EP3353385A1 - Turbine mit schnellschluss- und regelventilen - Google Patents
Turbine mit schnellschluss- und regelventilenInfo
- Publication number
- EP3353385A1 EP3353385A1 EP16778768.8A EP16778768A EP3353385A1 EP 3353385 A1 EP3353385 A1 EP 3353385A1 EP 16778768 A EP16778768 A EP 16778768A EP 3353385 A1 EP3353385 A1 EP 3353385A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- turbine
- valves
- control
- quick
- pneumatic
- 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
- 230000001105 regulatory effect Effects 0.000 title abstract description 14
- 238000000034 method Methods 0.000 claims abstract description 14
- 238000009420 retrofitting Methods 0.000 claims abstract description 5
- RNFJDJUURJAICM-UHFFFAOYSA-N 2,2,4,4,6,6-hexaphenoxy-1,3,5-triaza-2$l^{5},4$l^{5},6$l^{5}-triphosphacyclohexa-1,3,5-triene Chemical compound N=1P(OC=2C=CC=CC=2)(OC=2C=CC=CC=2)=NP(OC=2C=CC=CC=2)(OC=2C=CC=CC=2)=NP=1(OC=1C=CC=CC=1)OC1=CC=CC=C1 RNFJDJUURJAICM-UHFFFAOYSA-N 0.000 claims description 4
- 239000003063 flame retardant Substances 0.000 claims description 4
- 239000007788 liquid Substances 0.000 claims description 3
- 230000001012 protector Effects 0.000 claims 1
- 239000003921 oil Substances 0.000 description 18
- 238000012360 testing method Methods 0.000 description 7
- 230000008901 benefit Effects 0.000 description 5
- 239000012528 membrane Substances 0.000 description 5
- 238000013461 design Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 210000003171 tumor-infiltrating lymphocyte Anatomy 0.000 description 2
- 235000001674 Agaricus brunnescens Nutrition 0.000 description 1
- 235000008694 Humulus lupulus Nutrition 0.000 description 1
- 244000025221 Humulus lupulus Species 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 210000004072 lung Anatomy 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 230000035699 permeability Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 210000003813 thumb Anatomy 0.000 description 1
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, the quick-acting valves and the control valves can be actuated to ⁇ orderly switching and actuators.
- the present invention relates to a method for retrofitting an existing turbine, which has a turbine protection, turbine control, a hydraulic safety block, quick-closing valves and control valves, wherein the hydraulic quick-closing valves can be actuated via associated hydrau ⁇ lic shift actuators.
- Turbines of the type mentioned are known in the art in a variety of configurations. As is known, among other things, the turbine control takes over functions such as power control, pressure control, speed control, valve position control, measured value preparation, etc., just to a few
- the turbine protection covers all process ⁇ criteria, which may adversely affect the turbine or the Be ⁇ serving staff, and shuts down the turbine when appropriate limits are exceeded.
- the quick-and control valves are responsible for the control ⁇ operation for the supply, control and shut off the working fluid to the steam turbine.
- the function ⁇ ones "opening and closing" with quick-closing valves, and “opening, regulating and closing” for control valves primarily using hydraulic switching and actuators via a central hydraulic safety block and turbine control are controlled, in turn, in the control and regulating oil system the turbine are involved.
- Quick-acting valves typically use Vorsteue ⁇ tion, which is why not too large valve forces to deal with.
- the quick-acting valves do not provide any decisive components in the selection of the Oil systems usually come with low-pressure oil systems from 8 to 12 bar.
- Control valves can basically be divided into two groups, namely in pressure-relieved valves with design-related permeability and low actuating forces, such as unloaded pipe valves without advance, Einsitzven ⁇ tile with preheating or double seat valves, and in non-pressure-relieved but completely tight seat valves with high restoring forces, such as For example, thumb or mushroom valves, Vorhubventile or pipe valves with Vorhub.
- the Release part ⁇ ended control valves usually come with Niederbuchhydrau ⁇ lik 8-12 bar from.
