quality is achieved by means of several constructive measures, which in particular the lateral forces minimized between the armature and a pole tube, in which the armature is movably arranged.

Such a known constructive feature for reducing the transverse forces is there a very close running clearance between the armature and the pole tube. In order to achieve high magnetic forces, the aim is to achieve the thinnest possible separating layer, for example, instead of a sleeve or a thick coating. Such a very thin separation layer is usefully at a layer thickness of 10 μηι to 60 μηι. The thin separating layer can be achieved, for example, by chemical or galvanic deposition of the separating layer. As a chemical method, for example, chemical nickel plating can be used. Here, a layer thickness of 45 μηι has proved to be favorable, since a high magnetic force is achieved at acceptable transverse forces. With the existing existing methods, a layer thickness from 20 μηι has proven to be sufficiently reproducible. In contrast to, for example, galvanic nickel plating, in the chemical process no electrical voltage is applied across electrodes. The layer thickness is very homogeneous in chemical nickel plating.

To produce a proportional behavior of the transmission valve, a Polkernkonus is provided in DE 10 201 1 053 023 A1. With such a Polkernkonus but also different other force / displacement curves are feasible. However, the linear force / displacement curve is mostly desired to simplify the control.

Disclosure of the invention

An object of the invention is to provide a hydraulic valve, in particular as a hydraulic transmission valve, which combines the highest possible robustness with cost-effective design. The above object is achieved according to one aspect of the invention with the features of the independent claim.

Favorable embodiments and advantages of the invention will become apparent from the further claims, the description and the drawings.

It is proposed a hydraulic valve, in particular a hydraulic transmission valve, comprising a solenoid part with a magnetizable housing, which encloses a magnet coil on an outer circumference and at least a first end side, and with a pole tube arranged in the interior of the magnet coil, in which an armature in an armature space is provided axially displaceable, and a hydraulic part with a hydraulic piston, which is guided axially displaceably in a valve bush and by means of which at least one working port optionally with at least one supply connection and at least one tank connection is connectable. The armature is provided for driving the hydraulic piston. The valve sleeve is arranged along a longitudinal axis in extension of the pole tube. In this case, a fork plug is provided integrated in a bobbin. The pole tube in this case also includes a pole and / or a pole core of the solenoid part.

In the hydraulic valve according to the invention, the fork plug is integrated as an electrical connection of the magnetic coil in the bobbin. This can be done for example by encapsulation. The bobbin as a carrier of the magnetic coil thereby engages around the magnetic coil and also serves to receive the pole tube in the interior of the bobbin and thus also the magnetic coil. Conveniently, the bobbin can be made by means of a plastic injection molding process. The integration of the fork plug into the bobbin ensures a stable mechanical connection of the fork plug to the solenoid part. In addition, by encapsulating with plastic at the same time a good electrical insulation can be achieved, so that essential parts of the fork plug, which are not covered by a plug, can be formed safe to touch. In this way, a secure attachment and contacting of the fork plug is possible.

According to an advantageous embodiment, a coil wire of the magnetic coil may be provided wound around a pin of the fork plug. In this case, a welding sleeve can be inserted over the pin of the fork plug and the coil wire, which is then electrically and mechanically connected by means of pressing and a suitable welding process such as resistance welding with the pin and the wire. In this way, a robust and reliable connection is provided, which can reach a long life even under harsh operating conditions.

According to an advantageous embodiment of the fork plug having contact lugs, with jaws for non-positive retention of a mating contact. The contact lugs represent the contact elements for conducting the electrical current. The jaws as part of the contact lugs are used to make contact with a mating connector and provide a secure mechanical fixation of the contact elements of the mating connector on the fork connector.

According to an advantageous embodiment, the contact lugs can dive with a fixing portion in the bobbin and be provided at one end of the attachment portion, the jaws and at the other end of the pin facing the jaws. The attachment portion as a mechanical and electrical connection between the jaws and the pin, which is provided for electrical connection of the coil wire of the magnetic coil, serves to fix the tabs of the fork plug in the bobbin. For this purpose, the attachment portion is expediently encapsulated at least partially by the material of the bobbin, so that the contact lugs are securely fastened to the bobbin. According to an advantageous embodiment, the hydraulic valve may have a chip protection cover which covers the pole disk with ribs. The chip protection cover can prevent metallic chips, for example by abrasion in production or by friction of the moving parts of the hydraulic valve in operation, can cause a short circuit between the terminals of the solenoid. For this purpose, the chip protection cover can be pushed as Spanschutzkappe on the bobbin or formed by molding the bobbin with the fork plug. Further, the chip protection cover can serve as a support of the plug force when mounting a mating connector on the fork plug.

