EP3009597A1 - Kontrollierte Kühlung von Turbinenwellen - Google Patents

Kontrollierte Kühlung von Turbinenwellen Download PDF

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Publication number
EP3009597A1
EP3009597A1 EP14188998.0A EP14188998A EP3009597A1 EP 3009597 A1 EP3009597 A1 EP 3009597A1 EP 14188998 A EP14188998 A EP 14188998A EP 3009597 A1 EP3009597 A1 EP 3009597A1
Authority
EP
European Patent Office
Prior art keywords
steam
rotor
shield
cooling
turbomachine according
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Withdrawn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
EP14188998.0A
Other languages
German (de)
English (en)
French (fr)
Inventor
Armin De Lazzer
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 EP14188998.0A priority Critical patent/EP3009597A1/de
Priority to KR1020177013044A priority patent/KR101989713B1/ko
Priority to PL15774620T priority patent/PL3183426T3/pl
Priority to CN201580056361.0A priority patent/CN107002494B/zh
Priority to EP15774620.7A priority patent/EP3183426B1/de
Priority to PCT/EP2015/072911 priority patent/WO2016058855A1/de
Priority to JP2017520407A priority patent/JP6511519B2/ja
Priority to US15/517,312 priority patent/US10392941B2/en
Publication of EP3009597A1 publication Critical patent/EP3009597A1/de
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F01D5/081—Cooling fluid being directed on the side of the rotor disc or at the roots of the blades
    • 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
    • F01D5/081—Cooling fluid being directed on the side of the rotor disc or at the roots of the blades
    • F01D5/082—Cooling fluid being directed on the side of the rotor disc or at the roots of the blades on the side of the rotor disc
    • 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
    • F05D2260/20—Heat transfer, e.g. cooling
    • F05D2260/201—Heat transfer, e.g. cooling by impingement of a fluid

