WO2017005496A1 - Soupape hydraulique, notamment soupape de transmission hydraulique - Google Patents

Soupape hydraulique, notamment soupape de transmission hydraulique Download PDF

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Publication number
WO2017005496A1
WO2017005496A1 PCT/EP2016/064512 EP2016064512W WO2017005496A1 WO 2017005496 A1 WO2017005496 A1 WO 2017005496A1 EP 2016064512 W EP2016064512 W EP 2016064512W WO 2017005496 A1 WO2017005496 A1 WO 2017005496A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
armature
hydraulic valve
valve
pole
Prior art date
Application number
PCT/EP2016/064512
Other languages
German (de)
English (en)
Inventor
Michael BIERKOCH
Bernd Franz
Thomas Jacob
Dieter Maisch
Original Assignee
Hilite Germany Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hilite Germany Gmbh filed Critical Hilite Germany Gmbh
Priority to CN201690000936.7U priority Critical patent/CN208169646U/zh
Publication of WO2017005496A1 publication Critical patent/WO2017005496A1/fr

Links

Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/128—Encapsulating, encasing or sealing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/04—Construction of housing; Use of materials therefor of sliding valves
    • F16K27/048—Electromagnetically actuated valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/0606—Multiple-way valves fluid passing through the solenoid coil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0675—Electromagnet aspects, e.g. electric supply therefor
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/081—Magnetic constructions
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F7/1607—Armatures entering the winding
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F2007/062—Details of terminals or connectors for electromagnets
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/081—Magnetic constructions
    • H01F2007/083—External yoke surrounding the coil bobbin, e.g. made of bent magnetic sheet
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/081—Magnetic constructions
    • H01F2007/085—Yoke or polar piece between coil bobbin and armature having a gap, e.g. filled with nonmagnetic material
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F2007/1661—Electromagnets or actuators with anti-stick disc

Definitions

  • Hydraulic valve in particular hydraulic transmission valve
  • 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.
  • the gear valve 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.
  • a hydraulic valve 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.
  • 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 ⁇ to 60 ⁇ .
  • the thin separating layer can be achieved, for example, by chemical or galvanic deposition of the separating layer.
  • chemical nickel plating can be used.
  • a layer thickness of 45 ⁇ 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 ⁇ has proven to be sufficiently reproducible.
  • no electrical voltage is applied across electrodes.
  • the layer thickness is very homogeneous in chemical nickel plating.
  • 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.
  • 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.
  • 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.
  • 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.
  • the fork plug is integrated as an electrical connection of the magnetic coil in the bobbin.
  • 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.
  • 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.
  • 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.
  • a coil wire of the magnetic coil may be provided wound around a pin of the fork plug.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the chip protection cover can be pushed as Spantikkappe 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.
  • 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 Policrobial 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.
  • 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.
  • 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.
  • the pole disk can be at least partially encapsulated with a material of the bobbin.
  • 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.
  • the sealing of the bobbin against the hydraulic fluid and / or moisture is easier to maintain.
  • 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.
  • 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.
  • Verstemmungssegmente which are scraped off by means of a suitable tool from the housing and / or bent and pressed onto the pole disk.
  • Such caulking provides additional protection of the attachment of the housing and Polin.
  • the housing is provided welded to the pole plate.
  • the pole disk can be subsequently provided in the axial direction on the housing and in this way can be welded
  • 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.
  • the pin in particular of non-magnetic material be executed.
  • 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.
  • 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.
  • a recess for reducing its longitudinal bearing surface
  • the recess may be circumferentially formed as an annular groove on the circumference.
  • 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.
  • 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.
  • 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.
  • a low-friction power transmission between armature and hydraulic piston is possible.
  • both ends of the pin have a rounded end face, a mounting of the pin is independent of its orientation possible.
  • a hydraulic fluid reservoir may be provided in the bobbin, which is in communication with the armature space.
  • 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.
  • 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.
  • the bobbin in the armature space protruding projections may have as a stop for the anchor.
  • 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.
  • 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 Antiklebeact.
  • 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.
  • the spring plate is formed of non-magnetic material.
  • 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.
  • 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.
  • 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.
  • 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
  • a cone-shaped design allows a favorable focusing of the magnetic field generated by the magnetic coil.
  • 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.
  • 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.
  • the wall thickness in the region of the connecting web can be substantially lower than the continuous wall thickness of the pole tube.
  • 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.
  • 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.
  • the hydraulic valve according to the invention 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.
  • this side edge may be steeper than the opposite side edge of the incision.
  • Another advantage is an increase in the robustness of the magnet / valve against thermal influences / forces during operation.
  • the connecting bridge is mechanically relieved.
  • a functional influence of the magnet due to thermal deformation and different thermal expansions of the sensitive, thin-walled connecting web is avoided.
  • 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.
  • 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.
  • 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.
  • 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.
  • the armature can be guided in a recess of the pole tube.
  • 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.
  • 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.
  • 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.
  • a pin pin
  • Embodiment of the invention in a basic position
  • Embodiment of the invention in a basic position
  • FIG 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
  • Fig. 5 is a detail view of a pin of the fork plug
  • Fig. 6 is a plan view of a chip protection cover
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the sieve 21 has a spring guide 22.
  • 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.
  • 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.
  • the hydraulic piston 1 6 and the Antiklebeattach 14 ball studs are also significantly improved.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • 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.
  • housing 4 is provided welded to the pole plate 28.
  • 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.
  • 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.
  • the working connection A is connected to the supply connection P in the basic position shown.
  • 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.
  • 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 Antiklebecons.
  • 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.
  • 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.
  • 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.
  • 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.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