According to an advantageous embodiment, the pole disk can be provided integrated in the bobbin. The pole disc serves as a magnetic closure of the magnetizable housing, which encloses the magnetic coil on an outer circumference and on at least one end side, on the side facing away from the hydraulic piston end face of the magnetic coil. The pole disk can be designed, for example, as a magnetizable disc-shaped or annular body with recesses for cable feedthroughs, wherein the recesses can be bores, for example. The pole disk may in particular be designed symmetrically in order to obtain a favorable symmetrical magnetic circuit. This Polscheibe can be advantageously integrated into the bobbin, for example, be encapsulated with the plastic material of the bobbin when the solenoid is to be executed with the bobbin overmolded. Recesses in the pole disk can be suitably injected to fill it. Thus, the pole disk can be molded together with the magnetic coil in an injection molding process. In this way, the axial space can be reduced favorably. Also hereby a particularly compact design is possible. In addition, eliminates a separate assembly step for the pole piece. Also, the tolerance situation can be so uncritical Outer diameter can be shifted because the pole disc can be aligned so low to the solenoid and the pole tube.

Conveniently, the pole disk can be at least partially encapsulated with a material of the bobbin. In this way, the fixation of the pole disk in their relative orientation to the bobbin is much easier, since the two component, once they are encapsulated, can not move against each other. Also, the sealing of the bobbin against the hydraulic fluid and / or moisture is easier to maintain.

According to an advantageous embodiment, the housing may be caulked on the pole disk or welded to the pole disk. The housing is pushed during assembly over an outer periphery of the pole disk and is fixed for example on the pole disk via a press-fit. For additional attachment of the housing on the pole disk beyond a caulking of the housing can be effected via suitable Verstemmungssegmente, which are scraped off by means of a suitable tool from the housing and / or bent and pressed onto the pole disk. As a result, it is possible to achieve a purely axial caulking of the housing on the pole disk, so that any transverse forces which may be exerted during caulking are reduced. Such caulking provides additional protection of the attachment of the housing and Polscheibe. Alternatively or additionally, it is conceivable that the housing is provided welded to the pole plate. For example, the pole disk can be subsequently provided in the axial direction on the housing and in this way can be welded flush with the housing on an outer side.

According to an advantageous embodiment, an axial force transmission between the armature and hydraulic piston can be effected by means of a separately formed pins, wherein the pin can be provided in particular guided in the valve sleeve. Advantageously, the pin in particular of non-magnetic material be executed. Such a power transmission between armature and hydraulic piston allows a mechanical decoupling between the bearing of the armature and the bearing of the hydraulic piston. In this way it is possible that only axial forces are transmitted between the two components. Transverse forces on the armature and / or hydraulic piston are thereby advantageously reduced, whereby the friction of the run of armature and / or hydraulic piston can be reduced. Also, a separation of the power transmission between armature and hydraulic piston via a separate component, as it represents the pin, a more favorable tolerance design of pole tube and valve sleeve possible because both recesses, in which run armature and hydraulic piston, are separated in this way. The pin can advantageously be designed symmetrically with respect to a transverse plane in order to facilitate assembly, since it is not necessary to pay attention to the orientation of the installation position. A favorable diameter of the pin may be, for example, 2.0 mm to 2.5 mm.

According to an advantageous embodiment, the pin may have on its circumference a recess for reducing its longitudinal bearing surface, in particular the recess may be circumferentially formed as an annular groove on the circumference. However, other forms of the recess, in particular interrupted or angular recesses, are conceivable. Such a recess reduces the possible bearing surface of the pin in the valve sleeve and thus contributes to a reduction of the friction in an axial movement of the pin. The length and depth of the recess can be designed depending on the tolerance situation and the required guide length of the pin and of a stroke of the armature and the hydraulic piston. If the recess is advantageously designed as an annular groove, the pin can be manufactured as a simple turned part. Further, the recess with respect to the axial arrangement on the pin can be designed symmetrically to the longitudinal center of the pin and thus be independent of a mounting position in the hydraulic valve. The pin can be inserted first when assembling with the front or back side. Advantageously, the pin on at least one of its two ends, a pad surface reducing structure, such as a rounded end face, in particular a ball point having. Rounded end faces such as ball joints facilitate the transmission of power between the armature and hydraulic piston, as in this way tolerance errors in the alignment of armature and hydraulic piston to each other play a lesser role. In addition, a low-friction power transmission between armature and hydraulic piston is possible. Also, it is cheaper to manufacture when ball studs are attached to the pin than at an end face of the armature and hydraulic pistons since the pin is the easier part to fabricate. Also conceivable is a ring structure or nub structure or the like. In particular, both ends of the pin have a rounded end face, a mounting of the pin is independent of its orientation possible.

