EP0631056A1 - Dispositif d'entraînement pour une vanne de réglage - Google Patents
Dispositif d'entraînement pour une vanne de réglage Download PDFInfo
- Publication number
- EP0631056A1 EP0631056A1 EP94108751A EP94108751A EP0631056A1 EP 0631056 A1 EP0631056 A1 EP 0631056A1 EP 94108751 A EP94108751 A EP 94108751A EP 94108751 A EP94108751 A EP 94108751A EP 0631056 A1 EP0631056 A1 EP 0631056A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- volume
- oil
- actuator
- control valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 3
- 230000009471 action Effects 0.000 description 13
- 238000007789 sealing Methods 0.000 description 8
- 238000006073 displacement reaction Methods 0.000 description 5
- 238000013461 design Methods 0.000 description 4
- 238000005259 measurement Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 230000008569 process Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000007547 defect Effects 0.000 description 3
- 238000012937 correction Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 210000003746 feather Anatomy 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000009993 protective function Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000009420 retrofitting Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Images
Classifications
-
- 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
- F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2220/00—Application
- F05B2220/30—Application in turbines
- F05B2220/301—Application in turbines in steam turbines
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S91/00—Motors: expansible chamber type
- Y10S91/03—Large area valve
Definitions
- the invention relates to an actuator for a control valve according to the preamble of patent claim 1.
- An actuator for actuating a control valve with which, for example, the steam supply to a turbine of a power plant is regulated has a main piston of a piston-cylinder arrangement connected to the actuating rod of the control valve, which is acted upon on the one hand by spring force and on the other hand by oil under pressure.
- the spring force securely closes the control valve, as a result of which the steam supply is interrupted. This ensures that the turbine does not get out of control if the pressure of the oil should drop.
- the oil pressure in a drive volume, which acts on the main piston and actuates the control valve via it, is generated by an electro-hydraulic converter.
- An actuator with comparatively high dynamics is known from European patent application 0 430 089 A1.
- This actuator has a piston-cylinder arrangement in which on one side of the main piston there is a drive volume which can be pressurized with oil under pressure and on the other side an oil-filled buffer volume. With this actuator, an oil flow from the actuator volume is released through a plate valve directly attached to the piston-cylinder arrangement through a connecting line with a large cross-section directly attached to the piston-cylinder arrangement, so that the control valve is actuated very quickly .
- the invention seeks to remedy this.
- the invention as characterized in the claims, solves the problem of creating an actuator for a control valve which can be improved in its dynamic behavior with comparatively simple means.
- This actuator for a control valve has a control circuit which adjusts the actuator according to a setpoint specified by a higher-level system control system. It also has a main piston sliding in a master cylinder, with a drive volume on one side of the main piston that can be pressurized with oil under pressure, and a plate valve upstream of the drive volume. It has proven particularly advantageous that the plate valve is provided with a separate storage volume connected to a drain device. In this way, the plate valve can be arranged at any point in the area of the piston-cylinder arrangement of the actuator.
- a connecting line is provided between the drive volume and the plate valve, which leads through a connecting piece into a spring chamber of the plate valve.
- the separate storage volume is arranged concentrically around the spring chamber.
- the spring chamber under pressure and the sealing points of the plate valve are complete in this way surrounded by low pressure volumes. If oil should escape from the spring chamber under high pressure in the event of a defect, this escapes into the volumes mentioned, so that secondary damage is avoided with great certainty.
- FIG. 1 shows an actuator 1, which actuates a control valve 2, which regulates the amount of hot steam flowing through a hot steam line 3 to a turbine (not shown).
- the control valve 2 is connected by a valve spindle 4 to a main piston 6 sliding in a master cylinder 5.
- a drive volume 7 pressurized with oil is arranged below the main piston 6. Instead of the oil, another hydraulic fluid or a gaseous medium can also be provided.
- An oil-filled buffer volume 8 is provided above the main piston 6, in which a spring 9 is also arranged, which counteracts the oil pressure in the drive volume 7.
- a line 52 leads from the buffer volume 8 to a drain device, not shown.
- a rod 10 is provided on the spring side of the main piston 6, which connects the latter to a displacement measuring device 11.
- the displacement measuring device 11 monitors the stroke of the main piston 6 and continuously reports its position to a position controller 33, as indicated by an action line 40.
- the rod 10 and the valve spindle 4 penetrate the master cylinder 5 on opposite sides. The design of these pressure-tight penetrations is known and need not be described further here.
