EP1573212B1 - Electromagnet - Google Patents

Electromagnet Download PDF

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Publication number
EP1573212B1
EP1573212B1 EP03789234A EP03789234A EP1573212B1 EP 1573212 B1 EP1573212 B1 EP 1573212B1 EP 03789234 A EP03789234 A EP 03789234A EP 03789234 A EP03789234 A EP 03789234A EP 1573212 B1 EP1573212 B1 EP 1573212B1
Authority
EP
European Patent Office
Prior art keywords
armature
armature space
channel
electromagnet
pressure
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.)
Expired - Fee Related
Application number
EP03789234A
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German (de)
French (fr)
Other versions
EP1573212A1 (en
Inventor
Bernhard Adler
Horst Stegmaier
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
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Filing date
Publication date
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Publication of EP1573212A1 publication Critical patent/EP1573212A1/en
Application granted granted Critical
Publication of EP1573212B1 publication Critical patent/EP1573212B1/en
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B13/0442—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with proportional solenoid allowing stable intermediate positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/044—Removal or measurement of undissolved gas, e.g. de-aeration, venting or bleeding

Definitions

  • the invention relates to an electromagnet for actuating a valve.
  • Electromagnets are often used to operate valves in hydraulic systems. Such an electromagnet for actuating a valve is z. B. from DE 37 09 474 C1.
  • the solenoid actuates a valve closing body which cooperates with a sealing seat in response to the stroke of the valve closing body to a variable throttle.
  • the stroke of the valve closing body is generated by an armature moved in the axial direction by a magnetic field.
  • the armature can be moved in an axial direction in an armature space and is held by a spring acting axially on the armature in a defined starting position.
  • the cavities formed in the interior of the electromagnet are filled with the pressure medium during the operation of the electromagnet, so that the movement of the armature is damped.
  • the armature space or the armature space bounding in the axial direction of the pole tube is surrounded in the radial direction on the outside by a coil which generates a magnetic field during energization, which acts on the armature in the direction of the pole tube against the force of the spring with a magnetic force.
  • the rear armature space is thereby reduced in volume and the pressure medium therein is displaced.
  • a volume in which flows in the displaced pressure medium is connected via a vent valve device with the environment.
  • a vent valve device is provided in the electromagnet described in DE 37 09 474 C1, which connects via a transverse bore located around the armature ring gap with the environment of the electromagnet.
  • the vent valve device is constructed similar to a shuttle valve.
  • the arranged in the vent valve closing body has a lower specific gravity than the pressure medium used. Due to gravity, the closing body therefore releases as long as a flow-through cross section until the level of the pressure medium flowing along the valve closing body, which is pressed by the delivery pressure in the armature space during operation of the valve, has reached the closing body of the vent valve. The closing body then floats on the pressure medium and is pressed against the outwardly directed sealing seat, whereby the vent valve is closed.
  • the vent described has the disadvantage that when filling the valve is closed by the pressure medium.
  • the pressure medium when refilling the emptied armature space with the pressure medium, it is unavoidable that residues of trapped air in the relatively viscous pressure medium remain in the rear armature space. This air entrapment degrades the damping behavior and makes it difficult to tune the damping, since the movement of the armature different distributions of the air can occur.
  • the trapped air is only pushed back and forth during the movement of the armature, but can no longer escape from the armature space, since the vent valve remains closed.
  • a equipped with the described vent valve hydraulic valve therefore has a predetermined mounting position.
  • Another disadvantage is that the closing of the vent hole via the pressure medium, which is usually an oil. In a partial escape of the pressure medium from the armature space, for example, during a subsequent longer service life, it may therefore come to sticking of the closing body, whereby the function is no longer guaranteed at a restart.
  • DE 44 17 587 A1 discloses an electromagnet according to the preamble of claim 1.
  • the subject matter of claim 1 therefore differs from the known electromagnet in that at least a first channel portion of the return flow channel is arranged in a pole tube, and that in a housing cover a second Channel section of the return flow channel is provided, which opens out of the housing cover at a provided for engagement with a valve housing surface.
  • the object to be achieved by the present invention can thus be seen to provide an electromagnet for actuating a valve with a return channel for a pressure medium leakage current, which can be easily adapted to different valves and can be manufactured inexpensively.
  • the electromagnet according to the invention has the advantage that with the armature space, a return flow channel is connected, via which the leakage fluid entering the armature space flows into a tank volume. This achieves a lower but continuously occurring leakage current during operation of the electromagnet. On the one hand, this leakage current generates a slight negative pressure in the armature space, and on the other hand, air bubbles which have been transported into the region of the flow due to the movement of the armature can be removed together with the leakage flow via the return flow channel.
  • the return flow channel is open at any time during operation of the electromagnet, so that the pressure medium leakage current is maintained even when the electromagnet is approximately completely filled with the pressure medium remains. In this way, it is possible that air inclusions, which may still be present in the rear armature space even with an almost complete filling with pressure medium, are still removed from the interior of the electromagnet.
  • the air pockets are then conveyed by the movement of the armature into the area in which the flow occurs due to the pressure medium leakage. The movement of the trapped air is promoted on the one hand by the negative pressure generated by the flow and on the other hand by the turbulence which arises due to the flow.
  • the return flow channel opens directly into the armature space, since this results in a particularly effective venting.
  • the displaced from the rear armature space by the movement of the armature pressure medium thus transported the air bubbles contained in the rear armature space in the immediate vicinity of the leakage flow.
  • the entrainment of the air bubbles by the leakage flow is particularly simple and it results in a fast venting.
  • a further advantageous embodiment results in that the return flow channel is arranged in an extended region of the pole tube.
  • the leakage flow is not guided through the armature space, whereby the risk is reduced that dirt particles that may be contained in the leakage flow are transported to the anchor.
  • Such contaminants which are located in the region of the armature, have an adverse effect on the life of the electromagnet.
  • a higher flow velocity of the leakage flow is formed at the outlet in the pole tube due to the smaller flow cross-sections. which in turn improves the escape of trapped air bubbles.
  • the return flow channel in the electromagnet so that there is a direct connection possibility to the tank volume located in the actuated valve unit.
  • this is the return flow channel in a pole tube, which also takes over the leadership of the acting on the valve to be actuated plunger.
  • a first example of an adjusting device 1 is shown with an actuated by the solenoid according to the invention valve.
  • a control piston 2 is acted upon in a control pressure chamber 3 and a second control pressure chamber 4 with a control pressure.
  • the actuating pressures acting in the first and second actuating pressure chambers 3 and 4 act on the oppositely oriented piston surfaces of the actuating piston 2, at which a resultant force acts on a pressure difference.
  • a control pressure control valve 5 is provided to set the pressure difference in the two control pressure chambers 3 and 4.
  • the control pressure control valve 5 has a control piston 6 which is arranged axially displaceably in a bore of a housing 7. Furthermore, a first feed pressure bore 8 and a second feed pressure bore 9 are introduced into the housing 7. The first feed pressure bore 8 and second feed pressure bore 9 are connected to a feed pressure line 14, which may be connected, for example, to an auxiliary pressure source.
  • the feed pressure line 14 and the first feed pressure bore 8 or the second feed pressure bore 9 with a first actuating pressure line 12 or a second actuating pressure line 13 connectable.
  • the first actuating pressure line 12 is connected to a first actuating pressure channel 10 connected, which opens on the part of the control piston 6 in a first groove 15.
  • the second actuating pressure line 13 is connected via a second actuating pressure channel 11 with a second groove 16.
  • the control piston 6 has a first control piston section 17 and a second control piston section 18, respectively.
  • the two control piston sections 17 and 18 respectively have a first control pressure control edge 19 and a second control pressure control edge 20, which are arranged at the oppositely oriented ends of the respective control piston section 17 or 18.
  • the first control pressure control edge 19 and the second control pressure control edge 20 form with the respective first groove 15 and second groove 16 a variable depending on the axial position of the control piston 6 throttle point.
  • the first actuating pressure channel 10 is connected via the first groove 15 with a first feed pressure 21 and thus the first actuating pressure chamber 3 is depressed with the pressure from the feed pressure line 14.
  • the second actuating pressure channel 11 is connected via the second groove 16 with a second feed pressure groove 22 when the control piston 6 is deflected in the opposite direction.
  • a first expansion control edge 23 is arranged on the side remote from the first control pressure control edge 19 side of the first control piston portion 17.
  • a second expansion control edge 24 is arranged on the second control piston section 18.
  • the respective control pressure chamber 3 or 4 is expanded via the two expansion control edges 23 and 24 via the first groove 15 and the second groove 16 into a tank volume 25.
  • a volume equalization channel 26 of the rear control piston chamber 27 Also connected to the tank volume 25 is via a volume equalization channel 26 of the rear control piston chamber 27.
  • the slight volume fluctuations that arise in the rear control piston chamber 27 by an axial movement of the control piston 6 are thus compensated.
  • part of the control piston leakage is discharged via the volume equalization channel 26 into the tank volume 25.
  • a proportional solenoid 28 is provided, which is arranged on the housing 7 of the control valve 5.
  • the proportional magnet 28 has a plunger 29, wherein the plunger 29 acts on an end face 30 of the control piston 6.
  • a control force can be transmitted to the control piston 6 in the axial direction, which is generated by the proportional magnet 28 in response to a control signal which is supplied to the proportional solenoid 28 via an electrical connection, not shown. If the proportional magnet 28 is supplied with such a control signal via the electrical connection, it generates a force which displaces the control piston 6. In this case, a flow-through gap is generated by the axial movement of the control piston 6 at the first control pressure control edge 19.
