WO2000050794A1 - Magnetventil - Google Patents
Magnetventil Download PDFInfo
- Publication number
- WO2000050794A1 WO2000050794A1 PCT/EP2000/001013 EP0001013W WO0050794A1 WO 2000050794 A1 WO2000050794 A1 WO 2000050794A1 EP 0001013 W EP0001013 W EP 0001013W WO 0050794 A1 WO0050794 A1 WO 0050794A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- armature
- actuating magnet
- magnet according
- bore
- tappet
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0655—Lift valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0644—One-way valve
- F16K31/0651—One-way valve the fluid passing through the solenoid coil
Definitions
- the invention relates to a proportional actuating magnet, in particular for a hydraulic valve.
- the known actuating magnets have a pole with a valve cone receiving bore for receiving a valve cone and an essentially cylindrical pole tube with a pole tube bore for receiving an essentially cylindrical armature.
- an air gap of approximately 0.1 mm to 0.4 mm is provided between the armature and the pole tube bore, or on the side of the armature plunger, the armature space is open to the outside environment, so that the hydraulic fluid is throttled into the armature space without throttling. and can flow out. Air and dirt can get into the armature space unhindered and interfere with the function of the proportional actuating magnet.
- Vent screws have not proven to be suitable for venting, since a large number of vent screws would have to be provided in order to always ensure venting from the highest point in the magnet interior when the hydraulic solenoid valve is installed in different positions.
- Air bubbles present in the interior of the proportional actuating magnet are particularly disadvantageous since they reduce the compression modulus of the pressure fluid and thus considerably reduce the damping of the movement of the armature.
- the solenoid valve easily vibrates can be excited, which cause malfunctions in the operation of the hydraulic solenoid valve.
- dirt can get stuck in the armature bearing in the armature space and thus lead to failure of the actuating magnet.
- the invention is therefore based on the object of providing a hydraulic solenoid valve and a proportional actuating magnet, in particular for a hydraulic solenoid valve, with which reliable operation is always possible.
- an armature tappet is provided between the armature and valve cone, which has a smaller diameter than the armature and valve cone. Furthermore, in the area between the valve cone receiving bore and the pole tube around the armature tappet, a stowage area with a tappet passage opening is provided, an annular gap having a predetermined gap width being formed between the inside of the tappet passage opening and the outside of the armature tappet running in the tappet passage opening around the circumference of the tappet passage opening .
- the invention accordingly provides for the hydraulic fluid between the armature space and the external environment to flow in and out throttled on the side of the armature plunger, so that a back pressure builds up in the armature space on the side of the armature plunger, which dampens the movement of the armature.
- the inventive design of the area between the valve cone receiving bore and the pole tube always ensures good damping of the movement of the armature.
- the hydraulic fluid that flows into or out of the pole tube by a movement of the armature in the pole tube must be the Step through the annular gap, where it is subject to the influence of friction. This creates a resistance to the flow, which dampens the movement of the armature.
- the entry of dirt and air into the pole tube is effectively prevented by the design with the annular gap around the armature tappet.
- a particularly advantageous solenoid valve with a proportional actuating magnet results when the diameter of the armature plunger is chosen to be particularly small. On the one hand, this results in a low oil exchange between the pole tube and the valve cone receiving bore when the armature moves. On the other hand, with the same gap width, the annular gap area decreases proportionally with the diameter of the armature plunger. A small annular gap area increases the damping effect on the armature and reduces the risk of air and / or dirt entering the pole tube. In addition, the low oil exchange between the pole tube and valve cone receiving bore counteracts the entry of air and / or dirt into the pole tube.
- the armature plunger should advantageously not rub in the stowage area in order not to increase any hysteresis of the actuating magnet.
- the annular gap is reduced even further, for example to smaller dimensions than 0.1 mm. It is particularly advantageous to carry out the mounting of the armature so that only a small axial play occurs. When the armature is supported in this way, the gap width can namely be reduced even further without the armature tappet rubbing in the stowage area due to the axial displacements of the armature, which would increase the hysteresis of the actuating magnet.
