WO2017005497A1 - Soupape hydraulique, notamment soupape de transmission hydraulique - Google Patents

Soupape hydraulique, notamment soupape de transmission hydraulique Download PDF

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Publication number
WO2017005497A1
WO2017005497A1 PCT/EP2016/064521 EP2016064521W WO2017005497A1 WO 2017005497 A1 WO2017005497 A1 WO 2017005497A1 EP 2016064521 W EP2016064521 W EP 2016064521W WO 2017005497 A1 WO2017005497 A1 WO 2017005497A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
armature
valve
valve according
pole
Prior art date
Application number
PCT/EP2016/064521
Other languages
German (de)
English (en)
Inventor
Michael BIERKOCH
Thomas Jacob
Andreas Knecht
Dieter Maisch
Hartmut Weber
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 CN201690000943.7U priority Critical patent/CN208574225U/zh
Publication of WO2017005497A1 publication Critical patent/WO2017005497A1/fr

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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. 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.
  • 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 hydraulic fluid reservoir is provided in a bobbin, which is in fluid communication with the armature space.
  • the pole tube comprises a pole and / or a pole core of the solenoid part.
  • a hydraulic fluid reservoir is provided in the bobbin, which is in communication with the armature space.
  • the bobbin as a carrier of the magnetic coil engages around the magnetic coil and also serves to accommodate the pole tube inside the coil body and thus also the magnetic coil. In some cases, it is also useful to inject the pole tube in the coil carrier with.
  • the bobbin can be made by means of a plastic injection molding process.
  • 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 stands with the armature space in hydraulic fluid connection and can advantageously prevent air into the hydraulic valve, even with fluctuating fluid level.
  • a channel inside the armature can further direct the hydraulic fluid into a front part of the armature space facing the hydraulic piston. From the front armature space, the hydraulic fluid passes into a region of a pin, which is guided in the hydraulic bush and serves for the axial force transmission between the armature and the hydraulic piston. Thus, the hydraulic fluid is in fluid communication between the hydraulic fluid reservoir and the volume in which the pin is moving.
  • the hydraulic fluid reservoir is provided as a cavity in the bobbin and is thus to produce cost-neutral without additional tools.
  • 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. In this way, only hydraulic fluid from the armature space is pushed into the reservoir and sucked in from there. This reduces the dirt entry into the armature space.
  • the Hydraulic reservoir can advantageously be provided with a cover, or be constructively designed so that it is covered upwards, so that the hydraulic reservoir sucks or is filled via corner or a labyrinth hydraulic fluid. This reduces a dirt entry into the hydraulic reservoir and thus into the armature space.
  • the hydraulic reservoir is also arranged at the end of the solenoid part, which faces away from the hydraulic part, so that due to the prevailing there lower flow of hydraulic fluid less dirt can be whirled up and registered in the armature space.
  • 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 can be made in particular of non-magnetic material.
  • 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 may be provided in the normal operation by a stroke volume of the pins effected volume exchange of the hydraulic fluid with the hydraulic fluid reservoir.
  • the stroke volume between armature and hydraulic piston will be temporarily changed during a movement of the pin, causing a displacement of the volume of the hydraulic fluid in this area.
  • the hydraulic fluid volume in the guide area of the pin can increase and decrease in operation. Due to the hydraulic connection between the hydraulic fluid reservoir and the stroke volume of the pin, the hydraulic fluid can be pushed back and forth. If the capacity of the hydraulic fluid reservoir is large enough, the reservoir will suffice to replenish the stroke volume of the pin, even with smaller hydraulic leaks of the pin.
  • an exchange of the hydraulic fluid of the stroke volume of the pin is reduced with the hydraulic environment of the hydraulic valve and thus reduces the risk that potentially harmful abrasion can get into the area of the pin or the hydraulic piston.
  • the connection of the hydraulic reservoir with the hydraulic fluid of the environment can be done over corner or through a labyrinth, whereby a dirt entry into the hydraulic reservoir and thus into the armature space can be reduced.
  • a capacity of the hydraulic fluid reservoir can be a multiple, for example ten times, the stroke volume of the pin.
  • the replacement of the hydraulic fluid with the hydraulic environment of the hydraulic valve can be reduced if the capacity of the hydraulic fluid reservoir is in the range of ten times the stroke volume of the pin.
  • the reservoir is sufficient to compensate for minor hydraulic leaks to the hydraulic environment by guiding gaps of the moving parts of the hydraulic valve such as pin and hydraulic piston and thus to reduce the exchange.
  • the bottom of the hydraulic reservoir can conveniently in one intended installation position can be arranged significantly lower than the lower walls of the connecting holes in the armature space, whereby a dirt entry into the armature space can be reduced because possibly located in the hydraulic fluid dirt sinks and can settle at the bottom of the hydraulic reservoir.
  • a chip protection cover may be provided, wherein a part of the hydraulic reservoir is integrated in the chip protection cover and / or the chip protection cover serves as a cover for the hydraulic reservoir.
  • the hydraulic valve may have a chip protection cover, which covers the pole disk with ribs and / or forms a cover or a labyrinth over a suction point of the hydraulic reservoir.
  • the chip protection cover can prevent metallic chips, for example by abrasion and residual dirt from the production or by friction of the moving parts in the transmission and the hydraulic valves 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 chip protection cover can form a cover or a labyrinth for a suction point of the hydraulic reservoir, so that the suction point is covered upwards and hydraulic fluid is sucked or filled over the corner or over the labyrinth and thus a dirt entry into the hydraulic reservoir and thus into is reduced with this associated anchor space.
  • the pin may have at its periphery a recess for reducing its longitudinal support surface, in particular the recess may circumferentially around as an annular groove be educated.
  • 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.
  • a pole disk and / or a fork plug can be provided integrated into a 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 Polular 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.