- the displacement measuring device 11 can also be attached directly to the valve spindle 4 in the area outside the master cylinder 5.
- the plate valve 17 is flanged to a connecting flange (not shown) of the connecting line 15 such that one end 14a of the connecting piece 14 is connected to the connecting line 15 in a pressure-tight manner.
- the tubular connecting piece 14 has a cylindrical sealing seat 14b at the other end.
- the plate valve 17 has a plate 18, for example provided with an orifice 70, which is pressed by a compression spring 19 against the sealing seat 14b and at the same time against a sealing part 23 embedded in the housing 22. In the closed state, the plate 18 prevents oil from escaping from the spring space 20 into a volume 21 concentrically surrounding the connecting piece 14. The volume 21 merges into the intermediate volume 24. These two volumes surround the spring chamber 20 and the sealing points of the plate valve 17 concentrically.
- the spring chamber 20 pressurized with oil in the operating state shown is closed off against the intermediate volume 24 by means of a spring chamber cover 20a.
- the plate 18 is designed in such a way that it cannot jam.
- the compression spring 19 is arranged in a spring chamber 20 which is pressurized with oil through a bore 12 and an opening 13.
- the size of the spring chamber 20 is approximately 1,000 times smaller than the drive volume 7 with which it is in operative connection.
- the spring chamber 20 is also operatively connected to a proportional directional control valve 25 via a line 47.
- a proportional directional control valve 25 for example, the directly operated one Proportional directional control valve with position control of the type KFDG 4V - 3/5, series 20, from Vickers Systems GmbH, D 6380 Bad Homburg vdH can be used.
- the proportional directional valve 25 has two actuating magnets 26, 27, which cooperate with return springs, not shown, and in this case three hydraulic connections 28, 29, 30.
- the proportional directional control valve 25 is shown in the so-called "fail-safe" position.
- the proportional directional valve 25 has a stroke measurement 31 connected to a slide of the valve, which measures the respective position of the slide and, as indicated by an action line 32, passes this information on to a position controller 33 with an integrated power amplifier.
- the actuating magnets 26, 27 receive their commands from this position controller 33 with an integrated power amplifier. Furthermore, the position controller 33 has an input for feeding in an electrical signal, as indicated by the action line 40, from the displacement measuring device 11.
- a power amplifier EEA-PAM-533-A, series 20, from Vickers Systems GmbH, D 6380 Bad Homburg vdH, which is specially matched to the proportional control valve 25, can be used as the position controller 33, for example.
- This position controller 33 works together with a higher-order controller 36, as indicated by an action line 37.
- the controller 36 has further inputs 38, through which information and commands are fed in by a higher-level plant control system which controls the entire power plant.
- Oil is fed in under pressure through a line 45, and the necessary oil pressure is generated by a pump (not shown).
- the flow rate of the oil is limited to a maximum amount by an orifice 46 arranged in the course of the line 45.
- the flow rate of the oil is limited by an orifice 70 provided in the plate 18 of the plate valve 17, so that the orifice 46 can then be dispensed with.
- the Line 45 leads to the connection 28 of the proportional directional control valve 25, which in the illustration in FIG. 1 is not connected through to the connection 29.
- connection 29 is connected on the one hand to a line 47, which in turn is connected to the bore 12, which in the Spring chamber 20 of the plate valve 17 leads, and on the other hand with a line 48, which leads to a normally closed, designed as a plate valve safety valve 49.
- a line 50 leads into the intermediate volume 24 of the plate valve 17.
- the last piece of the line 50 is shown in FIG. 1a as a bore penetrating the wall of the housing 22.
- a line 51 branches off from the line 50 and establishes the connection with the connection 30 of the proportional directional valve 25.
- the lines 50 and 51 are designed as bores in the housing 22, this is possible because both the proportional directional valve 25 and the safety valve 49 is also flanged directly and pressure-tight to the housing 22, so that a monolithic valve block is formed.
- a drain port 24a leads from the intermediate volume 24 into a line leading to a drain device, not shown. From this drain device, the oil continues through the aforementioned pump back into line 45.
- the safety valve 49 is designed as a plate valve with a cylinder 53, a volume 55 which is pressurized with oil under pressure from a safety oil circuit through a line 54 and which is delimited by a valve plate 56 and with a valve spring 57 which controls the oil pressure acting on the valve plate 56 counteracts. It cannot be seen from the schematic illustration of the safety valve 49 that the valve plate 56 is designed in such a way that it is impossible to jam it.