According to an advantageous embodiment, a hydraulic fluid reservoir may be provided in the bobbin, which is in communication with the armature space. Alternatively, the hydraulic fluid reservoir may be provided in the housing. The reservoir, which can conveniently be filled once initial, for example, in a production-side test is in hydraulic communication with the armature space and can advantageously prevent air from entering the hydraulic valve. The reservoir can be sealed with a cover as a sealing disk on the side facing away from the armature space. The reservoir can also prevent the entry of possibly resulting from abrasion chips in the anchor space. Furthermore, the ability to displace the hydraulic fluid into the reservoir prevents additional undesirable damping. The reservoir may be favorably dimensioned such that the volume displacement effected by the stroke of the pin between the armature and the hydraulic piston is for example 10% of the reservoir volume. This way only Hydraulic fluid pushed from the armature space in the reservoir and sucked in from there again. This reduces the dirt entry into the armature space.

According to an advantageous embodiment, the bobbin in the armature space protruding projections may have as a stop for the anchor. For this purpose, the projections may be arranged on an armature on the side facing away from the hydraulic piston end face and project into the armature space. These projections can advantageously form the stop for the armature, so that the armature does not impinge flatly with its end face on the bobbin and rests. Due to the reduced contact surface of the armature on the bobbin as an anticaking effect can be achieved so low that the anchor when it stops against the bobbin does not stick to it, but can easily solve it again.

According to an advantageous embodiment, the armature can be provided biased by a spring in the direction of the hydraulic part and pressed to guide the spring, a spring plate in a recess of the armature. The spring plate can be provided by deep drawing formed from sheet metal and having a circumferential radial projection as a stop and Antiklebescheibe. The spring plate made of sheet metal can be made thin-walled and yet stiff in this way. A damping diaphragm can additionally be designed by an inner diameter, wherein the damping diaphragm can be as open as possible in order to achieve an effective damping. Due to the elastic design a secure pressing into the anchor is possible. By providing a radius as an insertion beforehand also a chip-free pressing can be ensured. Advantageously, the spring plate is formed of non-magnetic material.

According to an advantageous embodiment, the pole tube may have in a arranged in its outer circumference incision, preferably a V-shaped incision, a radially circumferential recess as a fine control contour. The recess may be formed, for example, as a circumferential annular groove. A favorable groove depth is in the range of 0.1 mm. The incision advantageously serves to focus the magnetic field lines of the magnetic coil in the direction of a region of the armature on the part of the armature facing the hydraulic piston. Due to the circumferential recess in the region of the incision, an additional favorable focus can be made in the direction of the armature, which can achieve a magnetic force gain and thus serve for fine control in the control / regulation of the armature. This is achieved particularly advantageously by the V-shape of the incision. This ensures a particularly efficient operating behavior of the hydraulic valve. Through the recess, a remaining wall thickness of the pole tube in the region of the incision can be additionally reduced with otherwise the same strength of the pole tube. In this way, effects of the magnetic field focused in the incision in the incision, as might occur, for example, due to a parasitic magnetic flux, can be reduced and the magnetic force in this region increased. As a result, the control behavior of the solenoid part can be further improved favorably at substantially constant strength of the pole tube against mechanical deformation due to external forces during manufacture and during operation of the hydraulic valve.

Advantageously, the pole tube on an outer surface in a longitudinal region between the first end face and one of these opposite the second end face of the magnetic coil having the annular circumferential recess. In order to make good use of the effect of focusing the magnetic field generated by the magnetic coil, it is expedient to arrange the incision on a part of the pole tube, which when properly installed. lies in the region between the two end faces of the magnetic coil. Thus, the effect can be exploited most favorably and used advantageously for a control of the armature.

