EP2513432B1 - Turbine à vapeur dans une construction à trois coques - Google Patents

Turbine à vapeur dans une construction à trois coques Download PDF

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Publication number
EP2513432B1
EP2513432B1 EP10790445.0A EP10790445A EP2513432B1 EP 2513432 B1 EP2513432 B1 EP 2513432B1 EP 10790445 A EP10790445 A EP 10790445A EP 2513432 B1 EP2513432 B1 EP 2513432B1
Authority
EP
European Patent Office
Prior art keywords
flow
pressure
inner casing
steam
cooling steam
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.)
Not-in-force
Application number
EP10790445.0A
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German (de)
English (en)
Other versions
EP2513432A1 (fr
Inventor
Christian Cukjati
Heinz Dallinger
Thomas Müller
Rainer Quinkertz
Norbert Thamm
Andreas Ulma
Michael Wechsung
Uwe Zander
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Siemens AG
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Siemens AG
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP10790445.0A priority Critical patent/EP2513432B1/fr
Publication of EP2513432A1 publication Critical patent/EP2513432A1/fr
Application granted granted Critical
Publication of EP2513432B1 publication Critical patent/EP2513432B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • 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

Definitions

  • the invention relates to a turbomachine comprising a rotor rotatably mounted about a rotation axis, an inner inner housing arranged around the rotor and an outer inner housing, wherein an outer housing is arranged around the inner inner housing and the outer inner housing, wherein the turbomachine forms a first flood formed for high pressure steam a second flood formed for medium-pressure steam, wherein the second flood is aligned opposite to the first flood.
  • a steam turbine conventionally includes a rotatably mounted rotor and a housing disposed about the rotor. Between the rotor and the inner housing, a flow channel is formed.
  • the housing in a steam turbine must be able to fulfill several functions.
  • the guide vanes are arranged in the flow channel on the housing and, secondly, the inner housing must withstand the pressure and the temperatures of the flow medium for all load and special operating cases.
  • the flow medium is steam.
  • the housing must be designed such that inlets and outlets, which are also referred to as taps, are possible. Another feature that a case must meet is the possibility of a shaft end passing through the case.
  • nickel-base alloys are suitable because they withstand the stresses occurring at high temperatures.
  • the use of such a nickel-based alloy is associated with new challenges.
  • the cost of nickel-base alloys is comparatively high and, in addition, the manufacturability of nickel-based alloys, e.g. limited by limited casting possibilities.
  • the use of nickel-based materials must be minimized.
  • the nickel-based materials are poor heat conductors.
  • the temperature gradients over the wall thickness are so rigid that thermal stresses are comparatively high.
  • the WO 2007 / 006754A1 discloses a combined steam turbine that is double-flow.
  • the DE 34 21 067 A1 discloses a three-shell turbomachine.
  • the high-pressure part and the medium-pressure part are accommodated in an outer housing.
  • the high-pressure part is supplied with live steam, which usually has the highest steam parameters such as temperature and pressure and directly flows from the steam generator to the high-pressure turbine section.
  • the steam flowing out of the high-pressure part after expansion is in turn passed out of the steam turbine and led to a reheater unit of a boiler, where it is heated again to a higher temperature, which may correspond to the live steam temperature.
  • This reheated steam is then passed back into the turbomachine in the medium-pressure part and then flows through a medium-pressure blading.
  • the high-pressure part and the medium-pressure part in this case have oppositely arranged flow directions.
  • Such embodiments are called reverse flow fluid machines. But there are also known flow machines, which are manufactured in a so-called single-flow design. In this type of construction, the high-pressure part and the medium-pressure part are arranged one after the other and are flowed through in the same flow direction.
  • the inner housing is in this case formed in an inner inner housing and an outer inner housing.
  • the inner inner housing is located in the region of the inflow area and must therefore withstand the high temperatures and the high pressures. Therefore, the inner inner housing is made of a suitable material, such as a nickel-based alloy or a higher quality material such as a steel, which comprises 9 - 10 wt .-% chromium. Between the inner inner housing and the rotor of the flow channel is formed.
  • the inner inner housing therefore has means, such as grooves, for carrying vanes therein.
  • To the inner case is a outer inner housing arranged.