- the line 54 normally leads through a directional control valve 58 and connects it to the volume 55.
- the directional control valve 58 is actuated by an electromagnet 59.
- An action line 60 indicates the path of the trigger command for the electromagnet 59.
- the plate valve 17 can be used in all systems regardless of the design of the respective master cylinder 5.
- the line 15 can generally be made comparatively short, so that the oil-filled line volume is correspondingly small, which advantageously increases the dynamics.
- the actuator is therefore very versatile.
- the interaction of the position controller 33 with the integrated power amplifier and the controller 36 as a common electronic control arrangement of a control circuit is particularly advantageous because the position controller 33 is specially adapted to the proportional directional control valve 25, so that no additional adjustments and adjustments are necessary.
- this electronic control system it is entirely possible to assemble this electronic control system from other elements or to transfer its function to a higher-level system control system if, for example, the protection concept of the power plant would require this.
- signals originating from the displacement measuring device 11 and from the stroke measurement 31 are processed continuously together with at least one setpoint value specified by the higher-level system control system according to a specified logic. In the event of deviations from this target value, this control arrangement generates correction signals which act on the actuating magnets 26, 27 of the proportional directional control valve 25 and cause the same to be reversed accordingly.
- a breakthrough through the plate 18 has a cylindrical opening 66, which is followed by a conical extension.
- a ball 67 is pressed into this conical extension by a spring 68, which is supported against a holder 69 connected to the plate 18, and closes the opening 66.
- Oil 66 can enter the connecting piece 14 through pressure and through this and further flow through the connecting line 15 into the drive volume 7 as soon as a pressure difference occurs that is large enough to overcome the force of the spring 68 and the oil pressure acting on the ball 67.
- FIG. 3 is similar to FIG. 2, except that in this case an opening with the opening 66 through the plate 18 is designed such that oil flows from the drive volume 7 through the connecting line 15 and through the connecting piece 14 into the spring chamber 20 can.
- an opening with the opening 66 through the plate 18 is designed such that oil flows from the drive volume 7 through the connecting line 15 and through the connecting piece 14 into the spring chamber 20 can.
- the cross section of the diaphragm 70 is designed to be significantly smaller than that of the opening 66.
- FIG. 5 shows a plate 18 with two valve arrangements similar to that shown in FIG. 2, but which allow oil to pass through in opposite directions with a corresponding differential pressure.
- the opening 66 which leads from the drive volume 7 into the spring chamber 20, has a substantially larger cross section than the second opening 66.
- FIG. 1 is considered in more detail.
- the control valve 2 must be comparatively in operation can be closed quickly.
- the closing speed is normally around 1 m / sec, while the opening speed, on the other hand, only requires speeds around 0.02 m / sec.
- These speed specifications are guide values; depending on the design of the power plant, there may also be significant deviations from these specifications.
- the actuator 1 can be adapted to the respective operating conditions with comparatively little effort. If the control valve 2 is to be moved in the opening direction, the proportional directional control valve 25 is actuated by the position controller 33, and is actuated in such a way that it is to the left of the position shown standing scheme applies.
- connection 28 and 29 are then connected through and oil under pressure flows from the line 45 through the proportional directional control valve 25.
- No oil can flow through line 48 in normal operation, since the safety valve 49 closes this line 48.
- the oil flows through the line 47, the bore 12 and the opening 13 into the spring chamber 20 of the plate valve 17 and from there through the opening of the plate 18, through the connector 14 and through the connecting line 15 into the drive volume 7.
- the oil pressure in Drive volume 7 moves the main piston 6 upward and thus the control valve 2 in the opening direction via the valve spindle 4.
- the position measuring device 11 monitors the stroke of the main piston 6 and continuously reports its position to the position controller 33, as indicated by the line of action 40.
- the position controller 33 controls the proportional directional valve 25 so that the oil flow is interrupted.
- the stroke measurement 31, the signals of which are processed in the position controller 33, monitors the operating behavior of the proportional directional valve 25.
- the movement of the main piston 6 is ended at the same time as this control.
- the spring 9 presses the main piston 6 down and thus the oil from the drive volume 7 until the end position of the control valve 2 is reached.
- the oil flows out very quickly, since the cross section released by the plate valve 17 is comparatively large, so that the flow process is not negatively influenced by it.