Definitions

  • the invention relates to a turbomachine, in particular a steam turbine, with an inflow region for supplying steam, a rotatably mounted rotor, a housing which is arranged around the rotor, wherein between the rotor and the housing, a flow channel is formed, wherein the flow channel with the Inlet region is fluidly connected to each other, with a shield which is designed such that during operation, a flowing into the inflow steam is deflected into the flow channel, wherein the shield has a coolant supply, which is designed such that in operation a cooling steam in a cooling region which is disposed between the shield and the rotor, is flowable.
  • Turbomachines such as steam turbines are flowed through a flow medium, which usually has high temperatures and pressures.
  • steam is used as a flow medium in a steam turbine as an embodiment of a turbomachine.
  • the steam parameters in the live steam inflow region are so high that the steam turbine is subjected to a high thermal load at various points.
  • the materials are thermally heavily loaded.
  • a steam turbine essentially comprises a turbine shaft, which is rotatably mounted, and a housing arranged around the turbine shaft.
  • the turbine shaft is thermally heavily loaded by the temperature of the incoming steam. The higher the temperature, the higher the thermal load.
  • Turbine blades are arranged in so-called grooves on the rotor. During operation, the grooves experience a high mechanical load. However, the thermal load reduces the tolerable mechanical load due to rotation and additional load due to the blades attached to the rotor.
  • thermodynamic point of view From a thermodynamic point of view, it makes sense to increase the input temperature of the steam, since the efficiency increases with higher inlet temperature. In order to expand the load capacity of the materials used in the steam turbine at high temperatures, the inflow regions of the shaft are cooled. If a suitable cooling method can be developed, one can do without the change to a higher quality, but more expensive material.
  • a steam turbine plant comprises at least one steam generator and a first steam turbine formed as a high-pressure turbine part, as well as further partial turbines, which are designed as medium-pressure or low-pressure turbine parts.
  • the steam After flowing through the live steam through the high-pressure turbine section, the steam is reheated to a high temperature in a reheater and fed into the medium-pressure turbine section.
  • the steam that comes from the high-pressure turbine part is called a cold reheater steam and is comparatively cool compared to live steam. This cold reheater steam is used as a cooling medium.
  • the object of the invention is to provide an improved cooling for a steam turbine.
  • a turbomachine in particular a steam turbine, with an inflow region for supplying steam, a rotatably mounted rotor, a housing which is arranged around the rotor, wherein between the rotor and the housing, a flow channel is formed, wherein the flow channel with the inflow area is fluidly connected to each other, with a shield which is designed such that during operation, a flowing into the inflow steam is deflected into the flow channel, wherein the shield has a coolant supply, which is designed such that in operation a cooling steam in a Cooling region, which is arranged between the shield and the rotor, is flowable, wherein the shield has a feed, which establishes a fluidic connection between the cooling region and the inflow region.
  • the invention thus relates to turbomachines, in particular steam turbines, which comprise a shield, which is arranged in the inflow region and shields the shaft from the hot flow medium.
  • a coolant supply is used, which leads a cooling steam to the rotor during operation.
  • the invention has the following idea: So far, a comparatively strong cooling of the rotor in the cooling area, ie obtained between the shield and the rotor surface. It is cooled with a cold reheater steam, which, however, leads to a very strong cooling of the rotor in the inflow area. In case of failure of the coolant, the rotor heats up very much in this area strong, resulting in undesirable extreme thermal cycling.
  • the shield in addition to the coolant supply, to form the shield with a feed through which the live steam can flow into the space between the rotor and the shield.
  • the flow rate of the coolant and the flow rate of the live steam through the supply is selected such that the temperature of the rotor in the inflow region heats up to a limit value.
  • This limit value is chosen such that in the event of failure of the cooling medium, heating to the maximum temperature, ie to heating without coolant, is moderate.
  • vapor is to be understood as meaning a flow medium which, in addition to water vapor, may be ammonia or a vapor-CO 2 mixture.
  • the invention thus avoids that the shaft causes damage due to unsafe failure behavior during cooling with very cold reheater steam or complex process engineering implementation with temperature-controlled cooling steam.
  • Such a new cooling arrangement is advantageous because it is passive. This means that no complex control technology and no control valves for temperature control of the cooling medium are required. Due to the low temperature differences in the component, a low thermal stress, a small additional local distortion due to cooling as well as a more robust behavior with short-term failure of the cooling is achieved.
  • the turbomachine is designed to be double-flowed. This means that the shield covers an area that allows the incoming steam to flow into a first flood and a second flood.
  • the coolant supply is designed such that, during operation, the cooling steam impinges tangentially on the rotor.
  • the coolant supply is not achieved radially through the shield, but guided substantially in the circumferential direction, so that the cooling steam undergoes a twist in the region between the shield and the rotor.
  • the feed can be designed such that, during operation, a vapor from the inflow region tangentially impinges on the rotor.
  • the FIG. 1 shows a steam power plant 1 in a schematic overview.
  • the steam power plant 1 comprises a high-pressure turbine part 2, which has a live steam feed 3 and a high-pressure steam outlet 4.
  • a live steam flows from a main steam line 5, wherein the live steam was generated in a steam generator 6.
  • a live steam valve 7 is arranged, which regulates the flow of the live steam through the high pressure turbine part 2.
  • a quick-acting valve is arranged (not shown), which closes the steam supply to the high-pressure turbine section 2 in the event of an error.