  • the outer inner housing is designed such that it is seen in the flow direction, adjacent to the inner inner housing and constitutes a boundary of the flow channel, wherein in the outer inner housing devices such as grooves, are provided to carry vanes can.
  • the outer inner casing is acted upon by vapor introduction into the cooling steam space with a steam having a lower temperature and a lower pressure, so that the material of the outer inner casing must be less heat-resistant than the material of the inner inner casing.
  • the outer inner housing is formed of a less high-quality material.
  • an outer housing is arranged around the inner inner housing and the outer inner housing.
  • the turbomachine has a first flood, which is acted upon by a high-pressure steam and flows in a first flow direction. Furthermore, the turbomachine has a second flood, which is acted upon by medium-pressure steam and flows in a second flow direction. The second flow direction is opposite to the first flow direction, so that this flow machine is designed in a so-called reverse flow design.
  • the high-pressure inflow region and the medium-pressure inflow region are surrounded or formed by an inner inner housing.
  • the inner inner housing is made of a higher quality material and only receives the high pressure and medium pressure inflow including the balance piston and the Leitschaufelnuten up to the stage, which is essential for temperature and strength reasons. As a result, the inner inner housing kept compact to save space and also has a lower weight.
  • a cooling steam flow line For the flow of cooling steam into the cooling steam space, a cooling steam flow line is provided.
  • the cooling steam flow line is fluidically connected to the second flow. This means that the medium-pressure steam is mainly flowed into the cooling steam space, which has ideal steam parameters to adequately cool the inner inner housing.
  • the first flood has a high-pressure outflow area and the second flood has a medium-pressure outflow area, wherein the outer inner housing extends from the high-pressure outflow area to the medium-pressure outflow area.
  • the outer inner housing therefore extends over almost the entire blading area of the rotor, with the outer inner housing having means for supporting vanes. However, not the entire flow area is formed with vanes in the outer inner housing. In the area of the inner inner housing, no vanes are arranged in the outer inner housing. In this area, the inner inner casing is sheathed by the outer inner casing.
  • the outer inner housing is in this case formed of an upper part and a lower part. The upper part and the lower part are in turn formed from one piece and extend over the first and second flood.
  • the outer inner housing along the first flood and the second flood is formed.
  • a cooling steam space is formed between the inner inner housing and the outer inner housing.
  • the cooling steam in operation between the inner inner casing and the outer inner casing simultaneously constitutes the insulation to the outer inner casing which defines the cooling steam space and the inner inner casing encloses and forms the expansion path behind the cooling steam extraction.
  • the outer inner housing is in contact with this cooling steam and can therefore be made or formed of a lower quality material than the inner inner housing.
  • the primary and secondary stresses in the outer inner casing are only affected by the difference between the vapor state of the vapor in the cooling steam space and the medium pressure exhaust steam.
  • Primary stresses are mechanical stresses that arise as a result of external loads, eg due to vapor pressures, weight forces and the like.
  • secondary voltages are meant, for example, thermoelectric voltages and represent mechanical stresses that arise as a result of unbalanced temperature fields or impediments to thermal expansion (thermal Verzwteil Heidelberg).
  • the turbomachine is formed, inter alia, in the cooling steam space with a drainage pipe, which at a standstill or startup drains an accumulating condensation water or ensures sufficient residual flow in the event of failure of a tap, which could be exemplified by steam extraction via nozzles from the refrigerator.
  • cooling steam space is formed with adedampfausströmungstechnisch for flowing cooling steam from the cooling steam space. Due to the continuous operation of the cooling steam from the cooling steam space in the operation, a very good cooling is obtained, whereby the material utilization (in particular primary and secondary stresses) are lower in the turbomachine.
  • the inner inner housing is in this case made of a higher quality material than the outer inner housing.
  • the inner inner housing is formed in a first embodiment of a high-chromium material comprising 9 - 10 wt .-% chromium.
  • the inner housing is formed from a nickel-based material.
  • the outer inner casing is formed of a material comprising 1 - 2 wt .-% chromium.
  • the steam turbine 1 shown in FIG. 1 is an embodiment of a turbomachine.