  • a fork plug as an electrical connection of the magnetic coil may conveniently also be integrated into the bobbin by encapsulation. In this way, a stable mechanical connection of the fork plug is ensured with the solenoid part. In addition, at the same time a good electrical insulation can be achieved by encapsulation, so that essential parts of the fork plug, which are not covered by a plug, can be formed safe to touch.
  • 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.
  • 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 flush with the housing on an outer side.
  • 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. In this way, a robust and reliable connection is provided, which can reach a long life even under harsh operating conditions.
  • 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 lead-in 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, the intended installation. lies in the region between the two end faces of the magnetic coil.
  • the incision may favorably have on its opposite side flanks a first conical contour and a second conical contour arranged opposite to a plane perpendicular to the longitudinal direction, the conical contours being able to be open towards the outer surface.
  • a conical design permits favorable focusing of the cone 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 may be arranged laterally in the connecting web at the transition to the conical side edge.
  • 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.
  • a large immersion depth of the armature into the magnet coil of the electromagnet part can also be designed easier to implement, whereby a favorable and effective operation of the hydraulic valve can be ensured. This improves the functioning of the entire hydraulic valve.
  • 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, which contributes to a cost reduction and 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 anchor is with the hydraulic piston coupled operatively connected, in particular mechanically coupled, in particular, the armature can be mechanically actuated by the hydraulic piston, for example 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 is a partially longitudinally cut hydraulic valve after a
  • Embodiment of the invention shows a cross section through the hydraulic valve from FIG. 3 in the region of the hydraulic fluid reservoir.
  • 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. Furthermore, the hydraulic valve 1 comprises the hydraulic part 2 with a hydraulic piston 1 6, which is guided axially displaceably in the valve bushing 5 and by means of which at least one working port A can be optionally connected to a supply port P and a tank port T.
  • 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 embedded in the housing 4, for example by means of press fit. 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 with a paragraph on extended 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.
  • advantageously transmitted only axial forces through the pin 23 and the tolerance situation is also significantly improved.
  • the hydraulic piston 1 6 and the Antiklebeattach 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.
  • 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 injected into the bobbin 8 provided so that a secure attachment of the fork plug 35 and thus a secure contact can be guaranteed.
  • 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.
  • Such caulking provides additional protection of the attachment of the housing 4 and pole disc 28.
  • the Housing 4 is welded to the pole plate 28 is provided.
  • 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. A repeated description of the same components as in FIG. 1 is dispensed with and reference is made to their description in FIG. 1 in order to avoid unnecessary repetitions.
  • 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 partially longitudinally cut hydraulic valve 1 according to an embodiment of the invention.
  • the armature 10 has the central channel 12, which can direct the hydraulic fluid further into the front part of the armature space 56 and to the concealed in the illustration stroke volume of the pin.
  • the chip protection cover 27 forms a cover or a labyrinth for a suction point of the hydraulic reservoir 26, so that the suction is covered up and hydraulic fluid is sucked or filled over corner or over the labyrinth and so a dirt entry into the hydraulic reservoir 26 and thus is reduced in the associated with this armature space 56.
  • the hydraulic reservoir 26 is also arranged at the end of the solenoid part 3, which faces away from the hydraulic part 2, so that less dirt can be whirled up and introduced into the armature space 56 by the lower flow of hydraulic fluid prevailing there.
  • the hydraulic reservoir 26 is formed as a hollow body in the bobbin 8, for example, manufactured as an injection molded part, the hydraulic reservoir 26 can be made without additional tools and thus largely cost-neutral.
  • FIG. 3 of the injected into the bobbin 8 fork 35 can be seen.
  • the connector-side part of the bobbin 8 is protected by the chip protection cover 27 against the ingress of foreign bodies, such as metallic abrasion, from the hydraulic fluid and possible electrical short circuits in the contacting of the magnetic coil 7 and the fork plug 35.
  • the largest part of the housing 4 and the hydraulic part 2 of the hydraulic valve 1 are shown in plan view from the outside.
  • FIG. 4 shows a cross section through the hydraulic valve 1 from FIG. 3 along the line IV-IV in the region of the hydraulic fluid reservoir 26.
  • the U-shaped hydraulic fluid is a recess in the bobbin 8 arranged in the housing 4 -Reservoir 26 to recognize.
  • two holes 1 10 are arranged, which represent the fluid connection to the underlying armature space 56.
  • the hydraulic fluid from the reservoir 26 can enter into the armature chamber 56 and also flow back again.
  • the bottom of the hydraulic reservoir 26 in the intended installation position illustrated is arranged significantly lower than the lower walls of the connecting bores 110 into the armature space 56, as a result of which a dirt entry into the armature space 56 can be reduced, possibly Dirt in the hydraulic fluid drops and can settle at the bottom of the hydraulic reservoir 26.
  • the pins 36 of the fork plug 35 protrude from the bobbin 8, which serve to contact the coil wire of the magnetic coil 7 by means of welding sleeves 108.
  • the jaws 102 of the fork plug protrude from the bobbin 8. At the jaws 102, a suitable mating connector for driving the magnetic coil 7 can be connected.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • General Engineering & Computer Science (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). Un réservoir de fluide hydraulique (150) se trouve dans un corps de bobine (8) et est en communication fluidique avec la chambre d'induit (56).
PCT/EP2016/064521 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique WO2017005497A1 (fr)

