EP0433791B1 - Antrieb für ein Speiseventil - Google Patents

Antrieb für ein Speiseventil Download PDF

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Publication number
EP0433791B1
EP0433791B1 EP90123496A EP90123496A EP0433791B1 EP 0433791 B1 EP0433791 B1 EP 0433791B1 EP 90123496 A EP90123496 A EP 90123496A EP 90123496 A EP90123496 A EP 90123496A EP 0433791 B1 EP0433791 B1 EP 0433791B1
Authority
EP
European Patent Office
Prior art keywords
valve
valves
line
pressure
test system
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90123496A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0433791A1 (de
Inventor
Rico Plangger
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.)
ABB Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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 ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Priority to AT90123496T priority Critical patent/ATE104014T1/de
Publication of EP0433791A1 publication Critical patent/EP0433791A1/de
Application granted granted Critical
Publication of EP0433791B1 publication Critical patent/EP0433791B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/20—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted
    • F01D17/22—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical
    • F01D17/26—Devices dealing with sensing elements or final actuators or transmitting means between them, e.g. power-assisted the operation or power assistance being predominantly non-mechanical fluid, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/16—Trip gear
    • F01D21/18—Trip gear involving hydraulic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/20—Checking operation of shut-down devices
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8158—With indicator, register, recorder, alarm or inspection means
    • Y10T137/8326—Fluid pressure responsive indicator, recorder or alarm