  • the steam turbine 1 comprises an outer housing 2, an inner inner housing 3, an outer inner housing 4 and a rotatably mounted rotor 5.
  • the rotor 5 is rotatably mounted about a rotation axis 6.
  • the outer housing 2 is formed from an upper part and a lower part, wherein the upper part is shown above the axis of rotation 6 and the lower part below the axis of rotation 6 in the plane of the drawing.
  • Both the inner inner housing 3 and the outer inner housing 4 likewise have an upper part and a lower part which, as in the case of the outer housing 2, is arranged above and below the axis of rotation 6.
  • the inner inner casing 3, the outer inner casing 4 and the outer casing 2 each have a horizontal parting line.
  • a high-pressure steam flows into a high-pressure inflow region 7. Subsequently, the high-pressure steam flows along a first flow direction 9 through a blading 8, not shown, which comprises guide vanes and rotor blades. The blades are hereby arranged on the rotor 5 and the guide vanes on the inner inner casing 3 and outer inner casing 4. The temperature and the pressure of the high-pressure steam are thereby reduced.
  • the high-pressure steam subsequently flows out of a high-pressure outflow region 10 out of the turbomachine to a reheater unit, not shown in greater detail. Furthermore, not shown, is the fluidic connection between the Hochdruckausström Scheme 10 and the reheater unit.
  • the medium-pressure blading 13 has guide vanes and rotor blades, not shown. The blades are hereby arranged on the rotor 5 and the guide vanes on the inner inner casing 3 and outer inner casing 4.
  • the medium-pressure steam flowing through the medium-pressure blading 13 then flows out of a medium-pressure outflow region 14 out of the outer inner casing 4 and then flows out of the turbomachine 1 via a discharge stub 15.
  • the inner inner casing 3 and the outer inner casing 4 are arranged around the rotor 5.
  • the outer casing 2 is arranged.
  • the inner inner housing 3 is formed in the region of the high-pressure inflow region 7 and the medium-pressure inflow region 11. Since the temperatures of the steam are highest in the high-pressure inflow region 7 and in the medium-pressure inflow region 11, the inner inner casing 3 is made of a material of higher value.
  • the inner inner casing 3 is formed of a nickel-based alloy.
  • the inner inner casing 3 is formed of a higher grade material comprising 9-10 wt.% Chromium.
  • the outer inner housing 4 may be formed of a less high-quality material.
  • the inner outer housing may be formed from a steel having 1-2% by weight chromium.
  • the outer inner housing 4 extends at least from the Hochdruckausström Suite 10 along the axis of rotation 6 to the medium-pressure Ausström Suite 14. That means that the inner inner housing 3 is disposed in the region of the high-pressure inflow region 7 and the medium-pressure inflow region 11 within the outer inner housing 4. Between the inner inner casing 3 and the outer inner casing 4, a cooling steam space 16 is formed. This cooling steam space 16 is formed with a cooling steam flow line for flowing cooling steam.
  • the cooling steam 16 is removed at a suitable location from the medium-pressure blading 13 and can be removed, for example, to a gap 17 between the inner inner casing 3 and the outer inner casing 4. In this case, the cooling steam space 16 must be sealed to the blading 8.
  • the cooling steam could optionally be supplied via the gap 17 from the medium-pressure blading 13 or via a second gap 22 from the blading 8. The respective other side would have to be closed by a suitable first seal 23 or second seal 24.
  • the outer inner casing 4 is formed along the first flow 18 and the second flow 19.
  • the cooling steam flow line is not shown in detail in the figure.
  • the outer inner housing 4 has aharidampfausströmungs effet for the flow of cooling steam from the cooling steam space 16.
  • the inner inner housing 3 takes the high-pressure inflow region 7 and the medium-pressure inflow region 11 including one Balancing piston 20 and not shown Leitschaufelnuten up to the stage, which is essential for temperature and strength reasons.
  • the inner inner housing 3 is characterized relatively small and thus cost-saving and offers a broadening of the potential suppliers because of the low tonnage.
  • the cooling steam flowing out of the cooling steam chamber 16 again leads to a good cooling effect.
  • This outflowing cooling steam can be guided, for example, through the outer inner housing 4 into an exhaust-steam space 21 or e.g. be removed by a tap.
  • the inner inner housing 3 and the outer inner housing 4 are sealed against each other by means of seals.
  • a drainage line not shown, which dissipates an accumulating condensate at a standstill or startup of the steam turbine 1 or ensures sufficient residual flow in case of failure of the tap.
  • the inner inner housing 3, the outer inner housing 4 and the outer housing 2 are pressure-bearing.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Claims (8)