- the gap width should be designed so that there is a noticeable damping of the movement of the armature when the armature moves due to the throttling of the hydraulic oil in the annular gap.
- the interior of the pole tube is also automatically vented, so that vent screws can be saved.
- the storage area is advantageously designed as a substantially circular disk-shaped baffle plate in which the tappet passage opening is arranged in the center. This results in a particularly simple manufacture and assembly of the actuating magnet according to the invention.
- a foil bearing is provided in the area between the outer surface area of the armature and the pole tube bore, which can also essentially completely fill the space between the outer surface of the armature and the pole tube bore. This results in a design of the interior of the pole tube in such a way that air pockets can only form with difficulty because the long, narrow gap between the pole tube and anchor is avoided by the foil bearing.
- the pole tube can have a closure cover on its side facing away from the valve cone receiving bore, which cover can contain various assemblies. So it is conceivable to use an adjusting device for the closure cover Setting the working point of the armature. This can be done, for example, by providing an adjusting screw in the cover.
- the closure lid can also have a restoring device for loading the armature with a restoring force.
- a reset device has proven itself, which in particular can also protrude into the armature.
- the space occupied by the resetting device is always flowed through by hydraulic fluid which, when the armature moves, moves within compensation holes provided in the armature. This effectively counteracts the formation and accumulation of air bubbles in the pole tube.
- the restoring device exerts a restoring force on the armature and can be designed such that in the armature movement direction, when the cone tip moves towards the valve seat, part of the magnetic force is stored in two pressure springs connected in series.
- an armature return spring is preloaded slightly and the preload force is limited by a stop.
- a vibration damping spring is pre-tensioned until the cone tip rests in the valve seat. The spring rate of the vibration damping spring is high. This feather will be few
- the armature can have a spring space extending in the axial direction of the armature, from the bottom of which bore at least one compensating bore to one End face of the anchor runs. This ensures thorough flushing of the armature with hydraulic fluid, which counteracts the formation of air bubbles.
- the invention is also implemented in a hydraulic solenoid valve which has a proportional actuating magnet designed according to the invention.
- FIG. 1 shows a cross section through a proportional actuating magnet according to the invention and FIG. 2 shows a cross section through a partial area of the actuating magnet from FIG. 1.
- Figure 1 shows a proportional actuating magnet 1 according to the invention in cross section.
- the actuating magnet 1 is essentially divided into an actuating coil 2 and a pole 3, on which the actuating coil 2 is placed and fastened with a plastic nut 4.
- the actuating coil 3 has a coil housing 5, which essentially has the shape of a pot.
- an annular disk 6 is inserted, which has a passage opening 7 in which the pole 3 is arranged.
- the coil housing is formed into a housing base 8, in which a bottom opening 9 is provided, which ends with the outside of the pole 3.
- a magnet coil 10 is arranged, which has a plurality of coil turns provided on a coil carrier 11, which are connected to two connecting lugs 12 provided on the outside of the coil housing 5.
- Solenoid 10 occupied volume inside the coil housing 5 is filled with a potting compound 13.
- the pole 3 is divided into a valve cone region 14 on the left in FIG. 1, which is followed by a pole tube 15 on the right in FIG. 1.
- a cone area 16 is provided, which is designed as an anti-magnetic material area which is connected in one piece with the valve cone area 14 and the pole tube 15.
- the transition region between the pole tube 15, the cone region 16 and the valve cone region 14 is shaped such that a force is generated on the valve cone 20 by the actuating magnet 1, which force is proportional to the current applied.
- the valve cone area 14 is provided with an axially extending and continuous valve cone bore 17.
- a valve seat 18 is inserted, in which an inlet nozzle 19 is arranged.
- a valve plug 20 inserted into the valve plug bore 17 projects with a plug tip 21 into the seat bore 22 of the valve seat 18 and forms a throttle gap with the valve seat edge 22a.
- the actuating magnet works as a direct operated proportional pressure relief valve and regulates the pressure in the inflow P.
