EP3353385B1 - Turbine mit schnellschluss- und regelventilen - Google Patents

Turbine mit schnellschluss- und regelventilen Download PDF

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Publication number
EP3353385B1
EP3353385B1 EP16778768.8A EP16778768A EP3353385B1 EP 3353385 B1 EP3353385 B1 EP 3353385B1 EP 16778768 A EP16778768 A EP 16778768A EP 3353385 B1 EP3353385 B1 EP 3353385B1
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EP
European Patent Office
Prior art keywords
turbine
quick
valves
pneumatic
control
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.)
Active
Application number
EP16778768.8A
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German (de)
English (en)
French (fr)
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EP3353385A1 (de
Inventor
Michael MAHALEK
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.)
Siemens AG
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Siemens AG
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 Siemens AG filed Critical Siemens AG
Priority to PL16778768T priority Critical patent/PL3353385T3/pl
Publication of EP3353385A1 publication Critical patent/EP3353385A1/de
Application granted granted Critical
Publication of EP3353385B1 publication Critical patent/EP3353385B1/de
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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
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/80—Repairing, retrofitting or upgrading methods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/40—Transmission of power
    • F05D2260/406—Transmission of power through hydraulic systems

Definitions

  • the present invention relates to a turbine with a turbine control, a turbine protection, at least one safety block, quick-closing valves and control valves, wherein the quick-closing valves and the control valves via associated switching and actuators can be actuated. Furthermore, the present invention relates to a method for retrofitting an existing turbine having a turbine protection, a turbine control, a hydraulic safety block, quick-closing valves and control valves, wherein the hydraulic quick-closing valves are actuated via associated hydraulic actuators.
  • Turbines of the type mentioned are known in the art in a variety of configurations.
  • the turbine control is known to take over functions such as power control, pressure control, speed control, valve position control, measurement processing, etc., to name just a few examples.
  • the turbine guard detects any process criteria that may adversely affect the turbine or the operator, and shuts down the turbine as soon as appropriate limits are exceeded.
  • the quick-closing and control valves are responsible for the supply, control and shut-off of the working fluid to the steam turbine during operation.
  • the "open and close" functions of quick-acting valves and “open, close and close” of control valves are primarily controlled by hydraulic actuators via a central hydraulic safety block and the turbine control, which in turn feeds into the turbine's control and regulating oil system are involved.
  • Control valves can basically be divided into two groups, namely in pressure relief valves with design-related permeability and low actuating forces, such as unloaded pipe valves without advance, single-seat valves with preheating or double seat valves, and in non-pressure-relieved but completely tight seat valves with high restoring forces, such as Thumb or mushroom valves, pre-stroke valves or pipe valves with forward stroke.
  • the relieved control valves usually come with low-pressure hydraulics from 8 to 12 bar.
  • Unloaded control valves require a medium-pressure hydraulics of 30 to 50 bar or a high-pressure hydraulics of 100 to 160 bar, depending on the pressure of the working fluid.
  • EP1026368 discloses a steam turbine wherein the live steam is supplied via hydraulically driven quick-closing valves and control valves.
  • DE 1946968 U discloses a pneumatic actuator with a spring-loaded diaphragm or a spring-loaded piston, characterized in that the actuating rod protrudes at both ends of the actuator and in this way, both pressure forces and tensile forces can be generated without changing the actuator.
  • EP2110592 A2 discloses a drive with an electric motor such as a permanent-magnet synchronous motor and a linear unit with a piston rod which is guided in a movement thread of a movement threaded nut and formed as a spindle.
  • EP 2620655 A1 discloses a drive system having a fluid flow source for generating pneumatic or hydraulic forces to drive the valve portion of the valve.
  • US 3556463 A relates to a shut-off valve for controlling the supply of a pressure medium in a medium receiving device.
  • a major disadvantage of turbines of the type described above is that the control and regulating oil system is very costly in terms of planning, purchase, installation, testing, commissioning and maintenance.
  • oil leaks especially at the hot front end of the turbine, a high risk of fire, which is associated with a corresponding risk to the turbine itself and the operating personnel.