- the closing movement of the control valve is initiated by lowering the oil pressure in the spring chamber 20, whereupon, if only a small stroke is to be made in the closing direction, the plate valve 17 only for a short time opens and oil can only briefly escape into the volume 21 and the intermediate volume 24. As soon as the desired value is reached, the plate valve 17 closes again immediately.
- the design of the plate 18 according to FIG. 5 also allows a small closing movement, for a larger stroke of the main piston 6 it is also necessary to open the plate valve 17 in this case.
- the proportional directional control valve 25 is shown in the central position in FIG. 1. This position is assumed if, for example, the actuating magnets 26, 27 should not receive any voltage due to a power failure. Reaching this position is ensured by spring force of springs provided in the interior of the proportional directional valve 25 under all circumstances. In this position, the spring chamber 20 is relieved of pressure by the lines 47, 51 and 50, so that the plate valve 17 opens, which, as already described, leads to a quick closing of the control valve 2. In this way it is ensured that the control valve 2 is always definitely closed even in the event of a fault, so that under no circumstances can damage to the turbine being operated as a result of a defect in the actuator 1.
- the safety valve 49 normally prevents a pressure drop in the line 48 in the direction of the drain device. However, if the pressure in the safety oil circuit drops, the pressure in the volume 55 also drops and the safety valve 49 releases the line 48, regardless of the position of the proportional directional control valve 25, so that the pressure can escape from the spring chamber 20 of the plate valve 17 the lines 47, 48 and 50, whereby, as already described, a quick closing process of the control valve 2 is initiated. This measure can also be used to reliably shut off the steam supply to the turbine.
- the directional control valve 58 is installed, which makes it possible as soon as it is switched electromagnetically to the right of the Shown position shown scheme that oil under pressure from line 45 through line 61 and through the directional control valve 58 can act on the volume 55, whereby the safety valve 49 is closed.
- the command path for the directional control valve 58, as indicated by the line of action 60, must, however, be blocked as soon as it is switched over to normal operation, since otherwise the safety oil circuit may no longer be able to act on the safety valve 49, so that the protective function of this circuit is not more would be guaranteed.
- the pressurized spring chamber 20 and the sealing points of the plate valve 17 are completely surrounded by volumes subjected to low pressure. If oil should escape from the spring chamber 20 under high pressure in the event of a defect, this escapes into the said volumes, so that secondary damage is avoided with great certainty.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Driven Valves (AREA)
- Control Of Turbines (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4320937 | 1993-06-24 | ||
DE4320937A DE4320937A1 (de) | 1993-06-24 | 1993-06-24 | Stellantrieb für ein Regelventil |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0631056A1 true EP0631056A1 (fr) | 1994-12-28 |
EP0631056B1 EP0631056B1 (fr) | 1996-05-01 |
EP0631056B2 EP0631056B2 (fr) | 1999-05-12 |
Family
ID=6491077
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP94108751A Expired - Lifetime EP0631056B2 (fr) | 1993-06-24 | 1994-06-08 | Dispositif d'entraínement pour une vanne de réglage |
Country Status (5)
Country | Link |
---|---|
US (1) | US5467683A (fr) |
EP (1) | EP0631056B2 (fr) |
JP (1) | JPH07139307A (fr) |
CN (1) | CN1102233A (fr) |
DE (2) | DE4320937A1 (fr) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1020647A1 (fr) | 1999-01-14 | 2000-07-19 | ABB Alstom Power (Schweiz) AG | Soupape à plaque |
CN102615264A (zh) * | 2012-03-28 | 2012-08-01 | 蚌埠市华艺压铸机制造有限责任公司 | 压铸机升降阀板增压截止阀 |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10058560A1 (de) * | 2000-11-24 | 2002-06-13 | Voith Turbo Kg | Elektrohydraulischer Stellantrieb |