- hydraulic fluid can flow from the inflow P into the seat bore 22 and the throttle gap at the valve seat edge 22a into the valve cone bore 17 and flow out of it again via tank connection openings 23 provided radially in the valve cone region 14.
- valve cone 20 In addition to the cone tip 21, the valve cone 20 also has two essentially cylindrical guide sections 24 which are provided with overflow flats 25 which are particularly clearly visible in this view.
- the two guide sections 24 are connected to one another by a connecting section 26 with a smaller diameter.
- the outside diameter of the The guide section is dimensioned such that the valve cone 20 is movably guided in the valve cone bore 17.
- valve cone region 14 of the pole 3 is provided on the one hand with a pole thread 27 and on the other hand with a stop shoulder 28 which, when the pole 3 is screwed in, bears against the valve housing in a valve housing (not shown in this view).
- an armature space 29 is formed with a cylindrical pole tube bore 62, in which an armature 30 with an essentially cylindrical shape is inserted so as to be axially displaceable.
- the pole tube bore 62 is completely lined with a foil bearing, not shown here, for example made of teflon material.
- the dimensions of the pole tube bore 62 and the armature 30 are selected so that the foil bearing completely fills the space between the outside of the armature 30 and the pole tube bore 62, the armature 30 still being freely movable within the pole tube bore 62.
- the armature 30 has in its plunger end face 31, which is located on the left in FIG. 1, in the middle a plunger pocket bore 32 into which a rod-shaped armature plunger 33 is inserted.
- an annular plunger shoulder 34 is formed on the anchor plunger 33, with which the anchor plunger 33 is supported on the plunger end face 31 of the armature 30.
- the end of the armature tappet 33 pointing away from the armature 30 lies on the end face of the guide section 24 of the valve cone 20 which is located on the right in FIG. 1.
- the armature plunger 33 runs in a region between the plunger end face 31 and the guide section 24 through a baffle plate 35, which in a transition region between the armature chamber 29 and the valve cone bore 17 into the pole 3 is inserted.
- the baffle plate 35 is provided with a centrally located tappet bore 36.
- the baffle plate 35 is tightly connected to the pole 3 on its outer circumference for a good function of the actuating magnet 1.
- the tappet bore 36 is so small that the armature tappet 33 can just be moved essentially frictionlessly within the tappet bore 36 when the armature 30 moves axially.
- the armature 30 also has a spring chamber 38 designed as a blind hole on a rear end side 37 opposite the plunger end face 31.
- the base of the spring chamber 38 is connected to the plunger end face 31 via two flow channels 39 in such a way that hydraulic fluid can pass through the flow channels 39 when the armature 30 moves within the armature space 29.
- the pole tube 15 is closed at its end on the right-hand side in FIG. 1 with a metallic closure cover 40.
- the closure cover 40 has a circumferential flanging groove 41 arranged on the outside, into which a pole tube edge 42 of the pole tube 15 is pressed into the pole tube 15 when the closure cover 40 is in the inserted state.
- an annular groove 43 is formed on the outside, into which a sealing ring 44 is inserted, so that there is a tight connection between the outside of the closure cap 40 and the inside of the pole tube 15 .
- a fixing thread 45 is formed on the outside of the closure cap 40 outside the pole tube 15 and cooperates with an internal thread of the plastic nut 4 which is complementary thereto.
- the plastic nut 4 can be screwed onto the closure cover 40, where it acts on the housing base 8 of the coil housing 5 with a nut underside 46 and presses it firmly against a valve housing, not shown in this view, into which the pole 3 is screwed.
- One on the underside of the washer 6 The provided locking cam 47, which engages in a locking cam opening (not shown in this view) in the valve housing, prevents the coil housing 5 from rotating with respect to the valve housing.
- the closure cap 40 has an axially extending and continuous adjusting screw bore 48 in the interior, into which an adjusting screw 49 is inserted.
- the adjusting screw 49 has a screw head 50, in which an hexagon socket opening 51 is formed.
- a threaded area 52 adjoins the screw head 50, which cooperates with a corresponding internal thread area on the closure cover 40.
- a plastic ring 53 is provided in the threaded area 52 between the closure cover 40 and the adjusting screw 49 to prevent the adjustment screw 49 from rotating in the closure cover 40.
