EP2211017A1 - Rotor doté d'un espace creux pour une turbomachine - Google Patents

Rotor doté d'un espace creux pour une turbomachine Download PDF

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Publication number
EP2211017A1
EP2211017A1 EP09001083A EP09001083A EP2211017A1 EP 2211017 A1 EP2211017 A1 EP 2211017A1 EP 09001083 A EP09001083 A EP 09001083A EP 09001083 A EP09001083 A EP 09001083A EP 2211017 A1 EP2211017 A1 EP 2211017A1
Authority
EP
European Patent Office
Prior art keywords
rotor
cooling
line
outlet
inlet
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Withdrawn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
EP09001083A
Other languages
German (de)
English (en)
Inventor
Peter Dr. Dumstorff
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Priority to EP09001083A priority Critical patent/EP2211017A1/fr
Publication of EP2211017A1 publication Critical patent/EP2211017A1/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Withdrawn legal-status Critical Current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
    • 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
    • F01D5/088—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor in a closed cavity
    • 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
    • F05D2260/20—Heat transfer, e.g. cooling
    • F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
    • F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam

Definitions

  • the invention relates to a turbomachine, wherein the rotor has a cooling inlet line for supplying cooling medium into the rotor and a cooling outlet line for discharging cooling medium from the rotor, wherein a connecting line is formed in the rotor, which fluidly connects the cooling inlet line and the cooling outlet line.
  • a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows.
  • gas turbines are traversed with gas and / or air as the working medium, which, however, is subject to completely different temperature and pressure conditions than the steam in a steam turbine.
  • steam turbines have e.g. At the same time, the working medium with the highest temperature, which flows into a partial turbine, has the highest pressure.
  • a steam turbine typically includes a vaned rotatably mounted rotor disposed within a casing shell.
  • the rotor When flowing through the flow space formed by the housing jacket with heated and pressurized steam, the rotor is set in rotation by the steam via the blades.
  • the attached to the rotor Shovels are also referred to as blades.
  • usually stationary guide vanes are mounted on the housing jacket, which engage in the intermediate spaces of the moving blades.
  • a vane is typically held at a first location along an interior of the steam turbine casing. In this case, it is usually part of a vane ring, which comprises a number of vanes, which are arranged along an inner circumference on the inside of the steam turbine housing. Each vane has its blade radially inward.
  • a vane ring at a location along the axial extent is also referred to as a vane row.
  • a number of vane rows are arranged one behind the other.
  • the steam turbine shafts which are rotatably mounted in the steam turbines, are subjected to a great deal of thermal stress during operation.
  • the development and production of a steam turbine shaft is both expensive and time consuming.
  • Steam turbine shafts are considered to be the most stressed and expensive components of a steam turbine. This increasingly applies to high steam temperatures.
  • steam turbines in contrast to the gas turbine, have no compressor unit and, moreover, the shafts of the steam turbine are generally accessible only radially.
  • Piston area is to be understood as the area of a thrust balance piston.
  • the thrust balance piston acts in a steam turbine such that a force caused by the working medium force is formed on the shaft in one direction counter-force in the opposite direction.
  • the object of the invention is therefore to provide a steam turbine, which can be operated at high steam temperatures.
  • a rotor for a turbomachine wherein the rotor has a cooling inlet line for supplying cooling medium into the rotor and a cooling outlet line for discharging cooling medium from the rotor, wherein a connecting line is formed in the rotor, which fluidly the cooling inlet line and the cooling outlet line connects to each other, wherein the connecting line is formed spaced from the axis of rotation.
  • the steam turbine shaft can be formed on the one hand creep stable and on the other hand reacts flexibly to thermal loads. For example, during a load change in which a higher thermal load can occur, the cooling causes the thermal load of the shaft to eventually decrease. This is especially true for areas which are particularly thermally stressed, such as e.g. the inflow area or the balance piston.
  • a hollow rotor has a lower mass compared to a solid shaft and thus also a lower heat capacity compared to a solid shaft and a larger flowed surface. As a result, a rapid warm-up of the steam turbine shaft is possible.
  • Another aspect of the invention is that the creep rupture strength of the material used for the rotor is increased by the improved cooling. The creep rupture strength can be increased by a factor greater than two compared to a solid shaft. This leads to an extension of the application of the rotor.
  • the rotor has a cooling medium inlet space, which fluidly connects the cooling inlet line to the connecting line.
  • This cooling medium inlet space is formed as a cavity, wherein the cooling inlet conduit and the cooling outlet conduit open into the cavity.
  • Such a cooling medium entry space formed as a cavity is comparatively easy to manufacture.
  • This cooling medium inlet space viewed in the radial direction from the axis of rotation, is formed between 50 and 90% of the rotor wheel radius measured in the region of the cavity. That Depending on the thermal conditions of this cooling medium inlet space can be suitably formed to provide a corresponding cooling medium vapor flowing through the connecting line to the cooling outlet conduit.
  • the rotor is formed with ademediumaustrittsraum which fluidly connects the cooling outlet line with the connecting line.