  • the pressure medium supplied via the feed pressure line 14 and the first feed pressure bore 8 can reach the first setting pressure chamber 3 via the first setting pressure passage 10.
  • the thus increased pressure in the first actuating pressure chamber 3 causes an adjustment of the actuating piston 2 against the force of a return spring 40 in the direction of its second end position.
  • the throttle point of the second discharge control edge 24 is opened in the second control piston section 18.
  • the second control pressure chamber 4 is expanded via the second control pressure line 13 and the second control pressure channel 11 in the tank volume 25.
  • a Mit supportiveausnaturalung 33 is provided in the adjusting piston 2, in which a driving head 32 is arranged, which is connected to the adjusting lever 31.
  • the adjusting lever 31 is rotatably mounted on a bearing pin 34, so that the adjusting movement of the actuating piston 2 leads to a rotation of the actuating lever 31.
  • Also rotatably mounted on the bearing pin 34 are a first leg 35 and a second leg 36.
  • the first leg 35 and the second leg 36 are connected via a tension spring 37 with each other, so that a deflection of one of the two legs relative to the other to a voltage the tension spring 37 leads.
  • a driving pin 38 is arranged at the opposite end to the driving head 32 of the actuating lever 31 end of the actuating lever 31.
  • the driving pin 38 moves in opposite directions to the actuating piston movement.
  • the driving pin 38 abuts against the second leg 36, so that the second leg 36 is deflected relative to the first leg 35 by the rotational movement of the actuating lever 31 and the spring 37 is tensioned.
  • the adjusting device 1 shown in FIG. 1a is actuated by exerting a force on the control piston 6 via the proportional magnet 28.
  • the proportional magnet 28 has a pole tube 50 surrounded by a coil, not shown, which is penetrated along its longitudinal axis by a through-hole 51.
  • the diameter of the through hole 51 is dimensioned so that the through hole 51 forms a leakage gap with the plunger 29.
  • the pole tube 50 is fastened by means of a screw connection 52 in a housing cover 53 of the proportional magnet 28.
  • a Sealing element 54 disposed in a groove provided for this purpose of the pole tube 50.
  • the plunger 29 projects slightly beyond the end face 55 of the pole tube 50 and rests there against the end face 30 of the control piston 6.
  • the through-bore 51 has a radially widened section 56, to which an armature space 57 formed as a recess of the pole tube 50 in the illustrated exemplary embodiment adjoins.
  • an armature space 57 formed as a recess of the pole tube 50 in the illustrated exemplary embodiment adjoins.
  • an armature 58 is arranged, which is in operative connection with the plunger 29.
  • anchor channels 59 are formed parallel to its longitudinal axis, which connect the two opposite end faces of the armature 58 with each other.
  • the armature 58 By energizing the coil elements of the electromagnet, not shown, the armature 58 is acted upon by the resulting magnetic field with a force in the axial direction, which shifts him so that the volume of the armature space 57 is reduced. Since the armature 58 is in operative connection with the plunger 29, this axial movement is transmitted to the plunger 29, which in turn transmits the axial movement to the end face 30 of the control piston 6. If the current for the coil elements is turned off, no force acts on the armature 58 and it is displaced to the right via the counter-force transmitted by the control piston 6 to the tappet 29 in the illustrated arrangement of FIG. There is a connection between the armature space 57 and the rear armature space, not shown in FIG. 1b, via the armature channels 59, so that a volume compensation takes place between the armature space 57 and the rear armature space.
  • the end face 30 of the control piston 6 is formed on an extension 60.
  • the extension 60 penetrates an opening 61 of a spring washer 62, which in a Receiving opening 63 of the housing 7 is arranged.
  • the spring washer 62 is arranged in the receiving opening 63 that the driven back by the opposing force control piston 6 abuts with a stop surface 64 there and undergoes a defined braking force there.
  • the stop surface 64 is formed on a guide portion 65.
  • the housing cover 53 has a cylindrical extension 66, which projects into the receiving opening 63 of the housing 7.
  • the spring washer 62 can be fixed in the receiving opening 63, for example via the cylindrical extension 66.
  • a further sealing element 67 is arranged in a groove of the housing cover 53, which seals the proportional magnet 28 relative to the housing 7.
  • a pressure medium leakage forms, through which it comes to a pressure medium flow from the feed pressure bore 8 on the guide portion 65 in the direction of the proportional magnet 28.
  • the pressure medium first fills the receiving opening 63 and then also flows through a gap 68, which is formed in the through hole 51 between the inner wall of the pole tube 50 and the plunger 29 arranged therein.
  • the armature space 57 forms a closed volume.
  • a first channel section 69 of a return flow channel is provided in the pole tube 50, which connects the widened region 56 of the through-hole 51 with a circumferential channel 70.
  • the encircling channel can be embodied, for example, as an undercut in the outlet region of the screw connection 52.
  • the flowing back pressure medium flows through a second channel section 71 of the return flow channel and a third channel section 73 back into the tank volume 25.
  • the second channel section 71 of the return flow channel opens at an end face 74 directed in the direction of the cylindrical extension 66.
  • a recess 75 is disposed in the end face 74 of the housing cover 53.
  • the recess 75 lies in a radially inner region relative to the second sealing element 67 and may, in order to compensate for assembly inaccuracies, extend over a larger area of the end face 74.
  • the cavity formed by the recess 75 is connected to the tank volume 25 via the third section 73.
  • the third section 73 is formed as a bore through a wall of the housing 7.
  • the pole tube 50 has a recess 76 for the armature 58.
  • an armature space 57 is formed in the pole tube 50, as shown in FIG. 2, or a rear armature space 77 whose volume in the illustrated position of the armature 58 is minimal.
  • In the radial direction of the rear armature space 77 is limited by the pole tube 50.
  • In the axial direction of the rear armature space 77 is bounded on the one hand by the armature 58 on the other hand by a closure member 78, wherein the closure piece 78 closes the pole tube 50 on its side remote from the end face 55 side.
  • the closure piece 78 is sealed with respect to the inner wall of the pole tube 50 with a further sealing element 79.
  • the armature space 57 and the rear armature space 77 are connected to each other via anchor channels 59 and 59 '. During a movement of the armature 58, the pressure medium located in the rear armature space 77 can thus flow into the armature space 57 and vice versa.
  • a sliding bearing 81 is arranged, in which the armature 58 is guided.
  • a second sliding bearing 82 is disposed in the through hole 51. The second sliding bearing 82 is arranged on the armature space 57 towards the oriented end of the through hole 51 and there carries the plunger 29 which is connected to the armature 58.
  • the through hole 51 is formed over its entire length to the armature space 57 with a constant diameter.
  • the gap 68 which is formed between the plunger 29 and the inner wall of the through hole 51 relative to the through hole of Fig. 1b is increased.
  • the pole tube 50 has a contact surface 83, in which a groove 84 is formed for receiving the first sealing element.
  • the intended for insertion into the groove 84 sealing element leaves a through-flow gap open, which connects an undercut 85 with the first channel portion 71.1. It has already been described for the embodiment of FIG. 1b that the undercut 85 forms a circumferential channel 70 in the region of an outlet of the screw connection 52.
  • the first channel section 71.1 connects the armature space 57 with the contact surface 83 and thus allows the return flow of the pressure medium flowing into the armature space 57 via the gap 68.
  • an overflow channel 86 is provided, which extends the through hole 51 at its the armature space 57 side facing in the radial direction so that the pressure medium past the second sliding bearing 82 in the Anchor space 57 can flow.
  • a Antiklebetion 87 is attached, which is the undesirable Magnetic bonding of the armature 58 prevented.
  • the Antiklebetion 87 is this made of non-magnetic material and centered in the embodiment of FIG. 2 at its inner diameter and bonded to the surface of the pole tube 50.
  • the flow path of the pressure medium through the proportional magnet 28 leads via the gap 68, via which the pressure medium, which has flowed past the guide section 65 of the control piston 6 due to the feed pressure, has entered the electromagnet 28. From the gap 68, the pressure medium continues to flow via the overflow channel 86 into the armature space 57. In order to enable a connection from the overflow channel 86 into the armature space 57, it is possible, for example, to provide corresponding recesses in the antikink disk 87. From the armature space 57, the pressure medium flows along the first channel section 71.1 in the direction of the tank volume 25 via the second channel section 71 and the third channel section 73.
  • Fig. 3 an embodiment is shown in which instead of the first sliding bearing 81 and the second sliding bearing 82 film bearings are used. Furthermore, in place of the overflow channel 86 of the already described to Fig. 1b radially enlarged portion 56 of the through hole 51 is formed.
  • the flow path of the pressure medium substantially corresponds to the flow path described in FIG.
  • the pressure medium leakage current leads through the armature space 57, so that a very efficient entrainment of air bubbles located in the armature space 57 takes place.
  • the transport of the air bubbles from the rear armature space 77 is effected by the movement of the armature 58 upon actuation of the proportional magnet 28.
  • the vent which is complete because of the continuous venting during operation, take place during commissioning of the proportional magnet 28.
  • An initially performed by means of a vent then additionally required bleed screw can therefore be omitted.
  • FIG. 4 shows a further exemplary embodiment in which a first channel section 71.2 is formed which leads from the undercut 85 into the widened region 56 of the through-hole 51.
  • the outflow of the first channel portion 71.2 in the extended area 56 of the through hole 51 has the advantage that the pressure medium leakage current does not pass through the armature space 57.
  • no pollution is transported into the region of the armature 58 by the pressure medium flowing through the electromagnet 28. Due to the short connection via the widened region 56, an increase in the service life of the proportional magnet 28 is thus achieved.
  • FIG. 5 to 7 substantially correspond to the embodiments of Figures 2 to 4.
  • a Antiklebeeibe 87 ' is used, which is centered at its outer periphery.
  • the Antiklebesorption 87 ' has as well as the Antiklebeept 87 from the embodiments of Figures 2 to 4 on a central recess, which, however, is dimensioned in its radial extent so large that the first channel portion 71.1 is connected via the central recess with the armature space 57 ,
  • the proposed venting is not limited to use in a proportional solenoid as used in the embodiments, but can also be used with solenoids or pushers.
  • the return flow channel can also be connected to the rear armature space 77.