Definitions

  • the invention relates to a drive for a feed valve with a hydraulically pressurized actuation line and with a device for controlling the pressure in the actuation line, which has three valves connected to one another to form a hydraulic 2-by-3 circuit.
  • a drive for a feed valve is known from the patent specification CH 666 132.
  • This drive which is operated with oil at comparatively low pressure, actuates, for example, a quick-closing valve, which serves as a feed valve for the steam feed of a turbine.
  • the oil under pressure or another hydraulic fluid acts on the actuator via an actuation line so that it can open or close the feed valve.
  • the pressure in the actuation line is controlled by a device which has three valves connected to one another to form a hydraulic 2 by 3 circuit.
  • These valves are designed as electromagnetically operated slide valves and each is monitored separately for its functionality, so that three monitoring circuits are necessary. These monitoring circuits have mechanical contacts that require maintenance. This device is less suitable for use at higher pressures.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problem of creating a drive for a feed valve which is suitable for a comparatively high pressure of the driving oil and whose functionality can be monitored with simple means.
  • FIG. 1 shows a schematic diagram of a part of the drive, namely the part that includes a device for controlling the pressure in an actuation line 1.
  • Oil is generally used as the medium for transmitting this pressure, but another hydraulic fluid or a gaseous medium can also be used for this.
  • a cylinder-piston arrangement of the drive is actuated, which opens or closes the associated feed valve, also not shown.
  • this feed valve will be open when the pressure in the actuating line 1 is fully present and as soon as the pressure drops, it will close quickly.
  • This device for controlling the pressure has three identical valves 2, 3 and 4 which are interconnected to form a hydraulic 2 by 3 circuit.
  • the oil pressurized by a pump not shown, reaches this device. Pressures in the range around 160 bar are used.
  • oil is fed under pressure directly into the actuating line 1 via a line 10 provided with an orifice 9, the Aperture 9 determines the flow rate of the oil.
  • Another line 12 provided with an orifice 11 feeds a small amount of oil under pressure into a line 13 of a test system 14.
  • the line 13 feeds a pressure switch 16 via a shut-off device 15.
  • the shut-off device 15 is usually only closed when the pressure switch 16 is revised.
  • the pressure switch 16 can contain, for example, a piezoelectric measuring element which works without mechanical contact and therefore practically maintenance-free.
  • the pressure switch 16 responds when the pressure falls below a set minimum value and emits an electrical signal to a higher-level plant control system, not shown, where this signal is processed further.
  • solenoid valves 25, 26, 27 are fed from the inlet 8.
  • the solenoid valves 25, 26, 27 are shown magnetically excited, in the event of a failure of the electrical energy or a shutdown of the same, the solenoid valves 25, 26, 27 are each by a schematically indicated spring 28, 29 and 30 in a second position shown sketched pressed.
  • the oil flows under pressure through the solenoid valves 25, 26, 27 through in each case a line 31, 32 and 33 which leads into a schematically illustrated drive volume 34, 35 and 36 of the valves 2, 3, 4.
  • the drive volume 34 is assigned to the valve 2, the drive volume 35 to the valve 3 and the drive volume 36 to the valve 4.
  • another output 37, 38 and 39 of the solenoid valves 25, 26, 27 is connected to an outlet 41 via a common line 40. In the drawn valve position, however, the outlets 37, 38, 39 are not traversed by oil.
  • valves 2, 3, 4 are designed as double valves, each having a seat valve and a slide valve, the type will be explained in more detail later in connection with FIG. 5.
  • Valves 2, 3, 4 are shown in FIG. 1, each with pressurized drive volume 34, 35, 36; if the supply of oil under pressure through the respective lines 31, 32, 33 is omitted, valves 2, 3, 4 each pressed by strong springs 42, 43 and 44 into a second switching position shown in FIG. 1. This ensures that the valves always assume a defined switching position even in the event of a malfunction.
  • each of the valves 2, 3, 4 has four further connections for oil lines.
  • the valve 2 has the connections 45, 46, 47 and 48.
  • the valve 3 has the connections 49, 50, 51 and 52.
  • the valve 4 has the connections 53, 54, 55 and 56.
  • connection 45 of the valve 2 is connected to the actuation line 1 and separated from the connection 46 by a schematically indicated slide valve.
  • the connection 46 is connected to the line 13 of the test system 14 via a line 60, in which a check valve 61 is attached.
  • the check valve 61 is arranged such that an oil flow out of the test system 14 is possible.
  • the connection 47 is connected to the outlet 41. Between the connections 47 and 48, the switching symbol for a seat valve is drawn inside the valve 2. In this switching position, no oil passage is possible between the two connections 47 and 48 in both directions, since there is always a lower pressure on the side of the drain 41.
  • the connection 48 is connected to the line 13 of the test system 14 via a check valve 62. Check valve 62 allows oil flow out of test system 14.
  • connection 49 of the valve 3 is connected to the actuation line 1 and it is separated from the connection 50 by an indicated slide valve.
  • the connection 50 is connected to the connection 48 of the valve 2 and at the same time to the test system 14 via the check valve 62.
  • the connection 51 is connected to the outlet 41. In this switching position, the connection between the connections 51 and 52 is blocked by an indicated seat valve.
  • the connection 52 is connected to the line 13 of the test system 14 via a check valve 63.
  • the check valve 63 allows an oil flow out of the test system 14.
  • connection 53 of the valve 4 is connected to the actuation line 1 and it is separated from the connection 54 by an indicated slide valve.
  • the connection 54 is connected to the connection 52 of the valve 3 and at the same time to the test system 14 via the check valve 63.
  • the connection 55 is connected to the outlet 41. In this switching position, the connection between the connections 55 and 56 is blocked by an indicated seat valve.
  • the connection 56 opens before the check valve 61 into the line 60, so that the connection 56 is operatively connected to the test system 14 via this check valve 61.
  • the schematic diagram according to FIG. 2 differs from FIG. 1 only in that the line 10 and the cover 9 are replaced by three lines 70, 71 and 72.
  • the line 70 connects the line 31 to the connection 45 of the valve 2 and at the same time to the actuating line 1.
  • a check valve 73 is installed in the line 70, which allows an oil flow from the line 31 in the direction of the actuating line 1, the amount of the flowing Oil is limited by an aperture 74 also provided in line 70.
