EP1573212A1 - Electroaimant - Google Patents

Electroaimant

Info

Publication number
EP1573212A1
EP1573212A1 EP03789234A EP03789234A EP1573212A1 EP 1573212 A1 EP1573212 A1 EP 1573212A1 EP 03789234 A EP03789234 A EP 03789234A EP 03789234 A EP03789234 A EP 03789234A EP 1573212 A1 EP1573212 A1 EP 1573212A1
Authority
EP
European Patent Office
Prior art keywords
armature
electromagnet
armature space
valve
space
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.)
Granted
Application number
EP03789234A
Other languages
German (de)
English (en)
Other versions
EP1573212B1 (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
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
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
Expired - Fee Related legal-status Critical Current

Links

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 actuate valves in hydraulic systems. Such an electromagnet for actuating a valve is, for. B. from DE 37 09 474 Cl known.
  • the electromagnet actuates a valve closing body, which interacts with a sealing seat depending on the stroke of the valve closing body to form 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 anchor is in one axial direction
  • Armature space movable and is held in a defined starting position by an axially acting spring on the armature.
  • the cavities formed in the interior of the electromagnet are during the operation of the
  • the armature space or the pole tube delimiting the armature space in the axial direction is surrounded in the radial direction on the outside by a coil which, when energized, generates a magnetic field which the armature in
  • the volume of the rear anchor space is reduced and the pressure medium inside is displaced.
  • the axial movement of the armature creates a volume on the opposite side of the armature, into which the displaced pressure medium flows.
  • the displaced pressure medium flows along the radially outer circumference of the armature, this annular gap being connected to the environment via a vent valve device. is.
  • the air in the armature space must be removed from the armature space when the electromagnet is started up.
  • a vent valve device is provided in the electromagnet described in DE 37 09 474 C1, which connects the annular gap around the armature to the surroundings of the electromagnet via a transverse bore.
  • the vent valve device is constructed similarly to a shuttle valve.
  • the closing body arranged in the vent valve has a lower specific
  • the closing body then floats on the pressure medium and is pressed against the outward-facing sealing seat, as a result of which the vent valve is closed.
  • the venting described has the disadvantage that the valve is closed by the pressure medium when it is filled.
  • the emptied armature space is refilled with the pressure medium, it is inevitable that residues of trapped air remain in the rear armature space in the relatively viscous pressure medium.
  • This air inclusion worsens the damping behavior and makes it difficult to adjust the damping, since different movements of the air can occur due to the movement of the armature.
  • the trapped air is only pushed back and forth when the armature moves, but can no longer escape from the armature space, since the vent valve remains closed.
  • Another disadvantage is that the function of the valve depends on the installation position of the electromagnet.
  • a hydraulic valve equipped with the described ventilation valve therefore has a predefined installation position.
  • vent hole is closed by the pressure medium, which is usually an oil. If the pressure medium partially escapes from the anchor space, e.g. during a subsequent long period of inactivity, the closing body may stick together, which means that the function can no longer be guaranteed if it is started up again.
  • the pressure medium which is usually an oil.
  • the electromagnet according to the invention has the advantage that a return flow channel is connected to the armature space, via which the leakage fluid entering the armature space flows into a tank volume. In this way, a small but continuously occurring leakage current is achieved during the operation of the electromagnet.
  • This leakage flow on the one hand creates a slight negative pressure in the armature space, on the other hand air bubbles which have been transported into the area of the flow due to the movement of the armature can be discharged together with the leakage flow via the return flow channel.
  • the return flow channel is open at all times during the operation of the electromagnet, so that the fluid leakage flow is maintained even when the electromagnet is approximately completely filled with the pressure medium remains.
  • air inclusions which may still be present in the rear armature space even when the pressure medium is almost completely filled, to be removed from the inside of the electromagnet.
  • the air inclusions are then moved by the movement of the armature in the area in which the flow occurs due to the pressure medium leakage.