Description

Die Erfindung betrifft einen Elektromagneten zur Betätigung eines Ventils.The invention relates to an electromagnet for actuating a valve.

Elektromagneten werden häufig zur Betätigung von Ventilen in hydraulischen Systemen eingesetzt. Ein solcher Elektromagnet zur Betätigung eines Ventils ist z. B. aus der DE 37 09 474 C1 bekannt. Der Elektromagnet betätigt dabei einen Ventilschließkörper, der mit einem Dichtsitz in Abhängigkeit von dem Hub des Ventilschließkörpers zu einer variablen Drossel zusammenwirkt.Electromagnets are often used to operate valves in hydraulic systems. Such an electromagnet for actuating a valve is z. B. from DE 37 09 474 C1. The solenoid actuates a valve closing body which cooperates with a sealing seat in response to the stroke of the valve closing body to a variable throttle.

Der Hub des Ventilschließkörpers wird durch einen in axialer Richtung durch ein Magnetfeld bewegten Anker erzeugt. Der Anker ist in axialer Richtung hierzu in einem Ankerraum bewegbar und wird durch eine axial auf den Anker wirkende Feder in einer definierten Ausgangsposition gehalten. Die in dem Inneren des Elektromagneten ausgebildeten Hohlräume sind während des Betriebs des Elektromagneten mit dem Druckmittel gefüllt, so dass die Bewegung des Ankers bedämpft ist. Der Ankerraum bzw. das den Ankerraum in axialer Richtung begrenzende Polrohr ist in radialer Richtung außen von einer Spule umgeben, welche bei Bestromen ein Magnetfeld erzeugt, das den Anker in Richtung des Polrohrs entgegen der Kraft der Feder mit einer magnetischen Kraft beaufschlagt.The stroke of the valve closing body is generated by an armature moved in the axial direction by a magnetic field. The armature can be moved in an axial direction in an armature space and is held by a spring acting axially on the armature in a defined starting position. The cavities formed in the interior of the electromagnet are filled with the pressure medium during the operation of the electromagnet, so that the movement of the armature is damped. The armature space or the armature space bounding in the axial direction of the pole tube is surrounded in the radial direction on the outside by a coil which generates a magnetic field during energization, which acts on the armature in the direction of the pole tube against the force of the spring with a magnetic force.

Der rückwärtige Ankerraum wird dabei in seinem Volumen reduziert und das darin befindliche Druckmittel wird verdrängt. Gleichzeitig entsteht durch die axiale Bewegung des Ankers auf der gegenüberliegenden Seite des Ankers ein Volumen, in das das verdrängte Druckmittel einströmt. Das verdrängte Druckmittel strömt dabei am radial äußeren Umfang des Ankers entlang, wobei dieser Ringsspalt über eine Entlüftungsventileinrichtung mit der Umgebung verbunden ist.The rear armature space is thereby reduced in volume and the pressure medium therein is displaced. At the same time created by the axial movement of the armature on the opposite side of the armature, a volume in which flows in the displaced pressure medium. The displaced pressure medium flows along the radially outer circumference of the armature along, this annular gap is connected via a vent valve device with the environment.

Die sich dabei in dem Ankerraum befindende Luft muss bei der Inbetriebnahme des Elektromagneten aus dem Ankerraum entfernt werden. Hierzu ist bei dem in der DE 37 09 474 C1 beschriebenen Elektromagneten eine Entlüftungsventileinrichtung vorgesehen, welche über eine Querbohrung den um den Anker herum befindlichen Ringsspalt mit der Umgebung des Elektromagneten verbindet.The air in the armature space must be removed from the armature space when the electromagnet is put into operation. For this purpose, a vent valve device is provided in the electromagnet described in DE 37 09 474 C1, which connects via a transverse bore located around the armature ring gap with the environment of the electromagnet.

Die Entlüftungsventileinrichtung ist ähnlich einem Wechselventil aufgebaut. Der in dem Entlüftungsventil angeordnete Schließkörper hat eine geringere spezifische Dichte als das verwendete Druckmittel. Aufgrund der Schwerkraft gibt der Schließkörper daher solange einen durchströmbaren Querschnitt frei, bis das Niveau des entlang dem Ventilschließkörper nachströmenden Druckmittels, welches bei Betrieb des Ventils durch den Förderdruck in den Ankerraum gedrückt wird, den Schließkörper des Entlüftungsventils erreicht hat. Der Schließkörper schwimmt dann auf dem Druckmittel und wird gegen den nach außen gerichteten Dichtsitz gedrückt, wodurch das Entlüftungsventil verschlossen ist.The vent valve device is constructed similar to a shuttle valve. The arranged in the vent valve closing body has a lower specific gravity than the pressure medium used. Due to gravity, the closing body therefore releases as long as a flow-through cross section until the level of the pressure medium flowing along the valve closing body, which is pressed by the delivery pressure in the armature space during operation of the valve, has reached the closing body of the vent valve. The closing body then floats on the pressure medium and is pressed against the outwardly directed sealing seat, whereby the vent valve is closed.

Neben dem erheblichen Aufwand, der durch die Integration eines solchen Wechselventils in den Elektromagneten entsteht, hat die beschriebene Entlüftung den Nachteil, dass beim Befüllen das Ventil durch das Druckmittel geschlossen wird. Insbesondere bei einem Wiederbefüllen des entleerten Ankerraums mit dem Druckmittel ist es unvermeidbar, dass in dem verhältnismäßig zähflüssigen Druckmittel Rückstände eingeschlossener Luft in dem rückwärtigen Ankerraum zurückbleiben. Dieser Lufteinschluss verschlechtert das Dämpfungsverhalten und machen es schwierig die Dämpfung abzustimmen, da durch die Bewegung des Ankers unterschiedliche Verteilungen der Luft auftreten können. Die eingeschlossene Luft wird bei der Bewegung des Ankers lediglich hin und hergeschoben, kann jedoch aus dem Ankerraum nicht mehr entweichen, da das Entlüftungventil verschlossen bleibt.In addition to the considerable effort that results from the integration of such a shuttle valve in the electromagnet, the vent described has the disadvantage that when filling the valve is closed by the pressure medium. In particular, when refilling the emptied armature space with the pressure medium, it is unavoidable that residues of trapped air in the relatively viscous pressure medium remain in the rear armature space. This air entrapment degrades the damping behavior and makes it difficult to tune the damping, since the movement of the armature different distributions of the air can occur. The trapped air is only pushed back and forth during the movement of the armature, but can no longer escape from the armature space, since the vent valve remains closed.

Ein weiterer Nachteil ist, dass die Funktion des Ventils abhängig von der Einbaulage des Elektromagneten ist. Ein mit dem beschriebenen Entlüftungsventil ausgerüstetes hydraulisches Ventil weist daher eine vorgegebene Einbaulage auf.Another disadvantage is that the function of the valve is dependent on the mounting position of the electromagnet. A equipped with the described vent valve hydraulic valve therefore has a predetermined mounting position.

Ein weiterer Nachteil ist, dass das Verschließen der Entlüftungsbohrung über das Druckmittel erfolgt, welches in der Regel ein Öl ist. Bei einem teilweisen Entweichen des Druckmittels aus dem Ankerraum, z.B. während einer darauf folgenden längeren Standzeit, kann es daher zum Verkleben des Schließkörpers kommen, wodurch die Funktion bei einer erneuten Inbetriebnahme nicht mehr gewährleistet ist.Another disadvantage is that the closing of the vent hole via the pressure medium, which is usually an oil. In a partial escape of the pressure medium from the armature space, for example, during a subsequent longer service life, it may therefore come to sticking of the closing body, whereby the function is no longer guaranteed at a restart.

Die DE 44 17 587 A1 offenbart einen Elektromagneten gemäß dem Oberbegriff des Anspruchs 1. Der Gegenstand des Anspruchs 1 unterscheidet sich daher von dem bekannten Elektromagneten dadurch, dass zumindest ein erster Kanalabschnitt des Rückflusskanals in einem Polrohr angeordnet ist, und dass in einem Gehäusedeckel ein zweiter Kanalabschnitt des Rückflusskanals vorgesehen ist, welcher aus dem Gehäusedeckel an einer zur Anlage an einem Ventilgehäuse vorgesehenen Fläche ausmündet.DE 44 17 587 A1 discloses an electromagnet according to the preamble of claim 1. The subject matter of claim 1 therefore differs from the known electromagnet in that at least a first channel portion of the return flow channel is arranged in a pole tube, and that in a housing cover a second Channel section of the return flow channel is provided, which opens out of the housing cover at a provided for engagement with a valve housing surface.

Die mit der vorliegenden Erfindung zu lösende Aufgabe kann somit darin gesehen werden, einen Elektromagneten zur Betätigung eines Ventils mit einem Rückflusskanal für einen Druckmittelleckagestrom zu schaffen, der in einfacher Weise an verschiedene Ventile angepasst werden kann und der kostengünstig gefertigt werden kann.The object to be achieved by the present invention can thus be seen to provide an electromagnet for actuating a valve with a return channel for a pressure medium leakage current, which can be easily adapted to different valves and can be manufactured inexpensively.

