WO2017005498A1 - Coupelle de ressort et vanne hydraulique, notamment vanne de transmission hydraulique - Google Patents

Coupelle de ressort et vanne hydraulique, notamment vanne de transmission hydraulique Download PDF

Info

Publication number
WO2017005498A1
WO2017005498A1 PCT/EP2016/064529 EP2016064529W WO2017005498A1 WO 2017005498 A1 WO2017005498 A1 WO 2017005498A1 EP 2016064529 W EP2016064529 W EP 2016064529W WO 2017005498 A1 WO2017005498 A1 WO 2017005498A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
armature
spring plate
valve
hydraulic valve
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/EP2016/064529
Other languages
German (de)
English (en)
Inventor
Michael BIERKOCH
Thomas Jacob
Jürgen PEILER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilite Germany GmbH
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 CN201690000944.1U priority Critical patent/CN208574226U/zh
Publication of WO2017005498A1 publication Critical patent/WO2017005498A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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

  • the invention relates to a spring plate and a hydraulic valve with a spring plate, 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, instead of, for example, 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 spring plate for guiding a spring for biasing an armature of a hydraulic valve, in particular a hydraulic transmission valve, which is as simple and inexpensive to manufacture
  • Another object of the invention is to provide a hydraulic valve with such a spring plate, in particular as a hydraulic transmission valve that combines the highest possible robustness with cost-effective design.
  • a spring plate in particular for a hydraulic valve, in particular a hydraulic transmission valve, wherein the spring plate is provided by deep drawing formed from sheet metal.
  • the spring plate is provided for guiding a spring, by means of which spring a longitudinally movable armature of the hydraulic valve is biased to assume a basic position of the hydraulic valve.
  • the spring plate may be expediently pressed into a recess of the armature.
  • the spring plate made of sheet metal according to the invention can be made thin-walled by forming by deep drawing and still stiff.
  • 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 effective damping for the flowing inside the spring plate hydraulic fluid.
  • the spring plate can be made as a prestressed component.
  • the spring plate is formed of non-magnetic material, such as non-magnetic stainless steel with a wall thickness in the range 0.15 mm to 0.2 mm, but other materials and wall thicknesses are low.
  • a circumferential radial projection may be provided as a stop and Antiklebesay.
  • a bent or flanged edge in the axial direction on the outer circumference of the projection of the spring plate of this can be pressed when pressed into the recess of the anchor only to this edge and then rests with this edge as a stop on an end face of the anchor.
  • this edge can protrude for example by additional bending, for example in a thickness of the sheet, so far beyond the end face of the anchor, that the radial projection can serve as an anti-adhesive disc of the anchor.
  • the spring plate may be formed as turned inside tube piece.
  • the spring plate can be made inexpensively by at least partially flanging a sheet metal part.
  • a wall thickness of the sheet metal part is advantageously maintained, which further simplifies the manufacturing process of the spring plate.
  • the spring plate may be useful in a manufacturing process by forming a brim on the sheet metal part, deepening the brim, turning over a part of the sheet metal part, pulling the folded part, and upsetting the solid part to enlarge a diameter of the tubular spring plate as a receptacle for the spring , getting produced.
  • the spring plate on one side of the circumferential radial projection double-walled and on the opposite Side be formed single-walled.
  • the radial projection can be made for example by deep drawing from a sheet metal blank.
  • the piece of sheet metal can be shaped by means of a punch to a pot with brim, which pot is then pressed from below through the piece of sheet metal.
  • the spring plate can be formed by crimping to a defined length in the form of a double-walled tube piece, which opens into the radial projection radially outward.
  • the double-walled part of the spring plate can be pressed so advantageous in the recess of the anchor.
  • the other non-flared part of the original sheet metal part on the opposite side of the spring plate may be continued single-walled to receive the spring.
  • the spring plate may be open on both sides.
  • the spring plate can thus form a channel for hydraulic fluid flowing through it, which can thus flow from an armature space to a hydraulic fluid reservoir and back through a channel formed in the interior of the armature and through the spring plate.
  • the damping diaphragm formed by the inner diameter of the spring plate may be selected as open as possible in order to achieve the most effective possible hydraulic damping of the spring plate.
  • 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 periphery 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 sleeve 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.
  • 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 pole tube comprises a pole and / or a pole core of the solenoid part.
  • the spring plate made of sheet metal according to the invention can be carried out in this way thin-walled and yet stiff.
  • 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 effective damping for the flowing inside the spring plate hydraulic fluid.
  • the spring plate can be made as a prestressed component.
  • the spring plate is formed of non-magnetic material, such as non-magnetic stainless steel with a wall thickness in the range 0.15 mm to 0.2 mm, but other materials and wall thicknesses are low.
