EP0604805B1 - Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal - Google Patents

Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal Download PDF

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Publication number
EP0604805B1
EP0604805B1 EP93119920A EP93119920A EP0604805B1 EP 0604805 B1 EP0604805 B1 EP 0604805B1 EP 93119920 A EP93119920 A EP 93119920A EP 93119920 A EP93119920 A EP 93119920A EP 0604805 B1 EP0604805 B1 EP 0604805B1
Authority
EP
European Patent Office
Prior art keywords
piston
oil
pressure
line
actuator
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
EP93119920A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0604805A1 (de
Inventor
Heinz Frey
Kamil Prochazka
Franz Suter
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
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Filing date
Publication date
Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0604805A1 publication Critical patent/EP0604805A1/de
Application granted granted Critical
Publication of EP0604805B1 publication Critical patent/EP0604805B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • 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

Definitions

  • the invention relates to an actuating device for a hydraulic actuator according to the preamble of claim 1.
  • Actuators for hydraulic actuators of conventional design are known, which are equipped with elaborate moving coils.
  • the mechanical components that belong to this actuating device are comparatively difficult and expensive to manufacture
  • Oil is pressurized. When the oil pressure drops, the spring force securely closes the control valve, thereby interrupting the steam supply. This ensures that the Turbine does not get out of control if the pressure of the oil should fail.
  • the oil pressure in a drive volume which acts on the main piston and actuates the control valve via it, is controlled by a simple electrohydraulic converter. When the control valve moves in the opening direction, oil is fed into the drive volume under pressure, but since this movement takes place comparatively slowly, comparatively small cross sections are sufficient for the supply of the oil.
  • control valve must be closed at a speed which is at least ten times higher. This requires a comparatively quick emptying of the drive volume, which however cannot be achieved due to the small cross-sections of the oil supply.
  • drain booster which releases large cross sections for the outflow of the oil after the shutdown.
  • an actuating device for a hydraulic actuator which actuates a control valve.
  • a control loop adjusts the actuator according to a setpoint specified by a higher-level system control system.
  • a plate valve is provided as a drain amplifier, which separates the oil from the Drive volume can flow out very quickly.
  • the plate of the plate valve has at least one opening, which enables the oil to work together under pressure in the spring chamber thereof and the oil in the drive volume of the actuator.
  • the invention seeks to remedy this.
  • the invention as characterized in the independent claims, solves the problem of creating an actuating device for a hydraulic actuator with a pressure-proportional control signal, which can be produced easily and inexpensively.
  • an actuating device for a hydraulic actuator with an amplifier for electrical signals, with at least one electrohydraulic converter connected upstream of the hydraulic actuator, with one provided between the electrohydraulic converter and the actuator hydraulic drain amplifier, to be improved in that a piston-cylinder arrangement acting as a converter is interposed between the actuator and the hydraulic drain amplifier.
  • the piston-cylinder arrangement is combined to form a common assembly with a first plate valve serving as a drain amplifier.
  • a further, particularly space-saving design of the actuating device results when a second plate valve, which is designed as part of the safety oil circuit, is combined with the piston-cylinder arrangement and the first plate valve to form a common assembly.
  • the plate valve which has a plate and a spring acting on it and arranged in a spring chamber, is arranged within the piston provided with openings in the piston-cylinder arrangement.
  • the spring chamber of the first plate valve is permanently connected to a drain for the oil via an adapted orifice.
  • FIG. 1 shows a schematically represented actuating device 1 for a hydraulic actuator 2 with a pressure-proportional control signal. Only one actuator 2 is shown here, but as a rule several actuators 2 are always actuated simultaneously by the actuating device 1.
  • the actuator 2 is hydraulically connected via a line 3 to a piston-cylinder arrangement 4.
  • This piston-cylinder arrangement 4 has a piston 5, which is oil-pressure-actuated between two stops 6, 7 against the force of a spring 8.