  • This cooling medium outlet space can in this case be designed and manufactured similarly to the cooling medium inlet space.
  • a cooling steam flows through the cooling inlet conduit, which is formed for example by a relaxed and cooled flow medium.
  • This compared to the live steam cooled cooling steam flows through the cooling inlet line into the cooling medium inlet space and from there into the connecting line.
  • the cooling medium flows out of the cooling medium outlet space into the cooling outlet line out of the rotor and can flow out of the rotor at a corresponding point where the steam parameters of the cooling medium are required.
  • the rotor has at least eight cooling inlet ducts. These eight cooling inlet ducts all open in the cooling medium inlet space.
  • At least eight cooling outlet lines are formed in the rotor, which extend substantially radially outwards.
  • At least eight connecting lines are also formed in an advantageous development.
  • the cooling inlet line and the connecting line at the same angular distance to a horizontal reference line.
  • the cooling inlet line and the connecting line would be arranged in the radial direction in a line. It is expedient for the same number of cooling inlet pipes and Connecting lines each two cooling inlet ducts and a connecting line in the radial direction arranged one behind the other.
  • the connecting line is formed substantially parallel to the axis of rotation. This results in that the cooling medium can pass well from the cooling medium inlet space to the cooling medium outlet space.
  • the rotor is formed with two floods, wherein the cooling inlet line is arranged in a first flood and the cooling outlet line in a second flood.
  • So-called twin-flow steam turbines are known. These are to be understood steam turbines in which the live steam strikes the rotor through a live steam line and from there relaxes and cools in two directions. The steam is released and cooled in a first tide and in a second tide. After exiting the first and the second flood, the flow medium flows together again.
  • the advantage of such a double-flow arrangement is that the thrust forces are compensated because the steam exerts a thrust in both directions and the thrust forces cancel each other out.
  • the cooling inlet line can thus be introduced after a suitable turbine stage in the first flood.
  • relaxed and cooled steam passes after this turbine stage in the rotor and can cool from there via the connecting line the inflow region of the rotor.
  • the cooling medium flows out via the cooling outlet line into a suitable turbine stage in the second flood out of the rotor and can be expediently converted into energy in the flow channel of the steam turbine still work relaxing.
  • FIG. 1 shows a cross-sectional view of a rotor 1 seen from the side.
  • the rotor 1 is designed as a double-flow rotor, ie, the rotor 1 comprises a first flood 2 and a second flood 3. For clarity, the blades are not shown.
  • live steam flows into a discharge area 5. From the discharge area 5, a first part of the live steam 6 flows in a flow channel along the first flood. Through the second flood 3, a second part 7 flows through a flow channel.
  • the steam flows via a cooling inlet line 8 into a cooling medium inlet space 9.
  • the cooling medium inlet space 9 is formed as a cavity. In this cooling medium inlet space 9, the cooling inlet line 8 opens.
  • the cooling inlet line 8 is radially aligned here. That is, as viewed from a rotation axis 10, the cooling inlet duct 8 is parallel to a straight line extending outward from the rotation axis 10. It will be in a first embodiment at least eight cooling inlet lines 8 are formed. In further alternative embodiments, fewer or more cooling inlet conduits 8 may be formed, depending on the steam parameters.
  • the cooling medium inlet space 9 extends in the radial direction from the axis of rotation 10 to a height H, wherein the height H of the cooling medium inlet space 9 is between 50 and 90% of the radius of the rotor.
  • the cooling medium inlet space 9 also opens a connecting line 11.
  • the connecting line 11 is aligned substantially parallel to the axis of rotation 10.
  • at least eight connecting lines 11 are arranged in the rotor 1.
  • the connecting line 11 then leads into a cooling medium outlet chamber 12.
  • a cooling outlet line 13 also opens into this cooling medium outlet space 12.
  • the cooling outlet line 13 can be substantially similar to the cooling inlet line 8.
  • the size and number of the cooling outlet lines 13 can be the size and number of the cooling inlet line 8 correspond.
  • the weld chambers can be used as the entrance and exit spaces. Due to the three-part design, the connecting bores between the inlet and the outlet space are comparatively easy to manufacture.
  • the cooling outlet line 13 again opens into the flow channel, not shown, of the second flood 3 and can be flowed in at a point downstream of a turbine stage, not shown in an energy-releasing manner.
  • the connecting line 11 is in this case formed at a distance from the axis of rotation 10.
  • FIG. 2 is a cross-sectional view of the section line along the line AA FIG. 1 to see.
  • the section AA leads through the rotor 1, wherein the section through the cooling medium outlet space 12 takes place. Therefore, in the FIG. 2 the cooling outlet lines 13 to see relatively clearly.
  • the cooling outlet lines 13 are aligned substantially in the radial direction.
  • the connecting line 11 and the cooling outlet line 13 are arranged one behind the other in the radial direction 14.
  • a smaller number of connecting lines 11 than the number of cooling outlet lines 13 may be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP09001083A 2009-01-27 2009-01-27 Rotor doté d'un espace creux pour une turbomachine Withdrawn EP2211017A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP09001083A EP2211017A1 (fr) 2009-01-27 2009-01-27 Rotor doté d'un espace creux pour une turbomachine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09001083A EP2211017A1 (fr) 2009-01-27 2009-01-27 Rotor doté d'un espace creux pour une turbomachine