  • a circumferential radial projection may be provided as a stop and Antiklebeface. Due to the radial projection on the outer circumference of the spring plate of this can be pressed when pressed into the recess of the armature only up to this stop and then lies flat with this projection as a stop on a front side of the armature. Also, this radial projection, for example, by additional Bending, for example, in a thickness of the sheet, as far protrude beyond the end face of the anchor, that the radial projection can serve as an anti-adhesive disc of the anchor. Thereby, a possible hydraulic or magnetic bonding of the armature is reduced at a stop of a pole tube, in which the armature is moved.
  • the spring plate may be formed as turned inside tube piece.
  • the spring plate can be manufactured inexpensively by at least partially flanging a sheet metal part.
  • a wall thickness of the sheet metal part is advantageously maintained, which further simplifies the manufacturing process of the spring plate.
  • the spring plate may be useful in a manufacturing process by forming a brim on the sheet metal part, deep drawing the brim, turning over a part of the sheet metal part, pulling the folded part, and upsetting the solid part to a diameter of the tubular spring plate as a receptacle for the spring enlarge, be produced.
  • the spring plate can be double-walled on one side of the circumferential radial projection and formed on the opposite side single-walled.
  • the radial projection can be made for example by deep drawing from a sheet metal blank.
  • the piece of sheet metal can be shaped by means of a punch to a pot with brim, which pot is then pressed from below through the piece of sheet metal. So can be formed over a beading on a defined length as a double-walled pipe section, which opens into the radial projection radially outward.
  • the double-walled part of the spring plate can be pressed so low in the recess of the anchor.
  • the spring plate may be open on both sides.
  • the spring plate can thus form a channel for hydraulic fluid flowing through it, which can thus flow from an armature space to a hydraulic fluid reservoir and back through a channel formed in the interior of the armature and through the spring plate.
  • the damping diaphragm formed by the inner diameter of the spring plate may be selected as open as possible in order to achieve the most effective possible hydraulic damping of the spring plate.
  • 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.
  • 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.
  • the 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.
  • 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.
  • a ring structure or nub structure or the like is conceivable.
  • both ends of the pin have a rounded end face, a mounting of the pin is independent of its orientation possible.
  • 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 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.
  • a fork plug as an electrical connection of the magnetic coil may conveniently also be integrated into the bobbin by encapsulation.
  • a stable mechanical connection of the fork plug is ensured with the solenoid part.
  • 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 pole disk can be encapsulated with a material of the bobbin at least in regions. In this way, the fixation of the pole disk is much easier in their relative orientation to the bobbin, since the two components, once they are encapsulated, can not move against each other. Also, the sealing of the bobbin against the hydraulic fluid and / or moisture is easier to maintain.
  • 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 also be effected via caulking segments, which are sheared off from the housing by means of a suitable tool and / or bent over and pressed onto the pole disk.
  • caulking segments which are sheared off from the housing by means of a suitable tool and / or bent over and pressed onto the pole disk.
  • 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 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.
  • 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. 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 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 anticaking effect can be achieved so that the anchor at Stop on the bobbin does not stick to it, but can easily be solved again.
  • 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 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 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 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 formed 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 thereby caused a magnet / 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, 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. In this way, the armature can be favorably aligned and guided in the axis of the solenoid, which is an advantage for an efficient drive of the hydraulic valve.
  • 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
  • Fig. 3 is a longitudinal section through a hydraulic valve after another
  • Embodiment of the invention in a basic position.
  • Figure 1 shows a longitudinal section through a spring plate 43 according to an embodiment of the invention.
  • the spring plate which is provided in particular for a hydraulic valve 1, in particular a hydraulic transmission valve 1, as shown in Figure 2, can be made by deep drawing formed from sheet metal.
  • FIG. 2 shows in a longitudinal section the hydraulic valve 1 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 spring plate 43 is provided for guiding the spring 40, by means of which spring 40 of the movable armature 10 in a longitudinal direction of the hydraulic valve 1 is biased to assume a basic position of the hydraulic valve 1.
  • the spring plate 43 is expediently pressed into a recess 32 of the armature 10.
  • the damping diaphragm 120 is designed by the inner diameter, wherein the damping diaphragm 120 is as open as possible in order to achieve an effective damping for the flowing inside the spring plate 43 hydraulic fluid.