Die Aufgabe wird durch den erfindungsgemäßen Elektromagneten mit den Merkmalen des Anspruchs 1 gelöst.The object is achieved by the electromagnet according to the invention with the features of claim 1.

Der erfindungsgemäße Elektromagnet hat den Vorteil, dass mit dem Ankerraum ein Rückflusskanal verbunden ist, über welchen das in den Ankerraum eintretende Leckagefluid in ein Tankvolumen abfließt. Damit wird während des Betriebs des Elektromagneten ein zwar geringer aber kontinuierlich auftretender Leckagestrom erreicht. Dieser Leckagestrom erzeugt einerseits in dem Ankerraum einen geringfügigen Unterdruck, andererseits können Luftbläschen, welche aufgrund der Bewegung des Ankers in den Bereich der Strömung transportiert wurden, mitsamt der Leckageströmung über den Rückflusskanal abgeführt werden.The electromagnet according to the invention has the advantage that with the armature space, a return flow channel is connected, via which the leakage fluid entering the armature space flows into a tank volume. This achieves a lower but continuously occurring leakage current during operation of the electromagnet. On the one hand, this leakage current generates a slight negative pressure in the armature space, and on the other hand, air bubbles which have been transported into the region of the flow due to the movement of the armature can be removed together with the leakage flow via the return flow channel.

Der Rückflusskanal ist während des Betriebs des Elektromagneten jederzeit offen, so dass auch bei einer näherungsweise vollständigen Befüllung des Elektromagneten mit dem Druckmittel der Druckmittelleckagestrom erhalten bleibt. Auf diese Weise ist es möglich, dass Lufteinschlüsse, die auch bei einer nahezu vollständigen Befüllung mit Druckmittel noch in dem rückwärtigen Ankerraum vorhanden sein können, noch aus dem Inneren des Elektromagneten entfernt werden. Die Lufteinschlüsse werden dann durch die Bewegung des Ankers in den Bereich befördert, in dem die Strömung aufgrund der Druckmittelleckage auftritt. Die Bewegung der eingeschlossenen Luft wird dabei einerseits durch den von der Strömung erzeugten Unterdruck und andererseits durch die Verwirbelung, die aufgrund der Strömung entsteht, begünstigt.The return flow channel is open at any time during operation of the electromagnet, so that the pressure medium leakage current is maintained even when the electromagnet is approximately completely filled with the pressure medium remains. In this way, it is possible that air inclusions, which may still be present in the rear armature space even with an almost complete filling with pressure medium, are still removed from the interior of the electromagnet. The air pockets are then conveyed by the movement of the armature into the area in which the flow occurs due to the pressure medium leakage. The movement of the trapped air is promoted on the one hand by the negative pressure generated by the flow and on the other hand by the turbulence which arises due to the flow.

In den Unteransprüchen sind vorteilhafte Weiterbildungen des erfindungsgemäßen Elektromagneten dargestellt.In the dependent claims advantageous developments of the electromagnet according to the invention are shown.

Insbesondere ist es vorteilhaft, dass der Rückflusskanal direkt in den Ankerraum ausmündet, da hierdurch eine besonders effektive Entlüftung erfolgt. Das aus dem rückwärtigen Ankerraum durch die Bewegung des Ankers verdrängte Druckmittel transportiert somit die in dem rückwärtigen Ankerraum enthaltenen Luftbläschen in die unmittelbaren Nähe der Leckageströmung. Damit ist die Mitnahme der Luftbläschen durch den Leckagestrom besonders einfach und es ergibt sich eine schnelle Entlüftung.In particular, it is advantageous that the return flow channel opens directly into the armature space, since this results in a particularly effective venting. The displaced from the rear armature space by the movement of the armature pressure medium thus transported the air bubbles contained in the rear armature space in the immediate vicinity of the leakage flow. Thus, the entrainment of the air bubbles by the leakage flow is particularly simple and it results in a fast venting.

Eine weitere vorteilhafte Ausführung ergibt sich, indem der Rückflusskanal in einem erweiterten Bereich des Polrohrs angeordnet ist. Durch eine solche Anordnung wird der Leckagestrom nicht durch den Ankerraum geführt, wodurch die Gefahr verringert wird, dass Schmutzpartikel, die in dem Leckagestrom enthalten sein können, bis zum Anker transportiert werden. Solche Verschmutzungen, welche sich im Bereich des Ankers befinden, wirken sich nachteilig auf die Lebensdauer des Elektromagneten aus. Gegenüber der Ausmündung des Rückflusskanals unmittelbar in den Ankerraum bildet sich bei der Ausmündung in dem Polrohr aufgrund der geringeren Strömungsquerschnitte eine höhere Strömungsgeschwindigkeit der Leckageströmung aus, die wiederum das Entweichen der eingeschlossenen Luftbläschen verbessert.A further advantageous embodiment results in that the return flow channel is arranged in an extended region of the pole tube. By such an arrangement, the leakage flow is not guided through the armature space, whereby the risk is reduced that dirt particles that may be contained in the leakage flow are transported to the anchor. Such contaminants, which are located in the region of the armature, have an adverse effect on the life of the electromagnet. Opposite the mouth of the return flow channel directly into the armature space, a higher flow velocity of the leakage flow is formed at the outlet in the pole tube due to the smaller flow cross-sections. which in turn improves the escape of trapped air bubbles.

Weiterhin ist es vorteilhaft, den Rückflusskanal so in dem Elektromagnet auszubilden, dass eine direkte Anschlussmöglichkeit an das in der betätigten Ventileinheit befindliche Tankvolumen gegeben ist. Gemäß einer vorteilhaften Weiterbildung des erfindungsgemäßen Elektromagneten befindet sich hierzu der Rückflusskanal in einem Polrohr, welches auch die Führung des auf das zu betätigende Ventil wirkenden Stößels übernimmt.Furthermore, it is advantageous to design the return flow channel in the electromagnet so that there is a direct connection possibility to the tank volume located in the actuated valve unit. According to an advantageous embodiment of the electromagnet according to the invention, this is the return flow channel in a pole tube, which also takes over the leadership of the acting on the valve to be actuated plunger.

Vorteilhafte Ausführungsbeispiele des erfindungsgemäßen Elektromagneten sind in der Zeichnung dargestellt und werden anhand der nachfolgende Beschreibung näher erläutert. Es zeigen:

Fig. 1a
eine schematische geschnittene Darstellung einer mit einem erfindungsgemäßen Elektromagneten betätigten Ventileinheit,
Fig. 1b
eine vergrößerte Darstellung eines Ausschnitts der Fig. 1a,
Fig. 2
eine geschnittene Teildarstellung eines ersten Ausführungsbeispiels eines erfindungsgemäßen Elektromagneten,
Fig. 3
eine geschnittene Teildarstellung eines zweiten Ausführungsbeispiels eines erfindungsgemäßen Elektromagneten,
Fig. 4
eine geschnittene Teildarstellung eines dritten Ausführungsbeispiels eines erfindungsgemäßen Elektromagneten,
Fig. 5
eine geschnittene Teildarstellung eines vierten Ausführungsbeispiels eines erfindungsgemäßen Elektromagneten,
Fig. 6
eine geschnittene Teildarstellung eines fünften Ausführungsbeispiels eines erfindungsgemäßen Elektromagneten, und
Fig. 7
eine geschnittene Teildarstellung eines sechsten Ausführungsbeispiels eines erfindungsgemäßen Elektromagneten.
Advantageous embodiments of the electromagnet according to the invention are illustrated in the drawings and will be explained in more detail with reference to the following description. Show it:
Fig. 1a
1 is a schematic sectional view of a valve unit actuated by an electromagnet according to the invention;
Fig. 1b
an enlarged view of a detail of Fig. 1a,
Fig. 2
a partial sectional view of a first embodiment of an electromagnet according to the invention,
Fig. 3
a partial sectional view of a second embodiment of an electromagnet according to the invention,
Fig. 4
a sectional partial view of a third embodiment of an electromagnet according to the invention,
Fig. 5
3 is a partial sectional view of a fourth embodiment of an electromagnet according to the invention,
Fig. 6
a sectional partial view of a fifth embodiment of an electromagnet according to the invention, and
Fig. 7
a sectional partial view of a sixth embodiment of an electromagnet according to the invention.