  • the movement of the enclosed air is on the one hand caused by that generated by the flow. Vacuum and on the other hand favored by the turbulence caused by the current.
  • the return flow channel opens directly into the armature space, since this results in a particularly effective ventilation.
  • the pressure medium displaced from the rear armature space by the movement of the armature thus transports the air bubbles contained in the rear armature space into the immediate vicinity of the leakage flow. This makes it particularly easy to take the air bubbles with you through the leakage flow and results in quick ventilation.
  • Another advantageous embodiment results from the fact that the return flow channel is arranged in an enlarged area of the pole tube.
  • the leakage flow is not conducted through the armature space, which reduces the risk that dirt particles, which may be contained in the leakage flow, are transported to the armature.
  • contamination which is located in the area of the armature, has a disadvantageous effect on the service life of the electromagnet.
  • a higher flow velocity of the leakage flow is formed when the outlet in the pole tube due to the smaller flow cross-sections, which in turn improves the escape of the enclosed air bubbles.
  • the return flow channel in the electromagnet is designed in such a way that there is a direct connection possibility to the tank volume located in the actuated valve unit.
  • the return flow channel is located in a pole tube, which also takes over the guiding of the tappet acting on the valve to be actuated.
  • La is a schematic sectional view of a valve unit actuated with an electromagnet according to the invention.
  • FIG. 1b shows an enlarged illustration of a detail from FIG.
  • FIG. 2 shows a sectional partial illustration of a first exemplary embodiment of an electromagnet according to the invention
  • Fig. 3 is a partial sectional view of a second embodiment of an inventive
  • FIG. 4 shows a sectional partial illustration of a third exemplary embodiment of an electromagnet according to the invention
  • FIG. 5 is a partial sectional view of a fourth embodiment of an electromagnet according to the invention
  • Fig. 6 is a partial sectional view of a fifth
  • Electromagnets and
  • Fig. 7 is a partial sectional view of a sixth
  • FIG. 1 a shows a first example of an adjusting device 1 with a valve actuated by the electromagnet according to the invention.
  • an actuating piston 2 in an actuating pressure chamber 3 and a second actuating pressure chamber 4 is acted upon by an actuating 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, to which a resulting force acts when there is a pressure difference.
  • a control pressure control valve 5 is provided for adjusting the pressure difference in the two control pressure chambers 3 and 4.
  • the steep 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 made in the housing 7. The first feed pressure bore 8 and the second feed pressure bore 9 are connected to a feed pressure line 14, which can be connected, for example, to an auxiliary pressure source.
  • the feed pressure line 14 or the first feed pressure bore 8 or the second feed pressure bore 9 can be connected to a first signal pressure line 12 or a second signal pressure line 13.
  • the first signal pressure line 12 is on a first signal pressure channel 10 connected, which opens on the part of the control piston 6 in a first groove 15.
  • the second signal pressure line 13 is connected to a second groove 16 via a second signal pressure channel 11.
  • the control piston 6 has a first control piston section 17 or a second control piston section 18.
  • the two control piston sections 17 and 18 have a first steep pressure control edge 19 and a second signal pressure control edge 20, which are arranged at the opposite oriented ends of the respective control piston section 17 and 18.
  • the first signal pressure channel 10 is thus connected via the first groove 15 to a first feed pressure groove 21, and thus the first signal pressure chamber 3 is pressurized with the pressure from the feed pressure line 14.
  • the second actuating pressure channel 11 is connected via the second groove 16 to 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 of the first control piston section 17 facing away from the first signal pressure control edge 19.
  • a second relaxation control edge 24 is also arranged on the second control piston section 18.
  • the respective actuating pressure chamber 3 or 4 is expanded into a tank volume 25 via the first relief 15 and the second groove 16 via the two expansion control edges 23 and 24.
  • the rear control piston chamber 27 is also connected to the tank volume 25 via a volume compensation channel 26. The slight volume fluctuations that arise in the rear control piston chamber 27 due to an axial movement of the control piston 6 are thus compensated.