La présente invention concerne une soupape hydraulique (1), notamment une soupape de transmission hydraulique, comprenant : une partie électro-aimant (3) comprenant un boîtier (4) magnétisable qui entoure une bobine magnétique (7) au niveau d'une périphérie extérieure (50) et au niveau d'au moins un premier côté frontal (52), ainsi qu'un tube polaire (6) disposé à l'intérieur de la bobine magnétique (7), dans lequel se trouve un induit (10) pouvant effectuer un mouvement axial dans une chambre d'induit (56) ; et une partie hydraulique (2) comprenant un piston hydraulique (16) qui peut effectuer un mouvement axial dans une chemise de soupape (5) et au moyen duquel au moins un raccord de travail (A) peut de manière sélective être relié à au moins un raccord d'alimentation (P) et à au moins un raccord de réservoir (T). Selon l'invention, l'induit (10) est conçu pour entraîner le piston hydraulique (16). La chemise de soupape (5) est disposée dans le prolongement du tube polaire (6) le long d'un axe longitudinal (L). Une fourche de contact (35) est intégrée à un corps de bobine (8).
PCT/EP2016/064512 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique WO2017005496A1 (fr)

Priority Applications (1)

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DE102015110725.5 2015-07-03
DE102015110725 2015-07-03
DE102015120983.7A DE102015120983A1 (de) 2015-07-03 2015-12-02 Hydraulikventil, insbesondere hydraulisches Getriebeventil
DE102015120983.7 2015-12-02

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PCT/EP2016/064521 WO2017005497A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique
PCT/EP2016/064507 WO2017005494A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique
PCT/EP2016/064494 WO2017005493A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique
PCT/EP2016/064529 WO2017005498A1 (fr) 2015-07-03 2016-06-23 Coupelle de ressort et vanne hydraulique, notamment vanne de transmission hydraulique
PCT/EP2016/064512 WO2017005496A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique

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PCT/EP2016/064507 WO2017005494A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique
PCT/EP2016/064494 WO2017005493A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique
PCT/EP2016/064529 WO2017005498A1 (fr) 2015-07-03 2016-06-23 Coupelle de ressort et vanne hydraulique, notamment vanne de transmission hydraulique

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CN110783054B (zh) * 2019-12-12 2024-07-02 威海万泰磁电科技有限公司 一种具有分体式联结体的电磁铁
DE102020204092A1 (de) 2020-03-30 2021-09-30 Continental Teves Ag & Co. Ohg Elektromagnetventil
DE102022205118A1 (de) 2022-05-23 2023-11-23 Zf Friedrichshafen Ag Verfahren zum Betreiben eines Stellmagneten

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CN208574226U (zh) 2019-03-05
DE102015120984A1 (de) 2017-01-05
WO2017005498A1 (fr) 2017-01-12
WO2017005494A1 (fr) 2017-01-12
CN208169648U (zh) 2018-11-30
WO2017005493A1 (fr) 2017-01-12
WO2017005497A1 (fr) 2017-01-12
CN208169646U (zh) 2018-11-30
DE102015120983A1 (de) 2017-01-05
CN208574225U (zh) 2019-03-05
DE102015120992A1 (de) 2017-01-05
CN208169647U (zh) 2018-11-30
DE102015120981A1 (de) 2017-01-05
DE102015120982A1 (de) 2017-01-05

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