In Fig. 1a ist ein erstes Beispiel einer Verstellvorrichtung 1 mit einem durch den erfindungsgemäßen Elektromagneten betätigten Ventil dargestellt. Zum Regeln eines Schwenkwinkels einer nicht dargestellten hydrostatischen Kolbenmaschine wird ein Stellkolben 2 in einer Stelldruckkammer 3 sowie einer zweiten Stelldruckkammer 4 mit einem Stelldruck beaufschlagt. Die in der ersten und zweiten Stelldruckkammer 3 und 4 wirkenden Stelldrücke wirken auf die entgegengesetzt orientierten Kolbenflächen des Stellkolbens 2, an dem bei einer Druckdifferenz eine resultierende Kraft angreift. Zur Einstellung der Druckdifferenz in den beiden Stelldruckkammern 3 und 4 ist ein Stelldruckregelventil 5 vorgesehen. Das Stelldruckregelventil 5 weist einen Regelkolben 6 auf, der in einer Bohrung eines Gehäuses 7 axial verschieblich angeordnet ist. Weiterhin sind in dem Gehäuse 7 eine erste Speisedruckbohrung 8 sowie eine zweite Speisedruckbohrung 9 eingebracht. Die erste Speisedruckbohrung 8 und zweite Speisedruckbohrung 9 sind mit einer Speisedruckleitung 14 verbunden, die beispielsweise an einer Hilfsdruckquelle angeschlossen sein kann.In Fig. 1a, a first example of an adjusting device 1 is shown with an actuated by the solenoid according to the invention valve. To control a swivel angle of a hydrostatic piston machine, not shown, a control piston 2 is acted upon in a control pressure chamber 3 and a second control pressure chamber 4 with a control pressure. The actuating pressures acting in the first and second actuating pressure chambers 3 and 4 act on the oppositely oriented piston surfaces of the actuating piston 2, at which a resultant force acts on a pressure difference. To set the pressure difference in the two control pressure chambers 3 and 4, a control pressure control valve 5 is provided. The control pressure control valve 5 has a control piston 6 which is arranged axially displaceably in a bore of a housing 7. Furthermore, a first feed pressure bore 8 and a second feed pressure bore 9 are introduced into the housing 7. The first feed pressure bore 8 and second feed pressure bore 9 are connected to a feed pressure line 14, which may be connected, for example, to an auxiliary pressure source.

Zum Einstellen der Stelldrücke in der ersten Stelldruckkammer 3 und der zweiten Stelldruckkammer 4 ist die Speisedruckleitung 14 bzw. die erste Speisedruckbohrung 8 oder die zweite Speisedruckbohrung 9 mit einer ersten Stelldruckleitung 12 oder einen zweiten Stelldruckleitung 13 verbindbar. Hierzu ist die erste Stelldruckleitung 12 an einem ersten Stelldruckkanal 10 angeschlossen, der seitens des Regelkolbens 6 in eine erste Nut 15 mündet. Ebenso ist die zweite Stelldruckleitung 13 über einen zweiten Stelldruckkanal 11 mit einer zweiten Nut 16 verbunden. Im Bereich der ersten bzw. zweiten Nut 15 bzw. 16 weist der Regelkolben 6 einen ersten Regelkolbenabschnitt 17 bzw. einen zweiten Regelkolbenabschnitt 18 auf. Die beiden Regelkolbenabschnitte 17 bzw. 18 weisen eine erste Stelldrucksteuerkante 19 bzw. eine zweite Stelldrucksteuerkante 20 auf, die an den entgegengesetzt orientierten Enden des jeweiligen Regelkolbenabschnitts 17 bzw. 18 angeordnet sind. Die erste Stelldrucksteuerkante 19 und die zweite Stelldrucksteuerkante 20 bilden mit der jeweiligen ersten Nut 15 bzw. zweiten Nut 16 eine in Abhängigkeit von der axialen Position des Regelkolbens 6 variable Drosselstelle aus. Durch die gemeinsame Bewegung der beiden Steuerkanten 19 bzw. 20 wird dabei jeweils eine Drossel geöffnet und gleichzeitig die andere Drossel geschlossen.To set the control pressures in the first control pressure chamber 3 and the second control pressure chamber 4, the feed pressure line 14 and the first feed pressure bore 8 or the second feed pressure bore 9 with a first actuating pressure line 12 or a second actuating pressure line 13 connectable. For this purpose, the first actuating pressure line 12 is connected to a first actuating pressure channel 10 connected, which opens on the part of the control piston 6 in a first groove 15. Likewise, the second actuating pressure line 13 is connected via a second actuating pressure channel 11 with a second groove 16. In the region of the first and second groove 15 and 16, the control piston 6 has a first control piston section 17 and a second control piston section 18, respectively. The two control piston sections 17 and 18 respectively have a first control pressure control edge 19 and a second control pressure control edge 20, which are arranged at the oppositely oriented ends of the respective control piston section 17 or 18. The first control pressure control edge 19 and the second control pressure control edge 20 form with the respective first groove 15 and second groove 16 a variable depending on the axial position of the control piston 6 throttle point. By the common movement of the two control edges 19 and 20, one throttle is opened while the other throttle is closed.

Je nach Bewegungsrichtung der Regelkolbens 6 wird damit der erste Stelldruckkanal 10 über die erste Nut 15 mit einer ersten Speisedrucknut 21 verbunden und damit die erste Stelldruckkammer 3 mit dem Druck aus der Speisedruckleitung 14 bedrückt. Analog wird der zweite Stelldruckkanal 11 über die zweite Nut 16 mit einer zweiten Speisedrucknut 22 verbunden, wenn der Regelkolben 6 in die entgegengesetzte Richtung ausgelenkt wird.Depending on the direction of movement of the control piston 6 so that the first actuating pressure channel 10 is connected via the first groove 15 with a first feed pressure 21 and thus the first actuating pressure chamber 3 is depressed with the pressure from the feed pressure line 14. Similarly, the second actuating pressure channel 11 is connected via the second groove 16 with a second feed pressure groove 22 when the control piston 6 is deflected in the opposite direction.

Auf der von der ersten Stelldrucksteuerkante 19 abgewandten Seite des ersten Regelkolbenabschnitts 17 ist eine erste Entspannungssteuerkante 23 angeordnet. Ebenso ist an dem zweiten Regelkolbenabschnitt 18 eine zweite Entspannungssteuerkante 24 angeordnet. In Abhängigkeit von der axial Position des Regelkolbens 6 wird über die beiden Entspannungssteuerkanten 23 bzw. 24 die jeweilige Stelldruckkammer 3 bzw. 4 über die erste Nut 15 bzw. die zweite Nut 16 in ein Tankvolumen 25 entspannt.On the side remote from the first control pressure control edge 19 side of the first control piston portion 17, a first expansion control edge 23 is arranged. Likewise, a second expansion control edge 24 is arranged on the second control piston section 18. Depending on the axial position of the control piston 6, the respective control pressure chamber 3 or 4 is expanded via the two expansion control edges 23 and 24 via the first groove 15 and the second groove 16 into a tank volume 25.

Ebenfalls mit dem Tankvolumen 25 verbunden ist über einen Volumenausgleichskanal 26 der rückwärtige Regelkolbenraum 27. Die geringfügigen Volumenschwankungen, die in dem rückwärtigen Regelkolbenraum 27 durch eine axiale Bewegung des Regelkolbens 6 entstehen, werden damit ausgeglichen. Außerdem wird ein Teil der Regelkolbenleckage über den Volumenausgleichskanal 26 ins Tankvolumen 25 abgeführt.Also connected to the tank volume 25 is via a volume equalization channel 26 of the rear control piston chamber 27. The slight volume fluctuations that arise in the rear control piston chamber 27 by an axial movement of the control piston 6 are thus compensated. In addition, part of the control piston leakage is discharged via the volume equalization channel 26 into the tank volume 25.

Um den Stellkolben 2 in seine zweite Endposition zu verstellen, ist ein Proportionalmagnet 28 vorgesehen, welcher an dem Gehäuse 7 des Regelventils 5 angeordnet ist. Der Proportionalmagnet 28 weist einen Stößel 29 auf, wobei der Stößel 29 auf eine Stirnfläche 30 des Regelkolbens 6 wirkt. Damit ist auf den Regelkolben 6 in axialer Richtung eine Steuerkraft übertragbar, welche durch den Proportionalmagneten 28 in Abhängigkeit von einem Steuersignal erzeugt wird, das dem Proportionalmagneten 28 über einen nicht dargestellten elektrischen Anschluß zugeführt wird. Wird dem Proportionalmagneten 28 über den elektrischen Anschluß ein solches Steuersignal zugeführt, so erzeugt er eine Kraft, die den Regelkolben 6 verschiebt. Dabei wird durch die axiale Bewegung des Regelkolbens 6 an der ersten Stelldrucksteuerkante 19 ein durchströmbarer Spalt erzeugt. Das über die Speisedruckleitung 14 und die erste Speisedruckbohrung 8 zugeführte Druckmittel kann über den ersten Stelldruckkanal 10 in die erste Stelldruckkammer 3 gelangen. Der somit in der ersten Stelldruckkammer 3 erhöhte Druck bewirkt eine Verstellung des Stellkolbens 2 entgegen der Kraft einer Rückstellfeder 40 in Richtung seiner zweiten Endposition.In order to adjust the actuating piston 2 in its second end position, a proportional solenoid 28 is provided, which is arranged on the housing 7 of the control valve 5. The proportional magnet 28 has a plunger 29, wherein the plunger 29 acts on an end face 30 of the control piston 6. Thus, a control force can be transmitted to the control piston 6 in the axial direction, which is generated by the proportional magnet 28 in response to a control signal which is supplied to the proportional solenoid 28 via an electrical connection, not shown. If the proportional magnet 28 is supplied with such a control signal via the electrical connection, it generates a force which displaces the control piston 6. In this case, a flow-through gap is generated by the axial movement of the control piston 6 at the first control pressure control edge 19. The pressure medium supplied via the feed pressure line 14 and the first feed pressure bore 8 can reach the first setting pressure chamber 3 via the first setting pressure passage 10. The thus increased pressure in the first actuating pressure chamber 3 causes an adjustment of the actuating piston 2 against the force of a return spring 40 in the direction of its second end position.

Gleichzeitig mit dem Öffnen der Drosselstelle an der ersten Stelldrucksteuerkante 19 wird im zweiten Regelkolbenabschnitt 18 die Drosselstelle der zweiten Entlastungssteuerkante 24 geöffnet. Der zweite Stelldruckraum 4 wird über die zweite Stelldruckleitung 13 sowie den zweiten Stelldruckkanal 11 in das Tankvolumen 25 entspannt.Simultaneously with the opening of the throttle point at the first control pressure control edge 19, the throttle point of the second discharge control edge 24 is opened in the second control piston section 18. The second control pressure chamber 4 is expanded via the second control pressure line 13 and the second control pressure channel 11 in the tank volume 25.