Conveniently, the incision at its opposite side flanks a first cone-shaped contour and with respect to a plane perpendicular to the longitudinal direction opposite thereto arranged second cone-shaped contour, wherein the conical contours can be formed open to the outer surface toward Such a cone-shaped design allows a favorable focusing of the magnetic field generated by the magnetic coil. Further, the mechanical stability of the pole tube can thereby be obtained in a favorable manner, so that the hydraulic valve can be controlled favorably over a wide range of mechanical and thermal stress. The slope of the conical contours may be formed differently steep, whereby a characteristic of the magnetic characteristic can be influenced.

Suitably, the first and the second cone-shaped contour may be connected by a connecting web, wherein a wall thickness of the connecting web may be less than a wall thickness of the pole tube. In particular, the wall thickness in the region of the connecting web can be substantially lower than the continuous wall thickness of the pole tube. Thus, wall thicknesses of the connecting web may typically be in the range of 0.2 to 0.3 mm, so that a magnetic effect of the pole tube in the region of the incision is almost completely interrupted. A possible thin connecting web has proven to be advantageous for the focusing of the magnetic field, so as to achieve a favorable controllability of the magnetic part.

Further, the incision on an inner surface of the pole tube may have at least one circumferential recess, wherein in particular the at least one recess may be arranged in the region of the connecting web. Due to the arrangement of at least one circumferential recess, which may be formed, for example, as a circumferential annular groove on the inner surface of the pole tube, the hydraulic valve according to the invention has the additional advantage of reducing the transverse magnetic forces in the region of the relief shoulder to minimize the magnetosuppression and thus the valve hysteresis. The recess in the incision can laterally in the connecting web at the transition to the conical trained side edge may be arranged. Advantageously, this side edge may be steeper than the opposite side edge of the incision.

Further advantages that result from a concept of the punctures on the inner surface of the pole tube, on the one hand, an increase in the robustness of the solenoid part / valve against forces introduced in the production of individual parts. Furthermore, the connecting web can be mechanically relieved at the pole hat, since the armature runs directly on only a part of the connecting web. A functional influence of the magnet due to plastic deformation of the thin-walled connecting web during the production of the Polhuts is reduced, such as deformation by torsion or elastic displacement of the wall during the pre-and finish machining of the pole tube, due to the wall thickness differences.

Another advantage is an increase in the robustness of the magnet / valve against thermal influences / forces during operation. The connecting bridge is mechanically relieved. Thus, a functional influence of the magnet due to thermal deformation and different thermal expansions of the sensitive, thin-walled connecting web is avoided.

Advantageously, the circumferential recess and the at least one recess on the pole tube can be arranged axially spaced. Such a spatial separation in the axial direction proves to be advantageous for the focusing of the magnetic field and in particular for the reduction of parasitic magnetic flux. In this case, the advantageous combination of externally arranged on the pole tube recess and in the radial direction thereto internal puncture at a distance of approximately the axial width of the recess and / or the recess, which may be, for example 0.2 mm to 0.3 mm, especially advantageous. The radial depth of the groove may conveniently be chosen in the range of 0.1 mm. Depending on the design of the hydraulic valve other sizes may be provided. According to an advantageous embodiment, the pole tube and the valve sleeve may be integrally formed. The hydraulic valve according to the invention, the pole tube and valve sleeve in one piece integrally formed, has significant advantages in the operation of the hydraulic valve, since possible component deformations and a resulting negative influence on the armature run in the pole tube and thus caused a magnetic / valve hysteresis can be reduced. By a common, one-piece production of pole tube and valve sleeve coaxiality of polar axis and valve sleeve axis is easier to achieve than in a production of pole tube and valve sleeve as separate components, since assembly inaccuracies play only a minor role. Both axes must therefore be reliably matched during production. This ensures a favorable configuration of the run of the armature in the pole tube and the hydraulic piston in the valve sleeve and an advantageous power transmission from the armature to the hydraulic piston.

Due to the coaxiality of the pole tube and the valve bush, a large immersion depth of the armature in the solenoid of the solenoid part can be realized in a structurally simpler manner, whereby a favorable and effective operation of the hydraulic valve can be ensured. This improves the functioning of the entire hydraulic valve.

The advantageous coaxiality of pole tube and valve bush further favors a reduction of the magnetic transverse forces on the armature, since the most accurate alignment of the armature run in the axis of the solenoid by the one-piece design of pole tube and valve sleeve is easier to achieve.