  1. Turbomachine
    comprenant un rotor ( 5 ) monté tournant autour d'un axe ( 6 ) de rotation, la turbomachine ayant un premier flux ( 18 ) constitué pour de la vapeur sous haute pression et un deuxième flux ( 19 ) constitué pour de la vapeur sous basse pression, le deuxième flux ( 19 ) étant dirigé en sens contraire du premier flux ( 18 ), le premier flux ( 18 ) ayant une zone ( 7 ) d'entrée sous haute pression et le deuxième flux ( 19 ) une zone ( 11 ) d'entrée sous pression moyenne et le carter ( 3 ) intérieur à l'intérieur étant disposé autour de la zone ( 7 ) d'entrée sous haute pression et de la zone ( 11 ) d'entrée sous pression moyenne,
    caractérisée par
    un carter ( 3 ) intérieur intérieur disposé autour du rotor ( 5 ) et un carter ( 4 ) intérieur extérieur, un carter ( 2 ) extérieur étant disposé autour du carter ( 3 ) intérieur intérieur et du carter ( 4 ) intérieur extérieur,
    un espace ( 16 ) pour de la vapeur de refroidissement étant constitué entre le carter ( 3 ) intérieur intérieur et le carter ( 4 ) intérieur extérieur
    et un conduit d'écoulement de vapeur de refroidissement étant prévu pour faire affluer de la vapeur de refroidissement dans l'espace ( 16 ) pour de la vapeur de refroidissement,
    dans laquelle le conduit d'écoulement de vapeur de refroidissement communique en technique des fluides avec le deuxième flux ( 19 ),
    dans laquelle le premier flux ( 18 ) a une zone ( 10 ) de sortie sous haute pression et le deuxième flux ( 19 ) une zone ( 14 ) de sortie sous pression moyenne, le carter ( 4 ) intérieur extérieur s'étendant de la zone ( 10 ) de sortie sous haute pression jusqu'à la zone ( 14 ) de sortie sous pression moyenne.
  2. Turbomachine suivant la revendication 1,
    dans laquelle le carter ( 4 ) intérieur extérieur est constitué le long du premier flux ( 18 ) et du deuxième flux ( 19 ) .
  3. Turbomachine suivant l'une des revendications précédentes, dans laquelle la chambre ( 16 ) pour de la vapeur de refroidissement est constituée en ayant un conduit de sortie de la vapeur de refroidissement pour faire sortir de la vapeur de refroidissement de l'espace ( 16 ) pour de la vapeur de refroidissement.
  4. Turbomachine suivant l'une des revendications précédentes, dans laquelle la zone ( 10 ) de sortie sous haute pression peut communiquer avec un conduit de surchauffeur intermédiaire.
  5. Turbomachine suivant l'une des revendications précédentes, dans laquelle le carter ( 3 ) intérieur intérieur est en un matériau de plus grande valeur que celui du carter ( 4 ) intérieur extérieur.
  6. Turbomachine suivant la revendication 5,
    dans laquelle le carter ( 3 ) intérieur intérieur est en un matériau à grande teneur en chrome qui comprend de 9 à 10% en poids de chrome.
  7. Turbomachine suivant la revendication 5,
    dans laquelle le carter ( 3 ) intérieur intérieur est en un matériau à base de nickel.
  8. Turbomachine suivant la revendication 5, 6 ou 7,
    dans laquelle le carter ( 4 ) intérieur extérieur est en un matériau qui comprend de 1 à 2% en poids de chrome.
EP10790445.0A 2009-12-15 2010-12-14 Turbine à vapeur dans une construction à trois coques Not-in-force EP2513432B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10790445.0A EP2513432B1 (fr) 2009-12-15 2010-12-14 Turbine à vapeur dans une construction à trois coques