- Unbalanced control valves Benö ⁇ term in dependence on the pressure of the working fluid a co teldruckhydraulik of 30 to 50 bar or a high-pressure hydraulics of 100 to 160 bar.
- 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.
- the present invention provides a turbine of the type mentioned, which is marked ⁇ characterized in that it is the at least one safety block is a pneumatic safety block, and that at least one switching drive for direct or indi ⁇ rect actuation a quick closing valve is a pneumati ⁇ shear switching drive.
- 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 switching drive instead of a hydraulic switching drive for switching a quick-acting valve, which is arranged for example in the region of the hot front end of the turbine, the risk of fire can be significantly reduced. As a result, high security for the turbine itself and the operating personnel is achieved. In addition, insurance costs can be reduced.
- pneumatic switching drives represent a simple, robust and cost-effective alternative to hydraulic switching drives .
- pneumatic actuators are very reliable, have little 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 and protection of the at least one pneumatic safety block are preferably constructed and introduced rich ⁇ tet that this drive control of the pneumatic switching or the pneumatic circuit drives takes place.
- 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. In such a structure of the pneumatic safety block can be the 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.
- Entspre ⁇ accordingly downtimes of the turbine to be avoided in the event of a failure of one of the directional valves.
- electric actuators and / or hydraulic actuators with independent oil supply see that operate in particular with a flame-retardant liquid.
- Electric actuators can be used instead of hydraulic actuators especially used when it is in the actuated control valves to balanced control valves.
- hydraulic actuators with independent ⁇ lve In contrast, they are used in particular for non-pressure relieved control valves.
- control valves are replaced by electric actuators ⁇ and / or by hydraulic actuators with autar ⁇ ker oil supply, it can be completely dispensed with a central control and regulating oil system, which is associated with a significant cost savings. It would then only borrow the lube oil system remain, 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 vorlie ⁇ ing 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 via associated hydraulic switching drives directly or indirectly actuated.
- the retrofitting method according to the invention is characterized in that at least a hydraulic switching actuator of a quick-closing 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 switching drives are preferably replaced by pneumatic switching drives, which is accompanied by the advantages described above.
- the control is modified such advantageous that the at least one pneumatic shift drive is controlled by the turbine ⁇ protection and the pneumatic safety block, which is associated with 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 with autonomous ⁇ lver ⁇ supply via the turbine protection and the turbine control is controlled.
- Figure 1 is a schematic view of a high-pressure Ven ⁇ tilzan a turbine according to an exporting ⁇ approximate shape of the present invention
- Figure 2 is a schematic view showing a controller of a medium-operated quick-acting valve of the high-pressure valve group shown in Figure 1;
- Figures 3-8 are schematic views showing a pneumati ⁇ 's security block in different operating positions.
- Figure 9 is a schematic view showing another
- FIG. 1 schematically shows a turbine 1, which in the present case is a steam turbine.
- the turbine 1 um ⁇ sums in a known manner a turbine control 2 and a turbine protection 3.
- the turbine control 2 assumes 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, which may adversely affect the turbine 1 or for the operating personnel, and switches the turbine 1 from be exceeded when corresponding limit values ⁇ .
- the turbine 1 has a number of valve groups, of which a high-pressure valve group 4 is shown by way of example in FIG.
- the Hochdruckventil- group 4 herein comprises a quick-closing valve 5, and three control valves 6, which are responsible for the supply, control, fences ⁇ tion of the live steam, the inside during Turbi ⁇ nen worriess in the direction of arrows 7 through a a housing 8 formed live steam 9 flows in the direction of the high pressure stage.
- the quick-closing valve han ⁇ delt the present case is a medium-actuated quick ⁇ -circuit valve, the pilot poppet are moved "closed” 10 and the main poppet 11 in dependence on the switch position of a control unit 12 via the live steam in the positions "open" or.
- control lines 13 and 14 are provided which connect the quick- action valve 5 with the control ⁇ device 12.