Priority Applications (1)

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DE102015110725 2015-07-03
DE102015110725.2 2015-07-03
DE102015120984.5 2015-12-02
DE102015120984.5A DE102015120984A1 (de) 2015-07-03 2015-12-02 Hydraulikventil, insbesondere hydraulisches Getriebeventil

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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/EP2016/064507 WO2017005494A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique
PCT/EP2016/064521 WO2017005497A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape 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/EP2016/064494 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/EP2016/064507 WO2017005494A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10371278B2 (en) 2016-03-07 2019-08-06 Husco Automotive Holdings Llc Systems and methods for an electromagnetic actuator having a unitary pole piece

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10190698B2 (en) * 2017-02-07 2019-01-29 Marotta Controls, Inc. Solenoid valves for high vibration environments
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

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4206210A1 (de) * 1992-02-28 1993-09-02 Rexroth Mannesmann Gmbh Elektromagnetisch betaetigbares druckbegrenzungs- oder druckregelventil
DE4425843A1 (de) * 1994-07-06 1996-01-11 Rexroth Mannesmann Gmbh Druckbegrenzungs- oder Druckregelventil, das insbesondere elektromagnetisch betätigbar ist
DE19810330A1 (de) * 1998-03-11 1999-09-16 Mannesmann Rexroth Ag Magnetventil
EP1233220A2 (fr) * 2001-02-15 2002-08-21 Eto Magnetic Kg Soupape magnétique proportionnelle
DE102004024301A1 (de) * 2003-11-29 2005-07-07 Continental Teves Ag & Co. Ohg Druckregelventil
DE102004025969A1 (de) * 2004-05-18 2005-12-15 Hydraulik-Ring Gmbh Magnetventil
US20090121817A1 (en) * 2007-11-09 2009-05-14 Denso Corporation Linear solenoid
WO2011021730A1 (fr) * 2009-08-17 2011-02-24 Unick Corporation Electrovanne
US20110142690A1 (en) * 2009-12-15 2011-06-16 Aisin Aw Co., Ltd. Pump apparatus, power transmission apparatus, and vehicle
DE102011053023A1 (de) 2011-08-26 2013-02-28 Hilite Germany Gmbh Hydraulisches Getriebeventil
US20140065895A1 (en) * 2012-08-28 2014-03-06 Hamanakodenso Co., Ltd. Solenoid
US20140318649A1 (en) * 2013-04-25 2014-10-30 Kefico Corporation Solenoid valve with magnet filter
WO2016004920A2 (fr) * 2014-07-11 2016-01-14 Hilite Germany Gmbh Soupape, notamment soupape hydraulique

