EP0926316A1 - Turbine à vapeur combinée à pressions multiples - Google Patents

Turbine à vapeur combinée à pressions multiples Download PDF

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Publication number
EP0926316A1
EP0926316A1 EP97811024A EP97811024A EP0926316A1 EP 0926316 A1 EP0926316 A1 EP 0926316A1 EP 97811024 A EP97811024 A EP 97811024A EP 97811024 A EP97811024 A EP 97811024A EP 0926316 A1 EP0926316 A1 EP 0926316A1
Authority
EP
European Patent Office
Prior art keywords
pressure
steam turbine
steam
cooling
combined multi
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
Application number
EP97811024A
Other languages
German (de)
English (en)
Other versions
EP0926316B1 (fr
Inventor
Peter Graf
Daniel Lewandowski
Werner Dr. Birke
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.)
General Electric Technology GmbH
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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 ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Priority to EP19970811024 priority Critical patent/EP0926316B1/fr
Priority to DE59711075T priority patent/DE59711075D1/de
Publication of EP0926316A1 publication Critical patent/EP0926316A1/fr
Application granted granted Critical
Publication of EP0926316B1 publication Critical patent/EP0926316B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings

Definitions

  • the invention relates to a combined multi-pressure steam turbine with a high-pressure and a medium-pressure range, a uniaxial rotor arrangement which limits the high-pressure and medium-pressure range on one side.
  • an outer housing which has inlet and outlet openings and at least partially surrounds the rotor arrangement and the high-pressure and medium-pressure region, and a separating device which seals the high-pressure region axially from the medium-pressure region to the rotor arrangement.
  • a combined high-pressure / medium-pressure steam turbine of the generic type is known from US Pat. No. 5,411,365 out, for reasons of simplified constructive interpretation and cost savings a separator 142 (see Fig. 2 of the US publication) through which the high pressure (HP) from the medium pressure range (IP) is separated.
  • the combined steam turbine is the combination of a high-pressure and medium-pressure steam turbine part, which by a single rotor shaft are penetrated and opposite directions of steam flow exhibit.
  • the one at the end of the high pressure steam turbine escaping steam flow is through an outlet opening and through a Corresponding supply line to the medium pressure area directly above via a reheater fed to the combined steam turbine.
  • the medium pressure range is axial against the high pressure area by the separator 142 and radially on the one hand limited by the rotor arrangement and on the other hand by the outer wall.
  • a disadvantage of this construction of a combined steam turbine is that the hot steam streams under pressure are in direct thermal contact occur with the outer housing, whereby the mechanical and in particular the thermal stress on the material of the outer casing in these areas very much is high. Therefore, to ensure a long life of the steam turbine in particular to design those areas of the outer housing accordingly strongly, who are exposed to the above-mentioned heavy loads. Be too high-quality materials are used for these housing parts, not least in contribute significantly to the total cost of the steam turbine.
  • the invention has for its object a combined high-pressure / medium-pressure steam turbine according to the preamble of claim 1 to develop such that constructive measures should be taken, the mechanical and in particular To reduce thermal stress on the outer casing of the steam turbine To be able to reduce stability requirements on the housing wall. Moreover it should be possible to choose materials for the outer casing inferior quality and thus more cost-effective housing components can.
  • a combined high-pressure / medium-pressure steam turbine with one High pressure and a medium pressure range a uniaxial rotor arrangement, which limits the high pressure and medium pressure range on one side, an outer housing, which has inlet and outlet openings and the rotor assembly and the High pressure and medium pressure area at least partially surrounds, as well as a separation device, which the high pressure area from the medium pressure area axially to the rotor assembly seals, developed in such a way that between the rotor assembly and the outer housing a combined HD / MD intermediate housing is provided, which with its from the side facing away from the rotor arrangement together with the outer housing Cooling volume includes that the intermediate housing, the rotor assembly in the medium pressure range at least partially surrounds it, and that surrounding the medium pressure region Intermediate housing in the steam flow direction a through channel is subordinate, which connects the medium pressure range with the cooling volume. This through channel is expediently at the same time a system-related tapping from the medium pressure range.
  • the intermediate housing according to the invention is used for the thermal separation of the are called steam streams that spread within the high and medium pressure range, of which the outer turbine encapsulates the entire turbine.
  • the outer turbine encapsulates the entire turbine.
  • active cooling of the inside of the outer casing and the outside of the Intermediate housing due to the expansion process within the medium pressure turbine cooled steam removed from the medium pressure range and in the between the intermediate case and the outer case forming space initiated.
  • the temperature of the outer case through targeted underflow with cooling steam to reduce by approx. 100 ° C and more than in the case of the conventional, direct application of the outer housing with Steam flows into the respective areas of the high and medium pressure turbine be initiated.
  • the intermediate housing preferably extends from areas of the medium-pressure steam turbine via the axial separator, which is used to adjust the vapor pressure between High-pressure and medium-pressure areas are provided in a ring around the rotor arrangement is, right down to the high pressure steam turbine area.
  • the intermediate housing preferably constructed with the separating device as a unit and encloses the adjacent areas on both sides, just like the separating device the rotor assembly.
  • the intermediate housing has sections to which guide vanes are attached are in engagement with the rotor blades of the high-pressure or medium-pressure steam turbine attached to the rotor arrangement.
  • the intermediate housing is also vapor-tight with the outer housing has so that the high pressure area of the high pressure steam turbine on one Side of the rotor assembly itself and on the other side of parts of the intermediate housing and the outer housing is limited.
  • the intermediate casing surrounds one in Steam flow direction front part of the rotor assembly such that guide vanes are firmly arranged on the intermediate housing, which between the on the rotor assembly protrude integrated blades.
  • the one enclosing the medium pressure range Intermediate housing includes the rotor assembly so far that the steam expanding through the rotor arrangement has cooled down until the Steam temperature well below the steam inlet temperature in the medium pressure range lowers.