The one-piece design of pole tube and valve sleeve further allows a reduction in the number of components of the hydraulic valve and consequent simplification of assembly, resulting in a cost reduction and a contributes to a lower number of errors in the assembly. Also, the overall operation of the hydraulic valve becomes more reliable because during operation, the risk of component deformation and concomitant functional impairment in valve operation can be reduced. A production of the one-piece component as a turned part is possible in a favorable manner.

Advantageously, the armature can be guided in a recess of the pole tube. In this way, the armature can be favorably aligned and guided in the axis of the solenoid, which is an advantage for an efficient drive of the hydraulic valve. By a favorable production of the pole tube as a rotating part, the recess can be made very accurately with low tolerances and thereby low-friction running of the armature can be ensured in the recess, whereby the response and operating parameters of the hydraulic valve can be improved.

Conveniently, the hydraulic piston can be arranged at an end remote from the armature by means of a spring element at an end facing away from the armature of the valve sleeve. The armature is operatively coupled to the hydraulic piston, in particular mechanically coupled, in particular the armature can be mechanically actuated by the hydraulic piston, e.g. indirectly with a pin (pin), which is arranged between the armature and hydraulic piston, or directly with a piston arranged on the small plunger. By supported on the valve sleeve spring element can be generated in a favorable manner, a restoring force, which favors operation of the magnetic drive of the hydraulic valve as a spring-mass oscillator. As a result, the entire operation of the hydraulic valve is favorably influenced.

Brief description of the drawings Further advantages emerge from the following description of the drawing. In the drawings, embodiments of the invention are shown. The drawings, the description and the claims contain numerous features in combination. The person skilled in the art will expediently also consider the features individually and combine them into meaningful further combinations.

They show by way of example:

1 shows a longitudinal section through a hydraulic valve after a

 Embodiment of the invention in a basic position;

2 shows a longitudinal section through a hydraulic valve after another

 Embodiment of the invention in a basic position;

3 shows a partial longitudinal section through the bobbin with integrated fork connector according to an embodiment of the invention.

Fig. 4 is a plan view of the hydraulic valve from the side of

 Fork plug;

Fig. 5 is a detail view of a pin of the fork plug;

Fig. 6 is a plan view of a chip protection cover; and

7 is a partial longitudinal section of the chip protection cover of Figure 6.

Embodiments of the invention In the figures, the same or similar components are numbered with the same reference numerals. The figures are merely examples and are not intended to be limiting.

FIG. 1 shows in a longitudinal section a hydraulic valve 1, in particular a hydraulic transmission valve in a basic position. It is a pressure control valve.

This hydraulic valve 1 is used for example in a dual-clutch transmission. For this purpose, valve bushings 5 of hydraulic parts 2 of a plurality of similarly constructed hydraulic valves are inserted into a control plate of the dual-clutch transmission. The valve sleeves 5 are designed as turned parts. Electromagnetic parts 3 of the transmission valves 1 respectively connected to the hydraulic parts 2 project out of the control plate and are surrounded by hydraulic fluid. Each of the solenoid parts 3 has a magnetizable housing 4.

The hydraulic valve 1 shown in Figure 1 comprises the solenoid part 3 with the magnetizable housing 4, which encloses a magnetic coil 7 on an outer circumference 50 and at least a first end face 52, and with a arranged inside the magnetic coil 7 pole tube 6, in which an armature 10 is provided axially displaceable in an armature space 56. Further, the hydraulic valve 1 comprises the hydraulic part 2 with a hydraulic piston 1 6, which is axially displaceable in the valve sleeve 5 and by means of which at least one working port A with either a supply port P and a tank port T is connectable. The armature 10 is provided for driving the hydraulic piston 1 6. The valve sleeve 5 is arranged along a longitudinal axis L in extension of the pole tube 6. The magnetic coil 7 is embedded in the bobbin 8 in the housing 4, for example by means of press fit added. Alternatively, the magnetic coil 7 may be encapsulated with plastic material of the bobbin 8.

As can be seen from FIG. 1, the valve bush 5 is provided in one piece with the pole tube 6, so that the hydraulic valve 1 has fewer components and the assembly process can be simplified. Due to the coaxiality of the pole tube 6 and the valve bushing 5, a large immersion depth of the armature 10 into the magnet coil 7 of the solenoid part 3 can be implemented in a structurally simpler manner, whereby a favorable and effective operation of the hydraulic valve 1 can be ensured. Thus, the operation of the entire hydraulic valve 1 is improved.