- the adjusting screw 49 has a sealing area 54, in the outside of which a sealing ring 55 is arranged, which effects a seal between the adjusting screw 49 and the adjusting screw bore 48.
- a rod-shaped return spring support 56 of the adjusting screw 49 extends into the spring chamber 38 of the armature 30.
- the return spring carrier 56 has at its end a stop disk 57, on which one end of a vibration damping spring 58 is supported.
- the other end of the vibration damping spring 58 is supported on a stop sleeve 59 fastened in the spring chamber 38, which is secured by a retaining ring 60 which is located both in a groove in the stop sleeve 59 and in a groove in the Spring chamber 38 engages, is fixed axially with respect to the armature 30.
- an armature return spring 61 is inserted in the interior of the stop sleeve 59 in a region between the return spring support 56 and the wall of the stop sleeve 59 the state shown in Figure 1 is compressed by the action of the vibration damping spring 58.
- FIG. 2 shows a cross section through a partial region of the armature 30 and the adjusting screw 49 in a state in which the armature 30 is shifted to the right compared to the state shown in FIG. 1.
- the stop disk 57 is firmly connected to the return spring support 56 by flanging over a material area.
- the actuating magnet 1 behaves as follows.
- the armature 30 is pulled into the pressure control position shown in FIG. 1, in which it acts on the valve cone 20 via the armature tappet 33 such that the cone tip 21 forms a predetermined throttle gap with the valve seat edge 22a.
- hydraulic fluid flows out of the valve cone bore 17 via the annular gap between the tappet bore 36 and the armature tappet 33 into the armature chamber 29.
- the hydraulic fluid in the armature chamber 29 displaced by the armature 30 and flows through the flow channels 39 in the armature 30 and via the spring chamber 38 in the rear armature space 63.
- the vibration damping spring 58 dampens the control strokes of the armature 30 in both directions. If a pressure oscillation occurs in the seat bore 22 and the pressure drops below the predefined value, the valve cone 20 moves to the left with the armature 30 and reduces the throttle gap between the valve edge 22a and the valve cone tip 21. At the same time, the vibration damping spring 58 moves higher. excited, and due to the high spring rate of this spring, the control stroke of the valve cone 20 is reduced to the left. If the pressure in the seat bore 22 rises above the predetermined value, the higher hydraulic force acting on the valve cone tip 21 pushes the valve cone 20 and the armature 30 to the right. The vibration damping spring 58 is relaxed according to its spring rate.
- the magnetic force previously stored in the vibration damping spring 58 is released and increases by the amount by which the spring force decreases. This reduces the control stroke of the valve plug to the right.
- the damping devices listed prevent the control movements of valve cone 20 and armature 30 from becoming too large, as a result of which permanent vibrations are effectively suppressed.
- the vibration damping spring 58 presses the armature 30 to the right by the preload stroke of this spring, which is only a few tenths of a millimeter. Subsequently, the armature return spring 61 pushes the armature 30 against the sealing cover stop surface 64. This creates a large throttle gap between the valve seat edge 22a and the valve cone tip 21, which offers only a small resistance to the flowing hydraulic fluid.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Magnetically Actuated Valves (AREA)