  • the piston 5 slides in a cylinder 11, in which two guides 9, 10, which are provided with seals, not shown here, are incorporated.
  • the cylinder 11 also has a buffer volume 12, which is connected by means of openings 13 to a spring chamber 14 on the other side of the piston 5.
  • the buffer volume 12 and the spring chamber 14 are connected via a line 15 provided with a comparatively large cross section to a drain for the oil, not shown here.
  • the buffer volume 12 and the spring chamber 14 are not filled with oil in normal operation.
  • a position indicator 16 connected to the piston 5 is arranged in the buffer volume 12.
  • the line 3 opens into this high-pressure duct 17.
  • Oil under pressure is in the high pressure channel 17 through an aperture 18, which acts as a breakthrough through a plate 19th a plate valve 20 is formed, fed.
  • the plate valve 20 of conventional design separates the high-pressure channel 17 from the buffer volume 12 in the closed state.
  • a spring 21 presses the plate 19 against the seal seats.
  • the plate 19 is guided in the plate valve 20 so that tilting or jamming of the same is excluded.
  • the spring 21 is arranged in a spring chamber 22 filled with oil under pressure.
  • the oil under pressure is fed through a line 23a, which leads to an electrohydraulic converter 24 and a line 23b, which leads the oil under pressure away from the electrohydraulic converter 24 into the spring chamber 22.
  • the pump arrangement for feeding into line 23a, which pressurizes the oil, and any pressure accumulators and pressure switches in this area are not shown here.
  • the spring chamber 22 is connected to the line 25 via a line 27 provided with an orifice 26.
  • An arrow 38 indicates the direction of flow of the oil flowing into the line 23a under pressure.
  • An arrow 39 indicates the direction of flow of the oil flowing through the line 3 into the actuator 2 under pressure.
  • An arrow 40 indicates the direction of flow of the oil flowing through the line 15 into the drain.
  • the spring chamber 22 is also connected via a further plate valve 28 to a line 29 which belongs to the safety oil circuit of the system.
  • this plate valve 28 opens and the pressure prevailing in the spring chamber 22 decreases into the spring chamber 14, whereupon the plate valve 20 also opens, with the result that the actuator 2 moves very quickly into its switch-off position.
  • the oil emerging in the spring chamber 14 and in the buffer volume 12 is always very quickly through the line 15 in the Drainage removed so that the movement of the piston 5 can not be influenced by this oil.
  • a proportional valve 30 with position control can be used as the electro-hydraulic converter 24, as shown in FIG.
  • This embodiment of the proportional valve 30 has, for example, two actuation coils for the electrical and two springs for the mechanical actuation of the valve piston.
  • the proportional valve 30 can assume three operating positions, namely the first one shown in FIG. 1 with energized actuation coils for normal operation, a second one, which is shown in FIG. 2, for the deactivation, and a third one, which is shown in FIG. 3, when it is not necessary to correct the position of the actuator 2, or when the actuation voltage has failed, so that the springs push the valve piston into the central position.
  • the proportional valve 30 is provided with a position indicator 31, the path measurement signals, as indicated by an action line 32, are passed into an amplifier 33 for further processing.
  • Lines of action 34 and 35 extending from the amplifier 33 indicate the electrical supply lines for the actuation coils of the proportional valve 30.
  • the amplifier 33 is also connected to the position indicator 16 of the piston-cylinder arrangement 4, as shown by the line of action 36, so that they too generated path measurement signals for further processing in the amplifier 33.
  • Another line of action 37 indicates the connection between the amplifier 33 and a higher-level system control system.
  • the amplifier 33 can be designed as a pure amplifier.
  • the feeding line 23a is interrupted by the proportional valve 30 and the line 23b is connected to the line 25, so that the oil can flow out of the spring chamber 22 into the outlet.
  • the plate valve 20 opens, so that the oil from the high-pressure channel 17 can flow very quickly, as indicated by the arrows 41, into the buffer volume 12 and further through the line 15 with a large cross section into the drain.
  • This also has the consequence that the piston 5 is pressed by the spring 8 to the left against the stop 6.
  • the oil from the drive volume of the actuator 2 flows simultaneously, as the arrow 42 shows, through the line 3 into the high-pressure channel 17 and from there into the drain.