  • Line 71 connects the line 32 with the connection 49 of the valve 3 and at the same time with the actuation line 1.
  • a check valve 75 and an orifice 76 are installed in the line 71, so that an oil flow from the line 32 in the direction of the actuation line 1 is possible.
  • the line 72 connects the line 33 to the connection 53 of the valve 4 and at the same time to the actuation line 1.
  • a check valve 77 and an orifice 78 are installed in the line 72, so that an oil flow from the line 33 in the direction of the actuation line 1 is possible.
  • FIG. 3 corresponds to the sketch according to FIG. 2, only the solenoid valves 25, 26, 27 have a second switching position and consequently also the valves 2, 3 and 4 actuated by them.
  • the solenoid valves 25, 26, 27 are here shown in the switch position in which they are pressed by the respective springs 28, 29, 30 when the electrical energy for the magnetic excitation fails or is deactivated.
  • the three lines 31, 32 and 33 are relieved of the oil pressure by the solenoid valves 25, 26, 27 and the line 40 to the outlet 41 and thus the three drive volumes 34, 35, 34 are emptied and the springs 42, 43, 44 press the valves 2, 3, 4 in the switching position shown in Fig. 3.
  • FIG. 4 shows a possible operating state of the device.
  • the valves 3 and 4 are switched as in FIG. 2, the valve 2 is switched analogously to FIG. 3.
  • This position of the valve 2 may have been deliberately created by controlling the energy for the magnetic excitation of the associated solenoid valve 25, as a result of which, as already described, the drive volume 34 is relieved of pressure, with the result that the spring 42 pushes the valve 2 into the presses the switch position shown, but it is also possible that there is a real malfunction which, for example, has interrupted the energy supply.
  • a conscious one The energy would be cut off if, for example, a functional check of the valve 2 is to be carried out.
  • FIG. 5 shows a schematic diagram of the valve 2, the valves 3 and 4 being constructed identically, the switching position being the same as that shown in FIG. 2.
  • the valve 2 is arranged in a cylindrical bore 80 of a hydraulic block, which also includes the valves 3 and 4.
  • the line 31 leads into the cylindrical drive volume 34.
  • the pressure of the oil in the drive volume 34 acts on a piston 81 which is arranged displaceably in the bore 80.
  • the piston 81 is formed in one piece, it has two sealing points, namely a sealing edge 82 which cooperates with an edge 83 of the bore 80 when the piston 81 moves upwards, and a sealing seat 84.
  • the valve 2 accordingly has in the upper part a slide valve with the sealing edge 82 between the connections 45 and 46 and in the lower part it has a seat valve with the sealing seat 84 between the connections 47 and 48.
  • the valve 2 When the valve 2 is opened, i.e. when the piston 81 moves upward, it has an advantageous effect that passing the edge 83 through the sealing edge 82 brings about a valve opening of the slide valve without causing a significant change in volume that occurs in the adjacent volumes and lines could lead to impermissible pressure fluctuations and the resulting incorrect actuation of the drive.
  • the spring 42 is indicated, which pushes the piston 81 upwards into a defined open position after a pressure drop in the drive volume 34.
  • the spring 42 is supported against a support 85.
  • FIG. 1 is considered in more detail.
  • the valves 2, 3, 4 and the solenoid valves 25, 26, 27 work perfectly and the actuating line 1 is under pressure, so that the feed valve is kept open. Trouble-free normal operation is guaranteed.
  • Oil is kept under pressure in the actuation line 1 from the inlet 8 via the line 10.
  • the pressure occurring there is in the range around 160 bar. Sealing of the actuating line 1 against the outlet 41 is ensured, namely two sealing points connected in series are used for this.
  • the first sealing point is always a slide valve, for example between connections 45 and 46 in valve 2, and the second sealing point connected in series, for example between connections 56 and 55 in valve 4, is always a seat valve.
  • the poppet valve must also withstand the full pressure applied by the test system 14.
  • the actuation line 1 is supplied with oil under pressure via the lines 70, 71 and 72.
  • This arrangement has the advantage that no oil is lost in the drain 41 when the oil pressure is raised in this hydraulic device.
  • the lines 70, 71, 72 can advantageously be accommodated inside the valves 2, 3, 4, so that additional lines, screw connections and sealing points are omitted, which increases safety.
  • the other function of the device according to FIG. 2 corresponds to that of the device according to FIG. 1.
  • FIG. 3 shows the so-called "fail safe” position of the device.
  • the solenoid valves 25, 26, 27 and the valves 2, 3, 4 have reached their rest position. In this position, the oil flows under pressure from the actuation line 1 into the outlet 41, both through the line that connects the actuation line 1 to the connection 45 of the valve 2 and through the corresponding lines that lead to the connections 49 or 53 of the valves 3 or 4 and through the second valve seat connected in series.
  • the feed valve closes with great certainty, so that the turbine fed by this feed valve cannot reach an uncontrollable operating state.
  • the check valves 61, 62, 63 the pressure escapes from the test system 14 at the same time, so that the pressure switch 16 also reports to the higher-level system control system that this unit has shut down.
  • the device works properly when all valves 2, 3, 4 and all solenoid valves 25, 26, 27 are fully functional, as previously described. However, it can now happen that a module of this unit fails. In this case, as shown in FIG. 4, proper functioning of the drive is also ensured.
  • the pressure in the actuation line 1 is maintained even after the valve 2 has been shut off, so that the feed valve remains open. Only the pressure in the test system 14 is somewhat reduced by the check valve 62, since the make-up through line 12 is too weak to maintain the full pressure when one of the check valves 61, 62, 63 opens.
  • the pressure switch 16 reports in In this case, a pressure drop in the test system 14, which is to be regarded as an indication of a malfunction in the device. A control of the device and its components is necessary, which leads to the finding of the defective parts and their repair. Continuous, trouble-free operation of the drive is guaranteed during this maintenance period.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
  • Fluid-Driven Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Control Of Fluid Pressure (AREA)
EP90123496A 1989-12-21 1990-12-07 Antrieb für ein Speiseventil Expired - Lifetime EP0433791B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT90123496T ATE104014T1 (de) 1989-12-21 1990-12-07 Antrieb fuer ein speiseventil.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH457489 1989-12-21
CH4574/89 1989-12-21