- Details Of Valves (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/890,838 US6628186B1 (en) | 1999-02-23 | 2000-02-09 | Solenoid valve |
JP2000601353A JP2002538387A (ja) | 1999-02-23 | 2000-02-09 | 電磁弁 |
EP00907523A EP1153235A1 (de) | 1999-02-23 | 2000-02-09 | Magnetventil |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19907732A DE19907732B4 (de) | 1999-02-23 | 1999-02-23 | Hydraulisches Magnetventil |
DE19907732.0 | 1999-02-23 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000050794A1 true WO2000050794A1 (de) | 2000-08-31 |
Family
ID=7898540
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2000/001013 WO2000050794A1 (de) | 1999-02-23 | 2000-02-09 | Magnetventil |
Country Status (5)
Country | Link |
---|---|
US (1) | US6628186B1 (de) |
EP (1) | EP1153235A1 (de) |
JP (1) | JP2002538387A (de) |
DE (1) | DE19907732B4 (de) |
WO (1) | WO2000050794A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7036788B1 (en) | 2002-11-28 | 2006-05-02 | Bosch Rexroth Ag | Directly controlled proportional pressure limiting valve |
Families Citing this family (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10139534A1 (de) | 2001-08-10 | 2003-02-20 | Bosch Rexroth Ag | Schließkörper, insbesondere Ventilkegel für ein Stetigdruckventil |
DE102004008796B4 (de) * | 2003-04-17 | 2019-12-24 | Continental Teves Ag & Co. Ohg | Verfahren und Vorrichtung zur Steuerung eines Hydraulikventils eines hydraulischen Systems sowie Steuergerät für ein hydraulisches System |
DE102006055796A1 (de) * | 2006-11-27 | 2008-05-29 | Robert Bosch Gmbh | Druckregelventil |
DE102008017654A1 (de) | 2007-04-12 | 2008-10-30 | Robert Bosch Gmbh | Bauteilanordnung |
DE102007029807B4 (de) * | 2007-06-27 | 2015-12-10 | Robert Bosch Gmbh | Polrohr und Betätigungsmagnet mit einem derartigen Polrohr |
US7552719B2 (en) * | 2007-12-04 | 2009-06-30 | Caterpillar Inc. | Solenoid assembly having slotted stator |
US7610888B2 (en) * | 2008-04-08 | 2009-11-03 | Caterpillar Inc. | Non-guided tappet and fuel injector using same |
DE102008030451A1 (de) * | 2008-06-26 | 2009-12-31 | Hydac Electronic Gmbh | Betätigungsvorrichtung |
JP5150425B2 (ja) * | 2008-09-11 | 2013-02-20 | 川崎重工業株式会社 | 油浸型ソレノイドの調整ネジ構造及びそれを備える油浸型ソレノイド |
US8433263B2 (en) * | 2008-09-24 | 2013-04-30 | Freescale Semiconductor, Inc. | Wireless communication unit, integrated circuit and method of power control of a power amplifier therefor |
WO2010049166A1 (de) * | 2008-10-31 | 2010-05-06 | Robert Bosch Gmbh | Elektromagnet |
JP5307517B2 (ja) * | 2008-11-14 | 2013-10-02 | カヤバ工業株式会社 | ソレノイド |
DE102009041604A1 (de) * | 2009-09-17 | 2011-03-24 | Svm Schultz Verwaltungs-Gmbh & Co. Kg | Elektromagnet |
EP2494244B1 (de) | 2009-10-26 | 2013-09-11 | Hydac Fluidtechnik GmbH | Magnetventil |
TWI474350B (zh) * | 2011-06-10 | 2015-02-21 | Nat Inst Chung Shan Science & Technology | Proportional electromagnet device |
DE102011055093B4 (de) * | 2011-11-07 | 2015-05-21 | Magna Powertrain Ag & Co. Kg | Reduzierung des Ölaustauschs in einem Magnetventil |
DE102012214624A1 (de) * | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Polrohr für eine Aktoreinrichtung |
DE102013107060A1 (de) * | 2013-07-04 | 2015-01-08 | Otto Egelhof Gmbh & Co. Kg | Schaltventil zur Regelung eines Massenstroms |
DE102013226619A1 (de) | 2013-12-19 | 2015-06-25 | Robert Bosch Gmbh | Verfahren zur Herstellung eines Polrohrs, Polrohr für einen Elektromagneten und Magnetventil |