  • the present invention provides a turbine of the type mentioned, which is characterized in that it is at least one safety block to a pneumatic safety block, and that at least one switching drive for direct or indirect actuation of a quick-closing valve is a pneumatic switching drive ,
  • direct operation is meant that the pneumatic switching drive acts directly on the valve stem of the quick-acting valve.
  • the pneumatic switching drive can form, for example, a component of a control device of a medium-operated quick-acting valve.
  • pneumatic shift actuators compared to hydraulic actuators represent a simple, robust and cost-effective alternative.
  • pneumatic actuators are very reliable, have only one Low wear and can be easily integrated into the turbine protection. Accordingly, associated with the use of pneumatic actuators low costs.
  • all the switching drives for actuating the quick-acting valves are pneumatic switching drives. In this way, the advantages described above are used optimally.
  • the turbine protection and the at least one pneumatic safety block are designed and set up in such a way that they are used to control the pneumatic switching drive or the pneumatic switching drives.
  • the control of the pneumatic shift actuators is easily integrated into the existing turbine protection, which also leads to a cost-effective design.
  • the pneumatic safety block advantageously has a plurality of series-connected 5/2 way valves, in particular three 5/2 way valves in 2 of 3 circuit.
  • the functions "opening, closing, venting and testing" can be realized without problems.
  • the main advantage associated with three 5/2 directional valves connected in series is that safe operation of the turbine is possible even if one of the directional control valves should fail. Accordingly, downtimes of the turbine are avoided in the event of failure of one of the directional control valves. In principle, it is of course also possible to use 3/2 way valves.
  • electric actuators and / or hydraulic actuators with self-sufficient oil supply are provided for actuating the control valves, which are operated in particular with a flame-retardant liquid.
  • Electric actuators can be used instead of hydraulic actuators especially when it comes to the control valves to be operated is relieved control valves.
  • Hydraulic actuators with self-sufficient oil supply are used in particular in non-pressure relieved control valves. If all the control valves are replaced by electric actuators and / or hydraulic actuators with self-sufficient oil supply, so can be dispensed with a central control and regulating oil system entirely, which is associated with a significant cost savings. It would then remain only the lubricating oil system, which is normally operated at about 2 bar. If the hydraulic actuators are operated with a self-sufficient oil supply with a flame retardant fluid, so the risk of fire is reduced to a minimum.
  • the present invention also proposes a method for retrofitting an existing turbine, which has a turbine protection, a turbine control, a hydraulic safety block, quick-closing valves and control valves, the quick-closing valves are directly or indirectly actuated via associated hydraulic actuators.
  • the retrofitting method according to the invention is characterized in that at least one hydraulic switching drive of a quick-acting valve is replaced by a pneumatic switching drive, and that a pneumatic safety block is provided which at least partially replaces the functions of the hydraulic safety block.
  • all hydraulic shift drives are preferably replaced by pneumatic shift drives, which is accompanied by the advantages described above.
  • control is modified such that the at least one pneumatic switching drive is controlled via the turbine protection and the pneumatic safety block, which is accompanied by a very simple and inexpensive construction.
  • At least one hydraulic actuator is replaced by an electric actuator.
  • At least one hydraulic actuator which is connected to a central control and regulating oil system of the turbine, replaced by a hydraulic actuator with self-sufficient oil supply.
  • the turbine control is modified such that the at least one electric actuator and / or the at least one hydraulic actuator is controlled with autonomous oil supply via the turbine protection and the turbine control.
  • FIG. 1 schematically shows a turbine 1, which in the present case is a steam turbine.
  • the turbine 1 includes in a known manner a turbine control 2 and a turbine protection 3.
  • the turbine control 2 takes over functions such as power control, pressure control, speed control, valve position control, measured value preparation, etc., to name but a few examples.
  • the turbine protection 3 detects all process criteria that can have a negative effect on the turbine 1 or on the operating personnel, and shuts off the turbine 1 as soon as corresponding limit values are exceeded.
  • the turbine 1 has a number of valve groups, of which in FIG. 1 an example of a high-pressure valve group 4 is shown.
  • the high-pressure valve group 4 comprises a quick-closing valve 5 and three control valves 6, which are responsible for supplying, regulating and shutting off the live steam, which flows in the direction of the arrows 7 through a live steam path 9 formed in a housing 8 in the direction of the high-pressure stage during turbine operation.