  • part of the control piston leakage is discharged into the tank volume 25 via the volume compensation channel 26.
  • a proportional magnet 28 is provided, which is arranged on the housing 7 of the control valve 5.
  • the proportional magnet 28 has a plunger 29, the plunger 29 acting on an end face 30 of the control piston 6.
  • a control force can thus be transmitted to the control piston 6 in the axial direction, which is generated by the proportional magnet 28 as a function of a control signal which is supplied to the proportional magnet 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.
  • the axial movement of the control piston 6 on the first signal pressure control edge 19 creates a flow-through gap.
  • the pressure medium supplied via the feed pressure line 14 and the first feed pressure bore 8 can reach the first signal pressure chamber 3 via the first signal pressure channel 10.
  • the pressure thus increased in the first actuating pressure chamber 3 effects 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 relief control edge 24 is opened in the second control piston section 18.
  • the second signal pressure chamber 4 is expanded into the tank volume 25 via the second signal pressure line 13 and the second signal pressure channel 11.
  • a driver recess 33 is provided in the actuating piston 2, in which a driver head 32 is arranged, which is connected to the actuating lever 31.
  • the actuating lever 31 is rotatably mounted on a bearing pin 34, so that the actuating movement of the actuating piston 2 leads to a rotation of the actuating lever 31.
  • a first leg 35 and a second leg 36 are also rotatably mounted on the bearing pin 34.
  • the first leg 35 and the second leg 36 are connected to one another via a tension spring 37, so that a deflection of one of the two legs relative to the other leads to a tension the tension spring 37 leads.
  • a driving pin 38 is arranged on the end of the adjusting lever 31 opposite the driving head 32 of the adjusting lever 31.
  • the driving pin 38 moves in the opposite direction to the actuating piston movement.
  • the driving pin 38 bears against the second leg 36, so that the second leg 36 is deflected relative to the first leg 35 by the rotary movement of the actuating lever 31 and the spring 37 is tensioned.
  • the adjusting device 1 shown in FIG. 1 a 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 by a through hole 51 along its longitudinal axis.
  • the diameter of the through hole 51 is dimensioned such 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 is arranged in a groove of the pole tube 50 provided for this purpose.
  • the plunger 29 projects slightly beyond the end face 55 of the pole tube 50 and bears against the end face 30 of the control piston 6.
  • the through-bore 51 On 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 in the exemplary embodiment shown as a recess in the pole tube 50 is connected.
  • An armature 58 is arranged in the armature space 57 and is operatively connected to the plunger 29.
  • Armature channels 59 are formed in the armature 58 parallel to its longitudinal axis and connect the two end faces of the armature 58 facing away from one another.
  • the armature 58 By energizing the coil elements of the electromagnet, not shown, the armature 58 is subjected to a force in the axial direction by the resulting magnetic field, which displaces it in such a way that the volume of the armature space 57 is reduced. Since the armature 58 is operatively connected to 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 switched off, there is no longer any force acting on the armature 58 and it is shifted to the right in the arrangement shown in FIG. 1b via the counterforce transmitted from the control piston 6 to the plunger 29. Between the armature space 57 and the rear armature space, not shown in FIG. 1b, there is a connection via the armature channels 59, so that volume equalization takes place between the armature around 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 in such a way that the control piston 6 driven back by the counterforce strikes it with a stop surface 64 and experiences a defined braking force there.
  • the stop surface 64 is formed on a guide section 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 with respect to the housing 7.
  • a pressure medium leakage is formed between the guide section 65 of the control piston 6 and the housing 7, as a result of which pressure medium flows out of the feed pressure bore 8 past the guide section 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-bore 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 enlarged area 56 of the through bore 51 to a circumferential channel 70.
  • the circumferential channel can, for example, be designed as an undercut in the outlet area of the screw connection 52.
  • the pressure medium flowing back 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 out on an end face 74 directed in the direction of the cylindrical extension 66.
  • a recess 75 is arranged in the end face 74 of the housing cover 53.