DE102015222745A1 (de) | 2015-11-18 | 2017-05-18 | Robert Bosch Gmbh | Ventil mit Stromregel- und Druckbegrenzungsfunktion |
DE102015224152B3 (de) * | 2015-12-03 | 2017-03-02 | Robert Bosch Gmbh | Betätigungsvorrichtung mit Polscheibe und Distanzscheibe |
DE102016119990B4 (de) * | 2016-10-20 | 2019-04-18 | Rausch & Pausch Gmbh | Schaltventil mit Aufpralldämpfung |
DE102016224315A1 (de) | 2016-12-07 | 2018-06-07 | Robert Bosch Gmbh | Pressverband mit umlaufenden Rillen |
EP3431847A1 (de) * | 2017-07-17 | 2019-01-23 | Microtecnica S.r.l. | Regelsystem und verfahren für ein elektroventil |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19527482A1 (de) * | 1994-07-29 | 1996-02-08 | Aisin Seiki | Elektromagnetisch betätigtes Ventil |
EP0759388A2 (de) * | 1995-08-18 | 1997-02-26 | Daewoo Electronics Co., Ltd | Elektromagnetventil sowie Modulator und Antiblockier-Bremssystem mit einem solchen Elektromagnetventil |
DE19611832A1 (de) * | 1996-03-26 | 1997-10-02 | Teves Gmbh Alfred | Sitzventil |
Family Cites Families (10)
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US1504773A (en) * | 1922-03-31 | 1924-08-12 | Marston Sheldon | Electromagnetic valve |
DE1111737B (de) * | 1960-01-29 | 1961-07-27 | Licentia Gmbh | Verfahren zur Herstellung von Elektromagneten und nach dem Verfahren hergestellter Elektromagnet |
US4100519A (en) * | 1975-12-31 | 1978-07-11 | Mac Valves, Inc. | Alignment means for a moveable pole-plunger assembly |
US4044324A (en) * | 1976-04-30 | 1977-08-23 | Ledex, Inc. | Coil compressed plunger cavity components for a wet type solenoid |
JPS5536911A (en) * | 1978-09-04 | 1980-03-14 | Hitachi Ltd | Electricity-position conversion device |
IT1187924B (it) * | 1986-02-19 | 1987-12-23 | Weber Spa | Valvola ad azionamento elettromagnetico per la dosatura e la polverizzazione del carburante per un dispositivo di alimentazione di un motore a combustione interna |
DE3915223A1 (de) * | 1989-05-10 | 1990-11-15 | Bosch Gmbh Robert | Elektromagnetisch betaetigtes wegeventil |
DE4137123A1 (de) * | 1991-11-12 | 1993-05-13 | Teves Gmbh Alfred | Drucksteuerventil |
US5455470A (en) * | 1994-03-17 | 1995-10-03 | Alliedsignal Inc. | Electrical machines and components thereof incorporating foil journal bearings |
US6076491A (en) * | 1994-05-03 | 2000-06-20 | Lotus Cars Limited | Valve control mechanism |
-
1999
- 1999-02-23 DE DE19907732A patent/DE19907732B4/de not_active Expired - Fee Related
-
2000
- 2000-02-09 WO PCT/EP2000/001013 patent/WO2000050794A1/de not_active Application Discontinuation
- 2000-02-09 EP EP00907523A patent/EP1153235A1/de not_active Ceased
- 2000-02-09 US US09/890,838 patent/US6628186B1/en not_active Expired - Lifetime
- 2000-02-09 JP JP2000601353A patent/JP2002538387A/ja active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19527482A1 (de) * | 1994-07-29 | 1996-02-08 | Aisin Seiki | Elektromagnetisch betätigtes Ventil |
EP0759388A2 (de) * | 1995-08-18 | 1997-02-26 | Daewoo Electronics Co., Ltd | Elektromagnetventil sowie Modulator und Antiblockier-Bremssystem mit einem solchen Elektromagnetventil |
DE19611832A1 (de) * | 1996-03-26 | 1997-10-02 | Teves Gmbh Alfred | Sitzventil |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7036788B1 (en) | 2002-11-28 | 2006-05-02 | Bosch Rexroth Ag | Directly controlled proportional pressure limiting valve |
Also Published As
Publication number | Publication date |
---|---|
DE19907732B4 (de) | 2008-08-28 |
EP1153235A1 (de) | 2001-11-14 |
DE19907732A1 (de) | 2000-08-24 |
JP2002538387A (ja) | 2002-11-12 |
US6628186B1 (en) | 2003-09-30 |
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