  • the quick-acting valve is a medium-actuated quick-acting valve whose pilot control cone 10 and main cone 11 are moved into the "open” or "closed” positions as a function of the switching position of a control unit 12 via the live steam.
  • control lines 13 and 14 are provided which connect the quick-release valve 5 to the control unit 12.
  • the control unit 12 comprises a pneumatic switching drive 15, which in the present case is designed as a membrane drive.
  • the switching drive 15 comprises a switching drive housing 16, which is provided with an air connection 17 and is divided in the interior via a membrane 18 into two chambers 19 and 20, wherein the membrane 18 by return springs 21, which are arranged in the chamber 19 without compressed air connection 17 are held in a starting position.
  • a spindle 22 is fixed, which is connected by means of a spindle coupling 23 with the valve spindle 24 of the control unit 12 and seals opposite valve seats 25a and 25b according to the switching position.
  • the live steam is released via the control line 14 to the control line 13 and ultimately acts on the main cone 11 of the quick-closing valve 5, which assumes the "closed" position.
  • the outlet 26 to the atmosphere or leakage steam line is closed. If the chamber 20, starting from the in FIG. 2 Compressed air is applied to the initial position shown, the valve spindle 24 is moved via the diaphragm 18 with the spindle 22 from the valve seat 25 a to the valve seat 25 b until it is sealed, the control line 14 closes and in this way the outlet 26 as well as a control channel 27 of the quick-closing valve 5 is opened to the atmosphere.
  • the pressure of the live steam keeps the pilot poppet 10 via the inlet bores 33 and the main poppet 11, respectively counter to the force of a spring 34, in the open position, both in the rear end position the passage of the live steam into the cylinder chamber 28 and in the control line 13 without leakage Shut off. Accordingly, the live steam can flow via an inlet screen 35 to the downstream control valves 6.
  • the triggering of the quick-closing valve 5 takes place by relieving the air pressure at the control unit. Accordingly, the chamber 20 of the switching drive 15 is not pressurized with compressed air.
  • the control line 13 is closed to the atmosphere by the valve stem 24 is pressed by the spring force of the return springs 21 via the spindle 22 with spindle clutch 23 on the valve seat 25b and subjected to the live steam pressure.
  • the cylinder chamber 28 is via the control line 13, the control channel 27 and the inflow bore 33 also pressurized.
  • the pilot poppet 10 thus receives a compressive force against the opening force, with the steam forces on the pilot poppet 10 compensate and this goes through the force of the spring 34 in the closed position.
  • the cylinder chamber 28 is acted upon via the inlet bores 33, an open control channel 36 and bores 37 and via the adjustable throttle 29 and the gap surface 30 with the pressure of the live steam.
  • the main cone 11 thus receives an opening force opposing pressure force.
  • the compressive forces on the main cone 11 are equalized, whereby it is closed by the force of the spring 34 and pressed against the associated valve seat.
  • FIGS. 3 to 8 show various functional positions of a pneumatic safety block 38 which is connected to the turbine protection 3 and designed to control the pneumatic switching drive 15 of the controller 12 of the quick-closing valve 5.
  • the safety block 38 comprises three identically constructed, electromagnetically actuated 5/2 directional control valves V1, V2 and V3 with spring return, which are arranged in series in 2 of 3 circuit, two pressure ports P1 and P2, a test port P3 and one with the compressed air port 17 of the switching drive 15 of the quick-closing valve 5 connected pressure output E1.
  • control valves 6 are double-seat control valves, each having two main cones 39 connected to one another, to which corresponding valve seats formed on the housing 8 are assigned.
  • the main cone 39 of the in FIG. 1 arranged rightmost control valve 6 are coupled to a spindle of an electric actuator 41, which in turn is connected to the turbine control 2 and the turbine protection 3, so that the main cone 39 moves under actuation of the actuator either in a closed position or in a fully or partially open position can be.
  • the main cones 39 of the other two control valves 6 are in turn transferred via the connected to the actuator 41 control valve in its fully or partially open position.
  • each return springs 42 are provided to move the main cone 39 in its closed position.
  • a hydraulic actuator with self-sufficient oil supply can be provided, which is advantageously operated with a flame-retardant liquid, even if this is not shown here.
  • Such hydraulic actuators with self-sufficient oil supply are known in the art, Therefore, a more detailed explanation is omitted here.