  • the proportional valve 30 is shown in the operating state with failed operating voltage, in which the springs determine the position of the valve shown. Both the feeding line 23a and the line 23b are blocked by the proportional valve 30. 3 shows the moment immediately after the failure of the actuation voltage. In addition, it is assumed that the safety oil circuit has not yet responded at this moment. The spring chamber 22 is pressurized with oil and this pressure cannot be reduced by the blocked line 23b, so that the actuator 2 is blocked in the position which it had assumed before the actuation voltage failed. Out Such a blockage of the actuator 2 is not permissible for safety reasons, since the turbine, the feed valve of which is regulated by means of this actuator 2, can no longer be switched off.
  • the line 27 with the permanently active diaphragm 26 was provided in order to avoid such extremely critical operating states.
  • this orifice 26 a small amount of oil flows continuously, this amount being continuously replaced by the oil under pressure through line 23b under pressure in normal operation, but in the present operating case, the amount of oil flowing off is sufficient to the pressure in the spring chamber in a useful period 22 to dismantle.
  • the aperture 18, which penetrates the plate 19 the pressure in the high-pressure channel 17 and thus also in the actuator 2 is simultaneously reduced.
  • the actuator 2 is guided directly into the defined switch-off position by this pressure reduction.
  • the undefined operating state can thus be overcome quickly and safely.
  • the safety oil circuit will usually also respond and reduce the pressure in the spring chamber 22. There is therefore a particularly advantageous redundancy of the safety devices.
  • FIG. 4 shows, similar to FIG. 1, a schematically represented actuating device 1 for a hydraulic actuator 2 with a pressure-proportional control signal.
  • the actuator 2 is hydraulically connected via a line 3 to a piston-cylinder arrangement 4.
  • This piston-cylinder arrangement 4 has a piston 5, which is oil-pressure-actuated between two stops 6, 7 against the force of a spring 8.
  • the piston 5 slides in a cylinder 11 in which three guides 9, 10 and 43, which are provided with seals (not shown here), are incorporated.
  • the cylinder 11 also has a buffer volume 12.
  • the buffer volume is 12 Connected via a line 15 having a comparatively large cross section to a drain for the oil, not shown here.
  • the buffer volume 12 is normally not filled with oil.
  • a position indicator 16 connected to the piston 5 is arranged in the buffer volume 12.
  • the line 3 opens into the high-pressure channel 17, the line 23b opens into the high-pressure channel 45.
  • Oil under pressure is fed through bores 46 designed as diaphragms, which run through a plate 47 of a plate valve 44, into a channel 5o provided with a comparatively large cross section.
  • the channel 5o is connected to the high-pressure channel 17.
  • the plate valve 44 arranged here within the piston 5 separates the high-pressure channel 17 and with it the channel 5o from the buffer volume 12.
  • a spring 21 presses the plate 47 against the seal seats.
  • the plate 47 is guided in the plate valve 44 so that tilting or jamming of the same is excluded.
  • the spring 21 is arranged in a spring chamber 22 filled with oil under pressure within the piston 5.
  • the oil under pressure is fed through a line 23a, which leads to an electrohydraulic converter 24 and a line 23b, which leads the oil under pressure away from the electrohydraulic converter 24 into the high-pressure channel 45. From the high-pressure channel 45, the oil reaches the spring chamber 22 through openings 48 in the wall of the piston 5.
  • the pump arrangement for feeding into the line 23a which pressurizes the oil, and any pressure accumulators and pressure monitors in this area are not shown here.
  • a line 25 in this position of the electro-hydraulic Converter 24 is interrupted, leads from this into the buffer volume 12.
  • the spring chamber 22 is permanently connected to the buffer volume 12 via a diaphragm 49, which is embedded as a fine bore in the bottom of the piston 5, and via this to the line 25.
  • the orifice 49 acts exactly the same as the orifice 26 described there.
  • an arrow 38 indicates the direction of flow of the oil flowing into the line 23a under pressure.
  • An arrow 39 indicates the direction of flow of the oil flowing through the line 3 into the actuator 2 under pressure.
  • An arrow 40 indicates the direction of flow of the oil flowing through the line 15 into the drain.
  • the spring chamber 22 is also connected through the openings 48 and via a further plate valve 28 to a line 29 which belongs to the safety oil circuit of the system.
  • this plate valve 28 opens and the pressure prevailing in the spring chamber 22 decreases through the openings 48 into the buffer volume 12, so that the plate valve 44 also opens, with the result that the actuator 2 moves very quickly into it Off position moves.