Publications (2)

Publication Number Publication Date
EP0433791A1 EP0433791A1 (de) 1991-06-26
EP0433791B1 true EP0433791B1 (de) 1994-04-06

Family

ID=4278633

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90123496A Expired - Lifetime EP0433791B1 (de) 1989-12-21 1990-12-07 Antrieb für ein Speiseventil

Country Status (9)

Country Link
US (1) US5143119A (cs)
EP (1) EP0433791B1 (cs)
JP (1) JPH04119272A (cs)
AT (1) ATE104014T1 (cs)
CZ (1) CZ282934B6 (cs)
DE (1) DE59005267D1 (cs)
DK (1) DK0433791T3 (cs)
ES (1) ES2054201T3 (cs)
RU (1) RU1838810C (cs)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59203461D1 (de) * 1991-11-04 1995-10-05 Asea Brown Boveri Speiseschaltung für eine Zweirohr-Hydraulik.
EP0626530B1 (de) * 1993-05-28 1999-03-31 LuK Fahrzeug-Hydraulik GmbH & Co. KG Ventilanordnung
JPH07239054A (ja) * 1994-02-24 1995-09-12 Komatsu Ltd パイロット圧操作型切換弁装置の操作圧検出構造
DE59710054D1 (de) * 1997-11-10 2003-06-12 Alstom Switzerland Ltd Verfahren zur Überwachung des Versorgungssystems einer Gasturbine mit Mehrbrennersystem sowie Vorrichtung zur Durchführung des Verfahrens
GB2332023B (en) * 1997-12-03 2002-07-03 Caterpillar Inc System and method for calibrating an independent metering valve
JP4369292B2 (ja) * 2004-05-06 2009-11-18 タイコ フローコントロールジャパン株式会社 緊急遮断弁装置
US7409965B2 (en) 2006-10-16 2008-08-12 Elliott Company Direct acting hydraulic trip block
CH699602A1 (de) * 2008-09-30 2010-03-31 Alstom Technology Ltd Hydraulische Auslöseeinheit für eine Ventileinheit in einer Kraftmaschinenanlage, insbesondere für ein Schnellschlussventil einer Turbinenanlage.
US8794268B2 (en) * 2010-11-05 2014-08-05 Dresser-Rand Company Voting hydraulic dump system
DE102011104530A1 (de) * 2011-02-04 2012-08-09 Robert Bosch Gmbh Hydraulische Stellanordnung
US9896962B2 (en) * 2014-02-28 2018-02-20 General Electric Company Trip manifold assembly for turbine systems
DE102015210274A1 (de) 2014-06-03 2015-12-03 Voith Patent Gmbh Mehrwegeventil, insbesondere ein 6/2-Wegeventil und Mehrwegeventilanordnung
CN106414907B (zh) 2014-06-03 2019-03-26 福伊特专利有限公司 用于蒸汽涡轮机的速关阀的液压控制装置和蒸汽涡轮设备
CN109322876A (zh) * 2018-09-27 2019-02-12 中船重型装备有限公司 一种盾构机液压油缸及阀组检测设备
KR102212434B1 (ko) * 2020-11-13 2021-02-04 (주)한빛산업 방향제어 유압밸브 및 이를 포함하는 시스템

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1128573A (en) * 1966-07-14 1968-09-25 Stal Laval Turbin Ab Hydraulic system for testing the operation of overspeed monitors
US4001654A (en) * 1975-07-31 1977-01-04 General Electric Company Testable protective system
DE3138561A1 (de) * 1981-09-28 1983-04-21 Siemens AG, 1000 Berlin und 8000 München Auf ihre funktionssicherheit hin pruefbare schutzeinrichtung fuer dampfturbinenanlagen
CH666132A5 (de) * 1984-07-20 1988-06-30 Bbc Brown Boveri & Cie Einrichtung zur ueberwachung von physikalischen groessen an anlagen.
AT400172B (de) * 1988-12-28 1995-10-25 Sgp Va Energie Umwelt Verfahren zum testen und testeinrichtung für dampfturbinen-regelventile

Also Published As

Publication number Publication date
CS633590A3 (en) 1992-04-15
RU1838810C (ru) 1993-08-30
JPH04119272A (ja) 1992-04-20
ES2054201T3 (es) 1994-08-01
EP0433791A1 (de) 1991-06-26
DE59005267D1 (de) 1994-05-11
DK0433791T3 (da) 1995-11-20
ATE104014T1 (de) 1994-04-15
CZ282934B6 (cs) 1997-11-12
US5143119A (en) 1992-09-01

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