  • the spring plate 43 may be made as a prestressed component. By this elastic design a secure pressing into the armature 10 on the closed contour of the spring plate 43 is possible. By providing the radius 122 as a lead-in chamfer-free press-fitting into the recess 32 of the armature 10 can be ensured.
  • the spring plate 43 is formed of non-magnetic material, such as non-magnetic stainless steel with a wall thickness in the range of 0.15 mm to 0.2 mm, but other materials and wall thicknesses are low.
  • the circumferential radial projection 44 is provided as a stop and Antiklebesay.
  • This can be pressed when pressed into the recess 32 of the armature 10 only to this edge 45 and then lies with the edge 45 as a stop on the front side of the armature 10th at.
  • this edge 45 protrude, for example, by additional bending, for example in the thickness of the sheet, as far as the end face of the armature 10, that the radial projection 44 serves as an anti-stick disc of the armature 10.
  • a possible hydraulic or magnetic bonding of the armature 10 is reduced at a stop of the pole tube 6, in which the armature 10 is moved.
  • the spring plate 43 is double-walled on the side of the circumferential radial projection 44 and formed on the opposite side single-walled.
  • the double-walled part of the spring plate can be pressed so low in the recess 32 of the armature 10.
  • the other non-crimped, single-wall part of the original tube piece receives the spring 40.
  • the spring plate 43 is open on both sides. Expediently, the spring plate 43 can thus form a channel for hydraulic fluid flowing through it, which can thus flow from the armature space 56 to the hydraulic fluid reservoir 26 and back through the channel 12 formed in the interior of the armature 10 and through the spring plate 43. In this way, a hydraulic balance between the armature chamber 56 and the hydraulic fluid reservoir 26 is ensured.
  • the damping diaphragm 120 formed by the inner diameter of the spring plate 43 may be selected as open as possible in order to achieve the most effective possible hydraulic damping of the spring plate 43.
  • the hydraulic valve 1 shown in Figure 2 comprises the solenoid part 3 with the magnetizable housing 4, which encloses a magnetic coil 7 on an outer periphery 50 and at least a first end face 52, as well as with a pole tube 6 arranged in the interior of the magnet coil 7, in which an armature 10 in an armature space 56 is provided so as to be axially displaceable.
  • 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 embedded in the housing 4, for example by means of press fit.
  • 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 working port A is connected to the supply port P in the basic position shown.
  • the spring 40 accommodated in the recess 41 of the pole tube 6 biases the armature 10 in the direction of the hydraulic part 2.
  • the spring plate 43 is pressed, which guides the spring 40 and serves at the same time by the circumferential radial projection 44 as a stop and Antiklebecons.
  • the axial force transmission between the armature 10 and the hydraulic piston 16 by means of a pin 23 which is guided in the valve sleeve 5 is arranged.
  • the pin 23 allows a decoupling between anchor and piston bearing.
  • a circumferential recess 24 on its circumference which is formed as a peripheral annular groove 68, thereby allowing a reduction of the support surface, whereby the friction can be reduced.
  • 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 by being at least partially encapsulated by the plastic material of the bobbin 8, for example, 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.
  • a provided in the bobbin 8 hydraulic fluid reservoir 26, which is preferably initially filled once, is in communication with the armature space 56 and prevents air from entering the hydraulic valve. 1 Furthermore, the possibility of displacement of the hydraulic fluid into the reservoir 26 prevents additional undesirable damping.
  • the reservoir 26 is dimensioned such that the volume shift caused by the pin stroke is reduced.
  • the hydraulic valve 1 In order to prevent a short circuit caused by foreign bodies between a forked plug, not shown, and the pole disk 28, the hydraulic valve 1 also has a chip protection cover 27, which covers the pole disk 28 with ribs.
  • the fork plug is also partially injected in the bobbin 8 provided so that a secure attachment of the fork plug and thus a secure contact can be guaranteed.
  • the coil wire is wound around the pin of the fork plug. Subsequently, a welding sleeve is inserted over the wound pin and pin and coil wire are connected by pressing and resistance welding appropriate.
  • 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 sheared off by means of a suitable tool of the housing 4 and / or bent and pressed onto the pole plate 28.
  • Verstemmungssegmente which sheared off by means of a suitable tool of the housing 4 and / or bent and pressed onto the pole plate 28.
  • a 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. 3 shows 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. 2 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 made in one piece.
  • the working connection A is connected to the supply connection P in the basic position shown.
  • a spring 40 accommodated in a recess of a pole tube insert 41 biases the armature 10 in the direction of the hydraulic part 2.
  • a spring plate 43 is pressed, which guides the spring 40 and at the same time by a circumferential radial projection 44 with a direction in the direction of the intended insertion chamfer bent or beaded rim 45 serves as a stop and Antiklebescene.
  • the spring plate 43 is advantageously formed by deep drawing from sheet metal.
  • the valve sleeve 5 of the second embodiment has a shorter end portion 46 of the hydraulic sleeve 5, which merges into the pole tube 6.