Publications (1)

Publication Number Publication Date
EP2211017A1 true EP2211017A1 (fr) 2010-07-28

Family

ID=40673887

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09001083A Withdrawn EP2211017A1 (fr) 2009-01-27 2009-01-27 Rotor doté d'un espace creux pour une turbomachine

Country Status (1)

Country Link
EP (1) EP2211017A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2572515C2 (ru) * 2014-04-09 2016-01-20 Федеральное государственное бюджетное научное учреждение "Всероссийский научно-исследовательский институт электрификации сельского хозяйства" (ФГБНУ ВИЭСХ) Устройство охлаждения вала свободной турбины газотурбинной установки
CN109236379A (zh) * 2018-09-11 2019-01-18 上海发电设备成套设计研究院有限责任公司 一种内部蒸汽冷却的高参数汽轮机的双流高温转子

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1820725A (en) * 1926-12-17 1931-08-25 Ass Elect Ind Elastic fluid turbine
JPS58155203A (ja) * 1982-03-12 1983-09-14 Toshiba Corp 蒸気タ−ビン
DE19620828C1 (de) * 1996-05-23 1997-09-04 Siemens Ag Turbinenwelle sowie Verfahren zur Kühlung einer Turbinenwelle
US20030133786A1 (en) * 2002-01-11 2003-07-17 Mitsubishi Heavy Industries Ltd. Gas turbine and turbine rotor for a gas turbine
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

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1820725A (en) * 1926-12-17 1931-08-25 Ass Elect Ind Elastic fluid turbine
JPS58155203A (ja) * 1982-03-12 1983-09-14 Toshiba Corp 蒸気タ−ビン
DE19620828C1 (de) * 1996-05-23 1997-09-04 Siemens Ag Turbinenwelle sowie Verfahren zur Kühlung einer Turbinenwelle
US20030133786A1 (en) * 2002-01-11 2003-07-17 Mitsubishi Heavy Industries Ltd. Gas turbine and turbine rotor for a gas turbine
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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2572515C2 (ru) * 2014-04-09 2016-01-20 Федеральное государственное бюджетное научное учреждение "Всероссийский научно-исследовательский институт электрификации сельского хозяйства" (ФГБНУ ВИЭСХ) Устройство охлаждения вала свободной турбины газотурбинной установки
CN109236379A (zh) * 2018-09-11 2019-01-18 上海发电设备成套设计研究院有限责任公司 一种内部蒸汽冷却的高参数汽轮机的双流高温转子

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