DE20115847U1 (de) | 2001-09-26 | 2001-12-13 | Loctite Deutschland GmbH, 81925 München | Vorrichtung zur Ventilbetätigung und zum Stellen des Ventilhubs |
US7137407B2 (en) * | 2005-02-22 | 2006-11-21 | Emerson Process Management Power & Water Solutions, Inc. | Trip manifold |
CN100393985C (zh) * | 2006-10-13 | 2008-06-11 | 成都发动机(集团)有限公司 | 精确调节顶压和紧急全关静叶的调节机构 |
DE102009009852B4 (de) | 2009-02-20 | 2023-07-06 | General Electric Technology Gmbh | Plattenablaufventil, insbesondere zum Beeinflussen des Ansteuerdrucks eines Regelventils |
CN107842642B (zh) * | 2017-12-12 | 2024-04-02 | 大连亨利测控仪表工程有限公司 | 高效能切断型单作用气动执行机构 |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3432890A1 (de) * | 1984-07-20 | 1986-01-23 | BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau | Einrichtung zur ueberwachung von physikalischen groessen an anlagen |
EP0430089A1 (fr) * | 1989-12-01 | 1991-06-05 | Asea Brown Boveri Ag | Actuateur |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2204270A (en) * | 1938-04-29 | 1940-06-11 | Watson Stillman Co | Surge valve for hydraulic presses |
CA1038260A (fr) * | 1974-05-14 | 1978-09-12 | Westinghouse Electric Corporation | Systeme de fermeture positive pour robinets a opercule flottant |
EP0127027B1 (fr) * | 1983-05-30 | 1988-03-09 | BBC Brown Boveri AG | Servomoteur électrohydraulique pour soupapes de turbines |
DD263801A1 (de) † | 1987-06-09 | 1989-01-11 | Goerlitzer Maschinenbau Veb | Hydraulische schaltung fuer entnahme- oder anzapf-schnellschlussventile von dampfturbinen |
-
1993
- 1993-06-24 DE DE4320937A patent/DE4320937A1/de not_active Withdrawn
-
1994
- 1994-06-02 US US08/253,250 patent/US5467683A/en not_active Expired - Lifetime
- 1994-06-08 DE DE59400247T patent/DE59400247D1/de not_active Expired - Lifetime
- 1994-06-08 EP EP94108751A patent/EP0631056B2/fr not_active Expired - Lifetime
- 1994-06-23 JP JP6141948A patent/JPH07139307A/ja not_active Withdrawn
- 1994-06-24 CN CN94107226A patent/CN1102233A/zh active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3432890A1 (de) * | 1984-07-20 | 1986-01-23 | BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau | Einrichtung zur ueberwachung von physikalischen groessen an anlagen |
EP0430089A1 (fr) * | 1989-12-01 | 1991-06-05 | Asea Brown Boveri Ag | Actuateur |
Non-Patent Citations (1)
Title |
---|
G. WEISS ET AL: "Weiterentwicklung der Regel- und Sicherheitssysteme für Dampfturbinen", VGB KRAFTWERKSTECHNIK, vol. 73, no. 4, April 1993 (1993-04-01), ESSEN, pages 345 - 351, XP000358566 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1020647A1 (fr) | 1999-01-14 | 2000-07-19 | ABB Alstom Power (Schweiz) AG | Soupape à plaque |
US6241211B1 (en) | 1999-01-14 | 2001-06-05 | Abb Alstom Power (Schweiz) Ag | Plate valve |
CN102615264A (zh) * | 2012-03-28 | 2012-08-01 | 蚌埠市华艺压铸机制造有限责任公司 | 压铸机升降阀板增压截止阀 |
Also Published As
Publication number | Publication date |
---|---|
CN1102233A (zh) | 1995-05-03 |
DE59400247D1 (de) | 1996-06-05 |
EP0631056B1 (fr) | 1996-05-01 |
JPH07139307A (ja) | 1995-05-30 |
DE4320937A1 (de) | 1995-01-05 |
US5467683A (en) | 1995-11-21 |
EP0631056B2 (fr) | 1999-05-12 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0496021B1 (fr) | Soupape d'arrêt pour système hydraulique de sécurité | |
EP1598560B1 (fr) | Dispositif de soupape hydraulique | |
DE102018201299B4 (de) | Dampfturbinenventil-Antriebsvorrichtung | |
DE102010053811A1 (de) | Störungssicheres Betätigungssystem | |
EP0540963B1 (fr) | Système d'alimentation pour système hydraulique divisé | |
EP0433791B1 (fr) | Actuateur pour une valve d'alimentation | |
EP0430089B1 (fr) | Actuateur | |
EP0631056B1 (fr) | Dispositif d'entraînement pour une vanne de réglage | |
EP0054602A1 (fr) | Soupape d'arrêt contrôlée par son propre fluide | |
EP0451543B1 (fr) | Système d'actionnement pour une vanne de régulation de vapeur | |
DE102012016838B4 (de) | Hydraulische Steuerschaltung für eine hydraulisch betätigte Gießeinheit | |
EP1082560B1 (fr) | Unite de commande pour une soupape de surete | |
DE4036564A1 (de) | Hydraulische einrichtung zur steuerung eines arbeitszylinders einer presse | |
EP3353385B1 (fr) | Turbine munie de soupapes à fermeture rapide et de soupapes de régulation | |
DE102014226623A1 (de) | Druckbegrenzungsventil und damit ausgestattete hydraulische Maschine | |
