EP1573212B1 - Electroaimant - Google Patents

Electroaimant 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 - Lifetime
Application number
EP03789234A
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German (de)
English (en)
Other versions
EP1573212A1 (fr
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
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
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Publication of EP1573212A1 publication Critical patent/EP1573212A1/fr
Application granted granted Critical
Publication of EP1573212B1 publication Critical patent/EP1573212B1/fr
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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (5)

  1. Electroaimant pour actionner un clapet, l'électroaimant (28) comprenant un induit mobile axialement dans un espace d'induit (57, 77), dont le mouvement axial transmet un poussoir (29) sur le clapet, et un canal de reflux (69, 71, 73) relié à l'espace d'induit (57, 77) étant prévu, sur lequel l'espace d'induit (57, 77) est relié à un volume tampon (25) pour répartir un flux de fuite de milieu de pression circulant du clapet vers l'espace d'induit (57, 77),
    caractérisé en ce qu'au moins une première section de canal (69) du canal de reflux (69, 71, 73) est positionnée dans un tube central (50) et que dans un couvercle de boîtier (53), une deuxième section de canal (71) du canal de reflux est prévue, laquelle débouche du couvercle de boîtier (53) dans une surface prévue pour reposer sur un boîtier de clapet (7).
  2. Electroaimant selon la revendication 1,
    caractérisé en ce que le canal de reflux (69, 71, 73) débouche dans une section élargie radialement (56) d'un perçage traversant (51) relié à l'espace d'induit (57, 77).
  3. Electroaimant selon la revendication 1,
    caractérisé en ce que le canal de reflux (69, 71, 73) débouche directement dans l'espace d'induit (57, 77).
  4. Electroaimant selon l'une des revendications 1 à 3,
    caractérisé en ce qu'un espace d'induit (77) arrière formé sur le côté de l'induit (58) opposé au poussoir (29) est relié à l'espace d'induit (57) au moyen d'au moins un canal d'induit (59).
  5. Electroaimant selon l'une des revendications 1 à 4,
    caractérisé en ce que le volume tampon relié à l'espace d'induit (57, 77) sur le canal de reflux (69, 71, 73) est un volume tampon (25) formé dans le clapet.
EP03789234A 2002-12-18 2003-12-11 Electroaimant Expired - Lifetime EP1573212B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10259314A DE10259314B4 (de) 2002-12-18 2002-12-18 Elektromagnet
DE10259314 2002-12-18
PCT/EP2003/014098 WO2004055392A1 (fr) 2002-12-18 2003-12-11 Electroaimant

Publications (2)

Publication Number Publication Date
EP1573212A1 EP1573212A1 (fr) 2005-09-14
EP1573212B1 true EP1573212B1 (fr) 2006-05-17

Family

ID=32519083

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03789234A Expired - Lifetime EP1573212B1 (fr) 2002-12-18 2003-12-11 Electroaimant

Country Status (4)

Country Link
US (1) US7131630B2 (fr)
EP (1) EP1573212B1 (fr)
DE (2) DE10259314B4 (fr)
WO (1) WO2004055392A1 (fr)

Cited By (1)

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DE102022206789A1 (de) 2022-07-04 2024-01-04 Robert Bosch Gesellschaft mit beschränkter Haftung Stellventil

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EP2138720A3 (fr) 2008-06-24 2010-01-20 MALI Holding AG Dispositif de réglage pour le réglage de machines à pistons axiaux.
JP5822141B2 (ja) * 2012-03-29 2015-11-24 Ｋｙｂ株式会社 サーボレギュレータ
DE102016010171A1 (de) * 2016-08-17 2018-02-22 Alpha Fluid Hydrauliksysteme Müller GmbH Elektroproportionales Mehrstufenventil
DE102022204198A1 (de) 2022-04-29 2023-11-02 Zf Friedrichshafen Ag Befüllen eines Ankerraums eines Aktors

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DE102022206789A1 (de) 2022-07-04 2024-01-04 Robert Bosch Gesellschaft mit beschränkter Haftung Stellventil

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EP1573212A1 (fr) 2005-09-14
DE10259314B4 (de) 2012-11-29
DE10259314A1 (de) 2004-07-15
WO2004055392A1 (fr) 2004-07-01
US20060158289A1 (en) 2006-07-20
DE50303406D1 (de) 2006-06-22

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