  • the steam flows from the High-pressure steam outlet 4 in a cold reheater line 8.
  • the steam in the cold reheater line 8 is compared to the steam parameters of the live steam in the main steam line 5 such that this cold reheater steam can be used as a coolant, which in the FIG. 1 is shown schematically by the coolant line 9.
  • the cold reheater steam is heated in a reheater 10 and passed through a hot reheater line 11 to a medium pressure turbine section 12.
  • the coolant line 9 can be led to the medium-pressure turbine part 12 in the inflow region (not shown).
  • the rotor of the medium-pressure turbine part 12 is connected to transmit torque to the rotor of the high-pressure turbine part 2 and to the rotor 21 of a low-pressure turbine part 13.
  • an electric generator 14 is torque-transmitting connected to the rotor 21 of the low pressure turbine section 13.
  • the steam flows from medium-pressure steam outlets 15 to the low-pressure turbine section 13
  • FIG. 1 selected medium-pressure turbine section 12 includes a first 29 and a second 30 flood.
  • the steam from the medium pressure steam outlets 15 is guided in an overflow line 16 to the low pressure turbine section 13.
  • the steam flows into a condenser 17 and will condense there to water. Subsequently, the vapor converted into water in the condenser 17 flows via a line 18 to a pump 19 and from there the water is led to the steam generator 6.
  • the high-pressure turbine part 2, the medium-pressure turbine part 12 and the low-pressure turbine part 13 is referred to as a steam turbine and represents an embodiment of a turbomachine.
  • FIG. 2 is an illustration of the inventive arrangement to see.
  • the FIG. 2 shows in particular an inflow region 20 of the medium-pressure turbine part 12.
  • the medium-pressure turbine part 12 comprises a rotor 21 which is about an axis of rotation 22 is rotatably mounted.
  • the rotor 21 includes a plurality of blades 23 disposed in grooves (not shown) on the rotor surface 24. Between the blades 23 vanes 25 are arranged, which are held on a housing (not shown).
  • a first vane row 26 is formed such that this vane row 26 holds a shield 27.
  • the shield 27 is designed in such a way that, during operation, a steam flowing into the inflow region 20 can be diverted into a flow channel 28. Since the in FIG.
  • medium-pressure turbine section 12 has a first flow 29 and a second flow 30, the flow channel 28 is divided into a first flow channel 31 and a second flow channel 32.
  • the incoming steam 33 is thus diverted to a first steam 34 and a second steam 35.
  • the first vapor 34 flows into the first flow channel 31.
  • the second vapor 35 flows into the second flow channel 32.
  • the medium-pressure turbine part 12 comprises a housing (not shown) which is arranged around the rotor 21, wherein the first flow channel 31 and the second flow channel 32 are formed between the rotor 21 and the housing, wherein the first flow channel 31 and the second flow channel 32 with the inflow region 20 are fluidically connected to each other.
  • vapor is to be understood as meaning a flow medium which, in addition to water vapor, may be ammonia or a vapor-CO 2 mixture.
  • the shield 27 has a coolant supply 36, which is designed such that, during operation, a cooling steam flows into a cooling region 37, which is arranged between the shield 27 and the rotor 21.
  • a cooling steam flows into a cooling region 37, which is arranged between the shield 27 and the rotor 21.
  • a vapor from the coolant line 9 is used, which comes from the cold reheater line 8. It can be used in alternative embodiments, another cooling steam.
  • the cooling steam from the coolant supply 36 thus flows to the Rotor surface 24 and cools a thermally stressed area, which is represented by a parabolic gray zone 38.
  • the temperature is shown in shades of gray. As in FIG. 2
  • the gray tone in the parabolic gray zone 38 is a little darker than the gray tones of the rotor 21. This means that the temperature in the parabolic gray zone 38 is greater than the temperature of the rotor 21.
  • a feeder 39 is now arranged in the shield 27 according to the invention.
  • This feed 39 establishes a fluidic connection between the cooling region 37 and the inflow region 20.
  • the feeder 39 can be designed as a bore or with a plurality of holes. These holes can be executed distributed on the circumference.
  • the feeder 39 can be arranged symmetrically with respect to the parabolic gray zone 38, which means that the feeder 39 is arranged in the direction of a central inflow direction 40. In FIG. 2 the supply 39 is not shown in the same direction as the central inflow 40, but a small distance further to the right.
  • FIG. 3 shows substantially the same arrangement as in FIG. 2 , On a repetition of the name and mode of action of the components is therefore omitted.
  • the difference in the presentation of the FIG. 3 is that a failure of the coolant supply 36 is symbolized by a cross.
  • the failure of the coolant supply 36 leads to a heating of the cooling region 37. This leads to a change in the temperature in the parabolic gray zone 38.
  • the gray tones are even darker than the gray area in FIG. 2 , This means that the temperature is higher than the normal operation in FIG. 2 you can see.
  • the temperature difference between the normal operation, as in FIG. 2 can be seen, and the Stör plante, the in FIG. 3 is shown, moderate. This means that the material of the rotor 21 undergoes a comparatively small temperature jump.
  • FIG. 4 shows a side view of the arrangement according to the invention.
  • the coolant supply 36 is formed in a first embodiment in the radial direction 41 towards the axis of rotation. This means that during operation the cooling steam strikes the rotor 21 radially.
  • the feeder 39 becomes in accordance with FIG. 4 such that, during operation, a vapor from the inflow region strikes the rotor 21 radially.
  • the FIG. 5 shows an alternative embodiment to the embodiment according to FIG. 4 ,
  • the FIG. 5 shows that the coolant supply 36 is formed such that during operation of the cooling steam tangentially impinges on the rotor 21.
  • the coolant supply 36 is carried out substantially in such a way that the shield receives a bore through which the steam can strike the rotor 21 tangentially. This leads to a twist of the vapor located in the cooling region 37.
  • the feed 39 is also formed in an alternative embodiment such that in operation, a vapor from the inflow 20 strikes tangentially to the rotor 21. This leads to a better mixing in the cooling area 37.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP14188998.0A 2014-10-15 2014-10-15 Kontrollierte Kühlung von Turbinenwellen Withdrawn EP3009597A1 (de)