  • the quick-closing valve 5 is controlled via the turbine guard 3 and the pneumatic safety block 38, and the control valves 6 are controlled via the turbine control 2 and the turbine guard. Accordingly, it is possible to dispense with a central control and regulating oil system, which entails a great cost reduction as well as a minimization of the risk of fire arising from such a control and regulating oil system in the event of a leak. This also applies if instead of the electric actuator 41, a hydraulic actuator is used with self-sufficient oil supply.
  • the present invention is not limited to such a high pressure valve group. Rather, according to the invention are all switching and actuators of quick-closing and control valves of the turbine 1, but at least all switching and actuators of Schnell gleich- and control valves at positions with high risk potential, in particular at the hot front end of the turbine 1, in the manner described above executed. Furthermore, it should be clear that this also applies to such quick-closing and control valves, which have a different structure than the valves 5 and 6 shown. Even if in FIG.
  • a quick-closing valve As an example of a quick-closing valve, a medium-operated quick-acting valve is shown, it should also be noted that directly operated quick-acting valves can be equipped with a pneumatic switching drive of the type described above. In such directly operated quick-acting valves, the pneumatic switching drive then acts directly on the spindle of the quick-acting valve. Depending on the quick-closing valve type, the direction of action of the switching drive can be retracted or extended in the unpressurized state with the spindle.
  • a structural design of a quick-closing valve 5 with extended spindle, in which it in the present case is a single seat quick-release pre-stroke shows FIG. 9 ,
  • the switching drive 15 is a diaphragm drive as already described and consists of a switching drive housing 16, which is provided with an air connection 17 and is divided in the interior via a membrane 18 into two chambers 19 and 20, wherein the membrane 18 by the return springs 21, which in the chamber 19 are arranged without compressed air connection 17, is held in a starting position.
  • a spindle 22 On the spring-loaded diaphragm 18, a spindle 22 is attached, which is connected by means of a spindle clutch 23 with the Vorhubspindel 43 and the main cone 44 presses in a valve seat 47 and seals in the "closed” position. If now the quick-closing valve 5 is subjected to live steam pressure in a chamber 48, this position "valve closed” will continue to exist.
  • the Vorhubspindel 43 is moved via the diaphragm 18 with spindle 22 from the valve seat 51 in the interior of the main cone 44 and the steam flow through a bore 52 of the main cone 44 to a space 49 in front of the closed Control valves released. After this space 49 has filled with steam and has reached about 75-80% of the live steam pressure, the main cone 44 lifts off from the valve seat 47 and moves to the cover 45 until it has reached the end position "valve open". The steam flow can now flow through a steam strainer 50 to the downstream control valves.
  • the triggering of the quick-closing valve 5 is carried out by relieving the air pressure on the switching drive 15. Accordingly the air flow into the chamber 20 of the switching drive 15 is interrupted and switched to the atmosphere. Thereby, the steam force is overcome in the opening direction of the Vorhubspindel 43 with the main cone 44 by the spring force of the return springs 21 via the spindle 22 with spindle clutch 23 and moves in the closing direction until the valve seat 47 is again vapor-tight. Thus, the starting position "valve closed” is reached again and acted on the Vorhubventil with live steam pressure.
  • the partial stroke test of the quick-action valve 5 can, similar to the hydraulic drive, be realized by opening an additional solenoid valve in the supply air line. In the chamber 20, the pressure is slowly lowered until the Vorhubventil moves under the spring force of the return springs 21 from the end position in the direction "close". A position change of 15-20% is sufficient for the partial stroke test.
  • the present invention proposes to convert an existing turbine comprising a turbine protection, a turbine control, a hydraulic safety block, quick-acting valves and control valves, wherein the quick-acting valves can be actuated via assigned hydraulic switching drives, such that the hydraulic switching drives of the quick-acting valves at least partially but preferably be completely replaced by pneumatic switching actuators, and that a pneumatic safety block is provided which replaces the functions of the hydraulic safety block at least partially.
  • hydraulic actuators of control valves of the existing turbine are preferably replaced by electric actuators and / or by hydraulic actuators with self-sufficient oil supply, so that it is possible to dispense with the entire control and regulating oil system of the existing turbine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
EP16778768.8A 2015-10-30 2016-10-04 Turbine mit schnellschluss- und regelventilen Active EP3353385B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL16778768T PL3353385T3 (pl) 2015-10-30 2016-10-04 Turbina z zaworami szybkozamykającymi i zaworami regulacyjnymi

