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EP2998506A1 - Système permettant de réduire le temps de démarrage d'une turbine à vapeur - Google Patents

Système permettant de réduire le temps de démarrage d'une turbine à vapeur Download PDF

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Publication number
EP2998506A1
EP2998506A1 EP14185572.6A EP14185572A EP2998506A1 EP 2998506 A1 EP2998506 A1 EP 2998506A1 EP 14185572 A EP14185572 A EP 14185572A EP 2998506 A1 EP2998506 A1 EP 2998506A1
Authority
EP
European Patent Office
Prior art keywords
rotor core
thermal exchange
exchange channels
steam
steam turbine
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.)
Withdrawn
Application number
EP14185572.6A
Other languages
German (de)
English (en)
Inventor
Amitrajit Basu
Gaurav Kumar
Anujkumar Yadav
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
Original Assignee
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 EP14185572.6A priority Critical patent/EP2998506A1/fr
Publication of EP2998506A1 publication Critical patent/EP2998506A1/fr
Withdrawn legal-status Critical Current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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/10—Heating, e.g. warming-up before starting
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/08—Heating, heat-insulating or cooling means
    • F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
    • 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
    • F05D2260/00—Function
    • F05D2260/85—Starting

Definitions

  • the method and system relates to reducing start-up time of a steam turbine, by enabling faster heating of the turbine rotor during start-up.
  • the rotor of the steam turbine is subjected to high temperature during operation. However, during start-up the rotor of the steam turbine will be at a much lower temperature than that of the steam. However, if such high temperature steam is introduced during the start-up of steam turbine, the rotor may experience a thermal shock, due to the temperature gradient existing between the outer surface (hot) and the inner core (cold) of rotor.
  • the components such as rotor of the steam turbine are pre-heated to certain temperature before starting the normal operation of the turbine.
  • the turbine is started up according to predefined start-up curves where the components such as rotors and valves are gradually preheated. Preheating of the rotor reduces the thermal stress experienced and increases the life of the rotor. But the pre-heating cycles are generally time consuming and non-productive.
  • various methods are used to preheat the rotor of the turbine during startup. For example, structural modifications are used to prevent the rotor from experiencing thermal shock.
  • the rotor is designed to having a smaller cross section.
  • the rotor is rotated at a pre-defined low speed to uniformly pre-heat the rotor.
  • the rotor is kept warm during standstill by using heating means, which is very costly.
  • the existing methods for preheating the rotor are either time consuming or economically unviable.
  • the start-up time for a turbine is crucial for a customer as it is non-productive.
  • the start-up time is critical for small turbines used in industrial or solar applications where daily start-up and shutdown is a norm. Therefore, the start-up time must be reduced for increasing the productivity of the turbine and decreasing the idle time.
  • the invention solves the object by providing a steam turbine comprising a rotor assembly having a rotor core extending in a longitudinal direction and one or more extended portions coupled to the rotor core and extending the rotor core in a radial direction.
  • the steam turbine includes at least one thermal exchange channel located on the one or more extended portions, wherein the thermal exchange channel is capable of having thermal communication between the rotor core and a steam surrounding the rotor core.
  • the rotor core is a solid metal part which extends longitudinally and has blades attached to it.
  • the rotor core has protrusions or extensions at many places for structural reasons. The portions of the rotor core with protrusions require a relatively large amount of time to get heated during start-up cycle.
  • the thermal exchange channels provide additional surface area for thermal exchange between the steam and the rotor core. During the preheating cycle, the thermal exchange channels exposes additional area to the surrounding steam for better heat exchange. Further, the preheating cycle or start-up cycle time is reduced by the aforementioned enhancement.
  • the rotor core has a first diameter and the one or more extended portions have a second diameter.
  • the rotor core is cylindrical in shape and extends longitudinally.
  • the rotor core has a first diameter along the longitudinal axis.
  • the one or more extended portions along the longitudinal axis have a second diameter.
  • the second diameter (of the extended portions) is greater than the first diameter (of the rotor core).
  • the extended portions at certain locations on the rotor core extend the rotor core in the radial direction. Therefore, the extended portions have a cross sectional diameter greater than that of the t rotor core.
  • the at least one thermal exchange channel is a tubular bore.