  • a proportional valve 30 with position control has also been used here as the electrohydraulic converter 24, as has already been shown in FIG.
  • the proportional valve 30 has, for example, two actuation coils for the electrical and two springs for the mechanical actuation of the valve piston, and, as already described, it can assume three operating positions.
  • a sealing edge of the proportional valve 30 which is in use regulates the amount of the through the lines 23a and 23b in the operating position shown in FIG flowing oil under pressure.
  • the proportional valve 30 is provided with a position indicator 31, the path measurement signals, as indicated by an action line 32, are passed into an amplifier 33 for further processing. Lines of action 34 and 35 extending from the amplifier 33 indicate the electrical supply lines for the actuation coils of the proportional valve 30.
  • the amplifier 33 is also connected to the position indicator 16 of the piston-cylinder arrangement 4, as shown by the line of action 36, so that they too generated path measurement signals for further processing in the amplifier 33.
  • Another line of action 37 indicates the connection between the amplifier 33 and a higher-level system control system.
  • the amplifier 33 can be designed as a pure amplifier. However, it often proves to be very useful to provide certain elements acting as regulators in the amplifier 33 itself, in order to achieve particularly fast signal processing and thus high dynamics of the actuating device 1.
  • the feeding line 23a is interrupted by the proportional valve 30 and the line 23b is connected to the line 25, so that the oil can flow out of the spring chamber 22 into the outlet.
  • the plate valve 44 opens, so that the oil from the high-pressure channel 17, as indicated by the arrows 41, can flow through the channel 50 into the buffer volume 12 and further through the line 15 into the drain.
  • the piston 5 is pressed by the spring 8 to the right against the stop 7.
  • the oil from the drive volume of the actuator 2 flows simultaneously, as the arrow 42 shows, through the line 3 into the high-pressure channel 17 and from there into the outlet, so that the actuator 2 moves quickly into its switch-off position.
  • FIG. 1 a volume flow consisting of oil under pressure is regulated by the electro-hydraulic converter 24.
  • This volume flow is converted into a pressure signal by the piston-cylinder arrangement 4, which serves as a converter.
  • This pressure signal acts in the high pressure channel 17 and holds the piston 5 against the force of the spring 8 in the position shown.
  • the position indicator 16 connected to the piston 5 reports this position of the piston 5 to a controller, which compares it with a setpoint specified by the higher-level system control system and which initiates any necessary corrections via the amplifier 33 and the electro-hydraulic converter 24.
  • Each correction has the effect of a change in the volume flow through the electro-hydraulic converter 24 and is converted into a corresponding pressure in the piston-cylinder arrangement 4.
  • This pressure which is effective in the high-pressure duct 17, acts on the actuator 2 or several actuators 2 and determines their stroke. This pressure can be increased if the actuator 2 is to open the feed valve for the turbine which it actuates. For this purpose, the excitation of the actuation coils of the proportional valve 30 is changed so that the control edge in engagement releases a larger cross section for the oil flowing through.
  • the measurement signals of the position indicator 16 are monitored and compared with predetermined target values, so that any incorrect deviation from known values is immediately recognized.
  • a certain cross-sectional change in the proportional valve 30 therefore corresponds to a certain pressure change speed and also a certain running speed of the piston 5 and the actuator 2.
  • the piston-cylinder arrangement 4 acts as a converter. The direct measurement of the position of the piston 5 and Integrating these measurement signals into the control process, which is controlled by the higher-level plant control system, prevents instabilities in this area with great certainty.
  • the somewhat more economical embodiment of the actuating device according to FIG. 4 also has the essential advantages of the embodiment described here.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)
  • Injection Moulding Of Plastics Or The Like (AREA)
  • Valve Device For Special Equipments (AREA)
EP93119920A 1992-12-28 1993-12-10 Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal Expired - Lifetime EP0604805B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4244304A DE4244304A1 (de) 1992-12-28 1992-12-28 Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal
DE4244304 1992-12-28