The advantageous embodiment of the coaxiality of pole tube 6 and valve sleeve 5 further favors a reduction of the magnetic transverse forces on the armature 10, since the most accurate alignment of the armature run in the axis of the solenoid 7 by a one-piece design of pole tube 6 and valve sleeve 5 is easier to achieve ,

The pole tube 6 has a favorable influence on the magnetic flux, for example, a V-shaped recess 9.

The armature 10 is provided in an armature space 56 forming recess 1 1 of the pole tube 6 axially displaceable and has a central channel 12, which is designed as a bore. This central channel 12 is extended with a shoulder at the front end of the armature 10 to a recess 13 of larger diameter, which is also designed as a bore. In this larger recess 13 an anti-adhesive disc 14 is used, which has one or more eccentric to the longitudinal axis L arranged small orifices apertures 15 which connect the armature space with the central channel 12. The anti-stick disc 14 prevents sticking of the armature 10 to the magnetically conductive valve sleeve 5 of the hydraulic part 2 with a fully disengaged armature 10. The hydraulic part 2 has the hydraulic piston 1 6, which is guided axially displaceably in the valve sleeve 5. The hydraulic piston 1 6 is arranged at an end facing away from the armature 10 60 supported by a spring member 17 on the valve sleeve 5. In this case, the hydraulic piston 1 6 against the force of the helical compression spring spring element 17 is displaceable, which is supported on a, attached in the valve sleeve 5 sieve 21. For guiding and centering the helical compression spring 17, the sieve 21 has a spring guide 22. Depending on the position of the hydraulic piston 1 6, the working port A by means of a circumferential annular groove 18 and longitudinal and transverse bores 20, 19 in the hydraulic piston 1 6 with the supply port P or the tank port T connectable.

If the hydraulic piston 1 6 is located in the initial position according to FIG. 1 due to the lack of application of a sufficiently large voltage to the magnet coil 7, the hydraulic fluid is conducted from the working port A to the tank outlet T.

The axial force transmission between the armature 10 and the hydraulic piston 16 by means of a pin 23 which is guided in the valve sleeve 5 is arranged. The pin 23 allows a decoupling between anchor and piston bearing. A circumferential recess 24 on its circumference, which is formed as a peripheral annular groove 68, thereby allowing a reduction of the support surface, whereby the friction can be reduced. At the same time advantageously only axial forces are transmitted through the pin 23 and the tolerance situation is also significantly improved. For a possible frictionless power transmission, the hydraulic piston 1 6 and the Antiklebescheibe 14 ball studs. In order to simplify these two components, it is alternatively conceivable to form a pad-reducing structure, preferably rounded end faces, in particular ball studs, on the pin 23. As can be seen further in FIG. 1, a pole disk 28 is provided integrated in the bobbin 8, for example by being at least partially encapsulated by the plastic material of the bobbin 8, or by injecting recesses of the pole disk 28. As a result, a smaller axial space is achieved and the assembly of the hydraulic valve 1 is simplified. The pole plate 28 serves as a magnetic closure of the magnetizable housing 4, which encloses the magnetic coil 7 on the outer circumference 50 and at least one end face 52 on the hydraulic piston 1 6 opposite end face 54 of the magnetic coil 7. The pole plate 28 may be magnetizable, such as disk-shaped or annular, be configured body with recesses for cable penetrations, wherein the recesses may be, for example, holes.

The bobbin 8 closes off the armature space 56 at one end of the hydraulic valve 1. In this case, protrusions 25 projecting into the armature space 56 form a stop for the armature 10, so that the bearing surface reduced as a result has an anti-adhesive effect.

A provided in the bobbin 8 hydraulic fluid reservoir 26, which is preferably initially filled once, is in communication with the armature space 56 and prevents air from entering the hydraulic valve. 1 Furthermore, the possibility of displacement of the hydraulic fluid into the reservoir 26 prevents additional undesirable damping. The reservoir 26 is dimensioned such that the volume displacement effected by the pin stroke is significantly lower than the reservoir volume. As a result, the dirt entry into the armature space 56 is reduced.

In order to prevent a short circuit caused by foreign bodies between a forked plug 35, not shown, and the pole disk 28, the hydraulic valve 1 further has a chip protection cover 27, which covers the pole disk 28 with ribs. The fork plug 35 is also partially in Spool 8 provided injected, so that a secure attachment of the fork plug 35 and thus a secure contact can be ensured.