  • steam inlet temperatures are in the medium pressure range about 500 - 600 ° C, which in the course of expansion when passing through the rotor arrangement of the medium-pressure steam turbine falls to well below 500 ° C.
  • Parts of the outer casing enclose the intermediate casing in the steam direction the medium-pressure steam turbine, however, are separated by a narrow one Through channel kept at a distance from the intermediate housing. Because of the narrow Through channel, more cooled steam enters the cooling volume the intermediate and outer housing. The steam expanded to below 500 ° C to cool the outer case to the lower temperature level, which causes the Material of the outer casing is exposed to lower thermal loads.
  • the cooling volume also has at least one large-dimensioned outlet opening through which the cooling steam can be discharged from the steam turbine.
  • the dimensioning the outlet opening is chosen to be significantly larger than the flow cross section the through-channel between the intermediate housing and the outer housing, so that a significantly lower pressure prevails in the cooling volume than in the medium pressure range of the steam turbine. For this reason, in addition to the lesser Thermal stress the outer casing also less strongly with high pressure loaded from the inside of the steam turbine, so that the mechanical load the material of the outer housing is less than that of conventional combined Steam turbines.
  • the present invention makes it possible to constructively design the outer housing dimension in a material-saving manner and also use materials, that only withstand the lower temperature and pressure conditions have to. A significant cost reduction in the construction of such steam turbines can be achieved.
  • the single figure shows a longitudinal section through a combined steam turbine, a high pressure area (HD) 1 and a medium pressure area (MD) 2 having.
  • the terms high pressure area and medium pressure area are intended to mean the areas Define the steam turbine arrangement through which the steam after entering the Steam turbine flows through. So it gets hotter and under high pressure Steam through the inflow duct 3 into the interior of the steam turbine by a Outer housing 4 is surrounded.
  • Inside the steam turbine is a uniaxial rotor arrangement 5 provided, the two separate blade regions 5 ' (HD) and 5 '' (MD).
  • the blade area 5 ′ of the rotor arrangement 5 is limited on one side the flow volume 6 of the high pressure area, which is connects directly to the outlet 7 of the inflow duct 3.
  • the steam flow in high pressure area 1 takes place from right to right on the left through the throughflow volume with guide vanes 8 and 9 blades 6.
  • the steam flowing through the high-pressure region enters the Input volume 10 of the medium pressure area 2 and flows through the medium pressure area from left to right until outlet 11 of the medium pressure range.
  • such combined steam turbines are also known as in Steam turbines flow through in the opposite direction.
  • the guide vanes and 8 blades 9 steam passing in the medium pressure region 2 escapes in the usual way via an outlet opening 12.
  • a separating device 13 is provided which radially rotates the rotor arrangement 5 Surrounds center area by means of an L-shaft seal 14. On both sides to the separator extends an intermediate housing 15, the casting technology with the separator 13 is connected.
  • An extension of the intermediate housing 15 delimits the side of the high-pressure region 1 the entry area of the flow volume 6.
  • the intermediate housing 15 projects beyond part of the rotor arrangement 5 'and points it in the steam flow direction first guide vanes 8, which in the space between the blades of the Project rotor assembly 5 '.
  • the intermediate housing 15 is in the high pressure region 1 moreover steam-tightly connected to the outer housing 4.
  • the intermediate housing 15 extends in a toroidal manner Form and closes with its, the rotor assembly 5 '' side, the Input volume 10 a.
  • the intermediate housing 15 is also in the medium pressure range formed such that it is in the steam flow direction with the first guide vanes 8 is connected, which in the spaces between the blades 9 of the rotor assembly Intervene 5 ''.
  • the intermediate housing 15 in the medium pressure range downstream, a part of the outer housing 4 encloses the rotor arrangement 5 ''.
  • the part of the outer housing that surrounds the rotor arrangement 5 ′′ is mounted at a distance from the intermediate housing 15, so that a through channel 16 is enclosed, through which a steam outlet radially to the rotor arrangement 5 ′′
  • the cooling volume 17 takes place, the cooling volume on the one hand from the intermediate housing 15 and on the other hand enclosed by the inside of the outer housing 4 is.
  • the medium pressure region initially passes through the passage 16 flowed through, expanded and therefore cooled steam partially into the Cooling volume 17 and the inside of the outer housing 4 and the outer surface to cool the intermediate housing 15.
  • the cooling volume 17 extends radially around the entire intermediate housing and also detects areas on the side of the high pressure area.
  • the outer housing can be opened via an outlet opening 18 4 cooling cooling steam escape.
  • a cooling line 21 is optionally provided, which with the cooling volume 17 is connected in such a way that it can be regulated by this line Increase in the flow of the cooling volume 17 cooling steam directly from the Cooling volume 17 can flow to the outside without the cooling steam leaving the outlet opening 18 must happen.
  • the additional cooling line 21 is particularly useful during start-up processes advantageous in cases of large load changes in the steam turbine, because in this way the cooling steam throughput through the cooling volume 17 within wide limits can be varied.
  • For a targeted control of the coolant vapor throughput serves at least one control valve 22 which is installed in the cooling line.
  • the Cooling line preferably opens into the outlet area 12 of the medium pressure area.
  • the inner contour of the cooling volume 17 is preferably designed such that no dead spaces are formed in the direction of flow of the cooling steam.
  • rectifiers which are designed in the form of flow openings 20
  • a uniform flow through the cooling volume is achieved before the cooling steam is passed on through the outlet opening 18.
  • the intermediate housing 15 is releasably fixed in the embodiment shown a hooking 19 connected to the outer housing 4.
  • cooled cooling steam at temperatures of can be branched below 500 ° C, preferably 450 ° C from the medium pressure region 16 and in this way the outer and intermediate casing of the steam turbine are crucial be cooled.
  • the above advantages in terms of less The result is a choice of materials and wall thickness.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP19970811024 1997-12-24 1997-12-24 Turbine à vapeur combinée à pressions multiples Expired - Lifetime EP0926316B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19970811024 EP0926316B1 (fr) 1997-12-24 1997-12-24 Turbine à vapeur combinée à pressions multiples
DE59711075T DE59711075D1 (de) 1997-12-24 1997-12-24 Kombinierte Mehrdruck-Dampfturbine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19970811024 EP0926316B1 (fr) 1997-12-24 1997-12-24 Turbine à vapeur combinée à pressions multiples