- the control unit 12 comprises a pneumatic switching drive 15, which in the present case is designed as a diaphragm 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 angeord ⁇ in the chamber 19 without compressed air connection 17 ⁇ are kept 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 position "closed.”
- the outlet 26 to the atmosphere or leakage steam line is closed.
- the pressure of the live steam keeps the pilot poppet 10 via the inflow ⁇ holes 33 and the main poppet 11, respectively against the force of a spring 34, in the open position, both in shut off the passage of the live steam into the cylinder chamber 28 or into the control line 13 without leakage loss. 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 is carried out by Ent ⁇ load of the air pressure at the control unit. Accordingly, the chamber 20 of the switching drive 15 is not supplied with compressed air.
- the control line 13 is closed towards ge ⁇ to the atmosphere by the valve stem 24 is urged by the spring force of the return springs 21 on the spindle 22 with the spindle clutch 23 on the valve seat 25b and subjected to the fresh steam pressure.
- the cylinder chamber 28 is pressurized via the control line 13, the control channel 27 and the inlet bore 33 as well.
- 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 on the Zuström ⁇ holes 33, an open control channel 36 and holes 37 and 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 directed opposite 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.
- Figures 3 to 8 show various operating positions of a pneumatic safety block 38 of the Schnell gleichven ⁇ TILs 5 is designed connected to the Turbi ⁇ nenschutz 3 and for driving the pneumatic switching drive 15 of the control device 12th
- the safety block 38 comprises three identically constructed, electromagnetically actuated 5/2 directional valves VI, V2 and V3 with spring return, which are arranged in series in 2 of 3 circuit, two pressure ports PI and P2, a test port P3 and one with the compressed air connection 17 of the switching drive 15 of the quick-closing valve 5 connected pressure output El.
- Quick-acting valve 5 in its closed position. If all three directional control valves VI, V2 and V3 are actuated, as shown in FIG. 4, a pressure is present both at the test port P3 and at the pressure exit El. Accordingly, the quick- closing valve 5 is in its open position ⁇ leads, so that the live steam in the direction of the control valves 6 can flow.
- Actuation of the switching drive 15 and the quick-closing valve 5 with reference to Figures 4 to 8 also possible if one of the directional control valves VI, V2, V3 should be defective, so that downtime of the turbine 1 can be avoided due to de ubender valves.
- control valves 6 are present at the double-seat control valves ⁇ with two interconnected main cones 39, which are assigned to corresponding trained on the housing 8 finished valve seats.
- the main cones 39 of the control valve 6, which is arranged on the far right in FIG. 1, are coupled to a spindle of an electric actuator 41, which in turn is connected to the turbine control 2 and the turbine control unit 2.
- contactor 3 is connected, so that the main poppets 39 can be moved under Betä ⁇ tion of the actuator either in a closed position or in a fully or partially open position.
- the main cones 39 of the other two control valves 6 are in turn transferred via the control valve connected to the control valve 41 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, which is why 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 when a hydrauli ⁇ shear actuator is used with self-sufficient oil supply in place of the electric actuator 41st
- the present invention is not limited to such a high-pressure valve group.
- FIG. 9 A structural design of a quick-closing valve 5 with extended spindle, which in the present case is a single-seat quick-closing pre-stroke valve, is shown in FIG. 9.
- the switching drive 15 is a membrane 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 are arranged in the chamber 19 without compressed air connection 17 is held in an initial position.