  • the thermal exchange channel can be for example, straight or contoured.
  • the thermal exchange channel may be fabricated to have an 'L' shape or a 'U' shape, in the extended portions of the rotor core. Further, the thermal exchange channel may have any orientation and cross section in order to increase the thermal exchange.
  • a plurality thermal exchange channel is interconnected.
  • the thermal exchange channels are interconnected to form a network.
  • the thermal exchange channels can be fabricated to be connected to each other in the extended portion and not extending to the first diameter of the rotor core. The interconnection of thermal exchange channels enables efficient thermal communication between the surround steam and the rotor core.
  • the interconnection of the plurality of thermal exchange channel provides a draining mechanism to drain condensed steam.
  • the interconnection of the plurality of thermal exchange channel prevents the accumulation of water in the thermal exchange channel, thus preventing formation of rust.
  • the draining mechanism includes at least one of a slanted thermal exchange channel.
  • the thermal exchange channel is slanted to enable the accumulated water to drain from the rotor core.
  • the rotor core is enclosed by an outer casing.
  • the steam may be released within the outer casing during start-up cycle.
  • the steam released during the start-up cycle is at a relatively lower temperature than the steam used during normal operation of the turbine.
  • the steam released during the start-up cycle is at a higher temperature than the rotor core thereby creating a thermal gradient.
  • Turbines are used in the industry mainly to generate power.
  • the turbines may include, for example, a steam turbine and a steam turbine.
  • the turbines normally include a rotor core to which blades are attached. During operation the rotor core rotates due to the impingement of pressurized fluids, thereby generating energy.
  • FIG 1 illustrates an exemplary rotor core assembly 1 according to a state of the art.
  • the rotor core 2 is cylindrical and extends longitudinally within an outer casing of the turbine (not shown in Figures).
  • There rotor core may have a diameter d1.
  • the diameter at the extended portions 3 may be d2, where d2 is greater than the diameter d1 of the rotor core 2.
  • the thickness of the metal increases at the regions on the rotor core where one or more extended portions, such as extended portions 3, are located. For example, regions such as balance pistons located on the rotor core.
  • the rotor core 2 is generally made up of high strength alloys or super alloys such as nickel and ferrous based alloys. Before the turbine is operated at normal levels, the rotor assembly needs to be pre-heated to avoid thermal shock. When the turbine is to be operated, a start-up cycle is initiated wherein the rotor is rotated at a low speed and steam at a relatively lower temperature is introduced into the outer casing.
  • the start-up cycle is performed to prevent the components of the turbine from experiencing thermal shock in case a high temperature steam is suddenly introduced into the casing.
  • thermal exchange takes place between the rotor core and the steam.
  • the rotor core which is at a lower temperature than the steam slowly begins to heat up.
  • the time taken for the rotor core and the associated components to heat depends upon the capacity of the turbine.
  • the time taken for the completion of the start-up cycle may range between 2-3 hours in some cases.
  • the start-up cycle is unproductive and affects the customers who need to run the start-up cycle on a daily basis.
  • FIG 2A illustrates a perspective view of the rotor core assembly with thermal exchange channels, in accordance with the invention.
  • the extended portions 3 of the rotor core assembly 1 are provided with one or more thermal exchange channels 4 for expediting the heating of the rotor core.
  • the thermal exchange channels 4 exposes additional area for the steam for efficient thermal communication.
  • the steam which is at a higher temperature than the rotor core interacts with the surface of the thermal exchange channels 4 and heats the rotor core. Therefore, the heating of the rotor core takes lesser time to heat up as compared with the heating time of the rotor core assembly 1 without the thermal exchange channels 4.
  • the thermal exchange channels 4 can have varying depth and diameter based on the location on the rotor core.
  • the depth and diameter of the thermal exchange channels 4 are based on a location such as, axial sections, exhaust and balance piston.
  • bigger thermal exchange channels 4 are preferred for better thermal interaction, provided the sizes of the thermal exchange channels 4 meet other requirements such as, strength and rotor dynamics, which varies according to the design.
  • FIG 2A illustrates the thermal exchange channels 4 which are generated by boring the extended portions 3 of the rotor core assembly 1.
  • the thermal exchange channels 4 in FIG 2A are horizontal in orientation and a spaced apart on the periphery of the extended portion 2.
  • FIG 2B illustrates a cross sectional view of the rotor core assembly with the thermal exchange channels, in accordance with the invention.