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015221311.0A DE102015221311A1 (de) 2015-10-30 2015-10-30 Turbine mit Schnellschluss- und Regelventilen
PCT/EP2016/073604 WO2017071912A1 (de) 2015-10-30 2016-10-04 Turbine mit schnellschluss- und regelventilen

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Publication Number Publication Date
EP3353385A1 EP3353385A1 (de) 2018-08-01
EP3353385B1 true EP3353385B1 (de) 2019-11-27

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EP16778768.8A Active EP3353385B1 (de) 2015-10-30 2016-10-04 Turbine mit schnellschluss- und regelventilen

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US (1) US10900375B2 (zh)
EP (1) EP3353385B1 (zh)
CN (1) CN108350750B (zh)
DE (1) DE102015221311A1 (zh)
PL (1) PL3353385T3 (zh)
WO (1) WO2017071912A1 (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3489470A1 (en) * 2017-11-22 2019-05-29 Siemens Aktiengesellschaft Turbine control system for a steam turbine and steam turbine
JP7417511B2 (ja) * 2020-12-16 2024-01-18 三菱重工コンプレッサ株式会社 弁装置及び蒸気タービン
CN114352360B (zh) * 2022-01-13 2024-09-20 中国长江动力集团有限公司 交直流保安操纵箱

Citations (1)

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Publication number Priority date Publication date Assignee Title
EP1026368A1 (de) * 1999-02-04 2000-08-09 Asea Brown Boveri AG Dampfturbine

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US3556463A (en) 1968-10-08 1971-01-19 Worthington Corp Trip valve system
EP0127027B1 (de) * 1983-05-30 1988-03-09 BBC Brown Boveri AG Elektrohydraulischer Stellantrieb für Turbinenventile
US4534702A (en) 1983-12-27 1985-08-13 United Technologies Corporation Pneumatic control valve actuator computer control arrangement
DE4446605A1 (de) * 1994-12-24 1996-06-27 Abb Patent Gmbh Ventil für eine Dampfturbine
DE102006040953B4 (de) 2006-08-31 2008-06-12 Armaturen-Wolff Friedrich H. Wolff Gmbh & Co. Kg Anordnung zur elektrischen Auslösung von mechanisch betätigbaren Schnellschlußventilen
DE102008019182A1 (de) 2008-04-17 2009-10-22 Voith Patent Gmbh Elektromechanischer Antrieb zur Betätigung von Ventilen
DE102008031317A1 (de) 2008-07-02 2010-01-07 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Kompressorsystem mit beschränktem Ansaugladedruck
US8794268B2 (en) * 2010-11-05 2014-08-05 Dresser-Rand Company Voting hydraulic dump system
CN103370546B (zh) * 2010-11-08 2018-06-26 罗伯特·博世有限公司 用于对具有调节或分配阀的阀门进行操纵的液压或气动的驱动装置
DE202011109158U1 (de) * 2011-12-15 2012-01-24 Karl Morgenbesser Elektrohydraulische Sicherheitssteuerung
EP2620655A1 (de) * 2012-01-30 2013-07-31 Siemens Aktiengesellschaft Antriebssystem für ein Ventil
US10119478B2 (en) * 2015-06-25 2018-11-06 Woodward, Inc. High reliability high flow redundant trip block
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EP1026368A1 (de) * 1999-02-04 2000-08-09 Asea Brown Boveri AG Dampfturbine

Also Published As

Publication number Publication date
US10900375B2 (en) 2021-01-26
BR112018007205A8 (pt) 2023-04-11
US20180306051A1 (en) 2018-10-25
DE102015221311A1 (de) 2017-05-04
PL3353385T3 (pl) 2020-06-01
CN108350750A (zh) 2018-07-31
BR112018007205A2 (pt) 2018-10-16
WO2017071912A1 (de) 2017-05-04
CN108350750B (zh) 2020-08-07
EP3353385A1 (de) 2018-08-01

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