Zur Rückkopplung der Stellbewegung des Stellkolbens 2 ist in dem Stellkolben 2 eine Mitnehmerausnehmung 33 vorgesehen, in welcher ein Mitnehmerkopf 32 angeordnet ist, der mit dem Stellhebel 31 verbunden ist. Der Stellhebel 31 ist auf einem Lagerbolzen 34 drehbar gelagert, so daß die Stellbewegung des Stellkolbens 2 zu einer Drehung des Stellhebels 31 führt. Ebenfalls auf dem Lagerbolzen 34 drehbar gelagert sind ein erster Schenkel 35 sowie ein zweiter Schenkel 36. Der erste Schenkel 35 sowie der zweite Schenkel 36 sind über eine Zugfeder 37 miteinander verbunden, so daß eine Auslenkung eines der beiden Schenkel relativ zu dem anderen zu einer Spannung der Zugfeder 37 führt.For the feedback of the adjusting movement of the adjusting piston 2, a Mitnehmerausnehmung 33 is provided in the adjusting piston 2, in which a driving head 32 is arranged, which is connected to the adjusting lever 31. The adjusting lever 31 is rotatably mounted on a bearing pin 34, so that the adjusting movement of the actuating piston 2 leads to a rotation of the actuating lever 31. Also rotatably mounted on the bearing pin 34 are a first leg 35 and a second leg 36. The first leg 35 and the second leg 36 are connected via a tension spring 37 with each other, so that a deflection of one of the two legs relative to the other to a voltage the tension spring 37 leads.

An dem zu dem Mitnehmerkopf 32 des Stellhebels 31 entgegengesetzten Ende des Stellhebels 31 ist ein Mitnahmestift 38 angeordnet. Bei einer Bewegung des Stellkolbens 2 und einer damit verbundenen Drehbewegung des Stellhebels 31 bewegt sich der Mitnahmestift 38 gegenläufig zu der Stellkolbenbewegung. Der Mitnahmestift 38 liegt an dem zweiten Schenkel 36 an, so daß durch die Drehbewegung des Stellhebels 31 der zweite Schenkel 36 relativ zu dem ersten Schenkel 35 ausgelenkt wird und die Feder 37 gespannt wird.At the opposite end to the driving head 32 of the actuating lever 31 end of the actuating lever 31, a driving pin 38 is arranged. During a movement of the actuating piston 2 and an associated rotational movement of the adjusting lever 31, the driving pin 38 moves in opposite directions to the actuating piston movement. The driving pin 38 abuts against the second leg 36, so that the second leg 36 is deflected relative to the first leg 35 by the rotational movement of the actuating lever 31 and the spring 37 is tensioned.

Die in der Fig. 1a dargestellte Verstellvorrichtung 1 wird betätigt, indem über den Proportionalmagneten 28 auf den Regelkolben 6 eine Kraft ausgeübt wird. Dieses Zusammenwirken wird anhand der Fig. 1b erläutert. Der Proportionalmagnet 28 weist hierzu ein von einer nicht dargestellten Spule umgebenes Polrohr 50 auf, welches entlang seiner Längsachse von einer Durchgangsbohrung 51 durchdrungen ist. Der Durchmesser der Durchgangsbohrung 51 ist so bemessen, dass die Durchgangsbohrung 51 eine Leckagespalt mit den Stößel 29 bildet. Das Polrohr 50 ist mittels einer Schraubverbindung 52 in einem Gehäusedeckel 53 des Proportionalmagneten 28 befestigt. Zur Abdichtung des Polrohrs 50 gegenüber dem Gehäusedeckel 53 ist ein Dichtelement 54 in einer dafür vorgesehenen Nut des Polrohrs 50 angeordnet.The adjusting device 1 shown in FIG. 1a is actuated by exerting a force on the control piston 6 via the proportional magnet 28. This interaction will be explained with reference to FIG. 1b. For this purpose, the proportional magnet 28 has a pole tube 50 surrounded by a coil, not shown, which is penetrated along its longitudinal axis by a through-hole 51. The diameter of the through hole 51 is dimensioned so that the through hole 51 forms a leakage gap with the plunger 29. The pole tube 50 is fastened by means of a screw connection 52 in a housing cover 53 of the proportional magnet 28. For sealing the pole tube 50 relative to the housing cover 53 is a Sealing element 54 disposed in a groove provided for this purpose of the pole tube 50.

Der Stößel 29 steht geringfügig über die Stirnfläche 55 des Polrohrs 50 hinaus und liegt dort an der Stirnfläche 30 des Regelkolbens 6 an. An der von der Stirnfläche 55 des Polrohrs 50 abgewandten Seite weist die Durchgangsbohrung 51 einen radial erweiterten Abschnitt 56 auf, an den sich ein im dargestellten Ausführungsbeispiel als Ausnehmung des Polrohrs 50 ausgebildeter Ankerraum 57 anschließt. In dem Ankerraum 57 ist ein Anker 58 angeordnet, der mit dem Stößel 29 in Wirkverbindung steht. In dem Anker 58 sind parallel zu seiner Längsachse Ankerkanäle 59 ausgebildet, die die beiden voneinander abgewandten Stirnseiten des Ankers 58 miteinander verbinden.The plunger 29 projects slightly beyond the end face 55 of the pole tube 50 and rests there against the end face 30 of the control piston 6. At the side facing away from the end face 55 of the pole tube 50, the through-bore 51 has a radially widened section 56, to which an armature space 57 formed as a recess of the pole tube 50 in the illustrated exemplary embodiment adjoins. In the armature space 57, an armature 58 is arranged, which is in operative connection with the plunger 29. In the armature 58 anchor channels 59 are formed parallel to its longitudinal axis, which connect the two opposite end faces of the armature 58 with each other.

Durch Bestromung der nicht dargestellten Spulenelemente des Elektromagneten wird der Anker 58 durch das entstehende Magnetfeld mit einer Kraft in axialer Richtung beaufschlagt, welche ihn so verschiebt, dass das Volumen des Ankerraums 57 verringert wird. Da der Anker 58 in Wirkverbindung mit dem Stößel 29 steht, wird diese axiale Bewegung auf den Stößel 29 übertragen, der seinerseits wiederum die axiale Bewegung auf die Stirnfläche 30 des Regelkolbens 6 überträgt. Wird der Strom für die Spulenelemente abgeschaltet, so wirkt auf den Anker 58 keine Kraft mehr und er wird über die von dem Regelkolben 6 auf den Stößel 29 übertragene Gegenkraft in der dargestellten Anordnung der Fig. 1b nach rechts verschoben. Zwischen dem Ankerraum 57 und dem in der Fig. 1b nicht dargestelltem rückwärtigen Ankerraum besteht dabei eine Verbindung über die Ankerkanäle 59, so dass zwischen dem Ankerraum 57 und dem rückwärtigen Ankerraum ein Volumenausgleich erfolgt.By energizing the coil elements of the electromagnet, not shown, the armature 58 is acted upon by the resulting magnetic field with a force in the axial direction, which shifts him so that the volume of the armature space 57 is reduced. Since the armature 58 is in operative connection with the plunger 29, this axial movement is transmitted to the plunger 29, which in turn transmits the axial movement to the end face 30 of the control piston 6. If the current for the coil elements is turned off, no force acts on the armature 58 and it is displaced to the right via the counter-force transmitted by the control piston 6 to the tappet 29 in the illustrated arrangement of FIG. There is a connection between the armature space 57 and the rear armature space, not shown in FIG. 1b, via the armature channels 59, so that a volume compensation takes place between the armature space 57 and the rear armature space.

Die Stirnfläche 30 des Regelkolbens 6 ist an einem Fortsatz 60 ausgebildet. Der Fortsatz 60 durchdringt eine Öffnung 61 einer Federscheibe 62, welche in einer Aufnahmeöffnung 63 des Gehäuses 7 angeordnet ist. Die Federscheibe 62 ist so in der Aufnahmeöffnung 63 angeordnet, dass der durch die Gegenkraft zurück getriebene Regelkolben 6 mit einer Anschlagfläche 64 daran anschlägt und dort eine definierte Bremskraft erfährt. Die Anschlagfläche 64 ist dabei an einem Führungsabschnitt 65 ausgebildet.The end face 30 of the control piston 6 is formed on an extension 60. The extension 60 penetrates an opening 61 of a spring washer 62, which in a Receiving opening 63 of the housing 7 is arranged. The spring washer 62 is arranged in the receiving opening 63 that the driven back by the opposing force control piston 6 abuts with a stop surface 64 there and undergoes a defined braking force there. The stop surface 64 is formed on a guide portion 65.

Der Gehäusedeckel 53 weist einen zylindrischen Fortsatz 66 auf, der in die Aufnahmeöffnung 63 des Gehäuses 7 hineinragt. Die Federscheibe 62 kann beispielsweise über den zylindrischen Fortsatz 66 in der Aufnahmeöffnung 63 fixiert werden. Zur Abdichtung ist in einer Nut des Gehäusedeckels 53 ein weiteres Dichtelement 67 angeordnet, welches den Proportionalmagneten 28 gegenüber dem Gehäuse 7 abdichtet.The housing cover 53 has a cylindrical extension 66, which projects into the receiving opening 63 of the housing 7. The spring washer 62 can be fixed in the receiving opening 63, for example via the cylindrical extension 66. For sealing a further sealing element 67 is arranged in a groove of the housing cover 53, which seals the proportional magnet 28 relative to the housing 7.