  • thermal exchange channels 4 extend into the extended portion 3 of the rotor core assembly but do not penetrate completely.
  • the thermal exchange channels 4 allow the steam, released during the start-up cycle to interact with the rotor core and expedite the heating up of the rotor core assembly 1.
  • FIG 3A illustrates a perspective view of the rotor core assembly with 'L' shaped thermal exchange channels, in accordance with the invention.
  • the thermal exchange channels are longer and extend deeper into the rotor core.
  • the steam enters into the thermal exchange channels 4 and heats the rotor core.
  • FIG 3B illustrates a cross sectional view of the rotor core with 'L' shaped thermal exchange channels, in accordance with the invention.
  • the thermal exchange channels 4 extend deep into the extended portion of the rotor core 2 and expedite the heating of the rotor core.
  • FIG 4A illustrates a perspective view of the rotor core assembly with 'U' shaped thermal exchange channels, in accordance with the invention.
  • the thermal exchange channels 4 are longer than the 'L' shaped thermal exchange channels, thereby exposing more area for thermal exchange.
  • FIG 4B illustrates a cross sectional view of the rotor core with 'U' shaped thermal exchange channels 4, in accordance with the invention.
  • FIG 5A illustrates a perspective view of the rotor core assembly with slanted thermal exchange channels 4, in accordance with an embodiment of the invention.
  • the slanted thermal exchange channels 4 facilitate in draining condensed steam which might get accumulated in the thermal exchange channels 4.
  • FIG 5B illustrates a cross sectional view of the rotor core assembly with the slanted thermal exchange channels 4, in accordance with the invention. In FIG 5B , it can be observed that due to the slanted thermal exchange channels 4 any condensed steam accumulated in the thermal exchange channels 4 are drained.
  • FIG 6A illustrates a perspective view of the rotor core assembly with interconnected thermal exchange channels, in accordance with the invention.
  • the thermal exchange channels 6 are parallel to the plane of the extended portion of the rotor core.
  • FIG 6B illustrates a cross sectional view of the rotor core with interconnected thermal exchange channels, in accordance with the invention.
  • the interconnection channel 6 connecting the thermal exchange channels 4 forms a draining mechanism to drain condensed steam.
  • the inner end of the thermal exchange channels 4 are connected to each other by an interconnection channel 6, as shown in FIG 6B .
  • Such an arrangement facilitates in draining any condensed steam within the thermal exchange channels 4.
  • the steam accumulated in the thermal exchange channels 4 may condense when the rotor core is decelerating.
  • the steam condensed in the thermal exchange channels 4 at the upper half of the rotor core is drained through one of the thermal exchange channels 4 in the lower half of the rotor core 2.
  • the thermal exchange channels 4 with interconnection thus prevent rusting of the metal in the rotor core assembly due to accumulation of moisture.
  • the thermal exchange channels reduce the start-up time of a turbine by expediting the pre-heating process.
  • the thermal exchange channels expose additional surface of the rotor core to the surrounding steam in order to heat up the rotor core faster.
  • the thermal exchange channels result in lesser downtime for the customers.
  • the thermal exchange channels can be used for rotor balancing. Balancing mass can be coupled to the thermal exchange channels to balance the rotor core assembly 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
EP14185572.6A 2014-09-19 2014-09-19 Système permettant de réduire le temps de démarrage d'une turbine à vapeur Withdrawn EP2998506A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14185572.6A EP2998506A1 (fr) 2014-09-19 2014-09-19 Système permettant de réduire le temps de démarrage d'une turbine à vapeur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14185572.6A EP2998506A1 (fr) 2014-09-19 2014-09-19 Système permettant de réduire le temps de démarrage d'une turbine à vapeur

Publications (1)

Publication Number Publication Date
EP2998506A1 true EP2998506A1 (fr) 2016-03-23

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ID=51570375

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14185572.6A Withdrawn EP2998506A1 (fr) 2014-09-19 2014-09-19 Système permettant de réduire le temps de démarrage d'une turbine à vapeur

Country Status (1)

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EP (1) EP2998506A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1536102A2 (fr) * 2003-11-28 2005-06-01 ALSTOM Technology Ltd Rotor pour une turbine à vapeur
EP1780376A1 (fr) * 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Turbine à vapeur
EP1911933A1 (fr) * 2006-10-09 2008-04-16 Siemens Aktiengesellschaft Rotor pour une turbomachine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1536102A2 (fr) * 2003-11-28 2005-06-01 ALSTOM Technology Ltd Rotor pour une turbine à vapeur
EP1780376A1 (fr) * 2005-10-31 2007-05-02 Siemens Aktiengesellschaft Turbine à vapeur
EP1911933A1 (fr) * 2006-10-09 2008-04-16 Siemens Aktiengesellschaft Rotor pour une turbomachine

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