Landscapes

  • 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

L'invention concerne une coupelle de ressort (143), destinée notamment à une vanne hydraulique (1), notamment une vanne de transmission hydraulique, la coupelle de ressort (143) étant formée par emboutissage profond d'une tôle. En outre, l'invention concerne une vanne hydraulique (1), notamment une vanne de transmission hydraulique, qui comprend un élément électromagnétique (3), pourvu d'un boîtier magnétisable (4) qui entoure une bobine magnétique (7) sur une périphérie extérieure (50) et sur au moins une première face d'extrémité (52) et d'un tube polaire (6) qui est disposé à l'intérieur de la bobine magnétique (7) et dans lequel un induit (10) est destiné à coulisser axialement dans une chambre d'induit (56), et comprend également un élément hydraulique (2) pourvu d'un piston hydraulique (16) qui est guidé de façon à coulisser axialement dans une douille de vanne (5) et au moyen duquel au moins un raccord de travail (A) peut être relié sélectivement à au moins un raccord d'alimentation (P) et à au moins un raccord de réservoir (T). L'induit (10) est destiné à entraîner le piston hydraulique (16). La douille de vanne (5) est disposé le long d'un axe longitudinal (L) dans le prolongement du tube polaire (6). L'induit (10) est conçu précontraint au moyen d'un ressort (40) en direction de l'élément hydraulique (2). Une coupelle de ressort (43) est enfoncée dans une cavité (32) de l'induit (10) pour le guidage du ressort (40). La coupelle de ressort (43) est façonnée en tôle par emboutissage profond et possède une partie saillante (44) radiale périphérique faisant office de butée et de rondelle anti-adhérence.
PCT/EP2016/064529 2015-07-03 2016-06-23 Coupelle de ressort et vanne hydraulique, notamment vanne de transmission hydraulique Ceased WO2017005498A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201690000944.1U CN208574226U (zh) 2015-07-03 2016-06-23 弹簧座和液压阀

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102015110725.2 2015-07-03
DE102015110725 2015-07-03
DE102015120992.6 2015-12-02
DE102015120992.6A DE102015120992A1 (de) 2015-07-03 2015-12-02 Federteller und Hydraulikventil, insbesondere hydraulisches Getriebeventil

Publications (1)

Publication Number Publication Date
WO2017005498A1 true WO2017005498A1 (fr) 2017-01-12

Family

ID=57582399

Family Applications (5)

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

Family Applications Before (2)

Application Number Title Priority Date Filing Date
PCT/EP2016/064512 Ceased WO2017005496A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique
PCT/EP2016/064494 Ceased WO2017005493A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique

Family Applications After (2)

Application Number Title Priority Date Filing Date
PCT/EP2016/064521 Ceased WO2017005497A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique
PCT/EP2016/064507 Ceased WO2017005494A1 (fr) 2015-07-03 2016-06-23 Soupape hydraulique, notamment soupape de transmission hydraulique

Country Status (3)

Country Link
CN (5) CN208169648U (fr)
DE (5) DE102015120983A1 (fr)
WO (5) WO2017005496A1 (fr)

Cited By (2)

* 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
DE102020204092A1 (de) 2020-03-30 2021-09-30 Continental Teves Ag & Co. Ohg Elektromagnetventil

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
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
DE102022205118A1 (de) 2022-05-23 2023-11-23 Zf Friedrichshafen Ag Verfahren zum Betreiben eines Stellmagneten

Citations (12)

* 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
DE19703759A1 (de) * 1997-02-01 1998-08-06 Teves Gmbh Alfred Mehrwege-Regelventil
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
US20080072975A1 (en) * 2006-09-21 2008-03-27 Denso Corporation Oil pressure control valve having actuator
US20090121817A1 (en) * 2007-11-09 2009-05-14 Denso Corporation Linear solenoid
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 (14)