Zwischen dem Führungsabschnitt 65 des Regelkolbens 6 und dem Gehäuse 7 bildet sich eine Druckmittelleckage aus, durch die es zu einem Druckmittelfluss aus der Speisedruckbohrung 8 an dem Führungsabschnitt 65 vorbei in Richtung des Proportionalmagneten 28 kommt. Das Druckmittel füllt zunächst die Aufnahmeöffnung 63 und durchströmt dann auch einen Spalt 68, welcher in der Durchgangsbohrung 51 zwischen der Innenwand des Polrohrs 50 und dem darin angeordneten Stößel 29 ausgebildet ist. Der Ankerraum 57 bildet ein geschlossenes Volumen aus.Between the guide portion 65 of the control piston 6 and the housing 7, a pressure medium leakage forms, through which it comes to a pressure medium flow from the feed pressure bore 8 on the guide portion 65 in the direction of the proportional magnet 28. The pressure medium first fills the receiving opening 63 and then also flows through a gap 68, which is formed in the through hole 51 between the inner wall of the pole tube 50 and the plunger 29 arranged therein. The armature space 57 forms a closed volume.

Um für das einströmende Druckmittel eine Abflussmöglichkeit zu schaffen und damit die zum Entlüften erforderliche Strömung zu schaffen, ist in dem Polrohr 50 ein erster Kanalabschnitt 69 eines Rückflusskanals vorgesehen, welcher den erweiterten Bereich 56 der Durchgangsbohrung 51 mit einem umlaufenden Kanal 70 verbindet. Der umlaufende Kanal kann beispielsweise als Freistich im Auslaufbereich der Schraubverbindung 52 ausgeführt sein. Das zurückfließende Druckmittel fließt über einen zweiten Kanalabschnitt 71 des Rückflusskanals und einen dritten Kanalabschnitt 73 zurück in das Tankvolumen 25.In order to create a drainage possibility for the inflowing pressure medium and thus to provide the necessary for venting flow, a first channel section 69 of a return flow channel is provided in the pole tube 50, which connects the widened region 56 of the through-hole 51 with a circumferential channel 70. The encircling channel can be embodied, for example, as an undercut in the outlet region of the screw connection 52. The flowing back pressure medium flows through a second channel section 71 of the return flow channel and a third channel section 73 back into the tank volume 25.

Der zweite Kanalabschnitt 71 des Rückflusskanals mündet an einer in Richtung des zylindrischen Fortsatzes 66 gerichteten Stirnseite 74 aus. Im dargestellten Ausführungsbeispiel ist in der Stirnseite 74 des Gehäusedeckels 53 eine Ausnehmung 75 angeordnet. Die Ausnehmung 75 liegt dabei in einem radial inneren Bereich relativ zu dem zweiten Dichtelement 67 und kann sich, um Montageungenauigkeiten auszugleichen, über eine größere Fläche der Stirnseite 74 erstrecken. Der durch die Ausnehmung 75 ausgebildeter Hohlraum ist über den dritten Abschnitt 73 mit dem Tankvolumen 25 verbunden. Der dritte Abschnitt 73 ist dabei als Bohrung durch eine Wand des Gehäuses 7 ausgebildet.The second channel section 71 of the return flow channel opens at an end face 74 directed in the direction of the cylindrical extension 66. In the illustrated embodiment, a recess 75 is disposed in the end face 74 of the housing cover 53. The recess 75 lies in a radially inner region relative to the second sealing element 67 and may, in order to compensate for assembly inaccuracies, extend over a larger area of the end face 74. The cavity formed by the recess 75 is connected to the tank volume 25 via the third section 73. The third section 73 is formed as a bore through a wall of the housing 7.

In Fig. 2 ist ein Teil eines erfindungsgemäßen Elektromagneten 28 dargestellt. Das Polrohr 50 weist eine Ausnehmung 76 für den Anker 58 auf. Je nach Position des Ankers 58 in axialer Richtung bildet sich in dem Polrohr 50 ein Ankerraum 57 aus, wie dies in der Fig. 2 dargestellt ist, oder ein rückwärtiger Ankerraum 77 aus, dessen Volumen in der gezeigten Stellung des Ankers 58 minimal ist. In radialer Richtung wird der rückwärtige Ankerraum 77 durch das Polrohr 50 begrenzt. In axialer Richtung ist der rückwärtigen Ankerraum 77 einerseits durch den Anker 58 andererseits durch ein Verschlußstück 78 begrenzt, wobei das Verschlußsück 78 das Polrohr 50 an seiner von der Stirnfläche 55 abgewandten Seite verschließt. Das Verschlußsück 78 ist gegenüber der Innenwand des Polrohrs 50 mit einem weiteren Dichtelement 79 abdichtet.2, a part of an electromagnet 28 according to the invention is shown. The pole tube 50 has a recess 76 for the armature 58. Depending on the position of the armature 58 in the axial direction, an armature space 57 is formed in the pole tube 50, as shown in FIG. 2, or a rear armature space 77 whose volume in the illustrated position of the armature 58 is minimal. In the radial direction of the rear armature space 77 is limited by the pole tube 50. In the axial direction of the rear armature space 77 is bounded on the one hand by the armature 58 on the other hand by a closure member 78, wherein the closure piece 78 closes the pole tube 50 on its side remote from the end face 55 side. The closure piece 78 is sealed with respect to the inner wall of the pole tube 50 with a further sealing element 79.

Der Ankerraum 57 sowie der rückwärtige Ankerraum 77 sind über Ankerkanäle 59 bzw. 59' miteinander verbunden. Bei einer Bewegung des Ankers 58 kann somit das in dem rückwärtigen Ankerraum 77 befindliche Druckmittel in den Ankerraum 57 strömen und umgekehrt. In einem radial erweiterten Bereich 80 der Ausnehmung 76 ist ein Gleitlager 81 angeordnet, in dem der Anker 58 geführt ist. Ein zweites Gleitlager 82 ist in der Durchgangsbohrung 51 angeordnet. Das zweite Gleitlager 82 ist dabei an dem zu dem Ankerraum 57 hin orientierten Ende der Durchgangsbohrung 51 angeordnet und führt dort den Stößel 29, der mit dem Anker 58 verbunden ist.The armature space 57 and the rear armature space 77 are connected to each other via anchor channels 59 and 59 '. During a movement of the armature 58, the pressure medium located in the rear armature space 77 can thus flow into the armature space 57 and vice versa. In a radial extended portion 80 of the recess 76, a sliding bearing 81 is arranged, in which the armature 58 is guided. A second sliding bearing 82 is disposed in the through hole 51. The second sliding bearing 82 is arranged on the armature space 57 towards the oriented end of the through hole 51 and there carries the plunger 29 which is connected to the armature 58.

In dem dargestellten Ausführungsbeispiel ist die Durchgangsbohrung 51 über ihre gesamte Länge bis zu dem Ankerraum 57 mit konstanten Durchmesser ausgebildet. Um der Druckmittelleckage keinen zu hohen Strömungswiderstand entgegenzusetzen, ist der Spalt 68, der zwischen dem Stößel 29 und der Innenwand der Durchgangsbohrung 51 ausgebildet ist gegenüber der Durchgangsbohrung aus Fig. 1b vergrößert. Das Polrohr 50 weist eine Anlagefläche 83 auf, in welcher eine Nut 84 zur Aufnahme des ersten Dichtelements ausgebildet ist. Das zum Einsetzen in die Nut 84 vorgesehene Dichtelement lässt einen durchströmbaren Spalt offen, welcher einen Freistich 85 mit dem ersten Kanalabschnitt 71.1 verbindet. Zu dem Ausführungsbeispiel der Fig. 1b wurde bereits beschrieben, dass der Freistich 85 einem umlaufenden Kanal 70 im Bereich eines Auslaufs der Schraubverbindung 52 ausbildet.In the illustrated embodiment, the through hole 51 is formed over its entire length to the armature space 57 with a constant diameter. In order not to oppose the pressure medium leakage to high flow resistance, the gap 68 which is formed between the plunger 29 and the inner wall of the through hole 51 relative to the through hole of Fig. 1b is increased. The pole tube 50 has a contact surface 83, in which a groove 84 is formed for receiving the first sealing element. The intended for insertion into the groove 84 sealing element leaves a through-flow gap open, which connects an undercut 85 with the first channel portion 71.1. It has already been described for the embodiment of FIG. 1b that the undercut 85 forms a circumferential channel 70 in the region of an outlet of the screw connection 52.

Der erste Kanalabschnitt 71.1 verbindet den Ankerraum 57 mit der Anlagefläche 83 und ermöglicht damit den Rückfluss des über den Spalt 68 in den Ankerraum 57 einströmenden Druckmittels. Um zwischen dem Spalt 68 und dem Ankerraum 57 ebenfalls eine durchströmbare Verbindung zu schaffen, ist ein Überströmkanal 86 vorgesehen, der die Durchgangsbohrung 51 an ihrer dem Ankerraum 57 zugewandten Seite in radialer Richtung so erweitert, dass das Druckmittel an dem zweiten Gleitlager 82 vorbei in den Ankerraum 57 strömen kann.The first channel section 71.1 connects the armature space 57 with the contact surface 83 and thus allows the return flow of the pressure medium flowing into the armature space 57 via the gap 68. In order to create between the gap 68 and the armature space 57 also a flow-through connection, an overflow channel 86 is provided, which extends the through hole 51 at its the armature space 57 side facing in the radial direction so that the pressure medium past the second sliding bearing 82 in the Anchor space 57 can flow.