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP09015540A EP2336506A1 (fr) 2009-12-15 2009-12-15 Turbine a vapeur dans une construction à trois coque
PCT/EP2010/069576 WO2011082984A1 (fr) 2009-12-15 2010-12-14 Turbine à vapeur en conception à triple enveloppe
EP10790445.0A EP2513432B1 (fr) 2009-12-15 2010-12-14 Turbine à vapeur dans une construction à trois coques

Publications (2)

Publication Number Publication Date
EP2513432A1 EP2513432A1 (fr) 2012-10-24
EP2513432B1 true EP2513432B1 (fr) 2013-12-04

Family

ID=42270231

Family Applications (2)

Application Number Title Priority Date Filing Date
EP09015540A Withdrawn EP2336506A1 (fr) 2009-12-15 2009-12-15 Turbine a vapeur dans une construction à trois coque
EP10790445.0A Not-in-force EP2513432B1 (fr) 2009-12-15 2010-12-14 Turbine à vapeur dans une construction à trois coques

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP09015540A Withdrawn EP2336506A1 (fr) 2009-12-15 2009-12-15 Turbine a vapeur dans une construction à trois coque

Country Status (5)

Country Link
US (1) US9222370B2 (fr)
EP (2) EP2336506A1 (fr)
JP (1) JP5551268B2 (fr)
CN (1) CN102803661B (fr)
WO (1) WO2011082984A1 (fr)

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5260311A (en) * 1975-11-12 1977-05-18 Toshiba Corp Turbine casing
JPS5932961B2 (ja) 1980-09-29 1984-08-13 日本国有鉄道 電気車の絶縁セクシヨンにおける旅客車用サ−ビス電源の瞬時停電防止方法
JPH0621521B2 (ja) 1983-06-10 1994-03-23 株式会社日立製作所 蒸気タ−ビンの主蒸気入口構造
JPS60195304A (ja) 1984-03-19 1985-10-03 Hitachi Ltd 蒸気タ−ビンケ−シングの熱応力制御装置
US4840537A (en) * 1988-10-14 1989-06-20 Westinghouse Electric Corp. Axial flow steam turbine
JP3620167B2 (ja) * 1996-07-23 2005-02-16 富士電機システムズ株式会社 再熱式軸流蒸気タービン
EP0860511B1 (fr) * 1997-01-27 2003-09-17 Mitsubishi Heavy Industries, Ltd. Acier de moulage à haute teneur en chrome, résistant aux températures élevées et réservoir sous pression, fabriqué avec cet acier
DE19909056A1 (de) * 1999-03-02 2000-09-07 Abb Alstom Power Ch Ag Gehäuse für eine thermische Turbomaschine
JP2000282808A (ja) * 1999-03-26 2000-10-10 Toshiba Corp 蒸気タービン設備
DE10353451A1 (de) 2003-11-15 2005-06-16 Alstom Technology Ltd Dampfturbine sowie Verfahren zum Herstellen einer solchen Dampfturbine
EP1559872A1 (fr) 2004-01-30 2005-08-03 Siemens Aktiengesellschaft Turbomachine
EP1624155A1 (fr) 2004-08-02 2006-02-08 Siemens Aktiengesellschaft Turbine à vapeur et procédé d'opération d'une turbine à vapeur
DE102006027237A1 (de) 2005-06-14 2006-12-28 Alstom Technology Ltd. Dampfturbine
EP1744017A1 (fr) * 2005-07-14 2007-01-17 Siemens Aktiengesellschaft Turbine combinée à vapeur et procédé de fonctionnement d'une turbine combinée à vapeur
EP2187004A1 (fr) * 2008-11-13 2010-05-19 Siemens Aktiengesellschaft Boîtier intérieur pour une turbomachine

Also Published As

Publication number Publication date
WO2011082984A1 (fr) 2011-07-14
JP2013513758A (ja) 2013-04-22
EP2336506A1 (fr) 2011-06-22
CN102803661B (zh) 2015-06-17
US20120257959A1 (en) 2012-10-11
US9222370B2 (en) 2015-12-29
JP5551268B2 (ja) 2014-07-16
CN102803661A (zh) 2012-11-28
EP2513432A1 (fr) 2012-10-24

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