* 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
DE19810330A1 (de) * 1998-03-11 1999-09-16 Mannesmann Rexroth Ag Magnetventil
DE10107164C1 (de) * 2001-02-15 2002-11-21 Eto Magnetic Kg Proportional-Wegemagnetventil
DE10227817A1 (de) * 2002-02-28 2003-09-11 Taiheiyo Kogyo Kk Regelventil für Kompressoren und dessen Herstellungsverfahren
DE602005014283D1 (de) * 2004-09-24 2009-06-10 Denso Corp Ventil zur Flusssteuerung
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
DE102009023592A1 (de) * 2008-06-26 2009-12-31 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulische Ventilvorrichtung zum Steuern zumindest eines Fluidstroms
WO2011021730A1 (fr) * 2009-08-17 2011-02-24 Unick Corporation Electrovanne
US20130298848A1 (en) * 2012-05-14 2013-11-14 Girard Systems Gas flow modulator and method for regulating gas flow

Patent Citations (12)

* 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
DE19703759A1 (de) * 1997-02-01 1998-08-06 Teves Gmbh Alfred Mehrwege-Regelventil
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
US20080072975A1 (en) * 2006-09-21 2008-03-27 Denso Corporation Oil pressure control valve having actuator
US20090121817A1 (en) * 2007-11-09 2009-05-14 Denso Corporation Linear solenoid
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 (2)

* 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
DE102020204092A1 (de) 2020-03-30 2021-09-30 Continental Teves Ag & Co. Ohg Elektromagnetventil

Also Published As

Publication number Publication date
CN208169648U (zh) 2018-11-30
DE102015120984A1 (de) 2017-01-05
DE102015120982A1 (de) 2017-01-05
CN208574225U (zh) 2019-03-05
DE102015120992A1 (de) 2017-01-05
WO2017005496A1 (fr) 2017-01-12
DE102015120981A1 (de) 2017-01-05
CN208169646U (zh) 2018-11-30
WO2017005493A1 (fr) 2017-01-12
DE102015120983A1 (de) 2017-01-05
CN208574226U (zh) 2019-03-05
CN208169647U (zh) 2018-11-30
WO2017005494A1 (fr) 2017-01-12
WO2017005497A1 (fr) 2017-01-12

Similar Documents

Publication Publication Date Title
EP2370675B1 (fr) Unité de commande électromagnétique pour un distributeur hydraulique et procédé de montage de ladite unité
DE102009006355A1 (de) Proportionalmagnet für ein hydraulisches Wegeventil und Verfahren zu dessen Herstellung
EP1073070A2 (fr) Electro-aimant et soupape hydraulique comprenant un électro-aimant
WO2017005498A1 (fr) Coupelle de ressort et vanne hydraulique, notamment vanne de transmission hydraulique
DE102013220593A1 (de) Elektromagnetisch ansteuerbares Saugventil
WO2007101550A2 (fr) Électro-aimant de levage ainsi que procédé de fabrication dudit électro-aimant
EP3529814B1 (fr) Actionneur électromagnétique
WO2014086345A1 (fr) Système de came coulissante et actionneur de came coulissante avec une broche d'entraînement reliée à une unité à magnétisme permanent
DE102018222614A1 (de) Elektromagnetische Betätigungseinrichtung
EP0722398B1 (fr) Groupe hydraulique pour systemes de freinage antipatinage d'automobiles
WO2010000527A1 (fr) Vanne magnétique pour un injecteur de carburant et injecteur de carburant
DE102022207702A1 (de) Dämpfungsventileinrichtung für einen Schwingungsdämpfer
EP2599095A1 (fr) Actionneur magnétique
DE19932747B4 (de) Verfahren zur Herstellung eines Druckregelventils für ein Automatikgetriebe eines Kraftfahrzeuges und nach dem Verfahren hergestelltes Druckregelventil
DE102008061949A1 (de) Betätigungselement einer elektromagnetischen Stelleinheit eines Hydraulikventils
DE102012209729A1 (de) Magnetventil
WO2021099007A1 (fr) Dispositif d'actionnement électromagnétique
DE102007004254A1 (de) Elektromagnetische Stellvorrichtung
WO2016173778A1 (fr) Unité de réglage électromagnétique pour un injecteur et injecteur pour une telle unité de réglage électromagnétique
DE102010000797A1 (de) Massivumformen einer magnetischen Trennung
DE102006009362A1 (de) Elektromagnetventil
DE102024105189A1 (de) Kolbenschieberventil mit zweiteiligem stellglied
DE202007002100U1 (de) Elektromagnetische Stellvorrichtung
DE102009053216A1 (de) Druckentlastetes 2/2-Wege-Schnellschaltmagnetventil
DE102012222989A1 (de) Linearaktuator

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16731884

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 16731884

Country of ref document: EP

Kind code of ref document: A1