An der den Ankerraum 57 in Richtung der Stirnfläche 55 begrenzenden Fläche des Polrohrs 50 ist eine Antiklebescheibe 87 befestigt, welche das unerwünschte magnetische Kleben des Ankers 58 verhindert. Die Antiklebescheibe 87 ist hierzu aus nicht magnetischem Material gefertigt und in dem Ausführungsbeispiel der Fig. 2 an ihrem Innendurchmesser zentriert und mit der Fläche des Polrohrs 50 verklebt.At the armature space 57 in the direction of the end face 55 delimiting surface of the pole tube 50, a Antiklebescheibe 87 is attached, which is the undesirable Magnetic bonding of the armature 58 prevented. The Antiklebescheibe 87 is this made of non-magnetic material and centered in the embodiment of FIG. 2 at its inner diameter and bonded to the surface of the pole tube 50.

Der Strömungsweg des Druckmittels durch den Proportionalmagneten 28 führt über den Spalt 68, über den das Druckmittel, welches aufgrund des Speisedrucks an dem Führungsabschnitt 65 des Regelkolbens 6 vorbei geströmt ist, in den Elektromagneten 28 eingetreten ist. Aus dem Spalt 68 strömt das Druckmittel weiter über den Überströmkanal 86 bis in den Ankerraum 57. Um eine Verbindung von dem Überströmkanal 86 in den Ankerraum 57 zu ermöglichen, ist es beispielsweise möglich, entsprechende Ausnehmungen in der Antiklebescheibe 87 vorzusehen. Aus dem Ankerraum 57 strömt das Druckmittel entlang des ersten Kanalabschnitts 71.1 in Richtung des Tankvolumens 25 über den zweiten Kanalabschnitt 71 und den dritten Kanalabschnitt 73.The flow path of the pressure medium through the proportional magnet 28 leads via the gap 68, via which the pressure medium, which has flowed past the guide section 65 of the control piston 6 due to the feed pressure, has entered the electromagnet 28. From the gap 68, the pressure medium continues to flow via the overflow channel 86 into the armature space 57. In order to enable a connection from the overflow channel 86 into the armature space 57, it is possible, for example, to provide corresponding recesses in the antikink disk 87. From the armature space 57, the pressure medium flows along the first channel section 71.1 in the direction of the tank volume 25 via the second channel section 71 and the third channel section 73.

In der Fig. 3 ist ein Ausführungsbeispiel gezeigt, bei dem an Stelle des ersten Gleitlagers 81 sowie des zweiten Gleitlagers 82 Folienlager verwendet werden. Weiterhin ist an Stelle des Überströmkanals 86 der bereits zu Fig. 1b beschriebene radial erweiterte Bereich 56 der Durchgangsbohrung 51 ausgebildet. Der Strömungsweg des Druckmittels entspricht im wesentlichen dem zu der Fig. 2 beschriebenen Strömungsweg. Der Druckmittelleckagestrom führt durch den Ankerraum 57, so dass eine sehr effiziente Mitnahme von sich in dem Ankerraum 57 befindenden Luftbläschen erfolgt. Der Transport der Luftbläschen aus dem rückwärtigen Ankerraum 77 erfolgt durch die Bewegung des Ankers 58 bei Betätigen des Proportionalmagneten 28. Damit kann die Entlüftung, die wegen des kontinuierlichen Entlüftens während des Betriebs vollständig ist, bei der Inbetriebnahme des Proportionalmagneten 28 erfolgen. Eine zunächst durchzuführende Entlüftung mittels einer dann zusätzlich erforderlichen Entlüftungsschraube kann daher entfallen.In Fig. 3, an embodiment is shown in which instead of the first sliding bearing 81 and the second sliding bearing 82 film bearings are used. Furthermore, in place of the overflow channel 86 of the already described to Fig. 1b radially enlarged portion 56 of the through hole 51 is formed. The flow path of the pressure medium substantially corresponds to the flow path described in FIG. The pressure medium leakage current leads through the armature space 57, so that a very efficient entrainment of air bubbles located in the armature space 57 takes place. The transport of the air bubbles from the rear armature space 77 is effected by the movement of the armature 58 upon actuation of the proportional magnet 28. Thus, the vent, which is complete because of the continuous venting during operation, take place during commissioning of the proportional magnet 28. An initially performed by means of a vent then additionally required bleed screw can therefore be omitted.

In Fig. 4 ist ein weiteres Ausführungsbeispiel gezeigt, bei dem ein erster Kanalabschnitt 71.2 ausgebildet ist, welcher von dem Freistich 85 in den erweiterten Bereich 56 der Durchgangsbohrung 51 führt. Das Ausmünden des ersten Kanalabschnitts 71.2 in den erweiterten Bereich 56 der Durchgangsbohrung 51 hat den Vorteil, dass der Druckmittelleckagestrom nicht durch den Ankerraum 57 führt. Damit wird durch das durch den Elektromagneten 28 strömende Druckmittel keine Verschmutzung in den Bereich des Ankers 58 transportiert. Durch die kurze Anbindung über den erweiterten Bereich 56 wird somit eine Erhöhung der Lebensdauer des Proportionalmagneten 28 erreicht.FIG. 4 shows a further exemplary embodiment in which a first channel section 71.2 is formed which leads from the undercut 85 into the widened region 56 of the through-hole 51. The outflow of the first channel portion 71.2 in the extended area 56 of the through hole 51 has the advantage that the pressure medium leakage current does not pass through the armature space 57. Thus, no pollution is transported into the region of the armature 58 by the pressure medium flowing through the electromagnet 28. Due to the short connection via the widened region 56, an increase in the service life of the proportional magnet 28 is thus achieved.

Die Ausführungsbeispiele der Figuren 5 bis 7 entsprechen im wesentlichen den Ausführungsbeispielen der Figuren 2 bis 4. Im Unterschied hierzu wird jedoch eine Antiklebescheibe 87' verwendet, welche an ihrem äußeren Umfang zentriert wird. Die Antiklebescheibe 87' weist wie auch die Antiklebescheibe 87 aus den Ausführungsbeispielen der Figuren 2 bis 4 eine zentrale Ausnehmung auf, welche hierbei jedoch in ihrer radialen Ausdehnung so groß bemessen ist, dass der erste Kanalabschnitt 71.1 über die zentrale Ausnehmung mit dem Ankerraum 57 verbunden ist.The embodiments of Figures 5 to 7 substantially correspond to the embodiments of Figures 2 to 4. In contrast, however, a Antiklebeeibe 87 'is used, which is centered at its outer periphery. The Antiklebescheibe 87 'has as well as the Antiklebescheibe 87 from the embodiments of Figures 2 to 4 on a central recess, which, however, is dimensioned in its radial extent so large that the first channel portion 71.1 is connected via the central recess with the armature space 57 ,

Die vorgeschlagene Entlüftung ist nicht auf einen Einsatz in einem Proportionalmagneten, wie er in den Ausführungsbeispielen verwendet ist, beschränkt, sondern kann auch bei Schaltmagneten oder Stoßmagneten eingesetzt wreden. Der Rückflusskanal kann außerdem auch mit dem rückwärtigen Ankerraum 77 verbunden sein.The proposed venting is not limited to use in a proportional solenoid as used in the embodiments, but can also be used with solenoids or pushers. The return flow channel can also be connected to the rear armature space 77.

Claims (5)

  1. Electromagnet for actuating a valve, the electromagnet (28) comprising an armature (58) which can be axially displaced in an armature space (57, 77) and of which the axial motion displaces a tappet (29) to the valve and a reflux channel (69, 71, 73) connected to the armature space (57, 77) being provided, via which the armature space (57, 77) is connected to a tank volume (25) for removing a pressure medium leakage flow that is flowing out of the valve into the armature space (57, 77),
    characterised in that
    at least one first channel portion (69) of the reflux channel (96, 71, 73) is arranged in a pole tube (50) and in that
    a second channel portion (71) of the reflux channel is provided in a housing cover (53) and which discharges from the housing cover (53) on a surface provided for abutment against a valve housing (7).
  2. Electromagnet according to claim 1,
    characterised in that
    the reflux channel (69, 71, 73) discharges in a radially expanded portion (56) of a through passage (51) connected to the armature space (57, 77).
  3. Electromagnet according to claim 1,
    characterised in that
    the reflux channel (69, 71, 73) discharges directly into the armature space (57, 77).
  4. Electromagnet according to any one of claims 1 to 3,
    characterised in that
    a rear armature space (77) constructed on the side of the armature (58) facing away from the tappet (29) is connected to the armature space (57) by means of at least one armature channel (59).'
  5. Electromagnet according to any one of claims 1 to 4,
    characterised in that
    the tank volume connected to the armature space (57, 77) via the reflux channel (69, 71, 73) is a tank volume (25) constructed in the valve.
EP03789234A 2002-12-18 2003-12-11 Electromagnet Expired - Fee Related EP1573212B1 (en)

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DE10259314A DE10259314B4 (en) 2002-12-18 2002-12-18 electromagnet
PCT/EP2003/014098 WO2004055392A1 (en) 2002-12-18 2003-12-11 Electromagnet

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DE50303406D1 (en) 2006-06-22
US7131630B2 (en) 2006-11-07
US20060158289A1 (en) 2006-07-20
WO2004055392A1 (en) 2004-07-01
DE10259314B4 (en) 2012-11-29
EP1573212A1 (en) 2005-09-14

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