- a spindle 22 is attached to the spring-loaded diaphragm 18, which spindle is connected to the prestroud spindle 43 by means of a spindle coupling 23 and presses the main cone 44 into a valve seat 47 and seals it in the "closed” position subjected to live steam pressure in a chamber 48, this position remains "Ven ⁇ til closed” continue to exist. If the chamber 20 is acted upon from the starting position with compressed air, 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 been filled with steam and about 75-80% of the live steam pressure he ⁇ has reached, lifts the main cone 44 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 be over
- the triggering of the quick-closing valve 5 is carried out by Ent ⁇ load of the air pressure at the switching drive 15. Accordingly, the air flow is interrupted in the chamber 20 of the switching drive 15 and connected to the atmosphere. This will be the
- the present invention proposes an existing turbine control a turbine protection, a turbine, comprising a hydraulic safety block-off valves and control valves, wherein the quick ⁇ closing valves hydraulic via associated switching actuators are actuated, the effect to convert that the hydraulic see switching actuators of the quick-closing valves at least partially, but preferably completely replaced by pneumatic shift 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 ⁇ the existing turbine also preferably be replaced by electric actuators and / or hydraulic actuators with Autar ⁇ ker oil supply, so that may be dispensed, the entire control and regulating oil system of the existing turbine.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Turbines (AREA)
Abstract
Description
Claims
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 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3353385A1 true EP3353385A1 (de) | 2018-08-01 |
EP3353385B1 EP3353385B1 (de) | 2019-11-27 |
Family
ID=57121231
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16778768.8A Active EP3353385B1 (de) | 2015-10-30 | 2016-10-04 | Turbine mit schnellschluss- und regelventilen |
Country Status (6)
Country | Link |
---|---|
US (1) | US10900375B2 (de) |
EP (1) | EP3353385B1 (de) |
CN (1) | CN108350750B (de) |
DE (1) | DE102015221311A1 (de) |
PL (1) | PL3353385T3 (de) |
WO (1) | WO2017071912A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3489470A1 (de) * | 2017-11-22 | 2019-05-29 | Siemens Aktiengesellschaft | Turbinenregelungssystem für eine dampfturbine und dampfturbine |
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 |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
NL103038C (de) * | 1956-02-03 | 1962-06-15 | ||
DE1946968U (de) | 1966-07-23 | 1966-09-29 | Eckhard Kaemmer | Pneumastischer stellantrieb. |
US3556463A (en) | 1968-10-08 | 1971-01-19 | Worthington Corp | Trip valve system |
DE3469777D1 (en) * | 1983-05-30 | 1988-04-14 | Bbc Brown Boveri & Cie | Electro-hydraulic actuator for turbine valves |
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 |
EP1026368A1 (de) * | 1999-02-04 | 2000-08-09 | Asea Brown Boveri AG | 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 |
KR101901121B1 (ko) * | 2010-11-08 | 2018-09-27 | 로베르트 보쉬 게엠베하 | 제어 또는 전환 밸브를 포함하는 아마추어의 작동을 위한 유압 또는 공압 구동기 |
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 |
US10648357B2 (en) * | 2015-10-02 | 2020-05-12 | Elliott Company | Pneumatic trip valve partial stroking arrangement |
-
2015
- 2015-10-30 DE DE102015221311.0A patent/DE102015221311A1/de not_active Ceased
-
2016
- 2016-10-04 US US15/770,232 patent/US10900375B2/en active Active
- 2016-10-04 PL PL16778768T patent/PL3353385T3/pl unknown
- 2016-10-04 WO PCT/EP2016/073604 patent/WO2017071912A1/de active Application Filing
- 2016-10-04 EP EP16778768.8A patent/EP3353385B1/de active Active
- 2016-10-04 CN CN201680063440.9A patent/CN108350750B/zh active Active
Also Published As
Publication number | Publication date |
---|---|
BR112018007205A2 (pt) | 2018-10-16 |
US20180306051A1 (en) | 2018-10-25 |
CN108350750A (zh) | 2018-07-31 |
BR112018007205A8 (pt) | 2023-04-11 |
CN108350750B (zh) | 2020-08-07 |
PL3353385T3 (pl) | 2020-06-01 |
EP3353385B1 (de) | 2019-11-27 |
WO2017071912A1 (de) | 2017-05-04 |
DE102015221311A1 (de) | 2017-05-04 |
US10900375B2 (en) | 2021-01-26 |
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