Publications (2)

Publication Number Publication Date
EP0604805A1 EP0604805A1 (de) 1994-07-06
EP0604805B1 true EP0604805B1 (de) 1996-02-28

Family

ID=6476690

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93119920A Expired - Lifetime EP0604805B1 (de) 1992-12-28 1993-12-10 Betätigungsvorrichtung für einen hydraulischen Stellantrieb mit druckproportionalem Stellsignal

Country Status (14)

Country Link
US (1) US5435227A (pl)
EP (1) EP0604805B1 (pl)
JP (1) JPH06280816A (pl)
KR (1) KR940015297A (pl)
CN (1) CN1031218C (pl)
CA (1) CA2112002A1 (pl)
CZ (1) CZ282082B6 (pl)
DE (2) DE4244304A1 (pl)
DK (1) DK0604805T3 (pl)
ES (1) ES2086179T3 (pl)
FI (1) FI935882A (pl)
HU (1) HU214887B (pl)
PL (1) PL172596B1 (pl)
SK (1) SK148593A3 (pl)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2101576T3 (es) * 1993-10-29 1997-07-01 Siemens Ag Servomotor, especialmente para una valvula de cierre rapido.
DE4414779C1 (de) * 1994-04-25 1995-11-02 Mannesmann Ag Multifunktionsventil
DE102009009852B4 (de) 2009-02-20 2023-07-06 General Electric Technology Gmbh Plattenablaufventil, insbesondere zum Beeinflussen des Ansteuerdrucks eines Regelventils
CN102518485A (zh) * 2011-12-13 2012-06-27 中广核工程有限公司 核电站汽轮机跳闸回油系统
EP3088683B1 (en) * 2015-04-30 2020-07-29 General Electric Technology GmbH Improved high-flow valve arrangement in steam turbine safety system
DE102017131004A1 (de) * 2017-12-21 2019-06-27 Moog Gmbh Stellantrieb mit hydraulischem Abflussverstärker
CN108953738B (zh) * 2018-07-12 2019-10-29 温州大学激光与光电智能制造研究院 双阀体装置系统的控制方法

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1263432B (de) * 1963-07-03 1968-03-14 Participations Eau Soc Et Druckmittelbetaetigtes Ventil insbesondere fuer Gasturbinenanlagen
DE1284236B (de) * 1965-08-03 1968-11-28 Maschf Augsburg Nuernberg Ag Hydraulische Einrichtung zur Beschleunigung des Schliessvorganges von Stellantrieben
US4274438A (en) * 1979-02-21 1981-06-23 Westinghouse Electric Corp. Method of diagnostic valve testing
DE3124904A1 (de) * 1980-07-04 1982-05-06 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid "stromventil mit einem hydraulisch verstellbaren drosselventil"
US4852850A (en) * 1987-05-14 1989-08-01 Westinghouse Electric Corp. Valve system with adjustable seating force
US4585205A (en) * 1984-06-13 1986-04-29 General Electric Company Fast opening valve apparatus
DE3532592A1 (de) * 1985-09-12 1987-03-19 Rexroth Mannesmann Gmbh 3-wege-druckminderventil mit sekundaerdruckueberwachung
EP0308762B1 (de) * 1987-09-24 1992-05-13 Siemens Aktiengesellschaft Einrichtung zum Regeln der Lage eines hydraulischen Vorschubantriebs, insbesondere einer hydraulischen Presse oder Stanze
DE3803268A1 (de) * 1988-02-04 1989-04-13 Bosch Gmbh Robert Messeinrichtung fuer einen arbeitszylinder
US5137253A (en) * 1989-12-01 1992-08-11 Asea Brown Boveri Ltd. Actuator
CH681380A5 (pl) * 1990-04-09 1993-03-15 Asea Brown Boveri
DE4030107A1 (de) * 1990-09-22 1992-03-26 Steag Ag Hydraulischer stellantrieb fuer steuer- und regelarmaturen

Also Published As

Publication number Publication date
CZ280593A3 (en) 1994-07-13
KR940015297A (ko) 1994-07-20
SK148593A3 (en) 1994-07-06
ES2086179T3 (es) 1996-06-16
CN1091500A (zh) 1994-08-31
HU9303764D0 (en) 1994-04-28
JPH06280816A (ja) 1994-10-07
PL301621A1 (en) 1994-07-11
DK0604805T3 (da) 1996-07-22
CZ282082B6 (cs) 1997-05-14
CA2112002A1 (en) 1994-06-29
FI935882A (fi) 1994-06-29
PL172596B1 (pl) 1997-10-31
HUT66418A (en) 1994-11-28
US5435227A (en) 1995-07-25
EP0604805A1 (de) 1994-07-06
HU214887B (hu) 1998-07-28
FI935882A0 (fi) 1993-12-27
CN1031218C (zh) 1996-03-06
DE59301731D1 (de) 1996-04-04
DE4244304A1 (de) 1994-06-30

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