  • the recess 75 lies in a radially inner area relative to the second sealing element 67 and can extend over a larger area of the end face 74 in order to compensate for mounting inaccuracies.
  • the cavity formed by the recess 75 is connected to the tank volume 25 via the third section 73.
  • the third section 73 is designed 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, the volume of which is minimal in the position of the armature 58 shown.
  • the rear armature space 77 is delimited by the pole tube 50.
  • the rear armature space 77 is on the one hand through the armature 58 and on the other hand through a closure piece
  • closure back 78 closes the pole tube 50 on its side facing away from the end face 55.
  • the closure back 78 is opposite the inner wall of the pole tube 50 with a further sealing element
  • the armature space 57 and the rear armature space 77 are connected to one another via armature channels 59 and 59 '.
  • the pressure medium located in the rear armature space 77 can flow into the armature space 57 and vice versa.
  • a slide bearing 81 is arranged, in which the armature 58 is guided.
  • a second slide bearing 82 is arranged in the through hole 51. The second slide bearing 82 is arranged at the end of the through hole 51 oriented toward the armature space 57 and there guides the plunger 29, which is connected to the armature 58.
  • the through hole 51 is formed over its entire length up to the armature space 57 with a constant diameter.
  • the gap 68 which is formed between the tappet 29 and the inner wall of the through-bore 51, is enlarged compared to the through-bore from FIG. 1b.
  • the pole tube 50 has a contact surface 83, in which a groove 84 is formed for receiving the first sealing element.
  • the sealing element provided for insertion into the groove 84 leaves open a gap through which a recess 85 connects the first channel section 71.1.
  • 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 to the contact surface 83 and thus enables the backflow of the pressure medium flowing into the armature space 57 via the gap 68.
  • an overflow channel 86 is provided, which extends the through bore 51 on its side facing the armature space 57 in the radial direction in such a way that the pressure medium passes the second slide bearing 82 into the Anchor room 57 can flow.
  • an anti-adhesive disc 87 is attached, which prevents the undesired prevents magnetic sticking of the armature 58.
  • the anti-adhesive disc 87 is made of non-magnetic material and, in the exemplary embodiment of FIG. 2, is centered on its inner diameter and glued 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. 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 anti-adhesive disc 87.
  • the pressure medium flows out of the armature space 57 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 shows an embodiment in which foil bearings are used instead of the first slide bearing 81 and the second slide bearing 82. Furthermore, instead of the overflow channel 86, the radially widened region 56 of the through-bore 51, which has already been described for FIG.
  • the flow path of the pressure medium essentially corresponds to the flow path described for FIG. 2.
  • the pressure medium leakage flow leads through the armature space 57, so that air bubbles located in the armature space 57 are carried very efficiently.
  • the air bubbles are transported out of the rear armature space 77 by the movement of the armature 58 when the proportional magnet 28 is actuated.
  • the venting which is complete because of the continuous venting during operation, can take place when the proportional magnet 28 is started up.
  • a ventilation to be carried out first by means of a then any additional vent screw required 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 enlarged area 56 of the through hole 51.
  • the opening of the first channel section 71.2 into the enlarged area 56 of the through bore 51 has the advantage that the pressure medium leakage flow does not lead through the armature space 57. No pollution is thus transported into the area of the armature 58 by the pressure medium flowing through the electromagnet 28.
  • the short connection via the extended area 56 thus increases the service life of the proportional magnet 28.
  • FIGS. 5 to 7 essentially correspond to the exemplary embodiments in FIGS. 2 to 4.
  • an anti-adhesive disc 87 ' is used, which is centered on its outer circumference.
  • the anti-adhesive washer 87 ' like the anti-adhesive washer 87 from the exemplary embodiments in FIGS. 2 to 4, has a central recess which, however, is dimensioned so large in its radial extent that the first channel section 71.1 is connected to the anchor space 57 via the central recess ,
  • the proposed venting is not limited to use in a proportional magnet, as used in the exemplary embodiments, but can also be used with switching magnets or shock magnets.
  • the return flow channel can also be connected to the rear anchor space 77.