EP0604805B1 (fr) | Dispositif de commande pour vérin hydraulique avec signal de réglage proportionnel | |
DE3225132A1 (de) | Hydraulisches sicherheitsbremsventil | |
EP2452078B1 (fr) | Dispositif constituant une restriction variable pour un écoulement fluidique | |
EP3037678B1 (fr) | Module de levage | |
EP1203161B1 (fr) | Soupape de securite de presse | |
EP0419946B1 (fr) | Moteur pour une vanne | |
EP2241764B1 (fr) | Soupape à siège dotée d'une fonction de soupape de dérivation et de compensateur de pression | |
EP0462387B1 (fr) | Système hydraulique de contrôle et sécurité | |
DE4236846C2 (de) | Geregelter elektrohydraulischer Stellantrieb für Hubventile, insbesondere Dampfventile von Dampfturbinen | |
EP3081371B1 (fr) | Soupape de reglage, utilisation d'une soupape de reglage et bloc de soupapes |
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 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB IT |
|
17P | Request for examination filed |
Effective date: 19950513 |
|
17Q | First examination report despatched |
Effective date: 19951004 |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
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 |
|
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: 19960501 |
|
REF | Corresponds to: |
Ref document number: 59400247 Country of ref document: DE Date of ref document: 19960605 |
|
ITF | It: translation for a ep patent filed | ||
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 19960708 |
|
ET | Fr: translation filed | ||
PLAV | Examination of admissibility of opposition |
Free format text: ORIGINAL CODE: EPIDOS OPEX |
|
PLBI | Opposition filed |
Free format text: ORIGINAL CODE: 0009260 |
|
PLBQ | Unpublished change to opponent data |
Free format text: ORIGINAL CODE: EPIDOS OPPO |
|
PLBF | Reply of patent proprietor to notice(s) of opposition |
Free format text: ORIGINAL CODE: EPIDOS OBSO |
|
26 | Opposition filed |
Opponent name: SIEMENS AG ZENTRALABTEILUNG TECHNIK ABTLG. ZT PA 3 Effective date: 19970127 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 19970513 Year of fee payment: 4 |
|
PLBF | Reply of patent proprietor to notice(s) of opposition |
Free format text: ORIGINAL CODE: EPIDOS OBSO |
|
PLBF | Reply of patent proprietor to notice(s) of opposition |
Free format text: ORIGINAL CODE: EPIDOS OBSO |
|
RAP2 | Party data changed (patent owner data changed or rights of a patent transferred) |
Owner name: ASEA BROWN BOVERI AG |
|
PLAW | Interlocutory decision in opposition |
Free format text: ORIGINAL CODE: EPIDOS IDOP |
|
PLAW | Interlocutory decision in opposition |
Free format text: ORIGINAL CODE: EPIDOS IDOP |
|
PUAH | Patent maintained in amended form |
Free format text: ORIGINAL CODE: 0009272 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: PATENT MAINTAINED AS AMENDED |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |
|
27A | Patent maintained in amended form |
Effective date: 19990512 |
|
AK | Designated contracting states |
Kind code of ref document: B2 Designated state(s): DE FR GB IT |
|
ITF | It: translation for a ep patent filed | ||
EN | Fr: translation not filed | ||
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E |
|
GBTA | Gb: translation of amended ep patent filed (gb section 77(6)(b)/1977) | ||
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20000512 Year of fee payment: 7 |
|
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: 20010608 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20010608 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20070626 Year of fee payment: 14 |
|
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: 20080608 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 59400247 Country of ref document: DE Representative=s name: ROESLER, UWE, DIPL.-PHYS.UNIV., DE Effective date: 20120621 Ref country code: DE Ref legal event code: R081 Ref document number: 59400247 Country of ref document: DE Owner name: ALSTOM TECHNOLOGY LTD., CH Free format text: FORMER OWNER: ALSTOM, PARIS, FR Effective date: 20120621 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20130628 Year of fee payment: 20 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R071 Ref document number: 59400247 Country of ref document: DE |
|
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 EXPIRATION OF PROTECTION Effective date: 20140611 |