Publications (2)

Publication Number Publication Date
EP0926316A1 true EP0926316A1 (fr) 1999-06-30
EP0926316B1 EP0926316B1 (fr) 2003-12-03

Family

ID=8230549

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19970811024 Expired - Lifetime EP0926316B1 (fr) 1997-12-24 1997-12-24 Turbine à vapeur combinée à pressions multiples

Country Status (2)

Country Link
EP (1) EP0926316B1 (fr)
DE (1) DE59711075D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1098070A1 (fr) * 1999-10-29 2001-05-09 Mitsubishi Heavy Industries, Ltd. Turbine à vapeur à refroidissement amélioré de la carcasse d'enveloppe
EP2031190A1 (fr) * 2007-08-28 2009-03-04 Siemens Aktiengesellschaft Turbine à vapeur dotée d'une alimentation réglée en agent de refroidissement

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2823891A (en) * 1953-05-20 1958-02-18 Westinghouse Electric Corp Steam turbine
US3189320A (en) * 1963-04-29 1965-06-15 Westinghouse Electric Corp Method of cooling turbine rotors and discs
EP0394894A1 (fr) * 1989-04-26 1990-10-31 Gec Alsthom Sa Stator interne HP-MP unique de turbine à vapeur avec climatisation controlée
WO1997025521A1 (fr) * 1996-01-11 1997-07-17 Siemens Aktiengesellschaft Arbre de turbine a vapeur a refroidissement interne

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2823891A (en) * 1953-05-20 1958-02-18 Westinghouse Electric Corp Steam turbine
US3189320A (en) * 1963-04-29 1965-06-15 Westinghouse Electric Corp Method of cooling turbine rotors and discs
EP0394894A1 (fr) * 1989-04-26 1990-10-31 Gec Alsthom Sa Stator interne HP-MP unique de turbine à vapeur avec climatisation controlée
WO1997025521A1 (fr) * 1996-01-11 1997-07-17 Siemens Aktiengesellschaft Arbre de turbine a vapeur a refroidissement interne

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1098070A1 (fr) * 1999-10-29 2001-05-09 Mitsubishi Heavy Industries, Ltd. Turbine à vapeur à refroidissement amélioré de la carcasse d'enveloppe
US6341937B1 (en) 1999-10-29 2002-01-29 Mitsubishi Heavy Industries, Ltd. Steam turbine with an improved cooling system for the casing
EP2031190A1 (fr) * 2007-08-28 2009-03-04 Siemens Aktiengesellschaft Turbine à vapeur dotée d'une alimentation réglée en agent de refroidissement

Also Published As

Publication number Publication date
DE59711075D1 (de) 2004-01-15
EP0926316B1 (fr) 2003-12-03

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