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4548047A (en) * 1981-11-11 1985-10-22 Hitachi, Ltd. Expansion valve
DE3506842A1 (de) * 1984-03-03 1985-09-12 Volkswagenwerk Ag, 3180 Wolfsburg Elektromagnetisches steuerventil
DE3814156A1 (de) * 1988-04-27 1989-11-09 Mesenich Gerhard Pulsmoduliertes hydraulikventil
DE4030963A1 (de) * 1990-10-01 1992-04-02 Bosch Gmbh Robert Elektromagnetbetaetigtes ventil
DE19703759A1 (de) * 1997-02-01 1998-08-06 Teves Gmbh Alfred Mehrwege-Regelventil
DE10227817A1 (de) * 2002-02-28 2003-09-11 Taiheiyo Kogyo Kk Regelventil für Kompressoren und dessen Herstellungsverfahren
EP1852603B1 (fr) * 2004-09-24 2009-04-29 Denso Corporation Vanne de contrôle de flux
US7581302B2 (en) * 2005-01-13 2009-09-01 G. W. Lisk Company, Inc. Solenoid valve combining a core and cartridge in a single piece
DE102005058846B4 (de) * 2005-12-09 2009-04-16 Thomas Magnete Gmbh Ventilbaukastensystem mit elektromagnetisch betätigtem Ventil
DE102006017451A1 (de) * 2006-04-13 2007-10-18 Robert Bosch Gmbh Magnetbaugruppe für ein Magnetventil
JP2008075763A (ja) * 2006-09-21 2008-04-03 Denso Corp アクチュエータ付バルブ装置
DE102009023592A1 (de) * 2008-06-26 2009-12-31 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulische Ventilvorrichtung zum Steuern zumindest eines Fluidstroms
US20130298848A1 (en) * 2012-05-14 2013-11-14 Girard Systems Gas flow modulator and method for regulating gas flow

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4206210A1 (de) * 1992-02-28 1993-09-02 Rexroth Mannesmann Gmbh Elektromagnetisch betaetigbares druckbegrenzungs- oder druckregelventil
DE4425843A1 (de) * 1994-07-06 1996-01-11 Rexroth Mannesmann Gmbh Druckbegrenzungs- oder Druckregelventil, das insbesondere elektromagnetisch betätigbar ist
DE19810330A1 (de) * 1998-03-11 1999-09-16 Mannesmann Rexroth Ag Magnetventil
EP1233220A2 (fr) * 2001-02-15 2002-08-21 Eto Magnetic Kg Soupape magnétique proportionnelle
DE102004024301A1 (de) * 2003-11-29 2005-07-07 Continental Teves Ag & Co. Ohg Druckregelventil
DE102004025969A1 (de) * 2004-05-18 2005-12-15 Hydraulik-Ring Gmbh Magnetventil
US20090121817A1 (en) * 2007-11-09 2009-05-14 Denso Corporation Linear solenoid
WO2011021730A1 (fr) * 2009-08-17 2011-02-24 Unick Corporation Electrovanne
US20110142690A1 (en) * 2009-12-15 2011-06-16 Aisin Aw Co., Ltd. Pump apparatus, power transmission apparatus, and vehicle
DE102011053023A1 (de) 2011-08-26 2013-02-28 Hilite Germany Gmbh Hydraulisches Getriebeventil
US20140065895A1 (en) * 2012-08-28 2014-03-06 Hamanakodenso Co., Ltd. Solenoid
US20140318649A1 (en) * 2013-04-25 2014-10-30 Kefico Corporation Solenoid valve with magnet filter
WO2016004920A2 (fr) * 2014-07-11 2016-01-14 Hilite Germany Gmbh Soupape, notamment soupape hydraulique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10371278B2 (en) 2016-03-07 2019-08-06 Husco Automotive Holdings Llc Systems and methods for an electromagnetic actuator having a unitary pole piece

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DE102015120982A1 (de) 2017-01-05
WO2017005493A1 (fr) 2017-01-12
WO2017005496A1 (fr) 2017-01-12
DE102015120984A1 (de) 2017-01-05
CN208169647U (zh) 2018-11-30
DE102015120983A1 (de) 2017-01-05
CN208574226U (zh) 2019-03-05
WO2017005494A1 (fr) 2017-01-12
CN208169648U (zh) 2018-11-30
CN208574225U (zh) 2019-03-05
DE102015120992A1 (de) 2017-01-05
DE102015120981A1 (de) 2017-01-05
WO2017005498A1 (fr) 2017-01-12
CN208169646U (zh) 2018-11-30

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