Landscapes

  • 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)

Abstract

L'invention concerne un électroaimant permettant d'actionner une soupape, ledit électroaimant (28) comprenant un induit (58) qui peut être déplacé dans le sens axial dans un espace d'induit (57, 77) et dont le mouvement axial déplace un coulisseau (29) sur la soupape. Il est prévu dans l'électroaimant un canal de reflux (71,1) relié à l'espace d'induit (57, 77), par l'intermédiaire duquel l'espace d'induit (57, 77) est raccordé à un volume de réservoir (25) pour évacuer un courant de fuite de milieu de pression s'écoulant hors de la soupape dans l'espace d'induit (57, 77).
EP03789234A 2002-12-18 2003-12-11 Electroaimant Expired - Fee Related 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 true EP1573212A1 (fr) 2005-09-14
EP1573212B1 EP1573212B1 (fr) 2006-05-17

Family

ID=32519083

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03789234A Expired - Fee Related 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)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102022206789A1 (de) 2022-07-04 2024-01-04 Robert Bosch Gesellschaft mit beschränkter Haftung Stellventil

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3709474C1 (en) * 1987-03-23 1988-03-31 Bosch Gmbh Robert Solenoid valve
JPH01266377A (ja) * 1988-04-18 1989-10-24 Diesel Kiki Co Ltd 電磁アクチュエータ
US5208570A (en) * 1992-04-06 1993-05-04 Caterpillar Inc. Solenoid construction and method for making same
DE4417587B4 (de) * 1994-05-19 2005-04-21 Linde Ag Regelmagnet für elektro-hydraulisch gesteuerte Anlagen
US6021813A (en) * 1995-09-26 2000-02-08 Mannesmann Rexroth Ag Electromagnetically actuated directional valve
US5788213A (en) * 1996-11-20 1998-08-04 Lectron Products, Inc. Electrically operated pressure control valve
DE19717807B4 (de) * 1997-04-26 2005-10-27 Bosch Rexroth Ag Von mindestens einem Elektromagneten betätigbares Wegeventil
US5986530A (en) * 1998-01-13 1999-11-16 Caterpillar Inc. Solenoid and method for manufacturing
JP2001065514A (ja) * 1999-08-31 2001-03-16 Sumitomo Electric Ind Ltd 比例圧力制御弁

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004055392A1 *

Also Published As

Publication number Publication date
WO2004055392A1 (fr) 2004-07-01
EP1573212B1 (fr) 2006-05-17
DE10259314B4 (de) 2012-11-29
DE50303406D1 (de) 2006-06-22
DE10259314A1 (de) 2004-07-15
US20060158289A1 (en) 2006-07-20
US7131630B2 (en) 2006-11-07

Similar Documents

Publication Publication Date Title
DE3802648C2 (fr)
DE60129285T2 (de) Elektromagnetisches Sitzventil
DE19907732B4 (de) Hydraulisches Magnetventil
EP1851098B1 (fr) Cylindre de frein a accumulateur a ressort et de service combine avec dispositif de respiration
EP0126291B1 (fr) Soupape commandée par un fluide sous pression
DE102004029106B4 (de) Dreiwege-Proportionalelektromagnetventil des Entlastungstyps
DE1242945B (de) Elektromagnetisch regelbarer hydraulischer Stossdaempfer
DE19700405A1 (de) Magnetventil
DE9402206U1 (de) Elektroproportionalmagnet-Ventileinheit
EP1573212B1 (fr) Electroaimant
EP2690327B1 (fr) Distributeur hydraulique
DE10145200B4 (de) Türschließer
DE102005051379B4 (de) Sanitäres Umstellventil
DE102008004531B3 (de) Elektromagnetischer Antrieb
DE2330943B2 (de) Elektromagnetisch betätigbarer Hydraulikschalter
EP0278333B1 (fr) Dispositif de commande pour un séparateur de tuyau
EP0182053B1 (fr) Vanne de régulation de pression électromagnétiquement commandée
DE69401196T2 (de) Abblasventil für ein dampfgefäss
DE2113602A1 (de) Absperrorgan mit druckentlastetem Verschlussorgan
DE2915505C2 (fr)
EP1703185A1 (fr) Soupape coaxiale
WO2004092591A1 (fr) Soupape de distribution a variation continue
DE102009051574A1 (de) Magnetventil
WO2017162372A1 (fr) Frein de rotor intégré
EP1331393B1 (fr) Pompe solénoide à transmission hydraulique

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050504

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT SE

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20060517

REF Corresponds to:

Ref document number: 50303406

Country of ref document: DE

Date of ref document: 20060622

Kind code of ref document: P

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20070220

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20071213

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20071218

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20071217

Year of fee payment: 5

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20081211

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20090831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081212

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20121219

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20130225

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50303406

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50303406

Country of ref document: DE

Effective date: 20140701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140701

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20131211