Priority Applications (8)

Application Number Priority Date Filing Date Title
EP14188998.0A EP3009597A1 (de) 2014-10-15 2014-10-15 Kontrollierte Kühlung von Turbinenwellen
KR1020177013044A KR101989713B1 (ko) 2014-10-15 2015-10-05 터빈 샤프트의 제어된 냉각
PL15774620T PL3183426T3 (pl) 2014-10-15 2015-10-05 Kontrolowane chłodzenie wałów turbin
CN201580056361.0A CN107002494B (zh) 2014-10-15 2015-10-05 涡轮轴的可控冷却
EP15774620.7A EP3183426B1 (de) 2014-10-15 2015-10-05 Kontrollierte kühlung von turbinenwellen
PCT/EP2015/072911 WO2016058855A1 (de) 2014-10-15 2015-10-05 Kontrollierte kühlung von turbinenwellen
JP2017520407A JP6511519B2 (ja) 2014-10-15 2015-10-05 タービンシャフトの制御された冷却
US15/517,312 US10392941B2 (en) 2014-10-15 2015-10-05 Controlled cooling of turbine shafts

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14188998.0A EP3009597A1 (de) 2014-10-15 2014-10-15 Kontrollierte Kühlung von Turbinenwellen

Publications (1)

Publication Number Publication Date
EP3009597A1 true EP3009597A1 (de) 2016-04-20

Family

ID=51726412

Family Applications (2)

Application Number Title Priority Date Filing Date
EP14188998.0A Withdrawn EP3009597A1 (de) 2014-10-15 2014-10-15 Kontrollierte Kühlung von Turbinenwellen
EP15774620.7A Not-in-force EP3183426B1 (de) 2014-10-15 2015-10-05 Kontrollierte kühlung von turbinenwellen

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP15774620.7A Not-in-force EP3183426B1 (de) 2014-10-15 2015-10-05 Kontrollierte kühlung von turbinenwellen

Country Status (7)

Country Link
US (1) US10392941B2 (pl)
EP (2) EP3009597A1 (pl)
JP (1) JP6511519B2 (pl)
KR (1) KR101989713B1 (pl)
CN (1) CN107002494B (pl)
PL (1) PL3183426T3 (pl)
WO (1) WO2016058855A1 (pl)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111550292A (zh) * 2020-04-24 2020-08-18 上海交通大学 中压缸涡流冷却优化方法及其冷却结构

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57188702A (en) * 1981-05-15 1982-11-19 Toshiba Corp Steam turbine rotor cooling method
EP0088944A1 (de) * 1982-03-16 1983-09-21 Siemens Aktiengesellschaft Axial beaufschlagte Dampfturbine, insbesondere in zweiflutiger Ausführung
DE3406071A1 (de) * 1983-02-21 1984-08-23 Fuji Electric Co., Ltd., Kawasaki Einrichtung zur kuehlung der rotoren von dampfturbinen
JPS59155503A (ja) * 1983-02-24 1984-09-04 Toshiba Corp 軸流タ−ビンのロ−タ冷却装置
WO1997049900A1 (de) * 1996-06-21 1997-12-31 Siemens Aktiengesellschaft Turbomaschine sowie verfahren zur kühlung einer turbomaschine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5337210A (en) * 1976-09-17 1978-04-06 Hitachi Ltd Cooling structure for steam turbine rotor
JPH04121401A (ja) 1990-09-12 1992-04-22 Hitachi Ltd コンバインドサイクル発電プラント
JP2594842Y2 (ja) * 1991-04-16 1999-05-10 三菱重工業株式会社 蒸気タービンロータの冷却装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57188702A (en) * 1981-05-15 1982-11-19 Toshiba Corp Steam turbine rotor cooling method
EP0088944A1 (de) * 1982-03-16 1983-09-21 Siemens Aktiengesellschaft Axial beaufschlagte Dampfturbine, insbesondere in zweiflutiger Ausführung
DE3406071A1 (de) * 1983-02-21 1984-08-23 Fuji Electric Co., Ltd., Kawasaki Einrichtung zur kuehlung der rotoren von dampfturbinen
JPS59155503A (ja) * 1983-02-24 1984-09-04 Toshiba Corp 軸流タ−ビンのロ−タ冷却装置
WO1997049900A1 (de) * 1996-06-21 1997-12-31 Siemens Aktiengesellschaft Turbomaschine sowie verfahren zur kühlung einer turbomaschine

Also Published As

Publication number Publication date
CN107002494A (zh) 2017-08-01
KR101989713B1 (ko) 2019-09-30
PL3183426T3 (pl) 2018-11-30
US10392941B2 (en) 2019-08-27
EP3183426B1 (de) 2018-06-27
CN107002494B (zh) 2019-08-16
US20170298738A1 (en) 2017-10-19
JP2017535709A (ja) 2017-11-30
WO2016058855A1 (de) 2016-04-21
EP3183426A1 (de) 2017-06-28
JP6511519B2 (ja) 2019-05-15
KR20170067886A (ko) 2017-06-16

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