For improved connection of the coil wire 37 to a pin 36 of the fork plug 35, the coil wire 37 is wound around the pin 36 of the fork plug 35. Subsequently, a welding sleeve 108 is inserted over the wrapped pin 36 and pin 36 and coil wire 37 are suitably connected by means of compression and resistance welding.

The housing 4, which projects beyond the pole disk 28, is additionally caulked on the pole disk 28. The housing 4 is pushed during assembly over an outer periphery of the pole plate 28 and is fixed for example on the pole plate 28 via a press-fit. For additional attachment of the housing 4 on the pole plate 28, a caulking of the housing 4 can also be effected via suitable Verstemmungssegmente, which are scraped off by means of a suitable tool of the housing 4 and / or bent and pressed onto the pole piece 28. As a result, it is possible to achieve a purely axial caulking of the housing 4 on the pole disk 28 so that any transverse forces which may be exerted during caulking are reduced. Such caulking provides additional protection of the attachment of housing 4 and pole disc 28. Alternatively or additionally, it is conceivable that the housing 4 is provided welded to the pole plate 28. For example, the pole plate 28 may be provided in the axial direction of the housing 4 and then welded in this manner on an outer side flush with the housing 4.

FIG. 2 is a longitudinal section of a second exemplary embodiment of a hydraulic valve 1 according to the invention in the basic position. In a repeated description of the same components as in Figure 1 is omitted and to avoid unnecessary repetition to the description in FIG 1 referenced. In the embodiment shown in Figure 2 pole tube 6 and valve sleeve 5 are designed as two components. The valve sleeve 5 of the second embodiment has a shorter end portion 46 of the hydraulic bushing 5, which is inserted into the pole tube 6.

In contrast to the first exemplary embodiment, the working connection A is connected to the supply connection P in the basic position shown. For this purpose, a spring 40 accommodated in a recess 41 of the pole tube 6 biases the armature 10 in the direction of the hydraulic part 2. In a recess 32 of the armature 10, a spring plate 43 is pressed, which guides the spring 40 and serves at the same time by a circumferential radial projection 44 as a stop and Antiklebescheibe. The spring plate 43 is advantageously formed by deep drawing from sheet metal. Due to the shorter length of the armature 10 due to the spring 40, the pin 23 is made shorter for axial power transmission.

FIG. 3 shows a partial longitudinal section through the bobbin 8 with integrated forked plug 35 according to an exemplary embodiment of the invention. The bobbin 8 can be made as a plastic injection molded part, which is made by molding the magnetic coil 7. The fork plug 35 can be expediently also injected into the bobbin 8, so as to ensure a secure attachment of the fork plug 35 and a reliable contacting of the not shown magnetic coil 7 and thus the hydraulic valve 1. In Figure 3 it can be seen how the fork plug 35, which has two contact lugs 100, is partially injected into the bobbin 8. The contact lugs 100 in this case comprise jaws 102, which serve for contacting by a not shown mating connector and are outside the overmolded area, and a fastening portion 104, which is partially injected into the bobbin 8 and a pin 36, which serves as a connection to a coil wire 37 of Magnetic coil 7 is used. Also, molded around by the material of the bobbin 8, the pole plate 28 is shown. The patch protection cover 27 prevents short circuits uncovered live parts of the fork plug 35, in particular the connection pins 36 by conductive impurities and components of the hydraulic fluid, such as by abrasion during operation of the hydraulic valve. 1

Figure 4 shows a plan view of the hydraulic valve 1 from the side of the fork plug 35. In the plan view of the fork plug 35 can be seen with its two contact lugs 100 which protrude through the exposed jaws 102. Further, the pins 36, which serve to contact the coil wire 37 of the magnetic coil 7, shown. This contacting is shown in Figure 5 as a section. The fork plug 35 is integrated in the bobbin 8 and partially encapsulated with the material of the bobbin 8. The pole plate 28 is partially integrated into the bobbin 8.

FIG. 5 shows a detailed view of a pin 36 of the fork plug 35. The rod-shaped pin 36, which can be seen in cross section, is surrounded by the welding sleeve 108. The coil wire 37 is inserted within the welding sleeve 37 between the pin 36 and an inner wall of the welding sleeve 108. Thus, by means of pressing the welding sleeve 108 and / or welding, for example by resistance welding, an electrically conductive connection between the coil wire 37 and pin 36 are produced. Such a connection also represents a mechanically reliable and durable durable connection.

FIG. 6 shows a plan view of the chip protection cover 27.

The chip protection cover 27 is designed as a plastic cap, which can be plugged onto the bobbin 8 as a mechanical conclusion. The chip protection cover 27 has various ribs 39, which serve to cover the free live parts of the fork plug 35 and the coil wire 37 of the solenoid 7. As a result, short circuits between the individual live parts of the hydraulic valve 1 through electrically conductive foreign body in the hydraulic fluid, such as abrasion of metallic parts, avoided.

FIG. 7 shows a partial longitudinal section of the chip protection cover 27. The chip protection cover 27 can be plugged onto the coil body 8 in the form of a mechanical protective cap and covers with its ribs 39, which have an irregular structure adapted to the contours of the coil body 8 and the fork plug 35 lying live parts of the fork plug 35 and the solenoid 7 from.

The features described do not necessarily have to be combined and can also be used individually in a hydraulic valve.

Claims

claims 1 . Hydraulic valve (1), in particular a hydraulic transmission valve, comprising an electromagnet part (3) with a magnetizable housing (4) which encloses a magnet coil (7) on an outer circumference (50) and on at least one first end face (52) and with a magnet Inside the magnetic coil (7) arranged pole tube (6) in which an armature (10) in an armature space (56) is axially displaceable, a hydraulic part (2) with a hydraulic piston (1 6), which axially displaceable in a valve sleeve ( 5) and by means of which at least one working connection (A) can be connected optionally to at least one supply connection (P) and at least one tank connection (T),  wherein the armature (10) is provided for driving the hydraulic piston (1 6),  wherein the valve sleeve (5) along a longitudinal axis (L) in extension of the pole tube (6) is arranged, and  wherein a fork plug (35) is provided integrated in a bobbin (8). 2. A hydraulic valve according to claim 1, wherein a coil wire (37) of the magnetic coil (7) is wound around a pin (36) of the fork plug (35) and the coil wire (37) and the pin (36) by means of a welding sleeve (108). pressed and welded. 3. Hydraulic valve according to claim 1 or 2, wherein the fork plug (35) comprises contact lugs (100), with clamping jaws (102) for non-positive retention of a mating contact. 4. A hydraulic valve according to claim 3, wherein the contact lugs (100) with a Insert mounting portion (104) in the bobbin (8) and at one end of the mounting portion (104), the jaws (102) and at the other end of the pin (36) are provided facing the jaws (102). 5. Hydraulic valve according to one of the preceding claims, wherein the hydraulic valve has a chip protection cover (27) which with ribs (39) covers a pole disc (28). 6. Hydraulic valve according to one of the preceding claims, wherein the pole disk (28) is provided integrated in the bobbin (8). 7. A hydraulic valve according to claim 5 or 6, wherein the housing (4) caulked on the pole plate (28) or welded to the pole plate (28) is provided. 8. Hydraulic valve according to one of the preceding claims, wherein an axial force transmission between armature (10) and hydraulic piston (1 6) by means of a separately formed pins (23), wherein the pin (23) is provided in particular in the valve sleeve (5) , wherein the pin (23) is designed in particular non-magnetic. 9. A hydraulic valve according to claim 8, wherein the pin (23) has at its periphery a recess (24) for reducing its longitudinal bearing surface, in particular wherein the recess (24) circumferentially around the annular groove (68) is formed. 10. Hydraulic valve according to one of the preceding claims, wherein in the bobbin (8) a hydraulic fluid reservoir (26) is provided which communicates with the armature space (56). 1 1. Hydraulic valve according to one of the preceding claims, wherein the bobbin (8) in the armature space (56) protruding projections (25) as a stop for the armature (10). 12. Hydraulic valve according to one of the preceding claims, wherein the armature (10) by means of a spring (40) in the direction of the hydraulic part (2) is provided biased and to guide the spring (40) a spring plate (43) in a recess (32) of the Anchor (10) is pressed, wherein the spring plate (43) is provided by deep drawing formed from sheet metal and having a circumferential radial projection (44) as a stop and Antiklebescheibe. 13. Hydraulic valve according to one of the preceding claims, wherein the pole tube (6) arranged in a in its outer periphery, preferably V-shaped, recess (9) has a radially circumferential recess (29) as a fine control contour. 14. Hydraulic valve according to one of the preceding claims, wherein the pole tube (6) and the valve sleeve (5) are integrally provided.